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WO1997024536A1 - Douilles de renfort radiales serrees servant a recentrer des paliers magnetiques - Google Patents

Douilles de renfort radiales serrees servant a recentrer des paliers magnetiques Download PDF

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Publication number
WO1997024536A1
WO1997024536A1 PCT/US1996/020396 US9620396W WO9724536A1 WO 1997024536 A1 WO1997024536 A1 WO 1997024536A1 US 9620396 W US9620396 W US 9620396W WO 9724536 A1 WO9724536 A1 WO 9724536A1
Authority
WO
WIPO (PCT)
Prior art keywords
flywheel assembly
backup
flywheel
axis
bushing
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/US1996/020396
Other languages
English (en)
Inventor
Robin M. Miller
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.)
Lear Corp EEDS and Interiors
Original Assignee
Lear Corp EEDS and Interiors
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 Lear Corp EEDS and Interiors filed Critical Lear Corp EEDS and Interiors
Publication of WO1997024536A1 publication Critical patent/WO1997024536A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/044—Active magnetic bearings
    • F16C32/0442—Active magnetic bearings with devices affected by abnormal, undesired or non-standard conditions such as shock-load, power outage, start-up or touchdown
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C39/00—Relieving load on bearings
    • F16C39/02—Relieving load on bearings using mechanical means
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/55—Flywheel systems

Definitions

  • the present application relates to backup bushings and especially to radially constrained backup bushings for use in conjunction with magnetic bearings.
  • the flywheel a balanced mass spinning around a constant axis that stores energy as rotational kinetic energy is one of humankind's earliest devices, serving as the basis for both the potter's wheel and the grindstone.
  • FES flywheel energy storage
  • mobile applications such as automotive and space applications
  • stationary applications such as utility load-leveling systems, uninterrupted power supplies, and as storage capacity for solar and wind power systems.
  • stationary refers to a system which is positioned primarily in a given geographic location as contrasted to a mobile system which is able to readily move between a variety of geographic locations.
  • FES systems generally include several principal components; namely a flywheel having a rotor and a hub, a motor/generator as well as magnetic bearings.
  • the system will also include a structural housing, a vacuum pump, electrical power input/output and electronic controls for the magnetic bearings.
  • the flywheel rotor of high specific strength (i.e. strength/density) composite materials in order to optimize the flywheel's performance.
  • the motor/generator is utilized to transfer electric power into the system to store it as kinetic energy when the system is acting as a motor and is also utilized to generate electric energy from the stored kinetic energy to transfer the electric energy out of the system when the system is operating as a generator.
  • High-performance FES systems operate in a vacuum to minimize windage losses, aerodynamic heating and rotor instability. These high-performance systems therefore include a structural housing which also serves as a containment vessel to enclose any debris resulting from the failure ofthe rotor.
  • Current FES systems also use magnetic bearings for supporting, or suspending the rotating flywheel within the housing.
  • the magnetic bearings utilized are either active or passive.
  • the flywheel is suspended by magnetic forces created by the magnetic bearings. These forces, along with the loads that act on the flywheel, are controlled and balanced by position or proximity sensors and electronic feedback circuits working together to control the stability ofthe flywheel by introducing magnetic flux forces by controlling the currents in electromagnetic windings within the bearing assembly.
  • Passive magnetic bearings use powerful permanent magnets with specific geometries to support and stabilize the spinning flywheel without resorting to feedback control. Passive bearings help minimize parasitic losses, are cost effective and are generally utilized in stationary systems where complex control logic is typically not needed during normal operation.
  • active bearings allow for more dynamic stability than passive bearings and are useful in mobile applications, such as in automobiles where compensation for road shocks and rotor balance to avoid flywheel instability is important.
  • “Whirl” is when the flywheel spins around within the clearance required for the magnetic bearings thereby causing extremely high rotating forces on the stationary components in the system and on traditional backup bearings. “Whirl” can shorten the life of the backup bearings and creates additional stress on the flywheel which can cause the flywheel to be damaged and break. Although traditional backup bearings help during emergency failure, they do not prevent the "whirl” phenomena and therefore do not spin the flywheel down to rest without possible damage to the system. In addition, for large, stationary systems with rotating flywheel weights over about 500 lbs the cost of these rolling element backup bearings can be prohibitive, especially since the market for these large, stationary systems is cost driven.
  • the present application provides for a cost effective backup bushing system which allows the flywheel to safely spin down to rest if there is an interruption in the power source to the magnetic bearings without allowing "whirl" to occur.
  • the present bushing system may also be utilized to re- center the flywheel assembly.
  • a backup bushing system for use with a flywheel assembly aligned and rotating about the axis of a stationary shaft, the backup bushing system comprising: a first bushing disposed substantially stationary with respect to the axis and having a first contact portion; and a second bushing spaced from the first bushing and disposed substantially stationary with respect to the axis and having a second contact portion. If the flywheel assembly is moved off-center with respect to the axis the flywheel assembly will engage the first and second contact portions ofthe first and second bushings. Upon engagement, the bushings operate to contain the rotation of the flywheel assembly between the contact portions thereby substantially maintaining the alignment of the flywheel assembly with respect to the axis and preventing "whirl" from occurring.
  • Fig. 1 is a cross-sectional view of a Flywheel Energy Storage (FES) system utilizing one embodiment of a backup bushing assembly according to the present application out of engagement with the flywheel assembly; and
  • FES Flywheel Energy Storage
  • Fig. 2 is a cross-sectional view of the embodiment of Fig. 1, in engagement with the flywheel assembly.
  • FIG. 1 there is illustrated a cross-sectional view of one embodiment of a Flywheel Energy Storage (FES) system 10 according to the present application.
  • System 10 consists of an outer vacuum housing 12, an inner containment ring 14, a rotating flywheel assembly 16, a stationary shaft 17 having an axis "Y", a motor/generator 24 and main bearings 26a,b,c.
  • System 10 is preferably designed to store a total energy of 15 kilowatt-hours (kWh) at a maximum speed of approximately 16,000 revolutions per minute (rpm).
  • the usable energy storage at constant power is 12.5 kWh over an operating range from about 4,000 rpm to approximately 16,000 rpm.
  • FES system 10 is a stationary system having a rotating flywheel assembly weighing approximately 1000 lbs. with the flywheel assembly 16 having a diameter of approximately 36 inches and an overall height of approximately 45 inches.
  • Housing 12 encloses vacuum chamber 13 in which the flywheel assembly 16 operates.
  • Inner containment ring 14 helps contain any debris resulting from failure ofthe flywheel assembly 16, if failure should occur.
  • Inner containment ring 14 which is located about flywheel assembly 16 is preferably made of a high tensile strength material, such as steel, in order to withstand the momentum of impact from any debris resulting from flywheel failure.
  • a housing 12 in conjunction with a containment ring 14 a number of various containment systems may be utilized by one of skill in the art.
  • the design of any containment system requires knowledge of: 1) the failure mode of the flywheel, 2) the kinematics of the failed pieces, and 3) response of the containment system. By evaluating each of these criteria one of skill in the art can design a suitable containment system for a particular FES system.
  • the motor/generator 24 is a brushless permanent magnet motor which is air-cooled so as to minimize cost.
  • the motor/generator 24 spins the flywheel assembly 16 up to speed to transfer electric power into the system to store it as kinetic energy when the system is acting as a motor and also operates to generate electric energy from the stored kinetic energy to transfer the electric energy out of the system by coupling to the flywheel assembly when the system is operating as a generator, as is known in the art.
  • motor/generator 24 is designed to be a 12.5kw, 100% duty factor, 480V permanent magnet, three-phase motor with 30kw maximum input and output. Alternate motor/generators may be utilized depending upon the particular application for the FES system. With continued reference to Fig.
  • flywheel assembly 16 consists of a composite rotor 18, a hub 20, a cylinder 21 which contains a back-iron (not shown) ofthe motor/generator 24 and a hub 22 containing the main bearings' rotors (not shown).
  • a composite rotor other types of rotors including metallic rotors may also be utilized.
  • an E-glass composite rotor is preferred because due to the large size of the present system a low cost, durable material which is easy to manufacture is desired.
  • a composite rotor is preferred because optimal energy storage can be accomplished by maximizing the ratio of energy to mass, termed the energy density, and the greatest energy density is found using the highest specific tensile strength flywheel material and also because metallic rotors tend to shatter into sharp piercing fragments if failure occurs while composite rotors do not.
  • Lightweight composite materials consisting of fibers in a matrix, typically have very high material strengths relative to their mass densities.
  • Rotor 18 is preferably made of an E-glass composite material, but alternatively may be made of any material which has a high specific strength. Regardless of the material utilized, some factors which determine the design of the flywheel assembly include the desired energy storage capacity, cost, number of cycles and size constraints, etc.
  • flywheel assembly 16 is supported by main bearings 26a,b,c as it rotates about stationary shaft 17.
  • main bearings 26a,b,c are preferably active, magnetic bearings and include an axial magnetic bearing as well as a pair of radial magnetic bearings.
  • Magnetic bearings are the preferred method of providing support to the flywheel assembly 16 because they have low frictional losses, high speed capability and are compatible with a vacuum environment (i.e., do not require lubrication).
  • the axial magnetic bearing suspends the flywheel assembly 16 within housing 12 while the radial magnetic bearings align the flywheel assembly 16 about shaft 17, as is known in the art.
  • the radial bearings can take approximately 300 lbs of load.
  • Sensors 28 are connected through a path to each active bearing axis for each bearing 26a,b,c, for a total of five axis (radial bearings x and y axis, axial bearing z axis) for the three bearings.
  • Sensors 28 are proximity sensors which provide electronic feedback in order to control the stability of the flywheel assembly by digitally controlling the bearing properties and operation in order to properly place the bearings and the flywheel relative to each other.
  • magnetic bearings 26a,b,c are permanent magnet biased active bearings operating constantly at all rotating speeds, although other magnetic bearings which would be known to those skilled in the art may be utilized depending upon the particular application.
  • Magnetic bearings 26a, b, c work well in most operating situations but do have load limits and may become unstable or even fail due to many reasons including, but not limited to, loss of power.
  • backup-bushing system 30 which provides backup to magnetic bearings 26a, b, c in situations where the magnetic bearings 26a, b, c become unstable or fail.
  • Backup bushing system 30 includes a first, conical bushing 32 disposed about shaft 17 and a second, conical bushing 34, spaced from bushing 32 and disposed about shaft 17. Both bushings 32, 34 are attached to stationary shaft 17 at opposite ends thereof by bolts, clamps or the like although bushings 32, 34 may be attached to shaft 17 in any manner as long as the bushings are stationary with respect to the shaft.
  • bushings 32, 34 are preferably made of brass or bronze and are approximately 22" and 18" in diameter, although alternate sizes and materials such as soft iron or nylon may be utilized, as long as acceptable bushing life is achieved.
  • bearings may be utilized in place of the bushings, if cost is not a factor. Whatever types of elements are utilized for backup, the bearings or bushings should have low friction losses, be capable of operating in a vacuum (i.e. are "dry" lubricated), be durable and should preferably be cost effective.
  • Bushings 32, 34 preferably each have a conical contact portion 32a, 34b such that if the flywheel assembly 16 rests on the bushings with gravity, the flywheel assembly would be centered within the two contact portions 32a, 34b.
  • Contact portions 32a, 34b are preferably disposed at an angle ⁇ from the center axis "Y" of shaft 17 so as to create a greater re-centering force when contacting rotating flywheel assembly 16.
  • the narrower angle ⁇ is, the greater the centering force on flywheel assembly 16.
  • ⁇ is between approximately 30° - 45°, with an angle of approximately 45° being illustrated in Figs. 1 and 2, the 45° angle creating approximately 1000 lbs of re-centering force when contact portions 32a, 34b contact flywheel assembly 16.
  • flywheel assembly 16 preferably includes a conical shaped contact surface 35a,b on either end corresponding to the shape of contact portions 32a, 34b such that upon contact with contact portions 32a, 34b the motion of the flywheel assembly 16 is contained between the contact portions 32a, 34b as the flywheel assembly is driven down to rest on bushing 32.
  • Contact surfaces 35a,b are preferably smooth surfaces with low friction so as to limit the heat and wear on the contact surfaces.
  • Fig. 1 which shows the flywheel assembly during operation and out of contact with bushings 32, 34 in conjunction with Fig. 2 which shows the flywheel assembly in contact with and resting on bushing 32
  • Fig. 2 which shows the flywheel assembly in contact with and resting on bushing 32
  • the operation of the bushing system 30 will now be described.
  • flywheel assembly 16 experiences mechanical failure and moves off-center causing magnetic bearings 26a,b,c to become misaligned, or if the magnetic bearings are not properly aligned for any reason, including electric failure ofthe bearings, the flywheel assembly will contact conical contact portions 32a, 34b of bushings 32, 34, respectively.
  • the conical shape of the bushings and the weight ofthe flywheel assembly combine to keep the motion of the flywheel assembly 16 contained between the contact portions
  • flywheel assembly 16 Because the motion of flywheel assembly 16 is weight loaded by gravity against the conical contact portions 32a, 34b the flywheel assembly is prevented from experiencing "whirl” and is able to remain substantially centered about shaft 17, until coming to rest on bushing 32.
  • the backup bushing assembly ofthe present embodiment thereby acts as an inexpensive fail-safe if there is an interruption in power.
  • the present embodiment is easy to manufacture, is cost effective, durable and may also be utilized to re-center flywheel assembly 16 as described hereinbelow.
  • the repulsive magnetic field created by the axial magnetic bearing can be reversed in order to create a magnetic attraction thereby pulling the flywheel assembly 16 into contact with the conical contact portions 32a, 32b of bushings 32, 34 in order to re-center the flywheel assembly.
  • the conical shape of the bushings and the weight of the flywheel assembly combine to keep the motion of the flywheel assembly 16 contained between the contact portions 32a, 34b whose shape acts to re-center the flywheel assembly with respect to shaft 17.
  • the axially magnetic bearing 26a can be returned to a repulsive magnetic bearing, thereby once again levitating the flywheel assembly 16.
  • the bushing assembly may be bearings instead of bushings
  • the magnetic bearings may instead be air bearings
  • the backup bushing assembly may be used with other systems which utilize magnetic or air bearings, other than a flywheel energy storage system.
  • the stationary shaft of the present application is shown as being vertical, the shaft may alternatively be disposed horizontally or at an angle. Therefore, the above description should not be construed as limiting, but merely as exemplifications of preferred embodiments. Those skilled in the art will envision other modifications within the scope and spirit ofthe claims appended hereto.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)

Abstract

Les systèmes de paliers tels que les paliers magnétiques sont largement utilisés de nos jours. Toutefois, ils sont tous susceptibles d'avoir des défaillances. C'est pourquoi on utilise souvent des systèmes de renfort en combinaison avec un système de paliers principal. Le système de douilles de renfort de la présente demande s'utilise avec un ensemble à volant d'inertie qui est aligné et tourne autour de l'axe d'un arbre fixe et comprend une première douille sensiblement fixe par rapport à l'axe, et qui présente un première partie de contact, et une deuxième douille, espacée par rapport à la première et sensiblement fixe par rapport à l'axe, et qui présente un deuxième partie de contact. Si l'ensemble à volant d'inertie subit un mouvement de décentrage par rapport à l'axe, il entre en contact avec les première et deuxième douilles. A l'entrée en contact, les douilles agissent pour contenir la rotation de l'ensemble à volant d'inertie entre les parties de contact, ce qui maintient sensiblement l'alignement de cet ensemble par rapport à l'axe et empêche le 'flottement'.
PCT/US1996/020396 1995-12-29 1996-12-16 Douilles de renfort radiales serrees servant a recentrer des paliers magnetiques Ceased WO1997024536A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US58141495A 1995-12-29 1995-12-29
US08/581,414 1995-12-29

Publications (1)

Publication Number Publication Date
WO1997024536A1 true WO1997024536A1 (fr) 1997-07-10

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PCT/US1996/020396 Ceased WO1997024536A1 (fr) 1995-12-29 1996-12-16 Douilles de renfort radiales serrees servant a recentrer des paliers magnetiques

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1425839A4 (fr) * 2001-09-13 2006-05-10 Beacon Power Corp Systeme de gestion d'incidents concu pour etre mis en oeuvre dans des systemes a volants d'inertie
US7109622B2 (en) * 2003-06-06 2006-09-19 Pentadyne Power Corporation Flywheel system with synchronous reluctance and permanent magnet generators
WO2008142363A1 (fr) * 2007-05-17 2008-11-27 Flybrid Systems Llp Dispositif de confinement d'un volant haute vitesse
EP4191091A1 (fr) * 2021-12-06 2023-06-07 Abb Schweiz Ag Dispositif de volant d'inertie pour un condensateur synchrone

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1400974A1 (de) * 1962-08-22 1969-01-16 Commissariat Energie Atomique Rotierende Maschine
DE3150122A1 (de) * 1981-12-18 1983-06-30 Teldix Gmbh, 6900 Heidelberg Magnetische lagereinrichtung
US4700094A (en) * 1984-12-17 1987-10-13 The Charles Stark Draper Laboratory, Inc. Magnetic suspension system
WO1992012566A1 (fr) * 1991-01-11 1992-07-23 American Flywheel Systems, Inc. Procede et appareil de stockage d'energie

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1400974A1 (de) * 1962-08-22 1969-01-16 Commissariat Energie Atomique Rotierende Maschine
DE3150122A1 (de) * 1981-12-18 1983-06-30 Teldix Gmbh, 6900 Heidelberg Magnetische lagereinrichtung
US4700094A (en) * 1984-12-17 1987-10-13 The Charles Stark Draper Laboratory, Inc. Magnetic suspension system
WO1992012566A1 (fr) * 1991-01-11 1992-07-23 American Flywheel Systems, Inc. Procede et appareil de stockage d'energie

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1425839A4 (fr) * 2001-09-13 2006-05-10 Beacon Power Corp Systeme de gestion d'incidents concu pour etre mis en oeuvre dans des systemes a volants d'inertie
US7365461B2 (en) 2001-09-13 2008-04-29 Beacon Power Corporation Crash management system for implementation in flywheel systems
US7109622B2 (en) * 2003-06-06 2006-09-19 Pentadyne Power Corporation Flywheel system with synchronous reluctance and permanent magnet generators
WO2008142363A1 (fr) * 2007-05-17 2008-11-27 Flybrid Systems Llp Dispositif de confinement d'un volant haute vitesse
US8234953B2 (en) 2007-05-17 2012-08-07 Flybrid Systems Llp High speed flywheel containment
EP4191091A1 (fr) * 2021-12-06 2023-06-07 Abb Schweiz Ag Dispositif de volant d'inertie pour un condensateur synchrone
WO2023104722A1 (fr) * 2021-12-06 2023-06-15 Abb Schweiz Ag Dispositif de volant pour condensateur syncrone

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