JET PUMP SYSTEM AND METHOD WITH IMPROVED EFFICIENCY

Abstract

The present disclosure is of a jet pump system, and reverse power generation system and other desirable applications consisting of an impeller with inlet vortex vanes and outlet vortex vanes. The inlet vortex vane induces rotational movement on mass entering the impeller inlet. The outlet vortex vanes remove swirl from mass exiting the impeller outlet. Embodiments include a jet pump system involving a pulley and belt which can allow for obstruction free movement of mass. In another embodiment the impeller is connected via an electromagnetic connection. In another embodiment the impeller acts as a rim-driven generator of electrical power. In another embodiment the drive pulley is a centrifugal clutch or uses a chain sprocket or tandem jet system in series.

Description

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a continuation-in-part of U.S. patent application Ser. No. 17/060,247 filed Oct. 1, 2020, which in turn claims priority to U.S. Provisional Patent Application No. 62/908,805 filed Oct. 1, 2019, both of which are incorporated herein by reference in their entirety.

FIELD OF INVENTION

This disclosure relates generally to a jet pump with improved efficiency.

BACKGROUND

Jet pumps include a motor, an impeller, a jet pump inlet, and a jet pump outlet. The motor causes the impeller of the jet pump to rotate so that fluid from the jet pump inlet is moved to the jet pump outlet. The fluid moves from the jet pump inlet to the jet pump outlet at a rate proportionate to the rotational speed of the impeller. The impeller rotation speed is proportional to the rotational speed of the drive shaft of the jet pump motor. In the prior art jet pumps, the motor output shaft is directly connected to the center axis of the jet pump impeller blades such that when the output shaft rotates, this rotation causes the impeller blades to rotate as well. Connecting the motor output shaft to the impeller in this manner results in an obstruction that causes increase flow resistance of fluid when it enters the impeller. The rotational speed of the motor shaft can be increased to compensate for the increased flow resistance caused by this direct motor output shaft connected to the impeller blades. However, increasing the rotational speed of the motor shaft requires an increase in energy supplied to the impeller, and therefore, decreasing the efficiency to operate the jet pump.

This background information is provided for the purpose of making known information believed by the applicant to be of possible relevance to the present invention. No admission is necessarily intended, nor should be construed, that any of the preceding information constitutes prior art against the present invention.

SUMMARY OF THE INVENTION

It is an object of the present invention to obviate or mitigate at least one disadvantage of the prior art.

An aspect of the present disclosure provides an impeller assembly including an impeller, an inlet vortex vanes, and an outlet vortex vanes. The impeller includes a cylindrical outer housing configured to rotate around a central longitudinal axis. Also, a plurality of blades where each of the plurality of axial blades including an inner edge, an outer edge, a leading edge, and a trailing edge. Each of the plurality of blades is arranged so that the inner edges of the plurality of blades meet at the central axis along a length of the inner edges. Each of the outer ends of the plurality of blades is attached to an inner circumference of the outer housing along a length of the outer edges. A mass flow may pass through each of a plurality of areas formed between adjacent blades of the plurality of blades. Each of the plurality of areas is isolated from another mass flow passing through others of the plurality of areas formed between other adjacent blades of the plurality of blades. Each of the plurality of blades is angled so that the leading edge of one of each of the plurality of blades overlaps the trailing edge of an adjacent one of the plurality of blades thereby preventing the mass flow from passing through each of the plurality of areas without impinging upon one of the plurality of blades.

The inlet vortex vanes are disposed in a coaxial arrangement in front of the impeller from a point of view of the mass flow. The inlet vortex vanes include a plurality of inlet vanes. A trailing edge of each of the plurality of inlet vanes is shaped to match a shape of the leading edge of each of the plurality of blades. The inlet vortex vanes are disposed to minimize a gap between the trailing edge of each of the plurality of inlet vanes and the leading edge of each of the plurality of blades.

The outlet vortex vanes are disposed in a coaxial arrangement to the rear of the impeller from the point of view of the mass flow. The outlet vortex vanes include a plurality of outlet vanes where a leading edge of each of the plurality of outlet vanes is shaped to match a shape of the trailing edge of each of the plurality of blades. The outlet vortex vanes are disposed to minimize a gap between the leading edge of each of the plurality of outlet vanes and the trailing edge of each of the plurality of blades.

In further embodiments, a ratio of a length of the outer edge of each of the plurality of blades to an inner diameter of the outer housing is substantially 0.8.

In further embodiments, the plurality of axial blades includes four blades, the plurality of inlet vanes includes 4 inlet vanes, and the plurality of outlet vanes includes 4 outlet vanes.

In further embodiments, the plurality of inlet vanes are angled to have an angle substantially the same as the angle of the plurality of blades of the impeller in proximity to the leading edge of the plurality of blades.

In further embodiments, the plurality of inlet vanes are angled to minimize the disturbance experienced by the mass flow as it exits the inlet vortex vanes and enters the impeller.

In further embodiments, the plurality of outlet vanes are angled to have an angle substantially the same as the angle of the plurality of blades of the impeller in proximity to the trailing edge of the plurality of blades.

In further embodiments, the plurality of outlet vanes are angled to have an angle to reduce mass disturbance of the mass flow as it exits the impeller and enters the outlet vortex vanes.

In further embodiments, the plurality of outlet vanes are angled to have an angle to direct the trajectory of mass exiting the impeller to minimize swirl.

In further embodiments, wherein the plurality of inlet vanes are stationary.

In further embodiments, the plurality of outlet vanes are stationary.

In further embodiments, wherein the leading edges of the plurality of blades form a pointed shape protruding outward towards the inlet vortex vanes.

In further embodiments, the trailing edges of the plurality of blades form a pointed shape protruding outward towards the outlet vortex vanes.

BRIEF DESCRIPTION OF FIGURES

Embodiments of the present disclosure will now be described, by way of example only, by reference to the attached Figures, wherein:

FIG. 1 illustrates a prior art jet pump with the impeller connected to the motor output shaft.

FIG. 2 illustrates an embodiment of a jet pump where the impeller is connected to a belt, which is in turn connected to the motor output shaft via a drive pulley in accordance with the present disclosure.

FIG. 3 illustrates prior art impeller component with a motor output shaft obstruction.

FIG. 4 illustrates a cut-away front/side view of an embodiment in accordance with the present disclosure.

FIG. 5 illustrates a cross-sectional side view of an embodiment in accordance with the present disclosure.

FIG. 6 illustrates a cut-away front/side view of an embodiment in accordance with the present disclosure.

FIG. 7 illustrates an inlet view of a magnetic rim-drive impeller that can be included in an embodiment in accordance with the present disclosure.

FIG. 8 illustrates a side view of a magnetic rim-drive impeller that can be included in an embodiment in accordance with the present disclosure.

FIG. 9 illustrates a side view of a jet pump that can be included in an embodiment in accordance with the present disclosure.

FIG. 10 illustrates a front view of the inlet, a back view of the outlet, and front view of the impeller, belt and pulley, spaced as if they were encased in the housing of a jet pump that can be included in an embodiment in accordance with the present disclosure.

FIG. 11 illustrates another front-side view of a jet pump embodiment in accordance with the present disclosure.

FIG. 12 illustrates the impeller and belt from a front view of a jet pump embodiment in accordance with the present disclosure.

FIG. 13 illustrates part of the inlet of a jet pump embodiment from a front view in accordance with the present disclosure.

FIG. 14 illustrate part of the outlet of jet pump embodiment from a back view in accordance with the present disclosure.

FIG. 15 illustrates a perspective view of an impeller with a cutaway section in accordance with the present disclosure.

FIG. 16 illustrates a side view of an impeller blade and its parts in accordance with the present disclosure.

FIG. 17 illustrates a cross sectional side view of an impeller in accordance with the present disclosure.

FIG. 18 illustrates a front view of an impeller showing the overlap of impeller blades in accordance with the present disclosure.

FIG. 19 illustrates an exploded, side view of an assembly including an inlet vortex vanes, an impeller, and an outlet vortex vanes in accordance with the present disclosure.

FIG. 20 illustrates a perspective view of an impeller and an inlet vortex vanes with cutaway sections in accordance with the present disclosure.

FIG. 21 illustrates a perspective cutaway view of an inlet vortex vanes and an outlet vortex vanes positioned in a housing in accordance with the present disclosure.

FIG. 22 illustrates a perspective view of a first alternate impeller with a cutaway section in accordance with the present disclosure.

FIG. 23 illustrates a perspective view of a second alternate impeller with a cutaway section in accordance with the present disclosure.

DETAILED DESCRIPTION

In the following description, features of the present disclosure are described by way of example embodiments.

The object of the present embodiments of the disclosure is to provide a jet pump apparatus that can be more efficiently move a mass. The definition of mass can be but is not limited to a fluid, liquid, gas, material, or any mixture.

Embodiments of the present disclosure can reduce the flow disturbance that can be experienced by a mass as it is pumped. Flow disturbance can include velocity fluctuations, asymmetric velocity profiles, swirl, and the like.

Embodiments of the present disclosure can reduce the disturbance applied to the mass as the mass is pumped so that the motion of the mass is smooth.

Embodiments of the present disclosure can include a constant velocity transmission. A person skilled in the art will understand that a constant velocity transmission can be a type of transmission that can maintain a constant speed.

FIG. 1 illustrates a schematic diagram of a prior art jet pump 100 which moves fluid. Motor 170 causes jet pump motor output shaft 110 to rotate. The rotation of jet pump motor output shaft 110 causes impeller blades 180 to rotate. The rotation of impeller blades 180 causes fluid to enter jet pump inlet 140 and then causes the fluid to be pulled into impeller inlet 130. The rotation of impeller blades 180 then causes the fluid that enters impeller inlet 130 to be forced through impeller housing 120 and exit impeller housing 120 at impeller outlet 160. The fluid that exits impeller housing 120 at impeller outlet 160 then exits jet pump 100 at outlet 150.

FIG. 2 illustrates a schematic diagram of an embodiment, jet pump 200. Mass can enter jet pump 200 through inlet 140. Motor 170 can cause jet pump motor output shaft 210 to rotate. The rotation of jet pump output shaft 210 can cause drive pulley 260 to rotate and in turn can cause belt 220 to move. The motion of belt 220 can cause impeller 230 to rotate. The rotation of impeller 230 can cause a mass to enter jet pump inlet 140 and then pull the mass into impeller inlet 240. The rotation of impeller 230 can then cause the mass that entered impeller inlet 240 to be forced through impeller 230 and to exit impeller 230 at impeller outlet 250. The mass that can exit impeller 230 at impeller outlet 250 can then exit jet pump 200 at outlet 150.

FIG. 3 illustrates a schematic diagram of a prior art impeller 300. Impeller blades 180 are connected to jet pump motor output shaft 110 via bearing 330. A drawback of connecting impeller blades 180 to output shaft 110 in this way is that output shaft 110, bearing 330, and seal 310 are directly in the path of mass entering impeller inlet 130. Therefore, output shaft 110, bearing 330 and seal 310 obstruct the flow of mass entering impeller inlet 130.

FIGS. 4, 5, and 6 each illustrate different views of embodiments of this disclosure that can overcome the prior art obstruction problem previously described and due to the presence of output shaft 110, bearing 330 and seal 310. In an attempt to overcome this obstruction problem, belt 220, which causes impeller 230 to rotate, is connected to impeller 230 and therefore does not obstruct the flow of mass entering impeller inlet 240. Therefore, this belt can be outside the path of mass entering the impeller inlet such that the impeller inlet can be obstruction free. As a result, impeller 230 can be more efficient than the prior art impeller 300 because prior art impeller 300 can require more energy to transfer the same amount of mass from jet pump inlet 140 to outlet 150. More energy is required by prior art impeller 300 because motor 170 may cause output shaft 210 to rotate less efficiently in order to compensate for the obstruction created by the prior art jet pump motor output combination of shaft 110, bearing 330, and seal 310. The embodiments illustrated by FIGS. 4, 5, and 6 can include a non-limiting example of an arrow-shaped impeller that can be designed to reduce resistance to movement of mass. However, other embodiments can comprise one or more differently shaped impellers that can alter the movement of mass differently than an arrow-shaped impeller.

FIG. 4 illustrates impeller 230 and its connection to motor output shaft 210. Inlet vortex vanes 410 can be placed and designed to direct mass that enters pump inlet 140 so that this mass can enter impeller 230 at an angle that is matched optimally to the angle of impeller blades 420. The shape, angle, and number of the inlet vortex vanes 410, the outlet vortex vanes 470, and impeller blades 420 can be varied. Embodiments can include inlet vortex vanes 410 with different optimal angles, the outlet vanes 470 with different optimal angles and impeller blades 420 with different optimal angles. In some embodiments, the optimal angles of the inlet vortex vanes 410, outlet vanes 470, and impeller blades 420 can be the same optimal angle. In other embodiments the optimal angles of the inlet vortex vanes 410 can be different from the optimal angles of outlet vanes 470, which can be different from the optimal angles of impeller blades 420. The optimal angle can be varied depending on numerous factors that include but are not limited to: 1) speed of rotation, 2) the type of mass and its properties, 3) the application of the embodiment, and 4) operational environment.

In one embodiment the angle of the impeller blade 420 matches the optimal angle of the mass flow that impinges on the impeller blades 420, and can result in more of the mass remaining disturbance free as it enters impeller 230. Mass or fluid that is disturbance free can result in more mass entering impeller 230 than fluid entering prior art impeller 300 when the impeller rotational speed is the same for impeller 230 and prior art impeller 300.

In the inlet 140, the Inlet vortex vanes 410 can be stationary and can be attached to the stationary inlet housing 430. In the outlet 150, the outlet vortex vanes 470 can be stationary and can be attached to the stationary outlet housing 440. The impeller 230 can rotate within the main housing 400.

FIG. 5 illustrates a cross-section schematic diagram of impeller 230 in a view that shows impeller 230's outlet. Inlet vortex vanes 410 can be placed and can be designed to allow an increase the amount of mass entering impeller 230 by minimizing the amount of disturbance of the mass. Inlet vortex vanes 410 can also cause the movement of mass entering impeller 230 to rotate in a direction that is opposite to the direction of the rotation of impeller 230. As the mass moves through impeller 230, the movement of the mass may be disturbed. In order to reduce the amount of mass disturbance, outlet vortex vanes 470 can be placed and designed so they can match the optimal angle of impeller blades 420. Outlet vortex vanes 470 can also direct the trajectory of the movement of mass exiting the impeller to minimize swirl. Designing and placing outlet vortex vanes 470 to reduce mass disturbance and reduce swirl can result in an increase the movement of the mass exiting the impeller 230. Increasing the amount of disturbance free mass movement can increase the movement of mass that exits impeller 230 when compared to the prior art impeller 300 for the same impeller rotational speed, shape, and size.

Due to the design and placement of inlet vortex vanes 410 and outlet vortex vanes 470, more of the mass that enters and exits impeller 230 can be disturbance-free. This improvement in the movement of mass can allow impeller 230 to rotate more slowly than prior art impeller 300 while moving the same amount of mass. Slower impeller rotation can be desirable for numerous reasons including for increase efficiency. Slower impeller rotation can mean less energy is required by motor 170 to rotate impeller 230 than prior art impeller 300 and therefore inlet vortex vanes 410 and outlet vortex vanes 470 can result in impeller 230 being more energy efficient than prior art impeller 300.

FIG. 6 illustrates a schematic diagram of impeller 230 in a view that shows embodiment impeller 230 from the side.

Referring back to FIG. 3, prior art impeller 300 can require wear ring 340 to act as a spacer between impeller blades 180 and impeller housing 120. However, wear ring 340 can result in gap 320 between impeller blades 180 and wear ring 340. Gap 320 causes a communication between high pressure outlet of the impeller 160 and 150 and inlet 130 and 140. This communication results in a reduction of performance and thrust due to less total fluid being removed because of movement backwards through the gap. This reduction of performance is known to a person skilled in the art as a loss of traction. A loss of traction can occur because gap 320 allows fluid to enter impeller 300 at a different speed than the fluid that enters impeller 300 via impeller blades 180. Fluid that enters impeller 300 at different speeds is known to a person skilled in the art as slippage. Slippage can decrease the efficiency of impeller 300. Therefore, impeller blades 180 must be rotated at a higher speed to reduce the effect of slippage and loss of traction.

Connecting impeller 230 to motor output shaft 210 via belt 220 can allow wear ring 340 to be replaced with bearing 450 and seal 460. Therefore impeller 230 can rotate within inlet housing 430 via bearing 450 and seal 460. A person skilled is the art will appreciate that the tip of an impeller blade can refer to the end of impeller blade 420 that can attach to all other impeller blades 420. The person skilled in the art will further appreciate that the other end of impeller blade 420 can attach to the impeller housing. Replacing wear ring 340 with bearing 450 and seal 460 can remove gap 320 with the result that impeller 230 experiences less slippage than prior art impeller 300. Since impeller 230 can have reduced slippage, impeller 230 can be more efficient than prior art impeller 300 and can rotate at a slower speed than prior art impeller 300 while moving the same amount of mass. Therefore impeller 230 can be efficient at slow and medium speeds where prior art impeller 300 must be rotated at higher speed in order to be efficient. Again, rotating impeller 230 at a slower speed than prior art impeller 300 can result in motor 170 requiring less energy to rotate impeller 230 than the amount of energy required to rotate prior art impeller 300. The impeller 230 with the impeller blade 420 can be attached in such a way as to replace the need to have a wear ring 340.

In another embodiment in accordance with the present disclosure, the pulley can be replaced with a centrifugal clutch. A centrifugal clutch can allow the speed of motor output shaft 210 to rotate at its peak operating speed and impeller 230 to rotate at a slower speed. A person skilled in the art will understand that the centrifugal clutch also allows for the extension of the pump efficiency curve to a broader range of speeds so that the speed of impeller 230 can be increased. A pump's efficiency curve can be used by a person skilled in the art to determine a pump's ability to produce a given flow rate (by setting the impeller's speed) at a certain head pressure. The use of a centrifugal clutch therefore can allow the motor to operate at its peak operating speed and the impeller to operate at a speed that meets a desired efficiency based on flow rate and head pressure.

In another embodiment impeller 230 can be used as a generator of energy. Mass can be supplied to impeller 230's inlet to causes impeller 230 to rotate. The resulting rotation of impeller 230 will cause output shaft 210 to rotate and rotate the winding of a generator (not shown) to generate electrical power. Impeller 230's higher efficiency than prior art impeller 180 can mean that impeller 230 can generate more energy for a given flow of mass than prior art impeller 300.

FIG. 7 illustrates an alternate magnetic-rim drive impeller 710 embodiment that can be included in an axial electric jet pump embodiment or other embodiment of the present disclosure. This alternative magnetic-rim-drive setup 700 can be include in an embodiment and can replace the impeller 230, belt 220, drive pulley 260, shaft 210, or motor 170. The magnetic-rim drive impeller 710 can include magnets 750, and magnetic-rim drive impeller blades 730. It can be housed in a magnetic-rim drive impeller housing 720 that can include windings 760 so that magnetic-rim drive impeller 710 of this embodiment can act as a rotor. The magnetic-rim drive impeller housing 720 can act as a stator of an electric motor. Unlike prior art that uses a shaft in flow, this embodiment can use a rim drive design to generate thrust.

The electromagnetic rim-drive setup 700 illustrated by FIG. 7 can included an embodiment where the wear ring (not shown) found in prior art axial electric jet pumps can be removed so that more magnetic rim-drive impeller blades 730 are driven by incoming mass entering magnetic rim-drive impeller 710 through inlet vortex vanes 410 (not shown) than prior art impeller blades 180. Therefore, if the magnetic-rim drive setup 700 is included in an embodiment in accordance with the present disclosure, the embodiment can be more efficient and can be smaller and lighter than prior art axial electric pumps or hydro generators.

Removal of a wear ring in an embodiment including the magnetic rim-drive setup 700 illustrated in FIG. 7 can allow the hub/bearing/seals 740 to be placed between the magnetic-rim drive impeller 710 and magnetic-rim drive housing 720.

The magnetic rim-drive setup 700 embodiment illustrated by FIG. 7 can also be configured and included in an embodiment to operate is a hydro generator. When operating as a generator, magnetic-rim drive impeller 710 can act as a rotor and the magnetic rim-drive impeller housing 720 can be the stator of the generator. These features can be applied to other possible embodiments as generally illustrated in FIGS. 4, 5 and 6, where impeller 420 can transmit rotation force to a shaft via a drive belt 220 to rotate a generator.

The size, angle, and shape of magnetic rim-drive impeller blades 730 can be optimized to move mass through this embodiment more efficiently or to achieve other desirable effects than the prior art. These desirable effects can be achieved using inlet vortex vanes to induce incoming mass movement at an optimum angle of attack to impeller blades for hydro generation.

A person skilled in the art will understand that obstructive mass can enter the impeller to cause blockage to the movement of mass through the jet pump system. As a result, this embodiment, in accordance with the present disclosure is designed so that impeller 710 can rotate in either a clockwise or counterclockwise direction to clear obstructive mass from the jet pump system.

FIG. 8 illustrates the side view of the axial electric jet pump with a magnetic rim-drive setup 700 that can be included in an embodiment. Mass can enter impeller 710 at magnetic-rim drive inlet 820 and exit at magnetic-rim drive outlet 810.

Embodiments of the present disclosure can operate when submerged in a mass. Other embodiments of the present disclosure can operate when not fully submerged in a mass. Non-limiting examples of applications where submerged and also not fully submerged embodiments can include propulsion, hydro generation, and circulation.

Other embodiments in accordance with the present disclosure can include a chain sprocket system embodiment or a Tandem jet pump system in series embodiment.

In a Tandem jet pump system there can be two jet pumps in series. The impeller housing of the second jet pump can be installed downstream of the outlet of the first jet pump. A reason to install the impeller of the second jet pump down-stream of the outlet of the first jet pump can be to eliminate or counteract rotational torque. A possible result therefore can be to reduce the torque when the first jet pump rotates the mass in one direction and the second jet pump rotates the mass in the opposite direction. Non-limiting examples of torque can any combination of the torque of the first jet pump, the second jet pump, the mass exiting the second jet pump or the like.

FIG. 9 illustrates an exploded side view of a jet pump that can be included in an embodiment.

FIG. 10 illustrates a front view of the inlet, a back view of the outlet, and front view of the impeller, belt, and pulley, spaced as if they were encased in the housing of a jet pump that can be included in an embodiment.

FIG. 11 illustrates a perspective, front-side view of a jet pump embodiment in accordance with the present disclosure.

FIG. 12 illustrates an impeller and belt from a front view of a jet pump according to an embodiment.

FIG. 13 illustrates part of the inlet of a jet pump embodiment from a front view.

FIG. 14 illustrate part of the outlet of jet pump embodiment from a back.

FIG. 15 illustrates a perspective view of an impeller 230 with a cutaway section to illustrate the curved nature of blades 420 of the impeller, according to an embodiment. As illustrated, inner edges 282 of each blade 420 meet along a central axis of the impeller and the inner edges 282 of each blade is attached along an entire length of the inner edges 282. As well, the outer edges 282 of each blade 420 are attached to an inner circumference of the outer housing along a length of the outer edges thereby ensuring that the entirety of a mass flow passing through the impeller passes through the areas created between adjacent blades.

FIG. 16 illustrates a side view of an impeller blade 420 as used in embodiment. Impellers include a plurality of blades 420. Four blades 420 are illustrated in FIG. 15 and other figures included herein, however other embodiments may have more or less blades, such as three blades or five blades. Each blade 420 may be viewed as having a plurality of edges. As illustrated, blade 420 includes a leading edge 280, a trailing edge 281, an inner edge 282, and an outer edge 283. Inner edges 282 of blades meet at the central axis of the impeller 230 without a central hub or a minimal central hub that may be required to ensure structural integrity of the impeller. In other words, the length of the inner edges 282 meet together in the center of the impeller. Outer edges 283 of the impeller are attached along their lengths to an inside surface of a cylindrical outer housing of the impeller. As the inner edges 282 and the outer edges are connected at the center and to the outer housing, the areas between edges 420 create a plurality of separate areas isolated from each other from the point of view a mass flow passing through the impeller 230. In other words, once a portion of the mass flow enters the impeller from the front (at the leading edge 280) and enters one of the areas between adjacent blades, it exits the impeller through the rear (at trailing edge 281) without mixing with other portions of the mass flow that are passing through other areas.

FIG. 17 illustrates a cross sectional side view of an impeller, according to an embodiment. Leading edges 280 of the impeller 230 blades form a pointed shape at the front of the impeller, in a direction to meet the mass flow as it enters the impeller. Trailing edges 281 form a flat shape on the rear of the impeller. It can be seen that the length of the cylindrical outer housing may substantially be the same length as the length of the outer edges 283 of the impeller blades whereby a shorter housing results in shorter blades and a longer housing results in longer blades.

FIG. 18 illustrates a front view of an impeller showing the overlap of impeller blades, according to an embodiment. When viewed from the front the leading edges 280 of each blade may have a curved shape. And curve backwards in a clockwise direction, where the trailing edge 281 of each blade may have a substantially straight edge. It can be seen that the leading edge of one blade overlaps the trailing of an adjacent edge in the counterclockwise direction. In this way, there does not exist a straight path for a mass flow to enter the front of the impeller and exit the rear of the impeller and the mass flow is required to contact a front facing face of each impeller blade. It is also clear that the overlapping of adjacent blades may be in the clockwise or counterclockwise direction and that the angle of each blade will determine the direction in which the impeller turns. Furthermore, as the length of the cylindrical outer housing may determine the length of the outer edges 283 and the inner edges 282 of the impeller, and that the leading edge of each of the plurality of blades overlaps the trailing edge of an adjacent blade, the length of the outer housing also affects the angle of each of the blades. In other words, if the outer housing has a long length, the angle of each blade will be angled to span the distance between blades over the longer length. Also, if the outer housing has a short length, the angle of each blade must be sharper in order to span the distance between blades over the shorter length. In both cases, a long length or a short length, the front view of the impeller as illustrated in FIG. 18 will look substantially the same, with no direct front to back passage through the impeller for a mass flow flowing through the impeller.

FIG. 19 illustrates an exploded, side view of an assembly including an inlet vortex vane, an impeller, and an outlet vortex vanes, according to an embodiment. The shape formed by the leading edges 280 of the impeller may be shaped to match the shape of trailing edges of the inlet vanes. In this case, the pointed or arrow shape of the leading edges of the impeller meet the inverted arrow shape of the trailing edges of the inlet vortex vanes. As well, the shape formed by the trailing edges 281 of the impeller may be shaped to match the shape of trailing edges of the inlet vanes. In this case, the flat shape of the trailing edges of the impeller can meet the flat shape of the leading edges of the outlet vortex vanes. It should be noted that FIG. 19 shows an exploded view of the three components; the impeller 230, the inlet vortex vanes 410, and the outlet vortex vanes 470, and therefore the three components are spaced apart for clarity. However, in embodiment, the three components may be places in close proximity, along the same central axis, in order to minimize the distance between the three components of the assembly, which may reduce turbulence and improve the efficiency of the impeller assembly.

In embodiments, the inlet vortex vanes 410 and the outlet vortex vanes 470 may be stationary with respect to the overall housing 140 and 150 of the impeller assembly while the impeller 230 may rotate within the housing formed by jet pump inlet 140 and jet pump outlet 150.

FIG. 20 a perspective view of an impeller and an inlet vortex vanes 410 with cutaway sections, according to an embodiment. FIG. 20 illustrates how the number, angle, or curve of the inlet vortex vanes can be made to match the number, angle, or curve of the impeller blades 420 in order to direct an incoming mass flow into the impeller and the areas between impeller blades. Depending on characteristics of the mass flow, such as the velocity or viscousness, it may be desirable to design the angle of the inlet vortex vanes and the angle of the impeller blades (partially determined by the length of the cylindrical housing) to obtain a particular turbulence or vortex of the mass flow.

FIG. 21 a perspective cutaway view of an inlet vortex vanes 410 and an outlet vortex vanes 470 positioned in a housing, according to an embodiment. In embodiment the inlet vortex vanes 410 and the outlet vortex vanes 470 may be fixed in place within the housing and not rotate.

In embodiments, the number, angle, or curve of the outlet vortex vanes 470 can be made to match the number, angle, or curve of the impeller blades 420 in order to remove some or all of a rotational movement (i.e., “twist”) imparted to the mass flow by the inlet vortex vanes 410 and the impeller. As such the shape of leading edges of the outlet vortex vanes 470 may be designed to match the shape of the trailing edges 281 of the impeller blades 420 and to minimize a gap between the components in the axial direction. Similarly, the number, angle, or curve of the outlet vortex vanes 470 may be designed taking into account the number, angle or curve of the impeller blades.

Embodiment may work bi-directionally. That is that an impeller, impeller assembly, or jet pump may accept a mass flow from either end. In these embodiments, the shape of the leading edges 280 and the trailing edges 281 of the impeller 230 may be modified to work equally well with a mass flow flowing in either direction. As well, the matching trailing edges of the inlet vortex vanes 410 and the outlet vortex vanes 470 may be similarly modified to match the shape of the impeller blades and reduce axial gaps between the impeller 230, the inlet vortex vanes 410, and the outlet vortex vanes 470. As an alternative to the impeller of FIG. 15 and FIG. 17, impellers as illustrated in FIG. 22 or FIG. 23 may be used with associated modifications to the inlet vortex vanes 410, and the outlet vortex vanes 470 for bi-directional applications. FIG. 22 illustrates a perspective view of a first alternate impeller with pointed leading edges and trailing edges while FIG. 23 illustrates a perspective view of a second alternate impeller with flat leading edges and trailing edges.

An aspect of the present disclosure provides a jet pump system. This jet pump system can comprise an impeller, inlet vortex vanes, and outlet vortex vanes.

In some embodiments of the jet pump, the impeller can be attached to a drive pulley by a belt. The drive pulley can be in turn connected to the output shaft of a motor so that when the motor causes the output shaft to rotate the output shaft can also cause the drive pulley to rotate. Rotation of the drive pully can in turn cause the belt to move and can in turn cause the impeller to rotate.

In some embodiments of the jet pump, the impeller can be electromagnetically connected to a housing.

In some embodiments of the jet pump, energy applied to the housing electromagnetically can cause the impeller to rotate.

In some embodiments of the jet pump, the rotation of the impeller by the mass entering the impeller can cause the housing to act as a generator of electrical power.

In some embodiments of the jet pump, the inlet vortex vanes of the impeller can direct mass that enters the jet pump to an angle matching the optimal angle of blades of the impeller.

In some embodiments of the jet pump, the inlet vortex vanes and the lack of an impeller shaft can remove a flow obstruction and can improve efficiency and can remove the source of a flow disturbance that can be caused by the obstruction. Removing the obstruction can result in a smooth mass flow striking the impeller at an optimum angle of attack and can create more thrust for a given impeller size and shape to motor output power ratio.

In some embodiments of the jet pump, the inlet vortex vanes of the impeller can cause a mass that enters the impeller to rotate in a direction that is opposite to the direction of rotation of the impeller.

In some embodiments of the jet pump, the outlet vortex vanes of the impeller can increase the flow of the mass and can also reduce flow swirl at the exit of the jet pump system.

In some embodiments of the jet pump, the outlet vortex vanes of the impeller can be matched to the optimal angle of the impeller blades.

In some embodiments of the jet pump, the outlet vortex vanes of the impeller can direct the trajectory of mass exiting the impeller to minimize swirl.

In some embodiments of the jet pump, the impeller can be connected to an impeller housing by a bearing and a seal and a retaining device.

In some embodiments of the jet pump, the output shaft of the motor can be connected to the drive pulley by a centrifugal clutch or constant velocity transmission.

A further aspect of the present disclosure provides a method of a jet pump system. The mass pumped by the jet pump system can enter the jet pump system through inlet vortex vanes and then can pass through an impeller and then can pass through outlet vortex vanes to exit the jet pump system.

In some embodiments of the jet pump system, the outlet vortex vanes can remove swirl at the exit the jet pump system.

Although the present disclosure has been described with reference to specific features and embodiments thereof, it is evident that various modifications and combinations can be made thereto without departing from the disclosure. The specification and drawings are, accordingly, to be regarded simply as an illustration of the invention as defined by the appended claims, and are contemplated to cover any and all modifications, variations, combinations or equivalents that fall within the scope of the present disclosure.

Claims

1. An impeller assembly comprising:

an impeller including; a cylindrical outer housing configured to rotate around a central longitudinal axis; a plurality of blades, each of the plurality of axial blades including an inner edge, an outer edge, a leading edge, and a trailing edge, each of the plurality of blades arranged so that the inner edges of the plurality of blades meet at the central axis along a length of the inner edges, each of the outer ends of the plurality of blades f; wherein a mass flow passing through each of a plurality of areas formed between adjacent blades of the plurality of blades is isolated from another mass flow passing through others of the plurality of areas formed between other adjacent blades of the plurality of blades; and wherein each of the plurality of blades is angled so that the leading edge of one of each of the plurality of blades overlaps the trailing edge of an adjacent one of the plurality of blades thereby preventing the mass flow from passing through each of the plurality of areas without impinging upon one of the plurality of blades;

an inlet vortex vanes disposed in a coaxial arrangement in front of the impeller from a point of view of the mass flow, the inlet vortex vanes including a plurality of inlet vanes, a trailing edge of each of the plurality of inlet vanes shaped to match a shape of the leading edge of each of the plurality of blades, the inlet vortex vanes disposed to minimize a gap between the trailing edge of each of the plurality of inlet vanes and the leading edge of each of the plurality of blades; and

an outlet vortex vanes disposed in a coaxial arrangement to the rear of the impeller from the point of view of the mass flow, the outlet vortex vanes including a plurality of outlet vanes, a leading edge of each of the plurality of outlet vanes shaped to match a shape of the trailing edge of each of the plurality of blades, the outlet vortex vanes disposed to minimize a gap between the leading edge of each of the plurality of outlet vanes and the trailing edge of each of the plurality of blades.

2. The impeller assembly of claim 1 wherein a ratio of a length of the outer edge of each of the plurality of blades to an inner diameter of the outer housing is substantially 0.8.

3. The impeller assembly of claim 1 wherein the plurality of axial blades includes four blades, the plurality of inlet vanes includes 4 inlet vanes, and the plurality of outlet vanes includes 4 outlet vanes.

4. The impeller assembly of claim 1 wherein the plurality of inlet vanes are angled to have an angle substantially the same as the angle of the plurality of blades of the impeller in proximity to the leading edge of the plurality of blades.

5. The impeller assembly of claim 1 wherein the plurality of inlet vanes are angled to minimize the disturbance experienced by the mass flow as it exits the inlet vortex vanes and enters the impeller.

6. The impeller assembly of claim 1 wherein the plurality of outlet vanes are angled to have an angle substantially the same as the angle of the plurality of blades of the impeller in proximity to the trailing edge of the plurality of blades.

7. The impeller assembly of claim 1 wherein the plurality of outlet vanes are angled to have an angle to reduce mass disturbance of the mass flow as it exits the impeller and enters the outlet vortex vanes.

8. The impeller assembly of claim 1 wherein the plurality of outlet vanes are angled to have an angle to direct the trajectory of mass exiting the impeller to minimize swirl.

9. The impeller assembly of claim 1 wherein the plurality of inlet vanes are stationary.

10. The impeller assembly of claim 1 wherein the plurality of outlet vanes are stationary.

11. The impeller assembly of claim 1 wherein the leading edges of the plurality of blades form a pointed shape protruding outward towards the inlet vortex vanes.

12. The impeller assembly of claim 1 wherein the trailing edges of the plurality of blades form a pointed shape protruding outward towards the outlet vortex vanes.