JP5025273B2 - Pump device and pump gate device - Google Patents

Description

  The present invention relates to a pump device in which a flow straightening plate is provided inside a suction casing disposed on the upstream side of an impeller.

  Conventionally, in an axial flow pump or a column-type submersible pump attached to an openable / closable water stop gate body installed at the boundary of a water channel, the elevation angle of water to the impeller is caused by a reverse swirling flow generated at the pump inlet. Since the shaft power gradually increases even when the suction flow rate is constant, an increase in shaft power is suppressed by driving the pump with an inverter-controlled synchronous motor for overcurrent protection or the like.

  However, when an induction motor is used as a drive source for cost reduction, it is difficult to control the rotational speed. For example, in a horizontal axis pump installed at a pump gate, as shown in FIG. A cantilever plate baffle 23 is provided on the upper side of a bell mouth-shaped suction casing 22 that is disposed on the upstream side of the impeller 18 and has a tip inclined downwardly. As shown in b), it has been considered that a plurality of rectifying plates 23 are provided radially in the bearing portion 17a of the drive shaft 17 provided on the upstream side of the impeller 18 in the radial direction.

  However, the rectifying plate shown in FIG. 11 (b) has a rectifying effect, but not only the passing particle size of the foreign matter is reduced, but the rectifying plate is fixed by both ends by the bearing portion and the inner peripheral wall of the suction casing. Therefore, long foreign matters such as strings are easily caught, and once caught, they cannot be removed due to the flow, and there is a problem that the flow passage area is reduced and the pump efficiency is lowered, and the rectification shown in FIG. Since the plate is fixed to the inner wall of the suction casing in a cantilevered manner, it is possible to avoid the trapping of foreign matter, but there is a problem that the rectifying effect is not sufficient due to the insufficient number of sheets. Therefore, it is conceivable to provide a plurality of cantilevered flow straightening plates along the circumferential direction on the inner peripheral wall of the suction casing, but simply increasing the number of flow straightening plates increases the flow resistance and lowers the pump efficiency, In addition, there is a problem that only small-diameter foreign matter can pass.

  On the other hand, as a technique for preventing the inclusion of foreign matter in the impeller, Patent Document 1 provides a sewage pump that can prevent foreign matter sucked together with sewage from reaching the impeller and reduce pump damage and trips. For the purpose, as shown in FIG. 12 (a), guide vanes for generating a swirling flow are provided on the inner peripheral surface of the suction casing provided on the upstream side of the impeller, and a foreign matter storage space is formed on the outer periphery of the suction casing. A sewage pump has been proposed in which a foreign matter storage part is provided and an opening that communicates the internal flow path of the suction casing and the foreign matter storage space is provided on the peripheral side part of the suction casing that corresponds between the guide vane and the impeller. In addition, the code | symbol shown in Fig.12 (a) does not respond | correspond with embodiment shown below.

Moreover, in patent document 2, as shown in FIG.12 (b), in order to provide the non-occlusion pump which can let this pass easily even if it is a fibrous foreign material, as shown in FIG. One or a plurality of rectifiers having a shape that pushes the foreign matter sucked into the pump toward the outer peripheral direction of the impeller and projecting outward from the center in the radial direction and using the outer periphery as a foreign matter guide side There is proposed a non-blocking pump that includes a straightening member, and that the foreign material guide side is formed in a tapered shape from the upstream side to the downstream side of the pump suction port. Similarly, the reference numerals shown in FIG. 12B do not correspond to the following embodiments.
Japanese Utility Model Publication No. 7-8600 JP-A-2005-90313

  However, in any of the above-described pump devices, the effect is scarce and further improvement has been desired from the viewpoint of suppressing an increase in shaft power while avoiding the trapping of foreign matters.

  In view of the above-described problems, an object of the present invention is to allow a pump device that allows passage while avoiding the trapping of foreign matter and effectively suppresses an increase in shaft power even when an induction motor is used as a drive source. And providing a pump gate device.

In order to achieve the above-mentioned object, the first characteristic configuration of the pump device according to the present invention is as described in claim 1 of the claims, inside the suction casing arranged upstream of the impeller. A pump device provided with a plurality of rectifying plates, wherein the rectifying plates are arranged such that a flow direction distribution in a cross section perpendicular to a flow path center line of the suction casing is aligned with a predetermined angle of attack with respect to the impeller. wherein the cantilever arranged at a suction gap inner peripheral surface in the circumferential direction of the casing, the protruding height of the axial direction of the suction casing, is set to 15% to 35% of the inner diameter of the suction casing Rutotomoni The protrusion heights are different from each other.

With such a configuration, it is possible to efficiently rectify in accordance with the flow velocity distribution in the radial direction of the reverse swirl flow, and a cross section perpendicular to the flow path center line of the suction casing (hereinafter referred to as a “cross section”). Since the flow direction distribution in the cylinder flows into the impeller with a predetermined angle of attack with respect to the impeller, an increase in shaft power is effectively reduced. Moreover, since the current plate is cantilevered on the inner peripheral surface of the suction casing, even a long foreign object can be easily detached from the free end side .

The flow velocity distribution of the reverse swirling flow generated in the water flowing into the suction casing varies depending on the radial direction. According to the above-described configuration, the rectifying plate is cantilevered on the inner peripheral surface of the suction casing with a space in the circumferential direction. Even if it is arranged , the protruding height in the axial direction is different, so that the problem of efficiency reduction and clogging of foreign matters due to the proximity of the current plate near the axial center of the suction casing can be solved. .

In the second feature configuration, in addition to the first feature configuration described above, in addition to the first feature configuration described above, the circumferential distance between the axial direction tip portion of each rectifying plate and the rectifying plate adjacent in the circumferential direction is The arrangement is such that the protruding heights in the axial direction are different so that they are substantially equal. With this configuration, there is a rectifying plate in the nectar even if it is separated from the axial center of the suction casing in the radial direction. As a result, the effect of preventing the swirling flow is enhanced, and the flow between the adjacent rectifying plates is efficiently rectified in those regions, so that the same rectifying action can be obtained as a whole.

In the third feature configuration, in addition to the second feature configuration described above, in addition to the second feature configuration described above, a rectifying plate having a high protruding height in the axial direction and a low rectifying plate are alternately arranged in the circumferential direction. It is in the point.

Similar to the above, the effect of preventing the swirling flow is enhanced, and the flow between the rectifying plates adjacent in those regions is efficiently rectified, so that a more uniform rectifying action can be obtained as a whole.

In the fourth feature configuration, as described in claim 4, in addition to any of the first to third feature configurations described above, the maximum protruding height in the axial direction of the rectifying plate is the blade. It is in the point that it is set to be substantially the same as the radial direction length of the wing of the car, and, as described above, this configuration provides a sufficient rectifying effect near the inner wall of the suction casing that has a large effect when flowing into the impeller. However, it is possible to sufficiently secure the passage diameter of the foreign matter in the vicinity of the axial center where the blade boss exists.

  In the fifth feature configuration, in addition to any one of the first to fourth feature configurations described above, the rectification adjacent to the front end in the axial direction of each rectifying plate in the circumferential direction is provided. A suction casing that has a circumferential distance with respect to the plate is set to 10% to 40% of the inner diameter of the suction casing, and has a great influence on the flow into the impeller by such a configuration as described above. It is possible to sufficiently ensure the passage diameter of the foreign matter in the vicinity of the shaft center where the blade boss exists while sufficiently ensuring the rectifying effect in the vicinity of the inner wall of the blade.

  In the sixth feature configuration, as described in claim 6, in addition to any one of the first to fifth feature configurations described above, the front edge portion of each rectifying plate is in the flow direction along the axial direction. It is in the point which is inclined to.

  According to the above-described configuration, even a long foreign material that flows into the suction casing and is caught by the current plate can be easily separated along the inclined front edge portion and prevented from being entangled.

In the seventh feature configuration, as described in claim 7, in addition to any of the first to sixth feature configurations described above, the rectifying plate is composed of eight plates and protrudes in the axial direction. Four rectifying plates having a low protrusion height in the axial direction are arranged between four rectifying plates having a high height.

According to the above-described configuration, the effect of preventing the swirling flow is enhanced, and the flow between the adjacent rectifying plates is efficiently rectified in those regions, so that a more uniform rectifying action is obtained as a whole, and the shaft power is increased. Can be effectively suppressed.

Characteristic feature of the pump gate device according to the invention, as described in the claim 8 is that a from the first described above is mounted a seventh one of the pump device of the freely water stop gate door opening and closing.

  According to the above-described configuration, it is possible to realize a pump gate device that has a foreign substance passage property, can effectively suppress an increase in shaft power, and can operate stably.

  As described above, according to the present invention, even when an induction motor is used as a drive source, the pump device and the pump can pass while avoiding the catching of foreign matters and effectively prevent an increase in shaft power. A gate device can be provided.

  The pump device according to the present invention will be described below. As shown in FIG. 3, a pump gate 3 in which the pump device according to the present invention is incorporated is installed at a boundary portion where the first water channel 1 (for example, a tributary river) and the second water channel 2 (for example, a main river) meet. Yes.

  As shown in FIGS. 1 to 3, the pump gate 3 is made of a concrete that supports a sluice column 4 (4 b) standing at the boundary, a floor member 4 c laid horizontally at the bottom of the water channel, and a lifting mechanism 7. A water stop gate 6 made of a steel plate is supported on the floor 4 (4a) by an elevating mechanism 7 so as to be opened and closed.

  The elevating mechanism 7 directly connects a pair of rack rods 7a fixed to the water blocking gate door body 6 through a joint 7b and a pinion gear in a gear box 7c disposed on the upper part of the water gate pillar 4 (4a). An electric motor 7f that rotates or reversely drives, a manual operation handle 7d, and a drive coupling mechanism 7e that drives the other gear box 7c side in conjunction with the electric motor 7f that is drivingly coupled to the one gear box 7c side. The water stop gate door body 6 supported by the rack bar 7a by rotating the pinion gear by the electric motor 7f or the manual operation handle 7d can be moved up and down.

  A pair of left and right through holes are formed in the central portion of the water stop gate body 6 so that the water channels 1 and 2 communicate with each other. The water stop gate in which the water stop gate door body 6 descends in each through hole. A horizontal axis axial flow pump 11 which is an example of a pump device according to the present invention for draining from the first water channel 1 to the second water channel 2 in the posture is installed.

  As shown in FIG. 4, the axial flow pump 11 includes a motor main body 16 and a main shaft 17 protruding from the motor main body 16 in a cylindrical pump casing 20 (20a, 20b, 20c) having a circular cross section. The impeller 18 attached to the tip is accommodated so as to coincide with the axis of the casing 20 so that the pump axis P1 is in a horizontal posture.

  The pump casing 20 (20a, 20b, 20c) includes a first casing 20a having a small diameter disposed on the suction side, a second casing 20b having a substantially truncated cone shape whose diameter is increased toward the downstream side, and a first casing 20a. The large-diameter third casing 20c is configured to be flange-connected, and the motor main body 16 is supported and fixed via five guide vanes 19 arranged in the circumferential direction on the inner wall of the second casing 20b. An internal space formed between the motor main body 16 and the casing 20 is configured as a discharge flow path.

  The motor main body 16 includes an oil chamber 16a including a mechanical seal 26 on the impeller 18 side, and sequentially includes a submersion chamber 16b, a first motor chamber 16c, and a second motor chamber 16d in the discharge port direction. An electric motor M to which a power supply line PL is connected is disposed between the first motor chamber 16c and the second motor chamber 16d.

  The impeller 18 is composed of a blade boss 18a bolted to the front end side of the main shaft 17 and a plurality of blades 18b bolted to the blade boss 18a. The front side edge is formed as a swept wing. The water flow sucked by the impeller 18 and turned into a swirl flow is rectified into a linear flow along the main shaft 17 by the guide vanes 19, and the swirl energy given by the impeller 18 is converted into pressure energy. The

  A ring-shaped casing liner 21 made of a metal harder than the first casing 20a is provided on a surface facing the impeller 18 in an inner peripheral portion of the first casing 20a. Grooves 21a are provided on the peripheral surface to avoid clogging of foreign matters.

  A suction casing 22 is flange-connected to the upstream end of the first casing 20a, and a flap valve mechanism 12 that can open and close the flow path is flange-connected to the downstream end of the third casing 20c. The third casing 20c is attached to the water stop gate body 6.

  The flap valve mechanism 12 includes a valve body 12b that is pivotally supported around a horizontal axis at the other end of a cylindrical portion 12a that is flange-connected to the third casing 20c at one end. When the axial flow pump 11 is operated, it swings to an open posture by the discharge pressure of water sucked from the suction cover 22, and when the axial flow pump 11 is stopped, it swings to a closed posture by its own weight to prevent backflow. .

  The suction casing 22 is formed in a cylindrical shape with a circular cross section on the upstream side of the impeller 18 with a predetermined curvature so that the tip thereof is inclined downward with respect to the pump shaft center P1, and air suction A tip opening 22a is formed at the tip so as to expand into a trumpet shape so as to be able to stably suck up to a low water level while avoiding the generation of vortices. An upper portion of the tip opening 22a is formed to be substantially horizontal at the same height as the pump axis P1, and so that a lower portion thereof is substantially perpendicular to the water channel bottom. Here, the upper part of the tip opening 22a is in a substantially horizontal posture, thereby suppressing the generation of suction vortices generated from the water surface. Further, by making the lower part of the tip opening 22a substantially perpendicular to the water channel bottom, the generation of vortices generated from the water channel bottom is suppressed.

  In order to prevent an increase in shaft power due to the water sucked by the operation of the impeller 18 turning in the suction casing 22 in the direction opposite to the rotation direction of the impeller 18, the inner peripheral surface of the suction casing 22 is prevented. A plurality of rectifying plates 23 having a protruding height in the direction of the axial center P2 of the casing 22 are cantilevered, with the rectifying surface or upper end surface thereof being curved along the axial center P2 with an interval in the circumferential direction. Therefore, the flow direction distribution in the cross section of the suction casing 22 along the axis P2 is orthogonal to the impeller 18 at a predetermined angle of attack, in this embodiment, the rotational surface of the blade 18b. It is configured to align in the direction.

  The flow velocity distribution on the transverse section of the reverse swirling flow generated in the water flowing into the suction casing 22 varies depending on the radial direction. According to the above configuration, the protruding height in the direction of the axis P2 is high. A plurality of different rectifying plates 23 can efficiently perform rectification corresponding to the flow velocity distribution in the radial direction of the reverse swirl flow, and the flow direction distribution in the cross section of the suction casing 22 is a predetermined angle of attack with respect to the impeller 18. Therefore, the increase in shaft power is effectively reduced. Moreover, since the rectifying plate 23 is cantilevered on the inner peripheral surface of the suction casing 22, even a long foreign object can be easily detached from the free end side.

  Hereinafter, for simplification of description, the case where the suction casing 22 is a cylindrical straight pipe will be described in detail. As shown in FIG. 5, the rectifying plates 23 are arranged at equal intervals in the circumferential direction at intervals of 90 degrees. The plate-shaped four first rectifying plates 24 and the same plate-shaped four second rectifying plates 25 disposed in the middle of the first rectifying plate 24 are configured as eight rectifying plates, The protruding height R1 of the first rectifying plate 24 is set to about 1/3 of the inner diameter 2R of the suction casing 22, and the protruding height R2 of the second rectifying plate 25 is set to about 1/2 of the inner diameter 2R of the suction casing 22. 6 is set. That is, the protruding heights of these rectifying plates are set in the range of 15% to 35% of the inner diameter of the suction casing.

  Accordingly, it is possible to sufficiently ensure the passage diameter of the foreign matter in the space near the shaft center P2 while sufficiently ensuring the rectifying effect in the vicinity of the inner wall of the suction casing 22 that has a great influence when flowing into the impeller 18. It becomes like this. For example, in the case of a suction casing having a diameter of about 300 mm, the protruding height of the first rectifying plate 24 is set to about 100 mm, and the protruding height of the second rectifying plate 25 is set to about 50 mm.

According to the above-described configuration, the circumferential distance L1 between the axially leading end portion 24a of the first rectifying plate 24 and the rectifying plate adjacent in the circumferential direction, that is, the first rectifying plate 24, and the second rectifying plate 25. The projecting height in the direction of the axis P2 is set so that the circumferential distance L2 between the axial direction front end portion 25a and the rectifying plate adjacent in the circumferential direction, that is, the first rectifying plate 24 is substantially equal, and the suction casing Even if it is separated from the shaft center P2 in the radial direction, the rectifying plate 23 exists in the nectar, so that the effect of preventing the swirling flow is enhanced, and the flow between the adjacent rectifying plates 23 is efficiently rectified in those regions. As a result, a uniform rectifying action can be obtained as a whole. At this time, the circumferential distance (L1, L2) between the axial direction tip of each rectifying plate and the rectifying plate adjacent in the circumferential direction is about 25% of the inner diameter of the suction casing.

  Another embodiment will be described below. In the above-described embodiment, the case where the front edge portion of each rectifying plate 23 has a shape that rises linearly along the direction of the axis P2 has been described. However, as shown by the alternate long and short dash line in FIG. When the front edge portion 23b of the rectifying plate 23 is configured to be inclined in the flow direction along the direction of the axis P2, it is a long foreign object that flows into the suction casing 22 and is caught by the rectifying plate 23. Also, it can be easily detached along the inclined front edge portion 23b and prevented from being entangled.

  In the above-described embodiment, the case where the maximum protruding height R1 of the rectifying plate 23 in the direction of the axis P2 is set to about １ ／ of the inner diameter of the suction casing 22 has been described. The maximum protrusion height R1 in the P2 direction may be set to be substantially the same as the radial length R3 of the blade 18b of the impeller 18. Even if configured in this way, it is possible to sufficiently ensure the rectifying effect in the vicinity of the inner wall of the suction casing 22 which has a great influence when flowing into the impeller 18.

  In the above-described embodiment, four flat plate-like first rectifying plates 24 arranged at equal intervals in the circumferential direction at intervals of 90 degrees, and the same flat plate-like four arranged in the middle of the first rectifying plate 24. The second rectifying plate 25 is composed of eight rectifying plates, the protruding height R1 of the first rectifying plate 24 is set to about １ ／ of the inner diameter 2R of the suction casing 22, and the second rectifying plate In the above description, the protrusion height R2 of 25 is set to about 1/6 of the inner diameter 2R of the suction casing 22, but the shape of the rectifying surface of the rectifying plate is a flat plate shape or a shape along the axis of the suction casing. The present invention is not limited, and any change can be made as long as it rectifies the impeller so as to align with a predetermined angle of attack.

Further, the number of rectifying plates is not limited to the above, and may be set as appropriate according to the diameter of the suction casing. For example, if the suction casing has a smaller diameter than that of the above-described embodiment, three first rectifying plates having a protruding height of about 1/3 of the casing inner diameter and a protruding height of about 1/6 of the casing inner diameter are provided. Three second current plates may be provided, and a total of six current plates may be arranged at equal intervals in the circumferential direction. In this case, the circumferential distance between the axial direction tip of each rectifying plate and the rectifying plate adjacent in the circumferential direction is about 35% of the inner diameter of the suction casing.

  On the contrary, if the suction casing has a larger diameter than that of the above-described embodiment, about 1/5 of the casing inner diameter is eight sheets, and about 1/6 is eight sheets. It may be arranged. In this case, the circumferential distance between the axial direction tip of each current plate and the current plate adjacent in the circumferential direction is about 13% of the inner diameter of the suction casing.

  Further, the present invention is not limited to the configuration in which the protruding height of the rectifying plate 24 is different from the first and second rectifying plates which are different in two stages, but is configured to provide three types of rectifying plates 24 having multiple stages, for example, three stages of protruding height. It is also possible to do. In this way, by arranging the protruding heights in the axial direction to be different so that the circumferential distance between the axial direction front end portion of each rectifying plate and the rectifying plate adjacent in the circumferential direction is substantially equal, A sufficient rectifying effect can be obtained. However, if the number of rectifying plates is increased, the flow resistance increases accordingly, and the efficiency is lowered.In addition, the gap between the rectifying plates is narrowed, so that the possibility of foreign matter deterioration and a long object being caught are increased. Therefore, it is necessary to determine the required number of sheets based on the pump rating and the like.

  In the above-described embodiment, the present invention is applied to a horizontal axial flow pump device used for a pump gate. However, the present invention is not limited to this, and pumps water from a reservoir like a column type axial flow pump. The present invention can be applied to an axial flow pump device having a vertical axis, and can also be applied to a mixed flow pump device.

  The specific structure, material, dimensions, and the like of each part described in the above-described embodiment are not particularly limited, and are appropriately designed within the scope of the effects of the present invention.

  The inventors of the present application have repeatedly made various thoughts and errors through experiments and numerical analysis, and have come to adopt the above-described configuration.

  Flow analysis in the case where the fluid (water) of the rated flow rate of the target pump device is sucked by the impeller 18 was performed on the various rectifying plate shapes shown in FIGS. 6B to 6F. (A) is a case where a current plate is not provided in the suction casing, and in an ideal case where no reverse swirl flow is generated in the suction casing, (b) is a case where a reverse swirl flow is generated and the suction casing has a diameter. (C) generates a reverse swirl flow along the direction, and (c) generates a reverse swirl flow and provides three current plates parallel to the radial direction in the suction casing. When the four first rectifying plates are provided radially at intervals in the circumferential direction by generating the reverse swirling flow, (e) generates the reverse swirling flow and causes the suction casing to move in the circumferential direction. When three first rectifying plates are provided radially at intervals, and three second rectifying plates are provided radially between them, (f) generates a counter-swirl flow and causes the suction casing to move in the circumferential direction. In addition to providing four first rectifying plates radially spaced apart from each other It is a case of providing four sheets of the second straightening vane radially therebetween.

  The protruding height of the first rectifying plate 24 is set to about 1/3 of the inner diameter 2R of the suction casing 22, and the protruding height R2 of the second rectifying plate 25 is set to about ６ of the inner diameter 2R of the suction casing 22. Is set.

  Streamlines obtained as a result of the analysis are shown in FIG. 7 to FIG. 9, and a characteristic diagram showing the shaft power increase prevention effect of the rectifying plate is shown in FIG. 10. As shown in FIGS. 7 to 9, it has become clear how the rectifying plate exerts a rectifying action on the swirling flow. As shown in FIG. 8C, in the parallel arrangement of the three rectifying plates, there is a portion where the turning speed component parallel to the rectifying plate cannot be rectified, so that a slight reverse turning flow flows into the impeller. For this reason, FIGS. 8D, 9E, and 9F are arranged radially along the radial direction so that the swirling flow passing through the rectifying plate hits one of the rectifying plates, and the passage of foreign matter. In consideration of the characteristics, the center portion of the flow path is cut out. However, as shown in FIG. 8D, in the four rectifying plates, since the rectifying plate interval is increased outside the flow path, a flow that does not hit the rectifying plate remains.

  Therefore, in order to further improve, a rectifying plate having a narrow width is arranged between the rectifying plates, and a wide plate and a narrow plate are alternately arranged so that the rectifying action can be exerted even on the outer peripheral side (e) and (f ) Was analyzed. When six rectifying plates having different heights in the radial direction are installed as shown in FIG. 9 (e), the shaft power remains slightly increased as shown in FIG. 10 (e), but as shown in FIG. 9 (f). When eight rectifying plates having different heights in the radial direction were installed, the shaft power increase was substantially zero as shown in FIG.

  In the case of FIG. 9 (e), the circumferential distance between the axial center tip of each rectifying plate and the rectifying plate adjacent in the circumferential direction is about 35% of the suction casing diameter. Considering the passage of foreign matter and the increase in shaft power, the ratio is preferably in the range of 10% to 40%. On the other hand, when the inner diameter of the suction casing changes along the flow path direction, the relationship between the protrusion height of the current plate and the casing inner diameter is considered in a cross section perpendicular to the flow path center. In the above embodiment, the suction casing has a circular cross section. However, the suction casing may be square or flat. In this case, it goes without saying that the casing inner diameter is the hydraulic diameter.

  As is clear from FIG. 10, at 100% Q, the shaft power suppression effect is in the order of (b <(d) <(c) <(e) <(f), and the eight rectifications in (f) When the plate was attached, even if the shaft power increased corresponding to the actual machine field, it was possible to operate with almost the same shaft power as when there was no reverse turning.

Front view of pump gate according to the present invention Rear view of pump gate according to the present invention (A) Top view of the pump gate according to the present invention, (b) Plan sectional view of the main part of the pump gate according to the present invention Sectional view of the pump device according to the invention It is explanatory drawing which shows an example of the baffle plate provided in the suction casing inner periphery of the pump apparatus, (a) is explanatory drawing which shows arrangement | positioning of the baffle plate seen from the inlet side of the suction casing, (b) is diagonal of a suction casing Explanatory drawing showing the arrangement of the current plate as seen from above Perspective view of the main part of the pump device subject to numerical analysis Streamline diagram obtained as a result of numerical analysis Streamline diagram obtained as a result of numerical analysis Streamline diagram obtained as a result of numerical analysis Characteristic chart showing shaft power rise prevention effect of rectifying plate Explanatory drawing of conventional current plate Explanatory drawing of conventional current plate

1: First water channel 2: Second water channel 3: Pump gate 4: Gate 4a: Sluice column 4b: Floor member 4 Concrete floor 6: Water stop gate door body 7: Lifting mechanism 7a: Rack bar 7b: Fitting 7c: Gear box 7d: Manual operation handle 7e: Drive coupling mechanism 11: Axial pump 12: Flap valve mechanism 16: Motor main body 16a: Oil chamber 16b: Submerged chamber 16c: Motor chamber 1
16d: Motor chamber 2
17: Main shaft 18: Impeller 18a: Blade boss 18b: Blade 19: Guide vane 20: Casing 20a: First casing 20b: Second casing 20c: Third casing 21: Casing liner 21a: Groove 22: Suction casing 22a: Tip Opening 23: Current plate 24: First current plate 25: Second current plate M: Electric motor

Claims (8)

A pump device in which a plurality of rectifying plates are provided inside a suction casing disposed on the upstream side of the impeller,
The rectifying plate is circumferentially spaced from the inner peripheral surface of the suction casing so that the flow direction distribution in a cross section perpendicular to the flow path center line of the suction casing is aligned with a predetermined angle of attack with respect to the impeller. arranged cantilevered Te, axial protrusion height in the direction of the suction casing, the set suction at 15% to 35% of the inner diameter of the casing Rutotomoni, the projection height is arranged differently pump apparatus. Axial tip and the circumferential adjacent in a direction the current plate and the circumferential distance of Claim 1, wherein are arranged with different protrusion heights in the axial direction substantially equal pump of each rectifying plate apparatus. The pump device according to claim 2, wherein the rectifying plate having a high protrusion height in the axial direction and the rectifying plate having a low protrusion height are alternately arranged in the circumferential direction. The pump device according to any one of claims 1 to 3, wherein a maximum protruding height of the rectifying plate in an axial direction is set to be substantially the same as a radial length of a blade of the impeller.   The circumferential distance between the axial direction front-end | tip part of each current plate and the current plate adjacent to the circumferential direction is set to 10%-40% of the internal diameter of the said suction casing. Pumping equipment.   The pump device according to any one of claims 1 to 5, wherein a front edge portion of each rectifying plate is inclined in a flow direction along the axial direction. The current plate is composed of eight sheets, and four current plates having a low protrusion height in the axial direction are arranged between four current plates having a high protrusion height in the axial direction. 6. The pump device according to any one of 6. A pump gate device comprising the pump device according to any one of claims 1 to 7 attached to a water stop gate body that can be freely opened and closed.