EP0595675A1 - Pumpe mit axialem Förderstrom - Google Patents

Pumpe mit axialem Förderstrom Download PDF

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Publication number
EP0595675A1
EP0595675A1 EP93402436A EP93402436A EP0595675A1 EP 0595675 A1 EP0595675 A1 EP 0595675A1 EP 93402436 A EP93402436 A EP 93402436A EP 93402436 A EP93402436 A EP 93402436A EP 0595675 A1 EP0595675 A1 EP 0595675A1
Authority
EP
European Patent Office
Prior art keywords
annular
rotor
pump
passage
axial
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP93402436A
Other languages
English (en)
French (fr)
Other versions
EP0595675B1 (de
Inventor
Xavier Pottier
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wilo Salmson France SAS
Original Assignee
Pompes Salmson SAS
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Pompes Salmson SAS filed Critical Pompes Salmson SAS
Publication of EP0595675A1 publication Critical patent/EP0595675A1/de
Application granted granted Critical
Publication of EP0595675B1 publication Critical patent/EP0595675B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
    • 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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
    • F04D29/448—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps bladed diffusers

Definitions

  • the present invention applies to a pump comprising, in a cylindrical annular pump body bore closed by a side plate: a rotor with centrifugal blades, an axial suction sleeve connected to this rotor, and an axial delivery outlet through the side plate.
  • centrifugal rotor pumps have an axial inlet which corresponds to the axial inlet of the rotor, but their delivery direction is generally either radial or tangential to the pump body.
  • the need has been expressed to produce a pump, the suction and discharge outlets of which are arranged axially with respect to the pump rotor and which are adjacent to each other.
  • These arrangements for axial start of the discharge are generally carried out by axial return of the tangential start of the annular collecting chamber of the radial flow at the outlet of the rotor.
  • the present invention proposes to produce an axial suction and axial discharge pump which uses a body of a conventional simple commercial pump closed by a side plate traversed by the suction and discharge conduits of the pump and which does not have the drawbacks of noise and fluid vibrations of the axial pumps previously produced, but which allows the realization of pumps maintaining good performance under different operating conditions, these pumps being somehow customized to their operating conditions.
  • the pump according to the invention comprises an annular collecting chamber formed in the pump body opposite the radial outlet of the rotor and which has a significant width and depth in cross section, preferably between 1/10 and 1/20 of the outer diameter of the rotor, and between the peripheral wall of the annular collecting chamber and the suction sleeve of the rotor, an annular partition is interposed which is provided at its periphery with an annular passage opening out on the lateral face of said annular chamber which is located on the side of the side plate and this annular passage is provided with fixed vanes whose general line is disposed inclined relative to the circumferential line of the annular passage, to capture the rotary component of the flow of liquid passing through said annular chamber, said annular partition delimiting, with the side plate, a delivery chamber connected on the one hand to the adite outlet of axial discharge and, on the other hand, to the annular collecting chamber via the annular passage.
  • the delivery chamber has a general form of interrupted ring extending in a plane perpendicular to the axis of the pump rotor and which is connected axially by a transverse passage formed through the side plate, to a delivery pipe with axial start.
  • the discharge chamber has, in the plane transverse to the axis of the pump rotor, the general shape of a spiral the cross section of which is of constant thickness and of increasing height in the direction of rotation of the outlet of the blades, from an end of small section close to said passage transverse to an end of large section opening onto said transverse passage.
  • the end of the spiral of small section is separated from the transverse passage by a tongue secured to the central body of the partition and which leaves from this central body towards the wall of the bore of the pump body.
  • the tongue preferably has the general shape of an arc which substantially tangents the circular periphery of the axial delivery passage formed through the side plate.
  • the fixed blades of the annular passage have, on the side of the annular collecting chamber, an inlet edge which is substantially radial and gradually flattening out to reach the delivery chamber, at an outlet edge inclined with respect to the radial direction.
  • the pump shown in FIG. 1 comprises, in a conventional manner, a rotor 1 rotating in a pump body 2.
  • the rotor 1 with centrifugal blades 3 is made of plastic and is fixed cantilevered and at the end on a shaft 4 secured to a rotor 5 of an electric motor, housed in a sealed manner with respect to the stator in a gap tube 6.
  • the carcass or the casing 7 of the motor electric is tightly fixed on the pump body 2 by isolating the stator of the motor and its winding 8 from the fluid conveyed by the pump, thanks to a front flange 9 made of sheet metal tightly connected to the air-gap tube 6 and carrying the front bearing 10 of the shaft 4, immersed in the fluid conveyed by the pump.
  • the pump body 2 has a bore 11 which forms an internal cylindrical cavity enveloping the rotor 1 and opening onto the flat front face 12 of the body 2.
  • the outlet of the bore 11 is sealed by a side plate 15, thanks at the interposition of an annular seal 13 in a groove 13a and using clamping screws 14 therefore each passes through a hole 14a of a lug 14b of the body 2 and is screwed into a threaded bore 14c of the plate 15.
  • the side plate or plate 15 carries respectively, in the center a suction pipe 16 and at its upper part (according to FIGS. 1 and 2), a discharge pipe 17.
  • the pipes 16 and 17 lead respectively to corresponding passages 16a and 17a formed through the plate 15.
  • the plate 15 can be replaced by a piece from the foundry, for example in one piece with inlet and outlet fittings, or by a drilled block.
  • annular chamber 18 which collects the flow of liquid which leaves the pump rotor 1 with components of radial speed and speed. tangential.
  • a sleeve 19 In the center of pump rotor 1, projecting outwards a sleeve 19 for entering the liquid into the rotor 1.
  • This sleeve 19 is connected to a suction sleeve 20 housed in the cavity of the bore 11 and applied in leaktight manner, by a gasket annular seal 21 housed in an annular groove 21a shown in FIG. 3, on the flat inner face 22 of the plate 15.
  • the annular collecting chamber 18 is here provided with a ring 23 which delimits the peripheral wall 23a of this chamber 18 but it is of course possible to provide, as shown in Figure 2, in place of the ring 23, a bore 23a of the pump body concentric with the inlet bore 11 and in shoulder with respect to the latter.
  • the annular collecting chamber 18, in order to fulfill its function of collecting the jets of liquid leaving the periphery of the rotor 1, must have, in cross section, a width and a significant depth or height h .
  • the width and the height h between the external periphery la of the rotor and the internal peripheral wall 23a are preferably between 1/10 and 1/20 of the external diameter of the rotor.
  • annular partition 24 which is here in one piece with the suction sleeve 20, is interposed between the peripheral wall 23a of the annular chamber 18 (materialized in fact by the inner wall of the ring 23) and the suction sleeve 20.
  • This annular partition 24 has at its periphery an annular passage 25 between on the one hand the lateral face of the annular chamber 18 which is situated on the side of the plate 15 and which in fact delimits this face, and on the other hand, a outlet 30 formed between the partition 24 and the plate 15.
  • the annular passage 25 is provided with blades or fixed fins 26 ( Figure 2) or 28 ( Figure 1).
  • the other lateral face 27 of the annular chamber 18 is constituted here by a shoulder formed at the bottom of the bore 11 or 23a (FIG. 2) of the pump body 2.
  • the blades 26 have a general line inclined with respect to the circumferential line of the annular passage 25.
  • the blades 26 have the hydraulic function of guiding the liquid threads towards the discharge chamber 30 by transforming into pressure at at least part of the rotary speed component of the flow of liquid leaving the rotor 1.
  • the blades 26 as shown in plan view in FIG. 4 have a completely radial and symmetrical shape with respect to the axis 4a of the pump rotor , with a radial inlet edge 26a and a radial outlet edge 26b.
  • the blades 28 housed in the passage 25 have, on the side of the annular collecting chamber 18, an inlet edge 28a substantially radial and their section is progressively flattened (at 28c) in the direction of the discharge chamber 30 to lead to this chamber by an edge 28b inclined relative to the radial direction.
  • the blades 26 and 28 of the passage 25 integral with a base inner ring 29 mounted on the periphery of the partition 24 and fixed, by gluing or by welding with overlapping faces 31, to the partition 24, but it is obvious that the blades 26 and 28 can come in one piece with the annular partition 24.
  • the discharge chamber 30 which is shown in front view in FIG. 3 has a general form of interrupted ring extending in a plane perpendicular to the axis 4a of the pump rotor.
  • the discharge chamber 30 in the form of an interrupted ring actually has the general shape of a spiral of decreasing cross section from the discharge passage 17a and delimited by a bottom of the spiral 32 which progressively approaches the wall of the bore. 11 without joining it, up to a tongue 33 integral with the partition body 24 and which extends in the direction of the bore 11 to come, if necessary (not shown in FIG. 3), to be applied to the wall interior of the bore 11 to form, in cooperation with this wall, the interrupted ring of the discharge chamber 30.
  • the discharge chamber 30 has the hydraulic function, not only of recovering the axial flow of liquid passing through the passage 25, but also of transforming the rotation speed components of the axial flow into pressure. guided by the blades 26 or 28, reducing this speed of rotation in a divergent.
  • the cross section of the delivery chamber 30 has a substantially constant thickness e between the side plate 15 and the wall 24a of the annular wall 24 and an increasing height from h1 to h2 from the proximity from the tongue 33 to the axial delivery passage 17a, that is to say in the direction of rotation of the pump rotor 1, corresponding to the outlet of the blades 26 or 28.
  • the tongue 33 preferably has the shape of an arc which comes to lick, or substantially tangent, the circular periphery of the axial delivery passage 17a.
  • the elements fulfilling the same functions as in the embodiment of Figure 1 are assigned the same reference marks. For reasons of clarity, only the most important of these benchmarks are indicated.
  • the blades 26 of the annular passage 25 are here arranged completely radially and the periphery of their inlet edge 26a is applied to a support shoulder 34 formed inside the bore 11 and which corresponds to the outlet of the bore 23a formed in the pump body 2 and determining the periphery of the annular collecting chamber 18.
  • the sections of suction pipe 16b and discharge pipe 17b start axially from the side plate 15 but describe a starting bend in a quarter of a circle so as to be found practically in alignment in opposite directions. Thanks to this arrangement, the pump and its sections of suction and discharge pipes can be inserted on a straight fluid pipe, by making an interruption of this straight pipe and by connecting the straight suction and discharge nozzles 16c and 17c.
  • the rotation of the rotor 1 causes the projection, by the centrifugal blades 3 of this last, of the liquid which fills the pump, towards the periphery of the outlet of the rotor, and consequently, the aspiration of the liquid to be pumped in the direction of arrow A.
  • the liquid leaving the periphery of the rotor 1 is projected in the annular collecting chamber 18 with an overpressure and respective components of radial speed and speed of rotation in the direction of rotation of the rotor 1.
  • the flow of liquid then engages between the fixed blades 26 or 28 which have a strong inclination relative to the axial direction of the rotor axis 4a.
  • the angle a between the circumferential direction and the mean line of the vane is of the order of 30 ° or less and the component of rotation of the flow is preserved by the vane 26, 28 and is decelerated gradually to be transformed into pressure in the spiral discharge chamber 30.
  • Such an arrangement of the vanes 28 is therefore capable of improving the efficiency of the transformation into pressure of the rotary speed component.
  • the blades 26 or 28 may have an angle of inclination a which varies along the blade in order to change the orientation of the component of the speed of rotation V R.
  • FIG. 5 shows an angle of inclination ⁇ 1 at the inlet 28a of the vane 28 which is greater than the angle of inclination ⁇ 2 at the outlet on the edge 28b, but it is obvious that the opposite can be done, as a function of the tangential speeds V R at the outlet of the rotor and of the section of the annular collecting chamber 18.
  • angles of inclination of blades ⁇ can be chosen as a function of the yields observed for the pump under its most common operating conditions. It is thus conceivable to have standard pumps according to the invention and in which only the crown 29 and its blades 26 or 28, is changed according to the particular operating conditions of the pump.
  • FIG. 2 uses the standard blades 26 capable of adapting to various operating conditions and, as already indicated, the suction fittings 16c and outlet 17c aligned and oriented in reverse direction allow the pump to be inserted directly onto a line of fluid propulsion.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
EP93402436A 1992-10-13 1993-10-05 Pumpe mit axialem Förderstrom Expired - Lifetime EP0595675B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9212214A FR2696793B1 (fr) 1992-10-13 1992-10-13 Pompe à refoulement axial.
FR9212214 1992-10-13

Publications (2)

Publication Number Publication Date
EP0595675A1 true EP0595675A1 (de) 1994-05-04
EP0595675B1 EP0595675B1 (de) 1997-07-30

Family

ID=9434479

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93402436A Expired - Lifetime EP0595675B1 (de) 1992-10-13 1993-10-05 Pumpe mit axialem Förderstrom

Country Status (4)

Country Link
EP (1) EP0595675B1 (de)
AT (1) ATE156245T1 (de)
DE (1) DE69312629T2 (de)
FR (1) FR2696793B1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3125278A1 (fr) 2021-07-19 2023-01-20 Gfic Propulseur vectoriel silencieux

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE455092C (de) * 1928-01-25 Samuel Maroger Kreiselpumpe, bei der die Saugwirkung durch den Unterdruck hervorgebracht wird, der sich an der Rueckseite in einer Fluessigkeit umlaufender Duesen bildet
US3499388A (en) * 1967-06-13 1970-03-10 Hale Fire Pump Co Centrifugal pump
JPS6166899A (ja) * 1984-09-10 1986-04-05 Ebara Corp 遠心圧縮機のリタ−ンチヤンネル
EP0361328A1 (de) * 1988-09-26 1990-04-04 CALPEDA S.p.A. Selbstansaugende Strahlpumpe mit axialem Diffusor
US5076758A (en) * 1990-07-18 1991-12-31 Ingersoll-Rand Company Centrifugal pumps

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE455092C (de) * 1928-01-25 Samuel Maroger Kreiselpumpe, bei der die Saugwirkung durch den Unterdruck hervorgebracht wird, der sich an der Rueckseite in einer Fluessigkeit umlaufender Duesen bildet
US3499388A (en) * 1967-06-13 1970-03-10 Hale Fire Pump Co Centrifugal pump
JPS6166899A (ja) * 1984-09-10 1986-04-05 Ebara Corp 遠心圧縮機のリタ−ンチヤンネル
EP0361328A1 (de) * 1988-09-26 1990-04-04 CALPEDA S.p.A. Selbstansaugende Strahlpumpe mit axialem Diffusor
US5076758A (en) * 1990-07-18 1991-12-31 Ingersoll-Rand Company Centrifugal pumps

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 10, no. 234 (M - 507)<2290> 14 August 1986 (1986-08-14) *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3125278A1 (fr) 2021-07-19 2023-01-20 Gfic Propulseur vectoriel silencieux

Also Published As

Publication number Publication date
EP0595675B1 (de) 1997-07-30
ATE156245T1 (de) 1997-08-15
DE69312629T2 (de) 1998-02-26
FR2696793B1 (fr) 1995-01-06
FR2696793A1 (fr) 1994-04-15
DE69312629D1 (de) 1997-09-04

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