WO2019096569A1 - Rotor pour une machine électrique - Google Patents

Rotor pour une machine électrique Download PDF

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Publication number
WO2019096569A1
WO2019096569A1 PCT/EP2018/079554 EP2018079554W WO2019096569A1 WO 2019096569 A1 WO2019096569 A1 WO 2019096569A1 EP 2018079554 W EP2018079554 W EP 2018079554W WO 2019096569 A1 WO2019096569 A1 WO 2019096569A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
laminated core
bore
vibration damper
rubber
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/EP2018/079554
Other languages
German (de)
English (en)
Inventor
Holger Fröhlich
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.)
Aumovio Germany GmbH
Original Assignee
Continental Automotive Technologies 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 Continental Automotive Technologies GmbH filed Critical Continental Automotive Technologies GmbH
Priority to CN201880067783.1A priority Critical patent/CN111448745B/zh
Publication of WO2019096569A1 publication Critical patent/WO2019096569A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K15/00—Processes or apparatus specially adapted for manufacturing, assembling, maintaining or repairing of dynamo-electric machines
    • H02K15/16—Centring rotors within the stators
    • H02K15/165—Balancing the rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/13107—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses for damping of axial or radial, i.e. non-torsional vibrations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
    • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
    • F16F15/1414—Masses driven by elastic elements
    • F16F15/1435—Elastomeric springs, i.e. made of plastic or rubber
    • F16F15/1442—Elastomeric springs, i.e. made of plastic or rubber with a single mass
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/30—Flywheels
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K1/00—Details of the magnetic circuit
    • H02K1/06—Details of the magnetic circuit characterised by the shape, form or construction
    • H02K1/22—Rotating parts of the magnetic circuit
    • H02K1/28—Means for mounting or fastening rotating magnetic parts on to, or to, the rotor structures
    • H02K1/30—Means for mounting or fastening rotating magnetic parts on to, or to, the rotor structures using intermediate parts, e.g. spiders
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/003—Couplings; Details of shafts
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/02—Additional mass for increasing inertia, e.g. flywheels
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/04—Balancing means
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K1/00—Details of the magnetic circuit
    • H02K1/06—Details of the magnetic circuit characterised by the shape, form or construction
    • H02K1/22—Rotating parts of the magnetic circuit
    • H02K1/32—Rotating parts of the magnetic circuit with channels or ducts for flow of cooling medium
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K9/00—Arrangements for cooling or ventilating
    • H02K9/19—Arrangements for cooling or ventilating for machines with closed casing and closed-circuit cooling using a liquid cooling medium, e.g. oil
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/16—Mechanical energy storage, e.g. flywheels or pressurised fluids

Definitions

  • the invention relates to a rotor for arrangement in an electric machine, wherein the rotor has an integrated vibration damper.
  • the invention also relates to an electric machine with the rotor according to the invention, as well as a motor vehicle with the electric machine according to the invention.
  • Electric machines with a rotor are well known.
  • the known electrical machines generally have a stator and a rotatable in the stator about a rotor axis rotatable rotor.
  • a rotating electric machine in which a torsional vibration damper is integrated into the rotating electric machine.
  • the electric machine has a rotor core with a first end and a second end.
  • the integrated torsional vibration damper consists of a torsionally flexible coupling and a torsion damper and provides a mechanical damping.
  • the integrated torsional vibration damper is on the rotatable Shaft of electric machine fastened by a flange.
  • the rotor lamination stack is attached to the first end to the integrated torsional vibration damper by suitable structural members, such as a mounting flange, and is not fixedly attached directly to the rotatable shaft.
  • a rotor for arrangement in an electric machine, with a hollow cylinder-shaped laminated core, on whose outer peripheral surface a Ro torblechonce can be arranged, and at the respective axial end of the laminated core carrier an end flange is arranged, wherein the respective end flange has a shaft journal, and in the hollow cylindrical shaped laminated core a
  • Vibration damper is arranged and / or formed.
  • a rotor for an electric machine which having hollow cylindrical shaped laminated core carrier.
  • This can be, for example, a hollow rotor shaft.
  • At least one rotor core can be arranged and / or arranged on the laminated core carrier.
  • the rotor laminated core can preferably be arranged rotationally fixed on the laminated core and transmit a torque to the laminated core.
  • a front flange is arranged, wherein each end flange has a shaft journal which is formed generally coaxial with the rotor axis of rotation.
  • the vibration damper acts directly on the rotor or on the hollow rotor shaft, so that the vibration damper unwanted vibrations and / or noise at the site of Ent stung reduce and thus can affect the operating characteristics of the rotor positively.
  • the vibrations of the rotor causing the noise can be transmitted to the vibration absorber.
  • the design of the vibration absorber is preferably tuned to the frequencies that may occur during operation of the rotor. These can preferably be determined in advance by simulations and / or tests. In this way, a rotor is provided with an integrated vibration absorber, which can have a reduced space and increased operating characteristics. In addition to the space-saving design, the manufacturing costs can also be reduced. In addition, the life and / or reliability of the rotor or electrical machine can be increased.
  • the vibration absorber comprises a rubber-elastic element with at least one arranged in the rubber-elastic element and / or embedded Tilgermasse.
  • the rubber-elastic element is preferably an elastomer, in particular a silicone elastomer, and most preferably a vulcanized silicone elastomer. Silicone elastomers are suitable and designed to convert vibra tion energy into heat.
  • the absorber mass can be designed as desired. As a rule, the absorber mass has a higher density than the rubber-elastic element.
  • the absorber mass is formed as a metal core, but this is not limited exclusively to a metal core. The advantage of a metal core is that it is easy and inexpensive to produce.
  • the absorber mass is held within the elastomeric element in the axial direction of the rotor and in the radial direction of the rotor, wherein the rubber elastic element oscillate at least partially in the radial direction as a result of rotation of the rotor about its axis of rotation can, and vibrates the absorber mass in the radial direction.
  • the absorber mass is positioned in the radial direction and in the axial direction within the rubber-elastic element.
  • the absorber mass acts within the rubber-elastic element as a vibrating mass and the rubber-elastic element takes over the function of the spring and the damper. Unwanted vibrations of the rotor as a result of its rotation stimulate the absorber mass to oscillate in the radial direction. In which the damping mass withdraws energy from the stimulating vibration, the vibration is dampened.
  • the absorber mass can be connected in different ways with the rubber-elastic element.
  • a preferred embodiment of the invention provides that the absorber mass cohesively and / or positively arranged in the rubber-elastic element.
  • the damping mass and the rubber-elastic element can be vulcanized together, pressed together and / or glued together. In this way, the absorber mass can be positioned in the rubber-elastic element.
  • the absorber mass is arranged centrally in the longitudinal direction of the Blechpa ketys, which does not mean that the absorber mass is on the rotor axis of rotation. Rather, the absorber mass is arranged in the radial direction at a distance from the rotor axis of rotation.
  • a preferred embodiment of the invention is that the vibration damper in a longitudinal section through the rotor has a rectilinear configuration.
  • the vibration absorber is preferably arranged coaxially in the laminated core and is clamped between the end flanges. In the radial direction, the vibration absorber over its entire length at a distance from the inner circumferential surface of the laminated core carrier, so that the absorber mass can oscillate in the radial direction.
  • the vibration damper has a dumbbell-shaped configuration in a longitudinal section through the rotor. Accordingly, the vibration absorber between the respective end portions on a central portion which comprises a reduced outer diameter relative to the respective end portions.
  • the end portions of the vibration absorber are based at least in sections against the inner circumferential surface of the laminated core carrier, whereby the vibration damper is positionally positionable in the laminated core carrier.
  • the middle section is designed such that it can oscillate in the radial direction. Accordingly, the absorber mass is arranged in the middle section.
  • vibration damper is arranged cohesively and / or positively in the laminated core and / or is connected to an inner circumferential surface of the laminated core carrier.
  • a cohesive connection is preferably a Klebever connection. Under a positive connection is to be understood that the rubber-elastic element is clamped to the laminated core and / or the end flanges and thus fixed in position.
  • the end flanges and the shaft journal having a coaxial first bore
  • the vibration absorber has a coaxial second bore
  • the first bore and the second bore are interconnected such that a continuous cooling channel is formed
  • a cooling passage through which a cooling medium can be transported, passes through the rotor.
  • the cooling channel is formed continuously.
  • the formed in the vibration absorber second hole connects to the formed in the end flanges and the shaft journal first holes.
  • the vibration damper itself forms a part of the cooling channel, ie the peripheral surface of the cooling channel. In this way, a rotor is provided which can be cooled in a simple manner, can have improved running properties, reduced installation space and reduced weight.
  • a cooling medium is preferably understood to mean a cooling liquid.
  • the cooling liquid is particularly preferably an oil.
  • an advantageous development of the invention is that the respective shaft journal has at least one radial bore, which is guided to the axial first bore.
  • a cooling medium can escape from the cooling channel via the radial bore and preferably be sprayed against winding heads of a stator surrounding the rotor.
  • the winding heads of the stator can be cooled by the rotor supplied and exiting through the radial bores cooling medium in a professional manner.
  • the invention also relates to an electric machine with the rotor according to the invention, wherein the rotor at least from
  • stator is surrounded in sections by a stator.
  • the invention relates to a motor vehicle with the electric machine according to the invention.
  • 1 shows a longitudinal section through a rotor with a built-in vibration damper according to a first embodiment of the invention
  • 2 shows a longitudinal section through the rotor with the inte grated vibration damper according to the first exemplary embodiment, wherein the vibration damper is positioned in the radial direction inside
  • Fig. 3 is a longitudinal section through the rotor with the inte
  • Fig. 4 shows an electric machine with the rotor according to the second embodiment of the invention.
  • FIG. 1 shows a rotor 10 for an electric machine 11.
  • the rotor 10 has a hollow cylindrical out formed laminated core 12.
  • the laminated core 12 may, for example, be a hollow rotor shaft.
  • the laminated core 12 preferably has an inner diameter of> 30 mm.
  • On the laminated core 12 a rotor core 14 is arranged.
  • the rotor core 14 is preferably rotatably mounted on the sheet metal package carrier 12. This means that the ro
  • terblechpers 14 at least partially rests on an outer peripheral surface 16 of the laminated core 12 and / or is preferably connected to this frictionally and / or cohesively. Thus, a rotational movement and / or a torque of the rotor laminated core 14 can be transferred to the laminated core 12.
  • a front flange 18 is arranged, wherein each end flange 18 has a shaft journal 20, which is formed coaxially with the rotor axis of rotation 22.
  • a rotor 10 is provided with an integrated vibration absorber 24, which may have a reduced space and increased operating characteristics.
  • the manufacturing cost can be re wreathd.
  • the vibration damper 24 is a vibrating mass-spring-damping system. It is provided that the vibration damper 24 comprises a rubber-elastic element 26 with we least one arranged in the rubber-elastic element 26 and / or embedded Tilgermasse 28.
  • the rubber elastic member 26 is a silicone elastomer.
  • Conelastomers are suitable and designed to convert vibra tion energy into heat.
  • the absorber mass 28 is formed in the present embodiment as a metal core.
  • the advantage of a metal core is that it is simple and inexpensive to produce and has a higher density compared to the silicone elastomer.
  • the absorber mass 28 is held within the elastomeric element 26 in the axial direction of the rotor 10 and in the radial direction of the rotor 10, wherein the elastomeric element 26 can swing as a result of rotation of the rotor 10 about its axis of rotation 22 at least partially in the radial direction, and the absorber mass 28 oscillates in the radial direction.
  • the absorber mass 28 acts within the rubber-elastic element 26 as a vibrating mass and the rubber-elastic element 26 takes over the function of the spring and the damper. Unwanted vibrations of the rotor 10 as a result of its rotation, the absorber mass 28 to vibrate in the radial direction. In which the absorber mass 28 the exciting vibration withdraws energy, the vibration is damped.
  • the absorber mass 28 is arranged centrally in the longitudinal direction of the laminated core 12, but this does not mean that the Til germasse 28 is located on the rotor axis of rotation 22. Rather, the absorber mass 28 is arranged in the radial direction spaced from the rotor axis Rehah 22. In the present embodiment, the absorber mass 28 is arranged radially outward.
  • the absorber mass 28 is glued to the rubber-elastic element 26, so that it is firmly or captively connected to the gum mielastic element 26.
  • the vibration damper 24 in longitudinal section through the rotor 10 has a straight course. That way is the
  • Vibration damper 24 arranged coaxially in the laminated core 12 and clamped between the end flanges 18. In the radial direction, the vibration damper 24 over its entire length at a distance from the inner circumferential surface 30 of the laminated core 12, so that the absorber mass 28 can oscillate in the radial direction.
  • the outer diameter of the vibration damper 24 in the region of the absorber mass 28 is smaller by at least 5 mm than the inner diameter of the laminated core 12.
  • FIG. 2 shows the known from Figure 1 rotor 10 according to the first embodiment, wherein in contrast to Figure 1, the absorber mass 28 is offset in the radial direction inwardly.
  • the natural frequency of the vibration absorber 24 can be adjusted.
  • the weight and / or size of the absorber mass 28 the natural frequency of the vibration tilgers 24 can be varied and set.
  • the end flanges 18 and the shaft journals 20 have a coaxial first bore 32.
  • the vibration damper 24 has a coaxial second bore 34, wherein the first bore 32 and the second bore 34 are connected to each other such that a continuous cooling channel 36 is formed. A part of the cooling channel 36 is thus formed by the vibration damper 24.
  • the cooling channel 36 is configured such that a cooling medium 38, preferably an oil, for cooling the rotor 10 can be passed through the cooling channel 36.
  • a rotor 10 is provided which is easily coolable, can have improved running characteristics and reduced installation space.
  • the respective shaft journal 20 has at least one radial bore 40, which is guided to the axial first bore 32.
  • the cooling medium 38 can escape from the cooling channel 36 via the radial bore 40 and preferably against winding heads 42 of a rotor 10 surrounding the stator 44 are injected.
  • the winding heads 42 of the stator 44 can be cooled by the rotor 10 to be guided cooling medium 38 in a simple manner.
  • FIG. 3 shows the rotor 10 with the integrated vibration absorber 24 according to a second preferred embodiment.
  • the vibration damper 24 in the second embodiment in a longitudinal section through the rotor 10 is not a rectilinear design but a han telförmige configuration.
  • the vibration damper 24 between the respective end portions 46 has a central portion 48 with an outer diameter reduced from the respective end portions 46.
  • the end portions 46 of the vibration damper 24 are based at least in sections against the inner circumferential surface 30 of the laminated core 12, whereby the vibration damper 24 is secure in the laminated core 12 is positionable.
  • the middle portion 48 is formed so that it can vibrate in the radial direction.
  • the absorber mass 28 is arranged in the middle section. Furthermore, it can be seen that the absorber mass 28 is arranged centrally in the radial direction within the rubber-elastic element 26.
  • the outer diameter of the vibration absorber 24 in the middle section is at least 5 mm smaller than the inner diameter of the laminated core 12.
  • FIG. 4 shows an electric machine 11 with the rotor 10 and the integrated vibration absorber 24 according to the second exemplary embodiment.
  • the rotor 10 is rotatably mounted within a housing 50 about the rotor axis of rotation 22, wherein the rotor 10 is circumferentially surrounded by the stator 44.
  • a shaft journal 20 of the rotor 10 is coupled to a transmission input shaft 52 of a transmission 54, so that a rotational movement of the rotor via the transmission input shaft 52 to the transmission 54 is transferable.
  • the cooling medium 38 which is transported through the coaxially formed cooling channel 36, is sprayed via the radial bores 40 in the shaft journal 20 as a result of rotation of the rotor 10 in the radial direction to the outside and sprayed against the winding heads 42 of the stator 44 to the winding heads 42 to cool.
  • vibration damper 24 bending vibrations of the rotor 10 can be effectively reduced, whereby the operating characteristics of the electric machine can be increased.
  • the arrangement of the vibration absorber 24 in the hollow cylinder-shaped laminated core 12, the space of the electric machine 11 can be reduced.

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  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)
  • Motor Or Generator Frames (AREA)

Abstract

La présente invention concerne un rotor (10) à disposer dans une machine électrique (11), avec un support de noyau feuilleté (12) de forme cylindrique creuse sur la surface périphérique (16) externe duquel peut être disposé un noyau feuilleté de rotor (14) et à chaque extrémité axiale du support de noyau feuilleté (12) est disposée une bride frontale (18). Chaque bride frontale (18) comprend des tourillons d'arbre (20) et un amortisseur d'oscillations (24) est disposé et/ou formé dans le support de noyau feuilleté (12) de forme cylindre creuse.
PCT/EP2018/079554 2017-11-16 2018-10-29 Rotor pour une machine électrique Ceased WO2019096569A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201880067783.1A CN111448745B (zh) 2017-11-16 2018-10-29 用于电机的转子

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017220422.2A DE102017220422B4 (de) 2017-11-16 2017-11-16 Rotor für eine elektrische Maschine
DE102017220422.2 2017-11-16

Publications (1)

Publication Number Publication Date
WO2019096569A1 true WO2019096569A1 (fr) 2019-05-23

Family

ID=64051563

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2018/079554 Ceased WO2019096569A1 (fr) 2017-11-16 2018-10-29 Rotor pour une machine électrique

Country Status (3)

Country Link
CN (1) CN111448745B (fr)
DE (1) DE102017220422B4 (fr)
WO (1) WO2019096569A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020114608A1 (de) 2020-06-02 2021-12-02 Winkelmann Powertrain Components GmbH & Co. KG. Rotor
CN115118037A (zh) * 2022-07-13 2022-09-27 珠海格力电器股份有限公司 电机转子、电机
DE102022119704A1 (de) * 2022-08-05 2024-02-08 Vibracoustic Se Elektromotorrotoranordnung
DE102022122183A1 (de) * 2022-09-01 2024-03-07 Bayerische Motoren Werke Aktiengesellschaft Elektrische Maschine

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008253039A (ja) * 2007-03-30 2008-10-16 Jtekt Corp 電動モータおよびそれを備える電動パワーステアリング装置
CN201181867Y (zh) * 2008-04-07 2009-01-14 广东威灵电机制造有限公司 一种永磁电动机转子
JP2009118714A (ja) * 2007-11-09 2009-05-28 Toyota Motor Corp 回転電機
US20100024571A1 (en) * 2008-07-30 2010-02-04 Horiba Ltd. Rotational testing system
US20100225121A1 (en) 2009-02-11 2010-09-09 Converteam Technology Ltd. Rotating Electrical Machines
DE102010062250A1 (de) * 2010-12-01 2012-06-06 Robert Bosch Gmbh Rotor mit einem Schwingungstilger
WO2012168419A1 (fr) * 2011-06-10 2012-12-13 Carnehammar, Lars Bertil Procédé, dispositif et système pour réduire la vibration dans un système rotatif d'un générateur d'énergie
EP2735764A1 (fr) * 2012-11-23 2014-05-28 WEGMANN automotive GmbH & Co. KG Procédé d'équilibrage d'une roue

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19726293A1 (de) * 1997-06-20 1998-12-24 Contitech Formteile Gmbh Hohle Antriebswelle mit integriertem Schwingungstilger
DE10005582A1 (de) * 2000-02-09 2001-09-06 Isad Electronic Sys Gmbh & Co Antriebsanordnung mit einem Antriebsstrang und einer elektrischen Maschine, z. B. in einem Kraftfahrzeug
JP4584651B2 (ja) * 2004-08-25 2010-11-24 カヤバ工業株式会社 緩衝器
JP5496822B2 (ja) * 2010-08-20 2014-05-21 東海ゴム工業株式会社 能動型制振器とその製造方法
DE102014107843B3 (de) 2014-06-04 2015-11-26 Thyssenkrupp Presta Teccenter Ag Medientransport in Rotorwelle
DE102014107845B4 (de) * 2014-06-04 2024-02-15 Thyssenkrupp Presta Teccenter Ag Ölverteilelement
DE102015223631B4 (de) 2015-11-30 2017-06-08 Thyssenkrupp Ag Gebaute Rotorhohlwelle mit Kühlmediumverteilelement

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008253039A (ja) * 2007-03-30 2008-10-16 Jtekt Corp 電動モータおよびそれを備える電動パワーステアリング装置
JP2009118714A (ja) * 2007-11-09 2009-05-28 Toyota Motor Corp 回転電機
CN201181867Y (zh) * 2008-04-07 2009-01-14 广东威灵电机制造有限公司 一种永磁电动机转子
US20100024571A1 (en) * 2008-07-30 2010-02-04 Horiba Ltd. Rotational testing system
US20100225121A1 (en) 2009-02-11 2010-09-09 Converteam Technology Ltd. Rotating Electrical Machines
DE102010062250A1 (de) * 2010-12-01 2012-06-06 Robert Bosch Gmbh Rotor mit einem Schwingungstilger
WO2012168419A1 (fr) * 2011-06-10 2012-12-13 Carnehammar, Lars Bertil Procédé, dispositif et système pour réduire la vibration dans un système rotatif d'un générateur d'énergie
EP2735764A1 (fr) * 2012-11-23 2014-05-28 WEGMANN automotive GmbH & Co. KG Procédé d'équilibrage d'une roue

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