JP4183612B2 - Axial flow pump - Google Patents

Description

  The present invention relates to an axial flow pump.

  Conventionally, an axial pump has been widely used as a pump for transporting a liquid such as water with a large flow rate and a low head. The general axial flow pump has three or four rotor blades, and the center line of the leading edge and the trailing edge is perpendicular to the rotation axis in both the meridian and circumferential directions. Has been.

  Thus, when the number of blades is about 3 to 4, the load per rotor blade is large and a pressure difference is generated between the front and back of the rotor blade. Furthermore, since the leading edge and the trailing edge are erected vertically, a large amount of leakage flow is generated in the gap between the tip of the rotor blade and the inner periphery of the casing, and a strong vortex is generated. Also, cavitation occurred depending on the pressure conditions.

  As an axial flow pump which suppresses generation | occurrence | production of such a cavitation, there exists a thing shown by Unexamined-Japanese-Patent No. 2002-364579 (patent document 1).

This document discloses an axial flow pump in which a rotor blade is advanced in the rotational direction of an impeller and is tilted forward in the meridian plane.
JP 2002-364579 A (paragraphs [0019] to [0022], FIGS. 2 and 3)

  For example, in the cavitation tunnel 100 shown in FIG. 12, an axial pump 105 is used to circulate water. When measuring the generated sound in the inspection area 103 of the cavitation tunnel, if noise is generated from the axial flow pump 105, noise is generated and the measurement accuracy is lowered. Therefore, the axial flow pump is reduced as much as possible. There is a need to.

  The above document aims to provide a large flow rate and low head pump that can be operated stably over the entire flow rate range (see paragraph [0008]), but does not take into account noise reduction. In particular, an embodiment in which there are two rotor blades is shown, and this imposes a heavy load on the rotor blades and cannot reduce noise.

  Further, although there is a description that the rotor blade is advanced (skewed) in the rotation direction, no examination is made as to how much advancement is necessary.

  In view of the above problems, an object of the present invention is to provide an axial pump that achieves low noise.

  In order to solve the above problems, the axial pump of the present invention employs the following means.

  The axial flow pump according to the present invention includes a plurality of rotating blades in an impeller rotatably disposed in a casing, and advances the rotating blades in the rotation direction of the impeller and on the upstream side in the meridian plane. In the axial flow pump inclined forward, the number of the rotor blades is 6 to 9, and the distance from the front edge of the center position on the blade chord in the outermost rotor cylinder cross section is the innermost rotor blade cylinder. The sweeping ratio divided by the distance from the front edge of the center position on the chord in the cross section is advanced so as to be 1.5 to 4.0.

  The sweep ratio is introduced as the degree of advancement of the rotor blades. By setting the sweep ratio to 1.5 to 4.0, it is possible to reduce loss, that is, noise, while securing the lift. When the sweep ratio is less than 1.5, the loss increases and the noise exceeds the allowable level. When the sweep ratio is larger than 4, the necessary lift cannot be secured.

  The sweep ratio is more preferably 2.2 to 3.4, and still more preferably 2.4 to 3.0.

  By reducing the number of rotor blades to 6 or more, the load per rotor blade is reduced. Thereby, the pressure difference between the front and back of the rotor blade is reduced, the leakage flow rate from the tip of the rotor blade is reduced, and the noise is reduced. On the other hand, when the number of rotor blades exceeds 9, not only the wet area of the rotor blades increases and the performance decreases, but also the cost increases.

  Further, since the rotor blade is tilted forward in the meridian plane, the viscosity loss can be reduced and various vortices can be reduced.

Further, in the axial flow pump of the present invention, the tip interval between the inner periphery of the casing and the tip of the rotor blade is 0.001 to 0.010 in a ratio to the blade span of the rotor blade. Features.

By setting the tip interval (tip clearance) to 0.010 or less as a ratio to the blade span, the initial cavitation can be kept low. Noise can be reduced by avoiding cavitation.

On the other hand, the smaller the ratio to the blade span is, the more effective the reduction of the initial cavitation is. However, when this ratio is less than 0.001, the tip interval is too small and the structure is not realized.

More preferably, the tip interval is 0.002 to 0.007 as a ratio to the blade span.

Further, the axial flow pump of the present invention comprises a plurality of fixed blades fixedly arranged on the downstream side of the respective rotary blades,
The axial distance between the trailing edge of the rotor blade and the leading edge of the fixed blade is 0.1 to 0.3 as a ratio to the rotor blade diameter.

  The shorter the distance between the shafts, the better the efficiency. However, the wake generated by the rotating blade collides with the immediately following fixed blade, which is not preferable from the viewpoint of noise. Therefore, the shaft interval is set to 0.1 or more in the ratio to the rotor blade diameter.

  As the shaft spacing increases, noise decreases but efficiency decreases. Therefore, the shaft interval is set to 0.3 or less in the ratio to the rotor blade diameter.

  Note that the “distance between axes” refers to the distance between the trailing edge of the rotating blade and the leading edge of the fixed blade. For example, when the impeller is viewed from the meridian plane, it is fixed to the trailing edge of the rotating blade. The closest distance to the wing's leading edge.

  According to the present invention, since the sweep ratio is set to 1.5 to 4.0, loss, that is, noise can be reduced while securing the head.

In addition, since the number of rotor blades is 6 to 9, it is possible to achieve both noise reduction while maintaining high performance.

Since the tip interval is about 0.001 to 0.010 as a ratio to the blade span, the initial cavitation can be suppressed low, and the noise can be reduced.

  Since the axial interval between the trailing edge of the rotor blade and the leading edge of the fixed blade is 0.1 to 0.3 in terms of the ratio to the rotor blade diameter, both high efficiency and low noise can be achieved.

  Embodiments of an axial flow pump according to the present invention will be described below with reference to the drawings.

  FIG. 1 is a perspective view of an impeller 1 used for an axial pump.

  The impeller 1 is rotatably arranged in a casing (not shown). A plurality of impellers (rotary blades) 3 are fixed to the impeller 1. In the present embodiment, the number of impellers 3 is seven. The impeller 3 is an open impeller that is not provided with a shroud at its tip.

  As shown in FIG. 2, the impeller 3 moves forward in the rotational direction of the impeller 1.

  That is, the impeller 3 has a shape in which airfoils as shown in FIG. On these airfoils, a chord 5 connecting the leading edge 7 and the trailing edge 8 is defined, and a center 9 is located on the chord. A center 9 on each chord 5 is arranged on a reference line L passing through the rotation center of the impeller 1. The impeller 3 is moved forward by shifting the center 9 in the rotation direction of the impeller 3. Here, the center 9 is a position (stacking center) on the chord 5 which is the maximum blade thickness.

  Here, a sweep ratio is introduced as a parameter representing the degree of advance.

  As shown in FIG. 3, the sweep ratio is the distance from the leading edge 7 at the center 9 position on the chord 5 in the cylindrical cross section of the outermost impeller 3, and the chord 5 in the cylindrical cross section of the innermost impeller 3. It is assumed that it is divided by the distance from the leading edge of the upper 9 positions.

  In the case shown in FIG. 3, the center 9a of the chord 5a in the cylindrical cross section of the outermost impeller 3 on the tip side is located at a position away from the leading edge 7 by 55% with respect to the total chord length. The center 9b of the chord 5b in the cylindrical cross section of the innermost impeller 3 on the hub side is a position away from the leading edge 7 by 25% with respect to the entire chord length. Therefore, in this case, the sweep ratio is 55/25 = 2.2.

  FIG. 4 is a view of the meridian plane of the impeller 1 including the impeller 3.

  The impeller 3 has a shape in which the leading edge and the trailing edge are inclined forward toward the upstream side of the fluid flow.

  A diffuser (fixed vane) 11 is disposed downstream of the impeller 3 as viewed from the fluid flow. Although not shown, the number of diffusers 11 is nine in the present embodiment.

  The axial flow pump having the above configuration rotates the impeller 1 by a driving source (not shown) and sends out fluid by the seven impellers 3 fixed to the impeller 1. The fluid sent out from the impeller 3 collects kinetic energy by the diffuser 11.

  Numerical analysis was performed on the axial flow pump having the specifications shown in Table 1.

Type A及びtype Bともに、本発明の軸流ポンプであり、回転方向に前進し、子午面内において前傾したインペラを７枚有している。また、ディフューザは９枚となっている。

Both Type A and Type B are axial flow pumps according to the present invention, and have seven impellers that move forward in the rotational direction and tilt forward in the meridian plane. There are 9 diffusers.

  The outer diameters of the impeller and diffuser are 300 mm for Type A and 500 mm for Type B.

  FIG. 5 shows an analysis result of examining the number of impellers.

  (A) shows the load per blade relative to the number of impellers.

  (B) shows the reduction ratio relative to the number of impellers.

  As can be seen from FIG. 5A, when the number of impellers is 6 or more, the load per blade is reduced, so that cavitation at the tip of the impeller can be prevented, and noise can be reduced.

  On the other hand, as can be seen from FIG. 5B, when the number of impellers exceeds 9, the reduction ratio increases and the efficiency decreases.

  From the above, the number of impellers is preferably 6 or more and 9 or less. More preferably, the number is 7.

  FIG. 6 shows an analysis result of examining the sweep ratio.

  In (a), the loss is shown relative to the sweep ratio.

  In (b), the total pressure is shown relative to the sweep ratio.

  In each figure, the sweep ratio is plotted for 1.0, 1.5, 2.2, 2.4, 3.0, 3.4, 4.0, 5.0.

  As can be seen from these figures, as the sweep ratio increases, the loss decreases (noise also decreases), but the total pressure, that is, the total lift also decreases. Therefore, a sweep ratio in the range of 1.5 to 4.0 is desirable. More preferably, it is 2.2-3.4, More preferably, it is the range of 2.4-3.0.

  FIG. 7 shows an analysis result of examining the interaxial distance between the impeller and the diffuser.

  The horizontal axis in FIG. 7 shows the dimensionless inter-axis distance, and the vertical axis shows the head relatively.

  The distance between axes was made dimensionless as follows. That is, the distance obtained by dividing the shortest distance between the hub-side rear edge of the impeller and the hub-side front edge of the diffuser by the outer diameter of the impeller was defined as the dimensionless inter-axis distance.

As can be seen from FIG. 7, the inter-axis distance is a dimensionless value of 0.2, and the head is the largest, and therefore the noise is also small.

The smaller the distance between the shafts, the better the efficiency. However, the wake generated by the impeller collides with the diffuser immediately after that, which is not preferable from the viewpoint of noise. Therefore, it is preferable that the dimensionless axis distance is 0.1 or more.

  As the distance between the axes increases, the noise decreases but the efficiency decreases. Therefore, it is preferable that the dimensionless center distance is 0.3 or less.

  FIG. 8 shows the analysis result of examining the effect of the gap (tip clearance) between the impeller tip and the inner periphery of the housing on the initial cavitation.

  FIG. 8 shows the result of study on Type A (see Table 1).

  In FIG. 8, the horizontal axis represents the flow rate, and the vertical axis represents the cavitation coefficient. The flow rate is a relative numerical value with 1.0 as a design point.

  A solid line indicates a chip clearance of 0.10 mm, and a broken line indicates a chip clearance of 0.50 mm. When the tip clearance of 0.10 mm is divided by the impeller blade span to make it dimensionless, the blade span of Type A is 67.5 mm, so the tip clearance of 0.0015 and 0.50 mm is 0.0074. Become.

  (A) is the analysis result about the cavitation in the impeller surface.

  (B) is an analysis result about cavitation in the tip clearance.

  As can be seen from (a), the difference in tip clearance does not affect the primary cavitation on the impeller surface.

However, as can be seen from (b), the difference in the tip clearance affects the initial cavitation in the tip clearance. Therefore, it is necessary to design in consideration of the tip clearance.

From the above examination results, the initial cavitation can be kept low by setting the tip clearance to about 0.0015 to 0.007 as a ratio to the blade span. Moreover, noise reduction is realized by avoiding cavitation in this way.

On the other hand, if the ratio with respect to the blade span is less than 0.001, the tip clearance is too small and difficult to manufacture.

FIG. 9 shows the static pressure coefficient for the tip clearance analyzed for Type A and made dimensionless by dividing by the blade span. It is shown that the static pressure coefficient decreases as the tip clearance increases.

However, if the ratio of tip clearance to blade span exceeds 0.010, cavitation generation is encouraged. Therefore, it is necessary to determine the ratio of the tip clearance to the blade span within a range not exceeding 0.01.

  FIG. 10 shows the head coefficient with respect to the cavitation coefficient analyzed for Type A.

  Initial cavitation is confirmed around the cavitation coefficient of 0.4, which is lower than the pump operating point (NPSHav). Therefore, it can be seen that cavitation does not occur.

  FIG. 11 shows the sound pressure level with respect to the cavitation coefficient analyzed for Type A.

  As can be seen from this figure, when the cavitation coefficient falls below 0.4, it can be seen that noise increases due to cavitation.

  In a region where the cavitation coefficient is 0.4 or more, low noise of 110 dB or less is realized.

  According to the axial flow pump concerning this embodiment explained above, the following operation effects can be obtained.

  Since the sweep ratio is 1.5 to 4.0, more preferably 2.2 to 3.4, loss or noise can be reduced while securing the head.

  Since the number of impellers is 6 to 9, more preferably 7, it is possible to achieve both noise reduction while maintaining high performance.

  Since the tip clearance is set to 0.001 to 0.010, more preferably about 0.002 to 0.007 as a ratio with respect to the blade span, the initial cavitation can be kept low, and the noise can be reduced. it can.

  Since the inter-axis distance between the impeller 3 and the diffuser 11 is 0.1 to 0.3, more preferably 0.2 as a ratio to the impeller diameter, it is possible to achieve both low noise while maintaining high efficiency. Can do.

  Since the number of impellers 3 is 7 and the number of diffusers 11 is 9, the pressure balance can be optimized to reduce noise.

It is the perspective view which showed the impeller concerning this embodiment. It is the figure which showed the impeller seen from the upstream from the flow of the fluid. It is a figure which shows the definition of a sweep ratio. It is the side view which showed the impeller and diffuser in a meridian surface. The analysis results for the number of impellers are shown. (A) shows the relative load per blade relative to the number of impellers, and (b) shows the number of impellers. The relative reduction ratio is shown. The analysis results for the sweep ratio are shown. (A) shows the loss relative to the sweep ratio, and (b) shows the total pressure against the sweep ratio. Shown relatively. The analysis results of examining the distance between the impeller and the diffuser are shown. The analysis result which examined about the influence which a tip clearance has on primary cavitation is shown, (a) shows cavitation in an impeller surface, and (b) shows about cavitation in tip clearance. The static pressure coefficient for the tip clearance analyzed for Type A is shown. The head coefficient with respect to the cavitation coefficient analyzed for Type A is shown. The sound pressure level for cavitation coefficient analyzed for Type A is shown. It is side sectional drawing which showed the cavitation tunnel provided with the axial flow pump.

Explanation of symbols

1 impeller 3 impeller (rotary blade)
11 Diffuser (fixed wing)

Claims (3)

Provided with a plurality of rotating blades on an impeller disposed rotatably in a casing,
In the axial flow pump in which each of the rotor blades is advanced in the rotation direction of the impeller and inclined forward in the meridian plane,
The number of rotor blades is 6-9,
The sweep ratio obtained by dividing the distance from the leading edge of the central position on the chord in the outermost rotor blade cross section by the distance from the leading edge of the center position on the chord in the innermost rotor blade cross section, An axial flow pump characterized by being advanced so as to be 1.5 to 4.0. 2. The axial flow according to claim 1, wherein a tip interval between an inner periphery of the casing and the tip of the rotor blade is 0.001 to 0.010 in a ratio to the blade span of the rotor blade. pump.
A plurality of fixed blades fixedly arranged on the downstream side of each of the rotor blades;

The axial distance between the trailing edge of the rotor blade and the leading edge of the fixed blade is 0.1 to 0.3 as a ratio to the rotor blade diameter. The described axial flow pump.

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