System for the heating and pumping of fluid

A fluid heating and pumping system comprising a housing that has an inlet and outlet opening as well as a plurality of turbine chambers. Each of the turbine chambers has: an inlet end, outlet end, is mounted to a driveshaft, a stator and rotor, and is constructed to create a circuitous flow path for fluid flow. Each of the rotors is: designed to move the fluid through the housing, and has a plurality of rotor vanes with each having a fin at the inlet end. The fin extends past the plane of an adjacent rotor vane to extend the circuitous flow path through the rotors. The fins, shearing plane, and outlet orifice all create thermal energy as the fluid is transferred along and between the rotor and stator vanes, through the shearing plane and between the adjacent turbine chambers as the fluid flows.

BACKGROUND

Typical water heating devices can be costly, hard to move, unreliable, and hazardous because these water heating devices have large tanks for storing stagnated water that use electric coils or burning apparatuses that cause the devices to break down easily. The system for heating and pumping fluid described hereafter is a durable, reliable, cost effective, and less hazardous alternative to the traditional water heating device on the market today.

SUMMARY

A fluid heating and pumping system comprising a housing having an inlet opening and an outlet opening and a plurality of turbine chambers within the housing. Each of the turbine chambers has an inlet end and an outlet end. Each of the turbine chambers comprises a stator and a rotor both of which are centered on an axis of rotation. Each of the turbine chamber rotors is mounted to a driveshaft. The driveshaft rotates about the axis of rotation. Each of the turbine chambers is constructed to create a circuitous flow path for fluid flow. A separating plate is located between the adjacent turbine chambers, the separating plate has at least one separating plate orifice through which fluid can flow between adjacent turbine chambers. Each of the rotors is designed to move the fluid axially or radially through the housing. Each of the rotors has a plurality of rotor vanes with each of the rotor vanes having a fin at the inlet end. The fin extends past the plane of an adjacent rotor vane to extend the circuitous flow path through the rotors. Each of the stators has a plurality of axially extending stator vanes. The rotors and stators are sized and mounted to form a shearing plane between them. Each of the stators has an end member with at least one outlet orifice situated at the outlet end to allow fluid to flow through at least one opening in an adjacent separating plate orifice. The fins, shearing plane, and outlet orifice create thermal energy as the fluid is transferred along and between the rotor vanes and stator vanes, through the shearing plane and between the adjacent turbine chambers as the fluid flows circuitously from the inlet opening to the outlet opening.

In some embodiments the fluid heating and pumping system, each of the rotor vanes could have a plurality of rotor orifices through which fluid can pass to further increase the thermal energy generated as the rotor rotates. The fluid heating and pumping system could have three turbine chambers within the housing. The fluid heating and pumping system could also further comprise an outlet opening that is perpendicular to the axis of rotation and have a turbine chamber that is positioned closest to the outlet opening, within the housing, be an outlet chamber that is designed to move the fluid radially through the outlet opening.

The fluid heating and pumping system could further comprise an outlet opening that is perpendicular to the axis of rotation and have a turbine chamber positioned closest to the outlet opening, within the housing, be an outlet chamber that has rotor vanes mounted both radially and parallel to the axis of rotation such that the fluid flows through the outlet opening. The fluid heating and pumping system could further comprise at least one of the turbine chambers having each of the rotor vanes and each of the stator vanes mounted at compound angles such that the axial length of each of the rotor vanes and stator vanes are at an acute angle with respect to the axis of rotation and the radial length of each of the rotor vanes and stator vanes are tilted at a second angle with respect to the surface of the drive shaft. The fluid heating and pumping system could have the inlet opening and the outlet opening both be mounted such that they extend perpendicular to the axis of rotation. The fluid heating and pumping system can have an outlet opening that is mounted parallel to the axis of rotation.

Those skilled in the art will realize that this invention is capable of embodiments that are different from those shown and that details of the devices and methods can be changed in various manners without departing from the scope of this invention. Accordingly, the drawings and descriptions are to be regarded as including such equivalent embodiments as do not depart from the spirit and scope of this invention.

DETAILED DESCRIPTION

Referring to the drawings, some of the reference numerals are used to designate the same or corresponding parts through several of the embodiments and figures shown and described. Corresponding parts are denoted in different embodiments with the addition of lowercase letters. Variations of corresponding parts in form or function that are depicted in the figures are described. It will be understood that variations in the embodiments can generally be interchanged without deviating from the invention.

Effective fluid heating and pumping is possible with the embodiment described herein and shown inFIG. 1. A fluid heating and pumping system10comprises an actuator12that is mounted to a housing having an inlet housing14and an outlet housing16. Typically, the inlet housing14has an inlet opening18, perpendicular to the axis of rotation38, through which the fluid enters the system10. However, the inlet housing14could have an inlet opening18that is parallel to the axis of rotation38. The fluid, to be heated, is part of a closed loop system in which the fluid, typically water, is continuously recycled through the system10and slowly heated up to a desired temperature. A thermostat, thermocouple, or other temperature sensitive feedback device may be incorporated into the system10to regulate when the system is turned off or on as required by the particular application.

The outlet housing16has an outlet opening20, perpendicular to the axis of rotation38, from which heated fluid can leave the system10. Both the inlet opening18and the outlet opening20have a variety connection options (not shown) such as but not limited to: quick disconnects, threaded ends, or flanges to connect to the system. The inlet housing14has a flange22which lines up to a corresponding flange24on the outlet housing16. The flanges22and24are joined by a plurality of fastening devices26such as nuts and bolts to form a leak-proof seal. A rubber gasket or other sealing feature could be incorporated between the flanges22and24to provide additional leak protection. In the embodiment shown in the figures, the inlet housing14and outlet housing16are joined to align the inlet opening18and outlet opening20so that fluids enter and leave the system10vertically. Generally, the system10is made of stainless steel or any non-corrosive material that is strong enough to withstand long term use.

The actuator12provides power to the entire system10and could be any drive system that will rotate the shaft. The actuator12can be releasably joined to a drive shaft28that runs through the center of the inlet housing14and the outlet housing16as well as rotates around an axis of rotation38. The actuator unit12forces the drive shaft28to rotate continuously and at a torque that is powerful enough to rotate the inner components of the system10(described in more detail below) through the viscosity of fluids flowing circuitously between the inlet opening18and the outlet opening20. A steel rod approximately ⅔ inch in diameter was found to be sufficient for a drive shaft28in the preferred embodiment of this system.

The inner workings of the system10for heating and pumping fluid is best understood by referring generally toFIGS. 2, 3, and 4. The inlet housing14has a cylindrical ball bearing joint30that supports the drive shaft28for rotating about the axis of rotation38. The drive shaft28has a sealing member32that locks into the ball bearing joint30to provide a leak proof seal between the inlet housing14and the drive shaft28. Fluid to be heated enters the inlet housing14through the inlet opening18and it subsequently passes directly into the outlet housing16. The sealing member32blocks any fluid from leaking out through the ball bearing joint30. The inlet housing14also has a collar15that helps to move the fluid flow from the inlet opening16to nearest turbine chamber34as well as prevent backflow of the fluid from the inlet opening16. However, the collar15is not necessary in all embodiments of the system such as embodiments where the inlet opening is parallel to the axis of rotation38).

Within the outlet housing16are located a plurality of turbine chambers34that each have an inlet end and an outlet end. These turbine chambers34include a single outlet chamber36that is positioned closest to the outlet opening20such that it is just below the outlet opening20within the outlet housing16. The actual number of turbine chambers34can vary with the particular application, but the preferred embodiment is as shown in the figures with two turbine chambers34and a third outlet chamber36although it will be understood that any number of turbine chambers34would also be effective. The turbine chambers34and the outlet chamber36are all centered on an axis of rotation38that runs through the drive shaft28. Each of the turbine chambers34comprises a fixed stator40around a rotor42, that is mounted to the drive shaft28, both of which are also centered on the axis of rotation38. Except for the outlet chamber36, the turbine chambers34are constructed to create a circuitous flow path for fluid flow. The outlet chamber36also has its own fixed stator44and rotor48both of which are centered on the axis of rotation38, but, as will be described in more detail below, they are configured differently than the stators40and rotors42of the turbine chambers34depending on the orientation of the outlet opening20.

As will be explained in more detail below, the angled shape of the rotors42in each turbine chamber34forces fluid from the inlet opening18through the circuitous path as shown inFIG. 3. Thus, except for the outlet chamber36, the turbine chambers34are constructed to create a circuitous flow path for fluid flow. The outlet chamber36is designed to move the fluid radially within the outlet housing16. The rotor vanes52, as discussed in more detail below, in the outlet chamber36are mounted both radially and parallel to the axis of rotation38. This movement of fluid causes pressure to build up within the outlet chamber38giving the fluid nowhere to go except through the outlet opening20to leave the system10.

As can be seen inFIG. 4, a guiding ridge50(in the preferred embodiment a thin wire of metal) is permanently attached to the inside of the outer housing16. The guiding ridge50provides a means against which the non-moving parts of the system10can be located and held in place within the outlet housing16. As will be shown below, each of the non-moving parts in the system have corresponding divots that line up with the guiding ridge50.

As can be best understood by comparingFIGS. 4 through 6C, the rotors42and48are each permanently joined to the drive shaft28so they are made to turn with the drive shaft28.FIG. 5Bshows the drive shaft28as seen from the actuator12and shows the sealing member32and rotor42of the first turbine chamber34.FIG. 5Cshows a view of the drive shaft28as seen from the outlet housing16.

With respect to the turbine chambers34, each of the rotors42has a plurality of rotor vanes52. Depending on whether the fluid is in a turbine chamber34or outlet chamber36, the rotors34are designed to move the fluid axially or radially through the outlet housing16. As more clearly shown inFIGS. 6A, 6B, and 6C, the rotor vanes52of the turbine chamber34are mounted neither perpendicular nor parallel to the axis of rotation38but: 1) form a tilted angle with respect to the axis of rotation38; and 2) the radial length of each of the rotor vanes52is not parallel with the drive shaft28but is tilted at a second angle with respect to the drive shaft28. At the inlet end of the turbine chamber34, each rotor vane52is bent into a fin54that extends past the plane of an adjacent rotor vane52. As shown inFIG. 3, this extends the circuitous flow path of fluid through the rotor42area. Each rotor vane52bends into an end barrier56at its outlet end. As shown inFIG. 2, a plurality of orifices58are drilled each rotor vane52.

The shape of the fin54in combination with axial and radial angles of the rotor vanes52is such that when the actuator12rotates the drive shaft28, fluid is forced to flow in an axial direction from the inlet opening18to the outlet opening20. The effect of the fins54and the angles of the rotor vanes52creates a fluid vortex that propels the fluid forward in an annular path of motion.

The angles of the rotor vanes52are best understood by comparingFIGS. 7A and 7B. The compound angles of the rotor vanes52are best understood with reference to the construction of the rotor42, the individual rotor vanes52, fins54, and the end barriers56. Each rotor vane52is formed from a single strip of sheet metal that is bent to form a fin52and its own portion of the end barrier56. At the inlet end of the rotor52, the single strip of sheet metal is bent at an angle X with respect to the rotor vane52to form a fin54. In the illustrated embodiment the angle X is 104.5 degrees. At the opposite end of the strip, the sheet metal is bent in the opposite direction at an angle Y to form a portion of the end barrier56of the rotor42. As best seen inFIG. 4, the fin54is cut to a length that enables it to extend past the plane of an adjacent rotor vane52and is shaped to fit tightly around the drive shaft28. All of the fins54together extend the circuitous flow path of the fluid from the inlet end of their respective rotor42and through their respective turbine chamber34. The end barrier portion56is also cut to engage an adjacent rotor vane52and fit tightly around the drive shaft28.

As is evident inFIG. 7A, the axial length of the rotor vane52is installed at a tilted angle Y to the axis of rotation38. The end barrier56is perpendicular to the axis of rotation38. In the embodiment illustrated inFIG. 7A, the rotor vane52is installed at an angle Y 193.5 degrees with respect to the axis of rotation38. Referring toFIG. 7B, the radial length of the rotor vane52is tilted with respect to the drive shaft28. In the end, the rotor vanes52on at least one of the rotors42are mounted at compound angles such that the axial length of each of the rotor vanes52is at an acute angle with respect to the axis of rotation38and the radial length of each of the rotor vanes52is tilted at a second angle with respect to the surface of the drive shaft28.

Once the plurality of rotor vanes52are formed with their fins54and end barriers56, an equal number of straight, parallel, shallow grooves (sometimes called script marks), are carved on the drive shaft28at the angle J (which represents the supplementary angle to angle Y) for the purpose of guiding where the rotor vanes52are to be mounted onto the drive shaft28. The preformed rotor vanes52are then inserted to fit tightly within the script marks on the drive shaft28and joined so that the rotor vanes52, fins54and end barriers56are permanently in their respective places. Once joined to the drive shaft28, all end barriers56are all welded together, the welds are smoothed over so the end of the rotor42is sealed to prevent fluid from passing through.

The rotor vanes52are mounted so that each rotor vane52maintains a equal distance to the adjacent rotor vanes52along their entire length from the fin54to the end barrier56. In the illustrated embodiment, there is an equal distance of 0.875 inches between each adjacent rotor vane52and each fin54partially overlaps the closest adjacent fin54in such a way as to form an inlet path as shown by the fluid flow arrows shown inFIG. 3and discussed below. The partially overlapping fins54prevent fluid backflow within the system.

ComparingFIGS. 7A and 7B, in the illustrated embodiment the strips of sheet metal from which the rotor vane52, fin54and end barrier56were formed were about 3.25 inches long and about one inch wide. The fin54is 1 inch long, and the rotor vane52is 1.5 inches long. The end barrier56is formed so that it is 0.75 inches high and there is a distance of 0.875 inches between the distal ends of the bodies of each adjacent rotor vane52, as stated above. The axial length of the combined rotor vane52and fin54, K, is approximately 1.8 inches. The dimensions of the rotor vane52, the fin54, and the end barrier56, the angles X between the rotor vane52and the fin54, and the angle Y between the axial length of rotor vane52and the end barrier56, and the substantially tangential angle formed by the radial length of the rotor vane52with the surface of the shaft28were all determined empirically. Those skilled in the art will recognize sizes of the components of the rotor42and the angles at which they are formed and mounted can be changed without departing from the scope of what has been taught through the illustrated embodiment.

The rotors48for the outlet chamber36can be seen by referring toFIGS. 8A, 8B, and 8C. Unlike the turbine chamber34, the rotor vanes60on the rotor48of the outlet chamber36are parallel with the axis of rotation38. The rotor vanes60comprise a plurality of fins62. As seen inFIGS. 8B and 8C, which show the front and rear views of a rotor48, each rotor vane60ends at an end barrier64.

The rotor48is best understood by following the steps of their construction of the rotor vanes60, their fins62, and the end barrier64. As shown inFIG. 9A, each rotor vane60, fin62and end barrier64is formed from a single strip of sheet metal. At one end of each strip the sheet metal is bent at an angle X′ with respect to the rotor vane60to form the fin62. In the illustrated embodiment the angle X′ is 104.5 degrees below the axis of rotation38. At the opposite end of the strip, the sheet metal is bent in the same direction at an angle Y′ to form the end barrier64of the rotor48. As seen inFIG. 4, the fin62is cut to a length that enables it to overlap adjacent fins62. As will be discussed below, the adjacent fins62form an inlet path between them to allow fluid to flow circuitously from the inlet opening18and through the outlet chamber36. The end barrier64is also cut to engage an adjacent end barrier64and fit tightly around the drive shaft28. A plurality of orifices66are drilled into the portion of the sheet metal that forms the rotor vane60.

As shown inFIG. 9A, the axial length of the rotor vane60is installed parallel to the axis of rotation38. The end barrier64is perpendicular to the axis of rotation38(at an angle Y′ that is 90 degrees with respect to the axis of rotation38). Referring toFIG. 9B, the radial length of the vane60is tilted with respect to the drive shaft28.

Once the plurality of rotor vanes60, fins62, and end barriers64have been formed, an equal plurality of script marks, are carved on the drive shaft28parallel to the axis of rotation38, for the purpose of guiding the rotor vanes60into their respective locations during construction. The preformed rotor vanes60are then inserted to fit tightly within the script marks on the drive shaft28and joined so that the rotor vanes60, fins62, and end barriers64are permanently in their respective places. Once joined to the drive shaft28, all end barriers64are all welded together, the welds are smoothed over so the end of the rotor48for the outlet chamber36is sealed to prevent heated fluid from passing through.

The rotor vanes60are mounted in a way so that each rotor vane60remains in a straight line from its fin62to the vane's distal end where the rotor vane60has been welded to form the end barrier64. In the illustrated embodiment, there is an equal distance of 0.875 inches between the distal ends of the bodies of each adjacent rotor vane60, and each fin62extends past the plane of the closest adjacent rotor vane60in such a way as to form an inlet path as shown by the fluid flow arrows shown inFIG. 3and discussed below.

ComparingFIGS. 9A and 9B, in the illustrated embodiment the strips of sheet metal from which the rotor vane60, fin62and end barrier64are formed are about 3.5 inches long and about one inch wide. The fin62is approximately 0.75 inches long, and the rotor vane60is approximately 2 inches long. The end barrier64is formed so that it is 0.875 inches high and there is a distance of 0.875 inches between the distal ends of the bodies of each adjacent vane, as stated above. The axial length of the combined rotor vane60and fin62, Q, is approximately 2 inches. The dimensions of the rotor vane60, the fin62and the end barriers64, the angles X′ between the rotor vane60and the fin62, and the angle Y′ between the axial length of rotor vane60and the end barrier64, and the substantially tangential angle formed by the radial length of the rotor vane60with the surface of the drive shaft28were all determined empirically. Those skilled in the art will recognize sizes of the components of the rotor48and the angles at which they are mounted can be changed without departing from the scope of what has been taught through the illustrated embodiment.

As noted above,FIGS. 2 through 9show that each of the rotor vanes52of each turbine chamber34has a plurality of rotor orifices58drilled into the portion of the sheet metal that forms the rotor vane52and that that each of the rotor vanes60of the outlet chamber36has a plurality of rotor orifices66drilled into the portion of the sheet metal that forms the rotor vane60. These rotor orifices58and66, allow fluid to pass through to further increase the thermal energy generated as the rotors42and48rotate. The rotor orifices58and66may be a series of holes, openings, slits or apertures and create additional thermal energy by causing friction between the fluid and the surfaces of the rotor orifices58and66of the rotor vanes52and60. Adding more thermal energy to the fluid making the fluid heat up more than the fluid would without these orifices58and66. The number of orifices58and66to be used and the size and shape of each orifice is determined empirically, depending on the type of fluid being used, its viscosity, and the thermal effects desired from fluid flow through the orifices58and66.

As shown inFIGS. 6A, 6B, 8A and 8B, the fins54and62, discussed above, are located at the inlet end of the turbine chambers34and the outlet chamber36. As can be best seen inFIGS. 6A and 8A, each fin54,62is bent inward towards the center line of the axis of rotation38, as explained above. Each fin54,62partially overlaps an adjacent fin54,62on its respective rotor42,48leaving enough space between the end of the overlapping fin54,62and the adjacent fin54,62so that fluid is able to pass through this space. This overlap is formed so that the plurality of fins54,62creates an impeller when the rotors42and48rotate, which causes a propelling force that cycles the fluid forward between the rotor vanes52,60, respectively.

Referring now toFIGS. 10A through 11C, each of the turbine chambers34comprises a fixed stator40which remains completely stationary while the rotors42rotate with the drive shaft28around the axis of rotation38. The stators40have stator divots68that help locate and position the stator40within the outer housing16by lining up with the guiding ridge50. This locks the entire stator40in place causing the stator40to be stationary while within the system10. Each of the stators40has a plurality of axially extending stator vanes70. The stator vanes70on at least one of the stators40are mounted at compound angles such that the axial length of each of the stator vanes70is at an acute angle with respect to the axis of rotation38and the radial length of each of the stator vanes70is tilted at a second angle with respect to the surface of the drive shaft28. The rotor42and stator40of each turbine chamber34is sized and mounted so as to form a shearing plane between them.

The stators40shown inFIGS. 10A through 10Care identical to the stators40shown inFIGS. 11A through 11Cexcept for the chamber entrance lip72. As shown inFIG. 3, each of the entrance lips72directs the fluid flow to the rotor vanes52. In the embodiment shown in the figures, the stator40of the first turbine chamber34does not require a lip of its own as the fluid flows directly into the rotor42from the inlet opening18. With this one exception, the stators40shown inFIGS. 10A through 11Care identical.

The stators40are best understood in connection with their construction. The stators40are created by releasably clamping strips of sheet metal that are each 1.5 inches in length and 0.625 inches wide to the distal end of the rotor vanes52. A donut shaped stator first end member74is then permanently joined to an end of the strip of sheet metal. A donut shaped second end member76is then permanently joined to the opposite end of the strip of sheet metal. Thus, each strip of sheet metal becomes an axially extending stator vane70when the construction of the stator40is complete. Moreover, the stator vanes70are joined to both the first end member74and the second end member76so that the stator vanes70are sandwiched between them. The stator vanes70line up with the rotor vanes52in each chamber but are staggered with respect to the stator vanes70in adjacent turbine chambers34to produce less shearing resistance.

The first end member74and the second end member76are the end walls of the turbine chamber34and the second end member76supports a separating plate78, explained below. The second end member76has at least one outlet orifice80that is situated at the outlet end to allow fluid to flow through at least one opening in an adjacent separating plate orifice80and into an adjacent turbine chamber34as discussed further below. The outlet orifice80is shown as a single opening but it could be multiple openings or any other configuration that will provide sufficient retention time of the fluid in a particular turbine chamber34against the need to maintain a fluid flow rate through the system.

Each stator40has an outer diameter G measured by the length of the diameter of the stator's40full cross-section. In the illustrated embodiment, each of the stators40has an outer diameter G that is approximately 3.5 inches. The inner diameter H of the stator40is measured by the diametrical length of the stator's40cross-section from one side of the stator's40inner circumference to the polar opposite side. In the illustrated embodiment inner diameter H is approximately 2 inches. Furthermore, each stator40has an outer diameter G and an inner diameter H of exactly the same length.

FIGS. 12A and 12B, show the stator44of the outlet chamber36. Each stator44comprises a series of stator vanes82that are parallel with the drive shaft28. As with the outlet chamber's36rotor vanes60, the stator vanes82now force the fluid primarily in the radial direction outward and away from the axis of rotation38as compared to the turbine chamber32which creates a vortex path that propels the fluid primarily in the axial direction.

The stators44are best understood in connection with their construction. The stator44is constructed by releasably clamping strips of sheet metal to the distal end of the rotor vanes60. A donut shaped first end member84is permanently joined to an end of the strip of sheet metal. A donut shaped second end member86is then permanently joined to the opposite end of the strip of sheet metal. In turn, each strip of sheet metal becomes an axially extending stator vane82on the completed stator44. The vanes are joined to both the first end member84and the second end member86so that the stator vanes82are sandwiched between them. The stator vanes82line up with the rotor vanes60in turbine chamber36but are staggered with respect to the stator vanes70in adjacent turbine chambers34. The strips of sheet metal that become the stator vanes82are each approximately 2 inches in length and a half an inch in width.

The first end member84rests on the side of the stator44that is closer to the inlet opening18while within the system (as shown inFIG. 2). The first end member84and the second end member86make up a section of the outlet chamber36. Both the first end member84and the second end member86have stator divots88that help locate and position the stator44within the outer housing16by lining up with the guiding ridge50. This locks the entire stator44in place causing the stator44to be stationary while within the system10. The first end member84has a chamber entrance lip90joined at its end around its inner circumference. As shown inFIG. 3, the entrance lip90directs the fluid flow to the rotor vanes60.

Referring toFIG. 4, circular shaped separating plates78are located between adjacent turbine chambers34and between a turbine chamber34and the outlet chamber36. The separating plates78separate the turbine chambers34and press up against the second end members76. The separating plate78is shaped so that it does not come into contact with any part of the end barriers56or fins54of the rotors42. The separating plate78also has at least one separating plate orifice80through which fluid can flow between the turbine chambers34and between a turbine chamber34and the outlet chamber36.

Referring toFIGS. 13A and 13B, the separating plate78is split vertically down the center creating two halves: the left half92and the right half94. When the two halves are fit together they form a complete separating plate78. In the construction of the system10, each half92and94is inserted between the turbine chambers34and around the drive shaft28such that the separating plate78is stationary. The separating plate78has a separating plate divot96cut from the left half92so that when the separating plate78is fit together it slides over the guiding ridge50(shown inFIG. 4) and locks in a stationary position. The guiding ridge50also serves to line up the outlet orifice80of the second end member76of the turbine chamber34that it presses against with the separating plate orifice80located on the right half94. This creates a channel through which fluid can flow between individual turbine chambers34or between a turbine chamber34and the outlet chamber36.

Referring toFIGS. 2 and 4, a chamber spacer100is used to establish a space between turbine chamber34and between the last turbine chamber34and the outlet chamber36. The chamber spacer100also holds each separating plate78in place up against its respective turbine chamber36within the system10. As seen inFIGS. 14A and 14B, each chamber spacer100also has a gap102that aligns with both the separating plate divots96and the stator divots68and88so that the chamber spacer100is stationary in a same manner as each of the stators40and44and separating plates78.

Referring generally toFIGS. 2 and 3, rotors42,48and stators40,44of each respective turbine chamber34and the outlet chamber36are sized and mounted so as to form a shearing plane between the rotor vanes52,60and stator vanes70,82. As the rotors42and48rotate, this movement causes the rotor vanes52and60to rapidly rotate past the corresponding stator vanes70and82, which provides a shearing action on the fluid, as the fluid passes between each of the vanes. This shearing action causes the fluid to rapidly heat while within each chamber. The shearing action is identical in all turbine chambers34and the outlet chamber36. Each of the turbine chambers34and the outlet chamber36independently heats the fluid so as to cause a heating effect as the fluid passes from the inlet opening18to the outlet opening20. Thus, as the fluid passes through the system10, the fluid incrementally becomes hotter from one chamber to the next until the fluid reaches its hottest temperature just as the fluid leaves through the outlet opening20. As the system10is connected to a closed fluid loop, continuous cycles of heated fluid will provide a constant supply of heated fluid for heating the structure in which the system is located.

The shearing planes are not the only source of fluid heating within the system10. The fins54and62and the resulting inlet path, the compound angles of the rotor vanes52, the rotor orifices58and66, the shearing plane, the outlet orifices80, and the separating plate orifices98create thermal energy as the fluid is transferred along and between the rotor vanes52and60as well as the stator vanes70and82, through the shearing planes and between the adjacent turbine chambers34and the outlet chamber36as the fluid flows circuitously from the inlet opening18to the outlet opening20. The temperature and flow can be further regulated by varying the RPM with the drive shaft28.

As shown inFIG. 3, the fluid flows between the turbine chambers34and the outlet chamber36in a circuitous manner. As fluid enters the system10, the fluid enters through the inlet opening18and passes directly into the first turbine chamber34through the gap between adjacent fins54of the rotor42. As the rotor42rotates, the fins54act as an impeller that both forces fluid forward as well as causes friction between the fluid and the fins54that is a factor in heating the fluid. After passing beyond the fins54, the fluid is further propelled forward by the vortex effect created by fluid flowing between the compound angles of the rotating rotor vanes52. As the fluid passes along one set of the rotor vanes52, the fluid is pushed through the rotor orifices58and between adjacent sets of rotor vanes52. Pushing the fluid between the rotor vanes52in this manner causes additional friction between the fluid and the rotor orifices58. The fluid is also forced upward beyond the shearing plane and between the stator vanes70as the fluid flows throughout and between the rotor vanes52. After being pushed along and between the rotor vanes52as well as between the corresponding stator vanes70, the fluid then passes through the channel created by the outlet orifices80in the second end member76and the corresponding separating plate orifice98into the next turbine chamber34(indicated inFIG. 3, but best show by comparingFIGS. 3 and 4). The fluid passing through these orifices creates another factor in heating the fluid. When the fluid exits one turbine chamber34and enters the next turbine chamber34or the outlet chamber36, the fluid goes past the chamber entrance lip72and90into the next chamber.

Fluid repeats the path discussed above through each turbine chamber34and finally through the outlet chamber36. However, because rotor vanes48and stator vanes44are parallel with the axis of rotation38, when the fluid reaches the outlet chamber36instead of being propelled forward by a vortex the fluid is propelled axially outward by the rotor vanes48and toward the outlet housing16creating pressure such that the fluid must escape through the outlet opening20and exit the system10. When the fluid exits the system10it will be warmer than when it entered the system10. Repeated cycles of the fluid passage in a closed loop will see the system10significantly increase the temperature of fluid passing through it.

It is understood that the number of turbine chambers34could be varied from as few as one to as many as will fit in the system10. The outlet housing16can also be expanded to house more than just three turbine chambers34. It should also be noted that the outlet chamber36as discussed above need only have rotor vanes and stator vanes that direct the fluid flow in a radial direction for embodiments in which the outlet opening20is perpendicular to the axis of rotation38of the drive shaft28. It is understood that there could be embodiments in which the outlet opening20, is parallel to the axis of rotation38of the drive shaft28. In these embodiments, the outlet chamber36would be configured to have rotors and stators similar to those of the turbine chambers34in that the rotor vanes and stator vanes would be angled to create a propelling force that cycles the fluid forward in an axial direction. In essence, there would be no discernable difference between the turbine chambers34and the outlet chamber36in these embodiments. Moreover, there could also be embodiments in which the surface of the turbine chambers34and36could be etched or coated with a material that will add texture to the surface to cause additional friction as fluid passes over the textured surface and increase the thermal energy generated.

As shown inFIG. 15, the inlet opening18aand the outlet opening20amay be parallel to the axis of rotation38a. This configuration gives the user different options for configuring the fluid heating and pumping system for installation. In addition, this embodiment shows one variation of feedback control for the system. Here a thermostat109ais mounted to the outlet opening20ato measure the temperature of the fluid leaving the system. This thermostat109ais connected to a motor control unit108aby means of a wire106a. It will be understood that this included solely for purposes of illustration as those of skill in the art will recognize that any feedback control system is could be similarly attached. The feedback control located at the outlet opening20aprovides an indication of how well the system is performing and would shut down the system when set temperature range is reached. However, if the feedback control were to be located at the inlet opening18a, this would indicate that the temperature of the fluid entering the system which, if the temperature is at a set target would signal the system to cease operation. It would also be possible to include feedback systems at both the inlet and the outlet openings to get a better sense of how well the system is performing.

This invention has been described with reference to several preferred embodiments. Many modifications and alterations will occur to others upon reading and understanding the preceding specification. It is intended that the invention be construed as including all such alterations and modifications in so far as they come within the scope of the appended claims or the equivalents of these claims.