EP3455502A1 - Flüssigkeitsheizpumpe zum fördern und aufheizen von flüssigkeit in einem wasserführenden haushaltsgerät - Google Patents
Flüssigkeitsheizpumpe zum fördern und aufheizen von flüssigkeit in einem wasserführenden haushaltsgerätInfo
- Publication number
- EP3455502A1 EP3455502A1 EP17723285.7A EP17723285A EP3455502A1 EP 3455502 A1 EP3455502 A1 EP 3455502A1 EP 17723285 A EP17723285 A EP 17723285A EP 3455502 A1 EP3455502 A1 EP 3455502A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- impeller
- diffuser
- liquid
- section
- axially
- 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.)
- Granted
Links
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- 238000010438 heat treatment Methods 0.000 title claims abstract description 222
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title description 25
- 230000002093 peripheral effect Effects 0.000 claims description 52
- 238000005406 washing Methods 0.000 claims description 29
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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
- F04D29/58—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
-
- 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
-
- 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
- A47L15/4285—Water-heater 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
- D06F39/04—Heating 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
- 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
-
- 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
- F04D29/40—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
- F04D29/448—Fluid-guiding means, e.g. diffusers especially adapted for liquid pumps bladed diffusers
-
- 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
Definitions
- Liquid heating pump for conveying and heating liquid in a water-conducting domestic appliance
- a so-called liquid heating pump which comprises a circulating pump and in combination with this additionally a heating device.
- rinsing liquid can be pumped via one or more supply lines to one or more spraying devices in the interior of the washing container of the domestic dishwasher and, on the other hand, by the heating device, the rinsing liquid to be sprayed by means of the circulating pump can be heated to a required heating temperature, if this is the case in each partial wash cycle - such as the cleaning cycle or the rinse cycle - a rinse cycle to be performed is required.
- Such a liquid heating pump is specified, for example, in WO 2008/125488 A2.
- the liquid heating pump provided there is designed according to the functional principle of a centrifugal pump or radial pump. It has, viewed along the flow path of the liquid conveyed in pumping operation, a centrally arranged intake channel, a rotor chamber arranged downstream of it in the flow direction of the conveyed liquid with a rotatably drivable impeller, in particular an impeller, after an approximately 180 ° deflection of the conveyed liquid, a ring-cycle downstream of the impeller chamber.
- Linderförmigen diffuser and / or pressure chamber which is arranged externally coaxially around a portion of the intake duct, a tubular heating device which forms a portion of the outer boundary wall of the diffuser and / or pressure chamber, and an output-side discharge nozzle.
- a tubular heating device which forms a portion of the outer boundary wall of the diffuser and / or pressure chamber
- an output-side discharge nozzle In the diffuser and / or pressure space downstream of the liquid outlet region of the impeller as a section whose inner boundary wall a fixed nozzle with a ring and formed on the outer shell of the vanes are provided, which have radially outward and may be slightly hired.
- the pumping capacity of this liquid heating pump may be insufficient under some circumstances.
- the venting behavior of such a In some cases, such as at the start of the rotational operation of the pump after a standstill phase, the liquid heating pump may be insufficient. As a result, it can happen that the heating device can not be properly or sufficiently flowed by the conveyed liquid, so that the thermal removal of the thermal power provided by the heating device can be impaired.
- the operating according to the principle of operation of a centrifugal pump heating pump of EP 2 495 444 A1 sucks to be pumped water via a central axial tubular inlet, which merges into an inlet-side pump cover when the impeller is driven and rotates.
- the impeller promotes the water radially and with a velocity component in the circumferential direction into a pump chamber. Their outer chamber wall is heated.
- the impeller extends with its underside, ie viewed in the suction direction with its rear impeller disc above a pump bottom, below which is the drive motor of this heat pump, on whose axis the impeller is seated.
- one or more fixed flow vanes are arranged, which extend in a helical manner with the pitch running in the direction of rotation of the impeller away from the pump bottom.
- at least one of the helical flow guide vanes extends to the underside, that is viewed in the suction direction up to the rear cover plate of the impeller.
- the one or more helically extending flow guide vanes are advantageously provided on the outer circumference of a circumferential support ring radially outwardly projecting, which is disposed substantially radially outside of an upper region, ie radially outside of a front region of the impeller viewed in the suction direction.
- This support ring is pushed there on the inlet side pump cover, where it forms a portion of an inner boundary wall of the pump chamber.
- the at least one projecting up to the bottom of the impeller helically extending Strömungsleitschaufel in the axial direction over the support ring over.
- the outside diameter of the support ring matches the outside diameter of the bottom of the impeller. This requirement may be unfavorable for some constructions of fluid heating pumps.
- the object of the invention is to provide an alternative, improved liquid heating pump for conveying and heating liquid in a water-conducting domestic appliance, in particular a household dishwasher-heating pump or washing machine-heating pump.
- liquid heating pump for conveying and heating liquid in a water-conducting domestic appliance, in particular household dishwasher-heating pump or washing machine heating pump,
- impeller rotatably drivable in the impeller space for conveying the liquid in a diffuser and / or pressure space arranged axially opposite to the suction direction and arranged at least around a partial section of the intake duct on the outside, in particular coaxially,
- the diffuser has a, in particular circular cylindrical, base body whose end wall facing the impeller space forms a front boundary wall of the impeller space, and wherein the main body of the diffuser on its end wall facing the impeller space limited by its position Outer circumference one or more in the direction of the impeller axially projecting vane sections, each projecting into a arranged around the outer periphery of the impeller around the liquid ejection area of the impeller and each inclined away from this outwardly, in particular deviating from the radial direction in the impeller direction, on the Axialaußenmantel the body to, in particular to the axial outer casing of the main body, extend, which is arranged radially further outward than the liquid ejection region of the impeller,
- This liquid heating pump constructed according to the invention is further improved, in particular with respect to its venting behavior.
- Leitschaufelabitese the position limited by the outer circumference of the diffuser basic body of its the impeller space facing end wall protrude axially towards the impeller in the peripheral liquid ejection region, can be largely avoided in particular that an air bubble from the diffuser and / or pressure chamber , in particular radially inwardly, flows back into the center of the impeller space when the impeller is driven in rotation.
- the front wall surface of the diffuser base body which faces the impeller space, has within its outer boundary one or more vane sections which protrude axially in the direction of the impeller and protrude into its peripheral liquid ejection region and respectively outwardly therefrom toward the axial outer jacket of the main body, in particular to the axial outer shell of the body extend radially outward than the liquid ejection region of the impeller is arranged, but not beyond the Axialaußenmantel the body in the radial direction addition, on the out of the impeller, preferably with a radial and circular velocity component, out-conveyed liquid flow-conducting favorable to its introduction into the diffuser and / or pressure chamber are acted upon.
- the formation of a fluid flow propagating in the axial direction through the diffuser and / or pressure chamber in a helical manner can be assisted by this one or more guide blade sections projecting axially on the end wall side. It is now possible to use the diffuser and / or pressure chamber largely independently of one another. pending on the impeller, in particular its geometry, position and / or size, in particular its outer diameter, to arrange and to dimension.
- the diffuser and / or pressure space can be relatively far away, preferably considerably further than in the case of the prior art, such as, for example, WO 2008/125488 A2, EP 2 495 444 B1 , fixed nozzles, each with a ring, on whose outer jacket radially outwardly facing vanes are formed.
- the diffuser construction according to the invention allows, preferably the diameter of the inner boundary wall of the diffuser and / or pressure chamber, and thus - if this is expediently at least partially formed by the Axialaußenmantel the diffuser base body - the diameter of the Axialaußenmantels the main body of the diffuser, and / or set the diameter of the outer boundary wall of the diffuser and / or pressure chamber largely independent of the outer diameter of the impeller greater than this.
- the impeller has an outer diameter which is selected between 40% and 80%, in particular between 60% and 70%, of the diameter of the axial outer shell of the, in particular nikzylinderformigen, body of the diffuser.
- the diffuser designed according to the invention advantageously provides degrees of freedom in the local positioning, and / or dimensioning of the passage cross-sectional area of the diffuser and / or pressure space.
- the heating device forms at least one, preferably axially extending, section of the outer boundary wall of the diffuser and / or pressure chamber to ensure sufficient flow of this heated section of the outer boundary wall with liquid for proper removal of the thermal energy provided there To ensure performance.
- the flow velocity of the liquid flowing through the diffuser and / or pressure space in a helical manner in the axial direction can be increased by a thermal heating power provided there by the heating device to dissipate properly.
- an initial section of the heating device can already be accommodated in the impeller space, which then extends further into the downstream diffuser and / or pressure space.
- an initial portion of the heating device forms a portion or the entire portion of the outer boundary wall of the impeller space.
- the diameter of the impeller space is selected to be approximately equal to the diameter of the outer boundary wall of the diffuser and / or pressure chamber.
- the dimensioning ratios specified above between the impeller outer diameter and the diameter of the diffuser axial outer jacket then apply correspondingly to the ratio between the impeller outer diameter and the outer diameter of the impeller space.
- the respective liquid heating pump (as seen on the end wall surface of the diffuser base body facing the impeller space) extends in the inventive liquid heating pump in the direction of the impeller space axially projecting vane section approximately from the outer circumference of the impeller or impeller away only to a radially outermost region within the encompassed by the outer periphery of the body end wall surface, in particular only to the outer periphery of the end wall surface of the diffuser basic body, but not in radial direction beyond.
- the peripheral liquid ejection region of the impeller is understood to be, in particular, that region around the outer circumference of the impeller from which the liquid is conveyed outwards between the voids of its impeller blades, in particular with a radial and a circular velocity component, when the impeller is driven in rotation. This corresponds in particular to a circle which is defined by the ends of the impeller blades.
- a fixed diffuser with an elongated preferably in the axial direction, in particular circular cylindrical base body is provided in which at the end face facing the impeller space limited by the outer circumference one or more vanes in the direction of impeller so axially protrude that they each protrude into a disposed around the outer periphery of the impeller around the liquid ejection area of the impeller and each outwardly therefrom, in particular deviating from the radial direction in the impeller direction inclined or inclined to the Axialaußenmantel the body to, in particular to the Axialaußenmantel of the main body, which is arranged radially further outward than the liquid ejection region, are in the rotation operation of the impeller of the liquid conveyed outwardly therefrom and also possibly contained or entrained in it
- flow guidance paths defined in the direction in particular with the exception of the axial outer casing of the main body which is radially
- These one or more axially projecting vane sections promote the removal of the liquid ejected or ejected by the rotationally driven impeller and any liquid contained therein or entrained therein. th air bubbles away from the liquid ejection region of the impeller out of the impeller space in this opposite to the suction, ie in the outflow axially downstream diffuser and / or pressure chamber into it.
- the one or more axially projecting vane sections thus run outwardly from the peripheral liquid ejection region of the impeller toward the outer axial jacket of the main body, in particular as far as the axial outer jacket of the main body, expediently in such a way as to untwist it otherwise around the impeller during its rotational operation cause adjusting circulation flow. In other words, they counteract the formation of a rotational flow in which the fluid ejected outwardly from the impeller during its rotational operation circulates it once or several times.
- the course of the respective axially projecting vane section is preferably selected such that the ejected at the periphery or outer circumference of the impeller in its rotational operation liquid only a circulation angle of less than 360 °, in particular between 45 ° and 180 °, preferably between 50 ° and 135 °, viewed from its exit point on the outer circumference of the impeller until, on the other hand, it passes radially further outside the axial outer casing of the main body of the diffuser.
- the one or more axially projecting vane sections therefore limit the circular or peripheral path of the liquid ejected from the impeller with a radial component and a rotational component in the circumferential direction to a fraction of a 360 ° full circle.
- the impeller space viewed around the outer circumference of the impeller, is more or less divided into a plurality of chambers by the one or more axially extending vane sections thereby reducing or avoiding the formation of a circulation flow where the liquid ejected from the impeller is one or more times its periphery circulates.
- the one or more axially projecting vane sections ensure that air, which is present for example after a standstill phase of the impeller in a liquid-free cavity of the diffuser and / or pressure chamber, can flow back into the center of the impeller space during startup or start of the impeller. If, during the liquid pumping operation, the liquid heating pump according to the invention is designed to draw in air, ie if air bubbles are contained in the liquid sucked into the interior of the impeller through the intake channel, the one or more axially projecting vane sections facilitate their removal by the conveyed liquid the impeller space in the diffuser and / or pressure chamber, through it and then out of the discharge nozzle.
- the respective axially projecting vane section performs an air bubble contained in the conveyed liquid preferably in the manner of a relative to the radial direction in the running direction of the impeller inclined ramp or other flow control from the peripheral diesstechniksaus- push area of the impeller outward on the axial outer shell of the main body of the diffuser , in particular to the axial outer shell of the base body, which is arranged radially further out than the liquid ejection region of the impeller.
- the liquid heating pump according to the invention is characterized by an improved venting behavior with a shorter venting time both in the current liquid feed operation and during starting or starting of the impeller.
- the liquid ejected from the impeller with a radial and a circular velocity component, ie velocity component in the circumferential direction, can flow only in a partial section, in particular a sector section, of the preferably rotationally symmetric, in particular approximately circular cylindrical, impeller space, viewed in the direction of rotation of the impeller from a first, axially projecting vane portion and a subsequent second axially projecting vane portion is limited.
- a liquid flow from the liquid discharge region of the impeller which lies between the first and the second axially extending vane section, flows from the outer circumference of the impeller in the direction, in particular, to the axial outer casing of the main body out into the diffuser and / or pressure chamber.
- air bubbles contained in the liquid are also pressed into the diffuser and / or pressure space of the conveyed liquid by the liquid via the respective guide vane section following the direction of rotation in the direction of rotation, in particular with respect to the radial direction in the direction of rotation.
- the profile of the respective end wall of the main body axially projecting from the impeller space facing stator blade section is selected such that it is radially effective for the out with a radial and a circular velocity component conveyed out of the impeller fluid.
- a portion of the kinetic energy imparted to the liquid by the rotating impeller may possibly already be converted into dynamic pressure.
- the liquid expelled from the rotating impeller retains a portion of its circular velocity component and is not fully decelerated in the direction of rotation of the impeller.
- the respective axially projecting vane section deviates from a circular arc section extending in the circumferential direction of the end wall, which follows the impeller rotational direction (and thus not in the form of a concentric circular ring section)
- the liquid can deflect with a radial direction component Direction to the axial outer shell of the body and / or the outer boundary wall of the impeller space to be milled.
- the kinetic energy induced by the rotationally driven impeller into the liquid may already be partially converted into dynamic pressure.
- the liquid entering the diffuser and / or pressure chamber retains a sufficiently large part of the kinetic energy imparted to it by the impeller, so that the heating device associated with the diffuser and / or pressure chamber can be charged with a liquid flow flowing past it quickly enough ,
- the heating device forms a partial section or the entire section of the outer boundary wall of the diffuser and / or pressure chamber-the electrical heating power provided by the heating device in the circumferential direction and in the axial direction is largely uniform and reliable the pumped in the pumping liquid can be removed without it comes to local overheating of the heating device. Also, less calcium can deposit on the heating device.
- Such a shape of the respective axially projecting vane section advantageously favor the detachment of the conveyed liquid from the peripheral outer circumference of the impeller into a flow path which (viewed from the impeller perpendicular to the end wall of the main body facing the impeller space) viewed from the liquid ejection region of the impeller leads to the axial outer casing of the base body and then merges into a movement path which continues in the axial direction from the impeller space through the preferably circular-ring-shaped diffuser and / or pressure space through the axial outer casing of the main body in a helical curve.
- the respective axially projecting vane section with its radially inner initial section substantially tangentially from an inner circumferential location Runs outward at the circle of the liquid ejection region of the impeller and opens with its radially outer end substantially tangentially at a different to this inner circumferential point, outer peripheral point on the outer peripheral circle of the Axialaußenmantels it body.
- the respective axially projecting vane section protrudes so far from the end wall of the main body of the diffuser toward the impeller that it faces, at least along its initial section facing the impeller liquid ejection region, in particular along its entire extension Width of the liquid ejection region of the impeller partially or completely covered from the outside.
- the axial outer casing of the main body of the diffuser forms at least one, in particular axially extending, section of an inner boundary wall of the diffuser and / or pressure chamber.
- the, in particular nikzylinderformige, base body of the diffuser has an axial outer sheath whose diameter is at least equal to 80%, in particular between 80% and 90%, preferably about 86%, selected the outer diameter of the diffuser and / or pressure chamber is.
- the radial gap width of the diffuser and / or pressure space can be reduced such that the liquid flowing through it has an increased flow velocity along its preferably helical track, which is sufficient to increase the electrical heating power produced by the diffuser and diffuser. and / or pressure chamber associated heating device is provided in a reliable manner ablate.
- the heating device has an
- the dead space volume in the pump housing for the liquid to be conveyed is reduced by this advantageous dimensioning of the diameter of the axial outer jacket of the diffuser in relation to the outer diameter of the diffuser and / or pressure chamber.
- the reduction of the annular passage cross-sectional area in the diffuser and / or pressure space results in an improved displacement effect for the liquid flowing therethrough. This results in a reduction of the total amount of liquid present in the liquid heating pump according to the invention.
- the expansion of the outer diameter of the main body of the diffuser to at least equal to 80%, in particular between 80% and 90%, preferably about equal to 86%, of the outer diameter of the diffuser and / or pressure chamber compared to a previous heating pump such.
- a previous heating pump such as WO 2008/125488 A2
- the heating device can now be operated with a higher local thermal power density.
- a heating device with a shorter axial length may be sufficient, if necessary, because of the now increased volume throughput.
- the outer diameter of the impeller is expediently chosen between 3.8 and 4.4 cm, in particular equal to about 4.2 cm.
- Your designed according to the design principle of the invention diffuser has three about 120 ° circumferentially offset from one another in the direction of the impeller space axially projecting vane sections.
- the respective axially projecting vane section expediently protrudes into the impeller space with an axial extent of between 3 mm and 8 mm, in particular of approximately 5 mm, on the end wall of the main body.
- This axial Er- extension corresponds approximately to the axial width of the peripheral liquid ejection region of the impeller with the addition of the axial gap between the impeller space facing end wall of the body and the suction-side end face of the impeller. This is formed when using a so-called closed-shaped impeller through the suction-side, front cover plate.
- throughput times of not more than 6 seconds, in particular between 3 seconds and 6 seconds, preferably of about 5 seconds, are advantageously made possible for air bubbles sucked in via the intake duct.
- the heating device in the diffuser and / or pressure chamber preferably on the subsection formed by it or the entire section formed by the outer boundary wall of the diffuser and / or pressure chamber, - in particular when using the inventively embodied liquid heating in a household dishwasher - an electricalmonyncopylast between 30 W / cm 2 and 50 W / cm 2 ready.
- the passage cross-sectional area of viewed in cross-section annular gap-shaped diffuser and / or pressure chamber suitably between 8 cm 2 and 20 cm 2 , in particular selected by about 12 cm 2 .
- liquid heating pump - the impeller especially at an outer diameter of about 4.2 cm, with a speed between 3800 and 4500 U / min, preferably at a speed of about 4200 U / min.
- the volumetric flow rate of the liquid conveyed is then so great that the heating power provided by the heating device can be transferred to the liquid flowing past it to such an extent that local overheating at the heating device leading to undesirable calcium deposits.
- the respective guide vane section projecting axially in the direction of the impeller is provided, in particular integrally formed, on the end wall of the main body of the diffuser facing the impeller chamber or the intake side of the impeller, such that it extends from its radially further inward beginning up to its radially further outward end seen an inclination relative to the going through its beginning radial direction of the impeller in its direction of rotation.
- the liquid ejected from the impeller can take up most of the kinetic energy imparted to it by the rotating impeller along its flow path, preferably helical section, from the peripheral liquid discharge region of the impeller to the further outer axial casing of the main body into the diffuser and / or pressure space take. It is particularly favorable if the one or more guide blade sections axially projecting in the direction of the impeller have a respective direction of curvature in the direction of rotation of the impeller on the end wall of the main body of the diffuser facing the impeller space. As a result, the hydraulic efficiency of the liquid pump according to the invention can be further improved.
- the respective axially projecting vane section therefore serves as a climbing aid or flow-guiding means for the liquid which is ejected radially further inwards from the outer circumference of the impeller into the diffuser and / or pressure space located further outward in the radial direction.
- the basic body of the diffuser can be structurally simply held and manufactured, and yet the liquid ejected there can already be distributed particularly uniformly around the diffuser and / or pressure space, in particular in circular cross-section, around the outer circumference of the impeller.
- the hydraulic efficiency of the liquid heating pump formed according to the invention is further improved, since undesirable losses of kinetics are avoided. shear energy that has been given to the liquid from the rotating impeller, are further improved avoided when entering the diffuser and / or pressure chamber.
- the respective axially projecting vane section can be arranged and formed on the end wall of the main body facing the impeller so that it at least with its initial section, in particular along its entire extension, from the outside the outer peripheral liquid ejection region of the impeller substantially over its axial width with a remaining Radial gap roofed, which is (in the direction of flow) selected in the region of its beginning, in particular between 0.5 mm and 2 mm.
- This radial gap provides sufficient clearance for unimpeded rotation of the impeller.
- the remaining radial gap is chosen so small that the formation of a circular flow around the impeller is largely avoided. Circulating leakage currents around the impeller are thereby largely avoided, so that the volumetric efficiency of the liquid heating pump is improved.
- the one or more blades of the impeller each have an inclined position relative to the radial direction of the impeller against the direction of rotation of the impeller, in particular a direction of curvature opposite to the direction of rotation of the impeller.
- the radially further inward beginning of the respective endally axially projecting vane section of the main body preferably has a contour that is independent of the contour of the output side. End of the respective blade of the impeller is different.
- one or more, in particular three, the liquid flow in the diffuser and / or pressure chamber radially projecting vane sections are provided on the Axialaußenmantel of the main body of the diffuser additionally.
- these radially projecting vane sections are each between 2 and 3 mm from the Axialaußenmantel the body radially into the diffuser and / or pressure chamber.
- they each have such a course on the axial outer casing of the base body that they force the liquid flowing into the diffuser and / or pressure chamber from the impeller space an axial direction component, ie they are formed axially effective on the liquid.
- they serve in particular to convert at least part of the kinetic energy contained in the fluid into dynamic pressure.
- the respective axially outer-shell-side radially projecting vane section runs in the form of a spiral section, in particular a helical-line section.
- the liquid flow passes through the diffuser and / or pressure chamber in such a way that it surrounds the diffuser base body or the inner boundary wall of the diffuser and / or pressure space in a helical or helical manner with a pitch or pitch in the axial direction.
- the heating device forms, for example, a partial section or the entire section of the outer boundary wall of the diffuser and / or pressure chamber.
- radially projecting vane sections are each arranged in the form of spiral sections offset from each other around the axial outer casing of the, in particular circular cylindrical, base body.
- they are positioned separated by approximately the same central angle range.
- the radially evenly distributed guide blade sections which are distributed substantially uniformly in the circumferential direction of the axial outer jacket, act to a large extent uniformly on the liquid conveyed through the diffuser and / or pressure space, which is preferably viewed in cross-section.
- they also serve, in particular, to avoid a direct short-circuit flow path for the conveyed liquid on its way from the inlet of the diffuser and / or pressure chamber to the discharge nozzle. In this way, the liquid flowing through the diffuser and / or pressure chamber along a helical path can be optimally heated by the heating device provided there.
- the respective axialaumantelmantel, radially projecting vane in view of the impeller space or the suction side of the impeller facing end wall of the base body section on the axial outer casing of the main body of the diffuser extends at least in an outer peripheral region of the main body, which is arranged between the radially outwardly arranged end of a first axially projecting vane section and the radially further inwardly arranged beginning of a second, axially projecting vane section viewed in the direction of rotation of the impeller lies.
- the connecting section expediently runs along an outer circumferential section of the end wall of the main body facing the impeller chamber.
- the connecting portion preferably has an axially projecting, in particular arcuate portion-like, web portion and in addition to the axial end face radially projecting, in particular helical, web portion.
- the radially projecting web section acts in the axial direction as a barrier or obstacle, which impedes or avoids, in the axial direction, a backflow of an air bubble from the diffuser and / or pressure chamber back into the impeller space and thus ultimately into the center of the impeller space. when the liquid heating pump is operating in pump mode.
- the axially projecting web portion serves as an extension of the radially outer end portion of the axially projecting vane portion of the combined guide vane and preferably allows a continuous transition in the associated axially outer shell side radially projecting vane section inside.
- the axially projecting web section has an axial extent or extension which decreases, in particular steadily, from its beginning connected to the axially projecting vane section to its end connected to the axially outer vane side radially projecting vane section.
- the axially projecting web portion in the impeller space counteracts the radial direction of ejection of the impeller as a barrier or obstacle that impedes or avoids a back flow of an air bubble from the diffuser and / or pressure chamber in the radial direction back to the center of the impeller space or when the sosstechniksutzpumpe works in pump mode.
- the connecting portion connects the end-side, axially projecting vane section with the axially outer shell-side, radially projecting vane section associated therewith, in particular in one piece and / or with the same material to form a continuous vane.
- the respective guide vane section projecting axially from the end wall of the main body into the impeller space extends arcuately, preferably in the form of a circular arc section or in a spiral section (viewed in a normal plane to which the axis of rotation of the impeller is perpendicular), and then passes radially outward into an outer edge zone the end wall of the base body by means of the preferably integrally formed on him connecting portion in the direction of rotation of the impeller considered following, axialau datemantel document associated, radially projecting, preferably helically extending vane section substantially continuously over.
- the axially projecting web section of the connecting section thereby extends the frontally axially projecting vane section, in particular in the form of a circular arc section.
- the radially projecting web section of the connecting section extends the axial outer casing-side, radially projecting guide blade section preferably in accordance with its shape, in particular spiral shape.
- the liquid (as viewed in the direction of the one or more axial guide vanes) sections equipped end wall of the main body) detached from the outer circumference of the rotating impeller and along a spiral portion-like route to the radially further outward diffuser and / or pressure chamber is promoted and then spatially viewed in the axial direction helically the main body circumferentially through the diffuser and / or pressure chamber moves.
- this further improves the hydraulic efficiency of the inventive liquid heating pump and its venting behavior.
- the respective radially projecting vane section on the axial outer shell of the main body of the diffuser and its upstream upwardly extending extension formed by the radially projecting web section of the connecting section extend in an outer circumferential region of the main body in the gap when looking toward the end wall of the main body facing the impeller between the radially outer end of a first axially extending Leitschaufel- section and the radially outer end of a viewed in the direction of rotation of the impeller adjacent, second axially projecting vane section.
- an axially projecting vane section and its connecting portion to its associated axially outer shell side radially projecting Leitschaufelab- section are arranged in the upper region of the Kaufradraum facing end wall of the body that they any above the body in the diffuser and / or pressure chamber existing air bubble in the way to flow back inward in the direction of the center of the impeller space in the rotary operation of the impeller.
- the radially projecting web portion of the connecting portion thereby causes an axial barrier for an air bubble, which is located downstream of the connecting portion in the diffuser and / or pressure chamber, so that the air bubble is prevented from flowing back into the impeller space in the rotational operation of the impeller. This results in an excellent self-deaeration behavior of the liquid heating pump according to the invention.
- the respective guide vane section projecting axially on the outer circumference of the main body ends at the end wall of the main body facing the impeller chamber or the intake side of the main body, at which peripheral end, viewed in the direction of rotation of the impeller, the axial outer sheath side
- the radially outwardly directed guide blade section viewed at the axial outer jacket of the main body, terminates at an axial distance from the end wall of the main body of the diffuser facing the impeller chamber or the intake side of the impeller.
- the diffuser can be produced in a simple manner by means of two tool parts or molded parts which can be moved away from one another in the axial direction and by plastic injection molding, and perfect demolding of the radially projecting and axially projecting guide blade sections (and their possibly existing connecting sections) on Basic body of the diffuser is enabled. It may be favorable, if appropriate, if the main body of the diffuser is fixed or attached to the housing of the centrally arranged intake duct. As a result, a redesign of the pump housing is avoided, so that it can be used for a variety of different types of sosstechniksriospumpen.
- the diffuser may be particularly simple when provided on the main body of the diffuser on the inside a pipe section, in particular is formed, which forms an axial section, in particular end portion of the centrally arranged intake duct.
- the diffuser can be installed particularly easily in the flow path of the liquid heating pump according to the invention. After successful tests, it has been found that, in particular, an embodiment of the invention is suitable for series production in household dishwashers.
- the constructed liquid heating pump is favorable, in which the inner diameter of the diffuser and / or pressure chamber or the outer diameter of the, in particular circular cylindrical, diffuser basic body whose Axialaußenmantel an axially extending portion or the entire portion of the inner boundary wall of the diffuser and / or Pressure chamber forms, between 5.5 cm and 6.5 cm, in particular equal to about 6.2 cm, and the outer diameter of the diffuser and / or pressure chamber whose outer boundary wall partially or completely formed in particular by the heating device, preferably a heating tube is , chosen between 7 cm and 7.5 cm, in particular approximately equal to 7.3 cm.
- the outer diameter of the impeller is expediently chosen to be between 3.8 and 4.4 cm, in particular equal to approximately 4.2 cm.
- the main body of the diffuser of this tested is designed as an elongated circular cylinder. Preferably, it has an axial length between 2 cm and 4 cm. It has three combined vanes according to the above explanations. When viewed in the circumferential direction, they are expediently arranged offset by approximately 120 ° to each other.
- the respective endally axially projecting Leitschaufelabitesver run preferably in the circumferential direction over a Zentriwinkel Scheme between 50 ° and 90 °, considered its connecting portion in the circumferential direction preferably over a Zentriwinkel Scheme between 30 ° and 60 ° and the axialaumantel document associated, radially projecting vane section preferably over a Zentriwinkel Suite between 50 ° and 90 °.
- the diffuser is in its fixed installation position expediently such angular position oriented aligned, that one of the three endally axially projecting vane sections in the polar coordinate system considered in the angular range between 10 ° and 90 °, its connecting portion in the angular range between 90 ° and 135 °, and the axialaumantel document associated, radially projecting vane section in the angular range between 135 ° and 205 ° runs.
- this liquid heating pump is advantageously for over the intake air sucked air bubbles a passage time of at most 6 seconds, in particular between 3 seconds and 6 seconds, preferably of about 5 seconds possible.
- This cycle time is related to the periods to be respected. individual liquid-carrying partial rinses of the rinse cycle of a dishwashing program of a domestic dishwasher to be carried out.
- the respective axially projecting vane section expediently projects into the impeller space with an axial extent of between 3 mm and 8 mm, in particular of approximately 5 mm, on the end wall of the main body.
- the invention also relates to a water-conducting household appliance, in particular domestic dishwasher or household washing machine, with a liquid heating pump designed according to the invention.
- FIG. 1 shows a schematic illustration of a domestic dishwasher with an advantageous embodiment variant of a liquid heating pump designed according to the invention
- Figure 2 is a schematic longitudinal sectional view of the liquid heating of
- FIG. 1 A first figure.
- FIG. 1 schematically in longitudinal section the diffuser of the liquid heating of
- FIG. 2 is a schematic perspective view of the liquid heating pump of FIG. 2 in the opened state, in which its first housing part with drive unit contained therein is omitted, the viewing direction being on the end wall of its second housing part facing the first housing part with the hydraulic unit contained therein;
- FIG. 5 shows the second housing part with the hydraulic unit of the liquid heating pump from FIG. 4 viewed in the axial outflow direction, wherein the rear cover disk of the impeller of the hydraulic unit, viewed in the suction direction, is omitted;
- FIG. 6 is a schematic perspective view of a detail of the liquid heating pump from FIG. 4, the diffuser of which, together with the impeller arranged in front of its frontal wall in the axial outflow direction,
- FIG. 7 is a perspective view of an advantageous modification or alternative of the diffuser according to the invention of FIG. 6, together with the impeller arranged in front of its frontal wall in the axial outflow direction, and FIG
- FIG. 8 shows a schematic perspective view of a further advantageous modification of the inventively embodied diffuser of Figure 6 with frontally associated impeller.
- FIGS. 1-8 corresponding parts are provided with the same reference numerals. In this case, only those components of a liquid or water-conducting household appliance are provided with reference numerals and explained, which are necessary for the understanding of the invention.
- FIG. 1 is a schematic side view of a household dishwasher 1. This has a washing container 2 for receiving liquid to be cleaned and then to be dried items such as dishes, pots, cutlery, glasses, cooking utensils and the like on.
- the rinsing container 2 preferably has a substantially rectangular floor plan (viewed from above) with a front side V facing a user in the operating position. There is a feed opening accessible from the front. This can be closed by a front door 3.
- the door 3 is shown in the figure 1 in the closed position and, for example, aufschwenkbar about a lower horizontal axis 3a.
- the feed opening can also be provided at another location of the washing container, for example in its upper side, and can be opened and closed with a closing element, such as a flap.
- washing baskets 4, 5 In the interior of the washing container 2, one or more receptacles such as washing baskets 4, 5 are provided for receiving or holding items to be washed.
- receptacles such as washing baskets 4, 5 are provided in the interior of the washing container 2.
- the number of rinse baskets may vary depending on the extent and type of household dishwasher 1.
- a so-called cutlery drawer may be additionally provided.
- These baskets 4, 5 are via one or more spraying devices 6, 7, 8 with fresh water FW and / or with circulating water, which may be added depending on be carried out OperaTINGgang the wash cycle of a dishwasher each with detergent, rinse aid, and / or other excipients ie with so-called rinsing liquor liquid or rinsing liquor, and thus in general terms with rinsing liquid FL acted upon, which contains predominantly water.
- spraying devices in each case preferably rotatable spraying arms are provided in the interior of the washing compartment 2.
- two rotatable spray arms 6, 7 housed in the washing compartment 2 which act on the items to be washed in the dish racks 4, 5, in particular with an upward spray component.
- the lower spray arm 6 is arranged below the lower dish rack 4.
- the upper spray arm 7 is arranged below the upper dish rack 5.
- other types of spray devices may be provided.
- one or more individual spray nozzles can be accommodated in the washing container 2 in a fixed manner.
- a spraying device 8 is arranged underneath the upper dish rack 5 and associated therewith. It includes one or more individual nozzles, the the liquid FL also carry with an upward component to the dishes in the upper dish rack 5. Alternatively, an application with a downward spray component is possible.
- liquid sprays can also be directed downwards onto the items to be washed in the lower dish rack 4.
- Other spraying devices are alternatively or additionally possible.
- a so-called overhead shower can be provided on the top wall of the washing compartment 2, which has been omitted here in FIG. 1 for the sake of simplicity of drawing.
- the rinsing baskets 4, 5 can be displaced forward, for example, on rollers 10, so as to achieve an access position for the user, in which the rinsing baskets 4, 5 can be loaded and unloaded comfortably.
- webs for the rollers 10 lateral rails in the washing compartment 2 are provided.
- at the respective front edge levels of the washing baskets 4, 5 pull and push handles to simplify the insertion and removal of the washing baskets 4, 5 may be provided.
- the predominant water-containing treatment liquid FL runs after being distributed in the washing container 2 while spraying onto the items to be washed down to a collecting area or pump sump 1 which is preferably recessed in the bottom of the washing container 2. There, the liquid passes through a sieve unit which is in the Figure 1 is additionally indicated by dashed lines. From this collection area, the liquid is passed in the spraying operation or circulating operation of the spraying devices to a liquid heating pump 12 which is fluidically connected to the collecting area 11 and / or drawn in by it.
- the liquid heating pump 12 comprises a circulating pump and, in addition thereto, a heating device.
- the circulation pump of the liquid heating pump 12 the liquid is pumped to a fluidically connected with it distribution unit 14, in particular water switch, and from there to the spray 6, 7, 8 passed. Possibly. the distribution unit can also be omitted.
- the distribution unit can also be omitted.
- FIG. 2 shows, in a schematic longitudinal section, a first advantageous exemplary embodiment of a liquid heating pump 12 designed according to the invention.
- This comprises two main assemblies: a first housing part 28 with a housing therein.
- the first housing part 28 of the electric motor 18 is mounted such that its drive shaft 20 is aligned substantially in the axial direction AR.
- the axial direction AR may preferably be substantially horizontal when the liquid heating pump 12 is installed below the bottom of the washing container 2 in the floor assembly of the household dishwasher 1. Alternatively, in the installed state, of course, they may also deviate from the horizontal, such as at an angle between 10 ° and 70 ° to the horizontal run.
- the first housing part 28 is substantially hollow cylindrical in shape.
- the drive shaft 20 protrudes from the hydraulic unit 19 facing end wall of the first housing part 28 with an end portion.
- an impeller 17 is applied to the front side firmly seated.
- This is in cross-section, ie in a sectional plane to which the axis of rotation 191 of the impeller is perpendicular, formed substantially circular.
- the second housing part 29 with the accommodated in it hydraulic unit 19 forms in the assembled state of the liquid heating 12, an axial extension of the first housing unit 28.
- the second housing part 29 is also formed substantially hollow cylindrical.
- the first housing unit 28 and the second housing unit 29 are joined together by way of preferably releasable coupling means or fastening means 30 to form a closed, compact pump housing in the axial direction.
- Both the first housing part 28 with the drive unit 18 accommodated therein and the second housing part 29 with the hydraulic unit 19 housed therein are each preferably substantially rotationally symmetrical with respect to the rotation axis 191 of the drive shaft 20 or its imaginary extension as the central axis of the liquid heating pump 12.
- the hydraulic unit 19 comprises a centrally arranged suction channel 16 for sucking the liquid FL in an axial suction direction 31 and for feeding the sucked liquid FL into an axially downstream impeller space 40.
- the liquid FL is symbolized by punctures in FIG.
- the central axis 192 of the intake duct 16 is aligned with the axis of rotation or central axis 191 of the drive shaft 20.
- the intake duct 16 is preferably formed by one or more circular-cylindrical pipe sections which are each arranged concentrically to the central axis 192 of the liquid heating pump 12.
- the impeller space 40 is viewed in the intake direction 31 by a Rear wall limited, which is formed by one or more wall parts on the end face of the first housing part 28, on which the drive shaft 191 protrudes with the end attached to her impeller 17 in the impeller space 40 against the suction direction 31. Furthermore, the impeller space 40 viewed in the intake 31 is limited by a front wall, which are formed by one or more wall parts on the end wall of the second housing part 29, which faces the first housing part 28.
- the axial width of the impeller space 40 is selected so that between the impeller 17 facing the end wall of the tubular, in particular circular cylindrical intake passage 16 and the suction-side end wall of the impeller 17, an axial gap ASP and a radial gap RS remains to ensure the free rotation of the impeller 17.
- the axial gap ASP has an axial width between 0.5 mm and 1, 5 mm and the radial gap RS an axial width between 0.5 mm and 1, 5 mm.
- the impeller is preferably formed here in the embodiment as an impeller. It has, viewed in the axial intake direction 31, a front cover plate 171 facing the intake channel 16 and an opposite one at the axial distance, the first one
- Between the two cover plates 171, 172 extend the blades 174 of the impeller 17.
- Both the front cover plate 171 and the rear cover plate 172 are respectively viewed from the intake passage 16 in the opposite direction to the axial intake 31, that is, curved backwards. In particular, they are each concave.
- a centrally arranged inlet opening 402 is provided, which is substantially aligned with the outlet opening 401 of the outlet channel 16.
- the rear cover plate 172 is closed.
- the impeller 17 is mounted on the drive shaft 20 such that it rotatably, that is not abutment arranged with its rear cover plate 172 in a receiving recess deepened in the axial direction AR in the rear wall of the impeller space 40 with a given axial gap to the rear wall is.
- the curvature of the rear cover plate 172 is continued or supplemented by the wall portion of the rear wall of the impeller space surrounding it radially further outside substantially without axial offset.
- the front cover disk 171, radially outer wall portion of the front wall of the impeller space 40 continues the curvature or curvature of the liquid-flowed inside of the front cover disk 171, largely without any axial offset.
- the impeller blades 174 each bridge the axial gap distance between the two axially spaced-apart, opposite cover plates 171, 172 and are attached to the mutually facing inner walls, in particular fortified. Between each two circumferentially adjacent impeller blades 174 is a
- the blades 174 of the impeller 17 are each curved opposite to the direction of rotation 60 of the impeller 17. They each extend in the form of an outwardly opening circular arc section or spiral section whose radially inner end begins approximately at the circumferential circle of the inlet opening 402 of the front cover disk 171 and whose radially outer end terminates approximately at the outer circumference or outer diameter of the front and rear cover disks 171, 172.
- the respective blade of the impeller is preferably set against the radial direction (viewed in a normal plane to which the rotation axis 191 is perpendicular).
- the impeller 17 If the impeller 17 is driven to rotate by means of the drive unit 18 via the drive shaft 20, the liquid FL present in the impeller space 40 will move outward from the center of the impeller 17 with a radial and a circular or azimuthal velocity component into the radially outer region of the impeller space 40 pressed. As a result, there is a higher pressure on the radially outer circumference of the impeller in the impeller space 40 than in the center thereof. In this way, the impeller 40 sucks liquid via the intake duct 16 out of the pump sump or collecting area 11.
- the impeller has a liquid ejection area around its outer peripheral edge from which, during pumping or rotational operation (ie, with a rotating impeller), the liquid is expelled outwardly from the passages between its blades.
- This peripheral liquid ejection area is designated by 173 in FIGS. 1-8.
- the impeller 17 of Figures 1-8 is the peripheral liquid ejection area between the front and rear shrouds 171, 172.
- the liquid FL conveyed in this way by the impeller 17 then flows in a diffuser and / or pressure space 50 arranged axially opposite to the suction direction 31.
- the latter is arranged at least along a partial section of the intake duct 16 around it. It surrounds the intake duct 16 substantially concentrically or coaxially.
- the diffuser and / or pressure chamber 50 is formed substantially annular.
- a diffuser or a flow conditioning device 23 is provided fixedly, which partially converts the kinetic energy induced into the liquid flow by the rotational movement of the impeller 17 into static pressure. It has an elongate base body 231, which forms an axially extending portion of the inner boundary wall or the entire inner boundary wall of the diffuser and / or pressure chamber 50.
- the base body 231 of the diffuser 23 may be supported on or attached to the housing of the centrally arranged intake duct 16.
- the base body 231 is additionally fixed or attached to the housing part 29 via an axially extending tubular support section SAB.
- the main body 231 preferably has an elongate, substantially circular cylinder-shaped tube whose end wall facing the impeller 17 is formed as a wall around the outlet opening 401 of the intake duct 16 and, viewed in the axial intake direction 31, forms the front boundary wall of the impeller space 30.
- This end wall has an annular receiving recess AM1 arranged around the outlet opening of the intake duct 16 for the front cover disk 171 of the impeller 17.
- the inner contour of this receiving well corresponds largely to the suction-side outer contour of the front cover plate 171.
- the axial depth is chosen so that the impeller 17 with its front cover plate 171 so immersed in this, that impeller inside between the inner wall of the front cover plate 171 and the opposite of the receiving trough AM1 in the direction of the impeller 17 projecting, radially outer edge face a largely flush, continuous transition results up to the remaining free radial gap RS to the freewheel of the impeller.
- the radially outer edge zone of the suction side of the impeller 17 facing end wall 233 of the base body 231 is suitably in the axial longitudinal extension of the Axialaußenmantels 232 of the nikzylinderformigen body 231 in the form of a round AB.
- This rounding AB is viewed from the intake passage 16 in the axial intake direction 31 also backwards, in particular concave, curved.
- This end-side rounding AB at the transition from the end wall 233 of the body 231 in the Axialaußenmantel 232, in particular in the circular cylindrical surface of the body 231 undesirable directional influences, swirl losses, or deceleration of the ejected from the impeller FL liquid FL are largely avoided.
- this rounding AB between the radially outer edge zone of the end wall 233 of the base body 231 and the Vietnamesezylinderformigen Axialaußenmantel 232 the reverse path of the liquid flow from the axial suction direction 31 in the 180 ° -back direction favors.
- a depression or channel may optionally be provided as a transition zone between the end wall 233 and the axial outer jacket 232 on the radially outer edge zone of the end wall 233 of the main body 231 facing the suction side of the impeller 17.
- the diffuser and / or pressure chamber 50 is associated with a heating device 26, which serves to heat the fluid FL conveyed by the impeller 17.
- the heating device forms a preferably axially extending portion or the preferably axially extending total portion of the outer boundary wall of the diffuser and / or pressure chamber 50.
- a heater 26 is provided in an axial direction AR extending, preferably circular cylindrical heating tube HZ in an advantageous manner.
- This heating tube HZ surrounds the Vietnamesezylinderformigen main body 231 from the outside substantially concentric or coaxial along an axial length or part here along in the embodiment of Figure 2 substantially along the total axial length of the body 231 with a predetermined radial gap distance 501 such that the diffuser and / or pressure chamber 50 between the Axialaußenmantel 232 of Vietnamese Vietnameseformigen body 231 and the Axialinnenmantel 261 of Vietnamese Vietnamese gap formed.
- the radial gap distance 501 of the diffuser and / or pressure chamber 50 between the Axialaußenmantel 232 of the preferably circular cylindrical body 231 and the smooth Axialinnenmantel 261 of the opposite radial further outside, preferably circular cylindrical heating tube HZ expediently chosen between 3 mm and 8 mm, in particular by about 5.5 mm. This is a significant reduction, in particular about halving the RadialspaltShats between the Axialaußenmantel 232 of the main body 231 and the liquid-flow Axialinnenrmantel construction 261 of the heating tube HZ over previously used in household dishwashers copestechniksLitepumpen.
- the particular Vietnamese Vietnamese body of the diffuser is preferably expanded or increased in the inventively designed sosstechnikscreampumpe that the outer diameter 503 of its Axialaußenmantels 232 at least equal to 80%, in particular between 80% and 90%, preferably about equal to 86% of the outer diameter 505 of the diffuser and / or pressure chamber 50 or the outer diameter 505 of the outer boundary wall 261 of the diffuser and / or pressure chamber 50 is.
- the diameter 505 of the impeller space 40 relative to the outer diameter 504 of the impeller 17 is increased.
- it is approximately equal to the diameter of the outer boundary wall of the diffuser and / or pressure chamber selected.
- an initial section of the heating device 26 can already be accommodated in the impeller space 40, which then extends further into the downstream diffuser and / or pressure space 50.
- an initial portion of the heater 26 forms a portion or the entire portion of the outer boundary wall of the impeller space.
- the heating device is expediently provided by a heating tube HZ, which forms the outer boundary wall 261 of the diffuser and / or pressure chamber 50 along a partial length or the total length of its axial extent.
- the heating tube HZ may in particular be e.g. comprise a circular cylindrical metal tube, the smooth inner circumferential surface or inner wall surface 261 is flowed through by the conveyed liquid. It has on its side facing away from the diffuser and / or pressure chamber 50 outer lateral surface preferably on an electrical insulation layer with applied thereto on the outside Schuleiterbahnen.
- the Schuleiterbahnen may expediently be covered by an additional cover layer, in particular electrical insulation layer to the outside.
- the electrical insulation layer, the heating conductors, and / or the cover layer may in particular be provided with a thick-film technology or with a physical vapor deposition method, e.g. PVD ("physical vapor depositon") method, of course, other types of heating tubes are also possible.
- PVD physical vapor deposition
- the heating device 26 preferably for heating the rinsing liquid to a desired temperature in each Opera Listegang, such as the cleaning cycle or rinse cycle, a dishwashing program to be performed an electricalmonynutzlast between 30 W / cm 2 and 50 W / cm 2 ready.
- a dishwashing program to be performed an electricalmonynMaplast between 30 W / cm 2 and 50 W / cm 2 ready.
- the passage cross-sectional area QF viewed in cross-section annular gap-shaped diffuser and / or pressure chamber 50 is advantageously between 8 cm 2 and 20 cm 2 , in particular selected by about 12 cm 2 .
- the impeller - in particular at an outer diameter of about 4.2 cm - expediently between 3800 and 4800 U / min, in particular around 4200 U / min, circulates in the pumping operation.
- the outer diameter of the impeller is chosen in particular between 3.8 and 4.5 cm, preferably about 4.2 cm.
- the circular-cylindrical diffuser main body of this successfully tested liquid heating pump expediently has an outer diameter of about 6.2 cm, and the heating tube an inner diameter of about 7.3 cm.
- the posstechnikssagenpumpe 12 has a centrally disposed intake passage 16 for sucking the liquid FL in an axial suction direction 31 and for supplying the sucked liquid in an axially downstream impeller space 40.
- an impeller 17 is provided rotatably driven to promote the liquid in a counter to the suction direction 31 axially downstream diffuser and / or pressure chamber 50.
- This diffuser and / or pressure space is preferably arranged coaxially around an axial section or the overall axial section of the intake duct 16 on the outside.
- the diffuser and / or pressure chamber 50 is assigned a fixed diffuser 23.
- This has a, in particular circular cylindrical, base body 231, the impeller 17 facing end wall 233 a suction, ie front boundary wall of the impeller space 40, and the Axialaußenmantel 232 a, in particular axially extending, section or the, in particular, axially extending, Entire portion of the inner boundary wall of the diffuser and / or pressure chamber 50 forms.
- the heating device 26 assigned to the diffuser and / or pressure chamber 50 for heating the conveyed liquid FL expediently forms at least one, in particular axially extending, section or the, in particular axially extending, overall section of the outer boundary wall 261 of the diffuser and / or pressure chamber 50.
- the diffuser and / or pressure chamber 50 which is arranged concentrically around the intake duct 16, follows, opposite to the intake direction 31, ie in the axial outflow direction, a housing outlet 271 with an associated exit side, in particular helical, preferably with an axial extent approximately tangentially outgoing, tubular discharge nozzle 272 for ejecting the liquid FL to.
- the outflow direction of the conveyed liquid pointing upwards in the exemplary embodiment of FIG. 2 is indicated by a directional arrow 34.
- the central axis ZA of the pressure port 272 is inclined relative to the radial direction RR against the axial intake direction 31, ie in the outflow direction, preferably at an acute angle SWI, in particular between 5 ° and 20 °, preferably by about 10 °.
- SWI acute angle
- the liquid heating pump 12 is expediently installed in a base support or a base assembly below the bottom of the washing container 2 in such a way that the discharge nozzle 272 extends from the second housing part 29 upwards in the direction of the bottom of the Rinse tank 2 protrudes.
- the liquid heating pump 12 is thus installed in the dishwasher 1 with a rotational axis of its drive shaft extending substantially in the horizontal or in the axial direction and thus lying in the bottom assembly below the bottom of the washing container 2.
- the outlet 271 is formed with the discharge nozzle 272 preferably as an outwardly opening spiral portion which is integrally formed on the second housing part 29 on the first housing part 28 facing away from the end wall and opposite the cross-sectional plane to which the axis of rotation 191 is perpendicular, opposite to the axial suction direction 31 or opposite to the direction of gravity inclined at an acute angle, the liquid flow, in the diffuser and / or pressure chamber 50 preferably in the form of a contrary to the intake 31 in the axial outflow direction migrating helix or helix on the Pressure port moves to be promoted from this under continuation of this flow movement of the discharge port 272.
- this helical flow path of the liquid FL in the diffuser and / or pressure space and subsequently into the discharge nozzle 272 is indicated by the flow arrow 33.
- the hydraulic-mechanical efficiency in particular captures pressure losses and friction losses in the components of the liquid heating pump. Their volumetric efficiency, however, is determined in particular by any leakage occurring.
- Deviating from or alternatively to the advantageous spatial-geometric shaping of the impeller space and / or the impeller arranged therein of the embodiment of Figure 2 may optionally also other configurations of the impeller space and / or the impeller be appropriate, as long as they each ensure that liquid from the pump sump 1 1 sucked through the intake passage 16 in the axial intake direction 31 in the impeller space 40 and can be deflected there by about 180 ° in the opposite direction in the downstream diffuser and / or pressure chamber 50 while the liquid in the impeller space by the rotational movement of the impeller in the radial direction as well as in the circular direction a sufficient speed component can be given.
- the impeller has spatially curved blades instead of simply curved blades, ie so-called SD blades.
- a so-called semi-axial - used semi-radial impeller instead, a so-called radial impeller in the impeller space 40 may be housed.
- a so-called closed impeller is provided, in which the impeller blades are connected on both sides, each with a disc. This increases the hydraulic efficiency and stabilizes the impeller.
- impellers whose rotating impeller vanes rotate the liquid, i. with a circular velocity component, the problem that centrifugal forces accumulate air in the center of the impeller space or around the hub 175 of the impeller and "clogs" the fluid passages between the vanes, as air accumulates in the center of the impeller space as the impeller rotates , the impeller can no longer build up sufficient pressure to suck liquid through the intake passage from the pump sump and through the impeller space and the downstream diffuser and / or pressure chamber back out to challenge the output side discharge nozzle.
- FIG. 4 schematically illustrates the liquid heating pump 12 of FIG. 2 in a perspective view in the opened state.
- FIG. 5 shows a frontal view of the first housing part 28 facing the end wall of the opened second housing part 29 of the liquid heating pump 12 of FIG 2 when viewed in the axial outflow direction, wherein also viewed in the intake 31 rear cover plate 172 of the impeller 17 of the hydraulic unit 19 is omitted.
- FIG. 6 illustrates diagrammatically, in perspective view, as a detail of the liquid heating pump 12 of FIG. Sor 23 together with the (viewed in the suction direction 31) after the frontal wall 233 arranged impeller 17th
- the three axially projecting vane sections 241, 242, 243 are fixedly arranged on the front wall of the stationary base body 231 facing the impeller in the circumferential direction in each case by approximately the same central angle of approximately 120 ° such that between each two circumferentially adjacent ones, axially protruding vane sections such as 241, 242 away from the peripheral liquid ejection region 173 of the impeller 17 a diesstechniksleitkanal such as RK12 is present, which leads in the impeller space 40 facing end wall 233 of the base body 231 outwardly to the Axialaußenmantel 232 of the main body 231.
- the respective axially projecting vane section 241, 242, 243 extends approximately from the circumferential circle, which is predetermined by the peripheral liquid outlet region 173 on the outer circumference of the impeller 17, to the outer circumferential circle of the circular cylindrical main body 231. It is attached to the impeller space 40 facing closed top surface 233 of the circular cylindrical body 231, which extends between the outer peripheral circle of the outlet opening 401 of the intake duct 16 and the outer periphery of the base body 231, mounted, in particular integrally formed. It may preferably be made of the same plastic material as the main body 231, here as the circular cylinder jacket.
- the respective axially projecting vane section is of the same material and integrally formed on the end face 233 of the main body 231 facing the impeller space 40.
- the respective in the impeller space 40 axially projecting vane portion 241, 242, 243 within the outer periphery of the here preferably circular cylindrical body 231, but not beyond the Axialaußenmantel the body in the radial direction addition.
- the smallest possible radial gap RS remains between the beginning A of the respective axially projecting vane section 241, 242, 243 and the outer circumference of the rotor Running wheel.
- the radial gap RS is selected between 0.5 mm and 2 mm.
- the respective axially projecting vane section 241, 242, 243 covers the entire axial extent ABR of the peripheral liquid outlet region 173 along its entire extension, which in this embodiment extends to the outer circumference of the circular cylinder jacket 232 of the main body 231 enough.
- the respective axially projecting vane section 241, 242, 243 extends in such a way that, viewed from its radially further inward beginning A to its radially outermost end E, it is inclined, in particular between 90 ° and 135 °, preferably approximately 120 °, relative to the radial direction RR of the impeller 17 in the direction of rotation 60 has.
- the liquid ejected from the liquid ejection region 173 of the impeller 17 with a radial and a circular or azimuthal velocity component forms a ramp rising from the peripheral liquid outlet region 173 to the outer circumference of the axial outer casing 232, ie it forms a climbing aid which consists of the Impeller 17 brings ejected liquid FL on a defined guideway, which leads from the peripheral liquid ejection region 173 to the Axialaußenmantel 232 of the main body 231.
- the respective axially projecting vane section 241, 242, 243 has an arcuate shape with a direction of curvature in the direction of rotation 60 of the impeller 17.
- the respective axially projecting vane portion such as 241 with its radially inner initial section AA preferably substantially tangentially from an inner circumferential location on the circle of the liquid ejection region 173rd Runs out of the impeller 17 to the outside and opens with its radially outer end portion EA largely tangentially at a different to this inner circumferential point, outer peripheral location on the outer peripheral circle of the Axialaußenmantels 232 of the body 231.
- the respective axially projecting vane section as viewed here in the embodiment of Figures 2-6 viewed from the front of its outer wall 233 in the axial outflow from its radially further inwardly arranged beginning A to its radially opposite end arranged opposite E is in the form of an outwardly opening circular arc section or spiral section. It is particularly favorable if the respective axially projecting vane section runs in the form of a spiral section, the radius of curvature of which increases from its radially inwardly arranged beginning A to its end E arranged radially further outwards.
- the three axially projecting vane sections 241, 242, 243 are integrally formed on the front wall 233 of the main body 231 facing the impeller space 40 in such a way that they each extend from their radially further inward beginning A to their radially outermost end E in the circumferential direction over a predetermined Zentriwinkel Colour, preferably between 45 ° and 90 ° (viewed in the direction of rotation 60) in the successfully tested diesstechniksutzpumpe, and thereby in each case in the plane defined by this end wall 233 of the body 231 plane or a plane parallel thereto a radial increase or a overcome radial distance which corresponds approximately to the radial distance RA between the liquid ejection region 173 and the Axialaußenmantel 232 of the base body 231.
- the respective axially projecting vane section therefore serves firstly as a release agent or climbing aid (in the radial direction) for the liquid FL ejected radially further inwards on the outer circumference of the impeller into the diffuser and / or pressure chamber 50 situated further outward in the radial direction.
- the freely axially protruding guide window sections around the outer circumference of the impeller serve as a circumferential interrupting means, which form the formation of a single or multiple 360 ° circular section. Prevent flow in the impeller space.
- the radial distance RA is between 5 mm and 10 mm.
- the respective axially projecting guide blade section 241, 242, 243 preferably has an axial extent of between 3 mm and 8 mm, in particular of approximately 5 mm.
- each other arranged guide vane sections 241, 242, 243 each considered approximately in an angular range between 45 ° and 90 ° in the circumferential direction, can be on the liquid flow, which from the Run impeller 17 at the peripheral liquid outlet region 173, largely uniformly with a radial and a circular Umlenkkomponente act and the liquid in the circumferential direction considered largely uniformly distributed in the annular cross-section diffuser and / or pressure chamber 50 initiate.
- an acute intermediate angle Wl of at most 50 °, in particular between 30 ° and 45 °, enclosed.
- the intermediate angle Wl is advantageously chosen to be approximately equal to 41 °.
- the intermediate angle Wl is comprised of the exit angle AW included between the tangential extension of the outer end portion of the respective impeller blade 174 and the tangent which abuts the intersection of the outer impeller blade end and the outer circumferential circle of the impeller 17 and the entrance angle EW included between the tangent at the beginning portion AA of the respective axially projecting vane portion such as 241 and the tangent at the intersection of the start portion AA of the vane portion such as 241 with the outer circumference of the impeller 17 thereon is created.
- the liquid by the rotational movement of the impeller blades has been given, minimizes or avoids the entry angle EW is expediently less than 15 °, in particular between 8 and 12 °, selected.
- the respective vane section such as e.g. 241, 242, 243 for the liquid ejected on the outer circumference of the impeller, a guide track or a guide path having a slightly greater slope than the flow path impressed by the impeller blades, the liquid from the outer circumferential circle 173 of the impeller 17 away in an axial outer jacket 232 of the diffuser basic body leading ascension path to force.
- the radially further inward beginning A of the respective axially projecting vane section expediently has a contour which is different from the contour of the output-side end of the respective impeller vane.
- the beginning A of the respective axially projecting vane section runs in the form of a bevel transverse to the end contour of the output side end of the respective vane of the impeller.
- an acute angle SW between 20 ° and 60 ° is enclosed between the axially extending edge of the outer end of the respective impeller blade and the edge of the start A of the respective axially projecting vane section transversely opposite this impeller vane end edge.
- three radially projecting vane sections 251, 252, 253, viewed in the direction of rotation 60 are each offset by approximately the same circumferential angle of preferably approximately 120 °.
- the respective helically shaped, radially projecting vane section on the axial outer casing has an axial pitch, preferably between 2.5 and 3.5 cm, in particular approximately 3 cm.
- a guide vane-free end section of the main body follows in the axial outflow direction.
- This has an axial length preferably between 2 cm - 5 cm in the case of the liquid heating pump tested for series production.
- the radially further outwardly arranged end portion EA of the respective end-side axially projecting vane portion such as 241 is here in the embodiment of the figures 2-6 via a particular integrally formed on him connecting portion VA with a viewed in the direction of rotation 60 of the impeller 17 subsequently associated, axialau conference- side radially projecting vane portion such as 251 connected.
- the connecting portion VA ensures a substantially continuous, uninterrupted, ie continuous transition between the end portion EA of the axially projecting on the end wall 233 of the body 231 Leitschaufelabitess such as 241 and the initial portion of him on the Axialaußenmantel 232 of the body 231 associated radially projecting Guide vane section such as 251.
- the connecting portion VA is preferably located a distance from the liquid ejection region 173 of the impeller 17, which corresponds in a normal plane to the axis of rotation about the radial distance between the outer periphery of the impeller 17 and the outer periphery of the end wall 233.
- the connecting section VA is preferably spaced from the impeller 17 by between 0.8 cm and 1.2 cm.
- the connecting portion VA extends along an outer peripheral portion of the suction side of the impeller 17 facing end wall 233 of the main body 231. It has an axially protruding, circular arc segment-like web section AST, which is viewed in the cross-sectional plane of the end wall 233 or mounted, as seen from the impeller space on the end wall 233 on the outer edge of the end wall 233 along a portion whose circular arc-shaped outer circumference, in particular is formed.
- a radially projecting web section RST is attached, in particular integrally formed, on the end face of the impeller space 40 facing this axially projecting, arcuate section-like web section AST along its entire length.
- the radially projecting web section RST forms an approximately 90 ° fold with respect to the axially projecting web section AST. It can be favorable, in particular, if the axial extent of the axially projecting web section AST decreases steadily from its axially projecting vane section such as 241 facing end to its the axialau datemantel documenten radially projecting vane section such as 251 end facing.
- the axially protruding land portion AST extends the frontally axially projecting vane portion such as 241 by a circular arc portion formed on a peripheral edge portion of the outer periphery of the end wall. If the axially projecting vane section, such as 241 in the plane of the end wall 233 viewed spiral portion-like, the axially projecting web portion AST according to an alternative embodiment, this Spiralabintroductorysverlauf the axially projecting vane section such as 241 below accordingly extend.
- the connecting portion VA connects the end-side axially projecting vane portion such as. 241 with this axially outer shell side associated, radially projecting vane portion such. 251, preferably in one piece and of the same material, to form a continuous guide vane.
- the hydraulic efficiency of the inventive designed liquid heating pump and its ventilation behavior are particularly improved. Because the radially projecting web portion RST counteracts the axial outflow direction as a barrier or obstacle, the or an axial backflow of an air bubble from the diffuser and / or pressure chamber back into the impeller space and thus ultimately difficult or avoid the center of the impeller space when the Liquid heating pump operates in pump mode.
- the axially extending land portion AST serves as an extension of the radially outer end portion of the axially projecting vane portion of the combined vane and preferably allows a continuous transition into its associated axially outer shell side radially projecting vane portion. In addition, it acts in the impeller against the radial direction of ejection of the impeller as a barrier or obstacle or the backward flow of an air bubble from the diffuser and / or pressure chamber radially inwardly back to the center of the impeller space difficult or avoids when the liquid heating pump operates in pumping operation ,
- the diffuser 23 is expediently positioned in its installed position in such a way that one of the three vane sections, such as the vane section 241 in FIG Polar coordinate system considered in the angular range between 10 ° and 90 °, its connecting portion VA in the angular range between 90 ° and 135 ° and the axialau hitman- side associated, radially projecting vane portion such as 251 in the angular range between 135 ° and 205 °.
- an air bubble in particular from the 12 o'clock range, ie from the upper zone of the diffuser and / or pressure chamber 50, can flow against the predetermined pump outflow direction when the liquid heating pump 12 designed according to the invention starts up in the impeller space 40.
- the radially projecting Web portion RST of the connecting portion VA causes an axial barrier for an air bubble, which is located downstream of the connecting portion VA in the diffuser and / or pressure chamber 50, so that this air bubble is prevented from, in the rotational operation of the Impeller 17 to flow back into the impeller space 40.
- Such an air bubble may be present in an upper cavity of the housing part 29, in particular after a standstill phase of the impeller of the liquid heating pump, and could flow back into the center of the impeller space during a start-up of the impeller in a conventional liquid heating pump (due to effective centrifugal forces which cause the liquid to flow) larger density ejects to the outside, while the air flows through the resulting negative pressure in the center of the impeller space there).
- the first axially projecting vane section 241 and its connecting section VA are arranged in the upper region of the main body 231 to the first axially outer shell side radially projecting vane section 251 such that they are located above the main body 231 in the diffuser and / or pressure chamber 50 existing air bubble in the way to flow back radially inward in the direction of the center of the impeller space 30 in the rotational operation of the impeller.
- This is particularly advantageous when starting, ie at the start of the impeller, an air bubble in an upper cavity of the second pump housing part 29, in particular in the upper region of the diffuser and / or pressure chamber 50 or this possibly downstream outlet 271 is present.
- the respective guide vane section projecting axially on the end wall 233 of the main body 231 facing the impeller chamber 30, such as, for example, ends. 241 on the outer circumference of the main body at that circumferential position at which the viewed in the direction of rotation 60 of the impeller 17 preceding, axialaumantel founded radially projecting vane portion such.
- the diffuser can be produced in a simple manner by means of two tool parts or molded parts movable in the axial direction toward and away from one another using a plastic injection molding process, thus permitting perfect demolding of the radially projecting and axially projecting vane sections on the main body of the diffuser.
- FIG. 7 shows schematically in a perspective view a modification of the diffuser 23 of FIGS. 2-6.
- the modified diffuser is designated by 23 * .
- the impeller 17 In the outflow direction (ie viewed in the opposite direction to the intake direction 31 in the 180 ° direction), the impeller 17 is arranged in front of its end face facing the impeller space.
- This diffuser 23 * has no combined guide vanes, but at the end face of the main body 231 of the modified diffuser 23 * facing the impeller space or the suction side, three individual, separate vane sections 241 * , 242 * , 243 * project axially in the direction of the impeller. They are each offset by approximately the same angle of approximately 120 ° in the circumferential direction. Their course otherwise corresponds to that of the axially projecting vane sections 241, 242, 243 of the diffuser 23 of FIGS. 2-6.
- Each is separated from the axially extending vane sections 241 * , 242 * , 243 * by a gap on the axial outer shell of the main body of the diffuser 23 * individual radially projecting vane sections 251 * , 252 * , 253 * provided. They have approximately the same spiral-segment-shaped course as the radially projecting vane sections 251, 252, 253 on the axial outer jacket 232 of the main body 231 of the diffuser 23 of FIGS. 2-6.
- the respective axially projecting vane section such as 241 *, is positioned in the circumferential direction such that it preferably intersects the gap between a first radially projecting vane section such as 253 * and a downstream radially projecting vane section as viewed in the direction of rotation 60 of the impeller such as 251 * in axial Viewed direction.
- This also largely avoids that an air bubble, which is located in the upper, about 12 o'clock range of the diffuser and / or pressure chamber, can flow back to the center of the impeller space when starting the impeller or in the rotational operation of the impeller.
- This modified diffuser 23 * can easily be replaced by the separate axially projecting vane sections 241 * , 242 * , 243 * and the separate, ie with these unconnected, separate, radially projecting vane sections 251 * , 252 * , 253 * produce two in the axial direction toward each other and wegbewegbewegbarer tool parts in plastic injection molding.
- a perfect demolding of the separate, radially projecting vane sections and the unconnected with these, separate, axially projecting vane sections on the main body of the diffuser is possible.
- FIG. 8 schematically shows, in a perspective view, a second modification of the diffuser 23 of FIGS. 2-6.
- the impeller (viewed in the axial outflow direction) is located in front of the front side of the diffuser facing the impeller space Basic body of the diffuser with drawn.
- the modified diffuser is designated 23 ** in FIG.
- the radially outer wall of the main body radially projecting vane sections 251 - 253 are omitted. It only has the guide blade sections 241-243 projecting axially into the impeller space 30.
- the respective axially projecting vane section 241-243 is formed in particular around the axially projecting arcuate web section AST supplemented.
- three axially projecting vane sections according to the embodiments of Figures 2-8. These are preferably each offset by approximately 120 ° in the circumferential direction to each other. In a corresponding manner, it is expedient to provide three radially projecting vane sections each offset by approximately 120 ° in the circumferential direction on the axial outer shell of the main body of the diffuser, as is the case in the embodiments of Figures 2-8.
- the production of the diffuser remains simple.
- the liquid in the impeller space and diffuser and / or pressure space which is annular in cross-section, can be acted on substantially uniformly.
- two axially projecting vane sections may be sufficient on the end face of the main body of the diffuser facing the impeller space. They then divide expediently the peripheral fluid outlet area around the outer circumference of the impeller viewed in approximately 180 ° - large angle ranges. This also already allows a circular flow to divide into two 180 ° parts, so that it can not come to form a 360 ° circulating circular flow.
- axially projecting vane sections can be. These are then in particular offset by approximately 60 ° in the circumferential direction offset from each other and each associated with a circumferential angle range between 40 and 60 °.
- These axially projecting vane sections may expediently be associated with a corresponding number of radially projecting vane sections on the axial outer casing of the main body.
- the following aspects in particular, individually or in combination, may be expedient:
- a stator or diffuser with guide vanes is secured against rotation concentrically around the intake passage.
- This stator or this diffuser has a base body, which is preferably circular cylindrical. It is in particular increased by expansion of its outer diameter as a solid to the heating surface of the heating pipe or heating tube out, which preferably forms an axial portion or the entire portion of the outer boundary wall of the diffuser and / or pressure chamber.
- the main body of the diffuser is designed as a hollow body. Due to the expansion of the outer diameter of the base body, the radial extent, ie the radial height of the spiral, axially effective Leitschaufelabitese proportionally decreases.
- the perfused by the water or from the liquid, preferably circular in cross-section diffuser and / or pressure chamber also decreases accordingly in cross-section, which increases at the same volume flow rate of flow in this area and thus the heat dissipation of the externally heated cylinder wall of the heating tube .
- the volume of water or liquid volume in the interior of the diffuser and / or pressure chamber also decreases accordingly. Due to the new geometry of the main body of the fixed stator or fixed diffuser, guide vanes acting radially on the stator in the axial direction and thus acting radially on the liquid ejected from the rotor can be placed directly around the impeller, in particular the impeller, which noticeably improve the ventilation behavior of the hydraulic unit after air entry during the liquid or water change or water change.
- one or more axially projecting vane sections are preferably provided in addition to one or more vane sections projecting radially on the axial outer jacket of the main body.
- one or more axially projecting vane sections are preferably provided in addition to one or more vane sections projecting radially on the axial outer jacket of the main body.
- the attachment of the stator in the pump housing can be angular position-oriented, in particular by latching, friction welding, ultrasonic welding, laser welding, mirror welding, gluing, and / or by simple axial clamping between other components of the hydraulic unit.
- latching friction welding
- ultrasonic welding ultrasonic welding
- laser welding mirror welding
- gluing gluing
- simple axial clamping between other components of the hydraulic unit.
- the geometry of the stator can preferably be designed so that a cost-effective production by plastic injection molding with simple open / close tools without slide is possible.
- liquid heating pump shows a lower failure behavior due to lime deposits from the water on the liquid-flow surface of the heating tube. This improves the heat transfer from the heating tube to the water. A deterioration of the heat transfer between the heating tube and the water as a result of calcium deposits as well as self-reinforcing effects due to "PTC effects” eg on heating conductors, which are applied to the outside of the heating tube, and associated "hot spots” are reduced or avoided. Otherwise, the heater would fail due to overheating and thermal breakdown of the electrical insulation layer of the heating tube.
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Abstract
Description
Claims
Priority Applications (1)
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PL17723285T PL3455502T3 (pl) | 2016-05-10 | 2017-04-25 | Pompa grzewcza do cieczy do tłoczenia i podgrzewania cieczy w prowadzącym wodę urządzeniu gospodarstwa domowego |
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DE102016208017.2A DE102016208017A1 (de) | 2016-05-10 | 2016-05-10 | Flüssigkeitsheizpumpe zum Fördern und Aufheizen von Flüssigkeit in einem wasserführenden Haushaltsgerät |
PCT/EP2017/059782 WO2017194301A1 (de) | 2016-05-10 | 2017-04-25 | Flüssigkeitsheizpumpe zum fördern und aufheizen von flüssigkeit in einem wasserführenden haushaltsgerät |
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EP3455502A1 true EP3455502A1 (de) | 2019-03-20 |
EP3455502B1 EP3455502B1 (de) | 2020-06-10 |
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US (1) | US11015616B2 (de) |
EP (1) | EP3455502B1 (de) |
CN (1) | CN109154307B (de) |
DE (1) | DE102016208017A1 (de) |
ES (1) | ES2802608T3 (de) |
PL (1) | PL3455502T3 (de) |
WO (1) | WO2017194301A1 (de) |
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US10993601B2 (en) * | 2019-01-25 | 2021-05-04 | Haier Us Appliance Solutions, Inc. | Dishwashing appliances and pump assemblies |
CN111503054B (zh) * | 2019-01-31 | 2022-05-10 | 三花亚威科电器设备(芜湖)有限公司 | 一种泵 |
CN109700411B (zh) * | 2019-02-12 | 2021-02-02 | 佛山市顺德区美的洗涤电器制造有限公司 | 水槽式洗碗机的冷凝装置及具有其的水槽式洗碗机 |
CN111120336A (zh) * | 2019-12-06 | 2020-05-08 | 广东沃顿科技有限公司 | 加热泵及洗涤设备 |
JP7021688B2 (ja) * | 2020-07-09 | 2022-02-17 | 株式会社鶴見製作所 | 水中ポンプ |
CN114069104A (zh) | 2020-08-07 | 2022-02-18 | 广东汉宇汽车配件有限公司 | 一种动力电池热管理系统用电加热装置 |
DE102021202130B4 (de) | 2021-03-05 | 2024-02-08 | BSH Hausgeräte GmbH | Wasserführendes Haushaltsgerät |
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DE102007017271A1 (de) | 2007-04-12 | 2008-10-16 | BSH Bosch und Siemens Hausgeräte GmbH | Pumpe mit Heizeinrichtung |
DE102010001212A1 (de) * | 2010-01-26 | 2011-07-28 | Robert Bosch GmbH, 70469 | Kreiselpumpe |
DE102010043727A1 (de) * | 2010-11-10 | 2012-05-10 | E.G.O. Elektro-Gerätebau GmbH | Pumpe |
DE102011005138A1 (de) | 2011-03-04 | 2012-09-06 | E.G.O. Elektro-Gerätebau GmbH | Pumpe |
CN102748329B (zh) * | 2011-04-15 | 2017-02-22 | 德昌电机(深圳)有限公司 | 加热泵 |
CN103089710B (zh) * | 2011-10-28 | 2016-07-06 | 德昌电机(深圳)有限公司 | 加热泵 |
DE102011055599A1 (de) * | 2011-11-22 | 2013-05-23 | Hella Kgaa Hueck & Co. | Pumpe für einen Temperaturkreislauf in einem Fahrzeug |
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2016
- 2016-05-10 DE DE102016208017.2A patent/DE102016208017A1/de not_active Withdrawn
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2017
- 2017-04-25 CN CN201780029185.0A patent/CN109154307B/zh active Active
- 2017-04-25 ES ES17723285T patent/ES2802608T3/es active Active
- 2017-04-25 EP EP17723285.7A patent/EP3455502B1/de active Active
- 2017-04-25 WO PCT/EP2017/059782 patent/WO2017194301A1/de unknown
- 2017-04-25 US US16/094,227 patent/US11015616B2/en active Active
- 2017-04-25 PL PL17723285T patent/PL3455502T3/pl unknown
Also Published As
Publication number | Publication date |
---|---|
ES2802608T3 (es) | 2021-01-20 |
DE102016208017A1 (de) | 2017-11-16 |
WO2017194301A1 (de) | 2017-11-16 |
EP3455502B1 (de) | 2020-06-10 |
PL3455502T3 (pl) | 2020-11-30 |
US20190093671A1 (en) | 2019-03-28 |
CN109154307A (zh) | 2019-01-04 |
CN109154307B (zh) | 2020-06-30 |
US11015616B2 (en) | 2021-05-25 |
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