JP2012184699A - Reverse running pump turbine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a reverse running pump turbine that can improve a water turbine efficiency with a simple configuration without increasing a manufacturing cost.SOLUTION: An edge part of a blade 11 of a runner 2 on its radially outer side has a curved surface shape to have a gradually-smaller curvature radius toward the tip end. A tongue piece part 20 provided at a border on a side of a casing 3 between a straight passage 16 and a circular passage 15 is shaped to be gradually-thinner toward the tip end from its base part side.

Description

  The present invention relates to a pump reverse turbine designed mainly for use as a pump.

A spiral pump and a diffuser pump are known as pumps used for pumping water (see, for example, Patent Document 1).
In this type of pump, an impeller having a plurality of blades extending in a substantially radial direction is arranged in a casing, and the liquid sucked from the axial direction of the casing by rotating the impeller by a drive source such as an electric motor. Is discharged radially outward while having a circumferential component. Each blade of the impeller is installed on a disk-shaped base member at equal intervals, and a radially outer region serving as a trailing edge during driving rotation is curved in a direction opposite to the rotation direction. The extending end of the rear edge of each blade is cut in a plane substantially along the tangential direction of the outer circumference of the impeller. Further, the casing is provided with a suction port on the end face in the axial direction, and on the outer peripheral side of the impeller, an annular passage that surrounds the outer periphery of the impeller, a linear passage that extends substantially tangentially from the annular passage, A discharge passage is provided.

  By the way, this type of pump is mainly used as a pump, and may be used as a pump reversing water turbine that converts a liquid flow into power as needed. For example, the pump reversing water turbine is operated as a pump when water is pumped into a water storage tank on the upper floor of a high-rise building, and is operated as a water wheel when surplus energy for discharging the pumped water is taken out as electric power.

JP-A-5-187398

When the conventional pump is used as a pump reversing water turbine, each part of the pump component is designed in a shape suitable for pump operation. Therefore, when operating as a water turbine, a water flow collides with each part of the pump component. Turbulence that occurs sometimes reduces the turbine efficiency.
As countermeasures, it may be possible to make the pump parts specially designed for both pump operation and water turbine operation, but in this case, the shape of each part of the pump parts becomes complicated and the addition of dedicated parts is also required. Forced to incur significant product costs.

  Accordingly, the present invention is intended to provide a pump reverse turbine that can increase the turbine efficiency with a simple configuration without causing an increase in product cost.

The pump reverse turbine according to the present invention employs the following means in order to solve the above problems.
The invention according to claim 1 is provided with a runner (corresponding to a pump impeller) having a plurality of blades extending substantially radially, and a casing that rotatably accommodates the runner therein. An annular passage that surrounds the outer peripheral side of the runner and a linear passage that extends in a substantially tangential direction from the annular passage, and during the operation of the pump, the liquid sucked from the axial direction by the rotation of the runner And a pump reverse turbine that rotates the runner by liquid introduced from the straight passage into the annular passage during the operation of the water turbine, and the radially outer edge of each blade of the runner is The curved surface shape is formed such that the radius of curvature gradually decreases toward the tip side.
Thus, when liquid is introduced from the straight passage into the annular passage during the water turbine operation, the liquid flows in from the radially outer side to the inner side of each blade of the runner, and at this time, a rotational force is generated in the runner. As the liquid flows along the radially outer edge of each blade, the liquid flows smoothly along the curved shape of the edge.

According to a second aspect of the present invention, in the pump reverse turbine according to the first aspect, the branch portion between the linear passage and the annular passage is provided with a tongue piece projecting inward of the casing substantially along the tangential direction of the annular passage. The tongue piece is formed in a shape in which the thickness gradually decreases from the base side toward the tip side.
Thus, when liquid is introduced from the straight passage during the water turbine operation, the liquid smoothly flows toward the tip side along the tongue piece protruding from the branch portion between the straight passage and the annular passage.

  According to this invention, at the time of water turbine operation, the curved surface shape provided at the radially outer edge of each blade of the runner allows liquid to flow smoothly between adjacent blades without incurring a collision loss. Therefore, the turbine efficiency can be increased with a simple configuration without causing an increase in product cost.

It is sectional drawing corresponding to the AA cross section of FIG. 2 of the pump reverse rotation water turbine of one Embodiment of this invention. It is sectional drawing corresponding to the BB cross section of FIG. 1 of the pump reverse rotation water turbine of one Embodiment of this invention. It is an enlarged view of the C section of Drawing 1 of a pump reversing turbine of one embodiment of this invention. It is an enlarged view of the D section of Drawing 1 of the pump reverse rotation turbine of one embodiment of this invention.

  Hereinafter, an embodiment of the present invention will be described with reference to the drawings. In the following description, unless otherwise specified, “upper” and “lower” mean up and down in the vertical direction. Moreover, the black arrow which does not attach | subject the code | symbol in each figure shows the flow of the liquid at the time of pump operation, and the white arrow which does not attach | subject the code | symbol similarly shows the flow of the liquid at the time of water turbine operation. .

1 and 2 are diagrams showing a schematic configuration of a pump reverse turbine 1 according to an embodiment of the present invention, and FIG. 1 is a cross-sectional view of the pump reverse turbine 1 cut in a substantially horizontal direction. These are sectional drawings which cut the pump reverse rotation turbine 1 in the substantially perpendicular direction.
The pump reversing water turbine 1 is in the form of a spiral pump, and includes a runner 2 having a plurality of blades 11 extending in a substantially radial direction, and a casing 3 that accommodates the runner 2 therein. A rotating shaft 4 is coaxially connected to the runner 2, and the rotating shaft 4 and the runner 2 are rotatably supported by the axial center portion of the casing 3. The rotary shaft 4 is connected to a generator motor (not shown) having both functions of a generator and a motor. 1 and 2 is the center of rotation of the rotating shaft 4 and the runner 2.

  The runner 2 includes a disk-shaped base member 12 connected to the rotating shaft 4, and a curved guide surface 12 a that protrudes while being curved toward the axial direction is provided on the lower surface side of the base member 12. On the curved guide surface 12a, the upper surface side of the plurality of blades 11 is fixed. The plurality of blades 11 are connected to each other on the lower surface side by a connecting ring 13. The opening at the center of the connecting ring 13 is an axial inlet / outlet of the runner 2 where the introduced liquid flows along the axial direction, and the gap between the adjacent blades 11, 11 is approximately the radial direction of the introduced liquid. The runner 2 that flows along the inlet / outlet in the radial direction is used.

Each blade 11 arranged on the base member 12 extends in a substantially radial direction of the base member 12 as described above, but more precisely, each blade 11 is radially outward as shown in FIG. Is curved in the direction opposite to the rotational direction P during pump operation with respect to the inner edge. Therefore, when the runner 2 rotates in the P direction during the pump operation, each blade 11 turns around the rotation center O and smoothly discharges the liquid introduced to the center side outward in the radial direction by centrifugal force.
Further, as shown in an enlarged view in FIG. 3, the radially outer edge of each blade 11 is not in a shape cut by a plane Q substantially along the tangential direction of the outer circumference of the runner 2, but toward the tip side. The curved surface has a gradually decreasing radius of curvature. In addition, 14 in FIG. 3 is a curved surface in which the radius of curvature of the radially outer edge of the blade 11 gradually decreases.

  On the other hand, the casing 3 includes an annular passage 15 that surrounds the outer peripheral side of the runner 2 and a linear passage 16 that extends substantially tangentially from the annular passage 15, and the inner peripheral side of the annular passage 15 is the outer peripheral side of the runner 2. It faces the radial inlet / outlet (the gap between the adjacent blades 11, 11), and the end of the straight passage 16 is connected to an external pipe (not shown) that becomes the discharge side during pump operation. Also, an axial center passage 17 communicating with the axial entrance / exit in the center of the runner 2 is provided in the approximate center of the lower surface of the casing 3, and the axial passage 17 serves as an intake side during pump operation. Connected to piping.

By the way, the wall 18b which comprises the annular channel | path 15 is integrally formed in the casing main body 18 containing the runner accommodating part 18a. The wall portion 18 b forms a substantially circular hollow cross section of the annular passage 15. Hereinafter, the wall portion 18b is referred to as a “hollow cross-section wall 18b”. A substantially straight straight pipe member 19 forming the straight passage 16 is joined to a part of the hollow cross-section wall 18b.
The inner diameter of the hollow cross-section wall 18b of the casing body 18 is not constant, the inner diameter of the region to which the straight pipe member 19 is connected is the largest, and the inner diameter gradually decreases from the region along the periphery of the runner accommodating portion 18a. It has become. Therefore, the annular passage 15 formed by the hollow cross-sectional wall 18b has a substantially spiral shape, and the inner diameter in the vicinity of the region of the hollow cross-sectional wall 18b that abuts against the side surface of the straight pipe member 19 is the smallest.
A portion between the region having the smallest inner diameter and the region having the largest inner diameter of the annular passage 15 becomes a branch portion between the straight passage 16 and the annular passage 15, and a tongue piece portion 20 is provided at the branch portion. The tongue piece 20 protrudes inside the casing 3 substantially along the tangential direction of the annular passage 15.

As shown in an enlarged view in FIG. 4, the tongue piece 20 is formed such that the thickness from the base side to the tip side is not constant, and the thickness gradually decreases from the base side to the tip side. Yes. And the front-end | tip part of the tongue piece part 20 is formed by the curved surface from which a curvature radius reduces gradually toward a front-end | tip.
2 is a rectifying plate that is attached in the casing body 18 and rectifies the flow of the liquid between the runner 2 and the annular passage 15. The rectifying plate 21 is not shown in FIG.

  In the above configuration, when the pump reverse turbine 1 is operated as a pump, the runner 2 is driven to rotate in the direction P in FIG. 1 by the power of the generator motor. Thus, when the runner 2 rotates, the liquid sucked from the lower axial passage 17 by the rotation of the blades 11 on the runner 2 is discharged to the straight passage 16 through the annular passage 15.

  On the other hand, when the pump reverse rotation turbine 1 is operated as a turbine, the liquid introduced into the straight passage 16 is caused to flow into the outer peripheral side of the runner 2 through the annular passage 15. In this way, when the liquid swirls and flows into the runner 2 from the outer peripheral side, the liquid presses each blade 11 on the runner 2 in the G direction, and from the radially outer side to the inner side substantially along the outer surface shape of each blade 11. And flows in. At this time, the liquid flowing into the center side of the runner 2 is discharged to the axial passage 17, and the runner 2 rotates in the G direction by the pressing force acting on each blade 11. As a result, the generator motor is driven through the rotating shaft 4 and generates electric power by the driving force.

  In this pump reversing turbine 1, the radially outer edge of each blade 11 of the runner 2 is formed in a curved shape with a radius of curvature gradually decreasing toward the tip side, so that the liquid is not in the runner 2 during the operation of the turbine. When flowing into the center side of the runner 2 along the radially outer edge of each blade 11, the liquid smoothly flows along the curved surface shape of the edge of each blade 11, as shown in FIG. 3. Therefore, it is possible to prevent the occurrence of loss due to the liquid colliding with the radially outer end of each blade 11 and to improve the turbine efficiency.

  In the case of the pump reversing turbine 1, the turbine efficiency can be improved by simply making improvements to the blades 11 of the runner 2 that can be easily molded and installed. be able to. That is, the runner 2 is a part that is manufactured in a different location before being installed inside the casing 3, and each blade 11 is assembled to the base member after processing. It can be carried out easily and does not interfere with the installation in the casing 3.

  Further, in this pump reversing turbine 1, a tongue piece portion 20 is provided at the branch portion between the straight passage 16 and the annular passage 15 on the casing 3 side so as to protrude inward of the caking 3 along the tangential direction of the annular passage 15. Since the tongue piece 20 has a shape in which the wall thickness gradually decreases from the base side toward the tip side, it is possible to suppress the occurrence of turbulent flow due to the wake at the tongue piece 20 during the water turbine operation. it can. In particular, in the case of this embodiment, the distal end portion of the tongue piece portion 20 is formed by a curved surface whose radius of curvature gradually decreases toward the distal end, so that the occurrence of wakes can be more reliably suppressed. Therefore, in this pump reverse rotation turbine 1, the turbine efficiency can be further improved.

  And also about the tongue piece part 20 by the side of this casing 3, since a turbine efficiency can be improved only by making a simple improvement in the position where shaping | molding and component installation are easy, it becomes advantageous when suppressing product cost. ing.

  In addition, this invention is not limited to said embodiment, A various design change is possible in the range which does not deviate from the summary.

DESCRIPTION OF SYMBOLS 1 ... Pump reverse rotation turbine 2 ... Runner 3 ... Casing 11 ... Blade | wing 15 ... Annular passage 16 ... Straight passage 20 ... Tongue piece part

Claims (2)

A runner having a plurality of blades extending substantially radially;
A casing for rotatably accommodating the runner therein;
With
Inside the casing, an annular passage that surrounds the outer peripheral side of the runner, and a linear passage that extends substantially tangentially from the annular passage,
During pump operation, the liquid sucked from the axial direction by rotation of the runner is discharged to the linear passage through the annular passage, and during runner operation, the runner is rotated by the liquid introduced from the straight passage into the annular passage. A pump reversing turbine,
A pump reversing water turbine characterized in that the radially outer edge of each blade of the runner is formed in a curved surface shape with a radius of curvature gradually decreasing toward the tip side. A branch portion between the linear passage and the annular passage is provided with a tongue portion projecting inward of the casing substantially along the tangential direction of the annular passage,
The pump reverse rotation turbine according to claim 1, wherein the tongue piece is formed in a shape in which the thickness gradually decreases from the base side toward the tip side.

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