WO2006102813A1 - Appareil d'oscillation pour moule de moulage continu - Google Patents

Appareil d'oscillation pour moule de moulage continu Download PDF

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Publication number
WO2006102813A1
WO2006102813A1 PCT/CN2005/002030 CN2005002030W WO2006102813A1 WO 2006102813 A1 WO2006102813 A1 WO 2006102813A1 CN 2005002030 W CN2005002030 W CN 2005002030W WO 2006102813 A1 WO2006102813 A1 WO 2006102813A1
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Prior art keywords
spring
crystallizer
kit
vibrating
frequency
Prior art date
Application number
PCT/CN2005/002030
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English (en)
French (fr)
Inventor
Hong Jiang
Zhiheng Tian
Original Assignee
Hong Jiang
Zhiheng Tian
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 Hong Jiang, Zhiheng Tian filed Critical Hong Jiang
Priority to BRPI0519891-7A priority Critical patent/BRPI0519891B1/pt
Priority to EP05814213.4A priority patent/EP1886746B1/en
Priority to KR1020097015964A priority patent/KR101105917B1/ko
Publication of WO2006102813A1 publication Critical patent/WO2006102813A1/zh

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
    • B22D11/00—Continuous casting of metals, i.e. casting in indefinite lengths
    • B22D11/04—Continuous casting of metals, i.e. casting in indefinite lengths into open-ended moulds
    • B22D11/053—Means for oscillating the moulds
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
    • B22D11/00—Continuous casting of metals, i.e. casting in indefinite lengths
    • B22D11/16—Controlling or regulating processes or operations
    • B22D11/166—Controlling or regulating processes or operations for mould oscillation
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
    • B22D11/00—Continuous casting of metals, i.e. casting in indefinite lengths
    • B22D11/16—Controlling or regulating processes or operations
    • B22D11/18—Controlling or regulating processes or operations for pouring
    • B22D11/181—Controlling or regulating processes or operations for pouring responsive to molten metal level or slag level
    • B22D11/186—Controlling or regulating processes or operations for pouring responsive to molten metal level or slag level by using electric, magnetic, sonic or ultrasonic means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
    • B22D19/00—Casting in, on, or around objects which form part of the product
    • B22D19/0009—Cylinders, pistons

Definitions

  • the present invention relates to a reformer of a continuous casting machine crystallizer, particularly a non-sinusoidal vibrating device.
  • the crystallizer vibrates according to the specified frequency, waveform and amplitude, especially the non-sinusoidal vibration with slow upper vibration speed and fast lower vibration speed, which can improve the lubrication effect of the mold flux and greatly reduce the between the shell and the crystallizer.
  • the frictional force reduces the cracking and heals the cracked shell, which significantly improves the surface quality and the casting speed of the slab.
  • the actuators of the crystallizer vibrating device designed according to the above requirements can be divided into two categories: one is a hydraulic servo system (EP0468607A11), which is composed of a high-power electro-hydraulic servo valve, a servo cylinder, a hydraulic pump station, etc., and the disadvantage is that the system Complex, costly and difficult to maintain.
  • the second type is the crank-link type mechanical transmission device (ZL99216172. X, ZL01205318. X).
  • This type of device uses a horizontal motor as the actuator, which is low in cost, but cannot adjust the amplitude and waveform on-line, and is difficult to adapt to high-efficiency continuous casting. Requirements.
  • the power of the vibration-vibrating devices of both types of devices is relatively large.
  • An object of the present invention is to provide a crystallizer vibrating apparatus which can reduce the frequency, waveform and amplitude of the vibration of the crystallizer while reducing the power of the vibration-requiring device.
  • the object of the present invention is achieved by determining the stiffness of the load-bearing spring set according to the vibration mass and the moment of inertia of the electric cylinder, so that the natural frequency of the vibration system is close to the required vibration frequency, thereby realizing the conversion of the kinetic energy and the potential energy of the vibration system close to equilibrium, thereby Use an electric cylinder as an actuator and reduce the power of the electric cylinder.
  • a hydraulic cylinder is provided under the spring kit to change the number of spring sets that support the vibrating gantry, thereby changing the natural frequency of the vibrating system to approximate the vibration frequency of the crystallizer.
  • the spring kit is divided into several sections by a partition plate, and the corresponding partition plate is fixed by a pneumatic card plate for changing the length of the spring kit supporting the vibration stage, thereby changing the natural frequency of the vibration system and vibrating the crystallizer The frequency is close.
  • the control system produces frequency, slope and amplitude.
  • the on-line adjustable waveform controls the electric cylinder to drive crystallizer vibration and controls the hydraulic cylinder or pneumatic chuck to change the number or length of the spring kit. Since the electric cylinder composed of the motor and the ball screw pair can easily realize the axial movement of the specified speed curve by programming, the amplitude, frequency and waveform are driven by the vertically mounted electric cylinder to drive the vibration table under the condition of torque and power. Online adjustable crystallizer sinusoidal or non-sinusoidal vibration is undoubtedly the easiest way. Only the up and down reciprocating motion of the electric cylinder nut is realized by the forward and reverse rotation of the motor rotor and the lead screw.
  • m is the mass of the vibrating portion of the crystallizer
  • I is the moment of inertia of the electric cylinder
  • d is the lead of the electric cylinder screw
  • k is the stiffness of the spring kit.
  • the vibration frequency of the crystallizer changes with the casting speed.
  • the actuator is required during the casting process in which the casting speed is increased from zero to the specified drawing speed.
  • the output power may be large, but the duration of this process is short, and the average output power of the electric cylinder in a short time is higher than the rated output power, which can meet the requirements of this condition.
  • the stiffness of the spring kit is proportional to the number of spring kits under the condition that the spring kits of the same length and stiffness are symmetrically distributed with respect to the center of gravity of the crystallizer and the vibrating table.
  • Crystallizer When the vibration frequency changes due to different working conditions (such as slab cross section and steel type change), the number of spring kits can be changed to match the stiffness of the spring kit with the required frequency.
  • the increase or decrease in the number of spring sets that support the vibrating gantry can be achieved by increasing the height of several spring sets and lowering the height of several other spring sets.
  • a hydraulic cylinder is placed under the spring kit, and the stiffness of the spring kit can be quickly adjusted by the control system.
  • the stiffness of the spring kit is inversely proportional to the length of the spring kit.
  • Each spring kit is divided into segments, for example, equally divided into n segments (ie each spring kit is superimposed by n identical springs) with a gap between each segment a plate, when the crystallizer and the vibrating table compress the entire spring set so that the system is in equilibrium and the height of the crystallizer reaches the zero position of the vibration, the spacers under the mth segment (from the top) are fixed by a pneumatic chuck.
  • the stiffness of the spring kit will increase to n/m times the original stiffness.
  • Figure 1 is a system diagram of a crystallizer vibrating device with an adjustable number of spring sets
  • Figure 2 is a plan view of the vibration device shown in Figure 1;
  • Figure 3 is a left side view of the vibration device of Figure 1;
  • Figure 4 is a schematic diagram of the crystallizer vibrating device with adjustable length of the spring kit.
  • the first embodiment of the present invention is shown in Figs. 1 to 3.
  • the crystallizer (101) sits on the vibrating table (102).
  • the four electric cylinders (104) are symmetrically distributed with respect to the center of gravity of the mold. Vibrating table
  • a pair of spring sets (103) that reduce the symmetry of the center of gravity of the crystallizer (101) and the vibrating table (102) can reduce the stiffness of the remaining spring kit to 3/4 of the original stiffness, corresponding spring pack compression The amount rises to 4/3 ⁇ .
  • the control cylinder (106) can be used to control the hydraulic cylinder (106) to lower the pair of spring sets (103) by ⁇ + s (s is the oscillating range of the crystallizer) and increase the other three pairs of spring sets by 1/3 ⁇ . .
  • the weight of the relative crystallizer (101) and the vibration gantry (102) can be reduced.
  • a pair of symmetrical distributions of 1 or 3 pairs of spring sets (103) reduces the stiffness of the remaining spring set (103) to 1/2 or 1/4 of the original stiffness.
  • the control system (105) generates a frequency, a slope and an amplitude.
  • the on-line adjustable waveform control electric cylinder (104) drives the crystallizer (101) to vibrate and controls the hydraulic cylinder (106) to change the number of spring sets (103).
  • a second embodiment of the invention is shown in Figure 4.
  • the crystallizer (201) sits on the vibrating table (202).
  • the four electric cylinders (204) are symmetrically distributed with respect to the center of gravity of the crystallizer.
  • the vibrating table (202) is supported by four identical spring sets (203), the spring sets (203) are supported on the base (208), and each spring set (203) is supported by two upper and lower springs (203a) and (203b). Superimposed, the effective length of the spring (203a) is 1/3 of the effective length of the spring (203b) with a partition (206) therebetween.
  • the diaphragm (206) is activated by the pneumatic chuck (207) under the condition that the crystallizer (201) and the vibrating table (202) compress the ⁇ length to be in equilibrium, and the spring kit (203) is fixed. Only (203a) works, and its stiffness is increased by 4 times. Similarly, each spring kit (203) can be divided into several sections, with a partition (206) between each section and a pneumatic chuck (207) corresponding to the compression balance of each partition (206). A wider range of adjustments are made to the stiffness of the spring kit (203).
  • the control system (205) generates a frequency, a slope, and an amplitude.
  • the on-line adjustable waveform control electric cylinder (204) drives the crystallizer (201) to vibrate and controls the pneumatic chuck (207) to change the length of the spring assembly (203).

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Continuous Casting (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Vibration Prevention Devices (AREA)
  • Moulds For Moulding Plastics Or The Like (AREA)
  • Casting Devices For Molds (AREA)

Description

结晶器振动装置 技术领域
本发明涉及连铸机结晶器振动装置， 特别是非正弦振动装置的改 进。
技术背景
结晶器按指定的频率、 波形和振幅振动， 特别是上振速度慢而下 振速度快的非正弦振动， 可改善结晶器保护渣的润滑作用， 大幅度减 小坯壳和结晶器之间的磨擦力， 减少拉裂并使拉裂的坯壳得到愈合， 使铸坯表面质量及拉坯速度明显提高。 按上述要求设计的结晶器振动 装置的致动器可分为两类： 一类为液压伺服系统（EP0468607A11) , 由 大功率电液伺服阀、 伺服油缸、 液压泵站等组成， 其缺点是系统复杂， 成本高且不易维护。 第二类为曲柄连杆式机械传动的装置 (ZL99216172. X, ZL01205318. X) , 这类装置用卧式电机作致动器， 成 本低， 但不能在线调整振幅和波形， 难于适应高效连铸的要求。 另外， 这两类装置的驱振动力设备的功率都比较大。
发明内容
本发明的目的是提供一种既可降低所需驱振动力设备功率， 又可 在线调整结晶器振动的频率、 波形和振幅， 而致动器为电动缸的结晶 器振动装置。
本发明的目的是这样实现的， 根据振动质量和电动缸的转动惯量 确定承重弹簧套件的刚度， 使振动系统的自然频率接近要求的振动频 率， 实现振动系统动能和势能接近平衡的转换， 从而可以用电动缸作 致动器并降低电动缸的功率。
弹簧套件下设液压缸， 用于改变支撑振动台架的弹簧套件的数 量， 以此改变振动系统的自然频率使与结晶器的振动频率接近。
用隔板将弹簧套件分成若干段， 用气动卡板将相应的隔板固定， 以用于改变支撑振动台架的弹簧套件的长度， 以此改变振动系统的自 然频率， 使与结晶器的振动频率接近。
控制系统产生频率、 偏斜率和振幅在线可调的波形控制电动缸驱 动结晶器振动， 并控制液压缸或气动卡板改变弹簧套件的数量或长 度。 由于电机和滚珠丝杠副所构成的电动缸通过编程很容易实现指定 速度曲线的轴向运动， 在扭矩和功率允许的条件下， 由竖直安装的电 动缸驱动振动台实现振幅、 频率和波形在线可调的结晶器正弦或非正 弦振动无疑是最简捷的方法。 只是电动缸螺母的上下往复运动是由电 机转子和丝杠的正向和反向转动来实现的。 在转动方向以每分钟达数 百次的高速切换过程中， 需要较大的扭矩和功率来实现有较大质量的 结晶器和振动台的上下加速运动以及有较大转动惯量的电机转子和滚 珠丝杠副的丝杠的正反向加速旋转运动， 而且后者需要的功率通常大 于前者。 这么大的扭矩和功率完全靠电动缸来提供是不现实的。 以往 在振动台下面设有弹簧套件， 而确定弹簧套件刚度的方法是使其与振 动质量构成的系统的自然频率与结晶器的振动频率相匹配。 本发明对 电动缸的转动惯量、 结晶器的振动部分的质量和弹簧套件的刚度进行 综合考虑， 求出系统的自然频率 fn:
Figure imgf000004_0001
式中 m是结晶器振动部分的质量， I 是电动缸的转动惯量， d是电动 缸丝杠的导程， k是弹簧套件的刚度。 当结晶器的振动频率接近 fn时， 结晶器振动部分的重力势能和弹簧套件的弹性势能与电动缸的转动动 能和结晶器的振动动能之间接近平衡转换而达到最佳补偿， 从而降低 所需电动缸的输出扭矩和功率， 实现用电动缸作致动器驱动结晶器按 指定的频率、 波形和振幅进行振动并降低所需电动缸的功率的目的。 通常结晶器的振动频率随拉坯速度而改变， 当弹簧套件的刚度按指定 拉坯速度调整好后， 在拉坯速度从零上升到指定拉速的开浇过程中， 所需致动器的输出功率可能较大， 但这个过程的持续时间较短， 而一 般电动缸短时间最大输出功率均比额定输出功率较高， 能适应这一工 况的妻求。
在长度和刚度相同的诸弹簧套件相对结晶器和振动台的重心对称 分布的条件下， 弹簧套件的刚度与弹簧套件的个数成正比。 当结晶器 的振动频率因工况不同 （如钢坯断面及钢种变化） 而有较大專围的变 化时， 可改变弹簧套件的数量， 使弹簧套件的刚度与需要的 ^动频率 匹配。 支撑振动台架的弹簧套件数量的增减可通过提升几个弹簧套件 的高度而降低其它几个弹簧套件的高度来实现。 在弹簧套件下面设置 液压缸， 通过控制系统可快速调整弹簧套件的刚度。
弹簧套件的刚度与弹簧套件的长度成反比， 将每个弹簧套件分成 若干段， 例如可等分成 n段（即每个弹簧套件由 n个相同的弹簧叠加 而成） ， 每段之间有隔板， 在结晶器和振动台将整套弹簧套件压缩使 系统处于平衡并使结晶器的高度达到振动的零位时， 用气动卡板将第 m段（从上边数）底下的隔板固定， 则弹簧套件的刚度将加大为原来 刚度的 n/m倍。
附图说明
本发明如图 1 ~图 4所示。
图 1是弹簧套件数量可调的结晶器振动装置系统图；
图 2是图 1所示振动装置的俯视图；
图 3是图 1所示振动装置的左视图；
图 4是弹簧套件长度可调的结晶器振动装置示意图。
具体实施方式
本发明的第一个实施例如图 1 ~图 3所示。 结晶器（101)坐在振动 台架（102)上。 4 个电动缸（104)相对结晶器重心对称分布。 振动台架
(102)由 8个长度和刚度相同的弹簧套件（103)支撑， 这 8个弹簧套件
(103)相对结晶器（101)和振动台架（1 02)的重心对称且均匀分布。 在 结晶器（101)和振动台架（102)的重力作用下这 8 个弹簧套件被压缩的 长度均为 δ而达到重力与弹力的平衡。 弹簧套件（103)下面设有安装 在底座（107)上的液压缸（106)， 用于改变弹簧套件的高度， 减少或增 加弹簧套件的个数。 减少支撑振动台架（102)的弹簧套件（103)的数量 就会相应的降低弹簧套件（103)的刚度。 例如， 减少相对结晶器（101) 和振动台（102)的重心对称分布的一对弹簧套件（103)， 可使剩余的弹 簧套件的刚度降低到原刚度的 3/4， 相应的弹簧套件压缩量上升到 4/3 δ。 为此， 可通过控制系统（105)控制液压缸（106)将这一对弹簧套件 (103)下降 δ +s ( s为结晶器的振程） 而将其它 3对弹簧套件提高 1/ 3 δ。 用类似的办法， 可以减少相对结晶器（101)和振动台架（102)的重 心对称分布的 1对或 3对弹簧套件（103)而使剩余的弹簧套件（103)的 刚度降低为原始刚度的 1/2或 1/4。 控制系统（105)产生频率、 偏斜率 和振幅在线可调的波形控制电动缸（104)驱动结晶器（101)振动， 并控 制液压缸（106)改变弹簧套件（103)的数量。
本发明的第二个实施例如图 4 所示。 结晶器（201)坐在振动台架 (202)上。 4个电动缸（204)相对结晶器的重心对称分布。振动台架（202) 由 4 个相同的弹簧套件（203)支撑， 弹簧套件（203)承托在底座（208) 上， 每个弹簧套件（203)由上下两个弹簧（203a)和（203b)叠加而成， 弹簧（203a)的有效长度是弹簧（203b)的有效长度的 1/3， 其间有隔板 (206)。 在结晶器（201)和振动台架（202)将弹簧套件（203)压缩 δ长度 而处于平衡状态的条件下， 启动气动卡板（207)将隔板（206)固定， 弹 簧套件（203)中只有（203a)起作用， 其刚度即提高 4 倍。 类似地， 可 将每个弹簧套件（203)分成若干段， 每段之间设隔板（206)并在对应每 块隔板（206)的压缩平衡位设气动卡板（207)， 即可对弹簧套件（203) 的刚度进行更大范围的调节。 控制系统（205)产生频率、 偏斜率和振 幅在线可调的波形控制电动缸（204)驱动结晶器（201)振动， 并控制气 动卡板（207)改变弹簧套件（203)的长度。

Claims

权 利 要 求
1、 一种连铸机结晶器振动装置， 它由承托结晶器的振动台架、 致动器、 支撑振动台架的弹簧套件、 承托致动器和弹簧套件的底座和 控制系统组成， 其特征在于： 致动器为电动缸。
2、 如权利要求 1所述的装置， 其特征在于： 弹簧套件底部设液 压紅， 用于改变支撑振动台架的弹簧套件的数量。
3、 如权利要求 1 所述的装置， 其特征在于： 弹簧套件旁设气动 卡板， 用于改变支撑振动台架的弹簧套件的长度。
4、 如权利要求 1— 3 所述的装置， 其特征在于： 控制系统产生 频率、 偏斜率和振幅在线可调的波形来控制电动缸驱动结晶器作正弦 或非正弦振动， 并控制相应的驱动系统改变弹簧套件的数量或长度。
PCT/CN2005/002030 2005-03-28 2005-11-28 Appareil d'oscillation pour moule de moulage continu WO2006102813A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
BRPI0519891-7A BRPI0519891B1 (pt) 2005-03-28 2005-11-28 Aparelho de oscilação para o molde de fundição contínua
EP05814213.4A EP1886746B1 (en) 2005-03-28 2005-11-28 Oscillating apparatus for the mold of continuous casting
KR1020097015964A KR101105917B1 (ko) 2005-03-28 2005-11-28 연속 주조용 몰드를 위한 오실레이팅 장치

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CNB2005100600497A CN1305604C (zh) 2005-03-28 2005-03-28 结晶器振动装置
CN200510060049.7 2005-03-28

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EP1886746B1 (en) 2014-11-12
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CN1305604C (zh) 2007-03-21
BRPI0519891A2 (pt) 2009-03-31

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