EP2275017B1 - Lave-vaisselle doté d'une pompe de recirculation - Google Patents

Lave-vaisselle doté d'une pompe de recirculation Download PDF

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Publication number
EP2275017B1
EP2275017B1 EP10168100.5A EP10168100A EP2275017B1 EP 2275017 B1 EP2275017 B1 EP 2275017B1 EP 10168100 A EP10168100 A EP 10168100A EP 2275017 B1 EP2275017 B1 EP 2275017B1
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EP
European Patent Office
Prior art keywords
impeller
dishwasher
thrust ring
region
sliding
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
EP10168100.5A
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German (de)
English (en)
Other versions
EP2275017A2 (fr
EP2275017A3 (fr
Inventor
Stephan Lutz
Hans-Holger Pertermann
Bruno Reiter
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.)
BSH Hausgeraete GmbH
Original Assignee
BSH Hausgeraete 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
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Priority to PL10168100T priority Critical patent/PL2275017T3/pl
Publication of EP2275017A2 publication Critical patent/EP2275017A2/fr
Publication of EP2275017A3 publication Critical patent/EP2275017A3/fr
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Publication of EP2275017B1 publication Critical patent/EP2275017B1/fr
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Classifications

    • 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
    • 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
    • F04D29/0473—Bearings hydrostatic; hydrodynamic for radial 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
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
    • F04D29/167—Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal flow wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/18—Rotors
    • F04D29/22—Rotors specially for centrifugal pumps
    • F04D29/2261—Rotors specially for centrifugal pumps with special measures
    • F04D29/2266—Rotors specially for centrifugal pumps with special measures for sealing or thrust balance

Definitions

  • the invention relates to a dishwasher, in particular a domestic dishwasher, with a washing compartment for receiving dishes, cutlery or similar objects to be cleaned, wherein the washing compartment via at least one circulating pump water is supplied and wherein the circulating pump comprises a fixed, centrally on a rotatable impeller inlet channel , according to the preamble of claim 1.
  • the marginal gap through which the backflow takes place can not be arbitrarily reduced, otherwise it could come to a contact between the rapidly rotating impeller and a fixed housing part. This is even more so, as in the operation of such a pump forcibly the impeller is subjected to an axial force in the direction of the intake passage, since a negative pressure is generated in front of the radial or centrifugal pump. Therefore, for the rotary impeller usually provides an axially retaining bearing on the axis or shaft of its rotation, which is complicated and expensive.
  • the DE 20 2005 020 138 U1 proposes to improve the seal and thus reduce the backflow before firmly provide a thrust washer on the impeller and there in addition to keep a sliding ring so movable that it is pulled axially against the run-up ring during operation.
  • the mounting of such a sliding ring is problematic, in particular, since in the case of impellers produced by injection molding, large tolerances occur and thus the axial travel available for the sliding ring varies. The requirements for the exact axial bearing of the impeller are thus rather increased.
  • the EP 0 221 300 A1 proposes to provide on one side of the housing angular split rings on the outer edges and the inner edges of wings of the impeller facing the steps of the housing. This, however, results in increased wear of the impeller areas sliding along the angular gap rings. These are also far radially outward, so that there is a very high peripheral speed, which increases the wear even more.
  • the FR-A-2911166 shows at the front end of the impeller of a pump, a sealing system by axially abutting parts. This should improve the tightness of the solenoid drive pump from the side of the stopper. A main bearing, however, remains necessary to intercept the forces of the rotating impeller in each case.
  • the invention is based on the problem to provide an efficient and inexpensive pump.
  • the impeller is mounted at its radially inner region, in particular its hub, opposite the intake channel and not only sealed. Due to the fact that one or more reinforced sliding regions or thrust rings are assigned to both the impeller and the pipe region delimiting the intake duct or a separate sleeve, the wear between their contact zones is not increased inadmissibly.
  • the radially far inward position of the one or more sliding regions, in particular on the suction-side end edge of the radially inner hub of the impeller is also favorable insofar as the peripheral speeds are low there, which further reduces wear and the large tolerances, in particular itself affect the far outward wings of the impeller, makes independent.
  • the storage function for the impeller form the sliding portion of the impeller and the thrust ring in its expiration successive in a double function and a sealing system against return of water in the intake and thereby significantly increase the efficiency of the pump.
  • the sliding region on the suction-side edge, preferably on the suction-side end, the radially inner hub of the impeller, preferably the Ansaugmunds, or at its centrally arranged, against the suction direction of the pump protruding cover plate is provided.
  • the centrally arranged hub of the impeller are arranged distributed in the circumferential direction a plurality of blades or blades, in particular integrally formed. These extend radially outward and, viewed in the suction direction of the impeller, have a, in particular convex, bend or curvature.
  • the respective wing is composed of an inner, substantially three-dimensionally bent, curved section and an outer, essentially two-dimensionally bent, curved section. It may be provided on the suction side and / or pressure side, if necessary, a cover plate on the hub of the impeller.
  • the sliding region of the impeller and the housing-fixed thrust ring can form not only an axial but also a radial bearing for the impeller, for example by being angled.
  • the sliding region and / or the thrust ring can be formed by, in particular separate, annular bodies by means of the impeller or the intake channel, so that they can also have an optimized surface hardness and structure for forming a water sliding film, for example through grooves. Also, an exchange of these parts may possibly be possible.
  • the sliding region and / or the thrust ring are formed by at least one reinforcement incorporated in the impeller or the suction channel, such as coal particles.
  • Such an integral sliding area can for example also be injected or by a 2K method be integrally formed on the impeller and / or a suction channel surrounding the tube area, so that the number of components and the assembly costs are minimized.
  • a sliding-reducing coating such as eg by Teflon, is possible in both cases.
  • the sliding region on the suction-side end edge of the impeller and the contact region of the stop ring facing this end edge can be provided merely with a sliding-reducing, abrasion-resistant coating.
  • a dishwasher according to the invention can form a standalone or a built-in or installable device, such as within a kitchenette.
  • Dishwasher 1 shown schematically is a domestic dishwasher with a washing container 22, which has a washing compartment 2 for receiving and cleaning of crockery, cutlery, cooking utensils or the like.
  • the flushing chamber 2 is here substantially cuboidal and delimited at five of its six outer surfaces of walls 3 of the washing container 22 and to the front of a door 4, which is hinged here only by way of example in its lower part pivotally mounted on a housing of the dishwasher 1.
  • one or more rotatable spray arms (not shown) for the distribution of possibly mixed with detergent rinse water and a plurality of receiving baskets 5 may be held.
  • the rinsing water can run through recesses in the ground in a circulating system in which at least one circulating pump 6 with a rapidly rotating - typically in the order of 2000 to 3500 revolutions per minute - impeller 7 is arranged.
  • FIG. 2 illustrated circulating pump 6s according to the prior art there is the rotatable about the axis 8s impeller 7s against an axle 9s axially mounted on a separate bearing 10s and thereby prevented from axial movement.
  • the circulating pump 6s conveys a rinsing water main stream HS radially outward into at least one discharge channel with the blades of its rotating impeller FIG. 2 has been omitted for clarity.
  • the axial bearing 10s is seated in the axial direction of the axle body 9s or viewed in the suction direction of the pump between the impeller 7s and the rotor 13s of the drive machine.
  • a relatively large edge gap 12s remains between the impeller 7s and the intake passage 11s, which extends both in the axial and in the radial direction, as compared to an exit-side mouth region of the intake passage 11s. It typically has an axial extent of two to three Millimeters and a radial extent of one to two millimeters. It must not be made substantially smaller, since the impellers 7s often produced by injection molding have a large tolerance up to approximately one millimeter and the tolerances can add up.
  • FIG. 3 an advantageous embodiment of the inventive construction of a circulating pump 6 is shown, which in turn is provided with an impeller designed as impeller 7. On its axis of rotation 8 leads centrally a suction channel 11, which promotes the pump to be pumped water in the drawing from the left to.
  • the inlet-side intake channel 11 of the circulation pump 6 is bounded by a pipe region 12.
  • This has here in the embodiment at its output-side area, which faces the front edge or Ansaugmund the radially inner hub of the impeller 7, a step or recess 141, in which a completely closed, ie all around running stop ring 14 fixed to the pipe area 12 is inserted.
  • the impeller 7 is arranged.
  • This sliding portion 13 contacts the stop ring 14 and is rotatably mounted on this.
  • this sliding portion 13 of the impeller 7 is water-film bearing on the thrust ring.
  • the impeller 7 is so axially mounted relative to the intake passage 11 that during operation of the sliding portion 13 of the impeller 7 on the thrust ring 14 of the intake passage 11 is rotatably movable.
  • the suction-side edge of the hub of the impeller 7 and the stop ring 14 contact each other with substantially planar contact surfaces, ie they lie flat against each other.
  • the stop ring 14 has a disk-shaped cross-sectional profile with a central through hole, the inner diameter of which corresponds to the inner diameter of the intake passage 11.
  • Indentation for receiving the stop ring 14 in the tube region 12 of the intake passage 14 is formed there so deeply in the radial direction that the stop ring 14 can be largely flush-fitted to the inner wall of the intake passage 14.
  • the impeller 7 rotates in operation with typically 2000 to 3500 revolutions per minute and promotes the water thereby in an outer annular channel - not shown here - and from there by a radial outlet port back in the direction of the washing compartment 2 of the washing compartment 22 back. Between the intake and the outlet side so creates a pressure difference of typically 200 to 400 mbar. In this case, a negative pressure is generated in the intake passage in front of the impeller 7.
  • the thrust ring 14 is positioned in the intake passage 11 such that the suction-side end edge of the hub of the impeller 7 is seated on it and thus at this contact area of thrust ring and hub of the edge gap SP between the blades or vanes of the impeller 7 and the tube portion 12 of the intake 11th liquid sealing is closed.
  • the thrust ring provides a thrust bearing for the impeller, so that viewed in the suction direction SR of the pump 6 behind the impeller 7 may possibly account for more axial bearings.
  • the thrust ring 14 and the sliding portion 13 thus form by their interaction (axial start-up of the impeller 7 against the stop ring 14) thus in operation an axial bearing for the impeller 7 and at least have almost the same diameter.
  • the stop ring 14 is formed by a relative to the intake passage 11 separate annular body, for example of a ceramic material, a metal or a slide-modified plastic.
  • the sliding portion 13 is formed by a built-in impeller 7 reinforcement, such as carbon particles, Teflon or the like, and thus an integral part of this component 7.
  • an impeller 7 for example, in a 2K spray process or by subsequent injection molding of the front sliding portion 13 are produced.
  • the sliding region 13 may also be formed by a coating of an abrasion-resistant and low-friction material, which is here applied to the suction-side end face, in particular the suction-side edge zone of the hub of the impeller.
  • both sliding regions namely sliding region 13 and thrust ring 14, could each be designed as separate or both as integrated units.
  • the impeller 7 and the tube portion 12 may be made of different materials, for example, from a lightweight and cheap to produce plastic, such as a POM (polyoxymethylene) - plastic.
  • the impeller 7 can at the beginning of its rotational movement axially on the intake passage 11 to move until the sliding portion 13 rolls on the stop ring 14, or in particular already sit from the beginning on the stop ring 14 such that it is allowed to roll and at the same time for a Sealing is ensured. It may be advantageous if at least either the sliding portion 13 and / or the stop ring 14 is provided with grooves on its axially facing surface, penetrate into the water and thereby form a thin lubricating film between the parts 13, 14.
  • the grooves may expediently be designed approximately sickle-shaped and have only a small depth, in particular of typically one tenth of a millimeter.
  • a coating with a friction-reducing material such as Teflon, be provided on their axially facing contact surfaces.
  • the axial movement of the impeller 7 to the intake passage 11 can react to the respective manufacturing tolerance - unlike a fixed thrust bearing - by the path of the axial movement of the impeller 7 until it comes to the contact of the parts 13, 14, each having different sizes is.
  • the invention is thus very insensitive to large manufacturing tolerances.
  • each other part pairing 13, 14 not only forms the mentioned thrust bearing, with the next bearing 10s can be saved, but the thrust ring 14 and facing him, suction side, end face sliding portion 13 of the impeller 7 form in a double function, a sealing system against the return of water through the edge gap SP in the intake passage 11.
  • the invention thus solves the above-mentioned
  • the stationary stop ring 14a is stepped, so that it is approximately L-shaped in longitudinal section and not only with an axial, but also with a radially inwardly facing surface in contact with the sliding portion 13a of the impeller 7 and this also to radial movement prevents.
  • friction-reducing and abrasion-resistant coatings and / or depressions in the axial and radial contact surfaces of the parts 13a, 14a to form a water film can be advantageous.
  • a further radial bearing behind the impeller 7 can be omitted, so that more components can be saved.
  • the circulating pump 6b is designed so that the impeller 7 rotates about a fixed axis 8.
  • a hub in particular a sleeve receptacle 16 sits concentrically fixed on its front end 151. It forms an axle holder for the stationary axle body 8 and at the same time acts as a hub, from which, here three, radially outwardly extending spokes 17, extend outwards, which hold a stop ring 14b on the outside.
  • This stop ring 14b is firmly seated in a cut-out or a step 141 of the pipe region 12 surrounding the intake duct 11 and is arranged concentrically with the hub 16.
  • the radially inner hub 71 of the impeller 7 comes into contact with the opposite end of the sleeve receptacle 16 facing away from the suction mouth during its rotational movement, so that a bearing of the impeller 7 is provided in the axial direction.
  • the suction mouth-side end of the end piece of each blade of the impeller dives into a cutout at the outlet of the inlet pipe 11 in such a way that there is formed a radial support for the impeller. If necessary, this can also be dispensed with, ie the foot extension of each wing, which lies radially further outwards, turns freely and then does not come into contact with the stop ring 14b.
  • the outer seated stop ring 14b closes at the same time the edge gap SP between the suction-side ends of the blades of the impeller 7 and the outer pump housing PG largely liquid-tight. Possibly. can there slide along the edge of the respective wing facing the exit of the inlet pipe on the thrust washer 14b, so that it is additionally supported in the axial direction.
  • the storage takes place as far radially inward as possible, so that there the circumferential speed of the impeller 7 is minimized at the storage 13b, 14b.
  • practically no axial and radial edge gap SP in the region of the bearing point of sliding portion 13b and stop ring 14b by the attractive force on the impeller 7 is present, whereby also here the sealing effect to reduce the reflux is given as in the first embodiments.
  • the return flow of water is reduced in the intake passage, but large component tolerances are significantly reduced for the effective operation of the pump in their importance.
  • a low-friction and possibly abrasion-resistant or abrasion-resistant material is preferably selected.
  • a stop ring such as 14 in FIG. 3 such in the edge gap or gap SP between the wings of the impeller 7 and the output side pipe portion 12 of the intake passage 11, which is formed in particular on the pump housing PG, is arranged and the suction side edge of the impeller 7, in particular its hub and / or wings, in whose Contacted rotational movement, that the suction-side front portion of the gap space or edge gap SP is largely liquid-sealed and in addition an axial and possibly radial bearing for the impeller is formed on the suction side.
  • the stop ring thus acts as a sealing ring and at the same time as a thrust bearing and possibly also as a radial bearing for the impeller.
  • the impeller may have on its suction-side hub a cover disc protruding counter to the suction direction. Then, preferably, this has a corresponding sliding area, with which the impeller rolls on the thrust ring.
  • the thrust bearing for the impeller is laid in the suction region of the pump, in particular integrated.
  • a stop ring is fixedly mounted in the suction pipe of the pump housing, and the appropriate counterpart, ie the sliding area at the suction side edge of the suction mouth of the impeller and / or its possibly suction side arranged cover sits in a corresponding position in the impeller.
  • the entire impeller or the impeller shell, in particular its suction-side part consist of a lubricious material.
  • An extra, separate slip ring as a single part can therefore be omitted.
  • Both parts i. Run-up ring and sliding area of the impeller, resulting in working position when rotating the impeller a movable, rotating sealing and sliding surface.
  • This sliding surface can advantageously have small, defined grooves that optimize the structure and the existence of a water sliding film.
  • a front radial bearing for the impeller in the run-up ring is integrated by suitable shaping.
  • At least the suction-mouth-side, front-side sliding region of the impeller and / or the thrust ring may be made of a sliding-modified, in particular as low-friction and abrasion-resistant material, in particular plastic. Possibly. Instead, a corresponding coating, which is friction and abrasion resistant, may be provided instead.
  • the sliding region of the impeller may also be formed by a sliding ring which is fixedly mounted, in particular integrated, on the suction-side end edge of the impeller.
  • an axial and / or radial bearing for the suction mouth region of the impeller in the feed channel of the pump housing, it may also be advantageous if when the thrust ring is provided at its center with an axle fixing, in particular Achshalterungshülse, extending from the spokes outwards, which hold an outer contact ring.
  • the impeller In the Achshalterung the suction-side end portion of a fixed axis or elongated body is held on the rear of the Achshalterung adjacent to this, the impeller is rotatably mounted.
  • the impeller is then preferably connected directly to the rotor extrusion of the circulation pump, ie impeller and rotor of the circulation pump rotate about the fixed axis.
  • Such a radial bearing has lower radial friction losses because of its small diameter.

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

Claims (10)

  1. Lave-vaisselle (1), en particulier lave-vaisselle ménager, avec un espace de lavage (2) pour l'accueil de vaisselle, couverts ou objets à laver semblables, dans lequel l'espace de lavage (2) est alimentable en eau via au moins une pompe de recirculation (6 ; 6a ; 6b) et dans lequel la pompe de recirculation (6 ; 6a ; 6b) englobe un canal d'aspiration (11) fixe, affluant de façon centrale vers une roue mobile rotative (7) et délimité par une zone de tuyau (12), caractérisé en ce que la roue mobile (7) est dotée, en l'extrémité (9) de son corps (10) ou de son arbre d'entraînement (15) dirigée vers la zone de tuyau (12) délimitante du canal d'aspiration (11), d'une zone de glissement (13 ; 13a ;13b) immobile par rapport à la roue mobile (7) et [d']un carter (PG) sur l'extrémité de la zone de tuyau (12) dirigée axialement vers la roue mobile (7) ou d'un logement à fourreau (16) affecté à celle-ci avec une bague de roulement (14 ;14a ;14b) fixe par rapport au canal d'aspiration (11), et en ce que durant l'exploitation, la zone de glissement (13 ; 13a ; 13b) est rotative par rapport à la bague de roulement (14 ; 14a ; 14b) et la zone de glissement ainsi que la bague de roulement (13 ; 13a ; 13b ; 14 ; 14a ; 14b) constituent en fonction double un coussinet pour la roue mobile (7) et un système d'étanchéité contre le retour d'eau dans le canal d'aspiration (11), dans lequel la roue mobile (7) est, en dehors de cet appui (13 ; 14), libre de ses points d'appui (10s) entravant son déplacement axial.
  2. Lave-vaisselle (1) selon la revendication 1, caractérisé en ce que la zone de glissement et la bague de roulement (13 ; 14 ; 13a ; 14a ; 13b ; 14b) constituent un coussinet axial pour la roue mobile (7).
  3. Lave-vaisselle (1) selon l'une des revendications précédentes, caractérisé en ce que la zone de glissement et la bague de roulement (13a ; 14a ; 13b ; 14 b) constituent un coussinet radial pour la roue mobile (7).
  4. Lave-vaisselle (1) selon l'une des revendications précédentes, caractérisé en ce que le coussinet constitué par la zone de glissement et la bague de roulement (13 ; 14 ; 13a ; 14a ; 13b ; 14 b) est lubrifié à l'eau.
  5. Lave-vaisselle (1) selon l'une des revendications précédentes, caractérisé en ce que la zone de glissement (13 ; 13a ; 13b) et/ou la bague de roulement (14 ; 14a ; 14b) est ou sont constituée(s) par un/des corps annulaire(s) séparé(s) par rapport à la roue mobile (7) resp. au canal d'aspiration (11).
  6. Lave-vaisselle (1) selon l'une des revendications précédentes, caractérisé en ce que la zone de glissement (13 ; 13a ; 13b) et/ou la bague de roulement (14 ; 14a ; 14b) est ou sont constituée(s) par un renforcement, par exemple des particules de charbon, incorporé à la roue mobile (7) resp. au canal d'aspiration (11).
  7. Lave-vaisselle (1) selon la revendication 6, caractérisé en ce que le renforcement incorporé est intégralement formé sur la roue mobile (7) et/ou une zone de tuyau (12) délimitant le canal d'aspiration (11) selon un procédé 2K.
  8. Lave-vaisselle (1) selon l'une des revendications précédentes, caractérisé en ce que la zone de glissement (13 ; 13a ; 13b) et/ou la bague de roulement (14 ; 14a ; 14b) est ou sont exécutée(s) de façon à réduire la friction, p.ex. avec un revêtement au téflon sur sa/leur surface axiale dirigée vers l'extérieur.
  9. Lave-vaisselle (1) selon l'une des revendications précédentes, caractérisé en ce que la zone de glissement (13 ; 13a ; 13b) et/ou la bague de roulement (14 ; 14a ; 14b) est ou sont dotée(s) de rainures pour constituer un film lubrifiant à l'eau sur sa/leur surface axiale dirigée vers l'extérieur.
  10. Lave-vaisselle (1) selon l'une des revendications précédentes, caractérisé en ce que la roue mobile (7) et une section de tuyau (12) délimitant le canal d'aspiration (11) sont exécutées en plastique au moins en dehors de leurs extrémités axiales dirigées l'une vers l'autre.
EP10168100.5A 2009-07-13 2010-07-01 Lave-vaisselle doté d'une pompe de recirculation Active EP2275017B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL10168100T PL2275017T3 (pl) 2009-07-13 2010-07-01 Zmywarka do naczyń z pompą cyrkulacyjną

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102009027645.9A DE102009027645B4 (de) 2009-07-13 2009-07-13 Geschirrspülmaschine mit einer Umwälzpumpe

Publications (3)

Publication Number Publication Date
EP2275017A2 EP2275017A2 (fr) 2011-01-19
EP2275017A3 EP2275017A3 (fr) 2017-04-05
EP2275017B1 true EP2275017B1 (fr) 2018-09-12

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EP10168100.5A Active EP2275017B1 (fr) 2009-07-13 2010-07-01 Lave-vaisselle doté d'une pompe de recirculation

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EP (1) EP2275017B1 (fr)
CN (1) CN101953672B (fr)
DE (1) DE102009027645B4 (fr)
ES (1) ES2692328T3 (fr)
PL (1) PL2275017T3 (fr)

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DE102011079887A1 (de) 2011-07-27 2013-01-31 BSH Bosch und Siemens Hausgeräte GmbH Wasserführendes Haushaltsgerät mit einer Heizpumpe
CN105286746B (zh) * 2015-10-23 2018-02-27 张文杰 一种全方位冲洗的洗碗装置
US10533568B2 (en) * 2017-10-30 2020-01-14 Daikin Applied Americas Inc. Centrifugal compressor with seal bearing
DE102019129494A1 (de) * 2019-10-31 2021-05-06 Nidec Gpm Gmbh Kühlmittelpumpe mit verbesserter Spaltdichtung

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Publication number Publication date
CN101953672B (zh) 2015-04-08
PL2275017T3 (pl) 2019-01-31
DE102009027645B4 (de) 2018-08-02
DE102009027645A1 (de) 2011-01-20
CN101953672A (zh) 2011-01-26
EP2275017A2 (fr) 2011-01-19
ES2692328T3 (es) 2018-12-03
EP2275017A3 (fr) 2017-04-05

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