JP2022053726A - Vortex pump - Google Patents

Abstract

To provide a vortex pump improved in pump efficiency.SOLUTION: An impeller 15 used for a vortex pump includes a plurality of blade grooves 15b in a circumferential direction of an outer peripheral end part on both side faces of a disk-like member. The blade grooves 15b adjacent to each other in the circumferential direction are partitioned by a blade 15c, and include: blade groove upstream side faces 15b1 as faces located in a direction opposite to a rotational direction R of the impeller 15 in the blade grooves 15b; and blade groove downstream side faces 15b2 as faces located in the rotational direction R in the blade grooves 15b. A diameter direction inner part of the blade groove upstream side faces 15b1 is formed so as to recline backward in a direction opposite to the rotational direction R with respect to a reference line connecting the rotation center P0 of the disk-like member and a radial direction inner end part P1 of the blade groove upstream side faces 15b1. A radial direction outer part of the blade groove downstream side faces 15b2 is formed so as to incline forward in the rotational direction R with respect to the reference line connecting the rotation center P0 and the radial direction inner end part P2 of the blade groove downstream side faces 15b2.SELECTED DRAWING: Figure 5

Description

The present invention relates to a vortex pump.

A vortex pump is known in which a disk-shaped impeller connected to a rotating shaft of a motor is rotated in a region sandwiched between a casing cover and a casing liner to discharge water sucked from a suction port from a discharge port. (See, for example, Patent Document 1).

A conventional vortex pump includes an impeller, a plurality of blades (blades) on the outer periphery of the impeller, and a blade groove formed between the blades. When the impeller is rotated at high speed, a circulating flow is formed in the water in the blade groove by the force of the impeller rotating and pushing out the water. Then, due to the pressure generated by this circulating flow, the water between the blades is discharged from the discharge port.

In such a vortex pump, it is important to smoothly generate, sustain, and strengthen the circulating flow generated by the rotation of the impeller in order to improve the pump efficiency, and the groove shape between the impeller blades has a large effect on the pump performance. Affect.

Japanese Unexamined Patent Publication No. 2016-173043

Various conventional vortex pumps with improved impellers have been developed, but they are still insufficient, and it is desired to provide a technology that makes it possible to further improve the pump efficiency.

Therefore, the present invention solves the above-mentioned conventional problems, and an object of the present invention is to provide a vortex pump capable of improving pump efficiency.

In order to achieve this object, the vortex pump according to the present invention is a vortex pump in which the liquid sucked from the suction port by the rotation of the impeller is discharged from the discharge port through the flow path, and the impeller. Provide a plurality of blade grooves in the circumferential direction of the outer peripheral end of both side surfaces of the disk-shaped member. The blade grooves adjacent to each other in the circumferential direction are partitioned by the blades and are a surface located in the blade groove in the direction opposite to the rotation direction of the impeller, which is an upstream side surface of the blade groove, and a surface located in the blade groove in the rotation direction. It has a side surface downstream of the blade groove. The radial inner part of the upstream side surface of the blade groove is tilted backward in the direction opposite to the rotation direction with respect to the reference line connecting the rotation center of the disk-shaped member and the radial inner end portion of the upstream side surface of the blade groove. It is formed. The radial outer portion of the downstream side surface of the blade groove is formed so as to tilt forward in the rotation direction with respect to the reference line connecting the center of rotation and the radial inner end portion of the downstream side surface of the blade groove. To achieve the intended purpose.

According to the present invention, it is possible to provide a vortex pump capable of improving pump efficiency.

FIG. 1 is a perspective view showing the appearance of the vortex pump according to the first embodiment of the present invention. FIG. 2 is an exploded perspective view of the pump portion cut vertically downward through the rotation axis. It is sectional drawing of the cross section parallel to the rotation axis of a pump part. FIG. 4A is a perspective view of the first surface of the impeller, and FIG. 4B is a perspective view of the second surface of the impeller. FIG. 5A is a front view and a cross-sectional view thereof when the first surface of the impeller is viewed from the front, and FIG. 5B is an enlarged view around the blade groove of the impeller. FIG. 6 is a perspective view of the casing cover. FIG. 7 is a perspective view of the casing liner. FIG. 8 is a schematic cross-sectional view orthogonal to the rotation axis showing the flow of water in the pump portion. FIG. 9 is an enlarged view of the periphery of the impeller blade groove in the first modification. FIG. 10 is an enlarged view of the periphery of the impeller blade groove in the second modification.

The vortex pump according to the present invention is a vortex pump in which a liquid sucked from a suction port due to rotation of an impeller is discharged from a discharge port through a flow path, and the impeller is an outer periphery of both side surfaces of a disk-shaped member. A plurality of blade grooves are provided in the circumferential direction of the end. The blade grooves adjacent to each other in the circumferential direction are partitioned by the blades and are a surface located in the blade groove in the direction opposite to the rotation direction of the impeller, which is an upstream side surface of the blade groove, and a surface located in the blade groove in the rotation direction. It has a side surface downstream of the blade groove. The radial inner part of the upstream side surface of the blade groove is tilted backward in the direction opposite to the rotation direction with respect to the reference line connecting the rotation center of the disk-shaped member and the radial inner end portion of the upstream side surface of the blade groove. It is formed. The radial outer portion of the blade groove downstream side surface is formed so as to tilt forward in the rotation direction with respect to the reference line connecting the center of rotation and the radial inner end portion of the blade groove downstream side surface.

With this configuration, the angle between the rotation direction and the radial inner part of the upstream side of the blade groove becomes small, and when the circulating flow collides with the upstream side of the blade groove and flows into the blade groove, the circulating flow flows. Flows into the blade groove relatively smoothly, so it is possible to improve the pump efficiency. At the same time, the radial outer portion of the downstream side surface of the blade groove is tilted forward with respect to the reference line connecting the rotation center of the disk-shaped member and the radial inner end portion of the downstream side surface of the blade groove, thereby rotating the direction of rotation. The angle between the blade groove and the radial outer part of the upstream side surface of the blade groove becomes smaller, and the flow flowing out from the blade groove in the radial direction along the downstream side surface of the blade groove flows in the disc-shaped member in the flow path. Since it smoothly joins the flow in the direction of rotation, it is possible to further improve the pump efficiency.

Further, in the vortex pump according to the present invention, the radial outer portion of the upstream side surface of the blade groove is in the rotational direction with respect to the reference line connecting the rotation center of the disk-shaped member and the radial inner end portion of the upstream side surface of the blade groove. It may be formed so as to lean forward.

As a result, the thickness of the blade is the thinnest in the outer portion in the radial direction, but the minimum thickness of the blade can be increased even when the number of blade grooves is the same, and the possibility that the blade has higher strength is improved. do. Further, the angle formed by the radial outer portion of the upstream side surface of the blade groove and the rotation direction of the impeller becomes smaller. Therefore, in the velocity vector of the circulating flow flowing near the upstream side surface of the blade groove, the rotation direction component becomes large and smoothly merges with the flow from the suction port to the discharge port through the flow path, further improving the pump efficiency. Will be possible.

Further, in the vortex pump according to the present invention, the radial inner portion of the downstream side surface of the blade groove is formed so as to be in contact with the reference line connecting the rotation center of the disk-shaped member and the radial inner end portion of the downstream side surface of the blade groove. May be done.

As a result, the width of the radial inner portion of the blade groove in the circumferential direction can be increased, and the circulating flow can easily flow into the blade groove. This makes it possible to further improve the pump efficiency.

Hereinafter, embodiments for carrying out the present invention will be described with reference to the accompanying drawings. The following embodiments are examples that embody the present invention, and do not limit the technical scope of the present invention. In addition, the same parts are designated by the same reference numerals throughout the drawings, and the second and subsequent explanations are omitted.

(Embodiment 1)
First, the outline of the vortex pump 1 according to the first embodiment of the present invention will be described with reference to FIGS. 1 to 3. FIG. 1 is a perspective view showing the appearance of the vortex pump 1. FIG. 2 is an exploded perspective view of the pump unit 2. FIG. 3 is a cross-sectional view of the pump portion 2 cut vertically downward through the rotating shaft 18. The vortex pump 1 is also referred to as a Wesco type pump or a cascade pump.

The vortex pump 1 is mainly installed in a well, and is a pump that sucks a liquid such as water from a suction port 11 and discharges a liquid such as water sucked from the suction port 11 from a discharge port 12. As shown in FIG. 1, the vortex pump 1 includes a motor 10, a suction port 11, a discharge port 12, a pump casing 13, and a casing cover 14.

The pump casing 13 is an outer frame of the vortex pump 1. A suction port 11 and a discharge port 12 are provided on the upper portion of the pump casing 13. The suction port 11 is an inlet for sucking the liquid into the vortex pump 1, and the discharge port 12 is an outlet for discharging the liquid from the vortex pump 1. A motor 10 is provided inside the pump casing 13. The motor 10 is a drive source for rotating the impeller 15, which will be described later.

A casing cover 14 is attached to the lower part of the pump casing 13. The casing cover 14 is a lid for forming the flow path 19 in the pump casing 13 together with the casing liner 17 described later.

As shown in FIG. 2, a pump portion 2 is formed inside the casing cover 14. That is, a concave portion is provided in the lower portion of the pump casing 13, and the concave portion includes a pump portion 2 provided with a casing cover 14, an impeller 15, a mechanical seal 16, and a casing liner 17. The pump unit 2 is a portion of the vortex pump 1 that exerts a pump function.

In the pump portion 2, a through hole 13h is provided in the concave portion at the lower part of the pump casing 13. The through hole 13h is a hole for allowing the rotating shaft 18 of the motor 10 to pass through to the pump portion 2 side. The rotation shaft 18 is a shaft fixed to the impeller 15 and for rotating the impeller 15 by the power of the motor 10.

A concave casing liner 17 is attached to the pump casing 13 along the inner wall of the recess of the pump casing 13. The casing liner 17 is a member for forming the flow path 19 together with the casing cover 14. The casing liner 17 is provided with a protruding hole 17h. The protruding hole 17h is a hole for penetrating the rotating shaft 18. That is, the rotating shaft 18 projects toward the casing cover 14 from the through hole 13h and the protruding hole 17h. A cylindrical mechanical seal 16 is installed on the rotating shaft 18 so as to close the protruding hole 17h. The mechanical seal 16 is a member for preventing the liquid from flowing out to the motor 10 side from the protruding hole 17h provided in the casing liner 17.

A disk-shaped casing cover 14 is attached to the surface opposite to the surface of the impeller 15 facing the casing liner 17. The casing cover 14 is fixed to the pump casing 13. At this time, the casing cover 14 is attached so as to be in contact with the casing liner 17. As a result, a flow path 19 (see FIG. 3), which is a region surrounded by the casing cover 14 and the casing liner 17, is formed in the pump casing 13.

The rotary shaft 18 penetrates the mechanical seal 16, and a disk-shaped impeller 15 is connected to the tip of the rotary shaft 18. The impeller 15 is included and attached to the flow path 19 formed by the casing cover 14 and the casing liner 17. One surface of the impeller 15 faces the casing cover 14, and the other surface faces the casing liner 17. The impeller 15 is a member that is rotated by a motor 10 to generate a circulating flow in the liquid by a blade groove 15b provided in the impeller 15, which will be described later, and discharge the liquid sucked from the suction port 11 from the discharge port 12. ..

The flow path 19 is a region filled with a liquid and causing a circulating flow in the liquid by the rotation of the impeller 15.

The state of the flow path 19 is as shown in FIG. That is, the casing cover 14, the impeller 15, and the impeller 15 and the casing liner 17 are installed facing each other in an extremely close state. The total of the gap from the casing cover 14 to the impeller 15 and the gap from the impeller 15 to the casing liner 17 is, for example, 0.09 mm to 0.17 mm. By making the gap extremely small in this way, the inflow and outflow of the liquid from the gap is suppressed, and the impeller 15 is rotated at high speed (for example, a 125 W motor 10) while protecting the circulating flow generated in the blade groove 15b described later. When used, it can be 3000 rpm).

Next, the structure of the impeller 15 will be described with reference to FIGS. 4 and 5. FIG. 4A is a perspective view of the first surface 15x of the impeller 15, and FIG. 4B is a perspective view of the second surface 15y of the impeller 15. FIG. 5A is a front view and a cross-sectional view thereof when the first surface 15x of the impeller 15 is viewed from the front, and FIG. 5B is an enlarged view of the periphery of the blade groove 15b of the impeller 15. The first surface 15x of the impeller 15 is a surface facing the casing cover 14, and the second surface 15y of the impeller 15 is a surface facing the casing liner 17. Here, since the first surface 15x and the second surface 15y have the same structure except that the degree of protrusion of the fixed portion 15e1 and the fixed portion 15e2, which will be described later, are different, the structure of the first surface 15x will be described. The description of the two-sided 15y structure will be omitted.

As shown in FIG. 4A, a fixing portion 15e1 is provided at the center of the first surface 15x of the impeller 15. The fixing portion 15e1 is a portion where the rotating shaft 18 is inserted and the impeller 15 is fixed to the rotating shaft 18. A first thick portion 15a1 which is an annular plane concentric with the impeller 15 is provided at a position on the outer peripheral side of the fixed portion 15e1 so as not to be in contact with the fixed portion 15e1. A plurality of blade grooves 15b are provided in the circumferential direction at the outer peripheral end portion of the impeller 15 so as to cut the first thick portion 15a1.

As shown in FIG. 5A, the adjacent blade grooves 15b are separated by the blades 15c, and the blades 15c form the blade groove upstream side surface 15b1 and the blade groove downstream side surface 15b2. Then, as shown in FIG. 5B, the entire upstream side surface 15b1 of the blade groove (the radial inner portion which is the radial center side region and the radial outer portion which is the radial outer edge side region) is an impeller. The direction different from the rotation direction R (opposite to the rotation direction R) with respect to the reference line (broken line passing through P1 in the figure) connecting the rotation center P0 of 15 and the radial inner end P1 of the blade groove upstream side surface 15b1. It is formed so as to tilt backward by an angle α (direction).

On the other hand, the radial inner portion of the blade groove downstream side surface 15b2 is formed so as to be in contact with the reference line connecting the rotation center P0 of the impeller 15 and the radial inner end portion P2 of the blade groove downstream side surface 15b2. The radial outer portion of the blade groove downstream side surface 15b2 is on a reference line (broken line passing through P2 in the figure) connecting the rotation center P0 of the impeller 15 and the radial inner end portion P2 of the blade groove downstream side surface 15b2. On the other hand, it is formed so as to tilt forward by an angle β in the rotation direction R. That is, the blade groove downstream side surface 15b2 has a shape in which the outer portion in the radial direction is selectively tilted forward.

Then, the liquid in the blade groove 15b is pushed by the blade groove upstream side surface 15b1 by the impeller 15 rotating at high speed, and a circulating flow is generated. In the vicinity of the blade 15c, a circulating flow F1 that flows outward in the radial direction of the impeller 15 along the upstream side surface 15b1 of the blade groove and a radial outward flow of the impeller 15 along the downstream side surface 15b2 of the blade groove. There is a circulating flow F2. The first thick portion 15a1 of the blade groove upstream side surface 15b1 faces the first facing portion 14a of the casing cover 14 described later in close proximity to protect the circulating flow generated in the blade groove 15b and the blade 15c. It is a part. Further, the first thick portion 15a1 prevents the liquid in the blade groove 15b from flowing out, and foreign matter that has entered the blade groove 15b and is larger than the gap between the impeller 15 and the casing cover 14 enters the gap. It is also a part to prevent.

A partition portion 15d having a curved surface formed in a bow shape toward the first surface 15x and the second surface 15y so as to divide the region in the blade groove 15b into the first surface 15x side and the second surface 15y side. It is provided. As shown in FIG. 4, the partition portion 15d is a member for dividing the region in the blade groove 15b into the first surface 15x side and the second surface 15y side.

Next, the casing cover 14 will be described with reference to FIG. FIG. 6 is a perspective view of the surface of the casing cover 14 facing the first surface 15x of the impeller 15. As shown in FIG. 6, on the surface of the casing cover 14 facing the first surface 15x of the impeller 15, the first facing portion 14a, the first wall portion 14b, the first flow path forming portion 14c, the pump casing contact portion 14d, and the like. And a central portion 14e.

A concave central portion 14e is provided at the center of the surface of the casing cover 14 facing the first surface 15x of the impeller 15. The central portion 14e is a portion for accommodating the fixed portion 15e1 provided on the first surface 15x of the impeller 15.

The casing cover 14 is provided with a first facing portion 14a, which is a substantially annular flat region, so as to surround the central portion 14e. The first facing portion 14a is provided with a contact portion 14f extending from the first facing portion 14a. The contact portion 14f is in contact with the outer edge of the casing cover 14. The first facing portion 14a is fixed to a part of the pump casing contact portion 14d via the contact portion 14f. The first facing portion 14a is close to and facing the first thick portion 15a1 on the first surface 15x of the impeller 15 to protect the circulating flow generated in the blade groove 15b, and the liquid in the blade groove 15b is released. This is a portion for preventing outflow and preventing foreign matter that has entered the blade groove 15b and is larger than the gap between the impeller 15 and the casing cover 14 from entering the gap. The contact portion 14f is a portion that extends from the first facing portion 14a and comes into contact with the casing cover 14.

A first flow path forming portion 14c recessed from the first facing portion 14a is provided on the outer periphery of the first facing portion 14a. The first flow path forming portion 14c is a flow path of the liquid in the flow path 19 when the liquid sucked from the suction port 11 is discharged to the discharge port 12 by the rotation of the impeller 15.

On the outer periphery of the first flow path forming portion 14c, a ring-shaped convex first wall portion 14b having a part removed is provided. The first wall portion 14b is a member for forming the first flow path forming portion 14c. Further, a contact portion 14f is fixed to a part of the portion where the first wall portion 14b is missing, and the missing portion is divided into two regions by the contact portion 14f. Of these two regions, the missing portion on the right side in FIG. 6 is an inlet for the liquid sucked from the suction port 11 to enter the first flow path forming portion 14c. On the other hand, the missing portion on the left side in FIG. 6 is an outlet for delivering the liquid to the discharge port 12. A pump casing contact portion 14d is provided on the outer periphery of the first wall portion 14b to contact the pump casing 13 and prevent liquid from leaking from the flow path 19.

Next, the casing liner 17 will be described with reference to FIG. 7. FIG. 7 is a perspective view of the casing liner 17 on the side facing the second surface 15y of the impeller 15. As shown in FIG. 7, the casing liner 17 on the side facing the second surface 15y of the impeller 15 has a second facing portion 17a, a second wall portion 17b, a second flow path forming portion 17c, a tongue portion 17d, and a protrusion. It is provided with a hole 17h.

A protruding hole 17h is provided in the center on the side of the casing liner 17 facing the second surface 15y of the impeller 15.

The casing liner 17 is provided with a second facing portion 17a, which is a substantially annular flat region, so as to surround the protruding hole 17h. The second facing portion 17a is connected to the tongue portion 17d. The second facing portion 17a is close to and facing the second thick portion 15a2 on the second surface 15y of the impeller 15 to protect the circulating flow generated in the blade groove 15b, and the liquid in the blade groove 15b is released. This is a portion for preventing outflow and preventing foreign matter that has entered the blade groove 15b and is larger than the gap between the impeller 15 and the casing liner 17 from entering the gap.

A second flow path forming portion 17c recessed from the second facing portion 17a is provided on the outer periphery of the second facing portion 17a. The second flow path forming portion 17c is a flow path of the liquid in the flow path 19 when the liquid sucked from the suction port 11 is discharged to the discharge port 12 by the rotation of the impeller 15.

On the outer periphery of the second flow path forming portion 17c, a ring-shaped convex second wall portion 17b is provided, which is partially missing. The second wall portion 17b is a member for forming the second flow path forming portion 17c. Further, a tongue portion 17d is provided in a part of the portion where the second wall portion 17b is missing, and the missing portion is divided into two regions by the tongue portion 17d. Of these two regions, the missing portion on the left side in FIG. 7 is an inlet for the liquid sucked from the suction port 11 to enter the second flow path forming portion 17c. On the other hand, the missing portion on the right side in FIG. 7 is an outlet for delivering the liquid to the discharge port 12. The tongue portion 17d is a member for preventing the liquid sent out to the discharge port 12 from returning to the inlet where the liquid sucked from the suction port 11 again enters the second flow path forming portion 17c.

Next, with reference to FIG. 8, the operation of the vortex pump 1 configured as described above will be described. FIG. 8 is a schematic cross-sectional view of the pump unit 2 showing the flow path of water and orthogonal to the rotation axis 18. As shown in FIG. 8, when the motor 10 rotates, the impeller 15 rotates at high speed in the flow path 19 filled with the liquid (water W). Then, the centrifugal force generated by the high-speed rotation of the impeller 15 acts on the water W in the blade groove 15b. As a result, the water W sucked from the suction port 11 obtains momentum from the impeller 15 rotated by the rotational drive of the motor 10 and obtains the total pressure during the period from the suction port side water channel Win to the discharge port side water channel Wout. While raising, it is discharged from the discharge port 12.

As described above, the radial inner portion of the blade groove upstream side surface 15b1 is tilted backward by an angle α with respect to the reference line connecting the rotation center P0 of the impeller 15 and the radial inner end portion P1 of the blade groove upstream side surface 15b1. By doing so, the angle formed by the rotation direction R and the radial inner portion of the blade groove upstream side surface 15b1 becomes small, and when the circulating flow collides with the blade groove upstream side surface 15b1 and flows into the blade groove 15b, Since the inflow is smoother than in the case of a conventional vortex pump (an impeller formed so that the upstream side surface of the blade groove and the downstream side surface of the blade groove are parallel to each other), the vortex pump 1 that ensures high pump efficiency can be used. It can be realized.

Further, the radial outer portion of the blade groove downstream side surface 15b2 is tilted forward with respect to the reference line connecting the rotation center P0 of the impeller 15 and the radial inner end portion P2 of the blade groove downstream side surface 15b2. The angle formed by the rotation direction R and the blade groove downstream side surface 15b2 becomes smaller, and the circulating flow F2 flowing out from the blade groove 15b in the radial direction of the impeller 15 along the blade groove downstream side surface 15b2 is in the rotation direction R in the flow path. Since it smoothly merges with the heading flow, it is possible to realize a vortex pump 1 that ensures high pump efficiency.

Further, the radial inner portion of the blade groove downstream side surface 15b2 is formed so as to be in contact with the reference line connecting the rotation center P0 of the impeller 15 and the radial inner end portion P2 of the blade groove downstream side surface 15b2. Ensuring a larger circumferential width of the radial inner part of the blade groove 15b than when it exists on the same plane as the radial outer part (a state in which the blade groove 15b is tilted forward by an angle α with respect to the reference line). This makes it easier for the circulating flow to flow into the blade groove, so that the eddy current pump 1 with even higher pump efficiency can be realized.

That is, the vortex pump 1 can be used to improve the pump efficiency.

Although the present invention has been described above based on the embodiments, the present invention is not limited to the above embodiments, and various improvements and modifications can be made without departing from the spirit of the present invention. It is easy to guess.

The first modification will be described with reference to FIG. FIG. 9 is an enlarged view of the periphery of the blade groove 25b of the impeller 25 in the first modification.

In the impeller 25 in the first modification, the blade groove upstream side surface 25b1 is relative to a reference line connecting the rotation center P0 of the impeller 25 (see FIG. 5A) and the radial inner end portion P1 of the blade groove upstream side surface 25b1. It has an inner part in the radial direction that is tilted backward by an angle α in the direction opposite to the rotation direction R, and a radial outer part that is tilted forward in the rotation direction R with respect to the reference line tangent to the inner part in the radial direction. It is different from the impeller 15 in the first embodiment in that it is formed. Other than this, the configuration of the impeller 25 is the same as that of the impeller 15 according to the first embodiment, and the vortex pump 1 using the impeller 25 also has the same configuration. Hereinafter, the contents already explained in the first embodiment will be omitted again as appropriate, and the differences from the first embodiment will be mainly described.

In the impeller 25 in the first modification, as shown in FIG. 9, the adjacent blade grooves 25b are separated by the blade 25c, and the blade 25c forms the blade groove upstream side surface 25b1 and the blade groove downstream side surface 25b2. The radial inner portion of the blade groove upstream side surface 25b1 is opposite to the rotation direction R with respect to the reference line connecting the rotation center P0 of the impeller 25 and the radial inner end portion P1 of the blade groove upstream side surface 25b1. It is formed so as to tilt backward by an angle α in the direction. The radial outer portion of the blade groove upstream side surface 25b1 is formed so as to be tilted forward by an angle γ in the rotation direction R with respect to the reference line in contact with the radial inner portion.

On the other hand, the radial inner portion of the blade groove downstream side surface 25b2 is formed so as to be in contact with the reference line connecting the rotation center P0 of the impeller 25 and the radial inner end portion P2 of the blade groove downstream side surface 25b2. The radial outer portion of the blade groove downstream side surface 25b2 is only an angle β in the rotation direction R with respect to the reference line connecting the rotation center P0 of the impeller 25 and the radial inner end portion P2 of the blade groove downstream side surface 25b2. It is formed to lean forward.

As described above, according to the impeller 25 in the first modification, when the number of blade grooves 25b is equal, the thickness (blade) in the tip region of the blade 25c is higher than that of the blade 15c of the impeller 15 in the first embodiment. Since the width between the groove upstream side surface 25b1 and the blade groove downstream side surface 25b2) is increased, the strength of the blade 25c can be improved. As a result, the resistance when a foreign substance is mixed in the impeller 25 is improved. Further, in the impeller 25, the angle formed by the radial outer portion of the blade groove upstream side surface 25b1 and the rotation direction R becomes smaller. That is, in the velocity vector of the circulating flow F1 flowing in the vicinity of the blade groove upstream side surface 25b1, the component in the rotation direction R becomes large, and the flow from the suction port 11 of the vortex pump 1 to the discharge port 12 through the flow path 19. Since the merging is smooth, the vortex pump 1 with even higher pump efficiency can be realized.

Next, a second modification will be described with reference to FIG. FIG. 10 is an enlarged view of the periphery of the blade groove 35b of the impeller 35 in the second modification.

In the impeller 35 in the second modification, the entire blade groove downstream side surface 35b2 (radial inner portion and radial outer portion) is the rotation center P0 of the impeller 35 (see FIG. 5A) and the blade groove downstream side surface. It differs from the impeller 15 in the first embodiment in that it is formed so as to tilt forward by an angle β in the rotation direction R with respect to the reference line connecting the radial inner end portion P2 of 35b2. Other than this, the configuration of the impeller 35 is the same as that of the impeller 15 according to the first embodiment, and the configuration of the vortex pump 1 using the impeller 35 is also the same. Hereinafter, the contents already explained in the first embodiment will be omitted again as appropriate, and the differences from the first embodiment will be mainly described.

In the impeller 35 in the second modification, as shown in FIG. 10, the adjacent blade grooves 35b are separated by the blades 35c, and the blades 35c form the blade groove upstream side surface 35b1 and the blade groove downstream side surface 35b2. Then, the entire blade groove upstream side surface 35b1 (radial inner portion and radial outer portion) becomes a reference line connecting the rotation center P0 of the impeller 35 and the radial inner end portion P1 of the blade groove upstream side surface 35b1. On the other hand, it is formed so as to tilt backward by an angle α in the direction opposite to the rotation direction R.

On the other hand, the entire blade groove downstream side surface 35b2 (radial inner portion and radial outer portion) serves as a reference line connecting the rotation center P0 of the impeller 35 and the radial inner end P2 of the blade groove downstream side surface 35b2. On the other hand, it is formed so as to tilt forward by an angle β in the rotation direction R. In the second modification, the thickness (width between the blade groove upstream side surface 35b1 and the blade groove downstream side surface 35b2) in the tip region of the blade 35c is set in the tip region of the blade 15c of the impeller 15 in the first embodiment. In order to make the thickness the same as that of the blade 35c, the thickness of the root portion (inward end portion side in the radial direction) of the blade 35c is increased. That is, the minimum circumferential width of the blade groove 35b is narrowed.

As described above, according to the impeller 35 in the second modification, the width of the radial inner portion of the blade groove 35b in the circumferential direction gradually widens, so that when the circulating flow flows into the blade groove 35b, the width thereof gradually increases. The loss is reduced, and when applied to the vortex pump 1, the pump efficiency of the vortex pump 1 can be improved.

Since the vortex pump according to the present invention makes it possible to improve the pump efficiency, it is useful as a vortex pump or the like used frequently for home use or the like.

1 Vortex pump 2 Pump part 10 Motor 11 Suction port 12 Discharge port 13 Pump casing 13h Through hole 14 Casing cover 14a First facing part 14b First wall part 14c First flow path forming part 14d Pump casing contact part 14e Center part 14f Contact Part 15 Impeller 15a1 1st thick part 15a2 2nd thick part 15b Blade groove 15b1 Blade groove upstream side surface 15b2 Blade groove downstream side surface 15c Blade 15d Partition part 15e1 Fixed part 15e2 Fixed part 15x 1st surface 15y 2nd surface 16 Mechanical seal 17 Casing liner 17a 2nd facing part 17b 2nd wall part 17c 2nd flow path forming part 17d Tongue part 17h Protruding hole 18 Rotating shaft 19 Flow path 25 Impeller 25b Blade groove 25b1 Blade groove upstream side 25b2 Blade groove downstream side 25c Blade 35 Impeller 35b Blade groove 35b1 Blade groove upstream side surface 35b2 Blade groove downstream side surface 35c Blade W water Win Suction port side water channel Wout Discharge port side water channel P0 Rotation center P1 Radial inward end P2 Radial inward end

Claims (3)

A vortex pump in which the liquid sucked from the suction port by the rotation of the impeller passes through the flow path and is discharged from the discharge port.
The impeller is provided with a plurality of blade grooves in the circumferential direction of the outer peripheral end of both side surfaces of the disk-shaped member.
The blade grooves adjacent to each other in the circumferential direction are partitioned by blades, and are located on the upstream side surface of the blade groove, which is a surface of the blade groove located in the direction opposite to the rotation direction of the impeller, and in the blade groove in the rotation direction. It has a surface on the downstream side of the blade groove and has a surface.
The radial inner portion of the blade groove upstream side surface is rearward in the direction opposite to the rotation direction with respect to the reference line connecting the rotation center of the disk-shaped member and the radial inner end portion of the blade groove upstream side surface. Formed to tilt,
The radial outer portion of the blade groove downstream side surface is formed so as to tilt forward in the rotation direction with respect to the reference line connecting the rotation center and the radial inner end portion of the blade groove downstream side surface. A vortex pump featuring. The radial outer portion of the blade groove upstream side surface is formed so as to tilt forward in the rotational direction with respect to the reference line connecting the rotation center and the radial inner end portion of the blade groove upstream side surface. The vortex pump according to claim 1. 1. 2. The vortex pump according to 2.

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