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WO2013060311A1 - Guidage d'un courant partiel en particulier dans un pompe à entraînement magnétique - Google Patents

Guidage d'un courant partiel en particulier dans un pompe à entraînement magnétique Download PDF

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Publication number
WO2013060311A1
WO2013060311A1 PCT/DE2012/000940 DE2012000940W WO2013060311A1 WO 2013060311 A1 WO2013060311 A1 WO 2013060311A1 DE 2012000940 W DE2012000940 W DE 2012000940W WO 2013060311 A1 WO2013060311 A1 WO 2013060311A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
impeller
medium
flow
magnetic coupling
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.)
Ceased
Application number
PCT/DE2012/000940
Other languages
German (de)
English (en)
Inventor
Günther Schneider
Michael Westib
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.)
Ruhrpumpen GmbH
Original Assignee
Ruhrpumpen GmbH
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 Ruhrpumpen GmbH filed Critical Ruhrpumpen GmbH
Publication of WO2013060311A1 publication Critical patent/WO2013060311A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/047—Bearings hydrostatic; hydrodynamic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/021—Units comprising pumps and their driving means containing a coupling
    • F04D13/024—Units comprising pumps and their driving means containing a coupling a magnetic coupling
    • F04D13/027—Details of the magnetic circuit
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F04D29/588—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps cooling or heating the machine

Definitions

  • Partial flow guide in particular a magnetic coupling pump
  • the invention relates to a magnetic coupling pump, which has a shaft with a through hole and an impeller-side sliding bearing and a rotor-bearing plain bearing, wherein on the shaft, an inner magnet rotor is arranged, which abuts at least partially on a bearing housing, wherein a medium gap is formed.
  • Such magnetic coupling pumps are generally known, and are described, for example, in DE 10 2009 022 916 A1.
  • the pump power from a drive shaft via a magnet-bearing rotor (outer rotor) without contact and substantially slipless on the pump-side magnet carrier (inner rotor, first drive element) is transmitted.
  • the inner rotor or the first drive element drives the pump shaft, which is mounted in a sliding bearing lubricated by the conveying medium, ie in a hydrodynamic slide bearing.
  • Between the outer rotor and the inner rotor, so between the outer and the inner magnet is a containment shell with its cylindrical wall.
  • the containment shell is connected at its flange to a pump component, for example a housing cover, and has a closed bottom opposite thereto.
  • a pump component for example a housing cover
  • the containment shell so the magnetic coupling pump reliably separates the product space from the environment, so that the risk of product leakage can be excluded with all the associated negative consequences.
  • a magnetic coupling pump is therefore the combination of a conventional pump hydraulics with a magnetic drive system. This system uses the attraction and repulsion forces between magnets in both coupling halves for non-contact and slip-free torque transmission. Especially when dealing with very valuable or very dangerous substances, the magnetic coupling pump therefore has great advantages.
  • EP 0 814 275 B1 deals with a hydrodynamic sliding bearing of a magnetic coupling pump, which is designed as a combined axial and radial bearing.
  • the slide bearing of EP 0 814 275 B1 has two bearing sleeves, two bearing bushes which can be slid on the bearing sleeves, a spacer sleeve arranged between the bearing sleeves and a spacer bush arranged between the bearing bushes.
  • the bearing sleeves and bushings are formed of a ceramic material, wherein the spacer sleeve or bushing is formed of a metal.
  • CONFIRMATION COPY should be and should be designed so that at any time sufficient lubrication passes through the medium to be conveyed in the plain bearing, proposes EP 0 814 275 B1, that the inner diameter of the bearing sleeves is greater than the inner diameter of the spacer sleeve. Furthermore, EP 0 814 275 B1 proposes that a partial flow of the conveying medium passes the impeller-free sliding bearing passing through a passage of the inner magnet rotor into the containment shell, from where the delivery medium passes into the passage bore of the shaft, and returned to the suction region of the pump becomes.
  • a disadvantage of this configuration may be that the desired positive guidance of the conveying medium partial flow is not given by the inner magnet rotor in the pressure chamber and from there into the hollow-drilled shaft, for example, if the corresponding pressure conditions are unfavorable.
  • the conveyed medium heated by the magnetic power loss could be pressed against the actually provided (forced) flow direction by the inner magnet rotor, or through the channel passage bore thereof against the axial bearing element remote from the rotor, so that the respective axial thrust loaded axial bearing element is already heated Partial conveying medium flow is lubricated, which can lead to a bearing damage in the worst case.
  • the invention has for its object to improve a magnetic coupling pump of the type mentioned by simple means or to create, in which always a secure cooling and lubrication is ensured with fluid.
  • the object is achieved by a magnetic coupling pump with the features of claim 1, wherein the medium gap has a Strömungsver- changing element.
  • the magnetic coupling pump has the inner magnet rotor and the bearing housing. Both lie with corresponding surfaces to each other, of course, a medium gap between the two surfaces (Trägeranlaufzone) is provided. Through the medium gap, a medium partial flow in the direction of Channel passage bore flow, wherein a leakage flow can flow through the medium gap. In this respect, the medium gap has only the function of a leakage gap, with neither cooling nor lubrication is absolutely necessary.
  • the respective plain bearing has radial bearing elements, that is to say a bearing bush and a bearing sleeve and the axial bearing element or a bearing disk. Between opposing sliding surfaces of the bearing bush and the bearing sleeve, a lubrication groove is provided which is introduced into the sliding surface of the bearing bush.
  • the respective lubrication groove can be embodied with a rounded profile, which has a curvature oriented away from this, with respect to a center axis of the bearing bush, that is to say it is preferably convex.
  • the pumped medium which is taken in a known manner to supply the sliding bearings but also for heat dissipation of the magnetic power loss, passes both through the impeller away lubrication past the bearing disk over and through the medium gap to the channel through-hole where both streams unify nigen and in the containment shell or be led into the pressure chamber.
  • the magnetic coupling pump on a second drive element which may also be referred to as an external magnet rotor. Between two magnet rotors the containment shell is arranged.
  • the cooling medium flow which flows into a cooling gap within the containment shell and ends in the bottom region of the containment shell, ie in a pressure space, is used to dissipate the heat loss.
  • the cooling medium flow is of course heated after passing through the cooling gap, with the invention advantageously a flow of heated medium from the pressure chamber is avoided to the impeller bearing plain bearing. From the pressure chamber, the cooling medium flow passes into the through hole of the shaft and is conveyed to the suction side of the conveying element or the magnetic coupling pump.
  • the flow through the hollow-bored shaft is well known in the art.
  • the impeller near the impeller in its course towards the outlet side to the impeller bearing disc is conical, with the impeller near the impeller preferably tapers to the outlet side.
  • a corresponding adaptation ie a corresponding conical configuration, can only be sufficient for the surface of the bearing bush close to the running wheel.
  • the flow change element can be embodied as a labyrinth, it being expedient to provide the grooves of the labyrinth in the corresponding surface of the bearing housing, that is to say in a non-rotating component.
  • the frontal pressure which acts on the inner end face of the inner magnet rotor, increases in parallel, which ensures that the amount of partial flow through the cooling gap or the cooling medium flow, as already mentioned, is increased, whereby e.g. In the case of low-boiling media to be conveyed, the heat input into the medium is reduced by the larger tangential flow through the cooling gap.
  • the axial thrust of the pump can be better controlled, since the prevailing pressure on the end face of the inner magnet rotor near the impeller is increased in magnitude, whereby the impeller-remote thrust bearing element or the bearing disk remote from the impeller is relieved.
  • FIG. 1 shows a detail of a magnetic coupling pump in one
  • Figure 1 shows a section of a magnetic coupling pump 1 with a pump shaft, for example as a stainless steel shaft, which carries an impeller, and which is mounted in a hydrodynamic sliding bearing, wherein the hydrodynamic sliding bearing externally lubricated by fluid, but also with another, product-compatible fluid can be.
  • the exemplary magnetic coupling pump 1 is known with its individual components per se, for example from EP 0 814 275 B1, which is why it is not described in detail.
  • the magnetic coupling pump 1 has a roller bearing near plain bearing and a drive bearing plain bearing.
  • the respective plain bearing has a bearing sleeve, a bearing bush 2 and a thrust bearing element 3 or a bearing disk 3.
  • a lubrication groove is arranged, which is introduced into the bearing bush 2.
  • the respective lubrication groove can be embodied with a rounded course, which has a curvature oriented away from this, with respect to a center axis of the bearing bush 2, ie is preferably convex.
  • the inner magnet rotor 4 engages over the bearing housing 6 in regions, so that a so-called carrier start-up zone 7 is formed, in which a medium gap 8 is arranged.
  • the medium gap 8 is thus arranged between mutually opposite surfaces of the bearing housing 6 and the inner magnet rotor 4.
  • the inner magnet rotor 4 is in operative connection with a driven outer magnet rotor 9.
  • a split pot 1 1 is arranged, which opposite to the impeller has a bottom 12, so that a pressure chamber 13 is formed.
  • a cooling gap 14 is arranged, which opens into the pressure chamber 13.
  • a through hole is introduced, which is open to the pressure chamber 13 out.
  • the through hole has a medium connection or a channel system to the impeller of the exemplary magnetic coupling pump 1.
  • the invention aims at the advantageous partial flow guide for cooling and lubrication of the magnetic coupling pump 1, for example, with pumped medium.
  • the fluid is removed at a point of high pressure in the impeller and passed through a bore through the housing cover in a collection bag.
  • the collection bag is formed on the one hand by a section of the can 11, a portion of the bearing housing 6 and the impeller near the end face of the inner magnet rotor 4.
  • the guided into the collection bag medium flow flows with a partial flow 16 through the cooling gap 14 into the pressure chamber 13, and is passed with a second partial flow 17 through the medium gap 8.
  • the lubricating medium flow which is removed at another location and is passed into a lubricating pocket between the plain bearings, is divided into two lubrication streams.
  • the first lubrication flow 20 flows through the off-wheels lubrication around the impeller remote thrust bearing element in a channel formation, which is designed as a channel passage bore 18, and through this into the pressure chamber 13.
  • the partial flow 17 via the medium gap 8 also passes into the channel passage bore 18th
  • the impeller near the wheel lubrication is made conical.
  • the impeller near the impeller narrowing tapered from its lubrication pocket oriented input side to the opposite outlet side in its inside diameter, wherein only the bearing bush is machined on its surface, that results in the conical shape of the wheel near lubrication.
  • the medium pressure at the outlet of the wheel-far lubrication is directly dependent on the feed amount of the medium in the collection bag.
  • the back pressure increases at the impeller near end face of the inner magnet rotor 4, resulting in a reduction of the axial thrust to the suction side, whereby the impeller-distant bearing disc 3 is relieved.
  • the end-side pressure on the impeller-near end face of the inner magnet rotor 4 has a smaller amount than the delivery of the magnetic coupling pump 1. From the cooling medium flow, a higher percentage flows through the cooling gap 14 into the pressure chamber 13 than through the medium gap 8 to the channel passage bore 18th
  • this advantageously has a flow modification element 19, preferably a throttle element 19 in the exemplary embodiment as a labyrinth 19, so that the amount of partial flow which flows through the medium gap 8 by way of example 10 - 30%, for example, reduced by 20%, at the same time the amount of the cooling medium flow through the cooling gap 14 by example 10 - 30%, for example, increased by 20%.
  • the end-side pressure on the impeller-near end side of the inner magnet rotor 4 is simultaneously increased, whereby the pressure at the outlet of the medium gap 8 is reduced, so that the first lubrication flow for the lubrication of the impeller-free slide bearing is forced into a low pressure range.
  • the throttle element 19 could also be designed as a delivery thread.
  • the target is when the throttle element 19 is arranged in the non-rotating component or in the bearing housing.
  • the throttle element 19 embodied as a labyrinth 19 has grooves 21 which are spaced apart from one another in the axial direction and which are arranged or introduced into the relevant surface of the bearing housing 6.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne une pompe à entraînement magnétique comprenant un arbre présentant un alésage traversant ainsi qu'un palier lisse situé côté roue, et un palier lisse situé à distance de la roue, un rotor magnétique interne (4) étant monté sur l'arbre, et venant en appui au moins par endroits sur un logement de palier (6), un intervalle pour fluide (8) étant formé entre les deux. La pompe à entraînement magnétique (1) est caractérisée en ce que l'intervalle pour fluide (8) comporte un élément de modification d'écoulement (19):
PCT/DE2012/000940 2011-10-28 2012-09-24 Guidage d'un courant partiel en particulier dans un pompe à entraînement magnétique Ceased WO2013060311A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201110117182 DE102011117182A1 (de) 2011-10-28 2011-10-28 Teilstromführung, insbesondere einer Magnetkupplungspumpe
DE102011117182.0 2011-10-28

Publications (1)

Publication Number Publication Date
WO2013060311A1 true WO2013060311A1 (fr) 2013-05-02

Family

ID=47075983

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2012/000940 Ceased WO2013060311A1 (fr) 2011-10-28 2012-09-24 Guidage d'un courant partiel en particulier dans un pompe à entraînement magnétique

Country Status (2)

Country Link
DE (1) DE102011117182A1 (fr)
WO (1) WO2013060311A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11590207B2 (en) 2016-09-29 2023-02-28 Ascendis Pharma Bone Diseases A/S Dosage regimen for a controlled-release PTH compound

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2840137A1 (de) * 1978-09-15 1980-03-27 Lederle Pumpen & Maschf Pumpen-motor-aggregat, insbesondere fuer normpumpen-aggregate
DE9116052U1 (de) * 1991-12-24 1992-02-20 Pumpenbau G. Schulte, 4040 Neuss Pumpe für Flüssigkeiten niedriger Viskosität oder nahe dem Siedepunkt
EP0555173A1 (fr) * 1992-02-03 1993-08-11 A/S De Smithske Pompe
US5248245A (en) * 1992-11-02 1993-09-28 Ingersoll-Dresser Pump Company Magnetically coupled centrifugal pump with improved casting and lubrication
EP0814275B1 (fr) 1996-06-20 2003-06-04 Klaus Union GmbH & Co.KG Palier lisse hydrodynamique pour le rotor d'une pompe
DE102009022916A1 (de) 2009-05-27 2010-12-16 Dst Dauermagnet-System Technik Gmbh Magnetkupplung sowie Spalttopf für eine Magnetkupplung

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2840137A1 (de) * 1978-09-15 1980-03-27 Lederle Pumpen & Maschf Pumpen-motor-aggregat, insbesondere fuer normpumpen-aggregate
DE9116052U1 (de) * 1991-12-24 1992-02-20 Pumpenbau G. Schulte, 4040 Neuss Pumpe für Flüssigkeiten niedriger Viskosität oder nahe dem Siedepunkt
EP0555173A1 (fr) * 1992-02-03 1993-08-11 A/S De Smithske Pompe
US5248245A (en) * 1992-11-02 1993-09-28 Ingersoll-Dresser Pump Company Magnetically coupled centrifugal pump with improved casting and lubrication
EP0814275B1 (fr) 1996-06-20 2003-06-04 Klaus Union GmbH & Co.KG Palier lisse hydrodynamique pour le rotor d'une pompe
DE102009022916A1 (de) 2009-05-27 2010-12-16 Dst Dauermagnet-System Technik Gmbh Magnetkupplung sowie Spalttopf für eine Magnetkupplung

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11590207B2 (en) 2016-09-29 2023-02-28 Ascendis Pharma Bone Diseases A/S Dosage regimen for a controlled-release PTH compound

Also Published As

Publication number Publication date
DE102011117182A1 (de) 2013-05-02

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