EP3467319A1 - Pompe centrifuge à joint d'étanchéité pour bride d'aspiration amélioré - Google Patents

Pompe centrifuge à joint d'étanchéité pour bride d'aspiration amélioré Download PDF

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Publication number
EP3467319A1
EP3467319A1 EP18000558.9A EP18000558A EP3467319A1 EP 3467319 A1 EP3467319 A1 EP 3467319A1 EP 18000558 A EP18000558 A EP 18000558A EP 3467319 A1 EP3467319 A1 EP 3467319A1
Authority
EP
European Patent Office
Prior art keywords
ring
centrifugal pump
pump
circular
wear ring
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
EP18000558.9A
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German (de)
English (en)
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EP3467319B1 (fr
Inventor
Roland Stracke
Günter Strelow
Joern Jacobsen
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 SE
Original Assignee
Wilo SE
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Publication date
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Priority to EP18000558.9A priority Critical patent/EP3467319B1/fr
Publication of EP3467319A1 publication Critical patent/EP3467319A1/fr
Priority to CN201920944830.8U priority patent/CN211314647U/zh
Application granted granted Critical
Publication of EP3467319B1 publication Critical patent/EP3467319B1/fr
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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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
    • F04D29/167—Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal flow wheel
    • 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
    • F04D29/426—Casings; Connections of working fluid for radial or helico-centrifugal pumps 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
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/622—Adjusting the clearances between rotary and stationary parts

Definitions

  • the invention relates to the technical field of centrifugal pumps, in particular so-called split-case pumps with a two-part housing.
  • the invention relates to a centrifugal pump having a pump housing and at least one impeller disposed therein for conveying a liquid from the suction side to the pressure side of the pump unit, the impeller having a suction neck which is sealed radially to the pump housing by a wear ring.
  • the invention relates to a centrifugal pump unit with a centrifugal pump according to the invention.
  • the impeller separates the interior of the pump housing in a suction side and a pressure side, wherein the impeller sucks the liquid to be pumped by the suction neck annularly surrounded suction mouth on the suction side, accelerated tangentially and ejects quasi radial to the pressure side.
  • This type of pump is therefore also called centrifugal pump and the impeller referred to as a radial impeller.
  • the impeller is sealed to the pump housing. This can basically be done axially or radially.
  • the axial seal In the case of the axial seal, a gasket rests against the axial outer edge of the suction neck. Due to the axial forces acting on the pump shaft to the intake side during operation, due to hydraulic pressure surges in the pipeline system connected to the pump and / or due to the mechanical drive of the centrifugal pump, the axial seal usually also acts as an axial bearing and is accordingly subject to high wear , That is why usually a radial Sealing of the suction neck preferred in which a suction ring sealingly bears radially on the outer circumference of the suction neck.
  • the quality of the seal between the pressure side and the suction side of the centrifugal pump also has a major influence on the hydraulic efficiency. To keep the losses low, it is necessary to make the gap between the impeller and pump housing as small as possible. Since the hydraulic forces can lead to a bending of the shaft and thus to a gap reduction, appropriate reserves must be taken into account in the dimensioning. Frequently used as suction rings so-called wear rings (English “wear ring”) are used, in which the gap is made smaller and a contact of the impeller and wear ring is deliberately accepted in a bending of the shaft. The operating gap ideally drags in after a certain time. In order to avoid blocking, a production-related minimum gap is also required here. However, this places high demands on the accuracy of the components during production and assembly.
  • the maintenance or replacement of the wear ring is associated with considerable labor and time and usually leads to a longer standstill of the centrifugal pump, usually of at least one or two days. It is first necessary to decouple the electric drive from the pump. For disassembly, the pumped liquid must also be removed from the pump housing be drained. Then the pump housing must be dismantled and the upper housing part lifted by crane. Thereafter, the pump shaft and impeller must be removed, so that the wear ring is accessible.
  • a centrifugal pump unit comprising a pump housing and at least one impeller arranged therein for conveying a liquid which has a suction neck, which is sealed radially to the pump housing by a slotted wear ring, wherein the pump housing has an adjusting unit, by means of which the diameter of the wear ring adjustable is.
  • the core of the invention is thus to provide a retractable and adjustable suction neck seal. Due to the adjustability or adjustability, the radial seal of the suction neck on the one hand after assembly of the pump can be set to a minimum gap, on the other hand readjust to a minimum gap during maintenance or service. As a result, significantly lower gap losses and thereby in turn a higher efficiency can be achieved. An exchange of the wear ring is no longer required by the adjustability.
  • the term “adjust” is used both for the initial setting after the pump has been assembled and for the “readjustment” after a corresponding number of operating hours.
  • the seal setting can be performed during pump operation. Disassembly or removal of the centrifugal pump from the connected hydraulic systems is not required for the adjustment. Thus, the maintenance costs are significantly reduced and downtime largely avoided, at least minimized.
  • a slotted wear ring is a ring which is interrupted at least at one point of its circumference by a slot, so that there opposite two circumferential ends of the wear ring spaced. This distance makes it possible to change the inner diameter of the wear ring, which is effected according to the invention by the adjustment. By reducing the diameter, the circumferential ends move to each other, so that the slot is smaller.
  • the wear ring has only one slot, so it is integrally formed, which facilitates handling when assembling the Saughalsdichtung and simplifies the overall design, since only one point of the wear ring a measure to prevent flow through the slot is required, as later is deepened.
  • the wear ring thus has approximately a C-shape in this one-piece embodiment variant.
  • the slot is significantly smaller compared to the circumference than a typical C-shape.
  • the slot may have a circumferential width between 0.5% and 3% of the circumference.
  • the wear ring can also be slit several times. This means that it consists of two or more ring segments, between the circumferential ends of each then a slot-forming distance is formed.
  • the sum of the slots in this embodiment may have a circumferential width between 0.5% and 3% of the circumference. It makes sense that the slots are the same size, so that with a number n of slots, each slot has a width in the circumferential direction between 0.5 / n% and 3 / n% of the circumference.
  • the adjusting unit is adapted to exert a radially inwardly directed force on the outer circumference of the wear ring.
  • This causes a radial compression of the wear ring with appropriate adaptation of Schlauerringinnen penmessers to the outer diameter of the suction neck of the impeller.
  • the sealing gap between the wear ring and the suction neck can thus be reduced to a minimum, theoretically even down to 0 mm.
  • the wear ring may for example consist of metal such as gunmetal, gray cast iron or stainless steel, but alternatively also of plastic such as PTFE.
  • the adjusting unit has an outer ring and an inner ring, between which a circular wedge connection, wherein the outer ring is angularly adjustable relative to the inner ring in the circumferential direction, the diameter of the inner ring is reducible and the wear ring on the radially inner side of the inner ring is applied.
  • the outer ring forms an outer part of the circular wedge connection
  • the inner ring forms an inner part of the circular wedge connection.
  • the inner circumference of the outer ring in this case carries a circular spline, the outer circumference of the inner ring a complementary circular spline.
  • a characteristic inherent in a circular spline connection is that the two rings are pressed against each other by their rotation relative to one another.
  • the forces in the circular spline connection act radially on the connection partners.
  • the outer ring exerts on the inner ring a radially inwardly directed force. This causes a reduction of the inner diameter of the inner ring, which in turn passes this to the wear ring, so that its inner diameter is also smaller and the sealing gap is reduced.
  • This has the advantage that a significantly more precise adjustment of the gap over the entire circumference is achieved and the readjustment of the sealing gap is particularly simple.
  • the outer ring is integrally formed.
  • a torque acting on a circumferential point acts on the entire ring in order to turn it.
  • This has the advantage over a multi-part design of the outer ring that the force and rotational movement does not have to be transmitted to the parts of the outer ring via appropriate means.
  • the structural design of the adjustment is particularly simple.
  • the integrally formed outer ring then has along its inner circumference said circular wedge profile in the form of at least one circular wedge. The inner circumference can thus carry a single, two or more circular wedges.
  • the inner ring can be made of a compressible material, for example of an elastomer.
  • a compressible material for example of an elastomer.
  • it is elastic and gives way as a result of a radially inward force.
  • the elasticity of long duration must be, in particular, should last several years, so that appropriate requirements are to be placed on the material.
  • the inner ring of a dimensionally stable material, in particular made of metal or plastic.
  • it in order to facilitate the reduction of the diameter, it must be provided here to slit the inner ring, so that there is a gap along the circumference between two corresponding circumferential ends. By reducing the diameter of these circumferential ends then move to each other and reduce the gap.
  • slot and slot are synonymous technically equivalent, but in the context of the invention, the term "gap" with respect to the inner ring and the term “slot” is used in relation to the wear ring.
  • the inner ring may be formed of only one circular segment. He is thus one-piece and thus has only a gap along its circumference. Its shape is essentially C-shaped.
  • the inner ring may be formed of only one circular segment. He is thus one-piece and thus has only a gap along its circumference. Its shape is essentially C-shaped.
  • the outer circumference of the circle segment is correspondingly formed at least one circular wedge complementary to the outer ring to cooperate with the at least one circular wedge of the outer ring.
  • a single complementary circular wedge may be formed along the outer circumference of the circle segment forming the inner ring.
  • two or more circular wedges may be present along the outer circumference of the one circular segment forming the inner ring.
  • the inner ring may be formed according to another embodiment of an annular arrangement of two or more circle segments. It is thus multi-part and suitably has along its circumference in each case a gap between two adjacent circle segments. Along the outer circumference of the circle segments is correspondingly formed at least one circular wedge complementary to the outer ring in order to connect to the at least one circular wedge of outer ring to cooperate. Thus, in a sub-variant, a single complementary circular wedge can be formed along the outer circumference of all circular segments forming the inner ring. The circular segments are thus also segments of a complementary circular wedge and together form this one complementary circular wedge. In another sub-variant, two or more complementary circular wedges are present along the outer circumference of all the circle segments forming the inner ring.
  • the number of circular segments of the inner ring is equal to the number of circular wedges of the outer ring or equal to the number of complementary circular wedges.
  • the distribution of the complementary circular wedges can preferably take place such that each circular segment on its back, i. carries on its radial outer side exactly one complete complementary circular wedge of the circular wedge connection. This simplifies the production of the circle segments, since the jump in height from one circular wedge to the next is not within a circle segment.
  • three circular wedges are formed along the inner circumference of the outer ring and the inner ring is formed from an annular arrangement of three circular wedge segments whose respective outer circumference in each case forms a complete complementary circular wedge to the circular wedges of the outer ring.
  • the inner ring can be dimensionally stable both in a one-part and in the segmented, multi-part embodiment variant, in particular made of metal or plastic, but alternatively can also be elastic, in particular made of an elastomer.
  • the circular segments of the inner ring are held radially displaceable. This simplifies assembly and ensures a defined movement. In addition, it is prevented by the holder that the inner ring rotates away in the circumferential direction and thus tightens or loosens the circular wedge connection. This could happen if the impeller starts at the wear ring punctually and this entrains due to the forces acting, which in turn would entrain the inner ring.
  • the circle segments are in particular stationary relative to the pump housing, so that the inner ring does not rotate when the outer ring is pivoted.
  • a minimum adjustment angle is required on the outer ring.
  • the outer ring can pivotably engage in an L-shaped support ring fastened to the pump housing.
  • This support ring thus engages around the outer ring on the outer peripheral side and on an axial end face and holds it in position.
  • the outer ring is thus also pivotable relative to the support ring and slides in this.
  • the support ring may have axially projecting guide pins which engage in corresponding recesses in the circular segments.
  • the recesses may for example be grooves or slots.
  • the grooves or slots may extend substantially radially or along a secant so that the entire segment can move radially.
  • the guide pins are distributed equidistantly along the circumference.
  • the guide pins can be formed for example by cylindrical pins.
  • the guide pins are screwed to the support ring. Alternatively, they can be welded, soldered, pressed or glued to it.
  • the present in Schl concerningring slot can basically have any shape. Its manufacture is particularly simple when the end edges of the circumferential ends are formed at right angles to the circumferential direction such that the slot extends purely axially between the circumferential ends. It thus has an I-shape and a minimum longitudinal extent. Alternatively, the longitudinal extent of the slot at an angle not equal to 90 degrees to the circumferential direction. Further, the circumferential ends may also be formed to provide other slot shapes, such as a V-shaped, U-shaped, Z-shaped, labyrinthine or meandering slot. It should be noted that the more complex the slot is designed, the better it seals off.
  • the slit forms, as it were, a bypass between the suction side and the pressure side of the impeller, part of the pumped liquid can flow through the slit from the pressure side on the impeller to the suction side.
  • a blocking means in the slot i. in particular sealingly rests between the circumferential ends of the wear ring.
  • the blocking means may be an elastic sealing element. This would then be compressed due to the reduction in the diameter of the wear ring, so that the slot is always tight.
  • the blocking means is a wing nut whose diametrically opposed wings in the intended mounted state extend into elongate recesses in the circumferential ends.
  • the recesses simultaneously forms guides in the circumferential movement of the circumferential ends and hold them in position via the positive connection with the thumbscrew.
  • the locking means in particular the thumbscrew, in a bore of one of the circular segments inlaid, in particular screwed.
  • the circular segments are identical. In this case, it is not necessary to distinguish between different types of circular segments when assembling the adjusting unit, in particular not between those having a bore for the locking means and those having no such hole to have. Thus, all circular segments have a corresponding hole for the locking means, however, only one of these holes is used in a simply slotted wear ring, the other holes are unused. In the case of a two or three slotted Schl constitutionrings, however, the other holes for a second and third locking means can be used, which then rests in accordance with the corresponding second and third slot.
  • the centrifugal pump comprises an actuator for pivoting the outer ring relative to the inner ring.
  • This is ideally accessible from outside the pump housing, possibly with an appropriate tool, so that no costly disassembly of pump components is required.
  • the actuating device may comprise a pin projecting radially from the outer ring and a screw inserted in the pump housing in a preferably tangential threaded bore which is operatively connected to the pin in such a way that the screwing depth of the screw determines the angular position of the pin.
  • the screw can be rotatably accessible from outside the pump housing.
  • the operation of this actuator is such that the screw, which may be a grub screw, for example, with increasing depth of engagement, the pin increasingly backwards (from the perspective of the screw), thereby changing the angular position and pivots the outer ring. This means that, in the initial state, the outer ring or pin is in an initial pivotal position from which it will move away as the screw is driven deeper into the threaded hole.
  • the actuating device may comprise a gear or worm wheel section, which is preferably arranged on the outer circumference of the outer ring or forms part of its outer circumference, and a helical worm engaging in the gear or worm wheel section.
  • the worm can be rotatably accessible from outside the pump housing.
  • the operation of this actuator is similar to the former. Instead of the screw but here the worm is rotated, the rotation, as in a Worm gear common, causing a shift of the gear or Schneckenradabitess along the extension of the worm, which changes the angular position of the outer ring.
  • the outer ring or pin is in the initial state in an initial pivotal position, from which it moves away when the worm is rotated.
  • the wear ring together with the adjustment unit or at least parts thereof, in particular together with the inner ring, the outer ring, the support ring and the pin or gear or Schneckenradabites form a preassembled, in particular interchangeable assembly, hereinafter called Saughalsdichtungsbautechnik, so that the assembly of the centrifugal pump and an exchange of the wear ring in case of service can be done easily and quickly.
  • An efficiency reduction of the centrifugal pump can be present not only by a worn wear ring, but also by an impeller damaged due to cavitation. In the latter case, of course, an adjustment of the sealing gap between the impeller and wear ring nothing, so that replacement of the impeller is required.
  • the pump housing a closable opening into the suction chamber in front of the impeller inspection opening for carrying out a flexible endoscope for the purpose of inspection of the gap between the wear ring and Impeller has. If this gap is correct, the assumption of a damaged impeller is close. Furthermore, the endoscope can help to achieve a precise adjustment of the sealing gap.
  • the centrifugal pump may have a second impeller, which has a further suction neck.
  • the impeller may be double-flow and have a further suction neck opposite the suction neck.
  • the additional suction neck can also be sealed radially to the pump housing by a corresponding second slotted wear ring, and the pump housing have a corresponding second adjustment unit, by means of which the diameter of the second wear ring is switched on or readjusted.
  • the second wear ring and / or the second adjustment unit can / may have the same features, properties and advantages as previously described with respect to the first wear ring or with respect to the first adjustment unit.
  • the invention is preferably used in so-called split-case pumps.
  • the pump housing can be divided axially, in particular consist of an upper housing part and a lower housing part, preferably such that the axis of rotation of the pump shaft is within the parting plane between the two housing parts.
  • the invention also relates to a centrifugal pump unit comprising a centrifugal pump according to the invention and an electromotive drive unit for driving the centrifugal pump unit.
  • the drive shaft of the drive unit is mechanically coupled to the pump shaft and drives the impeller mounted on the shaft.
  • Fig. 1 shows a centrifugal pump 50 for conveying a liquid in the design of a so-called split-case pump with a horizontally along the axis of rotation 18 in an upper housing part 1a and a lower housing part 1b divided pump housing 1 spiral design.
  • the housing parts 1a, 1b border in the parting plane 9 (see Fig. 2 ) to each other.
  • an impeller 2 is arranged rotatably on a pump shaft 4 by means of a shaft sleeve 46 with annular groove 47 (see FIG. 2 ) is mounted.
  • the pump shaft 4 is driven by an electric motor drive unit, not shown, with a clutch or a transmission between the pump shaft 4 and drive shaft is to allow a separate installation and assembly of the two devices.
  • Centrifugal pump 50 and drive unit together form a centrifugal pump unit.
  • the housing parts 1a, 1b have an enormous weight, in total up to a ton, so that a mounting and dismounting of the centrifugal pump 50 must be done with a crane.
  • the impeller 2 separates the interior of the pump housing 1 into a suction side 5, from which the impeller 2 sucks the liquid to be pumped, and a pressure side 7, which adjoins a spiral chamber 3 located radially outside the pump impeller 1.
  • the pump housing 1 forms a spiral housing 3a.
  • the impeller 2 accelerates the liquid and ejects it tangentially, wherein the spiral chamber 3 directs the liquid to the pressure side 7.
  • the impeller 2 is double-flow in this embodiment. This means that it is constructed essentially mirror-symmetrically and has two suction nozzles 5 opposite one another, through which the impeller 2 sucks the liquid. Due to the symmetry of the impeller 2 and the pump housing 1 is based on the symmetry plane of the impeller 2 constructed substantially symmetrically. Compared to conventional wheels radial design, the impeller blades 12 extend here in the axial direction to both sides to the respective suction mouth 5 out.
  • the double-flow impeller 2 of the embodiment variant described here lacks a support disk on which the blades are usually arranged in single-flow impellers.
  • the blades 12 are each covered on both sides by a cover plate 10, which, starting from its substantially radial extension at the outer edge in the form of a radial disc with increasing proximity to the pump shaft 4, viewed in cross section arcuate, in an axial extension in the form of a cylindrical Rings passes, which is concentric with the axis of rotation 18 and the suction mouth 5 of the impeller 2 limited.
  • This cylindrical ring of the cover plate 10 forms the suction neck 10a of the impeller 2 and may have a diameter up to 500mm.
  • the suction neck 10a must be at its radial Outer sealed to the pump housing 1 back to prevent backflow (bypass) of liquid from the pressure side 3, 7 to the suction side 5 of the impeller. Because this deteriorates the efficiency of the centrifugal pump 50 and affects the pump characteristic.
  • a wear ring 14 is present, which rests with its inner circumference 14a on the outside of the suction neck 10a, wherein a sealing gap between the suction neck 10a and wear ring 14 is given.
  • the wear ring 14 is made of metal such as gunmetal, gray cast iron or stainless steel, or made of plastic, for example PTFE.
  • the sealing gap Due to component and assembly tolerances of the sealing gap can not be precisely adjusted and is usually not constant over the circumference, which is for example due to a deflection of the shaft 4. In practice, it may therefore be found that the wear ring 14 partially rests on the suction mouth 10a and grinding in after commissioning. In addition, the sealing gap increases in operation due to wear and the efficiency decreases, so that a maintenance of the centrifugal pump 50 is required.
  • the centrifugal pump 50 comprises an adjusting unit 20, 21, 29, which allows precise adjustment of the sealing gap after assembly of the centrifugal pump 50, but also an adjustment of the sealing gap after many hours of operation, for example, in the context of proper maintenance or extraordinary service.
  • setting is inventively achieved in that the inner diameter of the wear ring 14 is changeable.
  • the wear ring 14 is slotted, and the adjusting unit 15, 21, 29 arranged to adjust the diameter of the wear ring 14.
  • an adjustable and adjustable suction neck seal is formed.
  • the wear ring 14 used here is simply slotted, it is thus one-piece and has a substantially C-shape. That is, the slot is interrupted at only one point of its circumference by a slot 24 so that there are two The circumferential ends 27a, 27b of the wear ring 24 are spaced from each other, see Fig. 4 , This distance makes it possible to change the inner diameter of the wear ring 14 to a certain extent, which is effected according to the invention by the adjustment unit 20, 21, 29.
  • the slot may have a width in the circumferential direction between 0.5% and 3% of the circumference, for example 12.5 mm. By reducing the diameter, the circumferential ends 27a, 27b move to each other, so that the slot 24 is correspondingly smaller.
  • the adjusting unit 15, 21, 29 is arranged here to exert a radially inwardly directed force on the outer circumference of the wear ring 14, which causes a radial compression of the wear ring 14 uniformly over the circumference and to a corresponding reduction of Schlchelringinnen penmessers, for example, depending on the size of the Wear ring leads up to 4mm.
  • the adjusting unit 15, 21, 29 is in the Figures 2 and 3 clearly visible, which represent a radial section through the suction neck 10a in the region of the Saughalsdichtung.
  • the adjusting unit 15, 21, 29 here essentially comprises an outer ring 21, an inner ring 15 and an actuating device 29. Between the outer ring 21 and the inner ring 15 there is a circular wedge connection, and the outer ring 21 is relative to the inner ring 15th angularly adjustable in the circumferential direction, which can be effected by the actuator 29.
  • the outer and inner rings 21, 15 are, independently of each other, made of metal, in particular stainless steel, or of plastic, e.g. PTFE, manufactured, and here in any case dimensionally stable.
  • the facing surfaces of the outer and inner rings 21, 15 are at least smoothed or have even lower surface roughness to minimize the friction between the circular wedges during pivoting of the outer ring 21.
  • the inner circumference 21a of the outer ring 21 carries a circular spline in the form of three circular wedges.
  • the individual circular wedges are clearly recognizable at their step-like transitions, since the radial thickness of the outer ring 21 increases in the circumferential direction along a circular wedge to a maximum and springs back stepwise to a minimum radial thickness at the beginning of the next circular wedge.
  • the outer ring 21 is in one piece and thus virtually forms a circular wedge ring.
  • the outer circumference 15a of the inner ring 15 carries a complementary circular wedge profile in the form of three complementary circular wedges.
  • the inner ring 15 is here in several parts, i. segmented, more precisely formed by three independent circular segments 15 which are arranged in a ring.
  • the three complementary circular wedges are distributed on the circular segments 15 such that each circular segment 15 has a complete complementary circular wedge on its outer periphery 15a.
  • the radial thickness of the circular segments 15 increases relative to the outer ring 21 in the opposite circumferential direction in each case.
  • the inner periphery 15b of the inner ring 15 is cylindrical.
  • the wear ring 14 abuts on it.
  • Both the circular wedges of the outer ring 21 and the circular wedges of the inner ring 15 have the shape of a logarithmic spiral, so that a centering effect on the wear ring 14 is achieved.
  • the circular segments 15 are spaced apart to form a gap 19 to allow a radial movement and thus a reduction of the inner diameter.
  • the inner circumference 21a of the inner ring 21 slides with the thinner end of the circular wedges ahead along the outer periphery 15a of the circumferentially fixed inner ring 15. Based on a fixed circumferential point thereby increases the radial thickness of the outer ring 21 and therefore also both rings 15, 21, whereby the outer ring 21 exerts a radial force on the inner ring 15. As a result, the circular segments 15 deviate with a radial movement, resulting in a reduction of the inner diameter of the inner ring 15, which in turn passes this on to the wear ring 14, so that its inner diameter is also smaller. This allows the adjustment of the sealing gap.
  • the gaps 19 become narrower.
  • substantially radially extending slots 17 are provided in the circular segments 15, in which eino cylindrical guide pins 18. Instead of slots can also be provided grooves.
  • Each circle segment 15 has a single such elongated hole 17, wherein the slots are arranged distributed equidistant.
  • the elongated holes 17 are formed in the portion of the circle segments 15 which has the largest radial thickness. The elongated holes 17 have a length such that a radial movement of the circular segments 15 to 2mm is possible.
  • the guide pins 18 are attached to a support ring 20, in particular bolted to this, welded, soldered, pressed or glued. They extend substantially axially away from the support ring 20.
  • the support ring 20 is here L-shaped formed from sheet metal and thus comprises an axial, disk-shaped portion 20 a and a cylindrical portion 20 b, as shown in Fig. 5 can be seen, which is an axial sectional view of the Saughalsdichtungsbautechnik 45 according to section line EE in Fig. 3 With regard to the inner circumference 14a of the wear ring 14 forms.
  • the support ring 20 surrounds the outer ring 21 on the outer circumference, which rests correspondingly slidably in the support ring 20.
  • the outer ring 21 is thus also pivotable relative to the support ring 20, but fixed in its movement in the axial direction.
  • the hole-disc-shaped portion 20a which covers the outer ring 21 at an axial end face and on its outer ring 21 directed to the axial inside the guide pins 18 carries.
  • a press ring 48 which is pressed into a radial recess in the cylindrical portion 20 b.
  • This radial recess is characterized by a smaller radial thickness of the cylindrical portion 20b of the support ring 20 at an axial end, on which the support ring 20 thus surrounds the press ring 48 on the outside circumference.
  • the support ring 20 is held on the pump housing via a positive connection with locking pins 23, which are part of a mounting bracket 22, in particular at its circumferential ends.
  • the bracket 22 is semicircular and lies on the outside of the support ring 20, see Fig. 2 , It is firmly connected to the pump housing 1 and to the lower housing part 1b.
  • the present in the wear ring 14 slot 24 has an I-shape in the embodiment shown here, as in Fig. 4 can be seen, which is a view from direction X according to Fig. 3 on the inner circumference of the wear ring 14 shows.
  • the slot 24 extends at right angles to the circumferential direction, axially parallel to the axis of rotation 18.
  • the end edges of the circumferential ends 27a, 27b are parallel to each other at right angles to the circumferential direction.
  • the outer ring 21 is behind the wear ring 14 something out. He thus has a greater axial length.
  • the inner ring 15 has an identical axial length as the wear ring 14 and is visible through the slot 24.
  • a blocking means 25 is arranged in the slot 24.
  • the locking means 25 is formed here by a wing nut with two diametrically extending away from a shaft 28 wings.
  • an elongated, circumferentially extending and open to the respective end edge recess 26a, 26b is provided, in each of which a wing of the wing nut 25 extends positively into it.
  • the recesses 26a, 26b serve as a guide and prevent axial displacement of the circumferential ends 27a, 27b.
  • the length of the recesses 26a, 26b is equal to or greater than the length of a wing.
  • the thumbscrew 25 is screwed with its shaft 28, which has a corresponding external thread, in a bore 16 with a corresponding internal thread in one of the circular segments.
  • the wear ring 14 is firmly connected via the thumbscrew 25 with the inner ring 15.
  • the overall arrangement of adjusting unit 15, 21, 29 and wear ring 14 is thus secured against rotation in the circumferential direction.
  • Part of the adjusting unit 15, 21, 29 is also an actuating device 29 for pivoting the outer ring 21 relative to the inner ring 15.
  • actuating device 29 for pivoting the outer ring 21 relative to the inner ring 15.
  • the outer ring 21 radially from a pin 31 in the form of an eyebolt, which is provided by a specially provided for this purpose 33rd in the support ring 20 in a formed in the pump housing 1, 1 a chamber 30 extends.
  • a ball joint 32 is arranged, which is connected to the axial end 35a of a screw 35, for example, a form-fitting, latched or threaded.
  • the ball joint 32 allows a balance of the angle between the pin 31 and the screw 25 when the outer ring 21 is pivoted.
  • ball joint 32 can be replaced by a simple hinge, since only an angle compensation in a spatial direction must be made here.
  • the screw 35 is designed as a grub screw and is also part of the actuator 29. It is located in a threaded bore 36, the tangential or slightly offset radially but parallel to a tangent to the mounting location of the pin 31 extends. The screwing depth of the screw 35 thus determines the angular position of the pin 31, since it presses with its axial end 35 a against the pin 31.
  • connection between the hinge 32 and the screw 35 need not be fixed, since only one movement of the pin 31 in one direction is required. This movement is effected when the screw 35 is screwed so far into the threaded bore 36 that it strikes against the pin 31, and is subsequently rotated beyond. If screw 35 were subsequently turned back, it merely moves away from pin 31 and outer ring 21 remains in the pivoted position.
  • a firm connection for example in the form of a positive connection (locked or threaded) has the advantage over the loose connection that a reversible adjustment, ie can be effected in two directions, turning back the screw 35 so again pivoting back of the outer ring 21 can reach. This allows a correction of the setting, for example, if the screw 35 was tightened too tight, the wear ring 14 thus firmly surrounds the suction mouth 10a.
  • the threaded bore 36 opens to the outside, so that the screw 35 is accessible from outside the pump housing. It can be rotated with a suitable tool without opening the pump housing 1, 1a.
  • the bore 36 is closed by a sealing plug 37, which is spaced to form a clearance 38 spaced from the grub screw 35.
  • the plug 37 is removed to actuate the actuator 29.
  • this actuator 29 is such that the screw 35 with increasing depth of engagement of the pin 31 increasingly to the rear, ie in the direction of the arrow ⁇ in Fig. 3 presses while changing its angular position and the outer ring 21 is pivoted.
  • a limitation of the angular adjustment can be achieved by a stop of the pin 31, for example by means of the recess 33 in the support ring 20 or through a wall of the chamber 30, which reaches the pin at maximum screwing depth of the screw 35.
  • the possible Winkelverstell Kunststoff Berlin the outer ring 21 is in Fig. 3 represented by dashed boundary lines. It can be between 0 ° and 15 ° or even between 0 ° and 20 °.
  • the wear ring 14 forms together with the inner ring 15, the outer ring 21, the support ring 20 and at least the pin 31 of the actuator 29 is a preassembled and optionally replaceable assembly 45, thus a Saughalsdichtungsbautechnik, so that the assembly of the centrifugal pump and an exchange of the wear ring in Servicing can be done easily and quickly.
  • the centrifugal pump 50 has an impeller 2 with two suction necks 10a, such Saughalsdichtungsbauech 45 corresponding to twice, as well as the actuators 29, which are operated independently can.
  • the wear ring 14 associated with the second suction neck 10a and / or the adjusting unit 15, 21, 29 associated with the second suction neck 10a thus have the same features, properties and advantages as previously described in relation to the wear ring 14 associated with the first suction neck 10a the adjusting means 15, 21, 29 associated with the first suction neck 10a are described.
  • a reduction in the efficiency of the centrifugal pump 50 can be present not only by a worn wear ring 14, but also by an impeller 2 damaged due to cavitation, so that an adjustment of the sealing gap would bring no improvement.
  • a double-flow impeller 2 according to Fig. 1 It should also be noted that two suction necks 10a, thus two sealing gaps are present, the wear rings 14 may wear different, so that only one of the two wear rings 14, an adjustment of the sealing gap is required.
  • Fig. 1 shows a simple measure to find the cause of the impairment of efficiency.
  • an endoscope 39 which in the usual way has a flexible tube 40 with a Bowden cable for navigating and end-side camera 42, and a monitor unit 41 for displaying the image captured by the camera 42, can easily be passed through the inspection opening 43 and the impeller 2 be navigated to take a picture of the impeller 2 and the sealing gap.
  • Such a revision opening 43 can in accordance with the centrifugal pump 50 Fig. 1 be present on both sides of the pump housing 1, 1b, so that both sides of the impeller are equally accessible.
  • the inspection opening 43 is sealed by a closure element 44, which is preferably self-sealing.
  • the endoscope 39 can help to achieve a precise adjustment of the sealing gap, since it can be seen via the camera image on the monitor unit 41 whether and how far the sealing gap has to be reduced.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP18000558.9A 2018-06-25 2018-06-25 Pompe centrifuge à joint d'étanchéité pour bride d'aspiration amélioré Active EP3467319B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP18000558.9A EP3467319B1 (fr) 2018-06-25 2018-06-25 Pompe centrifuge à joint d'étanchéité pour bride d'aspiration amélioré
CN201920944830.8U CN211314647U (zh) 2018-06-25 2019-06-21 离心泵及离心泵组件

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP18000558.9A EP3467319B1 (fr) 2018-06-25 2018-06-25 Pompe centrifuge à joint d'étanchéité pour bride d'aspiration amélioré

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EP3467319A1 true EP3467319A1 (fr) 2019-04-10
EP3467319B1 EP3467319B1 (fr) 2022-03-30

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110345082A (zh) * 2019-07-11 2019-10-18 浙江理工大学 叶轮时序角与跨距可调的两级离心泵装置及方法

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1545608A (en) * 1924-10-31 1925-07-14 Frederick Iron & Steel Company Centrifugal pump
US1639279A (en) * 1923-05-16 1927-08-16 Frederick Iron And Steel Compa Wearing ring for rotary elements
WO1998048173A1 (fr) * 1997-04-23 1998-10-29 Toyo Pumps North America Corporation Dispositif de reglage du jeu fonctionnel d'une turbine
US8690534B1 (en) * 2009-06-08 2014-04-08 Curtiss-Wright Electro-Mechanical Corporation Backup seals in rotary pumps
KR20160065333A (ko) * 2014-11-28 2016-06-09 현대중공업 주식회사 원심펌프

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1639279A (en) * 1923-05-16 1927-08-16 Frederick Iron And Steel Compa Wearing ring for rotary elements
US1545608A (en) * 1924-10-31 1925-07-14 Frederick Iron & Steel Company Centrifugal pump
WO1998048173A1 (fr) * 1997-04-23 1998-10-29 Toyo Pumps North America Corporation Dispositif de reglage du jeu fonctionnel d'une turbine
US8690534B1 (en) * 2009-06-08 2014-04-08 Curtiss-Wright Electro-Mechanical Corporation Backup seals in rotary pumps
KR20160065333A (ko) * 2014-11-28 2016-06-09 현대중공업 주식회사 원심펌프

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110345082A (zh) * 2019-07-11 2019-10-18 浙江理工大学 叶轮时序角与跨距可调的两级离心泵装置及方法
CN110345082B (zh) * 2019-07-11 2024-04-05 浙江理工大学 叶轮时序角与跨距可调的两级离心泵装置及方法

Also Published As

Publication number Publication date
CN211314647U (zh) 2020-08-21
EP3467319B1 (fr) 2022-03-30

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