Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D29/00—Details, component parts, or accessories
  • F04D29/18—Rotors
  • F04D29/22—Rotors specially for centrifugal pumps
  • F04D29/2261—Rotors specially for centrifugal pumps with special measures
  • F04D29/2288—Rotors specially for centrifugal pumps with special measures for comminuting, mixing or separating
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
  • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
  • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
  • F04D7/04—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous
  • F04D7/045—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being viscous or non-homogenous with means for comminuting, mixing stirring or otherwise treating

Definitions

• the present invention relates to a centrifugal pump for conveying liquids with solids and gas admixtures, in particular a Kanalradpumpe, according preamble of claim 1.
• the invention has for its object to provide a centrifugal pump, in which the ability to transport gas accumulations, is significantly improved.
• a free-flow pump comprises an impeller chamber in which an impeller is arranged, and a vortex chamber extending in front of the impeller chamber, which is provided by blades - Q -
• the per se known centrifugal pump in particular Kanalradpumpe, comprises, as is apparent from the preamble of claim 1, an impeller chamber in which an impeller is arranged, however, unlike free-flow pumps on no vortex chamber. ⁇
• the interior of the correspondingly redesigned housing of the inventive centrifugal pump now consists of a front and one of them separated by a virtual plane rear room part.
• the front part of the blade (s) extends while the impeller plate and the rear part of the blade (s) connected thereto are accommodated in the rear space part.
• FIG. 1 shows a section of a first embodiment of the channel wheel or centrifugal pump according to the invention
• FIG. 3 is a perspective view of a possible variant of an impeller with three auxiliary blades provided for the second embodiment
• FIG. 4 is a section of a third embodiment of the pump.
• the impeller 10 is mounted on a shaft 60 driven by a motor, not shown.
• the housing 1, the impeller 10 and the shaft 60 have a common axis of symmetry IA.
• the inner space 6 of the housing 1 consists of a front chamber part 5A encompassing an annular space or spiral collecting chamber 4 and a rear room part 5B separated from it by a virtual plane ⁇ T ⁇ .
• This plane ⁇ T ⁇ coat approximately with the (no reference drawing provided) level together, which includes the rear (also without. Reference numeral provided) surface line of the opening 3 and is orthogonal to the axis of symmetry IA.
• the impeller 10 comprises a number of preferably curved blades 15 carrying a number of preferably curved blades 15, having a front 12 and a rear surface 13, corresponding to the size of the solids. As a rule, as stated above, there are one to three blades (see also FIGS.
• the front part 15F and the rear part 15R of the blade (s) 15 extend in the front 5A respectively.
• the front edge 16 of the blade 15 may be in the immediate vicinity of the inner surface 7 of extending around the entrance
• Housing wall part 7A pass by. Thanks to this proximity, a certain degree of sealing is achieved, since the distance between said surface and said leading edge is on the order of tenths of a millimeter and in the Usually rather less than 0.5 mm.
• the peripheral edge 17 of the front part 15F of the blades 15 can move close to the liquid outlet 3.
• a defined depending on the design of the pump, rotationally symmetrical housing surface 8, 8A of the housing 1 preferably encloses narrow (that is of the order of a few millimeters) the impeller 11, that is its peripheral surface 14 and the example according to flush peripheral edges 17 of the blades 15 and the rear part 15R of these blades. According to the embodiment shown in FIG.
• the impeller plate is arranged such that its front surface is at least approximately in the virtual plane ⁇ T ⁇ , while the blades extend entirely in the impeller chamber located in front of this level ⁇ T ⁇ .
• Impeller chamber part 5B with the distance D corresponding volume is increased.
• the experiments have shown that the distance D in a range of 25% to 75% of Total width of the blades should be 15, preferably at about 50% of the total width.
• the rear surface 13 of the impeller plate 11 may be located in the immediate vicinity of the surface 9 of the rear wall 9A of the housing 1. According to a variant, however, a greater distance can be provided between the surfaces 13, 9 in order to leave room for ribs 18 (on the surface 13) or 19 (on the surface 9) attached to the one and / or other of these surfaces.
• the ribs 18 known per se may be curved radially or, for example, in a manner similar to the blades 15 (see FIG. 3, reference numeral 23).
• the ribs 19 which are not known, however, preferably run radially and fulfill the function of a swirl brake, avoiding one
• FIG. 2 shows a second embodiment which, in comparison to the first or the first embodiment described above
• the impeller plate 21 is provided with a blade system 25.
• This blade system consists on the one hand of at least one blade 25L which is identical or at least similar to the blade 15 and whose front edge 26A can move in the immediate vicinity of the inner surface 7 of the front wall part 7A of the housing 1 and additionally on the other hand consists of at least one narrower, preferably curved auxiliary blade 25S extending at least partially in the rear impeller chamber 5B.
• This means that the leading edge 26B of this auxiliary blade 25S is in the virtual plane ⁇ T ⁇ or in close proximity to that plane ⁇ T ⁇ Area can lie.
• the latter may be flat and parallel or oblique to the plane ⁇ T ⁇ or curved.
• edges 26B may be orthogonal to the axis of symmetry IA or may have a different course, for example outwardly or inwardly (for illustrative purposes, the dotted line 26C indicates a possible taper in the leading edge of the auxiliary blade 25S).
• the distance D between the front surface 22 of the impeller plate 21 and the front edge 26B corresponding to the width (or average width (detected at about half the radius of the impeller blade)) of the auxiliary blade 25S is to be in a range of 25% to 75% of the total width B g of the wide blades 25L, preferably at about 50% of the stated overall width, so that the blades 25S extend substantially only in the rear impeller chamber 5B.
• the impeller 20 of this second embodiment may comprise three wide blades 25L and three narrower auxiliary blades 25S, with one auxiliary blade 25S each being disposed between two blades 25L.
• the rear surface 23 of the impeller plate 21 may be in the immediate vicinity of the surface 9 of the rear wall 9A of the housing 1 or according to a variant between these surfaces 23, 9 a greater distance can be provided in order to leave enough space for the attachment of preferably radially extending ribs 28 (on the surface 23) and ribs 29 (on the surface 9) on one and / or other of these surfaces.
• an impeller 30 connected to the shaft 60 is enclosed by an axis 100A of a housing 100 having a liquid inlet 102 and exit 103.
• the housing 100 is similar to the housing 1 and has a front chamber 105A surrounded by a collection chamber 104 similar to the collection chamber 4 and a rear chamber 105B separated by the virtual plane ⁇ T ⁇ .
• the impeller 30 offset rearwardly by the distance D comprises a vane system 35 connected to an impeller blade 31, which consists of at least one wide vane 35L and at least one small auxiliary vane 35S, preferably three each, as mentioned in the second embodiment.
• Auxiliary blades 35S may be shaped similar to the auxiliary blades 25S, with only a leading edge 36B shown here.
• the auxiliary blades 35S and the impeller plate 31 are surrounded by an outer ring 34.
• the inner surface 34B of the ring 34 can be made conical with a cone angle of 2 ⁇ (with ⁇ preferably ⁇ 20 °).
• the impeller plate 31, the ring 34 and the associated Auxiliary vanes 35S extend in the impeller chamber 105B.
• the peripheral edges 37L which can be moved past in relative proximity to the liquid outlet 103 may run parallel or obliquely to the axis of symmetry 10OA or else be designed differently.
• the front edges 36A of the wide blades 35L are covered by a cover plate 40.
• the latter is in a pressed in a sealing gap 111, ring 110 in the vicinity of the - ⁇ stored input 102 of the housing 100 rotatably.
• the front surface 41 of the cover plate 40 can move in the immediate vicinity of the surface 107 of the wall portion 107A.
• This cover disk which is known per se, is often provided for stability reasons or for pumps with a low specific speed n q .
• the rear surface 33 of the impeller disc 31 may be in the immediate vicinity of the surface 109 of the rear wall 109A of the housing 100, or according to a variant between these surfaces 33, 109 a greater distance may be provided to allow for sufficient space for attaching preferably radially extending ribs 38 (on surface 33) and ribs 39 (on surface 109) on one and / or other of these surfaces.
• the impeller 31 may be provided with at least one hole 45.
• three or six holes 45 with axis 45A are distributed between the blades 35L and the auxiliary blades 35S and dimensioned accordingly.
• the axes 45A extend at a distance R parallel to the axis 100A.
• the dimension of the radius R is preferably selected to be approximately in an interval between one half and two thirds of the peripheral radius of the Impeller plate is located. It has been found that these holes 45 markedly improve the efficiency of escape of the gas to the outside.
• Embodiments are realized in which features of the described embodiments are combined with each other.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Structures Of Non-Positive Displacement Pumps (AREA)
• Iron Core Of Rotating Electric Machines (AREA)
• Reciprocating Pumps (AREA)
• Lubrication Of Internal Combustion Engines (AREA)

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• 2005
  • 2005-06-16 DE DE502005006506T patent/DE502005006506D1/de active Active
  • 2005-06-16 ES ES05750409T patent/ES2318497T3/es active Active
  • 2005-06-16 BR BRPI0520297-3A patent/BRPI0520297B1/pt not_active IP Right Cessation
  • 2005-06-16 JP JP2008516097A patent/JP5384103B2/ja active Active
  • 2005-06-16 AT AT05750409T patent/ATE421043T1/de active
  • 2005-06-16 EP EP05750409A patent/EP1891334B9/fr active Active
  • 2005-06-16 PL PL05750409T patent/PL1891334T3/pl unknown
  • 2005-06-16 WO PCT/CH2005/000337 patent/WO2006133577A1/fr active Application Filing
  • 2005-06-16 CA CA2611141A patent/CA2611141C/fr active Active
  • 2005-06-16 DK DK05750409T patent/DK1891334T3/da active
  • 2005-06-16 CN CN2005800501150A patent/CN101208521B/zh active Active
  • 2005-06-16 US US11/917,440 patent/US8025478B2/en not_active Expired - Fee Related

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