WO2023085098A1 - Rotor à disque creux orthotrope pour volant d'inertie destiné à un dispositif d'accumulation de puissance électrique à volant d'inertie, et son procédé de détermination de rapport de diamètre interne/externe optimal - Google Patents

Rotor à disque creux orthotrope pour volant d'inertie destiné à un dispositif d'accumulation de puissance électrique à volant d'inertie, et son procédé de détermination de rapport de diamètre interne/externe optimal Download PDF

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Publication number
WO2023085098A1
WO2023085098A1 PCT/JP2022/040017 JP2022040017W WO2023085098A1 WO 2023085098 A1 WO2023085098 A1 WO 2023085098A1 JP 2022040017 W JP2022040017 W JP 2022040017W WO 2023085098 A1 WO2023085098 A1 WO 2023085098A1
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WO
WIPO (PCT)
Prior art keywords
flywheel
orthotropic
storage device
disk rotor
hollow disk
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PCT/JP2022/040017
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English (en)
Japanese (ja)
Inventor
智 谷本
孝 中村
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ネクスファイ・テクノロジー株式会社
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Publication of WO2023085098A1 publication Critical patent/WO2023085098A1/fr

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
    • B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
    • B29C70/00—Shaping composites, i.e. plastics material comprising reinforcements, fillers or preformed parts, e.g. inserts
    • B29C70/04—Shaping composites, i.e. plastics material comprising reinforcements, fillers or preformed parts, e.g. inserts comprising reinforcements only, e.g. self-reinforcing plastics
    • B29C70/06—Fibrous reinforcements only
    • 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
    • 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
    • F16F15/305—Flywheels made of plastics, e.g. fibre reinforced plastics [FRP], i.e. characterised by their special construction from such materials
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02J—CIRCUIT ARRANGEMENTS OR SYSTEMS FOR SUPPLYING OR DISTRIBUTING ELECTRIC POWER; SYSTEMS FOR STORING ELECTRIC ENERGY
    • H02J15/00—Systems for storing electric energy
    • 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 present invention relates to a technique for improving the stored energy of a hollow disc (including a cylinder) rotor, which is the main element of the flywheel of a flywheel power storage device.
  • the present invention relates to a technique for improving the stored energy of a flywheel hollow disc rotor having orthotropic anisotropy in which the longitudinal elastic constant and tensile yield strength in the circumferential direction are higher than those in the radial direction.
  • a typical rotor that corresponds to this is a "fiber-reinforced plastic" rotor in which high-strength fibers are wound in the circumferential direction and the interstices of the fibers are impregnated and solidified with epoxy resin or the like, but it is not limited to this.
  • “orthotropic hollow disk (or cylinder) rotor” may be abbreviated as “rotor” and “flywheel” as "FW”.
  • the FW power storage device stores external electric power in the FW rotor as rotational kinetic energy through a means for mutually converting electrical energy and rotational kinetic energy, and conversely supplies the rotational kinetic energy of the FW rotor to the outside as electric power. It is a power storage device with a function of
  • FRP reinforced in the circumferential direction has characteristics suitable for FW rotors, such as "low density” and "high strength in the circumferential direction". It is expected that the FW storage device constructed using the FRP-FW rotor will be able to increase the stored energy by at least several times compared to the conventional metal FW rotor FW storage device.
  • such an FRP-FW rotor has strong orthotropic anisotropy. That is, it has a feature that the longitudinal elastic constant (Young's modulus) and the tensile yield strength are very large along the circumferential direction, and considerably small in the radial direction and the rotation axis direction perpendicular thereto.
  • FRP-FW rotor A typical example of an FRP-FW rotor is a FW high-strength carbon fiber reinforced plastic (CFRP)-FW rotor as described in FIGS. 1 and 5 of Patent Document 1 below.
  • CFRP carbon fiber reinforced plastic
  • the FW includes a hollow disk CFRP-FW rotor that stores rotational energy, a rotating shaft that transfers the rotational energy of the CFRP-FW rotor to a generator/motor, and the CFRP - a spoked hub connecting the FW rotor and said rotating shaft;
  • the high-strength carbon fiber of the CFRP-FW rotor is wound and laminated in the circumferential direction to strengthen the tensile yield strength so that it can fully withstand the strong tensile stress generated in the circumferential direction during rotation.
  • Such a structure is used because the rotational tensile stress that causes fracture is much stronger (typically one order of magnitude or more) in the circumferential direction than in the radial direction.
  • limit stored energy here is the basic amount when evaluating (comparing) the power storage performance of the rotor, and is the maximum rotational motion that can be stored before the rotor, which is increasing its rotational speed, is on the verge of breaking. refers to energy. Although the details will be described later, the limit storage energy of the FRP rotor strongly depends on the shape (specifically, the inner/outer diameter ratio ⁇ ).
  • an object of the present invention is to provide an orthotropic hollow disk rotor of a flywheel for a flywheel power storage device that maximizes the limit storage energy, and a method for determining the optimum inner/outer diameter ratio thereof.
  • the present invention relates to an orthotropic hollow disk rotor including an FRP (CFRP)-FW rotor, which is the main element of the flywheel of a flywheel power storage device, and the other main elements, such as the form of the hub and the rotating shaft, and the It can be applied regardless of the structure.
  • FRP FRP
  • the invention according to claim 1 provides an orthotropic hollow disc rotor for a flywheel for a flywheel power storage device, having an outer radius of b, an inner radius of a, and a height of h.
  • the volume ⁇ b 2 h of an imaginary solid disk whose base is a circle of radius b and whose height is h is defined as the “physique”
  • the invention according to claim 2 is the orthotropic hollow disk rotor of the flywheel for a flywheel power storage device according to claim 1, wherein the orthotropic anisotropy of the orthotropic hollow disk rotor includes at least a circumferential It is characterized by including an anisotropy in which the longitudinal elastic constant and tensile yield strength in the direction are higher than the longitudinal elastic constant and tensile yield strength in the radial direction.
  • the invention according to claim 3 is the orthotropic hollow disk rotor of the flywheel for a flywheel power storage device according to claim 1, wherein the density is ⁇ , the circumferential longitudinal elastic modulus is E ⁇ , and the radial longitudinal elastic modulus is When E r , ⁇ ⁇ is the Poisson's ratio in the circumferential direction, ⁇ y ⁇ is the tensile yield strength in the circumferential direction, and ⁇ yr is the tensile yield strength in the radial direction, the optimal inner/outer diameter ratio ⁇ OPT is E ⁇ , Er , ⁇ ⁇ , ⁇ y ⁇ , ⁇ yr and ⁇ are analytically determined.
  • the invention according to claim 4 is the orthotropic hollow disk rotor of the flywheel for a flywheel power storage device according to claim 2, wherein the voids of the high-strength fibers wound in the circumferential direction are impregnated with a matrix agent. It is characterized by being composed of a composite material.
  • the invention according to claim 5 is the orthotropic hollow disk rotor of the flywheel for a flywheel power storage device according to claim 4, wherein the high-strength fiber is carbon fiber, boron fiber, glass fiber, aramid fiber, or alumina fiber. , silicon carbide fibers, and various metal fibers, or composite fibers in which two or more of these are combined.
  • the invention according to claim 6 is the orthotropic hollow disk rotor of the flywheel for a flywheel power storage device according to claim 4, wherein the matrix agent is various resins including epoxy resin, or a lightweight low temperature rotor including Al or Mg. It is characterized by being a molten metal.
  • the orthotropic hollow disk rotor of the flywheel for a flywheel power storage device according to the first aspect, wherein the inner/outer diameter ratio in the vicinity of the optimum inner/outer diameter ratio ⁇ OPT is at least ⁇ OPT ⁇ 0. 1 to ⁇ OPT +0.1, preferably ⁇ OPT ⁇ 0.05 to ⁇ OPT +0.05.
  • the invention according to claim 8 is a method for determining the optimum inner/outer diameter ratio ⁇ OPT in the orthotropic hollow disk rotor of the flywheel power storage device flywheel according to claim 3, wherein at least the physical limit energy density U y / The step of expressing ( ⁇ b 2 h) as a function of the inner/outer diameter ratio ⁇ is included.
  • the invention according to claim 9 is the method for determining the optimum inner/outer diameter ratio ⁇ OPT according to claim 8, 1) The rotational stresses ⁇ ⁇ and ⁇ r (the subscript ⁇ means the circumferential direction and r means the radial direction) at the radius r point of the orthotropic hollow disk rotor as a function of r with ⁇ as a parameter a step of expressing as 2) obtaining the maximum points ⁇ ⁇ M and ⁇ rM of the functions ⁇ ⁇ and ⁇ r as function curves ⁇ ⁇ M ⁇ and ⁇ rM ⁇ of ⁇ ; 3) A step of converting the function curves ⁇ ⁇ M ⁇ and ⁇ rM ⁇ to obtain function curves b ⁇ y ⁇ of the critical peripheral speeds b ⁇ y and ⁇ (where ⁇ y is the limit of the orthotropic hollow disk rotor angular velocity) and 4) Subsequently, the step of converting the function curve b ⁇ y ⁇ into a
  • FIG. 4 is a diagram showing the relationship between the rotational stress ⁇ of the FW rotor and the radius r for explaining the first embodiment of the present invention
  • FIG. 4 is a diagram showing the relationship between the maximum rotational stress ⁇ M of the FW rotor and the inner/outer diameter ratio ⁇ for explaining the first embodiment of the present invention
  • FIG. 4 is a diagram showing the relationship between the peripheral speed b ⁇ y of the FW rotor and the inner/outer diameter ratio ⁇ for explaining the first embodiment of the present invention
  • FIG. 4 is a diagram showing the relationship between the rotational stress ⁇ of the FW rotor and the radius r for explaining the first embodiment of the present invention
  • FIG. 4 is a diagram showing the relationship between the maximum rotational stress ⁇ M of the FW rotor and the inner/outer diameter ratio ⁇ for explaining the first embodiment of the present invention
  • FIG. 4 is a diagram showing the relationship between the peripheral speed b ⁇ y of the FW rotor and the inner/outer diameter ratio
  • FIG. 4 is a diagram showing the relationship between the actual peripheral speed b ⁇ y of the FW rotor and ⁇ for explaining the first embodiment of the present invention
  • FIG. 4 is a diagram showing the relationship between the normalized limit energy (physical energy density) U y /( ⁇ b 2 h) and ⁇ of the FW rotor for explaining the first embodiment of the present invention
  • FIG. 4 is a diagram showing the relationship between the radial-to-circumferential maximum stress ratio ⁇ rM / ⁇ ⁇ M and ⁇ of the FW rotor for explaining the first embodiment of the present invention
  • FIG. 4 is a diagram showing the relationship between the mass critical energy density Dy of the FW rotor and ⁇ for explaining the first embodiment of the present invention
  • FIG. 8 is a diagram showing the relationship between U y /( ⁇ b 2 h) and ⁇ and the relationship between ⁇ rM / ⁇ ⁇ M and ⁇ of the FW rotor for explaining the second embodiment of the present invention
  • FIG. 10 is a diagram showing the relationship between U y /( ⁇ b 2 h) and ⁇ and the relationship between ⁇ rM / ⁇ ⁇ M and ⁇ of the FW rotor for explaining the third embodiment of the present invention
  • FIG. 10 is a diagram showing the relationship between U y /( ⁇ b 2 h) and ⁇ and the relationship between ⁇ rM / ⁇ ⁇ M and ⁇ of the FW rotor for explaining the fourth embodiment of the present invention
  • FIG. 11 is a diagram showing the relationship between U y /( ⁇ b 2 h) and ⁇ and the relationship between ⁇ rM / ⁇ ⁇ M and ⁇ of the FW rotor for explaining the fifth embodiment of the present invention;
  • the unit system is the SI unit system
  • the variables ⁇ ⁇ and ⁇ r are rotational stresses generated in the circumferential direction and the radial direction, respectively
  • ⁇ is the density of the material of the FW rotor 1 .
  • E ⁇ and E r are the Young's moduli (modulus of longitudinal elasticity) of the FW rotor 1 in the circumferential direction and the radial direction, respectively, and ⁇ ⁇ is the Poisson's ratio of the rotor 1 in the ⁇ direction. It can be seen that ⁇ r and ⁇ ⁇ are functions of the relative radius variable r/b with the inner/outer diameter ratio ⁇ as a parameter.
  • (b ⁇ ) 2 is a function that increases with the square of the peripheral speed b ⁇
  • (1 ⁇ 4 ) is a function that rapidly changes from 1 to 0 ( is a function that decreases to zero).
  • Carbon fiber T1000G (Toray Industries, Inc.) is a material widely known in the industry and academia as a carbon fiber with extremely high tensile yield strength.
  • the first column in Table 1 shows the elastic constants (Young's modulus E ⁇ , E r , Poisson's ratio ⁇ ⁇ ) and tensile yield strength ( ⁇ y ⁇ , ⁇ yr ) of the CFRP-FW rotor 1 circumferentially reinforced with T1000G.
  • the density ⁇ is listed.
  • the matrix agent used is epoxy resin 470-36S (Ashland Inc.). As a document on which these numerical values are based, "MA Conteh, E.C. Nsofor, J. Appl. Res. Tech., 14 (2016), pp. 184-190" (reference document 1) is cited.
  • FIG. 2 shows radial profiles of stresses ⁇ ⁇ and ⁇ r calculated using equations (2) and (3).
  • the vertical axis of the graph normalizes (divides) the stresses ⁇ ⁇ and ⁇ r by ⁇ (b ⁇ ) 2 .
  • the FW rotor 1 gradually accelerates the rotational angular velocity ⁇ (or the outer peripheral speed b ⁇ ), the maximum circumferential stress value ⁇ ⁇ M and the maximum radial stress value ⁇ rM inside the FW rotor 1 increase, and finally one of them
  • the FW rotor 1 yields (breaks) when the tensile yield strengths ⁇ y ⁇ and ⁇ yr of are exceeded. Reconsidering FIG. 4 according to this maximum stress failure model, it can be seen that the actual relationship between b ⁇ y and ⁇ for the FW rotor is shown in FIG.
  • FIG. 6 is obtained in this way.
  • the vertical axis in FIG. 6 is the critical energy normalized (divided) by ⁇ b 2 h . Since ⁇ b 2 h corresponds to the volume of an imaginary cylinder of height h whose base is a circle of radius b, i . It is a quantity that can be called "limiting energy density".
  • ⁇ OPT is the point where the curves b ⁇ ⁇ y and b ⁇ ry intersect (match). At this ⁇ point, circumferential yielding and radial yielding occur simultaneously, so
  • the critical stored energy here, the normalized critical stored energy
  • U y /( ⁇ b 2 h ) 128 kWh/m 3 , much lower than the 200 kWh/m 3 of the present invention.
  • FIG. 8 shows the result of plotting Dy of the FW rotor 1 of the first embodiment as a function of ⁇ .
  • the vertical axis b ⁇ y in FIG. 5 is converted to Dy .
  • D y is a function that consistently and monotonically increases in the effective interval 0 ⁇ 1 of the inner/outer diameter ratio. The closer ba is to zero, the higher Dy .
  • the present invention is not limited to CFRP, but is applicable to all FRP.
  • the third embodiment of the present invention is an example of optimization of the structure of the BFRP-FW rotor 1 made of boron fiber B(4) (manufacturer unknown) and epoxy resin 5505 (SICOMIN).
  • the third column of Table 1 shows the material properties of this circumferentially reinforced BFRP material. As a document showing this material property, "Mitsunori Miki, Materials 30 (1981) pp.943-948" (reference document 3) is cited.
  • the FW orthotropic hollow disk rotor 1 according to the present invention is not limited to the materials of the above embodiments, and can be applied to rotors using various orthotropic materials.
  • alumina fibers, silicon carbide fibers, and various metal fibers can be used as high-strength fiber materials.
  • lightweight low-temperature melting metals such as Al and Mg can also be used as matrix agents.
  • the present invention is an orthotropic hollow disk rotor of a flywheel for a flywheel power storage device that maximizes the limit accumulated energy, and a method for determining the optimum inner/outer diameter ratio thereof.
  • a flywheel rotor, which is a main element of a flywheel, according to the present invention can be applied to a flywheel power storage device regardless of the forms and structures of other main elements, such as a hub and a rotating shaft.
  • FW rotor flywheel orthotropic hollow disk rotor
  • b outer radius of FW rotor
  • a inner radius of FW rotor
  • h height of FW rotor
  • r radius (variable)
  • ⁇ azimuth angle (variable)
  • z central axis.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Composite Materials (AREA)
  • Power Engineering (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
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Abstract

L'objet de la présente invention est de produire : un rotor à disque creux orthotrope qui est destiné à un volant d'inertie d'un dispositif d'accumulation de puissance électrique à volant d'inertie et qui augmente au maximum une limite d'énergie accumulée ; et un procédé de détermination de rapport de diamètre interne/externe optimal du rotor à disque creux orthotrope. L'invention concerne donc un rotor à disque creux orthotrope 1 d'un volant d'inertie destiné à un dispositif d'accumulation de puissance électrique à volant d'inertie. Selon l'invention, lorsque l'on définit une « taille physique » comme étant le volume πb2h d'un disque solide imaginaire ayant un cercle d'un rayon externe b en tant que sa surface inférieure et ayant une hauteur h, le rapport de diamètre interne/externe optimal auquel est obtenue la limite de densité d'énergie accumulée maximale pour la taille physique pendant la rotation est λOPT = a/b ou est voisin de λOPT.
PCT/JP2022/040017 2021-11-09 2022-10-26 Rotor à disque creux orthotrope pour volant d'inertie destiné à un dispositif d'accumulation de puissance électrique à volant d'inertie, et son procédé de détermination de rapport de diamètre interne/externe optimal WO2023085098A1 (fr)

Applications Claiming Priority (2)

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JP2021182821A JP2023070559A (ja) 2021-11-09 2021-11-09 フライホイール蓄電装置用フライホイールの直交異方性中空円盤ロータ及びその最適内外径比の決定方法
JP2021-182821 2021-11-09

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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5359175A (en) * 1976-11-09 1978-05-27 Mitsubishi Heavy Ind Ltd Body of revolution
JP2000055134A (ja) * 1998-08-06 2000-02-22 Fuji Heavy Ind Ltd 複合材フライホイール装置

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5359175A (en) * 1976-11-09 1978-05-27 Mitsubishi Heavy Ind Ltd Body of revolution
JP2000055134A (ja) * 1998-08-06 2000-02-22 Fuji Heavy Ind Ltd 複合材フライホイール装置

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