A new impeller assembly for radial FANS and centrifugal pumps

Abstract

The present invention relates to a novel impeller (rotor) assembly for effective and advantageous use in machines and systems operating on aerodynamic and hydrodynamic principles, specifically in radial fans and centrifugal pumps. The assembly comprises a combination of profiled main blades and either profiled tip blades or intermediate blades, arranged around a central hub and extending outward at specific angles in a structured configuration. The invention effectively addresses noise issues in radial fans and centrifugal pumps while improving operational efficiency, reducing energy consumption, and extending component lifespan, all while ensuring compatibility with existing systems.

Description

[0001] A NEW IMPELLER ASSEMBLY FOR RADIAL FANS AND CENTRIFUGAL PUMPS

[0002] TECHNICAL FIELD

[0003] The present invention relates to an impeller assembly for use in radial fans (centrifugal fans) and centrifugal pumps, operating based on aerodynamic and hydrodynamic principles. Specifically, the invention relates to impellers (rotors) of radial fan systems and centrifugal pumps utilized in energy-absorbing machines and systems. Radial fans are employed in air conditioning systems, ventilation of enclosed spaces (such as hospitals, enclosed parking areas, factories, shopping malls, and schools), thermal power plants, mines, solid material transfer, cement factories, plaster factories, vacuum cleaners, range hood extractors, and road sweeping vehicles. Centrifugal pumps, on the other hand, are used for pumping and circulating liquid fluids, especially water.

[0004] PRIOR ART

[0005] Radial fans (centrifugal fans) operating based on aerodynamic principles and centrifugal pumps operating based on hydrodynamic principles provide motion to fluids through the rotation of the impeller using energy. These are powered machines used to create flow within a fluid, typically a gas such as air or a fluid such as water, consisting of a rotating arrangement of vanes or blades which act on the fluid. The rotating assembly of blades and hub is known as an impeller, a rotor, or a runner. Usually, it is contained within some form of housing or case. Radial fans (centrifugal fans) and centrifugal pumps are systems typically consisting of an impeller with blades made of flat sheet metal housed within a snail-shaped outer casing, a shaft with bearings attached to the impeller for rotation, coupling or pulley-belt assemblies, and an electric motor that generates rotational motion.

[0006] The rotational motion generated by the electric motor is transmitted to the shaft of the impeller (rotor) via a coupling or pulley-belt assembly. Since the shaft is fixed to the impeller in a radial fan or centrifugal pump, the impeller is rotated. There are also impellers directly mounted on the motor shaft. The fluid on the upper surfaces of the blades in the impeller is expelled outward from the center. The fluid is drawn through the suction port of the snail casing, which is aligned with the center of the impeller, and discharged through the outlet port located on the side of the casing. In this way, the fluid is set into motion, allowing radial fans to be used in ventilation, dust and gas suction along with air, and the transfer of solid materials combined with air. Centrifugal pumps are used to pump or circulate water or liquid fluids.

[0007] Currently, impellers are manufactured with backward-inclined blades, radial straight blades, and forward- inclined blades. Most commercially produced impellers feature blades made by bending plain sheet metal. Centrifugal pump impellers are typically produced through casting methods. In radial fans used for transporting materials such as wood chips, metal shavings, dust, and grains along with air, significant wear is a common issue. The high level of wear necessitates frequent replacement of the impeller, which consequently increases operating costs.

[0008] Although valuable solutions have been found in prior art applications, there remains a continual need for innovative and effective blade designs to further enhance the efficiency and applicability of aerodynamic and hydrodynamic systems. Further improvements in blade-profile design in critical energy consuming systems such as radial fans and centrifugal fluid pumps will play a central role in technological advancements in these fields. Such improvements, by further increasing the efficiency of energy conversion, are set to offer significant innovations that will yield considerable economic and environmental benefits.

[0009] BRIEF DESCRIPTION OF THE INVENTION

[0010] The primary objective of the present invention, based on the findings from the research and development conducted thereon, is to provide a novel impeller (rotor) assembly for use in radial fans and centrifugal pumps, effectively addressing the issues and demands encountered in conventional applications. Said impeller assembly, applicable to both radial fans and centrifugal pumps, enhances efficiency through the optimized blade structure thereof, resulting in significant energy savings. The efficient operation of radial fans and centrifugal pumps extends their service life and substantially reduces operating costs. Furthermore, another objective of the invention is to mitigate noise issues, as the improved efficiency of radial fans and centrifugal pumps leads to quieter operation.

[0011] The invention also aims to reduce the investment costs associated with fans.

[0012] Still another objective of the invention is to achieve higher compatibility and performance efficiency in different system configurations, tailored to the aerodynamic and hydrodynamic applications of existing systems. The replacement of an impeller of a radial fan or a centrifugal pump with the embodiment proposed by the invention allows conventional systems to operate efficiently with minimal cost and enhanced practicality.

[0013] The centrifugal pump impellers proposed by the invention are suitable for use in vertical and multistage centrifugal pumps.

[0014] The radial fans and centrifugal pumps of the invention are capable of operating in series and parallel configurations.

[0015] The dimensions, number of blades, blade surface area, and impeller diameter of radial fans are determined according to the required flow rate and pressure values. For applications requiring high flow rates, a doublesuction configuration is enabled. The suction ports are positioned in the axial direction of the fan, while the pressure ports are located in the radial direction thereof on the snail casing. In radial fans, the suction cross- sectional area is formed to be equal to or larger than the pressure cross-sectional area. The suction port is circular and centrally positioned on the impeller. The suction pipe of the fan is aligned with the suction port of the impeller without any contact therebetween. The outlet, which directs the pressurized flow, is located on the snail casing that forms the outer body of the fan, and may have a circular, rectangular, or square crosssection. The same applies to centrifugal pumps. While the operational principles of radial fans and centrifugal pumps are identical, radial fans are used for transferring gases, air, or air combined with solid materials, whereas centrifugal pumps are used for transporting liquid fluids. Centrifugal pump impellers are commonly made from composite materials, cast iron, bronze, or stainless steel.

[0016] Additionally, the profiled blades of the radial fan impeller according to the invention can be formed by pressing in a mold or manufactured using the extrusion method. Depending on the intended use, the fan can also be produced using composite materials, aluminum, bronze, iron, or their alloys.

[0017] The rotation direction of impeller of the radial fan and the centrifugal pump can be either clockwise or counterclockwise when viewed from the front perspective.

[0018] Another significant objective of the invention is to provide a radial fan impeller comprising single-suction or double-suction profiled blades, ensuring greater compatibility and performance efficiency in various system configurations and suitability for use in diverse aerodynamic and hydrodynamic environments.

[0019] Another objective of the invention is to offer solutions that achieve higher pressure in configurations utilizing main and tip profiled blades, and higher flow rates in configurations utilizing main and intermediate profiled blades.

[0020] Yet another objective of the invention is to provide solutions for issues such as noise generated when the fluid discharged from the impeller of a radial fan or a centrifugal pump strikes the casing wall, as well as excessive energy consumption by the fan motor and pump motor associated with said phenomenon.

[0021] In order to achieve said objectives, the present invention provides a novel impeller assembly for use in radial fans and centrifugal pumps, comprising a central hub to which at least two profiled main blades and tip blades, or at least two profiled main blades and intermediate blades, are connected, said blades extending outward from said hub and being configured to rotate around the central axis of the impeller, wherein each of the profiled blades, including the main, tip, and intermediate blades, comprises at least three lower surfaces, at least two upper surfaces, a leading edge surface, and a trailing edge surface, thereby forming a distinctive arrangement of profiled blades.

[0022] In the arrangement of the profiled blades, each of the main and tip profiled blades, or each of the main and intermediate profiled blades, is positioned at specific angles relative to the center of rotation, wherein said angles are determined based on design criteria such as flow rate, pressure, and the type of material to be transported, and the angles between the blades are equal.

[0023] BRIEF DESCRIPTION OF FIGURES

[0024] These and other objectives, aspects, structural and characteristic features, advantages, and embodiments of the present invention will become more apparent from- and will be understood more clearly by reference to- the following detailed description and the associated figures.

[0025] Figure 1: Front and side views illustrating the main components of a radial fan assembly according to the preferred embodiment of the invention.

[0026] Figure 2: Front and side views illustrating a single-suction radial fan impeller with profiled main and tip blades, showing the blade arrangement and main components thereof, according to the preferred embodiment of the invention.

[0027] Figure 3: Front and side views illustrating a single-suction radial fan impeller with profiled main and intermediate blades, including the arrangement of the blades and main components thereof, according to the preferred embodiment of the invention.

[0028] Figure 4: Front and side views illustrating a double-suction radial fan impeller with profiled main and tip blades, including the arrangement of the blades and main components thereof, according to the preferred embodiment of the invention.

[0029] Figure 5: Front and side views illustrating the main components of a centrifugal pump assembly according to the preferred embodiment of the invention.

[0030] Figure 6: Front and side views illustrating the profiled main and tip blades of a centrifugal pump impeller rotating clockwise, as seen from the motor side, according to the preferred embodiment of the invention.

[0031] Figure 7: Front and side views illustrating the profiled main and tip blades of a centrifugal pump impeller rotating counterclockwise, as seen from the motor side, according to the preferred embodiment of the invention.

[0032] Figure 8: Front and side views illustrating the surfaces of the profiled main and tip blades of a centrifugal pump impeller and the directions of the fluid flow, according to the preferred embodiment of the invention. Figure 9: A representative view illustrating the surfaces of the profiled main and tip blades of a centrifugal pump impeller and the directions of the pressure forces generated, according to the preferred embodiment of the invention.

[0033] Figure 10: Front and side views illustrating the profiled main and intermediate blades of a centrifugal pump impeller rotating counterclockwise, as seen from the motor side, according to the preferred embodiment of the invention.

[0034] Figure 11: Front and side views illustrating the surfaces of the profiled main and intermediate blades of a centrifugal pump impeller and the directions of the fluid flow, according to the preferred embodiment of the invention.

[0035] Figure 12: Front and side views illustrating the surfaces of the profiled main and intermediate blades of a centrifugal pump impeller and the directions of the pressure forces generated, according to the preferred embodiment of the invention.

[0036] The components or elements corresponding to the reference numbers used in the figures are listed below:

[0037] 1 Drive shaft of a single-suction radial fan impeller.

[0038] 2 Hub flange.

[0039] 3 Base flange of the radial fan impeller.

[0040] 4 Bolts and washers securing the base flange of the radial fan impeller to the hub flange.

[0041] 5 Suction port flange of the single-suction radial fan impeller.

[0042] 6 Shaft of a double-suction radial fan impeller.

[0043] 7 Middle flange of the double-suction radial fan impeller.

[0044] 8 Hub flange of the double-suction radial fan impeller.

[0045] 9 Bolts and washers securing the middle flange to the hub flange in the double-suction radial fan impeller.

[0046] 10 First suction port flange of the double-suction radial fan impeller.

[0047] 11 Second suction port flange of the double-suction radial fan impeller.

[0048] 21 Hub flange of the centrifugal pump impeller.

[0049] 22 Suction port flange of the centrifugal pump impeller.

[0050] 30 Profiled main blade of the radial fan impeller with profiled tip blades.

[0051] 31 Profiled tip blade of the radial fan impeller.

[0052] 40 Profiled main blade of the radial fan impeller with profiled intermediate blades.

[0053] 41 Profiled intermediate blade of the radial fan impeller.

[0054] 50 Profiled main blade of the centrifugal pump impeller with profiled tip blades.

[0055] 60 Profiled tip blade of the centrifugal pump impeller.

[0056] 70 Profiled main blade of the centrifugal pump impeller with profiled intermediate blades. 80 Profiled intermediate blade of the centrifugal pump impeller.

[0057] 100 Pressure forces on profiled main blades of the impeller with profiled tip blades in a centrifugal pump and a radial fan.

[0058] 200 Pressure forces on profiled tip blades of the impeller in a centrifugal pump and a radial fan.

[0059] 300 Pressure forces on profiled main blades of the impeller with profiled intermediate blades in a centrifugal pump and a radial fan.

[0060] 400 Pressure forces on profiled intermediate blades of the impeller in a centrifugal pump and a radial fan.

[0061] 500 Fluid flow directions at the suction port of the impeller with profiled tip blades in a centrifugal pump and a radial fan.

[0062] 600 Fluid flow directions at the discharge port of the impeller with profiled tip blades in a centrifugal pump and a radial fan.

[0063] 700 Fluid flow directions at the suction port of the impeller with profiled intermediate blades in a centrifugal pump and a radial fan.

[0064] 800 Fluid flow directions at the discharge port of the impeller with profiled intermediate blades in a centrifugal pump and a radial fan.

[0065] Yl. Leading edge surface of the profiled main blade of an impeller with profiled tip blades.

[0066] Y2. First upper surface of the profiled main blade of an impeller with profiled tip blades.

[0067] Y3. First lower surface of the profiled main blade of an impeller with profiled tip blades.

[0068] Y4. Second upper surface of the profiled main blade of an impeller with profiled tip blades.

[0069] Y5. Second lower surface of the profiled main blade of an impeller with profiled tip blades.

[0070] Y6. Third lower surface of the profiled main blade of an impeller with profiled tip blades.

[0071] Y7. Trailing edge surface of the profiled main blade of an impeller with profiled tip blades.

[0072] Yll. Leading edge surface of the profiled tip blade of an impeller.

[0073] Y12. First upper surface of the profiled tip blade of an impeller.

[0074] Y13. First lower surface of the profiled tip blade of an impeller.

[0075] Y14. Second upper surface of the profiled tip blade of an impeller.

[0076] Y15. Second lower surface of the profiled tip blade of an impeller.

[0077] Y16. Third lower surface of the profiled tip blade of an impeller.

[0078] Y17. Trailing edge surface of the profiled tip blade of an impeller.

[0079] Y21. Leading edge surface of the profiled main blade of an impeller with profiled intermediate blades.

[0080] Y22. First upper surface of the profiled main blade of an impeller with profiled intermediate blades.

[0081] Y23. First lower surface of the profiled main blade of an impeller with profiled intermediate blades.

[0082] Y24. Second upper surface of the profiled main blade of an impeller with profiled intermediate blades.

[0083] Y25. Second lower surface of the profiled main blade of an impeller with profiled intermediate blades.

[0084] Y26. Third lower surface of the profiled main blade of an impeller with profiled intermediate blades.

[0085] Y27. Trailing edge surface of the profiled main blade of an impeller with profiled intermediate blades.

[0086] Y31. Leading edge surface of the profiled intermediate blade an impeller. Y32. First upper surface of the profiled intermediate blade of an impeller.

[0087] Y33. First lower surface of the profiled intermediate blade of an impeller.

[0088] Y34. Second upper surface of the profiled intermediate blade of an impeller.

[0089] Y35. Second lower surface of the profiled intermediate blade of an impeller.

[0090] Y36. Third lower surface of the profiled intermediate blade of an impeller.

[0091] Y37. Trailing edge surface of the profiled intermediate blade of an impeller.

[0092] While the invention is described hereinafter by way of example for several embodiments and illustrative drawings, those skilled in the art will recognize that the invention is not limited to the embodiments or drawings described. It should be understood, that the drawings and detailed description thereto are not intended to limit the invention to the particular form disclosed, but on the contrary, the intention is to cover all modifications, equivalents and alternatives falling within the spirit and scope of the present invention as defined by the appended claims. The headings used herein are for organizational purposes only and are not meant to be used to limit the scope of the description or the claims. As used in this specification, expressions such as "may" are used in a permissive sense (i.e., meaning having the potential to), rather than the mandatory sense (i.e., meaning must). Similarly, words such as "include", "there is", "have", "contain" and "exist" also mean "comprise", but not limited to.

[0093] DETAILED DESCRIPTION

[0094] The impeller of the invention is suitable for use in both radial fans and centrifugal pumps, as they share similar structural configurations, enabling a unified description applicable to both. These powered machines operate on aerodynamic or hydrodynamic principles, imparting motion to fluids through a rotating assembly of vanes or blades, commonly referred to as an impeller, rotor, or runner. For the purposes of this specification, the term "impeller" is used to encompass all such rotating assemblies, including cases where "rotor" may also be commonly applied, such as in radial fans.

[0095] Figure 1 represents front and side views illustrating the main components of an assembly according to the present invention, designed for use in systems such as radial fans where rotational motion (mechanical energy) generated by an electric motor is utilized to move substances such as air, gas, or solid particles combined with air.

[0096] Likewise, Figure 5 represents front and side views illustrating the main components of an assembly according to the present invention, designed for use in systems such as centrifugal pumps, where rotational motion generated by an electric motor is utilized to move liquid fluids, such as water.

[0097] The impeller (rotor) assemblies for radial fans and centrifugal pumps according to the invention are disclosed as combinations of profiled main blades together with profiled tip blades and / or profiled intermediate blades. According to a preferred embodiment, as illustrated in Figures 2, 8, and 9, the profiled main blades (30, 50) and profiled tip blades (31, 60), which constitute the impeller assembly for a radial fan or a centrifugal pump (i.e. the impeller of a single-suction radial fan or centrifugal pump), are the primary elements thereof. Said profiled blades are arranged around a center of rotation in a specific form and at specific attack angles, and in sufficient numbers. In order to ensure continuity and compatibility between the two types of profiled blades, the leading edge surfaces (Yll) of the profiled tip blades are aligned with the trailing edge surfaces (Y7) of the profiled main blades.

[0098] In another preferred embodiment illustrated in Figures 3, 10, 11, and 12, the profiled main blades (40, 70), which are incorporated into the impeller of the single-suction radial fan or centrifugal pump, are positioned around a center of rotation at calculated attack angles and in calculated numbers.

[0099] The trailing edge surfaces of the profiled main blades taper outward toward the outer diameter of the impeller, creating an expanding gap between two adjacent profiled main blades. Intermediate profiled blades (41, 80) are placed in these gaps to convert the empty space into a useful area. In both cases, the blades are mounted on the radial fan impellers between the fan base flange (3) and the suction-port end flange (5). For centrifugal pump impellers, they are mounted between the hub flange (21) and the suction-port flange (22). The fan impeller base flange (3) is secured to the hub flange (2) with bolts (4). After the manufacturing process is completed, the impeller in radial fans or centrifugal pumps is balanced to ensure operational stability and are made ready for use. The same method is applied to double-suction fan impellers.

[0100] The number of profiled blades in both the radial fan impeller and the centrifugal pump impeller varies. The exact number of profiled blades is determined through the design process. For instance, the number of blades can be reduced by increasing the impeller diameter or blade length while maintaining the same functionality. The blade numbers shown in the figures are representative. Similarly, the materials used for the fan impeller and pump impeller may vary depending on their intended function.

[0101] The term "fluid" mentioned herein refers to air, air mixed with gases, chemical gases, and liquids.

[0102] The impeller of the present invention for use in radial fans and centrifugal pumps are compatible with all manufacturing methods. The aerodynamic and hydrodynamic efficiency, which enhances the performance of radial fans and centrifugal pumps according to the invention, is explained in greater detail below.

[0103] Due to the fact that radial fans and centrifugal pumps operate on the same principles, the description provided herein applies to both. The only distinction lies in the density of the fluids they handle.

[0104] The impeller is typically driven by rotational motion (mechanical energy) supplied by an electric motor. Profiled blades are arranged in a specific pattern around the impeller shaft, positioned between flanges. (Figures 2, 3, 4, 6, 7, and 10). The impeller with profiled tip blades in radial fans and centrifugal pumps (Figures 8-9) comprises profiled main blades (40, 50) and profiled tip blades (31, 60), each comprising at least seven surfaces and being present in equal numbers. Before the impeller begins to rotate, the fluid remains stationary and motionless. Upon initiation of rotational movement, the fluid on the convex upper surfaces of the profiled main blades (Y2 and Y4) and the convex upper surfaces of the profiled tip blades (Y12 and Y14) is expelled outward, that is, toward the trailing edge surface (Y7) of the profiled main blade and the trailing edge surface (Y17) of the profiled tip blade, as illustrated in Figure 8. This phenomenon occurs simultaneously across all profiled blades on the rotating impeller. As the fluid on the upper surfaces of said profiled blades displaces, a vacuum is created at the suction port of the impeller. Said vacuum causes the fluid in the suction pipes of the fan or pump to move (500) toward the impeller, as illustrated in Figure 8. Consequently, the fluid is drawn through the suction port, pressurized, and expelled through the discharge pipe of the snail casing. Once the suction and discharge process begins, the fluid striking the leading edge surfaces (Yl) of the profiled main blades is flows toward the upper surface (Y2) and lower surface (Y3) of the profiled main blades. Since Y2 and Y3 are convex, the fluid accelerates over these surfaces, resulting in a pressure drop in this region. At the end of Y3, the surface curves inward, transitioning into a concave form that generates surface Y5 toward the middle section of the profiled main blade. Since the Y5 surface and the subsequent Y6 surface are concave, the cross- sectional area between the profiled main blades increases. Due to the larger cross-sectional area in the Y5 and Y6 region, the fluid velocity decreases, and the pressure rises in this zone. Consequently, pressure forces (100) are generated, as illustrated in Figure 9, from the Y5 and Y6 surfaces on the lower side of the profiled main blade toward the Y2 and Y4 surfaces on the upper side of the profiled main blade. Said pressure forces are in the direction of rotation of the impeller. The accelerated fluid on the Y4 surface of the profiled main blade immediately moves to the Y12 surface of the adjacent profiled tip blade, then to the Y14 surface, and finally exits (600) the impeller with an even higher velocity from the trailing edge surface (Y17) of the tip blade, as illustrated in Figure 8. Since the Y13 and Y12 surfaces of the profiled tip blade are convex, the fluid velocity increases slightly on these surfaces, leading to a drop in pressure. Toward the middle section of the profiled tip blade, the Y13 surface transitions to a concave form, forming the Y15 surface. Due to the concave shape of Y15 and the subsequent Y16, the cross-sectional area between the profiled tip blades increases. In the Y15 and Y16 region, the larger cross-sectional area causes the fluid velocity to decrease and the pressure to rise. Similarly, as illustrated in Figure 9, pressure forces (200) are generated from the lower surfaces (Y15 and Y16) toward the upper surfaces (Y12 and Y14) of the profiled tip blades. These pressure forces align with the rotation direction of the impeller.

[0105] Likewise, the impeller with profiled intermediate blades for a radial fan and centrifugal pump (Figures 3-10) comprises profiled main blades (40, 70) and profiled intermediate blades (41, 80), each comprising at least seven surfaces and being present in equal numbers. Before the impeller begins to rotate, the fluid remains stationary and motionless. Upon initiation of rotational movement, the fluid on the convex upper surfaces of the profiled main blades (Y22 and Y24) and the convex upper surfaces of the profiled intermediate blades (Y32 and Y34) is expelled outward, that is, toward the trailing edge surface (Y27) of the profiled main blade and the trailing edge surface (Y37) of the profiled intermediate blade. This phenomenon occurs simultaneously across all profiled blades on the rotating impeller. As the fluid on the upper surfaces of the profiled blades displaces, a vacuum is created at the suction port of the impeller. Said vacuum causes the fluid in the suction pipes of the fan or pump to move (700) toward the impeller, as illustrated in Figure 11. Consequently, the fluid is drawn through the suction port, pressurized, and expelled through the discharge pipe of the snail casing. Once the suction and discharge process begins, the fluid striking the leading edge surfaces (Y21) of the profiled main blades flows toward the upper surface (Y22) and lower surface (Y23) of the profiled main blades. Since Y22 and Y23 are convex, the fluid accelerates over these surfaces, resulting in a pressure drop in this region. At the end of Y23, the surface curves inward, transitioning into a concave form that generates surface Y25 toward the middle section of the profiled main blade. Since the Y25 surface and the subsequent Y26 surface are concave, the cross-sectional area between the profiled main blades increases. Due to the larger cross-sectional area in the Y25 and Y26 region, the fluid velocity decreases, and the pressure rises in this zone. Consequently, pressure forces (300) are generated, as illustrated in Figure 12, from the Y25 and Y26 surfaces on the lower side of the profiled main blade toward the Y22 and Y24 surfaces on the upper side of the profiled main blade. Said pressure forces are in the direction of rotation of the impeller.

[0106] The same aerodynamic or hydrodynamic phenomenon described above also applies to the profiled intermediate blades.

[0107] With the initiation of rotational motion, the fluid on the convex upper surfaces (Y32 and Y34) of the profiled intermediate blades is propelled and expelled outward toward the trailing edge surface (Y37). This process occurs simultaneously across all profiled intermediate blades on the rotating impeller. As the fluid on the upper surfaces of these profiled blades displaces, a vacuum is created at the suction port of the impeller. This vacuum causes the fluid in the suction pipes of the fan or pump to move (700) toward the impeller, as illustrated in Figure 11. Consequently, the fluid is drawn through the suction port, pressurized, and expelled through the discharge pipe of the snail casing. Once the suction and discharge process begins, the fluid striking the leading edge surfaces (Y31) of the profiled intermediate blades flows toward the upper surface (Y32) and lower surface (Y33) of the profiled intermediate blades. Since Y32 and Y33 are convex, the fluid accelerates over these surfaces, resulting in a pressure drop in this region. At the end of Y33, the surface curves inward, transitioning into a concave form that generates surface Y35. Since the Y35 surface and the subsequent Y36 surface are concave, the cross-sectional area between the profiled intermediate blades (80) and the profiled main blades (70) increases. Due to the larger cross-sectional area in the Y35 and Y36 region, the fluid velocity decreases, and the pressure rises in this zone. Consequently, as illustrated in Figure 12, pressure forces (400) are generated from the Y35 and Y36 surfaces on the lower side of the profiled intermediate blades toward the Y32 and Y34 surfaces on the upper side of the profiled main blades. These pressure forces act in the rotational direction of the impeller. In double-suction fan impellers with both profiled tip blades and profiled intermediate blades, the aerodynamic phenomenon occurring on each suction side are identical to those described for single-suction embodiments.

[0108] As a result of the pressure forces explained above, the fan and pump systems operating with the impeller according to the present invention consume less energy.

[0109] The impeller assembly described herein comprises a hub structure designed suitably to adapt to existing centrifugal pumps or axial fans. In order to minimize noise levels in fan or pump applications, the profiled blades are engineered with rounded transitions between surfaces, eliminating sharp edges and promoting smoother fluid dynamics. The descriptions of specific elements in the figures, including directional references such as the upper and lower surfaces of the profiled blades or their positions are arrangements, are solely intended to aid understanding and should not be interpreted as limiting the scope of the invention. A person skilled in the art will immediately recognize that these configurations may vary based on the placement of the impeller. Similarly, individual examples, such as radial fans or centrifugal pumps with different configurations serving specific purposes, should not be considered limiting to the scope of the invention, as the primary focus of the invention is the adaptable arrangement of unique impellers with profiled blade structures. For instance, integrating profiled intermediate blades into radial fan impellers or centrifugal pump impellers with profiled tip blades.

Claims

1. CLAIMS1. An impeller (rotor) assembly for use in radial (centrifugal) fans and centrifugal pumps, connected to a central hub (2, 8 or 21), comprising;- at least two profiled main blades (30 or 50) and at least two profiled tip blades (31 or 60); or- at least two profiled main blades (40 or 70) and at least two profiled intermediate blades (41 or 80); wherein- said blades are arranged around the central hub and extending outward at specific angles in a structured configuration, and configured to rotate around the central axis of the impeller, ensuring continuity and compatibility between said two types of profiled blades;- each of said profiled blades comprises at least two upper surfaces (Y2-Y4, Y12-Y14, Y22-Y24 or Y32-Y34), at least three lower surfaces (Y3-Y5-Y6, Y13-Y15-Y16, Y23-Y25-Y26 or Y33-Y34-Y36), a leading edge surface (Yl, Yll, Y21 or Y31), and a trailing edge surface (Y7, Y17, Y27 or Y37).

2. The impeller assembly according to Claim 1, characterized in that the profiled tip blades (31) is positioned consecutively with the profiled main blade (30) in a structured configuration to ensure continuity and compatibility in radial fans.

3. The impeller assembly according to Claim 1, characterized in that the profiled intermediate blades (41) are positioned within the gaps between the profiled main blades (40) in a structured configuration, in radial fans.

4. The impeller assembly according to Claim 1, characterized by comprising a double-suction configuration with profiled tip blades (10, 11), in radial fans.

5. The impeller assembly according to Claim 1, characterized by comprising a double-suction configuration with profiled intermediate blades, in radial fans.

6. The impeller assembly according to any one of the preceding claims, characterized by comprising a hub (2, 8) structure adaptable to conventional radial fans.

7. The impeller assembly according to any one of the preceding claims 1 to 5, characterized by rotating clockwise or counterclockwise directions when viewed from the motor in radial fans.

8. The impeller assembly according to Claim 1, characterized in that the profiled tip blades (60) is positioned consecutively with the profiled main blade (50) in a structured configuration to ensure continuity and compatibility in centrifugal pumps.

9. The impeller assembly according to Claim 1, characterized in that the profiled intermediate blades (80) are positioned within the gaps between the profiled main blades (70) in a structured configuration, in centrifugal pumps.

10. The impeller assembly according to any one of the preceding claims 1, 8 and 9, characterized by comprising a hub (21) structure adaptable to conventional centrifugal pumps.

11. The impeller assembly according to any one of the preceding claims 1, 8, 9 and 10, characterized by rotating both clockwise and counterclockwise directions when viewed from the motor in centrifugal pumps.

12. The impeller assembly according to any one of the preceding claims 1, 8, 9, 10 and 11, characterized in that the adapted centrifugal pumps are configured to be connected to each other in both series and parallel arrangements.

13. The impeller assembly according to anyone of the preceding claims, characterized in that said profiled impeller blades are positioned between two flanges (3-5 or 21-22) fixed to the central hub.

14. The impeller assembly according to anyone of the preceding claims, characterized in that the profiled blades are comprise rounded transitions between surfaces, free of sharp edges, to reduce noise levels in fan or pump applications.

15. The impeller assembly according to any of the preceding claims, characterized in that it is made of composite materials, aluminum, bronze, iron, or their alloys.

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