Description:TECHNICAL FIELD
[0001] The present disclosure in general relates to a pumps, and more specifically, relates to a technical configuration of an impeller for centrifugal water pumps used for circulating water in internal combustion engines of motor vehicles. In addition, the impeller can also be utilized in pumps used for other purposes and for liquids other than water.

BACKGROUND OF THE INVENTION
[0002] Background description includes information that may be useful in understanding the present invention. It is an admission that any of the information provided herein is prior art or relevant to the presently claimed invention, or that any publication specifically or implicitly referenced is prior art.
[0003] The automotive industry has always been known to be very competitive as far as its design and material usage are concerned. Hence, there is need to elevate the automotive industry, as the industry is facing great market pressure to develop high quality products more quickly at lower cost. Moreover, there is also a need to reduce weight in order to improve automobile efficiency and cost.
[0004] Therefore, the present disclosure focuses on improving an overall efficiency of an automobile by enhancing the cooling of the engine. It also focuses on cooling of the exhaust gas circulated in the exhaust gas regulation unit. The cooling of the engine as well as of the exhaust gas are enhanced by improving an efficiency of pump.
[0005] The engine cooling unit as well as exhaust gas regulation unit in general utilises a centrifugal pump to drive a flow of coolant through passages formed in the engine block. In case of the engine cooling unit 100 as shown in FIG.1 through block diagram, the pump 102is connected to an outlet 104-O provided at a lower header block of the radiator 104 that forces water in the engine block ( including crank case block & cylinder head ) 106 through the passages provided in a crank case. The water takes away the heat from the engine block 106 and through return line 108, the hot water moves back to the radiator 104 through an inlet port 104-I provided at an upper header tank of the radiator. This circulation of cold water only happens, when the temperatures rises above a certain level. Here, a thermostat valve 110 plays a major function. Hence, when the temperature of the engine increases beyond a certain limit, the thermostat valve 110 got opened that results in the circulation of the cold water from the radiator module 104 to the engine block 106. The temperature range is also defined in the block diagram.
[0006] On the other hand, in case of the exhaust gas regulation unit that works parallel with the engine cooling unit, the EGR cooler takes water from the radiator unit through pump, and after cooling the exhaust gas, the hot water goes back to the radiator unit. In this manner, the water pump helps in forced circulation of water in the engine cooling unit and the exhaust gas regulation unit that helps in carrying away the heat from the engine cooling unit as well as from the exhaust gas regulation unit.
[0007] The centrifugal pump conventionally includes a casing containing a pumping chamber, a driven impeller to pump water by centrifugal force, an inlet aligned axially with the impeller and an outlet whose initial channel is tangent to the impeller vanes. In addition, the pump chamber or volute needs to be filled or substantially filled with liquid for the pump to operate.
[0008] Centrifugal pumps perform best when used with water, oils or other liquid products of low viscosity. The efficiency of the pump will decrease while pumping highly viscous products. In addition, centrifugal pumps are ideal for moving high volumes of thin liquids, not recommended for thick fluids.
[0009] Moreover, one of the biggest drawbacks of existing centrifugal pumps is their sensitivity to operating environment. The problems such as cavitations and other vibrations arises in pump caused by the surrounding conditions that results in significant damage and expensive repairs due to pitting on the impeller or casing in centrifugal pumps.
[0010] Although in many cases, cavitations can be prevented before it even begins by ensuring a good technical configuration. Hence, there is need to modify the technical configuration of centrifugal pump in order to overcome all the above-mentioned shortcomings. This in turn improves the overall performance of the pump that results in an augmentation in the efficiency of the pump, as the efficiency of any product is considered as a unique selling proposition of the product.
[0011] Most of the existing prior arts related to this particular field of technology fails to provide a pump having better efficiency performance under varying load and speed conditions.
[0012] Therefore, there is need in the art to provide a simple, compact, and cost effective pump that helps in increasing the overall efficiency of the engine under varying load and speed conditions.

OBJECTS OF THE INVENTION
[0013] A general or primary object of the present disclosure is to provide an efficient and economical centrifugal pump that works under different load & speed conditions of an engine.
[0014] It is another object of the present disclosure is to provide the centrifugal pump that increases the cooling efficiency of the engine cooling unit and the EGR unit.
[0015] It is another object of the present disclosure is to provide the centrifugal pump that incurs less maintenance cost.
[0016] It is yet another object of the present disclosure is to provide the centrifugal pump that is impervious to the operating environment.
[0017] It is further object of the present disclosure is to provide the centrifugal pump that sustain the problem of cavitations.
[0018] It is further object of the present disclosure is to provide the centrifugal pump that overcomes problem of vibration arises due to surrounding condition.
[0019] It is yet further object of the present disclosure is to provide the centrifugal pump that gives better performance & reliability.
[0020] It is yet another object of the present disclosure is to provide the centrifugal pump that reduces the chances of pitting on the impeller or casing of the pumps.
[0021] It is yet another object of the present disclosure is to provide the centrifugal pump that helps in improving the performance and reliability of the engine as well as the agricultural vehicle.
[0022] These and other objects of the present invention will become readily apparent from the following detailed description taken in conjunction with the accompanying drawings.

SUMMARY
[0023] In accordance with an embodiment, the present disclosure provides an impeller for increasing an efficiency of a centrifugal pump, the impeller comprising a circular base plate with a hole in a centre, wherein the centre of the hole of the circular base plate aligned with a central axis of the impeller; a connector boss having a lower end and an upper end, wherein the connector boss integrated with the hole formed at a centre of the circular base through the lower end, and the centre of the connector boss coincides with the central axis of the impeller; a circular shroud formed at a defined distance with the hole of the circular base plate in concentric manner, wherein an annular space provided in between a lower end of the connector boss and the circular shroud comprises a concave shaped structure; and a plurality of vanes extending outwards from the periphery of the lower end of the connector boss, wherein each vane placed equidistantly with one another having a root region proximal to the connector boss and a tip region distal from the connector boss terminating at an outer periphery of the circular base plate.
[0024] In accordance with an aspect, the diameter of the circular base plate ranges in between 90 mm to 90.5 mm.
[0025] In accordance with an aspect, the thickness of the circular base plate is 3mm.
[0026] In accordance with an aspect, the connector boss is of hollow cylindrical shape.
[0027] In accordance with an aspect, an outside diameter of the connector boss ranges in between 27.5 mm to 28.5mm.
[0028] In accordance with an aspect, an inside diameter of the connector boss ranges in between 15.80 mm to 15.87mm.
[0029] In accordance with an aspect, the height of the connector boss ranges in between 14.50 mm to 15 mm.
[0030] In accordance with an aspect, the connector boss is attached in the hole of the circular base plate for engaging a drive shaft of a motor.
[0031] In accordance with an aspect, the circular shroud is of diameter ranges in between 48 mm to 49 mm.
[0032] In accordance with an aspect, the plurality of vanes disposed around the connector boss in the radial manner.
[0033] In accordance with an aspect, the vanes are of rectangular shaped structure.
[0034] In accordance with an aspect, the vane comprises an upper and a lower rectangular surface.
[0035] In accordance with an aspect, the length of the vane from the lower end of the connector boss ranges in between 45 mm to 47 mm.
[0036] In accordance with an aspect, the upper rectangular surface of each vane comprises a C-shaped undercut extending outwards from a root region to a mid-region of the vanes.
[0037] In accordance with an aspect, the length of the C-shaped undercut formed on the upper surface of each of the vane ranges between 15.5 mm to 16 mm.
[0038] In accordance with an aspect, the upper surface of each of the vane comprises a flat rectangular surface extending from the mid-region to the tip region of the vanes.
[0039] In accordance with an aspect, the length of the rectangular shaped surface formed on the upper surface of each of the vane ranges between 30 mm to 31mm.
[0040] In accordance with an aspect, the lower surface of each of the vane comprises a concave shaped structure extending outwards from a root region to the mid region of the vanes.
[0041] In accordance with an aspect, the lower surface of each of the vane comprises a rectangular shaped structure extending outwards from the mid region to the tip region of the vanes.
[0042] In accordance with an aspect, the tip region of the vane is disposed in the same plane as that of the root region.
[0043] In accordance with an aspect, the angle between the vanes of the impeller is 300.
[0044] In accordance with an aspect, the impeller is made of cast iron grade 20.
[0045] In accordance with an aspect, the flat rectangular surface formed on the upper surface of the vanes is disposed at an angle of 1050 with the central axis of the impeller.
[0046] In accordance with an aspect, a balancing drill hole is formed on each vane at a diameter of 75 mm from the central axis of the impeller.
[0047] In accordance with an aspect, the diameter of the balancing drill hole is 6 mm.
[0048] In accordance with an aspect, the depth of the balancing drill hole is 1 mm.
[0049] Various objects, features, aspects and advantages of the inventive subject matter will become more apparent from the following detailed description of preferred embodiments, along with the accompanying drawing figures in which like numerals represent like components.

BRIEF DESCRIPTION OF THE DRAWINGS
[0050] The accompanying drawings are included to provide a further understanding of the present disclosure, and are incorporated in and constitute a part of this specification. The drawings illustrate exemplary embodiments of the present disclosure and, together with the description, serve to explain the principles of the present disclosure.
[0051] FIG.1 illustrates an engine cooling unit through block diagram in accordance with the prior art.
[0052] FIG.2A depicts a layout of the engine in accordance with the present disclosure.
[0053] FIG.2B depicts an enlarged view of the pump housing and connection with the shaft in accordance with the present disclosure.
[0054] FIG.3A also depicts an enlarged view of the pump housing and connection with the shaft in accordance with the present disclosure
[0055] FIG.3B depicts a front view of the impeller in accordance with the present disclosure.
[0056] FIG.4 depicts an isometric view of the impeller in accordance with the present disclosure.
[0057] FIG.5A depicts a cross-sectional view of the blade in accordance with the present disclosure.
[0058] FIG.5B depicts a two-dimensional view of the impeller in accordance with the present disclosure.
[0059] FIG.6 depicts a full load curve for an engine in accordance with the present disclosure.
[0060] FIG.7 depicts a water temperature curve for a pump in accordance with the present disclosure

DETAILED DESCRIPTION
[0061] The following is a detailed description of embodiments of the disclosure depicted in the accompanying drawings. The embodiments are in such details as to clearly communicate the disclosure. However, the amount of detail offered is not intended to limit the anticipated variations of embodiments; on the contrary, the intention is to cover all modifications, equivalents, and alternatives falling within the spirit and scope of the present disclosure as defined by the appended claims.
[0062] If the specification states a component or feature “may”, “can”, “could”, or “might” be included or have a characteristic, that particular component or feature is not required to be included or have the characteristic.
[0063] Exemplary embodiments will now be described more fully hereinafter with reference to the accompanying drawings, in which exemplary embodiments are shown. This disclosure may however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. These embodiments are provided so that this disclosure will be thorough and complete and will fully convey the scope of the disclosure to those of ordinary skill in the art. Moreover, all statements herein reciting embodiments of the disclosure, as well as specific examples thereof, are intended to encompass both structural and functional equivalents thereof. Additionally, it is intended that such equivalents include both currently known equivalents as well as equivalents developed in the future (i.e., any elements developed that perform the same function, regardless of structure).
[0064] Various terms as used herein. To the extent a term used in a claim is not defined below, it should be given the broadest definition persons in the pertinent art have given that term as reflected in printed publications and issued patents at the time of filing.
[0065] As used in the description herein and throughout the claims that follow, the meaning of “a,” “an,” and “the” includes plural reference unless the context clearly dictates otherwise. Also, as used in the description herein, the meaning of “in” includes “in” and “on” unless the context clearly dictates otherwise.
[0066] The recitation of ranges of values herein is merely intended to serve as a short hand method of referring individually to each separate value falling within the range. Unless otherwise indicated herein, each individual value is incorporated into the specification as if it were individually recited herein. All methods described herein can be performed in any suitable order unless otherwise indicated herein or otherwise clearly contradicted by context. The use of any and all examples, or exemplary language (e.g. “such as”) provided with respect to certain embodiments herein is intended merely to better illuminate the invention and does not pose a limitation on the scope of the invention otherwise claimed. No language in the specification should be construed as indicating any non-claimed element essential to the practice of the invention.
[0067] Groupings of alternative elements or embodiments of the invention disclosed herein are not to be construed as limitations. Each group member can be referred to and claimed individually or in any combination with other members of the group or other elements found herein. One or more members of a group can be included in, or deleted from, a group for reasons of convenience and/or patentability. When any such inclusion or deletion occurs, the specification is herein deemed to contain the group as modified thus fulfilling the written description of all groups used in the appended claims.
[0068] Aspects of the present disclosure relatesto an efficient and economical impeller for a centrifugal pump that works efficiently under different load and speed conditions of an engine.
[0069] FIG.2A depicts a layout of the engine in accordance with the present disclosure. It depicts a crankshaft 202 that converts the reciprocating motion of a piston into rotational motion. In addition, the front end of a crankshaft 202 is attached to a gear, sprocket, pulley 204, and vibration damper. The gear or sprocket is used to drive the camshaft, and the pulley 204 attached to the face of the crankshaft 202 is responsible to actuate a water pump 208 through a shaft 210 attached with the pulley 206 placed near the water pump 208. The enlarged view of the pump housing and connection with the shaft is depicted in FIG.2B & FIG.3A. Here, the water pump 208 is a centrifugal pump particularly adapted to incorporation and connection to an internal combustion engine.
[0070] Generally, in accordance with the present disclosure, the water pump 208 includes a pump housing 208-H connected with the shaft 210 coming out of the pulley 206. The water pump 208 further comprises a lower inlet port 208-I for taking the cold water from the outlet of the radiator module, and an upper port 208-U connected with the thermostat valve that regulates the flow of water when the temperature of the engine reaches above the required temperature.
[0071] The water pump 208 further comprises a special intake chamber overlying an impeller 300 having rectangular shaped blades. The intake chamber is formed with a spiral discharge portion and is located over the central portion of the impeller, such that the incoming water is directed in a spiral fashion projecting axially inwardly toward the impeller 300 and spirally about the axis of the impeller, with the water introduced into the impeller 300 adjacent the radially inner ends of the radial blades.
[0072] In addition, the central portion of the impeller 300 is provided with a connector boss that helps in building up the connection between the shaft 210 and the impeller 300 that in turn rotates the impeller. Moreover, a unitised seal 212 is provided in between the connector boss 304, and the shaft 210. The unitized seal is a dual action seal. This type of seal provides less wear and tear and better leak protection. In this manner, the housing 208-H of the pump 208 stays fixed on the shaft 210 and the impeller 300 rotates with the connector boss.
[0073] The defined technical configuration of the impeller 300 provides a highly efficient introduction of the water into the impeller and in particular, essentially eliminates cavitations without the development of special spiral blades.
[0074] FIG.3B depicts a front view of the impeller in accordance with the present disclosure.
[0075] FIG.4 depicts an isometric view of the impeller in accordance with the present disclosure.
[0076] The impeller 300 comprisesa circular base plate 302, wherein the centre of the circular base plate 302 is aligned with a central axis 300-C of the impeller 300. The diameter of the circular base plate 302 ranges in between 90 mm to 90.5 mm. The thickness of the circular base plate is 3mm.
[0077] The impeller further comprises a connector boss 304 of hollow cylindrical shape having a lower end 304-L and an upper end 304-U, wherein the connector boss 304 is integrated at a centre of the circular base plate 302 through the lower end 304-L as a single piece and the centre of the connector boss 304-C coincides with the central axis 303-I of the impeller 300. The outside diameter 304-OD of the connector boss 304 ranges in between 27.5 mm to 28.5mm, and an inside diameter 304-ID of the connector boss 304 ranges in between 15.80 mm to 15.87mm. The height 304-H of the connector boss 304 ranges in between 14.50 mm to 15 mm.
[0078] The impeller 300 further comprises a circular shroud 306 that is formed at a defined distance from the lower end 304-L of the connector boss 304 in a concentric manner. The annular space provided in between a lower end 304-L of the connector boss 304 and the circular shroud 306 comprises a concave shaped structure. The circular shroud 306 is of diameter ranges in between 48 mm to 49 mm.
[0079] It further comprises a plurality of vanes 308 extending outwards from the periphery of the lower end 304-L of the connector boss 304, wherein each vane 308 placed equidistantly with one another having a root region 308-R proximal to the lower end 304-L of the connector boss 304 and a tip region 308-T distal from the connector boss 304 terminating at an outer periphery of the circular base plate 302. The plurality of vanes 308 disposed around the connector boss in the radial manner. In addition, the vanes 308 are of rectangular shaped structure. The length of the vane 308 from the lower end of the connector boss 304 ranges in between 45 mm to 47 mm. The vanes 308 also comprises an upper 308-US and a lower 308-LS rectangular surface.
[0080] In order to define the structure of the vanes 308, the vanes 308 are divided in to three regions- root region 308-R, mid region 308-M, and tip region 308-T. The upper rectangular surface 308-US of each vane 308 comprises a C-shaped undercut extending outwards from a root region 308-R to a mid-region 308-M of the vanes. The length of the C-shaped undercut formed on the upper surface of each of the vane ranges between 15.5 mm to 16 mm. The upper surface of each of the vane further comprises a flat rectangular surface extending from the mid-region 308-M to the tip region 308-T of the vanes. The length of the rectangular shaped surface formed on the upper surface of each of the vane ranges between 30 mm to 31mm.
[0081] As mentioned earlier, the vanes 308 comprises the lower surface 308-LS, wherein the lower surface 308-LS of each of the vane308 comprises a concave shaped structure extending outwards from a root region 308-R to the mid region 308-M of the vanes. The concave shaped structure of the vanes at the lower surface and the concave structure provided in the annular space formed in between a lower end 304-L of the connector boss 304 and the circular shroud 306 helps in establishing a strong connection between the vanes 308 and the circular base plate 302. This in turn improving the strength of the structure. The lower surface of each of the vane comprises a rectangular shaped structure extending outwards from the mid region 308-M to the tip region 308-Tof the vanes.
[0082] The tip region 308-T of the vane 308 is disposed in the same plane as that of the root region 308-R. The number of vanes around the connector boss 304 is 12 and the angle between the vanes 308 of the impeller is 300. Here, the impeller is made of cast iron grade 20 that increases the strength of the impeller. In addition, the flat rectangular surface formed on the upper surface 308-U of the vanes 308 is disposed at an angle of 1050 with the central axis of the impeller.
[0083] Moreover, a balancing drill hole 310 is also formed on each vane 308 at a diameter of 75 mm from the central axis of the impeller. The diameter of the balancing drill hole is 6 mm, and the depth of the balancing drill hole is 1 mm.
[0084] FIG.5A depicts a cross sectional view of the blade in accordance with the present disclosure.
[0085] FIG.5B depicts a 2D view of the impeller in accordance with the present disclosure.

TEST RESULTS
[0086] The graph shown in FIG.6 illustrates that the water pump enclosing the proposed impeller is tested on 65hp power rating with maximum torque of 280Nm. As per the graph, the water pump performs efficiently up to the level of 65hp power rating with maximum torque of 280Nm.
[0087] The graph shown in FIG.7 illustrates about the increment in the cooling efficiency of the water pump due to the proposed technical configuration of the proposed Impeller in water pump up to the level of 65hp power rating with maximum torque of 280Nm. The targeted maximum water outlet temperature is 110°C during extreme hot condition. The targeted maximum water outlet temperature is 100°C during normal ambient condition. As shown in the FIG.7, the defined technical configuration of the impeller helps in achieving maximum 100°C at the normal ambient condition (25±3°C) and also the 110°C during extreme hot conditions.
[0088] When the water outlet temperature exceeds the temperature of 110°C, the ECU automatically control the functioning of the engine by decreasing the level of required power output and the torque output.

WORKING MECHANISM
[0089] The automotive water pump in which the proposed impeller is mounted is driven by a belt connected to the engine’s crankshaft. The pump circulates the fluid when the engine is running. The water pump is vital to the operation of a car engine as it ensures that coolant flows through the cylinder head, radiator, hoses, and cylinder block and maintains the optimum automotive operating temperature; it is usually driven by a belt from a crankshaft pulley or sprocket.
[0090] This automotive water pump uses centrifugal force and impeller blades to move coolant through the various hoses and channels that make up the cooling system. After the coolant flows around the engine, usually at the front of the car, it is hosed to the radiator, where the hot coolant is cooled by air movement along with the radiator fins. It then leaves the radiator and returns to the water pump, where the process starts over.
[0091] As mentioned, the proposed impeller comprises 12 powerful blade (Fins) providing the optimum efficiency to the diesel engine without consuming more power. The specially configured rectangular shaped vanes with C-shaped undercut, gives the better radial flow of water to pass through the defined flow path. In addition, the configured undercut in blades gives additional swirl to the flow that is required in the cylinder block for proper absorption of excessive heat.
[0092] Also it helps in reduce the chances of water backflow when the cooled water passed through the cylinder block that in turn protects the combustion chamber from failure arises due to engine overheating.
[0093] It also helps in controlling the in cylinder combustion that in turn results in proper burning of fuel inside the combustion chamber that reduces the chances of formation of NOx. When the controlled combustion takes place, the generation of heat release during the combustion has been controlled significantly. Due to the controlled combustion it prevents from the combustion peak firing pressure. By controlling overheating of the engine during combustion it helps in reducing the friction between the components present inside the engine. All the above mentioned measures helps in improving the engine specific fuel consumption.
[0094] In addition, the thermostat present in the system with the capacity of 0.9bar pressure helps in maintaining the required temperature in the cylinder block. When the temperature in the cylinder block exceeds the required limit, the cooling system will get initiated.
[0095] Furthermore, the Impeller is made of cast iron grade 20 IS 210 that make the impeller cost-effective with good casting property, better vibration and damping ,increase corrosion resistance compared to unalloyed steels, typically 3-4times stronger in compression then tension.
[0096] In all, due to the proposed technical configuration of the impeller, the centrifugal pump become highly efficient that makes the cooling system more effective and the proposed technical configuration helps in easy mounting of the impeller inside the casing of the pump that makes the pump well- integrated, compact and aesthetically pleasing secured easily inside the engine block.
[0097] In addition to this, due to the proposed configuration of the impeller, the pump works efficiently that helps radiator module to effectively serves two purposes – the first one is to reduce the temperature of the exhaust gases that can be further mixed with the fresh charge entering the intake manifold through inlet port, this in turn results in the reduction of NOx emission. The second one is to cool the engine through proper circulation of coolant such as water.
[0098] In all, the proposed technical configuration of the impeller increases the overall efficiency of pump that in turn engine as well as an agricultural vehicle.
[0099] It should be apparent to those skilled in the art that many more modifications besides those already described are possible without departing from the inventive concepts herein. The inventive subject matter, therefore, is not to be restricted except in the spirit of the appended claims. Moreover, in interpreting both the specification and the claims, all terms should be interpreted in the broadest possible manner consistent with the context. In particular, the terms “comprises” and “comprising” should be interpreted as referring to elements, components, or steps in a non-exclusive manner, indicating that the referenced elements, components, or steps may be present, or utilized, or combined with other elements, components, or steps that are not expressly referenced. Where the specification claims refers to at least one of something selected from the group consisting of A, B, C ….and N, the text should be interpreted as requiring only one element from the group, not A plus N, or B plus N, etc.
[00100] The foregoing description of the specific embodiments will so fully reveal the general nature of the embodiments herein that others can, by applying current knowledge, readily modify and/or adapt for various applications such specific embodiments without departing from the generic concept, and, therefore, such adaptations and modifications should and are intended to be comprehended within the meaning and range of equivalents of the disclosed embodiments. It is to be understood that the phraseology or terminology employed herein is for the purpose of description and not of limitation. Therefore, while the embodiments herein have been described in terms of preferred embodiments, those skilled in the art will recognize that the embodiments herein can be practiced with modification within the spirit and scope of the appended claims.
[00101] While the foregoing describes various embodiments of the invention, other and further embodiments of the invention may be devised without departing from the basic scope thereof. The scope of the invention is determined by the claims that follow. The invention is not limited to the described embodiments, versions or examples, which are included to enable a person having ordinary skill in the art to make and use the invention when combined with information and knowledge available to the person having ordinary skill in the art.

ADVANTAGES OF THE INVENTION
[00102] The present disclosure provides an efficient and economical centrifugal pump that works under different load & speed conditions of an engine.
[00103] The present disclosure provides the centrifugal pump that increases the cooling efficiency of the engine cooling unit and the EGR unit.
[00104] The present disclosure provides the centrifugal pump that incurs less maintenance cost.
[00105] The present disclosure provides the centrifugal pump that is impervious to the operating environment.
[00106] The present disclosure provides the centrifugal pump that sustains the problem of cavitations.
[00107] The present disclosure provides the centrifugal pump that overcomes problem of vibration arises due to surrounding condition.
[00108] The present disclosure provides the centrifugal pump that gives better performance & reliability.
[00109] The present disclosure provides the centrifugal pump that reduces the chances of pitting on the impeller or casing of the pumps.
[00110] The present disclosure provides the centrifugal pump that helps in improving the performance and reliability of the engine as well as the agricultural vehicle.

, Claims:
WE CLAIM
1. An impeller (300) for increasing an efficiency of centrifugal pump, the impeller (300) comprising:
a circular base plate (302), wherein the centre of the circular base plate(302) aligned with a central axis of the impeller;
a connector boss (304)having a lower end (304-L) and an upper end (304-U), wherein the connector boss (304) integrated at a centre of the circular base plate (302) through the lower end (304-L) forming a single piece, and the centre of the connector boss (304) coincides with the central axis of the impeller (300);
a circular shroud (306) formed at a defined distance from the lower end (304-L) of the connector boss(304) in concentric manner, wherein an annular space provided in between a lower end of the connector boss (304-L) and the circular shroud (306) comprises a concave shaped structure; and
a plurality of rectangular-shaped vanes (308) extending outwards from the periphery of the lower end (304-L) of the connector boss (304), wherein each vane (308) placed equidistantly with one another having a root region (308-R) proximal to the connector boss (304) and a tip region (308 -T) distal from the connector boss (304) terminating at an outer periphery of the circular base plate (302);
characterized in that an upper rectangular surface of the rectangular shaped vane includes a C-shaped undercut extending outwards from a root region (308-R) to a mid-region (308-M) and a flat rectangular surface extending from the mid-region (308-M) to the tip region (308-T) of the vanes, and
the lower rectangular surface of the rectangular shaped vane includes a concave shaped structure extending outwards from a root region (308-R) to the mid region (308-M) and a rectangular shaped structure extending outwards from the mid region (308-M) to the tip region (308-T) of the vanes.
2. The impeller (300) as claimed in claim 1, wherein the diameter of the circular base plate (302) ranges in between 90 mm to 90.5 mm.

3. The impeller (300) as claimed in claim 1, wherein the thickness of the circular base plate (302) ranges in between 3 mm to 4 mm.

4. The impeller (300) as claimed in claim 1, wherein the connector boss (304) is of hollow cylindrical shape.

5. The impeller (300) as claimed in claim 4, wherein an outside diameter (304-OD) of the connector boss (304) ranges in between 27.5 mm to 28.5mm.

6. The impeller (300) as claimed in claim 4, wherein an inside diameter (304-ID) of the connector boss (304) ranges in between 15.80 mm to 15.87mm.

7. The impeller (300) as claimed in claim 4, wherein the height (304-H) of the connector boss (304) ranges in between 14.50 mm to 15 mm.

8. The impeller (300) as claimed in claim 4, wherein the connector boss (304) is integrated to the centre of the circular base plate forming the single piece for engaging a drive shaft of a motor.

9. The impeller (300) as claimed in claim 1, wherein the circular shroud (306) is of diameter ranges in between 48 mm to 49 mm.

10. The impeller (300) as claimed in claim 1, wherein the plurality of vanes (308) disposed around the connector boss (304) in the radial manner.

11. The impeller (300) as claimed in claim 10, wherein the vanes (308) are of rectangular shaped structure.

12. The impeller (300) as claimed in claim 10, wherein the vanes (308) comprises an upper (308-US) and a lower (308-LS) surface.

13. The impeller (300) as claimed in claim 10, wherein the length of the vane (308) from the lower end (304-L) of the connector boss (304) ranges in between 45mm to 47 mm.

14. The impeller (300) as claimed in claim 10, wherein the length of the C-shaped undercut formed on the upper surface (308-US) of each of the vane (308) ranges between 15.5 mm to 16 mm.

15. The impeller (300) as claimed in claim 10, wherein the length of the rectangular shaped surface formed on the upper surface (308-US) of each of the vane ranges between 30 mm to 31mm.

16. The impeller (300) as claimed in claim 1, wherein the length of the concave shaped structure extending outwards formed on the lower surface (308-LS) of each of the vane ranges between 15.5 mm to 16 mm.

17. The impeller (300) as claimed in claim 12, wherein the length of the rectangular shaped structure formed on the lower surface (308-LS) of each of the vane ranges between 30 mm to 31mm.

18. The impeller (300) as claimed in claim 12, wherein the tip region (308-T) of the vane (308) is disposed in the same plane as that of the root region (308-R).

19. The impeller (300) as claimed in claim 10, wherein the number of vanes formed on the impeller ranges from 12 to 14.

20. The impeller (300) as claimed in claim 10, wherein the angle between the vanes of the impeller is an acute angle.

21. The impeller (300) as claimed in claim 1, wherein the impeller is made of cast iron grade 20.

22. The impeller (300) as claimed in claim 12, wherein the flat rectangular surface formed on the upper surface (308-US) of the vanes (308) is disposed at an angle of 1050 with the central axis of the impeller.

23. The impeller(300) as claimed in claim 1, wherein a balancing drill hole (310) is formed on each vane at a diameter of 75 mm from the central axis of the impeller.

24. The impeller (300) as claimed in claim 23, wherein the diameter of the balancing drill hole (310) ranges between 6 mm to 8 mm.

25. The impeller (300) as claimed in claim 23, wherein the depth of the balancing drill hole (310) ranges between 0.5mm to 1 mm.