JP2007051551A - Double suction volute pump - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve pump efficiency in a double suction volute pump for enabling low pulsation, and using an impeller of a different phase. <P>SOLUTION: This double suction volute pump uses an impeller part 4 of the different phase having first and second two impeller parts 4a and 4b of imparting a phase shift to a preset position of a blade 7; and is provided with a straightening vane 11. This straightening vane restrains a secondary flow brought about by asymmetry of an outlet flow from the first and second respective impeller parts. Thus, the pump efficiency can be enhanced while effectively making the most of the low pulsation forming action by the impeller of the different phase by restraining the secondary flow such as a swirling flow being the cause of reducing the pump efficiency. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a centrifugal pump, and more particularly to a double suction centrifugal pump having two suction ports.

  In the centrifugal pump, the fluid is boosted mainly by centrifugal force generated by the rotation of the impeller. A typical example of a centrifugal pump is a double suction centrifugal pump. In both suction centrifugal pumps, a double-structured impeller in which two first and second impeller parts formed by providing a plurality of blades are combined in a back-to-back state (this includes two impellers). It is usually formed in a structure that is combined back to back).

  For both of these suction centrifugal pumps, a predetermined phase shift (for example, 1/2 or 1/4 of the pitch between the blades) is given to the setting position (setting phase) of the blade between the first and second impeller units. A structure using such an impeller is known. This structure is also called a low pulsation type, and since the blades in the first and second impeller portions are out of phase with each other, the pressure fluctuation caused by the interference between the blade and the start of volute winding ( Pressure pulsation) can be reduced, and therefore vibration and noise of the pump can be reduced (for example, Patent Document 1 and Non-Patent Document 1). Note that examples of both suction centrifugal pumps are also disclosed in Patent Documents 2 to 5, for example.

JP 2002-133891 A JP 2003-184786 A JP 2005-23816 A JP 2003-120590 A JP 2001-295791 A “Turbo Pump” edited by Turbo Machinery Association (p.168, Fig. 11.9)

  As described above, the structure using an impeller having a different phase has an excellent characteristic that pressure fluctuation can be reduced. However, on the other hand, there is a problem of a decrease in pump efficiency. This problem will be described with reference to FIGS. (A) of FIG. 5 has shown the state which carried out the cross section to the vertical direction of the conventional common both suction centrifugal pump. As can be seen in this figure, both suction centrifugal pumps have a pump casing 1 in which a suction casing 2 and a volute casing (discharge casing) 3 are integrally combined. The volute casing 3 accommodates an impeller 4 having a different phase therein, and the inside thereof is a volute flow path (discharge flow path) 5. It is made to discharge by the volute channel 5. The volute channel 5 has a double volute structure. That is, the volute channel 5 is divided into two by the partition wall 6 in the middle of the volute channel 5 so as to branch into the outer volute channel 5a and the inner volute channel 5b. Such a double volute structure is used for the purpose of reducing the radial fluid force in the impeller 4 in order to reduce the thrust force applied to the rotating shaft 4 s of the impeller 4.

  As shown in FIGS. 5B and 5C, the impeller 4 has a double structure in which the first impeller portion 4a and the second impeller portion 4b are combined back to back. Each of the first and second impeller parts 4a and 4b has the same number (five in the illustrated example) of blades 7 (the blade 7a is a blade of the first impeller portion 4a, and the blade 7b is a second blade) The blades of the wheel portion 4b are provided, and a predetermined phase shift (a phase shift of ½ of the pitch between the blades in the example in the figure) is given to the set positions of the blades 7 between them.

  In such an impeller 4, generally, the fluid flow in the inter-blade channel is not uniform in the circumferential direction of the impeller 4. That is, as shown in FIG. 5B, the first impeller portion 4a has a flow velocity distribution D1 in which the flow velocity in the radial direction of the impeller gradually changes from one blade 7 to the next blade 7. And the 2nd impeller part 4b also has the same flow velocity distribution D2. And each non-uniform | heterogenous flow velocity distribution D1, D2 has produced the shift | offset | difference according to the phase shift of the blade | wing 7 between both the impeller parts 4a and 4b. For this reason, as shown in FIG. 6, a difference is produced in the flow velocity between the outlet flows in the two impeller portions 4a and 4b. In other words, a high flow velocity side and a low flow velocity side are generated across the boundary surface between the two impeller portions 4 a and 4 b, and asymmetry occurs in the outlet flow of the impeller 4. When this asymmetry occurs, the flow on the side with the higher flow velocity will affect the side with the lower flow velocity across the boundary surface. As a result, the volute cross section (the volute in the direction intersecting the fluid flow direction) A swirling flow C is caused as a secondary flow along the inner wall surface on the outer periphery side of the volute channel in the direction of the cross section of the channel 5. The swirling flow C changes with time according to the rotation of the impeller 4 in the same volute cross section. Such a secondary flow affects the direction of the main flow of the fluid in the volute channel 5. Therefore, the direction of the main flow changes with time in the same volute cross section, and the high-speed flow coming out of one impeller part decelerates while mixing with the low flow velocity region from the other impeller part while being twisted in time. Will be going. Such a state brought about by the impeller 4 having the different phase increases the mixing loss as compared with the impeller having the same phase. That is, in the impeller of the same phase that does not give a phase shift to the setting position of the blade between the first and second impeller parts, the flow is uniform and symmetrical as shown in FIG. Although it naturally decelerates in the radial direction while making a turn, compared to such a case, the impeller 4 having a different phase increases the mixing loss, and thus reduces the pump efficiency.

  The present invention has been made on the basis of the above knowledge, and an object of the present invention is to improve the pump efficiency of a double suction centrifugal pump that uses an impeller with different phases that enables low pulsation.

  For the above purpose in the present invention, each of the first and second impeller parts has a first impeller part and a second impeller part each provided with a plurality of blades. In the double suction centrifugal pump, the first impeller unit includes an impeller having a predetermined phase shift at the set position and a volute channel that discharges fluid that has been pressurized by the impeller. A rectifying plate is provided that suppresses the secondary flow caused by the asymmetry between the outlet flow from the outlet and the outlet flow from the second impeller unit.

  Further, in the present invention, for the above-described both suction centrifugal pumps, the rectifying plate is configured to divide the volute flow path along the boundary surface of the first and second impeller parts by dividing the volute flow path into its radial total width and total length. So that it is provided.

  Further, in the present invention, in the above-described two-suction centrifugal pump, the volute channel is divided into two by a partition partway from the middle to be branched into an outer volute channel and an inner volute channel, The first rectifying plate portion is formed from the volute winding start portion of the volute channel to the vicinity of the branch portion to both the outer and inner volute channels. The volute channel is provided so as to be divided into two over the entire radial width thereof, and the second rectifying plate portion is arranged so that the inner volute flow from the vicinity of the branch portion to the vicinity of the junction of the outer and inner volute channels. The road is provided so as to be divided into two over its entire radial width.

  Further, in the present invention, in the above-described two-suction centrifugal pump, the volute channel is divided into two by a partition from the middle to branch into an outer volute channel and an inner volute channel. A rectifying plate and a second rectifying plate are provided, and the first rectifying plate has a volute for a volute channel from a volute winding start portion of the volute channel to a vicinity of a branching portion to both the outer and inner volute channels. The second rectifying plate is provided so as to bisect from the inner peripheral wall surface of the flow path over a certain range of radial width, from the vicinity of the branching section to the vicinity of the junction of the both outer and inner volute flow paths. The inner volute channel is provided so as to be divided into two parts over a certain range of radial width from the inner side surface of the partition wall.

  In the present invention, a rectifying plate is provided, and the secondary flow caused by asymmetry with the outlet flow from each of the first and second impeller portions in the impeller of different phase is suppressed by the rectifying plate. . For this reason, according to the present invention, it is possible to effectively suppress the secondary flow such as the swirling flow that causes the pump efficiency to be reduced, and therefore, while effectively utilizing the low pulsation action by the impeller of different phase, the pump efficiency Therefore, it is possible to realize a double suction centrifugal pump with higher performance.

  Hereinafter, modes for carrying out the present invention will be described. FIG. 1 shows the structure of a double suction centrifugal pump according to the first embodiment. FIG. 1A shows a state in which both suction centrifugal pumps according to the present embodiment are sectioned in the longitudinal direction, and FIG. 1B is along the line AA in FIG. The main part is shown in a cross-sectional state. The double suction centrifugal pump of this embodiment is common to the conventional double suction centrifugal pump described with reference to FIG. 6 in its basic structure. Therefore, hereinafter, a configuration characteristic of the present invention will be mainly described, common portions are denoted by the same reference numerals as those in FIG. 6, and description thereof will be omitted as appropriate.

  The characteristic configuration of the present invention is that a rectifying plate 11 is provided in the volute channel 5. As shown in FIG. 2, the rectifying plate 11 has a function of rectifying the outlet flow S1 from the first impeller portion 4a and the outlet flow S2 from the second impeller portion 4b so as to be isolated. In order to realize this function, in this embodiment, the rectifying plate 11 is provided so as to divide the volute flow path 5 into two along its entire radial width and total length along the boundary surface between the two impeller parts 4a and 4b. ing.

  In this way, the outlet flows S1 and S2 having different flow velocities from the first impeller portion 4a and the second impeller portion 4b are separated by the rectifying plate 11 and rectified, thereby having the different phases described above. In the flow velocity asymmetry of the outlet flow in the impeller 4, the phenomenon that the flow on the side with the higher flow velocity affects the side with the lower flow velocity is prevented, thereby generating a secondary flow like the swirl flow C in FIG. 6. Can be effectively suppressed. That is, it is possible to effectively suppress the swirl flow C that causes a reduction in pump efficiency in the impeller 4 having a different phase, thereby improving the pump efficiency.

  FIG. 3 shows the structure of a double suction centrifugal pump according to the second embodiment. The relationship between (a) and (b) in FIG. 3 is the same as that in FIG. This embodiment is different from the first embodiment in the installation range of the rectifying plate 12 with respect to the volute channel 5. That is, the rectifying plate 12 in the present embodiment is composed of the first rectifying plate portion 12a and the second rectifying plate portion 12b. The first rectifying plate portion 12a extends over the entire radial width of the volute channel 5 from the volute winding start portion 13 of the volute channel 5 to the vicinity of the branching portion to the outer volute channel 5a and the inner volute channel 5b. On the other hand, the second rectifying plate portion 12b is provided for the inner volute channel 5b from the vicinity of the branch portion to the vicinity of the junction of the outer volute channel 5a and the inner volute channel 5b. It is provided so as to be divided into two over its entire radial width.

  Such a rectifying plate 12 has the same effect as the rectifying plate 11 in the first embodiment, but also has a smaller area than the rectifying plate 11 in the first embodiment. 12 brings about an effect of reducing wall friction loss between the fluid and the fluid.

  FIG. 4 shows the structure of a double suction centrifugal pump according to the third embodiment. The relationship between (a) and (b) in FIG. 4 is the same as that in FIG. This embodiment is different from the first embodiment and the second embodiment in that the first rectifying plate 14 and the second rectifying plate 15 are provided. The first rectifying plate 14 has a diameter within a certain range from the inner wall surface on the outer peripheral side of the volute channel, with respect to the volute channel 5 from the volute winding start portion 13 to the vicinity of the branching portion to the outer volute channel 5a and the inner volute channel 5b. It is provided so as to divide into two over the direction width. On the other hand, the second rectifying plate 15 has a certain range from the inner surface of the partition wall 6 with respect to the inner volute channel 5b from the vicinity of the branch portion to the vicinity of the junction of the outer volute channel 5a and the inner volute channel 5b. It is provided so as to divide into two over the radial width.

  These rectifying plates 14 and 15 are intended to obstruct the secondary flow as described above, that is, the secondary flow such as the swirl flow C (FIG. 6) along the inner wall surface of the volute flow path in the direction of the volute cross section. The secondary flow inhibition function suppresses the generation of a secondary flow such as the swirling flow C. Therefore, the above-mentioned “a certain range from the inner wall surface on the outer periphery side of the volute flow path” and “a certain range from the inner surface of the partition wall 6” are ranges in which the secondary flow can be effectively inhibited. Such rectifying plates 14 and 15 have a smaller area than the rectifying plate 12 in the second embodiment, and can further reduce wall friction loss with the fluid.

  INDUSTRIAL APPLICABILITY The present invention makes it possible to improve the pump efficiency of a double suction centrifugal pump using an impeller with different phases that enables low pulsation, and can be widely used in this field.

It is a figure which shows the structure of the both suction vortex pump by 1st Embodiment. It is a figure which shows the effect | action of the baffle plate in 1st Embodiment. It is a figure which shows the structure of the both suction vortex pump by 2nd Embodiment. It is a figure which shows the structure of the double suction vortex pump by 3rd Embodiment. It is a figure which shows the general structure of the conventional different phase impeller type | mold double suction centrifugal pump. It is a figure which shows the state of the impeller exit flow in the both suction vortex pumps of FIG. It is a figure which shows the state of the impeller exit flow in the same phase impeller type | mold both suction centrifugal pump.

Explanation of symbols

4a 1st impeller part 4b 2nd impeller part 5 Volute flow path 5a Outer volute flow path 5b Inner volute flow path 6 Partition 7 (7a, 7b) Vane 11, 12 Rectification plate 12a First baffle plate 12b Second rectifying plate portion 13 Volute winding start portion 14 First rectifying plate 15 Second rectifying plate C Swirl flow (secondary flow)
S1 Outlet flow from the first impeller part S2 Outlet flow from the second impeller part

Claims (4)

A first impeller part and a second impeller part each provided with a plurality of blades, and a predetermined phase shift between the first and second impeller parts at a set position of the blades; In both suction centrifugal pumps provided with a given impeller and provided with a volute flow path for discharging a fluid subjected to pressure increase by the impeller,
Both suctions characterized in that a rectifying plate is provided to suppress the secondary flow caused by the asymmetry between the outlet flow from the first impeller part and the outlet flow from the second impeller part. Centrifugal pump.   The said baffle plate is provided so that the said volute flow path may be divided into 2 along the radial direction full width and full length along the boundary surface of both said 1st, 2nd impeller parts. Double suction centrifugal pump.   The volute channel is divided into two by a partition wall in the middle of the volute channel so as to be branched into an outer volute channel and an inner volute channel, and the rectifying plates are a first rectifying plate portion and a second rectifying plate portion. The first rectifying plate portion is 2 over the entire width in the radial direction of the volute channel from the volute winding start portion of the volute channel to the vicinity of the branching portion to both the outer and inner volute channels. The second rectifying plate portion is divided into two parts over the entire radial direction width of the inner volute channel from the vicinity of the branching portion to the vicinity of the junction of the outer and inner volute channels. The double-suction centrifugal pump according to claim 1, which is provided to do so. The volute channel is divided into two parts by a partition wall in the middle of the volute channel to be branched into an outer volute channel and an inner volute channel, and a first rectifier plate and a second rectifier plate are provided as the rectifier plate. The first rectifying plate has a certain range from the inner wall surface on the outer peripheral side of the volute channel with respect to the volute channel from the volute winding start portion of the volute channel to the vicinity of the branching portion to both the outer and inner volute channels. The second rectifying plate is provided so as to divide into two parts over the radial width, and the partition wall is formed on the inner volute channel from the vicinity of the branch portion to the vicinity of the junction of the outer and inner volute channels. The double-suction centrifugal pump according to claim 1, which is provided so as to divide into two parts over a certain range of the radial width from the inner side surface.

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