WO2017194300A1 - Pompe de chauffage pour liquide destinée au refoulement de liquide dans un appareil électroménager à circulation d'eau - Google Patents

Pompe de chauffage pour liquide destinée au refoulement de liquide dans un appareil électroménager à circulation d'eau Download PDF

Info

Publication number
WO2017194300A1
WO2017194300A1 PCT/EP2017/059772 EP2017059772W WO2017194300A1 WO 2017194300 A1 WO2017194300 A1 WO 2017194300A1 EP 2017059772 W EP2017059772 W EP 2017059772W WO 2017194300 A1 WO2017194300 A1 WO 2017194300A1
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
diffuser
liquid
section
radially
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.)
Ceased
Application number
PCT/EP2017/059772
Other languages
German (de)
English (en)
Inventor
Hans-Holger Pertermann
Stephan Lutz
Igor Hoffmann
Markus Wecker
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BSH Hausgeraete GmbH
Original Assignee
BSH Hausgeraete GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by BSH Hausgeraete GmbH filed Critical BSH Hausgeraete GmbH
Priority to CN201780029137.1A priority Critical patent/CN109154308A/zh
Priority to US16/092,490 priority patent/US20190128284A1/en
Priority to EP17718949.5A priority patent/EP3455503A1/fr
Publication of WO2017194300A1 publication Critical patent/WO2017194300A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • 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 
    • D06F39/08—Liquid supply or discharge arrangements
    • D06F39/083—Liquid discharge or recirculation arrangements
    • D06F39/085—Arrangements or adaptations of pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—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
    • D06F33/00—Control of operations performed in washing machines or washer-dryers 
    • D06F33/30—Control of washing machines characterised by the purpose or target of the control 
    • D06F33/47—Responding to irregular working conditions, e.g. malfunctioning of pumps 
    • D—TEXTILES; PAPER
    • D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F39/00—Details of washing machines not specific to a single type of machines covered by groups D06F9/00 - D06F27/00 
    • D06F39/04—Heating 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 household appliance, in particular McSuggchirr GmbHmaschinen- Bankpumpe or washing machine heating pump, with a centrally disposed suction duct for sucking the liquid in an axial suction direction and feeding the sucked liquid in an axially downstream impeller space,
  • impeller rotatably mounted in the impeller chamber for conveying the liquid in a counter to the suction considered the impeller space axially downstream diffuser space, which is arranged at least around a portion of the intake duct on the outside,
  • the diffuser has a, in particular circular cylindrical, base body with an axial outer shell whose diameter is at least equal to 80%, in particular between 80% and 90%, preferably about equal to 86% of the outer diameter of Diffuser and / or pressure chamber is selected, with a the diffuser chamber associated heating device for heating the pumped liquid, wherein the heater at least one, in particular axially extending, portion of an outer boundary wall of the diffuser space and the Axialaußenmantel of, in particular circular cylindrical body of the diffuser to - forms at least one, in particular axially extending, section of an inner boundary wall of the diffuser space,
  • This liquid heating pump constructed according to the invention is further improved, in particular with regard to its heat dissipation.
  • 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 radial gap width of the diffuser and / or pressure space which is preferably annular in the cross-section, can be reduced so that the liquid flowing through it has an increased flow velocity along its preferably helical path, which is sufficient to increase the electrical heating power produced by the provided to the diffuser and / or pressure chamber heating device is provided to remove in a reliable manner.
  • local overheating and concomitant damage to the heating device are largely avoided.
  • the heating device has an axially extending partial section of the outer boundary wall of the diffuser and / or pressure chamber and the axial outer jacket (axial outer jacket) of the main body of the diffuser has an axially extending, partial section of the inner boundary wall of the diffuser and / or or pressure chamber forms.
  • the heating device can expediently be designed as a heating tube extending in the axial direction.
  • this advantageous dimensioning of the diameter of the axial outer sheath of the diffuser in relation to the outer diameter of the diffuser and / or pressure chamber reduces the dead space volume in the pump housing for the liquid to be conveyed.
  • an improved displacement effect for the liquid flowing therethrough is accompanied. 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 as WO 2008/125488 A2 at the same volume flow of conveyed liquid whose flow velocity in the diffuser chamber, preferably already from the axial beginning portion of the diffuser and / or pressure chamber, so far increased that the provided by the heater thermal heating power in a reliable manner largely on the flowing liquid largely completely transfer.
  • the heating device can now be operated with a higher local thermal power density.
  • 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, wherein the main body of the diffuser on its end face facing the impeller space limited by its outer circumference one or more in the direction impeller axially projecting Leitschau- has feiabitese, each projecting into a arranged around the outer periphery of the impeller around the impeller and liquid ejection in each case outwardly therefrom, in particular deviating from the radial direction in the impeller direction, to the Axialaußenmantel the body to, in particular up to Axial outer shell of the body, extend, which is disposed radially outward than the liquid ejection region of the impeller.
  • the thus constructed liquid heating pump is further improved, in particular with respect to its venting behavior. Due to the one or more vane sections which, due to the outer circumference of the diffuser main body, protrude axially from the end wall facing the rotor chamber to the impeller in the peripheral liquid ejection region, it can largely be avoided that an air bubble from the diffuser and / or or pressure space, 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, preferably has within its outer boundary one or more vane sections which protrude axially in the direction of the impeller and project into its peripheral liquid ejection region and respectively outwardly therefrom toward the axial outer casing 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, can on the out of the impeller, preferably with a radial and circular velocity component, out conveyed Liquid flow-conducting low to be acted on their introduction into the diffuser and / or pressure chamber.
  • 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 arrange and dimension the diffuser and / or pressure chamber largely independently of the impeller, in particular of its geometry, position and / or size, in particular its outer diameter.
  • 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.
  • This advantageous diffuser construction with the one or more guide blade sections axially projecting into the impeller space permits, preferably the diameter of the inner boundary wall of the diffuser and / or pressure chamber, and thus - if this is expediently formed at least partially by the axial outer casing of the diffuser main body - set the diameter of the Axialaußenmantels of the main body of the diffuser, and / or 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 of between 40% and 80%, in particular between 60% and 70%, of the diameter of the axial outer shell of the, in particular circular cylindrical, body of the diffuser is selected.
  • the advantageously designed diffuser advantageously provides degrees of freedom in local positioning of the diffuser and / or pressure chamber and / or dimensioning of the passage cross-sectional area of the diffuser and / or pressure chamber with the guide vane sections projecting axially into the impeller space.
  • the heating device forms at least one, preferably axially extending, section of the outer boundary wall of the diffuser and / or pressure chamber, in order to ensure sufficient flow of this heated section of the outer boundary wall with liquid for proper removal of the there to ensure the thermal power provided.
  • the flow velocity of the diffuser and / or pressure space preferably be increased helically in the axial direction advancing liquid such that a there provided by the heating device provided thermal heat output can be properly dissipated.
  • the one or more guide blade sections projecting axially from the end wall of the diffuser base body and projecting into the liquid ejection area of the impeller, it is now advantageously possible to significantly increase the diameter of the impeller space relative to the outer diameter of the impeller, and in particular significantly more than the radial play usually required for the free rotation of the impeller.
  • 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.
  • a starting section of the heating device forms a partial section or the entire section of the outer boundary wall of the rotor chamber.
  • the axial length of such an advantageously designed diesstiksSWe can be compared to the axial length of previous diesstechniksutzpumpen shorten, so that for them (compared to a construction in which the initial portion of the heating device only begins in the diffuser and / or pressure space,) less Slot is required in the household appliance such as in the bottom assembly of a dishwasher.
  • the average diameter of the impeller space selected 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 liquid heating pump designed according to the invention extends in the variant embodiment described above as being advantageous of the diffuser base body) of the respective in the direction of the impeller space axially projecting vane portion approximately from the outer periphery 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 Body, but not in the radial direction beyond.
  • a fixed diffuser with a, preferably elongated in the axial direction, in particular circular cylindrical body in which at the end face facing the impeller space limited by the outer periphery one or more vanes in the direction of impeller protrude axially such that they each protrude into a disposed about the outer periphery of the impeller around the impeller liquid ejection region and each inclined away from this outwardly, in particular deviating from the radial direction in the impeller direction or inclined to the Axialaußenmantel the body to, in particular to extend to the axial outer shell of the body, which is arranged radially further outward than the liquid ejection area, are in the rotational operation of the impeller of this outwardly promoted liquid and also possibly contained in it or entrained air bubbles vo
  • flow guidance paths defined in the direction in particular with the exception of the axial outer casing of the main body which is
  • These one or more axially extending vane sections promote the removal of the liquid ejected from the rotary driven impeller and any air bubbles contained or entrained therefrom, away from the impeller space and out of the impeller space into the suction direction, i.e., the suction direction. in the outflow axially downstream diffuser and / or pressure chamber into it.
  • ßigerweise such that they cause a Entwirbelung the otherwise surrounding the impeller during its rotational operation adjusting circulating 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 outlet on the outer circumference of the impeller to the opposite radially outwardly disposed axial outer casing of the main body of the diffuser passes.
  • 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 advantageous diffuser design which has one or more end wall axially projecting vane sections, can be particularly improved avoided that accumulates in the rotational operation of the impeller during the conveyance of liquid air in the center of the impeller space, in particular around the hub of the impeller around.
  • 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.
  • the one or more axially projecting vane sections facilitate their removal by the conveyed liquid from the impeller space into the diffuser and / or pressure chamber, through it and then out of the discharge nozzle.
  • the respective axially projecting Leitschaufelab- section leads 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 guide from the peripheral liquid ejection region of the impeller outward to the Axialaußenmantel the main body of the diffuser, in particular to the Axialaußenmantel the body, which is arranged radially further out than the liquid ejection region of the impeller.
  • the thus formed liquid heating pump is therefore characterized by an improved venting behavior with a shorter venting time both in the current liquid conveying operation and when starting or starting the impeller.
  • the liquid heating pump constructed according to the advantageous embodiment during the rotational operation of the impeller there is less or no accumulation of air in the center of the impeller space around the hub or impeller shaft, even though not on the input side air is sucked into the centrally arranged intake duct of the liquid heating pump during the conveyance of the liquid.
  • This may be the case, for example, if the liquid level in the intake duct is lower than the interior height of the intake duct, so that above the liquid level there is a remaining air-filled empty space in the intake duct.
  • 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 sector section, of the preferably rotationally symmetrical, in particular approximately circular cylindrical, impeller space, viewed in the direction of rotation of the impeller from a first, axially projecting one Guide 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 does not fully retract Direction of rotation of the impeller slowed down.
  • 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 rotation direction (and thus not in the form of a concentric circular ring section)
  • the liquid can deflect with a radial direction component in the direction the Axialau outer shell of the body and / or the outer boundary wall of the impeller space to be impressed.
  • 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 the pressure chamber retains a sufficiently large part of the kinetic energy imparted 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.
  • it winds helically or helically around the axial outer casing of the preferably circular-cylinder-shaped basic body through the preferably annular-ring-shaped diffuser and / or pressure space to the outlet-side discharge nozzle. It thus moves along this helical trajectory with an axial and a circular flow velocity component through the diffuser and / or pressure space.
  • the heating device forms a partial section or the entire section of the outer boundary wall of the diffuser and / or pressure chamber-the electric heating power provided by the heating device is largely uniform and reliable in the circumferential direction and in the axial direction the pumped in the pumping liquid can be removed without causing local overheating of the heater. Also, less calcium can deposit on the heating device.
  • Such a shape of the respective axially projecting vane section favor the detachment in an advantageous manner the conveyed liquid from the peripheral outer circumference of the impeller in a flow path, which (viewed from the impeller perpendicular to the impeller space facing end wall of the body considered) snail-like from the liquid ejection region of the impeller leads to the Axialaußenmantel the body and then merges into a trajectory, the in the axial direction of the impeller space through the preferably circular ring-shaped diffuser and / or pressure chamber through the axial outer shell of the base body continues to encircle helically.
  • the respective axially projecting vane section with its radially inner initial section substantially tangentially from a inner circumferential point on the circle of the liquid ejection region of the impeller runs outward and opens with its radially outer end substantially tangentially at a different from this inner circumferential point, outer peripheral point on the outer peripheral circle of the Axialaußenmantels it body.
  • the respective axially projecting vane section viewed in the plane of the front wall or a plane parallel thereto, runs in the form of a spiral section whose radius of curvature is arranged radially further out from its radially further inward beginning to its opposite End increases.
  • the respective axially projecting vane section projects so far from the impeller facing the end wall of the main body of the diffuser in the direction impeller that it at least along its the impeller liquid ejection region facing the starting portion, in particular along its entire extension, the axial width of the Liquid ejection region of the impeller partially or completely covered from the outside.
  • Liquid pump further improved.
  • For circular liquid leakage currents are largely avoided, which could lead to their demixing and then to an unwanted Heilblasenan- collection in the center of the impeller space due to their centrifugal or centrifugal motion associated centrifugal forces and the different densities of liquid, especially water, and air when the impeller rotates in pumping operation of the liquid heating pump.
  • the liquid heating pump constructed in accordance with the invention is favorable for series use in household dishwashers, in which the inside diameter of the diffuser and / or pressure space or, equivalently, the outside diameter of the, in particular circular cylindrical, Diffuser basic body whose Axialaußenmantel forms an axially extending portion of the inner boundary wall of the diffuser and / or pressure chamber, 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 or pressure chamber whose outer boundary wall is partially or completely formed in particular by the heating device, preferably a heating tube, is selected between 7 cm and 7.5 cm, in particular approximately equal to 7.3 cm.
  • 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 preferably has three by 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 extent corresponds approximately to the axial width of the peripheral liquid ejection region of the impeller with the addition of the axial gap dimension between the end wall of the main body facing the impeller chamber and the suction-side end face of the impeller. This is formed when using a so-called closed trained 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 section formed by it or the overall section of the outer boundary wall of the diffuser and / or pressure space formed by it, in particular when using the liquid heating pump according to the invention in a household dishwasher, has an electrical surface heating load between 30 W / cm 2 and 50 W / cm 2 .
  • 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
  • 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 rotates, then the volume flow rate of funded liquid is so large that the heating power provided by the heating device can be transferred as far as the liquid flowing to them, that local overheating of the heating device, which lead to unwanted calcification, thermal damage or even failure of the heating device could be largely avoided.
  • 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. It may optionally be favorable, if the radially outer edge zone of the suction side of the impeller facing end wall of the main body of the diffuser merges into the axial longitudinal extension of the Axialaußenmantels of the main body in the form of a rounding. As a result, the hydraulic efficiency of the liquid heating pump designed according to the invention is further improved, since undesired losses of kinetic energy, which has been imparted to the liquid by the rotating impeller, are further improved 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 engages externally with the outer circumferential liquid ejection region of the impeller over its axial width, at least with its initial section, in particular along its entire extension a remaining radial gap, which (in the flow direction) is selected in the region of its beginning, in particular between 0.5 mm and 2 mm.
  • This radial gap provides a sufficient clearance for the 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. Around the impeller circulating leakage currents 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 which is different from the contour of the output end of the respective vane of the impeller.
  • 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 profile on the axial outer casing of the base body that they impose an axial directional component on the fluid flowing into the diffuser and / or pressure chamber from the impeller space, 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 axial outer-blade side radially projecting vane section runs in the form of a spiral section, in particular helix 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.
  • the helical section or helix section of the respective axially outer shell side radially projecting vane section advantageously advantageously causes a barrier which prevents backflow of an air bubble possibly present in the diffuser and / or pressure chamber against the axial pump. Outflow direction in the impeller space difficult or prevented.
  • 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.
  • 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 respective guide vane section projecting axially from the end wall of the main body into the impeller space preferably arcuately, preferably spirally extending, via a connecting section, in particular integrally formed with it in the direction of rotation of the Impeller considered subsequent, axialITAmantel document assigned Neten, radially projecting, preferably helically extending, Leitschaufelabites continuously, in particular substantially continuously, is connected to a combined guide vane.
  • This combined guide vane allows the fluid to have a flow path that is even further improved in terms of flow, from the peripheral fluid ejection region of the impeller in the impeller chamber into and through the diffuser and / or pressure chamber.
  • 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 vane and preferably allows a continuous transition in the associated, axially outer shell side radially projecting vane portion 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 diffuser as a whole can be easily manufactured.
  • 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 (viewed in the direction of the end wall of the main body equipped with one or more axial vane sections) detached from the outer periphery of the rotating impeller and along a spiral portion-like route to the diffuser and / or radially outer diffuser or pressure chamber is promoted and then viewed spatially in the axial direction helically the base 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 extends on the axial outer jacket of the main body of the diffuser and its upstream extension formed by the radially projecting web section of the connecting section in an outer peripheral region of the main body in the gap between the radially outer end of a first axially extending vane portion and the radially outer end of a viewed in the direction of rotation of the impeller adjacent, second axially projecting vane portion.
  • the respective radially projecting vane section on the axial outer shell of the main body of the diffuser and its upstream extension extends through the radially projecting web section of the connecting section in an outer peripheral region of the main body in the gap when looking at the suction side of the impeller facing end wall of the main body the radially outer end of a first axially projecting vane section and the radially outer end of a viewed in the direction of rotation of the impeller adjacent, second axially projecting vane section.
  • 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. In this way, an excellent self-deaeration behavior of the liquid heating pump according to the invention results.
  • the respective guide vane section axially projecting 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 the circumferential outer end of the main body when viewed in the direction of rotation of the impeller viewed radially downstream guide vane portion downstream viewed at the axial outer shell of the body ends with an axial distance to the impeller space or the suction side of the impeller facing the end wall of the main body of the diffuser sors.
  • the diffuser can be moved in a simple manner by means of two tool parts or molded parts movable toward one another and away from one another in the axial direction can be produced in plastic injection molding and proper demolding of the radially projecting and axially projecting vane sections (and their possibly existing connecting sections) is made possible on the main body of the diffuser. 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 can be installed particularly easily in the flow path of the liquid heating pump according to the invention.
  • the outer diameter of the impeller is expediently chosen between 3.8 and 4.4 cm, in particular equal to about 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 as described above. When viewed in the circumferential direction, they are expediently arranged offset by approximately 120 ° to each other.
  • the respective endally axially projecting Leitschaufelabitesvernote preferably runs 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 Leitschaufelab- preferably cuts over a Zentriwinkel Suite between 50 ° and 90 °.
  • the diffuser in its fixed installation position is expediently aligned such angular position oriented that considered one of the three frontally axially projecting vane sections in the polar coordinate system 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 °.
  • 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 favorable in connection with the time periods to be kept of the 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 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 corresponds in the case of an impeller in which the liquid ejection region between the front and rear cover plate, approximately their axial distance 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.
  • the invention also relates to a water-conducting household appliance, in particular household dishwasher or household washing machine, with a liquid heating pump designed according to the invention.
  • FIG. 1 shows a diagrammatic longitudinal sectional view of the diffuser of the liquid heating pump of FIG. 2, schematically showing in perspective 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 directed to the end wall of its second housing part facing the first housing part with 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 in
  • FIG. 6 is a schematic perspective view of a detail of the liquid heating pump of FIG. 4, the diffuser of which, together with the impeller arranged in front of the end wall thereof 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 viewed in the axial outflow direction before the frontal wall disposed impeller, and
  • 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.
  • liquid heating pump which is installed in a domestic dishwasher.
  • This liquid heating pump may also be used in other liquid-conducting domestic appliances, such as e.g. in a washing machine as a component of the washing unit or posstechniksumisselznikanks be provided.
  • 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.
  • a closing element such as a flap.
  • one or more receptacles such as washing baskets 4, 5 are provided for receiving or holding items to be washed.
  • exactly two rinse baskets or baskets 4, 5 are provided one above the other.
  • 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 sprayers 6, 7, 8 with fresh water FW and / or with circulating water, the depending on be carried out OperaTINGgang the rinse cycle of a dishwashing program in each case with detergent, rinse aid, and / or other excipients may be added, ie with so-called rinsing liquor or rinse liquor, and thus in general terms with rinsing fluid FL acted upon, which contains predominantly water.
  • 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.
  • FIG. 1 In the exemplary embodiment of FIG.
  • a spraying device 8 is arranged underneath the upper dish rack 5 and associated therewith. It comprises one or more individual nozzles, which also convey the liquid FL with an upward component to the dishes in the upper dish rack 5.
  • 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 may be provided on the top wall of the washing container 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.
  • As tracks for the rollers 10 side rails are provided in the rinse tank 2.
  • the predominant water-containing treatment liquid FL After being distributed in the washing container 2, it sprays onto the items to be washed downwards to a collection area or pump sump 1 which is preferably recessed in the bottom of the washing container 2.
  • the liquid passes through a sieve unit, which is additionally indicated by dashed lines in FIG. From this collecting area, the liquid in the spraying operation or circulating operation of the spraying devices is conducted to a liquid heating pump 12 which is fluidically connected to the collecting area 11 and / or sucked in by it.
  • the liquid heating pump 12 comprises a circulating pump and, in addition thereto, a heating device.
  • a circulation pump of the liquid heating pump 12 the liquid is pumped to a distributor unit 14, in particular a water distributor, which is in fluid communication with it, and from there to the spray devices 6, 7, 8. Possibly. the distribution unit can also be omitted.
  • a drainage pump 9 for pumping out the liquid from the washing container 2, this is pumped out of the washing container 2 by means of a drainage pump 9 as wastewater AW.
  • 2 shows a schematic longitudinal section of a first advantageous exemplary embodiment of a liquid heating pump 12 designed according to the invention.
  • first housing part 28 with a drive unit 18 accommodated therein, in particular an electric motor housed therein, and a second housing part 29 with a hydraulic unit 19 accommodated therein.
  • 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, it can also deviate from the horizontal, for example at an angle between 10 ° and 70 ° to the horizontal.
  • the first housing part 28 is formed substantially hollow cylindrical.
  • 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 over, preferably again detachable, coupling means or fastening means 30 assembled into 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 suction direction 31 limited by a rear wall, which is formed by one or more wall parts on the front side of the first housing part 28, at which the drive shaft 191 with the end to her fixed impeller 17 protrudes into the impeller space 40 against the suction 31. Furthermore, the impeller space 40 is viewed in the suction direction 31 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. Into this front wall of the impeller space 40, the intake duct 6 with its circular exit opening 401, viewed in cross-section, opens centrally, i.
  • 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 Housing part 28 facing the rear cover plate 172 on. Between the two cover disks 171, 172, the blades 174 of the impeller 17 extend. Both the front cover disk 171 and the rear cover disk 172 are curved in the opposite direction to the axial intake direction 31, ie, backwards, viewed from the intake duct 16. In particular, they are each concave. In the front cover disk
  • a centrally arranged inlet opening 402 is provided, which is substantially aligned with the outlet opening 401 of the outlet channel 16.
  • the impeller 17 is mounted on the drive shaft 20 so as to rotate freely with its rear cover plate 172 in a receiving recess recessed in the axial direction AR in the rear wall of the impeller space 40 with a predetermined axial gap to the rear wall and thus freely rotatable, i. is not arranged abutting.
  • 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, opposite cover plates 171, 172 and are attached to their mutually facing inner walls, in particular fastened. Between each two circumferentially adjacent impeller blades 174, a fluid passage is present.
  • 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). 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 over the Suction channel 16 from the pump sump or collection area 1 1 after.
  • the impeller has a liquid ejection area around its outer peripheral edge from which, during pumping or rotational operation (i.e., 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 peripheral liquid ejection region is located 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 circular.
  • a diffuser or a flow conditioning device 23 is provided fixedly, which partially converts the kinetic energy induced into the liquid flow by the rotation 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. It may be expedient that - as here in the exemplary embodiment of FIG. 2 - a pipe section is provided on the inside of the base body 231 of the diffuser 23, in particular being integrally formed, which has an axial section, preferably an impeller 17. turned end portion, the centrally arranged intake duct 16 forms.
  • 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 elongated, essentially 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 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.
  • the reverse path of the liquid flow from the axial suction direction 31 in the 180 ° -back direction favors.
  • the end wall 233 of the suction side of the impeller 17 may optionally be provided on the radially outer edge zone Base 231 a trough or channel may be provided as a transition zone between the end wall 233 and the Axialaußenmantel 232.
  • 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 circular-cylindrical base body 231 from the outside substantially concentrically or coaxially along an axial length or as here 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 Axialaußen- coat 232 of the circular cylindrical body 231 and the Axialinnenmantel 261 of the circular cylindrical heating tube HZ viewed in cross section, ie considered in a normal plane to which the axis of rotation is perpendicular, is formed annular gap-shaped.
  • 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 circular-cylindrical basic body of the diffuser in the inventive liquid heating pump is preferably expanded or enlarged such that the outer diameter 503 of its axial outer jacket 232 is at least 80%, in particular between 80% and 90%, preferably approximately equal to 86% of the outer diameter 505 of the diffuser and / or pressure chamber 50 or of 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 section of the heating device 26 forms a partial section or the entire section of the outer boundary wall of the rotor wheel 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 comprise, for example, a circular cylindrical metal tube whose smooth inner lateral 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 insulating layer, the heating conductor tracks, and / or the covering layer may in particular be applied with a thick-film technology or with a physical vapor deposition method, such as PVD ("physical vapor depositon") method.
  • PVD physical vapor depositon
  • other types of heating tubes are also possible.
  • liquid heating pump such as 12, which has been successfully tested for series use in household dishwashers
  • the heating device 26 preferably for heating the rinsing liquid to a desired temperature in each Ambizzigang, such as the cleaning cycle or rinse cycle, 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 of 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 .
  • This dimensioning is particularly favorable when the impeller - in particular at an outer diameter of about 4.2 cm - expediently between 3800 and 4800 U / min, in particular by about 4200 revolutions per minute, in 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 advantageously has an outer diameter of about 6.2 cm, and the heating tube has an inner diameter of about 7.3 cm.
  • the liquid heating pump 12 has a centrally arranged suction channel 16 for sucking the liquid FL in an axial suction direction 31 and for feeding the sucked liquid into 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 side, ie front boundary wall of the impeller space 40, and the Axial- outer jacket 232 a, in particular axially extending portion or the, in particular axially extending, the entire section 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 50th
  • the diffuser and / or pressure chamber 50 which is arranged concentrically around the intake duct 16, follows the intake direction 31, ie, in the axial outflow direction, a housing outlet 271, which preferably extends with an axial extension in a helical or spiral section, with an associated exit side, laterally, in particular approximately tangentially outgoing, tubular discharge nozzle 272 for ejecting the liquid FL after.
  • 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 floor assembly below the bottom of the washing container 2 in such a way that the discharge nozzle 272 protrudes upward from the second housing part 29 in the direction of the bottom of the washing container 2.
  • the liquid heating pump 12 is thus installed in the dishwasher 1 with an axis of rotation of its drive shaft running essentially 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 end wall and with respect to the cross-sectional plane to which the axis of rotation 191 perpendicular runs, opposite to the axial suction direction 31 and 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 moved to the discharge nozzle to be conveyed out of this under continuation of this flow movement from the discharge nozzle 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 detects 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 shape 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 suction direction 31 in the impeller space 40 and there can be deflected 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 Radial direction and in the circular direction can be given a sufficient speed component.
  • 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.
  • FIG. 4 schematically illustrates the liquid heating pump 12 of FIG. 2 in a perspective view in the opened state. In this case, the first housing part 28 with the preferably electric drive unit 18 contained therein is omitted. 4, FIG.
  • 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, whereby the rear cover disc 172 of the impeller 17 of the hydraulic unit 19, which is viewed in the intake direction 31, is also omitted.
  • FIG. 6 schematically illustrates, in perspective view, as a detail of the liquid heating pump 12 of FIG. 4, its diffuser 23 together with the impeller (viewed in the suction direction 31) after the front wall 233 thereof.
  • the three axially projecting vane sections 241, 242, 243 are on the front wall of the stationary base body 231 facing the impeller space is arranged fixedly offset in the circumferential direction by approximately the same central angle of approximately 120 ° such that between each two circumferentially adjacent, axially projecting vane sections such as 241, 242 from the peripheral liquid ejection region 173 of FIG Impeller 17 away a remplisstechniksleitkanal such as RK12 is present, which leads in the impeller space 40 facing the end wall 233 of the base body 231 outwardly to the Axialaußenmantel 232 of the base body 231.
  • the diesstiksleitkanal RK12 viewed in the direction of rotation 60 of the impeller 17 between the first axially extending vane portion 241 and the circumferentially following, second axially extending vane portion 242, the diesstiksleitkanal RK12, between the second axially projecting vane portion 242 and the circumferentially following, third axially projecting Guide vane portion 243 of the copesstechniksleitkanal RK23 and between the third axially extending vane portion 243 and the circumferentially following the first axially projecting vane section 241 of the copessmaschinesleitkanal RK31 provided.
  • 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.
  • At least its initial section AA covers the axial width AB of the liquid outlet region 173 between the two cover plates 171, 172 of the impeller 17.
  • a radial gap RS remains between the beginning of the respective axially projecting vane portion 241, 242, 243 and the Outer circumference of the impeller.
  • 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 the exemplary 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 one of the peripheral liquid outlet Area 173 to the outer periphery of the Axialaußenmantels 232 rising ramp, ie it forms a climbing aid that brings the expelled from the impeller 17 fluid FL on a defined guideway leading 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 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 projecting Leitschau- feiabitese around the outer circumference of the impeller seen around serve as a means of interruption in the circumferential direction, which prevent the formation of a single or multiple 360 ° - circular flow in the impeller space.
  • the radial distance RA is between 5 mm and 10 mm.
  • the respective axially projecting vane 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 By axially offset in the circumferential direction about the same central angle of about 120 ° to each other arranged guide vane sections 241, 242, 243, each seen in approximately an angular range between 45 ° and 90 ° when viewed in the circumferential direction, can be on the liquid flow, the from the impeller 17 at its peripheral liquid outlet region 173 flows, 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, if possible low holds or avoids the entrance 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 such as, for. 241, 242, 243 expediently has a contour which is different from the contour of the output-side end of the respective impeller blade.
  • the beginning A of the respective axially projecting vane section in the form of a chamfer runs transversely to the final contour of the output side end of the respective blade of the impeller.
  • an acute angle SW between see in the axial direction extending edge of the outer end of the respective impeller blade and transversely opposite this Laufradschaufel- end edge transverse edge of the beginning of the respective axially projecting vane section an acute angle SW between 20 ° and 60 ° included.
  • 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 helical section of the respective radially projecting vane section 251, 252, 253 begins at the end of the axial outer jacket 232 facing the impeller space 40, ie at the axial longitudinal location of the main body, from which it extends away in the axial outflow direction.
  • the respective helical 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 endally axially projecting vane portion such as 241 is here in the embodiment of 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 below, axiallyau jointman- tel lake radially projecting Leitschaufelabexcellent such as 251 connected.
  • the connecting portion VA ensures a substantially continuous, uninterrupted, ie continuous transition between the end portion EA of the end wall 233 of the main body 231 axially projecting vane portion such as 241 and the initial portion of him on the Axialaußenmantel 232 of the base 231 associated radially projecting vane portion as eg 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 spatially separated 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 section-like web section AST, which is viewed in the cross-sectional plane of the end wall 233 or when viewed from the impeller space from on the end wall 233 at the outer edge of the end wall 233 along a portion whose circular arc-shaped outer circumference attached, in particular is formed.
  • a radially projecting web section RST is mounted, in particular integrally formed, on the front side 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.
  • the axially projecting web section AST extends the frontally axially projecting vane section, such as e.g. 241 by a circular arc portion which is integrally formed on a peripheral edge portion of the outer periphery of the end wall. If the axially projecting vane section, such as e.g. 241 in the plane of the end wall 233 is formed spirally section-like, the axially projecting web section AST according to an alternative embodiment, this Spiralabintroductorysverlauf the axially projecting vane section such. 241 subsequently extend accordingly.
  • the connecting portion VA connects the end-side axially projecting vane section, such as 241, to the radially outer vane section, for example 251, which is axially outer shell-side, preferably integrally and in the same material, to form a continuous 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 extending vane portion of the combined vane and preferably allows a continuous transition in its associated axial outer on the shell side radially projecting vane section into it. 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 the polar coordinate system viewed in the angular range between 10 ° and 90 °, its connecting portion VA in the angular range between 90 ° and 135 ° and the axialau wearman- Telescopically assigned, radially projecting vane section such as 251 in the angular range between 135 ° and 205 ° extends.
  • one of the three vane sections such as the vane section 241 in the polar coordinate system viewed in the angular range between 10 ° and 90 °, its connecting portion VA in the angular range between 90 ° and 135 ° and the axialau jointman- Telescopically assigned, radially projecting vane section such as 251 in the angular range between 135 ° and 205 ° extends.
  • 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 downstream of the connecting portion VA in the diffuser and / or pressure chamber 50, so that this air bubble is prevented from being in the Ro- tion 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 stoppage 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 affecting the liquid due to its greater density) flings outwards 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, radially inward toward the center of the impeller space 30 during rotation operation of the impeller flow back.
  • This is particularly advantageous if, during start-up, ie when starting the impeller, an air bubble is present 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 downstream outlet 271. Possibly.
  • 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 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.
  • the respective axially projecting vane section such as 241 *, is positioned in the circumferential direction such that it preferably projects the gap between a first radially projecting vane section such as 253 * and a radially projecting following in the direction of rotation 60 of the impeller Leitschaufelabites such as 251 * viewed in the axial direction covers.
  • 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 non-connected, separate, axially projecting vane sections on the main body of the diffuser is made 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
  • 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.
  • the respective guide vane section 241, 242, 243 projecting axially on the end face 233 of the main body 231 facing the impeller space 30 in the direction of the impeller 17 stands axially less far towards the impeller at its radially outer end section EA than radially further inwards lying beginning section AA.
  • 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 each offset by approximately 60 ° in the circumferential direction against 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.
  • stator or diffuser with guide vanes is secured against rotation concentrically around the intake channel.
  • This stator or this diffuser has a base body, which is preferably circular cylindrical. He is In particular, it is enlarged by expansion of its outer diameter as a volume body toward the heating surface of the heating pipe or heating pipe, which preferably forms an axial section or the entire section of the outer boundary wall of the diffuser and / or pressure space.
  • 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 basic body of the stationary stator or fixed diffuser, guide vanes acting radially on the stator in the axial direction and thus radially acting on the liquid ejected from the rotor can be placed directly around the impeller, in particular the impeller, surrounding the venting behavior the hydraulic unit noticeably improve after air entry during 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.
  • a radially projecting vane section and depending on this associated axially projecting vane section of the stator preferably each other directly.
  • Noise excitations of the water due to the axially projecting blade edges can be reduced or prevented by bevelling or rounding off the flowed-on blade edges facing the impeller, in particular the impeller.
  • the diameter of the stator, number, height, slope and / or curvature of the axially and radially projecting vane sections and position thereof can be optimized accordingly to the desired results.
  • the attachment of the stator in the pump housing can angular position oriented in particular by latching connection, friction welding, ultrasonic welding, laser welding, mirror welding, gluing, and / or by simple axial clamping between other components of the hydraulic unit.
  • stator With an airtight seal of the inside of the stator from the rest of the hydraulic system, positive effects on hygiene, water consumption, carryover of dirt liquor and frost resistance are to be expected. This can be done by additional sealing elements as well as by training as a 2K plastic part or inexpensively by welding.
  • 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 Due to the increased flow velocity of the water on the heated surface of the heating device also results in a better heat dissipation with reduced temperature load on the heater with consequent lesser tendency to form limescale and hot spots.
  • the combination of radial and axial vane sections improves the venting behavior of the pump after a water change, switching over of the spray level or during concentricity losses. Therefore, the liquid heating pump constructed according to these advantageous aspects is less likely to fail under extreme operating conditions. It is also distinguished by an improved efficiency of its hydraulic part or its hydraulic unit by optimized flow guidance. In sum, their overall performance, reliability, and longevity improve.
  • the trained according to the design principle of the invention liquid heating pump shows a lower failure behavior due to lime deposits from the water on the liquid-flow surface of the heating tube.

Landscapes

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

Abstract

La pompe de chauffage pour liquide (12) selon l'invention présente un compartiment à roue (40) pourvu d'une roue (17) qui est entraînée en rotation, et un compartiment de pression et à diffuseur (50) qui comporte un diffuseur (23) fixe et est monté axialement en aval dans le sens d'écoulement. Un dispositif de chauffage (26) est affecté au compartiment de pression et à diffuseur (50). Le diffuseur présente un corps de base, notamment de forme cylindrique circulaire, comprenant une surface latérale externe axiale (232) dont le diamètre (503) est choisi au moins égal à 80%, notamment compris entre 80% et 90%, de préférence environ égal à 86%, du diamètre externe (505) du compartiment de pression et/ou à diffuseur (50).
PCT/EP2017/059772 2016-05-10 2017-04-25 Pompe de chauffage pour liquide destinée au refoulement de liquide dans un appareil électroménager à circulation d'eau Ceased WO2017194300A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201780029137.1A CN109154308A (zh) 2016-05-10 2017-04-25 用于输送和加热在导水的家用电器中的流体的流体热泵
US16/092,490 US20190128284A1 (en) 2016-05-10 2017-04-25 Liquid heating pump for conveying and heating liquid in a household appliance which uses water
EP17718949.5A EP3455503A1 (fr) 2016-05-10 2017-04-25 Pompe de chauffage pour liquide destinée au refoulement de liquide dans un appareil électroménager à circulation d'eau

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016208020.2A DE102016208020A1 (de) 2016-05-10 2016-05-10 Flüssigkeitsheizpumpe zum Fördern und Aufheizen von Flüssigkeit in einem wasserführenden Haushaltsgerät
DE102016208020.2 2016-05-10

Publications (1)

Publication Number Publication Date
WO2017194300A1 true WO2017194300A1 (fr) 2017-11-16

Family

ID=58609436

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2017/059772 Ceased WO2017194300A1 (fr) 2016-05-10 2017-04-25 Pompe de chauffage pour liquide destinée au refoulement de liquide dans un appareil électroménager à circulation d'eau

Country Status (5)

Country Link
US (1) US20190128284A1 (fr)
EP (1) EP3455503A1 (fr)
CN (1) CN109154308A (fr)
DE (1) DE102016208020A1 (fr)
WO (1) WO2017194300A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113662486A (zh) * 2020-05-13 2021-11-19 佛山市威灵洗涤电机制造有限公司 加热泵和洗碗机

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109957930B (zh) * 2017-12-25 2024-10-29 青岛海尔洗涤电器有限公司 一种自动投放装置及洗衣机
CN111503053B (zh) * 2019-01-31 2025-02-14 三花亚威科电器设备（芜湖）有限公司 泵
CN109700412B (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 水槽式洗碗机及其干燥系统和干燥方法
CN111207090B (zh) * 2020-02-25 2024-12-31 汉宇集团股份有限公司 一种带加热功能的混流泵及应用该泵的设备
DE102020107376B4 (de) * 2020-03-18 2021-11-25 Schaeffler Technologies AG & Co. KG Kühlvorrichtung mit einem durch einen Kühlmittelstrom rotatorisch antreibbaren Verteilerring; sowie elektrische Antriebseinheit
CN113513481B (zh) * 2020-04-10 2024-08-06 佛山市百斯特电器科技有限公司 一种集热泵及其洗碗机
EP3901466B1 (fr) * 2020-04-24 2023-10-25 E.G.O. Elektro-Gerätebau GmbH Procédé de fonctionnement d'une pompe
US11879479B2 (en) 2020-04-30 2024-01-23 Foshan Shunde Midea Washing Appliances Manufacturing Co., Ltd. Flow guiding element, heat collecting pump and dishwasher
CN111481147B (zh) * 2020-04-30 2022-02-25 佛山市顺德区美的洗涤电器制造有限公司 导流元件、集热泵及家用电器
CN117212184A (zh) * 2020-08-07 2023-12-12 汉宇集团股份有限公司 电动汽车电源热管理系统用电泵
CN114688091B (zh) * 2020-12-31 2025-05-16 宁波方太厨具有限公司 一种水泵的蜗壳结构及双泵系统、清洗机
US20240392720A1 (en) * 2023-05-23 2024-11-28 Ralf Centmayer Engine coolant management
DE102023135001A1 (de) * 2023-12-13 2025-06-18 E.G.O. Elektro-Gerätebau GmbH Pumpe und Haushaltsgerät mit einer solchen Pumpe
US20250295286A1 (en) * 2024-03-21 2025-09-25 Haier Us Appliance Solutions, Inc. Dishwashing appliance and electric motor for a fluid pump thereof

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008125488A2 (fr) 2007-04-12 2008-10-23 BSH Bosch und Siemens Hausgeräte GmbH Pompe avec dispositif de chauffage
EP2495444A2 (fr) 2011-03-04 2012-09-05 E.G.O. Elektro-Gerätebau GmbH Pompe
EP2549119A2 (fr) * 2011-07-20 2013-01-23 E.G.O. ELEKTRO-GERÄTEBAU GmbH Pompe
EP2677178A2 (fr) * 2012-06-22 2013-12-25 E.G.O. Elektro-Gerätebau GmbH Pompe
EP2730788A2 (fr) * 2012-11-12 2014-05-14 Coprececitec, S.L. Pompe de circulation de fluides adaptée à un appareil ménager

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007060193A1 (de) * 2007-12-14 2009-06-25 BSH Bosch und Siemens Hausgeräte GmbH Wasserführendes Haushaltsgerät
JP6157302B2 (ja) * 2013-10-10 2017-07-05 株式会社鶴見製作所 竪型電動ポンプのモータ冷却装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008125488A2 (fr) 2007-04-12 2008-10-23 BSH Bosch und Siemens Hausgeräte GmbH Pompe avec dispositif de chauffage
EP2495444A2 (fr) 2011-03-04 2012-09-05 E.G.O. Elektro-Gerätebau GmbH Pompe
EP2495444B1 (fr) 2011-03-04 2015-07-01 E.G.O. ELEKTRO-GERÄTEBAU GmbH Pompe
EP2549119A2 (fr) * 2011-07-20 2013-01-23 E.G.O. ELEKTRO-GERÄTEBAU GmbH Pompe
EP2677178A2 (fr) * 2012-06-22 2013-12-25 E.G.O. Elektro-Gerätebau GmbH Pompe
EP2730788A2 (fr) * 2012-11-12 2014-05-14 Coprececitec, S.L. Pompe de circulation de fluides adaptée à un appareil ménager

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113662486A (zh) * 2020-05-13 2021-11-19 佛山市威灵洗涤电机制造有限公司 加热泵和洗碗机
CN113662486B (zh) * 2020-05-13 2022-09-20 佛山市威灵洗涤电机制造有限公司 加热泵和洗碗机

Also Published As

Publication number Publication date
CN109154308A (zh) 2019-01-04
US20190128284A1 (en) 2019-05-02
DE102016208020A1 (de) 2017-11-16
EP3455503A1 (fr) 2019-03-20

Similar Documents

Publication Publication Date Title
WO2017194300A1 (fr) Pompe de chauffage pour liquide destinée au refoulement de liquide dans un appareil électroménager à circulation d'eau
EP3455502B1 (fr) Pompe de chauffage pour liquide destinée au refoulement et au chauffage de liquide dans un appareil électroménager à circulation d'eau
EP2230985B1 (fr) Appareil ménager à circulation d'eau
EP2150165B1 (fr) Pompe avec dispositif de chauffage
EP3008346B1 (fr) Pompe
DE102017223262A1 (de) Geschirrspülmaschine mit zumindest einer Lufttrocknungseinrichtung
DE1628625B2 (de) Fluessigkeitsverteilungssystem fuer geschirrspuelmaschinen
EP2677178A2 (fr) Pompe
EP2495444A2 (fr) Pompe
DE102012103418A1 (de) Rotationsfilter für einen Geschirrspüler
WO2012062839A1 (fr) Pompe
DE102011079887A1 (de) Wasserführendes Haushaltsgerät mit einer Heizpumpe
WO2024208710A1 (fr) Lave-vaisselle domestique avec dispositif de pompe, et dispositif de pompe pour appareil ménager à circulation d'eau
DE102009002224B4 (de) Wasserführendes Haushaltsgerät, insbesondere Geschirrspülmaschine
EP3047150B1 (fr) Appareil ménager à circulation d'eau comprenant une pompe à rotor noyé
EP3146883B1 (fr) Lave-vaisselle, notamment lave-vaisselle ménager
DE4341215A1 (de) Kreiselpumpe, insbesondere zur Verwendung als Umwälzpumpe für Geschirrspülmaschinen und Waschmaschinen
DE3123275C2 (de) Kreiselpumpe für Geschirrspülmaschinen
EP3545812B1 (fr) Lave-vaiselle, en particulier lave-vaiselle pour le ménage
DE102015116248B3 (de) Geschirrspülmaschine, insbesondere Haushaltsgeschirrspülmaschine
WO2025056317A1 (fr) Pompe et appareil ménager équipé d'une telle pompe
EP1576291B1 (fr) Appareil menager a eau comprenant une pompe d'evacuation et pompe d'evacuation
DE1628625C3 (de) Flüssigkeitsverteilu ngssystem für Geschirrspülmaschinen
DE10033402A1 (de) Kreiselpumpe
WO2018010837A1 (fr) Procédé et installation de traitement de produits alimentaires liquides sensibles à la chaleur et pompe centrifuge pour une telle installation

Legal Events

Date Code Title Description
NENP Non-entry into the national phase

Ref country code: DE

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 17718949

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2017718949

Country of ref document: EP

Effective date: 20181210