EP2994642B1 - Pumpenanordnung - Google Patents

Pumpenanordnung Download PDF

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Publication number
EP2994642B1
EP2994642B1 EP14720596.7A EP14720596A EP2994642B1 EP 2994642 B1 EP2994642 B1 EP 2994642B1 EP 14720596 A EP14720596 A EP 14720596A EP 2994642 B1 EP2994642 B1 EP 2994642B1
Authority
EP
European Patent Office
Prior art keywords
impeller
pump arrangement
arrangement according
auxiliary
channels
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
EP14720596.7A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2994642A1 (de
Inventor
Patrick Drechsel
Jörg Engelbrecht
Jürgen Gröschel
Christoph Jäger
Markus Lay
Wolfram Wetzel
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.)
KSB SE and Co KGaA
Original Assignee
KSB SE and Co KGaA
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 KSB SE and Co KGaA filed Critical KSB SE and Co KGaA
Publication of EP2994642A1 publication Critical patent/EP2994642A1/de
Application granted granted Critical
Publication of EP2994642B1 publication Critical patent/EP2994642B1/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
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0606—Canned motor pumps
    • F04D13/0626—Details of the can
    • 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
    • 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
    • F04D13/025—Details of the can separating the pump and drive area
    • 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
    • F04D29/06—Lubrication
    • F04D29/061—Lubrication 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F04D29/5866—Cooling at last part of the working fluid in a heat exchanger
    • F04D29/5873—Cooling at last part of the working fluid in a heat exchanger flow schemes and regulation thereto
    • 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

  • the invention relates to a pump arrangement, in particular magnetic coupling pump arrangement, with a formed by a pump housing of the pump assembly interior, a bottom having a containment shell which hermetically seals a chamber enclosed by him against the interior formed by the pump housing, a rotatable about an axis rotatable impeller shaft, an an impeller arranged at one end of the impeller shaft, an inner rotor disposed at the other end of the impeller shaft, an auxiliary impeller disposed in the chamber, and an outer rotor cooperating with the inner rotor.
  • the US 4,850,818 A shows a magnetic coupling pump with a formed as an inner rotor magnetic holding element.
  • the magnet holding element is provided with blades on the front side, along its outer edge, in order to ensure a low liquid pressure behind the end face of the magnetic element.
  • the object of the invention is to provide a magnetic coupling pump assembly with an easy to manufacture forced lubrication current drive with improved efficiency.
  • the object of the invention is achieved in that the auxiliary wheel of semi-open design and is fixed with its open side on the bottom of the gap pot facing end side of the inner rotor.
  • the auxiliary impeller is attached with its open side to the bottom of the gap pot facing end side of the inner rotor, it is possible to use the advantages of a closed channel wheel by a much easier to manufacture open impeller.
  • the impeller has no hub and is easy to assemble and disassemble.
  • the containment shell has a base body with an open side and an open side opposite by means of a curved bottom closed side and the Hilfsmoorrad has a support plate whose facing the bottom of the gap pot outer surface has a curvature.
  • the curvature of the outer surface of the support disc substantially corresponds to the curvature of the bottom of the can, the dead space usually spanned by the curved bottom of the can is filled, whereby no additional required by the magnetic coupling axial space is used up.
  • the pressure resistance of the split pans is not unnecessarily reduced.
  • a paraboloid-like elevation is ideally provided in the middle of the support disk.
  • a plurality of elevations are formed on the support disk with a radial distance to the elevation, which form blades and corresponding impeller channels of the auxiliary impeller.
  • the impeller ducts have a channel bottom, which is similar to a einhsymmetricigen basket bow. This leads to an improvement of the flow guidance.
  • the upper side of the blades facing away from the support disk has a step near the channel entry edge.
  • the stage serves as an abutment shoulder and centering device for exact alignment of the attached to the inner rotor auxiliary wheel.
  • the impeller shaft and the inner rotor form a cover disk of the auxiliary wheel opposite the support disk.
  • impeller passages are formed in the elevations forming the blades, which impeller extend in the radial direction from the outer circumferential surface to near the step.
  • the further impeller channels have a channel bottom, which at least partially has a curvature which substantially corresponds to the curvature of the outer surface of the carrier disk.
  • the impeller shaft has an axial passage which communicates with the fluid inlet region of the auxiliary impeller.
  • fluid channels are provided in the inner rotor, which open into the other impeller channels of the auxiliary rotor.
  • the Fig. 1 and 2 show a pump assembly 1 in the form of a magnetic coupling pump assembly.
  • the pump arrangement 1 has a multipart pump housing 2 of a centrifugal pump, which comprises a hydraulic housing 3 designed as a spiral housing, a housing cover 4, a bearing support lantern 5, a bearing support 6 and a bearing cover 7.
  • the hydraulic housing 3 has an inlet opening 8 for sucking in a conveyed medium and an outlet opening 9 for ejecting the conveyed medium.
  • the housing cover 4 is arranged at the inlet opening 8 opposite side of the hydraulic housing 3.
  • the bearing carrier 6 is attached to the housing cover 4 opposite side of the bearing support lantern 5.
  • the bearing cap 7 is in turn secured to the side facing away from the bearing support lantern 5 side of the bearing support 6.
  • a split pot 10 is attached to the side facing away from the hydraulic housing 3 side of the housing cover 4 and extends at least partially by a pump housing 2, in particular from the housing cover 4, from the bearing support lantern 5 and the bearing support 6 limited interior 11.
  • the containment shell 10 seals one of hermetically sealed to him and the housing cover 4 chamber 12 from the interior 11 from.
  • a impeller shaft 13 extends from a limited by means of the hydraulic housing 3 and the housing cover 4 flow chamber 14 through an opening provided in the housing cover 4 opening 15 into the chamber 12th
  • An impeller 16 is fastened to a shaft end of the impeller shaft 13 located within the flow chamber 14, an inner rotor 17 arranged inside the chamber 12 is arranged at the opposite end of the shaft, which has two shaft sections 13a, 13b with increasing diameters.
  • the inner rotor 17 is equipped with a plurality of magnets 18, which are arranged on the side of the inner rotor 17 facing the gap pot 10.
  • an auxiliary wheel 20 is fastened by means of screws 19 or other suitable fastening means.
  • a bearing assembly 21 operatively connected to the impeller shaft 13 which is rotatably driven about the rotation axis A is arranged.
  • An unillustrated drive motor preferably an electric motor, drives a drive shaft 22.
  • the drivable about the axis of rotation A drive shaft 22 is arranged substantially coaxially with the impeller shaft 13.
  • the drive shaft 22 extends through the bearing cap 7, the bearing support 6 and at least partially into the bearing support lantern 5.
  • the drive shaft 22 is mounted in two housed in the bearing support 6 ball bearings 23, 24.
  • a plurality of magnets 25-bearing outer rotor 26 is arranged.
  • the magnets 25 are arranged on the side of the outer rotor 26 facing the containment shell 10.
  • the outer rotor 26 extends at least partially over the containment shell 10 and cooperates with the inner rotor 17, such that the rotating outer rotor 26 by means of magnetic forces the inner rotor 17 and thus the impeller shaft 13 and the impeller 16 also set in a rotational movement.
  • the Indian Fig. 3 Enlarged pot 10 shown has a substantially cylindrical body 27.
  • the main body 27 is open at the side facing the housing cover 4 and closed at the side opposite the open side by means of a curved bottom 28.
  • a ring-like connection flange 29 is arranged, which is integrally formed with the base body 27 or fixed thereto by welding or other suitable fastening means or devices, such as screws, rivets or the like.
  • the connecting flange 29 has a plurality of bores 30 extending parallel to the axis of rotation A, through which screws 31 can be inserted and screwed into corresponding threaded bores in the housing cover 4.
  • the bottom 28 of the split pot 10 is formed by a substantially spherical segment-shaped dome region 32 and an outer, the transition region between the base body 27 and dome region 32 forming rim region 33.
  • the auxiliary wheel 20 has a support plate 34, the bottom 28 of the gap pot 10 facing outer surface has a curvature.
  • the curvature of the outer surface of the support plate 34 substantially corresponds to the curvature of the bottom 28 of the can 10 in the middle of the support plate 34 is a paraboloid-like elevation 35 in a fluid inlet region 36 is provided.
  • a plurality of elevations are formed on the support disk 34 with a radial distance to the elevation 35, which blades 37 form a channel inlet edge 38 facing the elevation 35 and corresponding impeller ducts 39 of the auxiliary impeller 20.
  • the elevation 35 contributes to an improvement in the flow guidance of the medium when it enters the impeller channels 39 of the auxiliary impeller 20.
  • the blades 37 extend curved from the fluid inlet region 36 to an outer circumferential surface 40 of the auxiliary rotor 20.
  • the impeller channels 39 have a channel bottom 41, which in turn has a curved shape which substantially corresponds to the curvature of the outer surface of the support disk 34.
  • the channel bottom 41 the impeller channels 39 is formed in the longitudinal section shown similar to a einhsymmetricigen basket bow, as in the Fig. 6 shown.
  • the impeller channels 39 have a first width W1 at the fluid inlet region 36 and a second width W2 at the outer lateral surface 40, wherein the second width W2 is greater than the first width W1 or at least the first width W1.
  • the support disk 34 facing away from the top of the blades 37 has near the channel inlet edge 38, a step 42 which serves as a contact shoulder and centering device for the attached to the inner rotor 17 auxiliary impeller 20.
  • a step 42 which serves as a contact shoulder and centering device for the attached to the inner rotor 17 auxiliary impeller 20.
  • Due to its semi-open design the auxiliary wheel 20 is both casting technology, as easy to demold, as well as by mechanical processing, since the impeller channels are easily ausfräsbar, easy to manufacture.
  • each blade 37 preferably has at least one recess 45. This generates an additional pressure increase.
  • At least one passage openings 46 are provided in the housing cover 4 and at least one radial passage opening 48 is provided in a bearing ring carrier 47 which fixes the bearing arrangement 21.
  • the through-opening 48 extends through a flange-like region 49 with which the bearing ring carrier 47 positioned coaxially with the axis of rotation A and extending into the chamber 12 is fastened to the housing cover 4 by means of a screw connection, not shown.
  • the passage openings 46 and 48 connect the flow chamber 14 with an inner region 50 of the bearing ring carrier 47th
  • fluid may be withdrawn from the flow chamber 14 and supplied to the bearing assembly 21 via the ports 46 and 48, respectively.
  • the conveying medium is conveyed from the inner region 50 into an axial passage 52 which extends from a region of the impeller shaft 13 which is surrounded by the bearing assembly 21 to the end of the impeller shaft 13 located within the chamber 12 and thus to the auxiliary impeller 20 extends.
  • the axial channel 52 is thus in communication with the fluid inlet region 36 of the auxiliary impeller 20.
  • at least one further radial bore 53 is formed, which is also in communication with the axial passage 52 formed in the impeller shaft 13.
  • the auxiliary wheel 20 promotes the medium used for cooling and lubrication radially outward into the chamber 12, from where it has several in the Fig. 1 shown axial through holes 54 formed in the flange-like region 49 and in the housing cover 4 formed through holes 55 is conveyed back into the flow chamber 14.
  • the Fig. 5 to 8 show a further embodiment of the invention. That in the Fig. 5 Auxiliary impeller 20 shown in detail has blades 37 formed by elevations on the support disk 34, which impeller channels 39 define radially outwardly extending from the fluid inlet region 36. In the exemplary embodiment shown, the blades 37 extend in a straight line from the fluid inlet region 36 to the outer lateral surface 40 of the auxiliary impeller 20.
  • the impeller channels 39 have a first width W1 at the fluid inlet region 36 and a second width W2 at the outer lateral surface 40, the second width W2 being greater as the first width W1 or at least the first width W1 corresponds.
  • impeller channels 56 are formed, which also extend in the radial direction also substantially straight, ie without or without significant curvature, from the outer surface 40 to close to the level 42 and have a channel bottom 57, at least partially a vault which substantially corresponds to the curvature of the outer surface of the support plate 34.
  • the channel bottom 57 of the impeller 56 is formed in a longitudinal section similar to a einhsymmetricigen basket bow, as in the Fig. 7 shown.
  • the impeller passages 56 extend from the region 42 adjacent the step to the outer skirt surface 40 and have a first width W3 at a fluid inlet region 56a and a second width W4 at the outer lateral surface 40, the second width W4 being greater than the first width W3 or at least the first width W3 corresponds.
  • the Fig. 6 to 8 show a pump assembly 1, which with a according to the Fig. 5 shown auxiliary impeller 20 is equipped.
  • the view of Fig. 6 and 7 correspond to the view of Fig. 1
  • the view of Fig. 8 corresponds to the view of Fig. 2
  • the at least one radial bore 53 leads into one in comparison to the Fig. 1 and 2
  • the bearing ring carrier 47 has fluid channels 58 running parallel to the axis of rotation A, which connect the inner region 50 of the bearing ring carrier 47 with the chamber 12 enclosed by the gap pot 10 and the housing cover 4.
  • the Fig. 7 shows the in the Fig. 6
  • fluid channels 59 are provided, which are arranged at approximately the same radial distance from the axis of rotation A, as the fluid channels 58 of the bearing ring carrier 47 and thus, at least in the position shown, with these lie substantially in alignment.
  • the fluid channels 59 open into the impeller channels 56 of the at the bottom 28 of the gap pot 10 facing end face of the inner rotor 17 arranged auxiliary impeller 20th
  • the auxiliary impeller 20 is shown with either the impeller ducts 39 or the impeller ducts 39 and the impeller ducts 56. It is understood that the auxiliary impeller 20 may also be provided exclusively with the impeller channels 56.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP14720596.7A 2013-05-08 2014-04-29 Pumpenanordnung Active EP2994642B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013007849.0A DE102013007849A1 (de) 2013-05-08 2013-05-08 Pumpenanordnung
PCT/EP2014/058706 WO2014180712A1 (de) 2013-05-08 2014-04-29 Pumpenanordnung

Publications (2)

Publication Number Publication Date
EP2994642A1 EP2994642A1 (de) 2016-03-16
EP2994642B1 true EP2994642B1 (de) 2019-11-27

Family

ID=50628816

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14720596.7A Active EP2994642B1 (de) 2013-05-08 2014-04-29 Pumpenanordnung

Country Status (16)

Country Link
US (1) US10288073B2 (ko)
EP (1) EP2994642B1 (ko)
JP (1) JP6411468B2 (ko)
KR (1) KR102079724B1 (ko)
CN (1) CN105452669B (ko)
AU (1) AU2014264829B2 (ko)
BR (1) BR112015027900B1 (ko)
DE (1) DE102013007849A1 (ko)
DK (1) DK2994642T3 (ko)
ES (1) ES2773278T3 (ko)
HU (1) HUE048740T2 (ko)
MX (1) MX2015015299A (ko)
RU (1) RU2679070C2 (ko)
SG (1) SG11201508905RA (ko)
WO (1) WO2014180712A1 (ko)
ZA (1) ZA201508073B (ko)

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KR20160118612A (ko) * 2015-04-02 2016-10-12 현대자동차주식회사 전동식 워터 펌프
AU2016259326B2 (en) * 2015-11-17 2021-02-11 Cornell Pump Company LLC Pump with front deflector vanes, wear plate, and impeller with pump-out vanes
MX2019004713A (es) 2016-11-01 2019-12-11 Psg Worldwide Inc Bomba centrifuga sin selladura, magneticamente acoplada.
US10240600B2 (en) 2017-04-26 2019-03-26 Wilden Pump And Engineering Llc Magnetically engaged pump
DE102019002392A1 (de) 2019-04-02 2020-10-08 KSB SE & Co. KGaA Wärmesperre
DE102019002797A1 (de) * 2019-04-17 2020-10-22 KSB SE & Co. KGaA Spalttopf
CN111156174B (zh) * 2019-12-31 2021-04-13 六安市中盛泵阀制造有限公司 一种多功能磁力泵
RU199022U1 (ru) * 2020-05-07 2020-08-07 Открытое акционерное общество "Пензенский завод компрессорного машиностроения" (ОАО "Пензкомпрессормаш") Насос вертикальный герметичный
DE102021133447A1 (de) 2020-12-17 2022-06-23 KSB SE & Co. KGaA Magnetkupplungspumpenanordnung
WO2022129463A1 (de) 2020-12-17 2022-06-23 KSB SE & Co. KGaA Magnetkupplungspumpenanordnung

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Also Published As

Publication number Publication date
RU2015148039A3 (ko) 2018-03-02
SG11201508905RA (en) 2015-11-27
KR102079724B1 (ko) 2020-04-03
HUE048740T2 (hu) 2020-08-28
BR112015027900A8 (pt) 2018-07-31
BR112015027900B1 (pt) 2022-03-15
JP2016518551A (ja) 2016-06-23
MX2015015299A (es) 2016-02-18
DK2994642T3 (da) 2020-02-17
EP2994642A1 (de) 2016-03-16
JP6411468B2 (ja) 2018-10-24
CN105452669B (zh) 2019-03-29
BR112015027900A2 (ko) 2017-05-09
DE102013007849A1 (de) 2014-11-13
WO2014180712A1 (de) 2014-11-13
US10288073B2 (en) 2019-05-14
CN105452669A (zh) 2016-03-30
ZA201508073B (en) 2016-10-26
RU2679070C2 (ru) 2019-02-05
US20160084256A1 (en) 2016-03-24
KR20160005090A (ko) 2016-01-13
AU2014264829A1 (en) 2015-11-12
RU2015148039A (ru) 2017-06-14
ES2773278T3 (es) 2020-07-10
AU2014264829B2 (en) 2017-04-20

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