US20110058946A1 - Fan and method for operating a fan - Google Patents

Fan and method for operating a fan Download PDF

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Publication number
US20110058946A1
US20110058946A1 US12/991,311 US99131109A US2011058946A1 US 20110058946 A1 US20110058946 A1 US 20110058946A1 US 99131109 A US99131109 A US 99131109A US 2011058946 A1 US2011058946 A1 US 2011058946A1
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US
United States
Prior art keywords
fan
hub
rpm
regions
air flow
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.)
Abandoned
Application number
US12/991,311
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English (en)
Inventor
Adamo Sadikovic
Stefan Richl
Bernd Altvater
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.)
Robert Bosch GmbH
Original Assignee
Individual
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 Individual filed Critical Individual
Assigned to ROBERT BOSCH GMBH reassignment ROBERT BOSCH GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: RICHL, STEFAN, SADIKOVIC, ADAMO, ALTVATER, BERND
Publication of US20110058946A1 publication Critical patent/US20110058946A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—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
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
    • 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
    • F04D29/30—Vanes
    • F04D29/305—Flexible vanes

Definitions

  • the invention is based on a fan and a method for operating a fan as generically defined by the preambles to the independent claims.
  • the fan in an electric power tool performs the task first of cooling the thermally stressed components in the electric power tool, and second, of regulating the idling rpm of the motor by means of a suitable idling moment.
  • a universal motor for instance, by means of a fan disposed on the armature shaft, the universal motor is protected against uncontrolled revving during idling.
  • a low load moment is also created by supporting the armature shaft at the bearing points; in comparison to the load moment from the fan, however, the load moment from the bearing is low.
  • an electrical appliance such as a vacuum cleaner, the air flow fed by the fan is employed, for instance being aspirated.
  • the invention is based on a fan, in particular a radial fan, having a fan hub and a rotational axis, in which a plurality of fan blades for deflecting an air flow are disposed around the rotational axis.
  • an adjusting device be provided for rpm-dependent adjustment of an air flow at the fan blades.
  • the air flow at the fan blades can be varied, both by the fan blades themselves and additionally, or alternatively, by suitable fixtures in the fan.
  • the fan can have fan blades that are curved forward or backward, or uncurved fan blades.
  • the fan is used in an electric power tool or an electrical appliance, such as a vacuum cleaner, and is driven by the electric motor thereof.
  • a strong deflection of the flow in the fan and a high air flow rate produce a high torque at the shaft of the motor (in this case the electric motor).
  • a slight flow deflection or a lesser air flow rate produces a lesser torque.
  • the flow deflection can be varied by the fan blades themselves, or additional elements may be provided that vary the air flow as a function of rpm.
  • the flow deflection by the fan blades can be accomplished passively, for instance via flexible regions of the fan blades, and/or via an active control mechanism that acts on the fan blades.
  • the adjustment of the air flow is done such that at low rpm, for instance at an operating point under load of the tool/appliance cooled by the fan, a lesser flow deflection takes place than at higher rotary speeds, for instance in idling, specifically in such a way that at low rotary speeds, the greatest possible air flow is delivered.
  • the flow deflection can be done for instance with fan blades, in particular with additional adjusting mechanisms in the fan blades.
  • the flow deflection can be achieved by means of flaps, for instance.
  • the adjustment of the air flow in the first alternative, can be done such that at high rpm an adequate load moment, which with an unvaried air flow would be less, acts on the motor shaft.
  • an increased ratio between the volume flow in the rpm can be established, for optimal cooling performance.
  • the result together with the centrifugal force and the fluid force that is, the force that is exerted by the air flow, and given a suitable embodiment of the fan blades, leads to a suitable deformation of the fan blades and to an increase in the flow direction, to an increase in the fan moment, and to a reduction in the idling rpm. Because of the lesser blade deformation at the operating point (that is, at a lesser rpm), there are a lesser flow deflection and a lower fan torque, and thus better overall efficiency of an electric power tool in which the fan is disposed.
  • a region that is deformable by centrifugal force and/or fluid force in at least one of the fan blades can form a component of the adjusting device.
  • the fan blade along its longitudinal chord, can be connected at least in some regions to the fan hub, which is also known as the bottom plate of the fan blades, and can be separate from the fan hub in some regions.
  • the fan blades can be connected in at least some regions on a fan cover disk that rotates with them and can be separate in some regions. The fan cover disk is located facing the fan hub in such a way that the fan blades are disposed between the fan cover disk and the fan hub.
  • the fan blade in the unconnected region can be embodied as more flexible than in the connected region. However, it can also be embodied flexibly throughout.
  • an adaptation of the fan characteristic of the radial fan can advantageously be achieved by means of passive blade deformation, utilizing the incident fluid and centrifugal forces for optimizing the operating performance of electric power tools.
  • the idling rpm can be reduced, and as a consequence, component vibration can be lessened. This also increases the brush service life in the AC range and postpones fatigue in the material. Noise emissions from the preferred electric power tool can be reduced as well.
  • movable elements which vary the air flow as a function of rpm can be provided on the fan hub and/or on the fan cover disk. This is especially preferred in the second alternative.
  • the fan blades can additionally be adjustable, or can also be embodied rigidly. These movable elements, preferably flaps, can change their position as a function of the centrifugal force of the fan.
  • the flaps may be an integral component of the fan, or separate components that are disposed on the fan.
  • the embodiment can be such that an optimal air flow guidance takes place, with a corresponding high air flow.
  • a lesser air flow can be delivered.
  • a separate device from the fan hub and/or the fan cover disk, for adjusting the fan blades may be provided, for instance in a manner known in exhaust gas turbochargers or for the adjustment of the rotor blades of a helicopter.
  • the flow geometry of the fan can be designed favorably for every instance of operation.
  • the fan could first be operated by the first alternative, that is, at increased fan moment at high rpm. In a load situation (lesser rpm), the air quantity decreases, until such time as the motor temperature, after a brief time, has risen so much that more cooling air is needed. A switch could then be made over to the second alternative, which in the load situation makes a high cooling air flow possible.
  • an adjustment, for instance active adjustment, of the air flow at the fan blades and/or at movable flaps could then be provided, via actuators.
  • a method for operating a fan in which an air flow at the fan blades is varied as a function of rpm in such a way that at high rotary speeds, a higher moment of the fan is established, compared to an rpm-dependent moment characteristic without adjustment. This is a preferred mode of operation in accordance with the first alternative.
  • a method for operating a fan in which an air flow at the fan blades is varied as a function of rpm in such a way that at low rotary speeds, a greater ratio between volume flow and rpm is established than at high rotary speeds.
  • the invention can advantageously be employed in radial fans or semiaxial fans, which axially aspirate an air flow and radially or semiaxially output cooling air.
  • the invention can also be employed in axial fans, which axially aspirate an air flow and axially output it.
  • the invention can be used especially advantageously for electric power tools having motors or universal motors that have a fan, or in general in fans that are used for cooling motors.
  • the invention such as the principle of passive blade deformation, can advantageously be employed in any electric power tool with a suitably high motor rpm, given suitable fan geometry.
  • FIGS. 1 a - 1 c show a perspective view of a rearward-curved preferred fan with a plurality of fan blades ( FIG. 1 a ), a detailed view with internal attachment of one fan blade to the fan hub ( FIG. 1 b ), and a detailed view with external attachment of one fan blade to the fan hub ( FIG. 1 c );
  • FIGS. 2 a , 2 b show a perspective view of a forward-curved preferred fan with a plurality of fan blades with external attachment to a fan hub ( FIG. 2 a ) and a detailed view with external attachment of one fan blade ( FIG. 2 b ) to a fan hub;
  • FIGS. 3 a - 3 c show an effect of a resultant force on a rearward-curved fan blade with internal attachment ( FIG. 3 a ) and with an external attachment ( FIG. 3 b ) to a fan hub, and an effect of a force on a forward-curved fan blade with external attachment to a fan hub ( FIG. 3 c );
  • FIGS. 4 a , 4 b show a plan view on a detail of a preferred fan with movable flaps ( FIG. 4 a ) and a side view of a movable flap at various rotary speeds ( FIG. 4 b ).
  • FIGS. 1 a - 1 c and 2 a , 2 b show a fan 10 with a fan hub 18 .
  • a plurality of fan blades 12 for deflecting an air flow is disposed on the fan hub 18 about a rotational axis 14 .
  • the inflow direction of the air flow is in the axial direction in the center region 16 of the fan hub 18 .
  • a shaft, not shown, is disposed at the center of the center region 16 .
  • no cover disk is shown, since it would conceal the fan blades 12 .
  • a fan cover disk of this kind is known in the most various versions, for instance with or without exit-side deflection of the flow in the circumferential region of the cover disk.
  • the cover disk may also be solidly connected to the fan blades 12 and rotate with them.
  • the fan blades 12 can also be fully attached in their length to the cover disk and attached only partly to the fan hub 18 , so that they protrude radially past the fan hub 18 .
  • FIGS. 1 a through 1 c show rearward-curved fan blades 12 , while forward-curved fan blades 12 are shown in FIGS. 2 a , 2 b .
  • the direction of rotation is clockwise, as an example.
  • an adjusting device 26 , 28 for rpm-dependent adjustment of an air flow is provided at the fan blades 12 .
  • the fan blades 12 can be connected to the fan hub 18 in the region 16 near the center of the fan hub 18 , or in the region of its circumference.
  • the unconnected regions of the fan blades 12 can deform under the influence of centrifugal force and of the fluid force, that is, the pressure exerted by the air flow.
  • these regions can be embodied in flexible fashion.
  • a region 26 a (near the circumference) or 28 a (near the center) of the fan blades 12 that is deformable by centrifugal force and fluid force forms a component of the adjusting device 26 , 28 .
  • the fan blades 12 along their longitudinal chord 20 , can be connected at least in some regions to the fan hub 18 and separate at least in some regions from the fan hub 18 .
  • an attachment 30 of its regions 28 a near the rotational axis ( FIGS. 1 a and 1 b ) or a (partial) attachment 32 of its regions 26 a near the circumference ( FIG. 1 c ) on the fan hub 18 is provided.
  • an attachment 32 of their regions 26 a near the circumference to the fan hub 18 is provided, as can be seen in FIGS. 2 a , 2 b .
  • the fan blades 12 are connected (attachment 32 ) to the fan hub 18 , while the region near the center of the fan blades 12 is detached from the fan hub 18 .
  • the fan blades 12 and the fan 10 should be designed correspondingly suitably so as to attain the applicable goal in combination with the rpm-dependent deformation of the fan blades 12 or with an expedient adjusting mechanism in the second alternative.
  • Adapting the geometry to adapt the flow guidance can be done passively by an intentional, variable-rpm blade deformation on the basis of the elasticity of the material of the radial fans, utilizing fluid and centrifugal forces. If space is adequate, active blade adjustment (mechanical adjusting mechanism) can in principle also be done. With the increase in the rpm, the centrifugal force acting on the fan structure rises.
  • FIGS. 3 a through 3 c show a position of the fan blades 12 at equal rotary speeds and under the influence of centrifugal and fluid forces.
  • Position 12 a corresponds to undeformed fan blades 12 .
  • the deformation of the fan blades 12 in the unconnected regions is clearly visible; a rearward-curved fan blade 12 with internal attachment, that is near the center, to the fan hub, not shown, in FIG. 3 a and with an external attachment, that is, near the circumference, to a fan hub in FIG. 3 b is shown.
  • FIG. 3 c shows a forward-curved fan blade with external attachment to the fan hub, not shown.
  • FIG. 4 a shows a plan view on a preferred fan 10 (the fan blades are not shown), in which the elements 40 , embodied for instance as flaps, are provided in the manner of tongues stamped halfway out of the fan hub 18 .
  • FIG. 4 b shows a side view of the fan 10 . It can be see how at low rotary speeds, an air flow L 1 is relatively weakly deflected by the element 40 embodied as a flap. In this state, the air flow L 1 is delivered optimally.
  • the element 40 a embodied as a flap lifts somewhat away from the fan 10 and deflects the air flow L 2 more strongly than at lower rotary speeds. In this case, the flap causes the air to leave the fan 10 sooner.
  • the idling rpm of an electric power tool or electrical appliance can advantageously be reduced. This can be achieved by means of a greater deflection of the air flow in the idling mode of the electric power tool. At the same time, in the operating points of the tool or appliance (lower rpm), good overall efficiency can be attained.
  • the mode of operation of the second alternative can be explained in conjunction with a vacuum cleaner, as an example.
  • the fan of a vacuum cleaner delivers a certain quantity of air, which should be as large as possible to make good vacuuming possible. If the vacuum cleaner sticks to a surface an air flow can no longer be aspirated, then the rpm of the fan rises, since air is no longer being delivered and power is no longer being demanded from the driving electric motor.
  • the operating behavior of the fan in this range of high rotary speeds in the second alternative now has the effect that the suction of the vacuum cleaner is weaker, and the vacuum cleaner can easily be freed from the surface. The rpm then drops again, since air can be aspirated again. As a result of the operating behavior at lesser rpm in the second alternative, the air flow can increase again, and vacuuming can continue in the normal fashion.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US12/991,311 2008-05-05 2009-01-08 Fan and method for operating a fan Abandoned US20110058946A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102008001556.3 2008-05-05
DE102008001556A DE102008001556A1 (de) 2008-05-05 2008-05-05 Lüfter und Verfahren zum Betreiben eines Lüfters
PCT/EP2009/050158 WO2009135698A1 (fr) 2008-05-05 2009-01-08 Ventilateur et procédé permettant de faire fonctionner un ventilateur

Publications (1)

Publication Number Publication Date
US20110058946A1 true US20110058946A1 (en) 2011-03-10

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ID=40442083

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/991,311 Abandoned US20110058946A1 (en) 2008-05-05 2009-01-08 Fan and method for operating a fan

Country Status (5)

Country Link
US (1) US20110058946A1 (fr)
EP (1) EP2283237A1 (fr)
CN (1) CN102099586A (fr)
DE (1) DE102008001556A1 (fr)
WO (1) WO2009135698A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140154106A1 (en) * 2012-12-03 2014-06-05 John Arthur Notaras Motorized portable blower apparatus
WO2014150494A2 (fr) * 2013-03-15 2014-09-25 Regal Beloit America, Inc. Roue de ventilateur centrifuge dotée de pales de ventilateur de forme variable et procédé de montage

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010002673A1 (de) * 2010-03-09 2011-09-15 Robert Bosch Gmbh Handwerkzeugmaschinenlüfter
CN103516134B (zh) * 2013-03-26 2015-11-25 宁波市成大机械研究所 一种电机用轴流风扇
DE102017223185A1 (de) * 2017-12-19 2019-06-19 BSH Hausgeräte GmbH Lüfterrad für ein Hausgerät, Lüfter mit Lüfterrad und Hausgerät mit Lüfter
CN214660989U (zh) 2021-04-30 2021-11-09 中强光电股份有限公司 风扇结构

Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2370600A (en) * 1943-11-11 1945-02-27 Gen Electric Centrifugal fan
US2406499A (en) * 1943-08-23 1946-08-27 Bendix Aviat Corp Fluid transmission
US2766964A (en) * 1952-06-25 1956-10-16 Nils T Almquist Self-governing turbine
US3006534A (en) * 1959-11-02 1961-10-31 Westinghouse Electric Corp Centrifugal fans
US3358773A (en) * 1966-06-06 1967-12-19 Eaton Yale & Towne Variable delivery fan
US3782853A (en) * 1970-10-09 1974-01-01 Bosch Gmbh Robert Fan blade assembly
US3856432A (en) * 1973-09-27 1974-12-24 Us Army Self-governing turbine speed limiter
US4540337A (en) * 1982-05-10 1985-09-10 A/S Kongsberg Vapenfabrikk Ram air turbines
US4900227A (en) * 1988-06-14 1990-02-13 Thomson-Brandt-Armements Wind power of hydraulic power machine with axial feed, radial outflow, and variable geometry vanes, and projectiles fitted with wind power or hydraulic power machines of this type
US5742107A (en) * 1993-12-28 1998-04-21 Mitsubishi Denki Kabushiki Kaisha Rotary cooling fan
US5993158A (en) * 1997-10-17 1999-11-30 Dbs Manufacturing, Inc. Method and apparatus for aeration using flexible blade impeller
US6474936B1 (en) * 2001-04-13 2002-11-05 Hewlett-Packard Company Blower impeller apparatus with one way valves
US6547519B2 (en) * 2001-04-13 2003-04-15 Hewlett Packard Development Company, L.P. Blower impeller apparatus with pivotable blades
US7309935B2 (en) * 2001-11-09 2007-12-18 Robert Bosch Gmbh Fan impeller for electrical machines

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DE168085C (fr) *
DE280189C (fr) *
DE662032C (de) * 1935-03-29 1938-07-02 Siemens Schuckertwerke Akt Ges Umlaufender Luefter mit geringer Geraeuschentwicklung
DE1016361B (de) * 1956-01-05 1957-09-26 Bbc Brown Boveri & Cie Elektrische Maschine mit Radialluefter
EP0103042B1 (fr) * 1982-09-14 1986-08-13 Siemens Aktiengesellschaft Ventilateur comprenant des pales automatiquement réglables autour de leur axe longitudinal afin d'éviter des vitesses de rotation indésirables
DE4434598A1 (de) * 1994-09-28 1996-04-04 Braun Ag Radiallüfter zur Luftkühlung eines elektrischen Kleinmotors
DE19715167C2 (de) * 1997-04-11 1999-08-12 Volker Schirm Vorrichtung zum Betrieb eines Lüfters oder einer Wasserpumpe

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2406499A (en) * 1943-08-23 1946-08-27 Bendix Aviat Corp Fluid transmission
US2370600A (en) * 1943-11-11 1945-02-27 Gen Electric Centrifugal fan
US2766964A (en) * 1952-06-25 1956-10-16 Nils T Almquist Self-governing turbine
US3006534A (en) * 1959-11-02 1961-10-31 Westinghouse Electric Corp Centrifugal fans
US3358773A (en) * 1966-06-06 1967-12-19 Eaton Yale & Towne Variable delivery fan
US3782853A (en) * 1970-10-09 1974-01-01 Bosch Gmbh Robert Fan blade assembly
US3856432A (en) * 1973-09-27 1974-12-24 Us Army Self-governing turbine speed limiter
US4540337A (en) * 1982-05-10 1985-09-10 A/S Kongsberg Vapenfabrikk Ram air turbines
US4900227A (en) * 1988-06-14 1990-02-13 Thomson-Brandt-Armements Wind power of hydraulic power machine with axial feed, radial outflow, and variable geometry vanes, and projectiles fitted with wind power or hydraulic power machines of this type
US5742107A (en) * 1993-12-28 1998-04-21 Mitsubishi Denki Kabushiki Kaisha Rotary cooling fan
US5993158A (en) * 1997-10-17 1999-11-30 Dbs Manufacturing, Inc. Method and apparatus for aeration using flexible blade impeller
US6474936B1 (en) * 2001-04-13 2002-11-05 Hewlett-Packard Company Blower impeller apparatus with one way valves
US6547519B2 (en) * 2001-04-13 2003-04-15 Hewlett Packard Development Company, L.P. Blower impeller apparatus with pivotable blades
US7309935B2 (en) * 2001-11-09 2007-12-18 Robert Bosch Gmbh Fan impeller for electrical machines

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140154106A1 (en) * 2012-12-03 2014-06-05 John Arthur Notaras Motorized portable blower apparatus
WO2014150494A2 (fr) * 2013-03-15 2014-09-25 Regal Beloit America, Inc. Roue de ventilateur centrifuge dotée de pales de ventilateur de forme variable et procédé de montage
WO2014150494A3 (fr) * 2013-03-15 2014-11-13 Regal Beloit America, Inc. Roue de ventilateur centrifuge dotée de pales de ventilateur de forme variable et procédé de montage
US9689264B2 (en) * 2013-03-15 2017-06-27 Regal Beloit America, Inc. Centrifugal fan impeller with variable shape fan blades and method of assembly

Also Published As

Publication number Publication date
CN102099586A (zh) 2011-06-15
DE102008001556A1 (de) 2009-11-12
WO2009135698A1 (fr) 2009-11-12
EP2283237A1 (fr) 2011-02-16

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Owner name: ROBERT BOSCH GMBH, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:SADIKOVIC, ADAMO;RICHL, STEFAN;ALTVATER, BERND;SIGNING DATES FROM 20100909 TO 20100913;REEL/FRAME:025381/0279

STCB Information on status: application discontinuation

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