EP0182145B1 - One piece synthetic material fan impeller - Google Patents

One piece synthetic material fan impeller Download PDF

Info

Publication number
EP0182145B1
EP0182145B1 EP85113621A EP85113621A EP0182145B1 EP 0182145 B1 EP0182145 B1 EP 0182145B1 EP 85113621 A EP85113621 A EP 85113621A EP 85113621 A EP85113621 A EP 85113621A EP 0182145 B1 EP0182145 B1 EP 0182145B1
Authority
EP
European Patent Office
Prior art keywords
hub
ring
fan wheel
piece
spring bars
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.)
Expired - Lifetime
Application number
EP85113621A
Other languages
German (de)
French (fr)
Other versions
EP0182145B2 (en
EP0182145A1 (en
Inventor
Gerhard Reichert
Friedrich Riedel
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.)
Siemens AG
Original Assignee
Siemens AG
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6249954&utm_source=***_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0182145(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Siemens AG filed Critical Siemens AG
Priority to AT85113621T priority Critical patent/ATE50836T1/en
Publication of EP0182145A1 publication Critical patent/EP0182145A1/en
Application granted granted Critical
Publication of EP0182145B1 publication Critical patent/EP0182145B1/en
Publication of EP0182145B2 publication Critical patent/EP0182145B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers

Definitions

  • the invention relates to a one-piece plastic fan wheel according to the preamble of claim 1; Such a fan wheel is known from DE-C2-29 39 385.
  • fan wheels are driven by small DC motors. These motors are permanently magnetically excited on the stator side; An armature winding is accommodated in the rotor in open slots.
  • the delivered torque pulsates per revolution with the number of slots or a multiple thereof (slot frequency).
  • slot frequency the number of slots or a multiple thereof.
  • this pulsation of the output torque leads to the fact that the wheel tangent executes a small relative movement per revolution in time with the grooving frequency. If this grooving frequency finds a resonance surface in the tangential wheel direction, e.g. in the form of the blade ring of the radial fan, a disturbing frequency tone can be heard at a certain number of revolutions.
  • this excitation can be kept small, but not completely avoided.
  • a radial fan wheel is also known, in which the transmission of undesirable imbalances of the blade ring on the drive shaft and the associated noise-related greater uneven running should be avoided by such elastic intermediate parts between the hub comprising the drive shaft and the blade ring , which compensate for the radial displacement of the blade ring due to unbalance loads by their own deformation and can thereby keep away from the drive shaft and its bearings; for this purpose, in the case of a one-piece plastic part design, the intermediate parts are arranged as essentially tangential partial arc pieces between the hub and the blade ring.
  • the invention has for its object to arrange the spring bars acting as damping elements in the fan wheel with simple manufacturing technology means that with guaranteed low noise, consistently good running properties can be achieved even with long service life.
  • the transmission of a tangential vibration excitation on the motor side to the blade ring can be prevented with certainty and nevertheless good running properties can be guaranteed in a technically simple manner over long operating times, since additional centrifugal loads, e.g. due to dust or dirt deposits, do not lead to an imbalance increase due to radial or axial softness or compliance of the connecting piece between the hub and the blade ring.
  • the fan wheel is radially and axially stable and contains no long, arched, individual springs between the hub and the blade ring, no changes in running and unbalance occur in the heating and air conditioning systems of motor vehicles in continuous operation; at the same time, resonance transmissions between the motor drive shaft and the blade ring are nevertheless avoided, and at the same time the intermediate piece between the hub and the blade ring can be designed without being influenced by the aforementioned problems or solutions with regard to its design.
  • the tangential blade ring natural frequencies are between approximately 200 and 600 Hz.
  • the tangential natural wheel frequency must often be less than 200 Hz, i.e. the intermediate webs must be deeply coordinated or appear soft relative to the wheel mass.
  • the axial length of the spring bars is smaller than the axial length of a hub ring.
  • the axial length of the spring bars is advantageously mutually narrowed and the spring bars are alternately axially offset in the circumferential direction.
  • a closed, low-swirl intermediate piece will be provided between the outer hub ring and the blade ring. If the intake cross section is too narrowly narrowed on one side for the engine in a double-flow fan wheel design, the intake cross section for the engine side can advantageously be opened via openings in the intermediate piece.
  • At least one driver stop is provided on the inner hub ring and is assigned to a spring bar; this can prevent excessive torsional loads on the spring bars.
  • the two-flow plastic fan impeller shown in simplified form in FIG. 1, comprises the drive shaft 4 of a motor 17 with a two-part hub.
  • the hub has an inner hub ring 3 and an outer hub ring 1 arranged concentrically at a radial distance therefrom.
  • Spring bars 2 establish a connection between the outer hub ring 1 and the inner hub ring 3.
  • An intermediate piece 5 with openings 8 adjoins the outer hub ring 1 and extends to the blade ring with the wheel blades 6 and 7.
  • the thickness s2 of the spring bars 2 cannot fall below a minimum thickness. If the frequency tuning requires a softer spring, this can be done by reducing the axial length 12 or 12 of the spring bars 2 (FIG. 4, 5).
  • FIG. 3 shows an axial top view of the spring bars 2 or 2a, which are alternately axially offset over the circumference, the axial length of which can be seen from the sectional views according to FIGS. 4, 5; this results in a particularly simple manner in a soft torsion spring with a radially and axially stable fan wheel.
  • 10 drive stops are designated on both sides of a spring bar, which serve as protection against excessive torsional loads on the spring bars in the event of start-up blocking impacts.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Braking Arrangements (AREA)

Abstract

A single-piece plastic fan wheel for a radial fan comprises a hub, a blade ring having fan blades and an intermediate piece interconnecting the hub and the blade ring. The hub comprises an inner hub ring attachable to the drive shaft of a motor and an outer hub ring connected to the inner hub ring by a plurality of axially and radially extending resilient strips which serve to damp tangential vibrations emanating from the motor owing to pulsations in the torque output thereof.

Description

Die Erfindung bezieht sich auf ein einstückiges Kunststoff-Lüfterrad gemäß Oberbegriff des Anspruchs 1; ein derartiges Lüfterrad ist aus der DE-C2-29 39 385 bekannt.The invention relates to a one-piece plastic fan wheel according to the preamble of claim 1; Such a fan wheel is known from DE-C2-29 39 385.

In Kraftfahrzeugen werden Lüfterräder durch kleine Gleichstrommotoren angetrieben. Diese Motoren werden statorseitig permanentmagnetisch erregt; im Rotor ist eine Ankerwicklung in offenen Nuten untergebracht. Pro Umdrehung pulsiert das abgegebene Drehmoment mit der Nutenzahl oder derem Vielfachen (Nutungsfrequenz). Diese Pulsation des abgegebenen Drehmomentes führt bei einem auf die Motor-Antriebswelle starr aufgezogenen Lüfterrad dazu, daß die Radtangente pro Umdrehung im Takte der Nutungsfrequenz eine geringe Relativbewegung ausführt. Findet nun diese Nutungsfrequenz in tangentialer Radrichtung eine Resonanzfläche, z.B. in Form des Schaufelkranzes des Radialgebläses, so ist bei bestimmter Umdrehungszahl ein störender Frequenzton hörbar. Durch motorseitige Maßnahmen, wie z.B. einer Nutungsschrägung, kann diese Erregung zwar klein gehalten, aber nicht ganz vermieden werden.In motor vehicles, fan wheels are driven by small DC motors. These motors are permanently magnetically excited on the stator side; An armature winding is accommodated in the rotor in open slots. The delivered torque pulsates per revolution with the number of slots or a multiple thereof (slot frequency). In the case of a fan wheel rigidly mounted on the motor drive shaft, this pulsation of the output torque leads to the fact that the wheel tangent executes a small relative movement per revolution in time with the grooving frequency. If this grooving frequency finds a resonance surface in the tangential wheel direction, e.g. in the form of the blade ring of the radial fan, a disturbing frequency tone can be heard at a certain number of revolutions. Through measures on the engine side, e.g. sloping, this excitation can be kept small, but not completely avoided.

Bisher wurde versucht, die Arbeitspunkte des Lüfters außerhalb dieser Resonanzstellen zu legen. Zur Lösung dieses Problems ist es durch die eingangs genannte DE-C2-29 39 385 bekannt, zwischen der mit der Motorantriebswelle verbundenen Nabe und dem Schaufelkranz des Lüfters ein Zwischenstück aus Speichen vorzusehen, die wie ein Bündel parallel geschalteter Federn wirken sollen. Diese Speichen sind derart bogenförmig ausgebildet, daß das durch sie gebildete Zwischenstück schalenförmig gewölbt den antreibenden Motor zumindest teilweise umhüllt.So far, attempts have been made to place the operating points of the fan outside of these resonance points. To solve this problem, it is known from the aforementioned DE-C2-29 39 385 to provide an intermediate piece of spokes between the hub connected to the motor drive shaft and the blade ring of the fan, which should act like a bundle of springs connected in parallel. These spokes are curved in such a way that the intermediate piece formed by them, arched in a bowl-shaped manner, at least partially envelops the driving motor.

Durch die FR-A-2 431 049 ist weiterhin ein Radiallüfterrad bekannt, bei dem die Übertragung von unerwünschten Unwuchten des Schaufelkranzes auf die Antriebswelle und die damit bedingte geräuschbehaftete größere Laufunruhe durch solche elastische Zwischenteile zwischen der die Antriebswelle umfassenden Nabe und dem Schaufelkranz vermieden werden soll, die durch eigene Verformung die radiale Verschiebung des Schaufelkranzes aufgrund von Unwuchtbelastungen kompensieren und dadurch von der Antriebswelle und deren Lagern fernhalten können; dazu sind bei einstückiger Kunststoffteilausbildung die Zwischenteile als im wesentlichen tangential verlaufende Teilbogenstücke zwischen der Nabe und dem Schaufelkranz angeordnet.From FR-A-2 431 049 a radial fan wheel is also known, in which the transmission of undesirable imbalances of the blade ring on the drive shaft and the associated noise-related greater uneven running should be avoided by such elastic intermediate parts between the hub comprising the drive shaft and the blade ring , which compensate for the radial displacement of the blade ring due to unbalance loads by their own deformation and can thereby keep away from the drive shaft and its bearings; for this purpose, in the case of a one-piece plastic part design, the intermediate parts are arranged as essentially tangential partial arc pieces between the hub and the blade ring.

Der Erfindung liegt die Aufgabe zugrunde, mit einfachen fertigungstechnischen Mitteln die als Dämpfungselemente wirkenden Federstege so in dem Lüfterrad anzuordnen, daß bei gewährleisteter Geräuscharmut gleichbleibend gute Laufeigenschaften auch bei hohen Betriebsstandzeiten erreichbar sind.The invention has for its object to arrange the spring bars acting as damping elements in the fan wheel with simple manufacturing technology means that with guaranteed low noise, consistently good running properties can be achieved even with long service life.

Die Lösung dieser Aufgabe gelingt bei einem Lüfterrad der eingangs genannten Art durch die Lehre des Anspruchs 1; vorteilhafte Ausgestaltungen der Erfindung sind jeweils Gegenstand der Unteransprüche.This object is achieved with a fan wheel of the type mentioned at the outset by the teaching of claim 1; advantageous embodiments of the invention are the subject of the dependent claims.

Bei dem erfindungsgemäßen Lüfterrad können die Übertragung einer tangentialen motorseitigen Schwingungsanregung auf den Schaufelkranz mit Sicherheit verhindert und trotzdem in fertigungstechnisch einfacher Weise über lange Betriebszeiten gute Laufeigenschaften gewährleistet werden, da zentrifugale Zusatzbelastungen, z.B. durch Staub- oder Schmutzablagerungen, nicht zu einer Unwuchtvergrößerung aufgrund radialer bzw. axialer Weichheit oder Nachgiebigkeit des Verbindungsstückes zwischen der Nabe und dem Schaufelkranz führen.With the fan wheel according to the invention, the transmission of a tangential vibration excitation on the motor side to the blade ring can be prevented with certainty and nevertheless good running properties can be guaranteed in a technically simple manner over long operating times, since additional centrifugal loads, e.g. due to dust or dirt deposits, do not lead to an imbalance increase due to radial or axial softness or compliance of the connecting piece between the hub and the blade ring.

Da das Lüfterrad radial sowie axial stabil ist und keine langen, gewölbt gebogenen Einzelfedern zwischen Nabe und Schaufelkranz enthält, treten in Heizungs- und Klimaanlagen von Kraftfahrzeugen im Dauerbetrieb keine Lauf- und Unwuchtveränderungen auf; gleichzeitig werden trotzdem Resonanz- übertragungen zwischen der Motor-Antriebswelle und dem Schaufelkranz vermieden, wobei gleichzeitig das Zwischenstück zwischen der Nabe und dem Schaufelkranz hinsichtlich seiner konstruktiven Auslegung von den vorgenannten Problemen bzw. Lösungen unbeeinflußt ausgelegt werden kann.Since the fan wheel is radially and axially stable and contains no long, arched, individual springs between the hub and the blade ring, no changes in running and unbalance occur in the heating and air conditioning systems of motor vehicles in continuous operation; at the same time, resonance transmissions between the motor drive shaft and the blade ring are nevertheless avoided, and at the same time the intermediate piece between the hub and the blade ring can be designed without being influenced by the aforementioned problems or solutions with regard to its design.

Es hat sich gezeigt, daß bei Kraftfahrzeug-Radialgebläsen die tangentialen Schaufelkranz-Eigenfrequenzen zwischen etwa 200 und 600 Hz liegen. Zum Erreichen einer wirksamen Dämpfung muß dann die tangentiale Radeigenfrequenz vielfach kleiner als 200 Hz sein, d.h. die Zwischenstege müssen relativ zur Radmasse tief abgestimmt sein bzw. weich wirken. Um bei dem erfindungsgemäßen Kunststoff-Lüfterrad zur tiefen Frequenzabstimmung eine weiche Feder auch bei einer nicht zu unterschreitenden Mindeststärke der Federstege erreichen zu können, ist nach einer vorteilhaften Ausgestaltung vorgesehen, die axiale Länge der Federstege kleiner als die axiale Länge eines Nabenringes auszuführen. Um trotzdem ein radial und axial laufstabiles Lüfterrad gewährleisten zu können, werden in zweckmäßiger Weise die axiale Länge der Federstege wechselseitig geschmälert und die Federstege in Umfangsrichtung wechselweise axial versetzt angeordnet.It has been shown that in the case of motor vehicle radial fans, the tangential blade ring natural frequencies are between approximately 200 and 600 Hz. In order to achieve effective damping, the tangential natural wheel frequency must often be less than 200 Hz, i.e. the intermediate webs must be deeply coordinated or appear soft relative to the wheel mass. In order to be able to achieve a soft spring in the plastic fan impeller according to the invention for deep frequency tuning even with a minimum thickness of the spring bars, the axial length of the spring bars is smaller than the axial length of a hub ring. In order nevertheless to be able to ensure a radially and axially stable fan wheel, the axial length of the spring bars is advantageously mutually narrowed and the spring bars are alternately axially offset in the circumferential direction.

Normalerweise wird man ein geschlossenes, wirbelarmes Zwischenstück zwischen dem äußeren Nabenring und dem Schaufelkranz vorsehen. Wenn bei einer zweiflutigen Lüfterradausführung der Ansaugquerschnitt einseitig für den Motor zu stark eingeengt wird, kann in vorteilhafter Weise über Durchbrüche im Zwischenstück der Ansaugquerschnitt für die Motorseite geöffnet werden.Normally, a closed, low-swirl intermediate piece will be provided between the outer hub ring and the blade ring. If the intake cross section is too narrowly narrowed on one side for the engine in a double-flow fan wheel design, the intake cross section for the engine side can advantageously be opened via openings in the intermediate piece.

Um bei hohen Verdrehungsmomenten, z.B. Anlaufblockierungsstößen, ein An- bzw. Abbrechen der Federstege mit Sicherheit verhindern zu können, ist nach einer vorteilhaften Ausgestaltung der Erfindung am inneren Nabenring wenigstens ein Mitnehmeranschlag vorgesehen, der einem Federsteg zugeordnet ist; dadurch kann übermäßigen Verdrehungsbelastungen der Federstege vorgebeugt werden.In order to avoid high torsional moments, e.g. Starting blocking impacts to be able to prevent the spring bars from starting or breaking off with certainty, according to an advantageous embodiment of the invention, at least one driver stop is provided on the inner hub ring and is assigned to a spring bar; this can prevent excessive torsional loads on the spring bars.

Die Erfindung wird im folgenden anhand eines in der Zeichnung schematisch dargestellten Ausführungsbeispieles näher erläutert; es zeigt:

  • FIG 1 ein Lüfterrad gemäß der Erfindung in einem axialen Schnitt,
  • FIG 2 eine stirnseitige Draufsicht auf das Lüfterrad gemäß FIG 1,
  • FIG 3 eine stirnseitige Draufsicht auf eine Nabe für ein erfindungsgemäßes Lüfterrad mit zusätzlichen Mitnehmeranschlägen,
  • FIG 4 einen axialen Schnitt durch die Nabe gemäß FIG 3 im Schnittverlauf IV-IV,
  • FIG 5 einen axialen Schnitt durch die Nabe gemäß FIG 3 im Schnittverlauf V-V.
The invention is explained in more detail below with reference to an embodiment shown schematically in the drawing; it shows:
  • 1 shows a fan wheel according to the invention in an axial section,
  • 2 shows a frontal top view of the fan wheel according to FIG. 1,
  • 3 shows an end view of a hub for a fan wheel according to the invention with additional driver stops,
  • 4 shows an axial section through the hub according to FIG. 3 in section IV-IV,
  • 5 shows an axial section through the hub according to FIG. 3 in the section VV.

Das in FIG 1 vereinfacht dargestellte zweiflutige Lüfterrad aus Kunststoff umfaßt mit einer zweiteiligen Nabe die Antriebswelle 4 eines Motors 17. Die Nabe weist einen inneren Nabenring 3 und einen in radialem Abstand dazu konzentrisch angeordneten äußeren Nabenring 1 auf. Federstege 2 stellen eine Verbindung zwischen dem äußeren Nabenring 1 und dem inneren Nabenring 3 her. An den äußeren Nabenring 1 schließt sich ein Zwischenstück 5 mit Durchbrüchen 8 an, das sich bis zum Schaufelkranz mit den Radschaufeln 6 und 7 erstreckt.The two-flow plastic fan impeller, shown in simplified form in FIG. 1, comprises the drive shaft 4 of a motor 17 with a two-part hub. The hub has an inner hub ring 3 and an outer hub ring 1 arranged concentrically at a radial distance therefrom. Spring bars 2 establish a connection between the outer hub ring 1 and the inner hub ring 3. An intermediate piece 5 with openings 8 adjoins the outer hub ring 1 and extends to the blade ring with the wheel blades 6 and 7.

Aus spritztechnischen Gründen kann für die Dicke s2 der Federstege 2 (FIG 2) eine Minimalstärke nicht unterschritten werden. Erfordert die Frequenzabstimmung eine weichere Feder, so kann dies durch Verkleinern der axialen Länge 12 bzw.1'2 der Federstege 2 (FIG 4, 5) geschehen.For reasons of injection technology, the thickness s2 of the spring bars 2 (FIG. 2) cannot fall below a minimum thickness. If the frequency tuning requires a softer spring, this can be done by reducing the axial length 12 or 12 of the spring bars 2 (FIG. 4, 5).

FIG 3 zeigt in axialer Draufsicht die über den Umfang wechselweise axial versetzten Federstege 2 bzw.2a, deren axiale Länge aus den Schnittbildern gemäß FIG 4, 5 ersichtlich ist; dadurch erreicht man auf besonders einfache Weise eine weiche Drehfeder bei radial und axial laufstabilem Lüfterrad. Mit 10 sind Mitnehmeranschläge jeweils beidseitig eines Federsteges bezeichnet, die bei Anlaufblockierungsstößen als Schutz gegen zu starke Verdrehungsbelastungen der Federstege dienen.3 shows an axial top view of the spring bars 2 or 2a, which are alternately axially offset over the circumference, the axial length of which can be seen from the sectional views according to FIGS. 4, 5; this results in a particularly simple manner in a soft torsion spring with a radially and axially stable fan wheel. With 10 drive stops are designated on both sides of a spring bar, which serve as protection against excessive torsional loads on the spring bars in the event of start-up blocking impacts.

Claims (6)

1. One-piece plastics fan wheel, in particular for the blower of a heating- and air-conditioning system in a motor vehicle, including a hub surrounding a drive shaft (4), and a blade ring with blades (6 or 7) held radially spaced thereto, by spring bars (2) operating like a bundle of springs connected in parallel, characterised in that the hub consists of an inner hub ring (3) and an outer hub ring (1) concentric thereto, and in that the spring bars (2) only extending radially, are provided as radially and axially stable connecting elements between the inner hub ring (3) and the outer (1) hub ring.
2. One-piece plastics fan wheel according to claim 1, characterised in that the axial length of the spring bars (2) is smaller than the axial length of one hub ring (1 or 3).
3. One-piece plastics fan wheel according to claim 2, characterised in that the spring bars (2) are arranged in the circumferential direction alternately offset in an axial manner.
4. One-piece plastics fan wheel with an intermediate piece (5) connecting the hub to the blade ring according to one of claims 1 to.3, characterised in that the intermediate piece (5) is closed.
5. One-piece plastics fan wheel with an intermediate piece (5) connecting the hub to the blade ring according to one of claims 1 to 3, characterised in that the intermediate piece (5) is provided with apertures (8).
6. One-piece plastics fan wheel according to one of claims 1 to 5, characterised in that the inner hub ring (3) has at least one driving attachment (10), which is associated with a spring bar (2).
EP85113621A 1984-11-09 1985-10-25 One piece synthetic material fan impeller Expired - Lifetime EP0182145B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85113621T ATE50836T1 (en) 1984-11-09 1985-10-25 ONE-PIECE PLASTIC FAN WHEEL.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3441077 1984-11-09
DE3441077 1984-11-09

Publications (3)

Publication Number Publication Date
EP0182145A1 EP0182145A1 (en) 1986-05-28
EP0182145B1 true EP0182145B1 (en) 1990-03-07
EP0182145B2 EP0182145B2 (en) 1994-03-09

Family

ID=6249954

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85113621A Expired - Lifetime EP0182145B2 (en) 1984-11-09 1985-10-25 One piece synthetic material fan impeller

Country Status (5)

Country Link
US (1) US4639193A (en)
EP (1) EP0182145B2 (en)
JP (1) JPS61116097A (en)
AT (1) ATE50836T1 (en)
DE (1) DE3576391D1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006038655A1 (en) * 2006-08-18 2008-02-21 Behr Gmbh & Co. Kg Axial blower, has hub for connecting blower with electrical driving motor in torsion-smooth manner, where hub is formed as cup-shaped, and recesses arranged in front area and covered by foil
DE102010028099A1 (en) * 2010-04-22 2011-10-27 Behr Gmbh & Co. Kg Axial

Families Citing this family (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USRE34456E (en) * 1985-10-08 1993-11-23 Papst Motoren Miniature axial fan
US4806081A (en) * 1986-11-10 1989-02-21 Papst-Motoren Gmbh And Company Kg Miniature axial fan
GB2185074B (en) * 1985-11-08 1990-12-19 Papst Motoren Gmbh & Co Kg Fan
US4815550A (en) * 1987-08-21 1989-03-28 Clark Equipment Company Engine cooling system for skid steer loaders
JPH05256299A (en) * 1992-03-13 1993-10-05 Toshiba Corp Blower
WO1994015113A1 (en) * 1992-12-23 1994-07-07 United Technologies Corporation Tubular elastomer damper
US5913659A (en) * 1993-11-22 1999-06-22 United Technologies Corporation Apparatus and method for adjusting rotor blade tracking
DE19531160A1 (en) * 1995-08-24 1997-02-27 Behr Gmbh & Co Rotor for radial fan, especially for vehicle air conditioning systems
US5814908A (en) * 1996-04-30 1998-09-29 Siemens Electric Limited Blower wheel with axial inlet for ventilation
DE29706216U1 (en) * 1997-04-08 1998-08-06 ebm Werke GmbH & Co., 74673 Mulfingen Arrangement for the vibration-isolating suspension of an electric motor
US6345956B1 (en) 1998-07-14 2002-02-12 Delta Electronics, Inc. Impeller of a blower having air-guiding ribs with geometrical configurations
DE19907910C2 (en) * 1999-02-24 2003-08-07 Valeo Klimasysteme Gmbh fan
DE19910813B4 (en) * 1999-03-11 2004-07-15 Emu Unterwasserpumpen Gmbh Strömungsmaschinenrad
US6709229B1 (en) * 2002-05-07 2004-03-23 Bill Lee Bi-directional incoming air flow fan
TWI281847B (en) * 2004-05-07 2007-05-21 Delta Electronics Inc Fan
US8202055B2 (en) * 2004-05-07 2012-06-19 Delta Electronics, Inc. Fan and impeller
TWI318730B (en) * 2005-05-27 2009-12-21 Delta Electronics Inc Blower and impeller structure thereof
DE102008062432A1 (en) 2008-12-17 2010-07-15 Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg Electromotive drive, in particular fan drive
US8881396B2 (en) 2011-02-07 2014-11-11 Revcor, Inc. Method of manufacturing a fan assembly
US9995316B2 (en) * 2014-03-11 2018-06-12 Revcor, Inc. Blower assembly and method
US10436223B2 (en) * 2014-03-24 2019-10-08 Delta Electronics, Inc. Fan
DE102014009146A1 (en) * 2014-06-20 2015-12-24 Ziehl-Abegg Se Electric motor with a rotor, a stator and an electronics housing and fan wheel for an electric motor
US11274677B2 (en) 2018-10-25 2022-03-15 Revcor, Inc. Blower assembly
CN115143141A (en) * 2019-02-12 2022-10-04 日本电产株式会社 Impeller and centrifugal fan with same

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB117756A (en) * 1900-01-01
US795938A (en) * 1903-08-17 1905-08-01 James M Seymour Jr Blower or fan.
US1827770A (en) * 1925-02-06 1931-10-20 Bbc Brown Boveri & Cie Rotary fan
US2047501A (en) * 1934-05-03 1936-07-14 Spontan Ab Steam or gas turbine
US2212555A (en) * 1938-01-20 1940-08-27 Heinze Electric Company Fan construction
US2442441A (en) * 1944-05-18 1948-06-01 Edward A Shellberg Air deflector
US2557201A (en) * 1948-07-26 1951-06-19 Punt Simon Centrifugal fan
FR1300199A (en) * 1961-06-17 1962-08-03 Centrifugal pump impeller, especially for small pumps
US3385516A (en) * 1966-03-31 1968-05-28 Gen Electric Fan construction
FR2181111A5 (en) * 1972-04-17 1973-11-30 Mecanique Ind Int
JPS5311609B2 (en) * 1974-01-12 1978-04-22
JPS5240808A (en) * 1975-09-26 1977-03-30 Toshiba Corp Fun made of plastic
US4150919A (en) * 1977-06-10 1979-04-24 Wallace Murray Corporation Radiator cooling fan construction
DD137612B1 (en) * 1978-07-10 1980-06-25 Werner Harms RADIAL IMPELLER
SE443408B (en) * 1979-09-28 1986-02-24 Sueddeutsche Kuehler Behr RADIAL SPLIT FOR HEATING OR AIR CONDITIONING INSTALLATIONS IN VEHICLES
DE2939385C2 (en) * 1979-09-28 1982-11-25 Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co KG, 7000 Stuttgart Radial fans, in particular for heating or air conditioning systems for vehicles

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006038655A1 (en) * 2006-08-18 2008-02-21 Behr Gmbh & Co. Kg Axial blower, has hub for connecting blower with electrical driving motor in torsion-smooth manner, where hub is formed as cup-shaped, and recesses arranged in front area and covered by foil
DE102010028099A1 (en) * 2010-04-22 2011-10-27 Behr Gmbh & Co. Kg Axial

Also Published As

Publication number Publication date
EP0182145B2 (en) 1994-03-09
ATE50836T1 (en) 1990-03-15
DE3576391D1 (en) 1990-04-12
EP0182145A1 (en) 1986-05-28
US4639193A (en) 1987-01-27
JPS61116097A (en) 1986-06-03

Similar Documents

Publication Publication Date Title
EP0182145B1 (en) One piece synthetic material fan impeller
EP2491250B1 (en) Axial fan
EP1446583B1 (en) Fan impeller for electrical machines
DE2939385C2 (en) Radial fans, in particular for heating or air conditioning systems for vehicles
DE10326996A1 (en) Decoupling device for electric motors and method for producing an electric motor
EP2510861B1 (en) Motor assembly for a domestic appliance powered by an electric motor
WO2000007279A1 (en) Commutator-small power motor
DE3631942C2 (en)
EP2381112B1 (en) Axial ventilator
DE8317312U1 (en) FAN WHEEL FOR A RADIAL BLOWER
WO2001041284A1 (en) Pole generator with vibration damping
DE19905075A1 (en) Ventilator rotor esp. for heater/air conditioner plant in motor vehicles ha deformable vibration damping elstomer part to connect hub to bore in rotor center
EP0181549A1 (en) Fan wheel
EP0855782B1 (en) Low noise electric motor, notably for a fan of a motor vehicle
DE102012210775A1 (en) Fastening device for an anchor plate package
DE19907910C2 (en) fan
DE102011053138A1 (en) Electrical external rotor motor has stator surface in which several slots are formed such that meandering flow of air is generated by fan wheels with rotor base arranged on stator face at inner side
EP0826262B1 (en) Low-noise electric motor, especially commutator motor
DE102015113188B4 (en) Electric motor for an electric compressor of an internal combustion engine
DE10258346A1 (en) Brush-less electric motor used e.g. in vacuum cleaner fans has a rotor with a permanent magnet unit for interacting with a stator coil
EP1181762B1 (en) Permanent-magnet-excited electromotor, especially with a variable rotational speed
DE102021209185A1 (en) Radial fan for a motor vehicle
DE112020002870T5 (en) FAN HUB INSULATOR
DE102019128221A1 (en) Radial fan
EP1510690B1 (en) Starter-generator device for vehicles

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT DE FR GB IT NL SE

17P Request for examination filed

Effective date: 19861107

17Q First examination report despatched

Effective date: 19871008

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT DE FR GB IT NL SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Effective date: 19900307

Ref country code: GB

Effective date: 19900307

REF Corresponds to:

Ref document number: 50836

Country of ref document: AT

Date of ref document: 19900315

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3576391

Country of ref document: DE

Date of ref document: 19900412

ET Fr: translation filed
ITF It: translation for a ep patent filed

Owner name: STUDIO JAUMANN

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
GBV Gb: ep patent (uk) treated as always having been void in accordance with gb section 77(7)/1977 [no translation filed]
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Effective date: 19901025

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

26 Opposition filed

Opponent name: BEHR GMBH & CO.

Effective date: 19901203

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19911017

Year of fee payment: 7

ITTA It: last paid annual fee
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19921026

PUAH Patent maintained in amended form

Free format text: ORIGINAL CODE: 0009272

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: PATENT MAINTAINED AS AMENDED

27A Patent maintained in amended form

Effective date: 19940309

AK Designated contracting states

Kind code of ref document: B2

Designated state(s): AT DE FR GB IT NL SE

ET3 Fr: translation filed ** decision concerning opposition
EUG Se: european patent has lapsed

Ref document number: 85113621.8

Effective date: 19930510

REG Reference to a national code

Ref country code: FR

Ref legal event code: TP

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20041007

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20041029

Year of fee payment: 20