EP2275017B1 - Geschirrspülmaschine mit einer Umwälzpumpe - Google Patents
Geschirrspülmaschine mit einer Umwälzpumpe Download PDFInfo
- 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
- Authority
- 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
Links
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 21
- 238000005406 washing Methods 0.000 claims description 13
- 238000007789 sealing Methods 0.000 claims description 12
- 238000000576 coating method Methods 0.000 claims description 7
- 239000011248 coating agent Substances 0.000 claims description 6
- 239000000463 material Substances 0.000 claims description 6
- 239000004033 plastic Substances 0.000 claims description 5
- 239000004809 Teflon Substances 0.000 claims description 4
- 229920006362 Teflon® Polymers 0.000 claims description 4
- 230000002787 reinforcement Effects 0.000 claims description 4
- 238000000034 method Methods 0.000 claims description 3
- 239000002245 particle Substances 0.000 claims description 3
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 claims description 2
- 229910052799 carbon Inorganic materials 0.000 claims description 2
- 230000001050 lubricating effect Effects 0.000 claims description 2
- 230000009977 dual effect Effects 0.000 claims 1
- 238000005299 abrasion Methods 0.000 description 7
- 238000004519 manufacturing process Methods 0.000 description 5
- 238000001746 injection moulding Methods 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 3
- 238000003860 storage Methods 0.000 description 3
- 238000010276 construction Methods 0.000 description 2
- 239000003599 detergent Substances 0.000 description 2
- 229920000642 polymer Polymers 0.000 description 2
- 229920006324 polyoxymethylene Polymers 0.000 description 2
- 239000008237 rinsing water Substances 0.000 description 2
- 239000007921 spray Substances 0.000 description 2
- 241001295925 Gegenes Species 0.000 description 1
- 229930040373 Paraformaldehyde Natural products 0.000 description 1
- 239000000654 additive Substances 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 229910010293 ceramic material Inorganic materials 0.000 description 1
- 238000004140 cleaning Methods 0.000 description 1
- 239000003245 coal Substances 0.000 description 1
- 238000010411 cooking Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000011010 flushing procedure Methods 0.000 description 1
- 239000002783 friction material Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000007373 indentation Methods 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 235000015095 lager Nutrition 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000010992 reflux Methods 0.000 description 1
- 239000002990 reinforced plastic Substances 0.000 description 1
- 238000007493 shaping process Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Images
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.
Landscapes
- 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)
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 (de) | 2011-01-19 |
EP2275017A3 EP2275017A3 (de) | 2017-04-05 |
EP2275017B1 true EP2275017B1 (de) | 2018-09-12 |
Family
ID=43034695
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10168100.5A Active EP2275017B1 (de) | 2009-07-13 | 2010-07-01 | Geschirrspülmaschine mit einer Umwälzpumpe |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP2275017B1 (es) |
CN (1) | CN101953672B (es) |
DE (1) | DE102009027645B4 (es) |
ES (1) | ES2692328T3 (es) |
PL (1) | PL2275017T3 (es) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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 |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3123275C2 (de) | 1981-06-12 | 1986-09-25 | Licentia Patent-Verwaltungs-Gmbh, 6000 Frankfurt | Kreiselpumpe für Geschirrspülmaschinen |
US4448359A (en) * | 1982-06-10 | 1984-05-15 | Hobart Corporation | Combination drain pump and grinding apparatus |
DE3536140A1 (de) | 1985-10-10 | 1987-04-16 | Klein Schanzlin & Becker Ag | Kreiselpumpenaggregat |
DE19513962B4 (de) * | 1995-04-13 | 2007-06-28 | Allweiler Ag | Radiale Kreiselpumpe |
CN2360035Y (zh) * | 1998-12-17 | 2000-01-26 | 无锡小天鹅梅洛尼洗碗机有限公司 | 洗碗机洗涤泵 |
CN1844675A (zh) * | 2005-04-07 | 2006-10-11 | 佛山市美的日用家电集团有限公司 | 一种用于洗碗机的洗涤泵 |
DE202005020138U1 (de) | 2005-12-22 | 2006-05-11 | Allweiler Ag | Kreiselpumpe, insbesondere Spiralgehäuse-Kreiselpumpe mit Dichtsystem |
FR2911166B1 (fr) | 2007-01-09 | 2012-08-03 | Siebec Soc | Pompe a entrainement magnetique et etancheite coulissante |
-
2009
- 2009-07-13 DE DE102009027645.9A patent/DE102009027645B4/de not_active Expired - Fee Related
-
2010
- 2010-07-01 ES ES10168100.5T patent/ES2692328T3/es active Active
- 2010-07-01 EP EP10168100.5A patent/EP2275017B1/de active Active
- 2010-07-01 PL PL10168100T patent/PL2275017T3/pl unknown
- 2010-07-13 CN CN201010229721.1A patent/CN101953672B/zh active Active
Non-Patent Citations (1)
Title |
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None * |
Also Published As
Publication number | Publication date |
---|---|
DE102009027645B4 (de) | 2018-08-02 |
CN101953672A (zh) | 2011-01-26 |
EP2275017A2 (de) | 2011-01-19 |
CN101953672B (zh) | 2015-04-08 |
DE102009027645A1 (de) | 2011-01-20 |
ES2692328T3 (es) | 2018-12-03 |
PL2275017T3 (pl) | 2019-01-31 |
EP2275017A3 (de) | 2017-04-05 |
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