KR102617798B1 - Impeller - Google Patents

Abstract

The present invention relates to an impeller that improves head and efficiency, and for this purpose, an impeller is included on one side of the pump to flow fluid from the suction port to the discharge port; The impeller includes a hub; a plurality of main vanes configured along a radial line on one side of the hub to induce suction of fluid; And a support vane configured on the other side of the hub to support the fluid sucked along the plurality of main vanes to improve head efficiency by dispersing the fluid and increasing the discharge pressure when the fluid is discharged toward the discharge port. An impeller that improves efficiency can be provided.

Description

Impeller that improves head and efficiency {Impeller}

The present invention relates to an impeller that improves head and efficiency.

In general, a centrifugal pump is a pump that rotates an impeller to give rotational force to water and pumps water through the action of centrifugal force. It includes an impeller with a vane, a shaft that supports the impeller, and a motor that rotates the shaft.

In the centrifugal pump, the fluid first enters the center of the impeller through the suction passage, receives rotational force while passing between the vanes, and the pressure increases. While passing through the vanes, the velocity energy is converted into pressure energy and enters the casing. The casing collects the fluid coming out of the impeller and discharges it through the discharge port.

Meanwhile, the impeller of a centrifugal pump can be divided into a closed type, a semi-open type, and an open type depending on the form in which the vane is connected to the shroud.

The closed type is a structure in which a vane is formed between two shrouds, the semi-open type is a structure in which a vane is formed on one side of one shroud, and the open type is a structure in which there is no shroud and the vane is formed on the hub axis.

In order to increase the head of the impeller of a conventional centrifugal pump, the pressure generation value must be increased by reducing the value on the discharge port side compared to the suction port side, and the discharge angle must be designed to be close to a right angle. Therefore, it is necessary to proceed with the method of making wooden molds for casting production. There is a problem that there is a limit to the lift that can be raised due to the limitation.

In addition, the closed type impeller has a problem in that the axial thrust increases because the areas where pressure acts on the front shroud and the back shroud are different, and it causes vibration during pump operation, ultimately shortening the life of the centrifugal pump.

Republic of Korea Patent No. 10-0541330 (announced on January 11, 2006) Republic of Korea Patent No. 10-1545278 (announced on August 19, 2015)

The present invention configures a support vane on the impeller, allowing the value of the pressure generated during discharge to adjust the lift rate of lift according to the ratio of the length of the support vane to the main vane, thereby enabling the head and efficiency to overcome the limitations of wooden mold manufacturing. Provides an impeller that improves.

In addition, the present invention allows the support vane core to be manufactured as a core when manufacturing the wooden mold of the impeller, so that it can be added when necessary, and also allows the support vane core to be removed when it is necessary to manufacture an impeller for a pump with a low head, ultimately resulting in a standard We provide an impeller that improves head and efficiency, allowing you to expand the applicability of the model.

The problems to be solved by the present invention are not limited to those mentioned above, and other problems to be solved that are not mentioned can be clearly understood by those skilled in the art from the description below. will be.

In order to solve the problem to be solved above, according to an embodiment of the present invention, an impeller is included on one side of the pump to flow fluid from the suction port to the discharge port; The impeller includes a hub; a plurality of main vanes configured along a radial line on one side of the hub to induce suction of fluid; And a support vane configured on the other side of the hub to support the fluid sucked along the plurality of main vanes to improve head efficiency by dispersing the fluid and increasing the discharge pressure when the fluid is discharged toward the discharge port. .

According to an embodiment of the present invention, the main vane starts at a position spaced at a certain interval around the hub and forms an end in a streamlined shape; This may include forming the end width to become narrower toward the end compared to the starting width.

According to an embodiment of the present invention, the cross-sectional shape of the vane is such that the partial surface corresponding to the inner surface based on the hub is formed as a streamlined surface to support the smooth flow of fluid; The partial surface corresponding to the outer surface based on the hub may include a diagonal diagonal surface formed to have support for the flow of fluid.

According to an embodiment of the present invention, the support vane starts at a position spaced at a certain distance from one end of the main vane and forms an end in a streamlined shape; The start width and end width may include a length ratio of 1:0.5 to 1.

According to an embodiment of the present invention, the cross-sectional shape of the support vane is such that the partial surface corresponding to the inner surface based on the hub is formed as a streamlined surface to support the smooth flow of fluid; The partial surface corresponding to the outer surface based on the hub may include a diagonal diagonal surface formed to have support for the flow of fluid.

According to an embodiment of the present invention, the impeller may include a closed-type impeller that is formed at each end of the hub and forms first and second shrouds so that a main vane and a support vane are formed on the inside.

According to an embodiment of the present invention, the first shroud or the second shroud includes at least one bag supporting the pressure imbalance caused by the difference in structural shape between the first and second shrouds to improve head efficiency. It may include a vane.

According to an embodiment of the present invention, the back vane may be formed in a streamlined shape to smoothly distribute the pressure acting on the shroud on which the back vane is configured.

According to an embodiment of the present invention, the back vane may include chamfers formed at each end to minimize friction with the fluid and support smooth dispersion.

According to the means for solving the problem of the present invention described above, by configuring a support vane in the impeller, the value of the pressure generated during discharge can be adjusted to adjust the lift rate according to the ratio of the length of the support vane to the main vane, thereby eliminating the limitations of wooden mold manufacturing. It has the effect of helping you overcome it.

In addition, according to the means for solving the problem of the present invention described above, the support vane is manufactured as a core when manufacturing the wooden mold of the impeller, so it can be added when necessary, and the support vane core can be removed when it is necessary to manufacture an impeller for a pump with a low head. This ultimately has the effect of expanding the scope of application of the standard model.

In addition, according to the problem-solving means of the present invention described above, there is an effect of shortening the standard production work time, such as production cost, production schedule, and mold management, by establishing a standard model for a centrifugal pump with a wide application range.

1 is a schematic diagram showing the use of a centrifugal pump according to the present invention.
Figure 2 is a cross-sectional view of the impeller according to the present invention.
Figure 3 is a side view of the impeller according to the present invention.
Figure 4 is a partial enlarged view showing the configuration of the main vane and support vane according to the present invention.
Figure 5 is an enlarged view of the main vane according to the present invention.
Figure 6 is an enlarged view of the support vane according to the present invention.
Figure 7 is a side view of the impeller showing the configuration of the back vane according to the present invention.

Hereinafter, specific embodiments of the present invention will be described with reference to the drawings. The detailed description below is provided to provide a comprehensive understanding of the methods, devices and/or systems described herein. However, this is only an example and the present invention is not limited thereto.

In describing the embodiments of the present invention, if it is determined that a detailed description of the known technology related to the present invention may unnecessarily obscure the gist of the present invention, the detailed description will be omitted. In addition, the terms described below are terms defined in consideration of functions in the present invention, and may vary depending on the intention or custom of the user or operator. Therefore, the definition should be made based on the contents throughout this specification. The terminology used in the detailed description is merely for describing embodiments of the present invention and should in no way be limiting. Unless explicitly stated otherwise, singular forms include plural meanings. In this description, expressions such as “comprising” or “comprising” are intended to indicate certain features, numbers, steps, operations, elements, parts or combinations thereof, and one or more than those described. It should not be construed to exclude the existence or possibility of any other characteristic, number, step, operation, element, or part or combination thereof.

Hereinafter, an impeller that improves head and efficiency will be described with reference to the attached drawings.

The impeller 10 of the present invention is mounted on a submersible pump 1, etc., as shown in FIG. 1, and forces the fluid to be discharged from the suction port to the discharge port using centrifugal force generated by rotation. In this case, the impeller 10 is applied to a centrifugal pump.

As shown in FIGS. 2 and 3, the impeller 10 includes first and second shrouds 110 and 120 at both ends, and the first and second shrouds 110 at the center. A hub 130 configured to support (120) and a plurality of main vanes configured between the first and second shrouds 110 and 120 to support suction and discharge of fluid by centrifugal force caused by rotation. (140) and a plurality of support vanes (150) configured between the first and second shrouds (110) and (120) and between the plurality of main vanes (140) to support the head lift rate to be adjusted. , and is configured on one or both sides of the first shroud 110 or the second shroud 120 to minimize the difference in pressure acting on each of the first and second shrouds 110 and 120 to achieve axial thrust. It can be configured to include at least one back vane 160 to reduce.

The first shroud 110 may be configured to have a certain area at one end of the hub 130, for example, at the front.

The second shroud 120 may be configured to have a certain area at the other end of the hub 130, for example, on the back.

In this case, the first and second shrouds 110 and 120 are configured to have a certain area at each end of the hub 130, thereby providing a cloud-type impeller. Accordingly, a flow path is formed in the impeller 10 to allow suction and discharge of fluid in the space between the first and second shrouds 110 and 120. That is, the impeller 10 has an inlet 12 formed between the first and second shrouds 110 and 120 at a position corresponding to the front of the hub 130, and an intake port 12 is formed at a position corresponding to the rear side of the hub 130. A discharge port 140 is configured between the first and second shrouds 110 and 120 in the position. In addition, the flow path formed between the first and second shrouds 110 and 120 is formed in a streamlined shape to induce a smooth flow of fluid from the suction port 12 to the discharge port 14.

In addition, the first shroud 110 is formed in a streamlined shape to minimize damage due to friction with fluid when the impeller 10 rotates at high speed due to the characteristics of the front of the hub 130, and the second shroud 120 ) is formed on the back of the hub 130, for example, is formed in a shape that adopts a structure to maintain airtightness with the motor configured on one side of the pump.

The hub 130 is located in the center, supports the first and second shrouds 110 and 120, and maintains a connection with the motor included in the pump 1, thereby supporting the impeller 10. Supports high-speed rotation. In this case, the center of the hub 130 includes an insertion hole 132 that supports the insertion and fixation of the motor shaft extending from the motor.

The main vane 140 is configured between the first and second shrouds 110 and 120 to discharge fluid from the suction port 12 to the discharge port 14 by centrifugal force caused by rotation.

As shown in FIGS. 4 and 5, the main vane 140 may be formed in a plurality radially around the hub 130. For example, the main vane 140 consists of 3 to 8 locations. Of course, it is not limited to this, and the main vane 140 may be located at different locations depending on the purpose, installation environment, or head efficiency.

The main vane 140 is formed to start at a certain distance (t1) from the hub 130 and end at the outer periphery of the shroud. In this case, the main vane 140 is formed in a streamlined shape like an involute curve to allow fluid to flow smoothly from the suction port 12 to the discharge port 14.

In addition, the part corresponding to the beginning located on the suction port 12 side of the main vane 140 is called the starting width (L1), and the portion corresponding to the end located on the discharge port 14 side is called the end width (L2). , the starting width (L1) and the ending width (L2) can be formed at a length ratio of 1:0.3 to 0.6. Here, the reason why the starting width is larger than the ending width is to minimize damage caused by impact with the fluid sucked by centrifugal force. In this case, if the end width L2 is less than 0.3 length ratio, the end of the main vane 140 may be easily damaged by fluid having centrifugal force, and if it exceeds 0.6, rotational efficiency may be reduced due to increased weight.

In addition, the main vane 140 has an obtuse angle a1 between its start and end with respect to the center of the hub 130. For example, the formation angle (a1) of the main vane 140 is formed from 100° to 130°.

In addition, as shown in FIG. 5, the main vane 140 has a first close contact surface 142 formed on the surface of the first shroud 110, and a second close contact surface formed on the surface of the second shroud 120 ( 144), but the first side 142 becomes narrower with respect to the second side 144 from the beginning to the end.

In addition, the cross section of the main vane 140 is a surface corresponding to the inner side based on the hub 130, which smoothly guides fluid from the starting width (L1) to the ending width (L2) of the main vane 140 and disperses fluid and shock. It is formed by a streamlined streamlined surface 146 that supports the hub 130, and is an oblique surface that supports the cross-sectional thickness and disperses the fluid to ensure smooth flow. It can be composed of (148).

The support vane 150 is configured between the first and second shrouds 110 and 120 and between the plurality of main vanes 140 to improve head efficiency. In this case, the support vane 150 allows the head efficiency to be adjusted by the length difference from the main vane 140, thereby providing the production of a standard model of wooden mold.

As shown in FIGS. 4 and 6, at least one of the support vanes 150 may be configured radially between the plurality of main vanes 140. In some cases, the support vane 150 may be omitted.

The support vane 150 is formed to start at a certain distance from the hub 130, that is, at a certain distance (t2) from the main vane 140, and end at the outer periphery of the shroud. In this case, the main vane 140 is formed in a streamlined shape like an involute curve to allow fluid to flow smoothly from the suction port 12 to the discharge port 14. In this case, the constant interval (t1) between the main vane 140 in the hub 130 and the constant interval (t2) between the main vane 140 and the support vane 150 are 1; It is formed in a length ratio of 1.5 to 3.

In addition, the part corresponding to the beginning located on the suction port 12 side of the support vane 150 is called the starting width l1, and the part corresponding to the end located on the discharge port 14 side is called the end width l2. , the starting width (l1) and the ending width (l2) can be formed at a length ratio of 1:0.5 to 1. Here, the reason why the starting width is larger than the ending width is to minimize damage caused by impact with the fluid sucked by centrifugal force. In this case, if the end width l2 is less than 0.5 length ratio, the end of the main vane 140 may be easily damaged by fluid having centrifugal force, and if it exceeds 1, rotational efficiency may be reduced due to increased weight.

In addition, the support vane 150 has a forming angle a2 between the start and end of the hub 130 at an acute angle. For example, the formation angle (a2) of the support vane 150 is formed from 30° to 75°.

In addition, as shown in FIG. 6, the support vane 150 has a first close contact surface 152 formed on the surface of the first shroud 110, and a second close contact surface formed on the surface of the second shroud 120 ( 154), but the first side 152 becomes narrower with respect to the second side 154 from the beginning to the end.

In addition, the cross section of the support vane 150 is a surface corresponding to the inner side based on the hub 130, and smoothly guides fluid from the starting width (l1) to the end width (l2) of the support vane 150 and disperses fluid and shock. It is formed by a streamlined streamlined surface 156 that supports the hub 130, and is an oblique surface that supports the cross-sectional thickness and disperses the fluid to ensure smooth flow. It can be composed of (158).

Ultimately, the support vanes 150 are formed in the space between the plurality of main vanes 140, and disperse the fluid sucked between the main vanes 140 and increase the head of the pump through an auxiliary action of increasing pressure energy. Enables efficiency to be improved or adjusted. Additionally, the support vane 150 may be omitted depending on the purpose of use of the pump, installation environment, or required head efficiency.

The back vane 160 is formed on the first shroud 110 or the second shroud 120 by offsetting the pressure difference that acts as an area imbalance due to the structural difference between the first and second shrouds 110 and 120. , Minimize shaft thrust to suppress vibrations and improve the durability of the pump. For example, the back vane 160 may be formed on the second shroud 120.

The back vane 160 is formed to have a certain height on a shroud, for example, the second shroud 120, and is formed radially with respect to the hub 130.

In addition, as shown in FIG. 7, the back vane 160 is formed in a streamlined shape to smoothly distribute the pressure acting on the shroud.

In addition, each end of the back vane 160 may be provided with a chamfer 162 that minimizes friction with the fluid and supports the fluid to smoothly distribute pressure.

Accordingly, the back vane 160 reduces axial thrust by offsetting the pressure imbalance caused by the structural shape difference between the first and second shrouds 110 and 120. In addition, when the back vane 160 is formed on the second shroud 120, it may have the side effect of reducing axial thrust by inducing the pressure acting on the back to flow into the discharge port 14.

The above description is merely an illustrative explanation of the technical idea of the present invention, and various modifications and variations can be made by those skilled in the art without departing from the essential characteristics of the present invention. Accordingly, the embodiments expressed in the present invention do not limit the technical idea of the present invention, but are for illustrative purposes, and the scope of the present invention is not limited by these embodiments. The scope of protection of the present invention should be interpreted in accordance with the claims below, and all technical ideas that are equivalent or within the equivalent scope should be construed as being included in the scope of rights of the present invention.

10: Impeller 110: First shroud
120: second shroud 130: hub
132: Insertion hole 140: Main vane
142, 152: first contact surface 144, 154: second contact surface
146, 156: streamlined side 148,158: diagonal side
150: Support vane 160: Back vane
162: Chamfer

Claims (9)

delete delete An impeller is included on one side of the pump to flow fluid from the suction port to the discharge port;
The impeller includes a hub;
a plurality of main vanes configured along a radial line on one side of the hub to induce suction of fluid; and
It includes a support vane configured on the other side of the hub to support the fluid sucked along the plurality of main vanes to improve head efficiency by dispersing the fluid and increasing the discharge pressure when the fluid is discharged toward the discharge port,
The main vane is,
Starting from positions spaced at regular intervals around the hub, the ends are formed in a streamlined shape;
It is formed so that the end width becomes narrower towards the end compared to the starting width.
The cross-sectional shape of the main vane is,
The partial surface corresponding to the inner surface based on the hub is formed as a streamlined surface to support the smooth flow of fluid;
The partial surface corresponding to the outer surface based on the hub is an oblique diagonal surface to have support for the flow of fluid;
An impeller that improves head and efficiency.
The method of claim 3, wherein the support vane is:
Starting from a position spaced at a certain distance from one end of the main vane, the end is formed in a streamlined shape;
The starting and ending widths have a length ratio of 1:0.5 to 1;
An impeller that improves head and efficiency, characterized in that it is formed.
According to paragraph 4,
The cross-sectional shape of the support vane is,
The partial surface corresponding to the inner surface based on the hub is formed as a streamlined surface to support the smooth flow of fluid;
The partial surface corresponding to the outer surface based on the hub is an oblique diagonal surface to have support for the flow of fluid;
An impeller that improves head and efficiency.
The method of claim 3, wherein the impeller is:
A closed type formed at each end of the hub and having first and second shrouds to form a main vane and a support vane on the inside;
An impeller that improves head and efficiency.
The method of claim 6, wherein the first shroud or the second shroud,
At least one back vane supporting the first and second shrouds to improve head efficiency by offsetting the pressure imbalance caused by the structural shape difference between the first and second shrouds;
An impeller that improves head and efficiency, comprising:
The method of claim 7, wherein the back vane is:
Streamlined so that the pressure acting on the shroud on which the back vane is constructed can be smoothly distributed;
An impeller that improves head and efficiency, characterized in that it is formed.
The method of claim 7, wherein the back vane is:
Chamfers formed at each end to minimize friction with the fluid and support smooth dispersion;
An impeller that improves head and efficiency, comprising: