EP1250531B1 - Turboradialgebläse - Google Patents
Turboradialgebläse Download PDFInfo
- Publication number
- EP1250531B1 EP1250531B1 EP01901200A EP01901200A EP1250531B1 EP 1250531 B1 EP1250531 B1 EP 1250531B1 EP 01901200 A EP01901200 A EP 01901200A EP 01901200 A EP01901200 A EP 01901200A EP 1250531 B1 EP1250531 B1 EP 1250531B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- rotor
- bearing
- stator
- cavity
- radial turbo
- 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
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
- F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
- F04D29/056—Bearings
- F04D29/059—Roller bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
- F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
- F04D25/0653—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump the motor having a plane air gap, e.g. disc-type
-
- 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
- F04D29/06—Lubrication
- F04D29/063—Lubrication specially adapted for elastic fluid pumps
Definitions
- the invention relates to a turbo radial fan with a rotatable mounted impeller and a motor driving the impeller like it e.g. is shown in WO 9908363A.
- Turbo radial blowers in vacuum technology are both in single stage as in a two-stage version usually like this built that impeller, motor and bearing spatially one behind the other are arranged, the impeller between the Storage is located or can be stored on the fly.
- the Bearing lubrication is carried out using oil, which is carried out by a Oil production facility is promoted to the bearings.
- Such Turbo radial fans have a large axial length and a large number of components. They require complicated balancing processes. There is also a risk of contamination of the Impeller area with the one intended for bearing lubrication Oil.
- the motor is in a vacuum, which makes it complex Winding insulation is required, with the consequence worse Heat transfers and a sealed cable duct for the power lines.
- the invention has for its object a turbo radial fan to create that has a compact design and out few components can be manufactured inexpensively.
- the bearing assembly is lubricated with grease, whereby at least one fat chamber is provided in the cavity of the impeller is.
- the bearing assembly is lubricated with grease, whereby at least one fat chamber is provided in the cavity of the impeller is.
- magnetic bearings use, which are also maintenance-free. Is conceivable also the combination of magnetic bearings and grease-lubricated bearings.
- the cavity of the impeller is preferably towards the rear open and at the rear end of the cavity is between the Impeller and the bearing mandrel formed a sealing gap.
- This Sealing gap prevents grease and bearing components from being sucked in from the cavity into the pump room. It is also possible to use a seal at this point, however then abrasion from the seal could get into the pump chamber.
- a heat-conducting spacer ring on the bearing mandrel Narrow heat transfer gap of at most 0.5 mm in width Dissipation of heat from the impeller is formed on the bearing mandrel.
- a pressure-tight can be between the impeller and the stator coils be arranged magnetically permeable partition.
- This partition can be made from a membrane, from a fiber composite material or a potting compound. It creates a vacuum seal between the pump room and the engine room, so the the stator contained in the engine compartment is on the atmosphere side and not in a vacuum room. This enables one easier and cheaper winding insulation of the stator windings.
- the stator housing is not pressure-tight Power feed-through required. Rather, a simple one Terminal box can be used.
- the cooling can also be done be significantly simplified by the fact that a cooling device is housed in the stator housing. This cooler cools both the stator and the bearing mandrel and causes heat dissipation from the impeller to the bearing mandrel transferred heat.
- turbo radial fan according to the invention is particularly suitable for high-speed fans, for example for use in rapidly flowing CO 2 lasers.
- the turbo radial fan has a stator housing 10 and Pump housing 11 on.
- the pump housing 11 contains one Pump chamber 12, in which a rotatable impeller 13 is arranged, which has a hub 14 and projecting vanes 15.
- the wings 15 have outer edges that correspond to the contour of the wall of the follow the pump housing 11 with a small gap. The pump sucks the fluid to be pumped axially and conveys it radially to the Outlets 16.
- the hub 14 of the impeller 13 contains a carrier part 17 which consists of a pipe section 18 and a flange section 19.
- the flange portion 19 forms the rear end wall of the impeller 13. It contains recesses in which permanent magnets 20 are arranged. These permanent magnets have one axial magnetic field alignment. This means that the North Pole N and the south pole S on a parallel to the impeller axis Line.
- the carrier part 17 and the hub 14 are made made of non-magnetic material.
- a partition 21 is adjacent to the permanent magnets 20 provided that the interior 22 of the stator 10 from the Pump room 12 separates.
- the partition 21 consists of a magnetic permeable membrane, preferably made of composite fiber material, or a potting compound. It creates a vacuum seal between the stator chamber 22 and the pump chamber 12.
- the impeller 13 has an inner cavity 23 which is at the front End is sealed with a cap 24.
- a bearing mandrel 25 projects into this cavity 23, on which the Impeller 13 is mounted with a bearing arrangement 26.
- To the Bearing arrangement include two rolling bearings, namely a front one Ball bearings 27 and a rear ball bearing 28. These ball bearings sit on the mandrel 25 and they support the pipe section 18 of the carrier part 17. At least each ball bearing borders a grease chamber 29 to the pasty grease for bearing lubrication contains. At least one of these camps can also be used as Magnetic bearings can be executed. In principle there is also one complete bearing design in magnetic bearings possible.
- a cap 30 is fastened to the outer end of the bearing mandrel 25, which supports a plate spring assembly 31, which in turn presses against the front ball bearing 27 and thus the Bearing arrangement keeps axially compressed.
- a spacer ring 32 made of a good heat-conducting material is in close contact with the mandrel 25.
- a heat transfer gap 33 with a width of at most 0.5 mm, preferably of about 0.4 mm, to dissipate the heat from the impeller 13 via the spacer ring 32 to bearing pin 25.
- a sealing gap 34 is formed between the rear end of the tube section 18 of the Carrier part 17 and the bearing mandrel 25. This sealing gap enables gas extraction from the Pump chamber 12 into the cavity 23. One of the cavities takes place Derivation through a hole (not shown) in the bearing mandrel 25.
- the sealing gap 34 represents the only opening in the cavity 23 represents
- stator 35 In the stator chamber 22 is the stator 35 with the Stator coils 36, which are embedded in an iron package 37.
- the stator 35 forms, together with the permanent magnets 20 containing carrier part 17, the disc motor 44.
- Die Stator coils 36 lie on the same circle on which the Move the permanent magnets 20 when the impeller 13 rotates.
- On Electronic commutator creates in the stator windings 36 circulating current, so that the stator windings generate a rotating magnetic field.
- the impeller 13 follows its permanent magnet 20 this magnetic field. It is about with the disc rotor motor almost a magnetic coupling for the contactless impeller drive.
- the air gap between the Stator coils 36 and the permanent magnet 20 is of the Partition 21 penetrates.
- This partition is sealing attached a base 38 which on a bottom wall 39 of the Stator housing 10 is fixed and part of Bearing mandrel 25 forms. Since the partition 21 of the stator 22 from separates the vacuum part, there is 22 atmospheric pressure in the stator space. There is one in the wall of the stator housing 10 Cable opening 40 for the passage of power cables. Further a pipe feed-through opening 41 is provided through which Pass pipes 42 which are part of one of Cooling water flows through the cooling coil, which is the cooling device 43 forms. The cooling device 43 cools both the Stator 35 and the bearing mandrel 25 and carries the heat from the entire fan housing.
- the turbo radial fan consists of few individual parts and is inexpensive to manufacture. It is largely maintenance-free.
Description
Claims (8)
- Turboradialgebläse mit einem drehbar gelagerten Laufrad (13) und einem das Laufrad treibenden Motor in Form eines permanenterregten Scheibenläufermotors (44), der an dem Laufrad (13) befestigte Permanentmagnete (20) mit axialer Magnetfeldausrichtung und ortsfeste Statorspulen (36) aufweist, wobei das Laufrad (13) mit einer Lageranordnung (26), welche in einem Hohlraum (23) des Laufrades untergebracht ist, auf einem in den Hohlraum (23) ragenden feststehenden Lagerdorn (25) gelagert ist,
dadurch gekennzeichnet , dass zwischen der den Hohlraum (23) begrenzenden Wand und einem gut wärmeleitend auf dem Lagerdorn (25) sitzenden Distanzring (32) ein schmaler Wärmeübertragungsspalt (33) von höchstens 0,5 mm Breite zur Ableitung von Wärme von dem Laufrad (13) auf den gekühlten Lagerdorn (25) gebildet ist. - Turboradialgebläse nach Anspruch 1, dadurch gekennzeichnet, dass die Lageranordnung (26) eine Fettschmierung mit mindestens einer Fettkammer (29) aufweist.
- Turboradialgebläse nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Hohlraum (23) des Laufrades (13) nur zur Rückseite hin offen ist und dass am rückwärtigen Ende des Hohlraums (23) zwischen dem Laufrad (13) und dem Lagerdorn (25) ein Dichtspalt (34) ausgebildet ist.
- Turboradialgebläse nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass zwischen dem Laufrad (13) und den Stätorspulen (36) eine druckdichte magnetisch durchlässige Trennwand (21) angeordnet ist.
- Turboradialgebläse nach Anspruch 4, dadurch gekennzeichnet, dass die Statorspulen (36) in einem unter Atmosphärendruck stehenden Statorgehäuse (10) enthalten sind, welches eine Kühlvorrichtung (43) enthält.
- Turboradialgebläse nach Anspruch 5, dadurch gekennzeichnet, dass ein Teil (38) des Lagerdorns (25) in wärmeleitendem Kontakt mit dem Stator (35) steht und aus diesem herausragt und dort der Einwirkung der Kühlvorrichtung (43) ausgesetzt ist.
- Turboradialgebläse nach Anspruch 1, dadurch gekennzeichnet, dass ein Lager in fettgeschmierter Ausführung und ein Lager, vorzugsweise das Untere, als passives Magnetlager ausgeführt ist.
- Turboradialgebläse nach Anspruch 1, dadurch gekennzeichnet, dass die Lageranordnung mit aktiven Magnetlagern ausgeführt ist.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10003153 | 2000-01-26 | ||
DE10003153A DE10003153A1 (de) | 2000-01-26 | 2000-01-26 | Turboradialgebläse |
PCT/EP2001/000758 WO2001055598A1 (de) | 2000-01-26 | 2001-01-24 | Turboradialgebläse |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1250531A1 EP1250531A1 (de) | 2002-10-23 |
EP1250531B1 true EP1250531B1 (de) | 2004-10-20 |
Family
ID=7628687
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01901200A Expired - Lifetime EP1250531B1 (de) | 2000-01-26 | 2001-01-24 | Turboradialgebläse |
Country Status (8)
Country | Link |
---|---|
US (1) | US6682324B2 (de) |
EP (1) | EP1250531B1 (de) |
JP (1) | JP2003524730A (de) |
KR (1) | KR100635692B1 (de) |
CN (1) | CN1178005C (de) |
AT (1) | ATE280328T1 (de) |
DE (2) | DE10003153A1 (de) |
WO (1) | WO2001055598A1 (de) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11437900B2 (en) | 2019-12-19 | 2022-09-06 | Black & Decker Inc. | Modular outer-rotor brushless motor for a power tool |
US11757330B2 (en) | 2019-12-19 | 2023-09-12 | Black & Decker, Inc. | Canned outer-rotor brushless motor for a power tool |
Families Citing this family (33)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10203778A1 (de) * | 2002-01-30 | 2003-07-31 | Siemens Ag | Elektrisch angetriebene Pumpe |
JP2003269369A (ja) * | 2002-03-13 | 2003-09-25 | Boc Edwards Technologies Ltd | 真空ポンプ |
EP1657448A1 (de) * | 2004-10-28 | 2006-05-17 | Asmo Co., Ltd. | Lüfter |
JP4539487B2 (ja) * | 2005-08-05 | 2010-09-08 | 株式会社Ihi | 電動機付過給機 |
JP4605380B2 (ja) * | 2005-08-08 | 2011-01-05 | 株式会社Ihi | 電動過給機 |
JP4692820B2 (ja) * | 2005-08-11 | 2011-06-01 | 株式会社Ihi | 電動機付過給機 |
JP4591828B2 (ja) * | 2005-08-22 | 2010-12-01 | 株式会社Ihi | 電動機付過給機 |
DE602006020239D1 (de) | 2006-01-24 | 2011-04-07 | Ihi Corp | Motorbetriebene Aufladung |
EP1813782B1 (de) | 2006-01-26 | 2009-08-05 | IHI Corporation | Turbo-Auflader |
EP1998008B1 (de) * | 2006-03-23 | 2019-03-13 | IHI Corporation | Hochgeschwindigkeitsrotationswellenanordnung für auflader |
JP4671177B2 (ja) * | 2006-06-02 | 2011-04-13 | 株式会社Ihi | 電動過給機 |
JP4753033B2 (ja) * | 2006-06-02 | 2011-08-17 | 株式会社Ihi | 電動過給機 |
EP2067960B1 (de) | 2006-08-18 | 2015-09-23 | IHI Corporation | Elektrischer auflader |
KR20090039770A (ko) * | 2006-08-18 | 2009-04-22 | 가부시키가이샤 아이에이치아이 | 전동 과급기 |
EP2167823B1 (de) * | 2007-05-23 | 2015-07-29 | Eppendorf, Inc. | Verstellbare nabe für sanitäres laufrad |
DE502007006457D1 (de) * | 2007-05-24 | 2011-03-24 | Lindenmaier Gmbh | Turbolader |
DE102008024764A1 (de) * | 2008-05-23 | 2009-11-26 | Oerlikon Leybold Vacuum Gmbh | Mehrstufige Vakuumpumpe |
US8523539B2 (en) * | 2008-06-19 | 2013-09-03 | The Board Of Regents Of The University Of Texas Systems | Centrifugal pump |
EP2273655B1 (de) * | 2009-07-07 | 2012-03-21 | Dietz-motoren GmbH & Co. KG | Elektrische Maschine |
JP2011055587A (ja) * | 2009-08-31 | 2011-03-17 | Ihi Corp | ターボ機械システム |
DE102009052931A1 (de) * | 2009-11-12 | 2011-05-26 | Siemens Aktiengesellschaft | Rotor für eine Strömungsmaschine |
CN102235383A (zh) * | 2010-04-26 | 2011-11-09 | 宁波龙泰电讯电机有限公司 | 一种前向离心式风机 |
GB2503531A (en) * | 2012-06-29 | 2014-01-01 | Samsung Electro Mech | Fan motor structure |
DE102013200655B4 (de) * | 2013-01-17 | 2015-11-05 | Yasa Motors Poland Sp. z.o.o. | Kombiniertes Radial-Axiallager und Nassläuferpumpe |
KR101429848B1 (ko) * | 2013-02-13 | 2014-08-12 | 한승주 | 자기 구동 확장공기충전장치 |
TWI553231B (zh) * | 2015-02-13 | 2016-10-11 | 佳世達科技股份有限公司 | 風扇及電子裝置 |
DE102015220988A1 (de) * | 2015-10-27 | 2017-04-27 | Robert Bosch Gmbh | Förderungseinheit, sowie Brennstoffzellenvorrichtung mit einer Förderungseinheit |
US20170356464A1 (en) * | 2016-06-08 | 2017-12-14 | Nidec Corporation | Blower apparatus |
DE102016214700A1 (de) * | 2016-08-08 | 2018-02-08 | Efficient Energy Gmbh | Elektrischer Scheibenläufer mit einem Druckreduzierer für den Motorspalt |
CN106224263A (zh) * | 2016-08-19 | 2016-12-14 | 联想(北京)有限公司 | 一种散热风扇和电子设备 |
CN114673728B (zh) * | 2020-12-24 | 2024-01-26 | 迈格钠磁动力股份有限公司 | 一种永磁推力悬浮轴承及其控制方法 |
CN114607626A (zh) * | 2021-08-25 | 2022-06-10 | 北京石头世纪科技股份有限公司 | 一种风机及清洁设备 |
US20240060499A1 (en) * | 2022-08-22 | 2024-02-22 | Hamilton Sundstrand Corporation | Rotor integrated axial flux electric motor |
Family Cites Families (15)
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US2693149A (en) * | 1950-09-13 | 1954-11-02 | Howard T White | Explosionproof motor-driven pump |
CH368575A (de) * | 1959-05-22 | 1963-04-15 | Robert Dipl Ing Coester | Axial förderndes Motorgebläse |
CH612736A5 (de) * | 1976-04-27 | 1979-08-15 | Papst Motoren Kg | |
FR2528127A1 (fr) * | 1982-06-04 | 1983-12-09 | Creusot Loire | Moto-compresseur centrifuge electrique integre a grande vitesse |
JPH02169899A (ja) * | 1988-12-21 | 1990-06-29 | Fanuc Ltd | レーザ用ターボブロア及びそれを用いたレーザ発振装置 |
JPH02222586A (ja) * | 1989-02-23 | 1990-09-05 | Fanuc Ltd | レーザ用ターボブロア及びレーザ発振装置 |
DE4214483A1 (de) * | 1992-05-07 | 1993-11-11 | Dornier Gmbh | Permanent-Magnet-Generator |
FR2696057B1 (fr) * | 1992-09-22 | 1997-06-13 | Aerospatiale | Moteur-couple allonge et dispositif de commande en debattement angulaire le comportant. |
US5332374A (en) * | 1992-12-30 | 1994-07-26 | Ralph Kricker | Axially coupled flat magnetic pump |
DE4301675A1 (de) * | 1993-01-22 | 1994-07-28 | Pierburg Gmbh | Elektronisch kommutierter Elektromotor |
US5906098A (en) * | 1996-07-16 | 1999-05-25 | Turbodyne Systems, Inc. | Motor-generator assisted turbocharging systems for use with internal combustion engines and control method therefor |
US5870894A (en) | 1996-07-16 | 1999-02-16 | Turbodyne Systems, Inc. | Motor-assisted supercharging devices for internal combustion engines |
US6132186A (en) | 1997-08-06 | 2000-10-17 | Shurflo Pump Manufacturing Co. | Impeller pump driven by a dynamo electric machine having a stator comprised of a mass of metal particles |
JP3084622B2 (ja) * | 1997-08-13 | 2000-09-04 | セイコー精機株式会社 | ターボ分子ポンプ |
US5951267A (en) * | 1997-09-24 | 1999-09-14 | Ingersoll-Dresser Pump Co. | Diaphragm for seal-less integral-motor pump |
-
2000
- 2000-01-26 DE DE10003153A patent/DE10003153A1/de not_active Withdrawn
-
2001
- 2001-01-24 KR KR1020027009556A patent/KR100635692B1/ko not_active IP Right Cessation
- 2001-01-24 CN CNB01804221XA patent/CN1178005C/zh not_active Expired - Fee Related
- 2001-01-24 JP JP2001555703A patent/JP2003524730A/ja active Pending
- 2001-01-24 WO PCT/EP2001/000758 patent/WO2001055598A1/de active IP Right Grant
- 2001-01-24 DE DE50104205T patent/DE50104205D1/de not_active Expired - Lifetime
- 2001-01-24 AT AT01901200T patent/ATE280328T1/de not_active IP Right Cessation
- 2001-01-24 US US10/182,107 patent/US6682324B2/en not_active Expired - Fee Related
- 2001-01-24 EP EP01901200A patent/EP1250531B1/de not_active Expired - Lifetime
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11437900B2 (en) | 2019-12-19 | 2022-09-06 | Black & Decker Inc. | Modular outer-rotor brushless motor for a power tool |
US11757330B2 (en) | 2019-12-19 | 2023-09-12 | Black & Decker, Inc. | Canned outer-rotor brushless motor for a power tool |
Also Published As
Publication number | Publication date |
---|---|
DE50104205D1 (de) | 2004-11-25 |
KR100635692B1 (ko) | 2006-10-17 |
CN1440493A (zh) | 2003-09-03 |
CN1178005C (zh) | 2004-12-01 |
US6682324B2 (en) | 2004-01-27 |
WO2001055598A1 (de) | 2001-08-02 |
ATE280328T1 (de) | 2004-11-15 |
EP1250531A1 (de) | 2002-10-23 |
US20030118461A1 (en) | 2003-06-26 |
DE10003153A1 (de) | 2001-08-02 |
KR20030017466A (ko) | 2003-03-03 |
JP2003524730A (ja) | 2003-08-19 |
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