EP3029332B1 - Axial geteilte pumpe - Google Patents

Axial geteilte pumpe Download PDF

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Publication number
EP3029332B1
EP3029332B1 EP15189336.9A EP15189336A EP3029332B1 EP 3029332 B1 EP3029332 B1 EP 3029332B1 EP 15189336 A EP15189336 A EP 15189336A EP 3029332 B1 EP3029332 B1 EP 3029332B1
Authority
EP
European Patent Office
Prior art keywords
sealing
pump
groove
sealing element
accordance
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.)
Active
Application number
EP15189336.9A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3029332A1 (de
Inventor
Willy Handloser
Thomas Welschinger
Heike Tischler
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.)
Sulzer Management AG
Original Assignee
Sulzer Management AG
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 Sulzer Management AG filed Critical Sulzer Management AG
Priority to EP15189336.9A priority Critical patent/EP3029332B1/de
Publication of EP3029332A1 publication Critical patent/EP3029332A1/de
Application granted granted Critical
Publication of EP3029332B1 publication Critical patent/EP3029332B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04D29/10—Shaft sealings
    • F04D29/12—Shaft sealings using sealing-rings
    • F04D29/126—Shaft sealings using sealing-rings 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
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage 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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal 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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/043—Shafts
    • 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
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/053—Shafts
    • 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
    • F04D29/086—Sealings 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
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/12—Shaft sealings using sealing-rings
    • F04D29/122—Shaft sealings using sealing-rings especially adapted for elastic fluid 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
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal 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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal 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
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid 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
    • F04D29/426—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
    • F04D29/624—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for elastic fluid 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
    • F04D29/628—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for liquid pumps

Definitions

  • the invention relates to an axially divided pump for conveying a fluid according to the preamble of the independent claim.
  • Axially split pumps also referred to as horizontally split pumps, are pumps in which the housing is split parallel to the axis of the shaft and thus has a base and cover. Both the lower part and the lid each have a flange, which are stacked for mounting the pump and then firmly connected to each other, for example, screwed.
  • Axially split pumps have long been well known and in many embodiments are usually manufactured as centrifugal pumps, for example as single or double-flow pumps and as single-stage or multi-stage pumps.
  • the impeller of the pump can be arranged between two bearings (Between-bearing pump).
  • Between-bearing pump The range of application of these pumps is also very broad, they are used for example in the oil and gas industry or in the water industry or in the field of energy production.
  • axially split pumps are designed for high operating pressure or high flow rates and are suitable for pumping over large geodesic heights, for pumping through water or oil pipelines, or for seawater desalination using reverse osmosis.
  • An alternative technology for sealing between the lower part and the lid, as for example in the WO-A-2014/083374 is to mount the flanges of the base and the top directly to each other without intervening seal. The respective surfaces of the two flanges then form sealing surfaces, which have direct contact with each other in the mounted state.
  • a sealing groove is provided in the lower part or in the lid or in the lower part and in the cover, which extends over the entire axial length of the pump and in which a cord-shaped sealing element, for example, an O-ring-like sealing element is inserted. Most of these sealing groove is provided for manufacturing and assembly reasons only in the lower part.
  • the lower part and the cover are firmly screwed together so that the sealing surfaces of the two flanges are in direct contact with each other and the cord-shaped sealing element is elastically deformed in the sealing groove, so as to ensure a reliable seal.
  • the cord-shaped sealing elements are usually made of an elastomer, as it is also used for commercial O-ring seals, for example, from the nitrile rubber nitrile-butadiene rubber (NBR: nitrile butadiene rubber).
  • NBR nitrile butadiene rubber
  • an inner cord-shaped sealing element may be provided for sealing the suction chamber against the pressure chamber and an outer cord-shaped sealing element, which seals the interior of the pump against the outside world, so the ambient pressure.
  • additional sealing grooves can be provided, each with inserted string-shaped elements to distinguish the different pressure chambers, in which different pressures prevail against each other.
  • One such critical location is the connection between the housing of the pump and the side covers of the pump, a point at which a total of three components adjoin one another, namely the lower part of the housing, the cover of the housing and the side cover.
  • the pump must be sealed against the environment or the ambient pressure. Leakages that occur here not only lead to a reduction in the efficiency of the pump, but can also lead to environmental stresses due to escaping fluid, for example in the case of liquids such as crude oil or crude oil, depending on the fluid delivered by the pump.
  • a cord-shaped sealing element is inserted into the sealing groove and inserted into the annular sealing groove an annular sealing element.
  • the invention is based on the finding that in particular at such contact points between two separate sealing elements, against which a planar -also non-curved end surface of a sealing element on a curved surface, for example, the lateral surface of a circular cross-section second sealing element.
  • This geometry requires a reduced contact surface between the two sealing elements, so that leakages can occur here more easily.
  • the annular groove for receiving the annular sealing member is formed jointly by the housing and the side cover, arise at this critical point additional sealing points, through which the effect of the sealing elements is improved, so that especially at very high operating pressure an extremely reliable seal is ensured between the housing of the pump and the side cover.
  • cord-shaped sealing element has a planar cross-sectional area on the second contact surface.
  • the sealing groove opens substantially perpendicularly into the annular groove.
  • the sealing groove is provided in the lower part of the housing, which in particular allows for easier production and easier assembly.
  • sealing groove extends from the second contact surface to the opposite end of the pump with respect to the axial direction, which is designed to receive a second side cover, which is suitable for closing the housing and in which the sealing groove, the cord-shaped sealing element is inserted, which extends over the entire longitudinal extent of the sealing groove.
  • annular groove formed by the recess and the projection has a substantially rectangular cross-sectional area perpendicular to its longitudinal extent.
  • the annular groove has a width in the radial direction which is greater than the width of the cord-shaped sealing element.
  • annular sealing element With respect to the annular groove an annular sealing element is inserted, which preferably has a circular or elliptical cross-sectional area.
  • the annular sealing element has a height in the axial direction, which is greater than the depth of the annular groove in the axial direction.
  • a further advantageous measure consists in that the sealing groove has at its junction in the second contact surface a recess which is arranged radially inwardly with respect to the sealing groove.
  • an elastic biasing element which exerts a radially outwardly directed bias on the cord-shaped sealing element.
  • the biasing element is resilient and extends parallel to the cord-shaped sealing element.
  • the biasing element is designed as a spring.
  • the annular sealing element and the cord-shaped sealing element is made of an elastomer, in particular of a nitrile rubber, especially of nitrile-butadiene rubber (NBR).
  • NBR nitrile-butadiene rubber
  • the inventive pump is particularly suitable for very high operating pressures and can preferably be designed as a centrifugal pump with a design pressure of at least 50 bar, preferably at least 100 bar.
  • Fig. 1 shows a perspective view of an embodiment of an inventive axially divided pump, which is generally designated by the reference numeral 1.
  • the pump 1 comprises a housing 2, which is divided axially, and a lower part 21 and a cover 22 includes.
  • Fig. 1 the lid 22 removed and indicated only symbolically.
  • Fig. 2 shows a plan view of the lower part 21 of the housing 2 of this embodiment.
  • the housing 2 comprises an inlet 5 for sucking a fluid to be delivered and an outlet 6 for the fluid.
  • the pump 1 comprises a rotatable shaft 3 whose longitudinal direction defines an axial direction A.
  • On the shaft 3 is at least one impeller 4, in the present case, there are two wheels 4, rotatably mounted, which promotes the fluid from the inlet 5 to the outlet 6.
  • a bearing device 7 is provided at both ends with respect to the axial direction A of the pump 1 to support the shaft 3 of the pump 1.
  • the representation according to left bearing device 7 ( Fig. 1 ) is further provided with a coupling 8 which is connectable to a drive, not shown, which causes the shaft 3 of the pump 1 in rotation.
  • axially divided pump 1 or axially split housing 2 means, as is generally customary, that the housing 2 is divided parallel to the longitudinal direction of the shaft 3, ie in a plane which contains the longitudinal axis of the shaft 3.
  • Fig. 1 and Fig. 2 illustrated pump 1 to an axially divided multi-stage - here two-stage centrifugal pump, which is designed einflutig and in a so-called Between-Bearing arrangement, ie the wheels 4 are located between the storage devices 7.
  • the invention is not limited to such pump types but is also suitable for all other pumps with axially split housing 1, for example, single-stage pumps, ie those with only one impeller 4, double-flow pumps with single-stage or multi-stage design or other types of pumps as centrifugal pumps.
  • the housing 2 of the pump 1 is closed in each case by a side cover 9, which simultaneously constitutes the end cover of the mechanical shaft seal in the present case.
  • the cover 22 and the lower part 21 of the housing 2 are in direct contact with each other in the mounted state, that is, no flat gasket is provided between these two parts, which prevents direct contact between the lower part 21 and the cover 22.
  • the lower part 21 comprises a first flange 211, which extends in the assembled state in the plane of the axial pitch of the housing 2 and whose upper surface according to the illustration forms a first sealing surface 212.
  • the cover 22 is provided with a second flange 221, which extends in the assembled state in the plane of the axial pitch of the housing 2 and its lower surface according to the representation ( Fig. 1 ) forms a second sealing surface 222.
  • the first sealing surface 212 and the second sealing surface 222 are in direct contact with each other to form a sealing connection between the lower part 21 and the cover 22 of the housing 2.
  • a sealing groove 213 is provided, which extends from the representation according to the left side cover 9 in the axial direction A of the inner contour of the pump 1 following up to the other side cover 9.
  • This seal groove 213 is provided on both sides of the shaft 3.
  • a cord-shaped sealing element 10 is inserted, which extends over the entire length of the sealing groove 213 and which seals the interior of the pump 1 from the environment.
  • the cord-shaped sealing element 10 usually has a round cross-section, as it is known for example from commercially available O-rings. Of course, it is also possible that the cord-shaped sealing element has a different cross section, for example a rectangular and in particular a square cross section. In this case, the cord-shaped sealing element 10 is dimensioned with respect to its diameter so that it protrudes beyond the edge of the sealing groove 213 in the unassembled state. When mounting the cover 22 on the lower part 21 thus the cord-shaped sealing element 10 is elastically deformed and thus ensures a reliable seal between the lower part 21 and the cover 22 of the housing. 2
  • the attachment of the cover 22 on the lower part 21 is preferably carried out by means of bolts or screws, which by the provided in the first sealing surface 212 holes or tapped holes (without reference numerals in Fig. 1 and Fig. 2 ), so that the lower part 21 and the cover 22 are screwed tightly and sealingly together.
  • sealing groove 213 in the cover 22 of the housing 2, or to provide a sealing groove both in the lower part 21 and in the cover 22.
  • the side cover 9 has a first contact surface 91, which cooperates with a second contact surface 23 which is provided on the housing 2 (see Fig. 3 ).
  • the second contact surface 23 surrounds the shaft 3 and extends both over the lower part 21 of the housing 2 and over the cover 22 of the housing 2.
  • Fig. 3 shows Fig. 3 in an enlarged view, the side cover 9 and a part of the housing 2 in a plan view of the lower part 21, wherein the side cover 9 is not yet joined to the housing 2.
  • the sealing groove 213 in the lower part 21 of the housing 2 which extends into the second contact surface 23 of the housing 2.
  • the sealing connection between the side cover 9 and the housing 2 is a particular challenge, because here three components adjoin one another, namely the side cover 9, the lower part 21 and the cover 22 of the housing 2.
  • the first contact surface 91 of the side cover 9 is replaced by one of his Boundary surfaces formed in the axial direction A.
  • the second contact surface 23 of the housing 2 is perpendicular to the axial direction A, so that it faces the first contact surface 91.
  • a recess 24 is provided in the second contact surface 23 of the housing 2, which recess is designed here as a central recess in the second contact surface 23.
  • a projection 92 is provided in the first contact surface 91 of the side cover 9, which is designed here as a central elevation.
  • the recess 24 and the projection 92 are designed and arranged to each other so that they together in the mounted state of the side cover 9 an annular groove 29 for receiving an annular sealing member 11 (see also Fig. 4 and Fig. 5 ) form.
  • the central recess which forms the recess 24 in the second contact surface 23, substantially formed with a circular cross-section whose diameter is greater than the diameter of the also formed substantially circular circular projection, which the projection 92nd forms in the first contact surface 91.
  • This annular groove 29 is thus bounded radially outwardly by the side wall 241 of the recess 24 in the second contact surface 23 of the housing 2 and radially inwardly the lateral boundary surface 921 of the projection 92 in the first contact surface 91 of the side cover 9.
  • Fig. 4 shows in a schematic representation of the annular groove 29, which results from the composition of the side cover 9 and the housing 2.
  • the annular sealing member 11 and the cord-shaped sealing member 10 is not shown. Further limited Fig. 4 on the illustration of the upper half of Fig. 3 because this is sufficient for understanding.
  • Fig. 5 is a representation similar to the one in Fig. 4 However, here are the annular sealing member 11 inserted into the annular groove 29 and the cord-shaped sealing member 10 in the seal groove 213.
  • the annular groove 29 which surrounds the shaft 3 of the pump 1.
  • the first contact surface 92 and the second contact surface 23 are in direct contact with each other after mounting the side cover.
  • the annular groove 29 perpendicular to its longitudinal direction extending in the circumferential direction has a substantially rectangular cross-sectional area.
  • This cross-sectional area is determined by the axial depth T of the annular groove 29 - ie its depth with respect to the axial direction A - and by the radial width B of the annular groove 29 - ie its width with respect to the radial direction perpendicular to the axial direction A.
  • the sealing groove 213 opens substantially perpendicularly into the annular groove 29. Since the end face of the cord-shaped sealing element 10 placed on the second contact surface 23 is preferably a planar, ie non-curved, cross-sectional area (see FIG Fig. 5 ), By this measure, the best possible contact between the cord-shaped sealing element 10th and realize the annular seal member 11 in the annular groove 29.
  • the radial width B of the annular groove 29 is greater than the width of the cord-shaped sealing element 10.
  • the sealing groove 213 is then arranged so that it opens centrally into the annular groove 29.
  • the annular sealing element 11, which is inserted into the annular groove 29, preferably has a circular or elliptical cross-sectional area, so that commercial sealing elements such as O-rings can be used here.
  • the annular sealing element has a different cross section, for example a rectangular and in particular a square cross section.
  • the annular sealing element 11 is preferably dimensioned such that its height, which means its extent in the axial direction A, is greater than the axial depth T of the annular groove 29. Namely, the annular sealing element 11 protrudes in the unassembled state of the side cover 9 with respect to the axial direction A beyond the projection 92 of the first contact surface 91 out.
  • the annular sealing member 11 When mounting the side cover 9 on the housing 2, consequently, the annular sealing member 11 is elastically deformed and in consequence in intimate contact with the end face of the cord-shaped sealing member 10 (see Fig. 5 ). With respect to the extent in the radial direction, the annular sealing element 11 is preferably dimensioned such that it fills the radial width B of the annular groove 29.
  • the cord-shaped sealing element 10 is preferably also an O-ring-like element, but not designed as a ring but as a cord with two ends, and an example circular or circular cross-sectional area perpendicular to its longitudinal extent. With respect to the width in the radial direction, the cord-shaped sealing member 10 is usually sized so that it does not completely fill the sealing groove 213, as in Fig. 5 is shown.
  • Suitable materials for both the annular sealing element 11 and the cord-shaped sealing element 10 are in particular all materials known per se, which are used for such seals, in particular elastomers such as nitrile rubber and especially nitrile-butadiene rubber (NBR).
  • elastomers such as nitrile rubber and especially nitrile-butadiene rubber (NBR).
  • the procedure is, for example, as follows:
  • the cord-shaped sealing element 10 is inserted into the sealing groove 213 provided in the lower part 21 of the housing 2 on both sides of the shaft 3 (see eg Fig. 2 ) so as to extend from the second contact surface 23 of the housing 2 along the axial direction A of the inner contour of the pump 1 following to the opposite axial end of the pump 1.
  • the cover 22 of the housing 2 can be connected to the lower part 21, wherein the cord-shaped sealing element 10 in the sealing groove 213 preferably elastically deformed and contributes to the seal between the lower part 21 and the cover 22.
  • the annular seal member 11 Before mounting the side cover 9, the annular seal member 11 is placed around the projection 92 in the side cover 9. After mounting the side cover 9 on the housing 2 then forms the annular groove 29, in which the annular sealing member 11 is inserted, which presses against the end face of the cord-shaped sealing member 10, which is inserted into the seal groove 213. This condition is in Fig. 5 shown.
  • FIG. 5 shows created by the common annular groove 29, whose one wall is formed by the side wall 241 of the recess 24, while the other wall is formed by the lateral boundary surface 921 of the projection 92, additional axial sealing surfaces 30 and additional radial sealing surfaces 31, which contribute to an improved seal between the housing 2 and the side cover 9.
  • the pump 1 can be designed, for example in one embodiment as a centrifugal pump, with a design pressure of at least 50 bar and preferably at least 100 bar.
  • Fig. 6 illustrated in a too Fig. 5 a particularly preferred variant of the embodiment of the inventive pump 1.
  • the reference numerals have the same meaning for the same or functionally equivalent parts.
  • the seal groove 213 at its junction in the second contact surface 23 and in the annular groove 29 has a recess 214 which is arranged radially inwardly with respect to the seal groove 213.
  • the recess 214 extends parallel to the sealing groove 213, such that the sealing groove 213 in its end region in the axial direction A over a length L has an enlarged by the width D of the recess 214 expansion in the radial direction.
  • the radially inner boundary surface 215 of the recess 214 is disposed so that it is closer to the shaft 3 than the lateral boundary surface 921 of the projection 92. Thereby exists between the lateral boundary surface 921 of the projection 92 and with respect to this radially inwardly arranged boundary surface 215th the recess 214 is a shoulder 216, which is part of the first contact surface 91 of the side cover 9.
  • an elastic biasing element 217 is preferably inserted, which exerts a radially outwardly directed bias on the cord-shaped sealing element 10.
  • the biasing member 217 is resilient, and more preferably as a spring designed.
  • the spring 217 extends parallel to the cord-shaped sealing element 10 and is dimensioned so that it is wider than the width D of the recess 214 with respect to the radial direction. After mounting the side cover 9, the spring 217 can be supported on the shoulder 216.
  • the biasing element 217 offers several advantages. During operation of the pump 1, the biasing element ensures an additional contribution, that even at lower operating pressures, so for example when starting the pump 1, immediately a sufficient sealing effect between the housing 2 and the side cover 9 is realized. Also with regard to the long-term operation of the pump 1, the biasing member 217 is advantageous. If it comes with increasing operating time of the pump 1 to degradation, fatigue or other changes or wear of the cord-shaped sealing member 10, these can be compensated by the action of the biasing member 217, because this the cord-shaped sealing member 10 reliably against the radially outer wall of the sealing groove 213rd suppressed.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Mechanical Sealing (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Sealing Devices (AREA)
EP15189336.9A 2014-12-05 2015-10-12 Axial geteilte pumpe Active EP3029332B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP15189336.9A EP3029332B1 (de) 2014-12-05 2015-10-12 Axial geteilte pumpe

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP14196438 2014-12-05
EP15189336.9A EP3029332B1 (de) 2014-12-05 2015-10-12 Axial geteilte pumpe

Publications (2)

Publication Number Publication Date
EP3029332A1 EP3029332A1 (de) 2016-06-08
EP3029332B1 true EP3029332B1 (de) 2019-05-01

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Country Status (11)

Country Link
US (1) US10273969B2 (pt)
EP (1) EP3029332B1 (pt)
KR (1) KR102468017B1 (pt)
CN (1) CN105673549B (pt)
AU (1) AU2015255273B2 (pt)
BR (1) BR102015029345B1 (pt)
CA (1) CA2912717C (pt)
ES (1) ES2725912T3 (pt)
MX (1) MX364482B (pt)
RU (1) RU2702450C2 (pt)
SG (1) SG10201509181PA (pt)

Cited By (1)

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RU227890U1 (ru) * 2024-05-31 2024-08-08 Павел Олегович Нечаев Насос самовсасывающий центробежный

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3029332B1 (de) * 2014-12-05 2019-05-01 Sulzer Management AG Axial geteilte pumpe
CN108087292A (zh) * 2018-01-05 2018-05-29 昆山益威科环保机械有限公司 一种带有循环冷却系统的耐空转水泵
CN110985395A (zh) * 2019-12-28 2020-04-10 安徽银龙泵阀股份有限公司 一种便于维修的离心泵
CN112392263B (zh) * 2020-11-04 2022-04-19 通号工程局集团城建工程有限公司 一种铝板幕墙安装施工方法
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BR102015029345B1 (pt) 2022-06-28
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US20160160873A1 (en) 2016-06-09
KR102468017B1 (ko) 2022-11-16
AU2015255273B2 (en) 2019-05-02
RU2015149193A3 (pt) 2019-04-24
CN105673549A (zh) 2016-06-15
RU2702450C2 (ru) 2019-10-08
MX2015015975A (es) 2016-06-06
EP3029332A1 (de) 2016-06-08
KR20160068648A (ko) 2016-06-15
ES2725912T3 (es) 2019-09-30
BR102015029345A2 (pt) 2016-08-09
AU2015255273A1 (en) 2016-06-23
MX364482B (es) 2019-04-29
CN105673549B (zh) 2020-04-21
SG10201509181PA (en) 2016-07-28
US10273969B2 (en) 2019-04-30
CA2912717C (en) 2022-11-29

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