EP2677178B1 - Pompe - Google Patents

Pompe Download PDF

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Publication number
EP2677178B1
EP2677178B1 EP13171905.6A EP13171905A EP2677178B1 EP 2677178 B1 EP2677178 B1 EP 2677178B1 EP 13171905 A EP13171905 A EP 13171905A EP 2677178 B1 EP2677178 B1 EP 2677178B1
Authority
EP
European Patent Office
Prior art keywords
pump chamber
pump
ring section
impeller
radial width
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
EP13171905.6A
Other languages
German (de)
English (en)
Other versions
EP2677178A3 (fr
EP2677178A2 (fr
Inventor
Tobias Albert
Uwe Kögel
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.)
EGO Elektro Geratebau GmbH
Original Assignee
EGO Elektro Geratebau 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 EGO Elektro Geratebau GmbH filed Critical EGO Elektro Geratebau GmbH
Priority to PL13171905T priority Critical patent/PL2677178T3/pl
Publication of EP2677178A2 publication Critical patent/EP2677178A2/fr
Publication of EP2677178A3 publication Critical patent/EP2677178A3/fr
Application granted granted Critical
Publication of EP2677178B1 publication Critical patent/EP2677178B1/fr
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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/445—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
    • A47L15/00—Washing or rinsing machines for crockery or tableware
    • A47L15/42—Details
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47L—DOMESTIC WASHING OR CLEANING; SUCTION CLEANERS IN GENERAL
    • A47L15/00—Washing or rinsing machines for crockery or tableware
    • A47L15/42—Details
    • A47L15/4214—Water supply, recirculation or discharge arrangements; Devices therefor
    • A47L15/4225—Arrangements or adaption of recirculation or discharge pumps
    • D—TEXTILES; PAPER
    • D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F39/00—Details of washing machines not specific to a single type of machines covered by groups D06F9/00 - D06F27/00 
    • D06F39/08—Liquid supply or discharge arrangements
    • D—TEXTILES; PAPER
    • D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F39/00—Details of washing machines not specific to a single type of machines covered by groups D06F9/00 - D06F27/00 
    • D06F39/08—Liquid supply or discharge arrangements
    • D06F39/083—Liquid discharge or recirculation arrangements
    • D06F39/085—Arrangements or adaptations of 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially 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
    • F04D29/588—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps cooling or heating the machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2210/00—Working fluids
    • F05D2210/10—Kind or type
    • F05D2210/11—Kind or type liquid, i.e. incompressible

Definitions

  • the invention relates to a pump of the kind that can be used particularly well for household appliances such as dishwashers or washing machines, the pump being designed as a radial pump.
  • Such radial pumps are for example from the EP 2150165 A known. They have a pump chamber with a central suction and a pump chamber outlet, an impeller rotating in the pump chamber to move fluid from the suction in the radial direction out of the impeller into the pump chamber and, after several revolutions in the pump chamber, out of it via the pump chamber outlet . Outside the impeller or, so to speak, downstream of the impeller in the fluid path, a substantially circular ring-shaped pump chamber ring section is provided in the pump chamber, which extends in the axial direction of the pump, away from the impeller against the direction of suction into the pump, i.e. towards the pump chamber outlet extends.
  • the invention is based on the object of creating a pump mentioned at the beginning with which problems of the prior art can be solved and, in particular, a pump can be created which works efficiently and, above all, can pump out air present in the pump chamber at the start of the pumping process.
  • the pump has a pump chamber with a central suction and with a pump chamber outlet, an impeller rotating in the pump chamber to convey fluid or to discharge the fluid from the suction in a radial direction from the impeller into the pump chamber.
  • the discharged fluid is moved to the pump chamber outlet for circulation in the pump chamber, whereby it also flows in the axial direction of the pump from the impeller against the suction direction to the outlet or pump chamber outlet.
  • a circular ring-shaped and circumferential pump chamber ring section is provided as part of the pump chamber, the pump chamber ring section having an extension essentially along the axial direction of the pump.
  • the axial length of the pump chamber ring section is several times or four to ten times the radial width of the pump chamber ring section, specifically the maximum radial width of the pump chamber ring section. It is preferably about five to seven times the maximum radial width of the pump chamber ring section.
  • the invention provides that the pump chamber ring section has a width that varies in the direction of rotation and is designed to be narrower in a compression region.
  • a narrow width, in particular in the radial direction can be at least 20% or 30% of the largest width. In particular, however, it is less than 70%.
  • the pump chamber or the entire pump is designed without a guide wheel or no guide elements in the manner of a guide wheel or the like. having.
  • Such guide elements are those elements or components which protrude from the other walls in the pump chamber and extend into the fluid path for the special conduction or diversion of the pumped fluid. This can simplify the structure of the pump.
  • the narrower pump chamber ring section it was possible to show in tests that the efficiency of the pump can be improved even without guide elements.
  • the pressure in the pumped fluid can be changed or increased and the speed of circulation of the fluid can be increased for improved delivery.
  • this increase in pressure also means that air that has collected in the pump chamber is better removed or transported away.
  • the maximum air volume in the pump chamber is reduced here, as there is less space available, which also helps here.
  • the pump chamber ring section becomes gradually or continuously narrower in the direction of circulation of the pumped fluid towards the compression area, so that then a small width given along the direction of rotation is essentially over a certain length of the compression area is constant. This can be at least 20% to 30% of the circumference, preferably up to 40% or 50%. The width in the circumferential direction is then advantageously wider again, this being slower and over a can take place even greater length away than towards the compression area.
  • the radial width of the pump chamber ring section remains essentially the same over at least half of the axial length of the pump chamber ring section or the pump chamber itself, preferably a little more than two thirds thereof. This area is preferably located close to the pump chamber outlet or extends to it.
  • the pump chamber ring section can also be designed to be slightly widened in the direction of the impeller, in particular as a transition to the remaining pump chamber in the area of the impeller itself.
  • the pump chamber tapers monotonically outside the impeller with regard to its width in the radial direction, that is to say with regard to its cross-sectional area, in the axial direction away from the pump chamber base.
  • This taper is advantageously strictly monotonous. An expansion only takes place at the outlet, but then in the circumferential direction.
  • the pressure conditions can be designed advantageously for good conveyance and, at the same time, good heating of conveyed fluid or water.
  • the conveying speed of the fluid can be increased here for an adjustment with regard to the heat absorption by the heating device, since the fluid becomes increasingly warmer as it passes through the pump chamber.
  • a heating device can be integrated into the pump in order to heat the fluid conveyed by the pump. It can advantageously be provided that an external pump chamber wall as the external wall of the pump chamber ring section, and in some cases also of the other pump chamber, is heated or part of a heating device or is formed by this. This pump chamber wall then particularly advantageously takes up at least 75%, advantageously at least 90% or even essentially the entire axial length of the pump chamber ring section or the pump chamber. Such a heating device can then be designed essentially as a round cylinder or as a pipe section, that is to say also continuously and advantageously seamlessly in the circumferential direction.
  • a higher heating power can be introduced into the fluid or the heat absorption from the heating device can be improved due to the partially narrower pump chamber ring section and the resulting increase in the speed of the pumped fluid.
  • a lower cover plate of the impeller is curved in such a way that it is curved radially inward towards an aforementioned intake port that forms the intake, so to speak in the axial direction away from a pump chamber bottom.
  • the lower cover disk of the impeller is advantageously curved radially outwards in the same axial direction. This curvature may be weaker than that radially inward, but it can still be distinct.
  • the impeller rotates above the above-mentioned pump chamber floor in the pump chamber, the pump chamber floor advantageously also being curved radially outside the impeller with the continuation of the curvature of the lower cover disk of the impeller in the radially outer area.
  • the curvature of the impeller is continuous and uniform and continues essentially continuously and uniformly in the pump chamber floor.
  • the impeller or its lower cover plate can be let into the pump chamber floor somewhat.
  • the pump chamber bottom then extends close to the pump chamber ring section with a certain curvature up to or even up to this and thus guides the fluid discharged from the impeller at an oblique angle against the heated pump chamber ring section for heating.
  • the mentioned area of the minimum width or cross-sectional area of the pump chamber ring section is advantageously in an area of the pump chamber or the pump just behind the point where the outlet emerges from the pump housing.
  • the outlet from the pump chamber goes out advantageously in the area of the greatest width or largest cross-sectional area, i.e. the molded outlet in this area moves out of the otherwise existing shape of the pump chamber and is shaped out.
  • a pump 11 is shown with a pump housing 12, as it emerges from the prior art mentioned in principle.
  • the pump housing 12 has a pump chamber 14, into which a central, axial suction 15 leads, and from which an outlet 16 leads out in the tangential direction.
  • the intake 15 leads precisely to a centrally arranged impeller 18 with a lower cover disk 18a and an upper cover disk 18b.
  • the impeller 18 is driven by a pump motor 19 and runs over a pump chamber bottom 21 with a step-like central recess therein which is adapted to the lower cover disk 18a.
  • the radially outer wall of the pump chamber 14 is formed by a tubular heating device 23, as for example from the EP 2150165 B is known, namely as a metallic tube of constant diameter with straight cut ends.
  • a tubular heating device 23 as for example from the EP 2150165 B is known, namely as a metallic tube of constant diameter with straight cut ends.
  • heating elements are provided for the heating device 23, advantageously thick-film heating elements.
  • the heating device 23 is held in the lower area in a V seal 26a for sealing, the V seal 26a rotating radially outside the pump chamber base 21 and close to it.
  • a sealing ring 26b with a round cross section is provided on the outside of the heating device 23.
  • the heating device 23 is thus sealed off from the outside against the pump housing 12 and forms the outer wall towards the inside the pump chamber 14. How from Fig. 4 As can be seen, the heating device 23 is circular or has a circular cross-section.
  • the pump chamber 14 has, radially outside the impeller 18, at approximately the same axial height, a transition region which merges into a pump chamber ring section 28.
  • the pump chamber ring section 28 is defined essentially in the area where the pump chamber 14 has approximately the same width in the radial direction, which does not change or can also decrease in the axial direction.
  • the outer wall of the pump chamber ring section 28 is also formed by the heating device 23, the inner wall is formed by an inner wall 30 of the pump housing 12. It can be seen that on both sides in the axial direction slightly above the fluid outlet from the impeller 18, this inner wall 30 and the heating device 23 run approximately at the same distance from one another, the pump chamber ring section 28 thus approximately the same width or also decreasing width in the axial direction Has direction.
  • the pump chamber ring section 28 now has approximately the same width or the same cross-section in the axial direction, or else a decreasing width, although the width varies in the circumferential direction, as shown in the sectional illustration in FIG Fig. 4 can be seen.
  • a section through the pump 11 is shown in which a width 29a of the pump chamber ring section 28 is approximately greatest at the top, while a width 29c is approximately minimal at the bottom right.
  • the sectional view according to CC of Fig. 4 shows this, and there is the sectioned longitudinal view of the Fig. 1 is shown as section AA.
  • Fig. 2 is to say that it is in the cut plan view of the Fig. 4 according to section BB shows an area in which the minimum width 29c is again present on the right in the case of the pump chamber ring section 28.
  • a mean width 29b is given on the left, which in FIG Fig. 4 is also shown.
  • the Fig. 3 shows a plan view of the pump 11 with the pump housing 12 including suction 15 and outlet 16, which merges into an outlet connection 17. More interesting, however, is the one pictured directly below Fig. 4 according to section CC of Fig. 1 , with the outlet 16 and outlet nozzle 17 still being shown in dashed lines. It can be seen that the heating device 23 runs coaxially to the intake 15 as the outer wall of the pump chamber 14.
  • the width of the pump chamber ring section 28, however, is determined by the differently extending inner wall 30. Approximately shown are the width 29a, which is approximately maximum, the middle width 29b and the smallest or narrow width 29c.
  • This narrow width 29c extends over an arc angle of approximately 120 ° to just before an electrical connection plug 24 which is arranged on the outside of the heating device 23. From here on, the width of the pump chamber ring section 28 expands again continuously over the middle width 29b up to the maximum width 29a. This maximum width 29a is approximately where the outlet 16 with the tube-like outlet connector 17 is separated from the pump chamber 14 or the pump chamber ring section 28 itself, which is approximately at section AA. From this area, the width tapers again with a taper 32 up to the taper end 32 ', where the smallest or narrow width 29c then begins again. The taper 32 extends over a range of approximately 70 °.
  • the width of the pump chamber ring section 28 is determined on the outside by the annular heating device 23 and on the inside by the inner wall 30.
  • the inner wall 30 of the pump chamber 14 or of the pump chamber ring section 28 is circular and concentric to the axis of rotation of the impeller 18 or to the longitudinal center axis of the suction 15.
  • the outside surrounding outer wall in particular also in the form of a heating device, is non-concentric in such a way that it is offset from this, so to speak, or is just non-circular.
  • the two walls could also be non-concentric to one another or to the longitudinal center axis of the pump.
  • the pump chamber ring section 28 has the same width or also a decreasing width over a certain axial length. At the same time, however, it should be noted that the increased width of the pump chamber ring section 28 is also present in the area radially outside of the impeller 18 and at its axial height. It is precisely in this way that the improved ventilation can be achieved.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Textile Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Water Supply & Treatment (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (10)

  1. Pompe (11), en particulier pour appareils ménagers tels que des lave-vaisselles ou des machines à laver, qui est réalisée sous forme de pompe radiale, avec une chambre de pompe (14) avec une aspiration centrale (15) et avec une sortie de chambre de pompe (16), une roue à aubes (18) tournant dans la chambre de pompe pour refouler du fluide et pour distribuer le fluide par l'aspiration dans la direction radiale hors de la roue à aubes (18) dans la chambre de pompe (14), le fluide distribué étant déplacé de manière à circuler dans la chambre de pompe jusqu'à la sortie de la chambre de pompe (16), une portion annulaire de chambre de pompe de forme annulaire circulaire et périphérique (28) étant prévue radialement à l'extérieur de la roue à aubes, en tant que partie de la chambre de pompe, la portion annulaire de chambre de pompe présentant essentiellement une étendue le long de la direction axiale de la pompe (11) à partir de la roue à aubes (18) dans le sens opposé à la direction d'aspiration jusqu'à la sortie de chambre de pompe (16), la longueur axiale de la portion annulaire de chambre de pompe étant quatre à dix fois plus grande que sa largeur radiale maximale (29a), caractérisée en ce que la portion annulaire de chambre de pompe (28) présente une largeur radiale variable (29a-c) et est réalisée de manière plus étroite dans la direction périphérique dans une région de compression (29c), la chambre de pompe (14) étant réalisée sans stator et ne présentant pas d'élément directeur à la manière d'un stator.
  2. Pompe selon la revendication 1, caractérisée en ce que la portion annulaire de chambre de pompe (28) est de plus en plus étroite de manière progressive ou continue dans la direction périphérique vers la région de compression (29c), en particulier sur une faible largeur radiale constante de la région de compression (29c), donnée sur une certaine longueur le long de la direction périphérique, et de préférence s'élargissant à nouveau dans la direction périphérique.
  3. Pompe selon la revendication 1 ou 2, caractérisée en ce que la largeur radiale dans la région de compression (29c) vaut au moins 20 % de la largeur radiale maximale (29a) de la portion annulaire de chambre de pompe (28), de préférence au moins 30 %, et en particulier moins de 70 %.
  4. Pompe selon l'une quelconque des revendications précédentes, caractérisée en ce que la portion annulaire de chambre de pompe (28) présente sur au moins 20 % de sa longueur ou d'une périphérie, la même faible largeur radiale constante (29c), de préférence inférieure à 50 %.
  5. Pompe selon l'une quelconque des revendications précédentes, caractérisée en ce que l'augmentation de la largeur radiale (29a-c) de la portion annulaire de chambre de pompe (28) dans la direction périphérique à l'écart de la région de compression (29c) est moins forte ou a lieu plus lentement que la diminution de la largeur radiale dans la direction périphérique vers la région de compression (29c).
  6. Pompe selon l'une quelconque des revendications précédentes, caractérisée en ce que dans la direction axiale de la pompe (11), la largeur radiale (29a-c) ou la section transversale de la portion annulaire de chambre de pompe (28) reste essentiellement uniforme, en particulier dans la région de la portion annulaire de chambre de pompe éloignée de la roue à aubes (18) dans la direction axiale, de préférence à proximité de la sortie de la chambre de pompe (16).
  7. Pompe selon l'une quelconque des revendications précédentes, caractérisée en ce que la chambre de pompe (14) se rétrécit de manière monotone dans la direction radiale à l'extérieur de la roue à aubes (18), de préférence se rétrécit de manière fortement monotone.
  8. Pompe selon l'une quelconque des revendications précédentes, caractérisée en ce qu'elle présente un dispositif de chauffage intégré (23) pour chauffer le fluide refoulé.
  9. Pompe selon la revendication 8, caractérisée en ce qu'une paroi de chambre de pompe située à l'extérieur est chauffée en tant que paroi extérieure de la portion annulaire de chambre de pompe (28) ou fait partie du dispositif de chauffage (23) et en particulier cette paroi de chambre de pompe occupe toute la longueur axiale de la portion annulaire de chambre de pompe, de préférence de toute la chambre de pompe (14).
  10. Pompe selon l'une quelconque des revendications précédentes, caractérisée en ce qu'un disque de recouvrement inférieur (18a) de la roue à aubes (18) est courbé de telle sorte qu'il soit courbé radialement vers l'intérieur vers une tubulure d'aspiration (17) en tant qu'aspiration (15), et de préférence radialement vers l'extérieur dans la même direction axiale, la chambre de pompe (14) présentant un fond de chambre de pompe (21) sur lequel tourne la roue à aubes (18), le fond de chambre de pompe étant courbé radialement à l'extérieur de la roue à aubes en se poursuivant de manière à correspondre approximativement à la courbure du disque de recouvrement inférieur (18a) et en l'occurrence se prolongeant dans une paroi extérieure de la chambre de pompe ou de la portion annulaire suivante de chambre de pompe (28).
EP13171905.6A 2012-06-22 2013-06-13 Pompe Active EP2677178B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL13171905T PL2677178T3 (pl) 2012-06-22 2013-06-13 Pompa

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201210210554 DE102012210554A1 (de) 2012-06-22 2012-06-22 Pumpe

Publications (3)

Publication Number Publication Date
EP2677178A2 EP2677178A2 (fr) 2013-12-25
EP2677178A3 EP2677178A3 (fr) 2015-04-22
EP2677178B1 true EP2677178B1 (fr) 2020-10-07

Family

ID=48578954

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13171905.6A Active EP2677178B1 (fr) 2012-06-22 2013-06-13 Pompe

Country Status (7)

Country Link
US (1) US9470242B2 (fr)
EP (1) EP2677178B1 (fr)
KR (1) KR20140000154A (fr)
CN (1) CN103511349A (fr)
DE (1) DE102012210554A1 (fr)
ES (1) ES2835185T3 (fr)
PL (1) PL2677178T3 (fr)

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DE102013200280A1 (de) 2013-01-10 2014-07-10 E.G.O. Elektro-Gerätebau GmbH Impellerpumpe
DE102013211180A1 (de) 2013-06-14 2014-12-18 E.G.O. Elektro-Gerätebau GmbH Pumpe
DE102014219891A1 (de) 2014-10-01 2016-04-07 E.G.O. Elektro-Gerätebau GmbH Pumpe und Haushaltsgerät mit einer Pumpe
DE102015206928B4 (de) 2015-04-16 2017-03-09 E.G.O. Elektro-Gerätebau GmbH Heizvorrichtung und Kraftfahrzeug
CN105570144B (zh) * 2015-12-17 2018-03-23 广东威灵电机制造有限公司 离心泵和用于离心泵的导流件
DE102016201975B3 (de) * 2016-02-10 2017-03-02 BSH Hausgeräte GmbH Wäschepflegegerät mit einer Pumpe
DE102016208020A1 (de) * 2016-05-10 2017-11-16 BSH Hausgeräte GmbH Flüssigkeitsheizpumpe zum Fördern und Aufheizen von Flüssigkeit in einem wasserführenden Haushaltsgerät
CN110857692B (zh) * 2018-08-23 2022-02-15 三花亚威科电器设备（芜湖）有限公司 泵
CN110107504B (zh) * 2019-05-20 2021-11-19 佛山市顺德区美的洗涤电器制造有限公司 加热泵和洗碗机
CN112797003B (zh) * 2019-11-13 2022-03-22 广东美的白色家电技术创新中心有限公司 集热泵
CN113513481A (zh) * 2020-04-10 2021-10-19 佛山市百斯特电器科技有限公司 一种集热泵及其洗碗机
PL3901466T3 (pl) 2020-04-24 2024-03-18 E.G.O. Elektro-Gerätebau GmbH Sposób eksploatacji pompy
DE102020129084A1 (de) 2020-10-23 2022-04-28 Ebm-Papst Mulfingen Gmbh & Co. Kg Rohrventilator
EP4130489A1 (fr) * 2021-08-03 2023-02-08 Bleckmann GmbH & Co. KG Douille de pression pour pompe à fluide et pompe comprenant la douille de pression
US11852162B2 (en) * 2021-12-17 2023-12-26 Robert Bosch Llc Centrifugal pump assembly

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Publication number Publication date
US9470242B2 (en) 2016-10-18
CN103511349A (zh) 2014-01-15
US20130343882A1 (en) 2013-12-26
DE102012210554A1 (de) 2013-12-24
PL2677178T3 (pl) 2021-04-19
EP2677178A3 (fr) 2015-04-22
EP2677178A2 (fr) 2013-12-25
ES2835185T3 (es) 2021-06-22
KR20140000154A (ko) 2014-01-02

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