DE3128372A1 - "PERIPHERAL CHANNEL PUMP" - Google Patents

Description

PATENT LAWYERS J. REITSTÖTTER W. KINZBBACH

PROF. DR. DR. DIPL. ING. DR. PHIL. DIPL. CHBM.

W. BUNTE <19S8-J97e) K. P. HÖLLBR

DR. ING. DR. RBR. NAT. DIPL. CHBM.

TBLBFONt (089) 37 65 TBLBXt B21E208 ISAR D

BAUERSTRASSB 22, 8000 MUNICH

Munich, July 17, 1981 M / 22 169

Friedrich Schweinfurter Bergstr. 6th

D-8 5 41 Röttenbach

Peripheral channel pump

POSTAL ADDRESS s POSTFACH 780, D-8000 MÖNCHEN

9 «1

Μ / 22 169

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The invention relates to a peripheral channel pump with a rotating Part or paddle wheel and a fixed part or housing, a conveying channel that starts from a suction opening Via at least one flow channel, as well as vane cells of the rotating part Sj corresponding to it, to an outlet opening leads.

With this special type of centrifugal pump, the pumped medium entering through the suction opening in the housing enters the flow channel and into the rotating vane cells of the impeller, with one extending from the vane cell and through the blade webs caused circulation flow forms which, supported by the centrifugal force, in a helically wound current path flows over the entire length of the flow channel and thereby from the beginning of the flow channel enters the vane cells of the rotating impeller several times up to the end of the flow channel, thereby transferring energy through the exchange of momentum from the impeller to the slower flowing volume flow with a lower energy state in the Flow channel takes place.

Centrifugal pumps of various types previously known under the term "side channel pump" all have the disadvantage the required very narrow side gap between the rotating and the fixed part, which complies with the tolerances to be observed, the manufacture and assembly, especially in the case of multi-stage execution, places high demands.

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There are special designs known in which appropriate constructive measures have been taken to reduce the sealing gap in to lay the easier and cheaper to master the radial plane, the results of which are particularly in the Dissertation by D. Schmitz, University of Dortmund: 1978, were published.

In summary, it can be stated that the solutions found so far have not produced satisfactory results. It has not been possible to relocate the sealing gap exclusively in the radial plane and still remain approximately the same To obtain energy transfer coefficient (pressure number). In addition, the previously known partial solutions require one high engineering and manufacturing effort.

The invention is based on the object of developing a simple, uncomplicated centrifugal pump in which the width of the sealing gap is determined exclusively by the radial production dimensions and the one at least the same Energy transfer rate (pressure number) as comparable conventional side channel pumps provides.

This object is achieved according to the invention in that the rotating part has at least one blade ring, which is open exclusively in the radial direction, of which Blade cells through blade webs that face the direction of rotation are inclined, are separated from each other, and that opposite, incorporated into the fixed part, at least one flow channel is located, which extends from the inlet opening in Direction of flow extends around a substantial part of the circumference to the outlet opening and that a radial gap seals the flow channel with the rotating part and that an interrupter is arranged in the flow channel, which is also sealed off from the rotating part by the radial gap is.

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The blade webs inclined to the direction of rotation preferably have a spirally curved course. The cross section of the vane cells perpendicular to the plane of rotation and the corresponding one The flow channel is preferably elliptical, but can also be circular or asymmetrical. the However, cross-sections of the flow channel and the vane cells can also have different contours. Asymmetrical and elliptical cross-sections are particularly advantageous in connection with spirally curved blade cells. In the plane of rotation seen, the vane cells have angled or circular / elliptical or other rounded cross-sections.

The impeller preferably has only one blade ring on the opposite side arranged flow channel. However, it is also advantageous to have a plurality of blade wreaths arranged next to one another with the corresponding, opposite flow channels.

The flow channel preferably has a constant cross-section in the direction of flow, but can also be closed or decreasing cross-sections be advantageous.

The construction according to the invention shows a high energy transfer coefficient and has the advantage that no axial side gaps are required to seal the impeller. This is unnecessary the very precise positioning of the impeller on the shaft and its backlash-free mounting in the axial direction. Particularly in the case of multi-stage construction, the advantages of the invention are clearly borrowed. For example, there are no parts between the impellers, such as side channel housings, transition housings, guide devices, etc. are necessary. Thus, one can already be placed on the shaft Insert the set of several impellers completely into the pre-assembled pump housing. The exclusively in the Sealing gap arranged in the radial plane enables the contactless operation of the impellers without additional effort. Through this the result is an extremely low-wear operation of the pump. The short transitions from level to level and the lack of anything else

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common parts between the impellers allow an extremely short design. The exclusively radially arranged blade ring allow very small impeller diameters, which means very flac Pump characteristics and very small pump diameters can be achieved.

By means of spirally curved blade webs arranged in the direction of rotation, which transport the medium within the To separate the vane cells from the pumping medium flowing more slowly in the flow channel, a displacement flow in a semi-axial direction out of the vane cell and into the Volume flow triggered into the flow channel. This creates a circulation flow that is caused by the centrifugal force field is supported and leads to more frequent re-entry of the medium into the vane cells than has previously been achieved was, so that surprisingly high energy transfer figures result.

As a rule, the impeller rotates with the blade ring inside a housing with arranged in the circumferential direction Flow channel. In a further advantageous embodiment however, the rotating part is designed as a ring-shaped impeller and rotates with the blade ring open to the center of the axis around the stationary part with incorporated therein Flow channel around. The inlet and outlet openings are centered on the axis. This results in an extremely compact construction without drive shaft, for installation in pipes etc.

Another advantageous embodiment of the invention results consists of the arrangement of two blade rings at an axial distance from one another, between which a closed one Centrifugal blade part is formed, the blades of which extend from a circular, axially centered suction opening, and a preferably spiral-shaped one in the circumferential direction Have arranged flow channel increasing cross-section. This leads in the direction of flow into the immediately following Vane cells and flow channels. This design results in a particularly high degree of efficiency and very low holding pressure levels (NPSH values) of the centrifugal pump.

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Another essential advantage of the invention results from the shape of the blade webs used. For example, they are made straight, at an angle to the direction of rotation used instead of the spiral-shaped curved blade webs, the centrifugal pump can simply be reversed by reversing the Direction of rotation in both directions of flow with "absolutely identical performance data. This effect is all the more More surprising than for such a reversal of the conveying direction, previously expensive sliding systems or two separate ones Pumps were necessary.

Further features and advantages of the invention emerge from the subclaims and from the following description of embodiments shown in the drawings.

Show it:

Figure 1 shows a cross section through an inventively designed Pump,

Figure 2 shows a section in the plane II-II of Figure 1,

FIG. 3 partial longitudinal sections through one designed according to the invention - Pump with internal flow channel and rotating blade ring on the outside, wherein the upper partial section corresponds to plane III from FIG. 4 and the lower part corresponds to plane V from FIG.

FIG. 4 shows a section through the pump housing in plane IV-IV of FIG. 3,

FIG. 5 shows a blade cell with a flow channel of asymmetrical cross section,

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Figure 6 shows the development of an impeller with spiral-shaped curved Shovel webs,

FIG. 7 shows the cross section of a symmetrical blade cell with flow channel in elliptical shape,

FIG. 8 shows the development of an impeller with straight, obliquely arranged blade webs,

FIG. 9 shows a cross section through the blade cell and flow channel in a circular shape,

Figure 10 shows a cross section through an impeller with double Blade ring with common flow channel,

Figure 11 is a development of an impeller with double Blade ring and spirally curved blade bars with middle bar,

FIG. 12 shows a cross section through an impeller with blade cells, which are separated by a central bar. and have separate flow channels,

FIG. 13 shows a cross section through an impeller with two inside one another passing blade rings and a common flow channel,

Figure 14 the. Development of an impeller with two inside each other overhanging blade rings and spirally curved blade webs without a central web.

FIG. 15 shows a cross section through an impeller with two inside one another passing blade rings and separate flow channels,

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FIG. 16 shows a development of an impeller with a double blade ring and straight blades arranged at an angle Shovel bars with center bar,

Figure 17 is a development of an impeller with double Blade ring and straight, diagonally arranged blade bars without center bar,

FIG. 18 shows the longitudinal section of a pump version open centrifugal wheel part arranged on the face side,

FIG. 19 shows a longitudinal section through an embodiment with double blade rings and a closed centrifugal wheel part arranged between them,

FIG. 20 a half longitudinal section of a pump design with four blade rings,

FIG. 21 a half longitudinal section through the further variant of an embodiment with several blade rings,

FIG. 22 shows a longitudinal section through a multi-stage embodiment in a link construction.

The embodiment shown in Figures 1 and 2 is single-stage and single-flow and consists of one Housing 10 and an impeller 21. The housing 10 sits down together from a housing ring 11 with suction opening 12 and Outlet opening 13, a bearing cover 14 and a housing cover 15 parallel thereto, each of which has one O-ring 16 sealed on the housing ring 11 and by means of the housing screws 17 are held together.

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In the housing 10 there is one in the bearing cover 14 via packing rings 18 sealed shaft 19 arranged by a not shown Drive motor, for example a two-pole electric motor, can be set in rotation, for example in the direction of the arrow can. The impeller 21 is fastened to the free end of the shaft 19 by means of a feather key 20.

The impeller 21 embodied as a disk is provided with a ring of vane cells 24, opposite to which a flow channel 23 is arranged, which is incorporated into the housing ring 11 The vane cells 24 are separated from one another by vane webs 25. The vane cells A (Figure 1) point in the plane of rotation seen on elliptical cross-sections, the remaining angled cross-sections.

The opposite flow channel 23 has one, the respective! Contour to be adapted to requirements, its cross-sectional area can remain the same, increase or decrease in the direction of flow. Here it has a constant contour that is concentric to the center of the impeller Cross-section on. Between the outlet opening 13 and the inlet opening 12, the flow channel 23 is through a jn Breaker 26 interrupted. The outer diameter of the impeller 21 is dimensioned in relation to the inner diameter of the housing ring 11 so that that a radial sealing gap 27 remains between the two, which separates the vane cells 24 and the flow channel 23 from the interior of the housing seals.

The pumped medium passes through the suction opening 12 in the housing 10 in the flow channel 23 and in the rotating vane cells 24 of the impeller 21. By the spirally curved or Blade webs 25 arranged obliquely to the direction of rotation, a displacement flow is generated in the semi-axial direction from the Blade cells 24 out and in, to the impeller peripheral speed slow volume flow of the flow channel into it solves. This causes the formation of a spatial circulation flow which, supported by the centrifugal force, flows into one helical or spiral-shaped stroke over the entire length of the

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Flow channel 23 flows. By means of spirally curved blade webs 25, compared to the side channel pump conventional type, a higher orbital velocity of the circulation flow achieved / which leads to more frequent re-entrances of the conveyed medium leads into the vane cells 24. This leads to a higher energy transfer from the impeller on the volume flow flowing more slowly in the flow channel 23 low energy state.

The delivery medium leaves the flow channel area on the pressure side via an outlet opening 13 in the housing 10. FIGS. 3 and 4 show a single-stage, single-flow circles Pump with rotating blade ring 22 and internal flow channel 23 is shown. In this embodiment the rotating part consists of an externally rotating impeller ring 21 with an incorporated blade ring 22. For storage of the impeller ring 21 are attached on both sides by O-rings 33 to the outside sealed bearing flanges 34, the mounted on the tubular extensions 36 of the standing part 10 with incorporated flow channel 23 and example; are sealed by radial sealing rings 37. The inlet opening 12 and the outlet opening 13 are respectively axially arranged.

It is driven, for example, by a V-belt via the V-belt pulley attached to the outside of the impeller ring 21 40. This version can for example be screwed into a pipeline or on the protruding Ends of the tubular extensions 36 are operated clamped.

The through the tubular extension 36 of the standing Part 1 ο axially sucked in pumped medium passes through the Inlet opening 41 in the flow channel 23 and in the vane cells 24 of the impeller ring 21 and is of taken this by almost one turn.

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After the energy transfer has taken place, it emerges from the flow channel through the inwardly directed outlet opening 42 23 and leaves the centrifugal pump through the outlet opening 30 of the tubular extension 36 on the side, which is opposite the suction side.

Straight, inclined to the circumferential direction of the display ledges 25 enable this centrifugal pump to be operated in both delivery directions by reversing the direction of rotation with constant funding data. FIGS. 5 to 9 show blade web shapes and conveyor cell and flow channel cross-sections in a single row arrangement. FIG. 6 shows the blade webs 25 in the development of an impeller helically curved shape.

The shown in Figure 8 / arranged obliquely to the direction of rotation, straight blade webs 25 enable the conveyance with the same conveying data in both directions.

In FIGS. 10 to 17, double-sided, i.e. two-row arrangements of blade rings 22 with spirally curved Blade bars 25 or straight, obliquely arranged blade bars 25 with and without a separating central web 43 and possible flow channels are shown.

The two emerging separately from the vane cells Circulation flows enter one another in FIGS. 10 and 13 common flow channel 23. In the arrangement of FIG. 12 there are the two flow channels 23 and blade rings 22 separated from each other, so that two different types and volumes of media can be conveyed separately.

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In Figure 18 is a single-stage, single-flow design shown in which the blade ring 22 and the flow channel 23 have a centrifugal blade part that is open at the end 46 is connected upstream. In the circumferential direction, this has a flow channel 47 with preferably in the circumferential direction increasing cross-section, corresponding to a spiral housing, which flows into the immediately following flow channel 23 flows out. This arrangement enables a higher overall efficiency, combined with a higher suction power.

In the variant of a single-stage, double-flow pump, the impeller 21 consists of two Blade rings 22 arranged at an axial distance with a closed centrifugal blade part arranged between them 53. Its blades start from an axially centered, circular suction opening 54 ″ and have one in the circumferential direction preferably spiral-shaped flow channel 55 of increasing cross-section, which in the flow direction in the two immediately adjoining radial flow channels 23 open. This arrangement makes one special high efficiency with very low holding pressure heights (NPSH value).

FIG. 20 shows a single-flow, multi-stage embodiment according to the invention with packing rings 18 on both sides shaft 19 sealed in the housing covers 15. The multi-stage impeller 21 has the shape a cylindrical roller with several blade rings opposite them are in the cylindrical, ring-shaped fixed part 10 incorporated the flow channels 23, and with an inner inlet opening 67 and an inner one Outlet opening 68 provided, which are directly connected to the outer openings for the inlet 12 and the outlet 13.

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This design could, for example, also have a single-stage, multi-stream design. Everyone would have Flow channel has its own inlet and outlet. In this arrangement the centrifugal pump would be able to handle several To convey different media in volume and type with the same delivery head at the same time.

A single-flow, multi-stage design can be seen in FIG. 21, in which the impeller 21 has a has stepped construction with a plurality of blade rings 22 of different diameter, which correspond to those Opposite flow channels 23 of different diameters incorporated in the housing 10.

This construction in a multi-stream, single-stage design each with corresponding, individual flow channels with their own inlet and outlet openings, for example convey several fluids of different volume and type at different delivery heights.

The one shown in Figure 22, vertical, single-flow, multi-stage The articulated centrifugal pump consists of individual impeller disks 21 with blades lined up on a shaft 19 wreaths 22, which are arranged opposite in the circumferential direction individual housing rings 93 with incorporated flow channels 23, which are connected to each other in the flow direction through transition channels 95 connected and by O-rings 91 from each other are sealed.

In a further preferred embodiment, the first radial channel step 96, consisting of an impeller disk 21 with blade ring 22 and housing ring 93 with flow channel 23, a closed one in the direction of flow Centrifugal blade part 46 is connected upstream in a housing 99.

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The shaft 19 is provided with parallel keys 20 for power transmission to the impeller disks 21 and in the slide bearing 101 stored in a base plate 102. The inlet opening is in the suction housing 104. Arranged on the drive side is provided with an outlet opening 13 and packing space 106 pressure housing 107. With the Housing screws 17 will hold the pressure housing 107 and the suction housing 104 against each other so that they with the between them, nested housing rings 93 form a compact pump, which at can generate the highest pressures with high efficiency.

Claims (15)

M / 22 169 Claims Peripheral channel pump with a rotating part or impeller and a fixed part or housing, a delivery channel which, starting from a suction opening, leads via at least one flow channel and blade cells of the rotating part ₃ corresponding thereto to an outlet opening, characterized in that the rotating part (21) has at least one, exclusively in the radial direction has open vane ring (22), the vane cells (24) of which by vane webs (25) facing the direction of rotation are inclined, are separated from each other, and that opposite, incorporated into the fixed part (10), at least one flow channel (23) is located, which extends from the inlet opening (12) in the direction of flow by a substantial part of the circumference to to the outlet opening (13) and that a radial gap (27) connects the flow channel (23) with the rotating Part (21) seals and that an interrupter (26) is arranged in the flow channel (23), which is also through the radial gap (27) is sealed from the rotating part (21). M / 22 169 - 2 - 2. Pump according to claim 1, characterized in that the vane cells (24) through straight, in the direction of rotation obliquely arranged blade webs (25) are separated from one another. Pump according to claim 1, characterized in that the vane cells (24) are formed by vane webs (25), which are spirally curved in the direction of rotation, are separated from each other. 4. Pump according to one of claims 1 to 3, characterized. characterized in that the vane cells (24) and / or the opposite flow channel (23) in the plane of rotation and / or have elliptical cross-sections seen perpendicular to it 5. Pump according to one of claims 1 to 3 / characterized characterized in that the vane cells (24) and / or the opposite flow channel (23) have circular cross-sections in the plane of rotation and / or perpendicular to it. Pump according to one of Claims 1 to 3, characterized characterized in that the vane cells (24) and / or the opposite flow channel (23) in the plane of rotation and / or have asymmetrical cross-sections seen perpendicular to it 7. .Pump according to one of the preceding claims, characterized in that the rotating part (21) is provided with a plurality of blade rings (22) which are separated from each other are separated. M / 22 169 - 3 - 8. Pump according to "one of claims 1 to 6, characterized in that the rotating part (21) has several blade rings (22) merging into one another having. 9 · Pump according to one of claims 7 or 8, characterized in that the blade rings (22) opposite separate flow channels (23) are assigned. 10. Pump according to one of claims 7 or 8, characterized in that opposite the blade rings (22) a common flow channel (23) is arranged. 11. Pump according to one of claims 1 to 7 or 9, characterized in that the rotating part (21) is stepped and provided with a plurality of blade rings (22), which are assigned in Opposite circumferential direction corresponding flow channels (23). 12. Pump according to one of the preceding claims, characterized in that it is assembled in a multi-stage arrangement in a link construction, wherein individual rotating parts 21 lined up on a shaft 19 and the standing parts arranged opposite them in the circumferential direction as a single housing (93) are designed with built-in flow channels (23), which can be directly or via transferring * - channels (95) are connected in the flow direction. M / 22 169 - 4 - 13. Pump according to one of the preceding claims, characterized in that the rotating part (21) has at least one blade ring (22) which is open towards the center of the axis and which surrounds at least one inside opposite arranged, flow channel (23) rotates around, whose inlet opening (12) and The outlet opening (13) are axially centered. 14. Pump according to one of claims 1 to 12, characterized in that the rotating part (21) front side, in one piece, has an open or closed centrifugal blade part (46), which is connected upstream of a radial blade ring (22) and its opposite flow channel (23) in the direction of flow. 15. Pump according to one of claims 1 to 12, characterized in that the rotating part (21) is arranged at least two at an "axial distance Has vane rings (22) with a centrifugal vane part (53) formed therebetween, which the Blade rings (22) and the oppositely assigned flow channels (23) is connected upstream in the direction of flow.