WO2015169267A1 - 一种振动破碎机 - Google Patents

一种振动破碎机 Download PDF

Info

Publication number
WO2015169267A1
WO2015169267A1 PCT/CN2015/083323 CN2015083323W WO2015169267A1 WO 2015169267 A1 WO2015169267 A1 WO 2015169267A1 CN 2015083323 W CN2015083323 W CN 2015083323W WO 2015169267 A1 WO2015169267 A1 WO 2015169267A1
Authority
WO
WIPO (PCT)
Prior art keywords
machine body
crushing
vibration
base
spring
Prior art date
Application number
PCT/CN2015/083323
Other languages
English (en)
French (fr)
Inventor
陈琛
Original Assignee
陈德兴
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 陈德兴 filed Critical 陈德兴
Priority to AU2015255410A priority Critical patent/AU2015255410A1/en
Publication of WO2015169267A1 publication Critical patent/WO2015169267A1/zh

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C19/00—Other disintegrating devices or methods
    • B02C19/16—Mills provided with vibrators

Definitions

  • the invention relates to a crushing device, in particular a vibration crusher.
  • the grinding action is mainly caused by the shear stress generated by the relative displacement of the material and the metal.
  • the crushing action is mainly caused by the compressive stress generated by the collision between the material and the metal.
  • the grinding and crushing action in the operation of the traditional equipment. It often happens at the same time.
  • the wear process because the metal compressive performance is much greater than the shear resistance, the most serious damage to the metal on the microscopic surface is the peeling of the metal particles caused by the shear stress of the material forming the cutting on the metal surface, so the traditional crusher has high wear-resistant material consumption.
  • the shortcomings of large maintenance are two different processes.
  • the characteristics of the vibration equipment are high-frequency vibration.
  • the high-frequency vibration of the fracture medium brings the contact time between the material and the medium to be extremely short, so that the displacement between the material and the medium can be almost neglected, that is, the cutting effect of the material on the metal medium is avoided.
  • the vibration is only impacted by the impact of the vibration, so that the metal medium can only withstand the compressive stress to maximize the performance of the metal material and avoid metal wear.
  • the vibration frequency is large, the average linear velocity of the device is much lower than that of other various crushing devices due to the small amplitude, which further greatly reduces the wear. It can be seen that vibration crushing is the fundamental method to improve the efficiency of the crusher and reduce the maintenance of the crusher.
  • the traditional vibrating mill or other vibrating crusher adopts a cylindrical design with a circular cross-sectional area and a large aspect ratio (2:1 or more).
  • the cylindrical body is selected, and the curvature of the crushing medium is measured by the curvature of the two sides of the cylinder.
  • the amplitude has a limiting effect, increasing energy consumption and reducing crushing efficiency. Due to its traditional sports characteristics, the low-energy area is too large to make the equipment large, and the output cannot exceed 100 tons per hour, which is difficult to meet the industrial production requirements.
  • the invention aims to provide a vibration crusher using different shapes of the body, and to make the material walk evenly in the cavity, so that the large The mass crushing medium moves only in the vertical direction as much as possible, colliding with the material to produce a crushing effect, and maximally avoiding the damage caused by the cutting and frictional forces on the metal.
  • the present invention adopts the following technical solutions:
  • a vibration crusher includes two sets of exciters respectively connected with a motor, a base, and a body elastically disposed on the base, the inside of the body has a cavity, and the cavity has a plurality of crushing media;
  • the vibrators are respectively connected to the two ends of the body;
  • the rotating shafts of the same group of exciters are synchronously connected with the steering by the connecting shafts, and the synchronizers are connected between the motors of the different sets of exciters, so that different sets of exciters are connected Synchronous reverse rotation;
  • the upper part of the upper part of the body is provided with an inlet, and the bottom of the body is provided with a discharge port opposite to the inlet, and the inlet is provided with a diffusion distribution of the material to be crushed to the entire space a material spreader of the cavity;
  • the cross section of the body is U-shaped, rectangular, the bottom side is shorter than the upper trapezoid, or the long axis is longitudinally distributed, and the body is located between the two sets of
  • the vibrating crusher is further designed in that the material spreader has a curved shape with a central upward bulge, and a bottom edge thereof is connected to the inner wall of the machine or is disposed at an upper portion of the inlet through a bracket, and a peripheral side thereof is disposed A number of holes or scattered blades for the material to pass through.
  • the vibration crusher is further designed in that the synchronizer comprises two intermeshing transmission teeth disposed on the base, and the two transmission teeth respectively pass through a set of sprocket chains or belt pulleys and different sets of excitation
  • the motor shaft corresponding to the vibrator is connected.
  • the vibration crusher is further designed in that the crushing medium is specifically a cylindrical alloy steel.
  • the vibration crusher is further designed such that a spring is connected between the lower portion of the body and the base, so that the body is elastically disposed on the base.
  • the vibration crusher is further designed in that the spring is a metal spring or an air spring or a rubber spring or a composite spring.
  • the invention has simple structure and low manufacturing cost, and has been proved by experiments to be suitable for medium-fine crushing sections with a discharge particle size of about 1-5 mm; the improved body shape can maximize the vibration amplitude of the crushing medium to produce maximum crushing. Capability, and is conducive to increase the filling rate and stacking height of the crushing medium, and the crushing effect is better.
  • the uniquely designed synchronizer eliminates the low-energy zone unique to traditional vibration equipment and increases production to 250-300 tons per hour or higher, much larger than conventional vibration equipment, breaking through the physical limitations of traditional vibration equipment and making it large. become possible.
  • Figure 1 is a front elevational view of an embodiment of the present invention.
  • Figure 2 is a cross-sectional view taken along line A-A of the embodiment of the present invention.
  • Figure 3 is a cross-sectional view showing the embodiment B-B of the present invention.
  • Figure 4 is a schematic diagram of a motor synchronizer.
  • Figure 5 is a schematic view of a material spreader.
  • Figure 6 is a schematic view of a conventional crusher cartridge body.
  • Fig. 7 is a schematic view showing the crusher body of the embodiment of the present invention.
  • Figure 8 is a schematic view showing the distribution of the first material in the existing vibration mill or crusher body.
  • Figure 9 is a schematic view showing the distribution of the second material in the existing vibration mill or crusher body.
  • Figure 10 is a schematic view showing the distribution of materials in the crusher of the present invention.
  • the vibrating crusher comprises two sets of exciter 3 respectively connected with the motor 1, a base 7 and a body 9 elastically disposed on the base, the inside of the body has a cavity, and the cavity has a plurality of crushing media 10;
  • the two sets of exciters 3 are respectively connected to the two ends of the body;
  • the rotating shafts of the same group of exciters 3 are synchronously connected with the steering by the connecting shafts, and the synchronizers 2 are connected between the motors corresponding to the different sets of exciters, so that
  • the vibrators of different groups are synchronously reversely rotated;
  • the upper center of the body is provided with an inlet port 6, and the bottom of the body is provided with a discharge port 4 opposite to the inlet port 6, and the inlet port is provided with Dispersing the material to be crushed to the material spreader 5 of the entire cavity;
  • the cross section of the body is U-shaped, correspondingly the cross section may also be rectangular, the bottom side is shorter than the upper trapezoid, or
  • a spring 8 is coupled between the lower portion of the body and the base such that the body is elastically disposed on the base.
  • the spring may be a metal spring or an air spring or a rubber spring.
  • the material spreader has a curved shape with a central upward bulge, and a bottom edge thereof is connected to the inner wall of the machine or disposed above the inlet through a bracket, and a plurality of holes for material passage are arranged on the circumferential side thereof. Or spread the leaves.
  • the synchronizer includes two intermeshing transmission teeth 12 disposed on the base, and the two transmission teeth respectively correspond to different sets of exciters through a set of sprocket chains or belt pulleys 13 respectively. Motor shaft drive connection.
  • the crushing medium is specifically a cylindrical alloy steel.
  • FIG. 6 is a schematic view of a conventional crusher bin
  • FIG. 7 is a schematic view of a crusher bin body according to an embodiment of the present invention, and a comparison of the stacking heights of the crushed media in the two figures can be seen by comparison.
  • FIG. 8 and FIG. 9 are schematic diagrams showing the distribution of materials in the vibrating mill or crusher body;
  • FIG. 10 is a schematic view showing the distribution of materials in the crusher of the present embodiment, wherein the mark 11 is a material distribution area, and the comparison can be seen by comparing the two figures. Comparison of new and traditional barrel material distribution.
  • the traditional vibrating mill or other vibrating dynamic crusher adopts a cylindrical design with a circular cross-sectional area as shown in Fig. 6.
  • the aspect ratio is about 3:1, and the aspect ratio is often larger (2:1 or more), regardless of the side.
  • the crusher body can obtain sufficient crushing capacity by greatly increasing the stacking height of the crushing medium.
  • the length of the body can be greatly shortened, and the long diameter (or length to width) ratio can be controlled at 2 From 1 or less, it can be seen from Figure 10 that the shorter body length allows the material to be evenly distributed after entering, making full use of all the space and crushing medium in the bin, further improving the efficiency of the crusher, and the shorter body makes the material travel path Greatly shortened and significantly improved crusher efficiency.
  • the use of the synchronizer eliminates the low-energy zone of the traditional vibration equipment, making it possible to enlarge the equipment. At present, the prototype production can reach 250-300 tons/hour. The experiment is compared with the traditional design.
  • the length of the crushing bin is 4 meters and the diameter is 1.3 meters.
  • the filling rate of medium is 40%, that is, the stacking height is 520mm, the processing capacity is 60 tons/hour, and the installed capacity is 220KW.
  • the length of the crushing bin of this new design test model is 2 meters, and the diameter of the bottom of the warehouse is 1.3 meters (that is, the warehouse width is 1.3 meters).
  • the crushing medium has a stack height of 1.3 meters. (The filling rate concept has no meaning for this design), the processing capacity can reach 120-150 tons / hour, and the installed capacity is 180KW.
  • the data proves that the crushing efficiency of the design is doubled, the weight is reduced by 3-4 tons, and the energy saving is about 15%-20%.
  • the width dimension of the conventional crusher ie, the diameter of the body
  • the barrel-shaped body of the conventional vibrating mill or crusher is limited by the shape
  • the stacking height of the crushing medium is limited by the diameter of the body.
  • the filling rate of the conventional vibrating mill or crusher is generally controlled to be less than 50%, and the conventional vibrating equipment cannot be developed to a large scale due to the existence of the low-energy region, and the output at the time of the trough is very low;
  • the body is free from the limitation of the diameter of the body, and can be conveniently Increasing the stacking height of the crushing medium, the stacking height shown in Fig. 8 can be easily doubled, the crushing efficiency is increased by about 1.5-2 times, and the pile wall has no vibration resistance regardless of the height of the crushing medium, and the filling rate of the crushing medium is basically no limit.
  • the improved body shape can maximize the vibration amplitude of the crushing medium to produce the maximum crushing capacity, and is beneficial to increase the stacking height of the crushing medium, prolong the time of the material passing through the crushing medium, and the stacking height of the crushing medium directly affects the crushing efficiency.

Landscapes

  • Engineering & Computer Science (AREA)
  • Food Science & Technology (AREA)
  • Crushing And Grinding (AREA)
  • Disintegrating Or Milling (AREA)

Abstract

一种振动破碎机，包括两组激振器（3）、底座（7）和弹性设置于底座（7）上的机体（9）、机体（9）内容有破碎介质；两组激振器（3）分别连接机体（9）两端；同组激振器（3）的转轴通过连接轴同步连接，不同组的激振器（3）对应的电机（1）之间连接有同步器（2）；机体（9）的上部中央设置有入料口（6），机体（9）的底部设置有与入料口（6）相对的出料口（4），入料口（6）内设置有物料散布器（5）；机体（9）的横截面为U型、矩形、梯形或者椭圆形，机体（9）位于两组激振器（3）之间的长度与机体（9）横截面的最大宽度之比小于等于2：1。所述振动破碎机适用于出料粒度要求在1-5毫米左右的中细碎段，机体（9）形状可以形成大幅的振动幅度，便于增大破碎介质填充率，同步器（2）可以完全消除振动设备的低能区，以产生最大的破碎能力，破碎效率更高。

Description

一种振动破碎机 技术领域
本发明涉及一种破碎设备，尤其是一种振动破碎机。
背景技术
在矿山、水泥、电力、化工等行业，传统中细碎解决方案如辊压机、立轴破、圆锥破、锤破机、球磨机等有着诸多不足和制约，如能耗高、磨损大，维修量大，效率不足等。在水泥行业中，普遍情况下球磨机仍被兼作为破碎机使用，致使生产效率低，能耗高、衬板消耗大，维修量大。随着球磨机多磨少破理论和的磨前预粉碎工艺的出现，球磨机生产效率被大大提高，目前主要的球磨机磨前预粉碎设备如高压辊压机，有着能耗高、投入大、磨损量大等缺点，制约了预粉碎工艺的普及。在矿山行业中普遍使用圆锥、锤破、立轴甚至球磨机作为中细碎设备，磨损大、能耗高、维修量大，造成高昂的生产成本。可以看出在世界范围内，中细碎解决方案在各行各业都急需一种优秀的设备带来革命性的突破。
破碎和研磨是两个不同的过程，研磨作用主要产生于物料与金属发生相对位移产生的剪切应力，而破碎作用主要产生于物料与金属碰撞产生的压应力，传统设备运行中研磨和破碎作用往往是同时发生。磨损过程中，因为金属抗压性能远大于抗剪切性能，微观上对金属伤害最大的是物料对金属表面形成切削的剪切应力造成金属微粒的剥落，所以传统破碎机有耐磨材料消耗大，维修量大的缺点。
振动设备的特性是高频振动，破碎介质高频率振动带来的是物料与介质接触时间极短，使物料和介质之间的位移可以几乎忽略不计，也就是避免了物料对金属介质的切削作用，而仅通过振动带来冲击进行破碎，使金属介质最大可能的只承受压应力，来最大限度的发挥金属材料性能和避免金属磨损。虽然振动频率大，但由于振幅不大，所以设备的平均线速度远低于其他各种破碎设备，进一步极大的减小磨损。可以看出振动破碎是提高破碎机效率和减少破碎机维修量的根本方法。
传统振动磨或其他震动破碎机机体采用筒形设计其截面积为圆形，长径比往往较大(2：1以上)，选用圆筒形机体，圆筒两侧的弧度对破碎介质的振动幅度产生限制作用，增加能耗、降低破碎效率。且由于其传统的运动特性，低能区过大，无法使设备大型化，产量无法超过每小时100吨，难以满足工业生产要求。
发明内容
本发明旨在提供一种采用不同形状机体的振动破碎机，并使物料在腔体内均匀散步，使大 质量破碎介质尽可能只在垂直方向发生运动，与物料进行碰撞产生破碎作用，最大限度地避免了切削和摩擦作用力对金属造成的破坏。为实现上述技术目的，本发明采用以下技术方案：
一种振动破碎机，包括两组分别连接有电机的激振器、底座以及弹性设置于底座上的机体、所述机体内部具有空腔，且该空腔内容有若干破碎介质；所述两组激振器分别连接所述机体的两端；同组激振器的转轴通过连接轴同步同转向连接，不同组的激振器对应的电机之间连接有同步器，使得不同组的激振器同步反转向转动；所述机体的上部中央设置有入料口，机体的底部设置有与所述入料口相对的出料口，所述入料口内设置有将待破碎物料扩散分布至整个空腔的物料散布器；所述机体的横截面为U型、矩形、底边短于上边的梯形、或者长轴纵向分布的椭圆形，所述机体位于两组激振器之间的长度与机体横截面的最大宽度之比小于2：1。
所述的振动破碎机，其进一步设计在于，所述物料散布器呈中部向上隆起的曲面状，其底部边缘与所述机体内壁连接或通过一支架设置在入料口上部，其周侧面设置有若干供物料通过的孔洞或散布叶片。
所述的振动破碎机，其进一步设计在于，所述同步器包括设置在底座上的两个互相啮合的传动齿，并且两个传动齿分别通过一组链轮链条或皮带皮带轮与不同组的激振器对应的电机转轴传动连接。
所述的振动破碎机，其进一步设计在于，所述破碎介质具体为圆柱状的合金钢。
所述的振动破碎机，其进一步设计在于，所述机体的下部与底座之间连接有弹簧，从而使得所述机体弹性设置于底座上。
所述的振动破碎机，其进一步设计在于，所述弹簧为金属弹簧或空气弹簧或者为橡胶弹簧或者为复合弹簧。
本发明结构简单，制造成本低，经过实验证明适用于出料粒度要求在1-5毫米左右的中细碎破碎段；改进的机体形状可以最大限度地发挥破碎介质的振动幅度，以产生最大的破碎能力，且有利于增加破碎介质的填充率和堆积高度，破碎效果更好。独特设计的同步器由于消除了传统振动设备特有的低能区使产量可提升至每小时250吨-300吨或更高，远大于普通传统振动设备，突破了传统振动设备的物理限制，使大型化成为可能。
附图说明
本发明的上述和/或附加的方面和优点从结合下面附图对实施例的描述中将变得明显和容易理解，其中：
图1是本发明实施例的主视图。
图2是本发明实施例A-A剖视图。
图3是本发明实施例B-B剖视图。
图4是电机同步器示意图。
图5是物料散布器示意图。
图6是现有破碎机仓体示意图。
图7是本发明实施例破碎机仓体示意图。
图8是现有振动磨或破碎机机体内第一种物料分布示意图。
图9是现有振动磨或破碎机机体内第二种物料分布示意图。
图10是本发明破碎机体内物料分布示意图。
图中：1、电机；2、同步器；3、激振器；4、出料口；5、物料散布器；6、入料口；7、底座；8、弹簧；9、机体；10、破碎介质；11、物料分布区域。
具体实施方式
下面详细描述本发明的实施例，所述实施例的示例在附图中示出，其中自始至终相同或类似的标号表示相同或类似的元件或具有相同或类似功能的元件。下面通过参考附图描述的实施例是示例性的，仅用于解释本发明，而不能理解为对本发明的限制。
在本发明的描述中，除非另有规定和限定，需要说明的是，术语“安装”、“相连”、“连接”应做广义理解，例如，可以是机械连接或电连接，也可以是两个元件内部的连通，可以是直接相连，也可以通过中间媒介间接相连。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语的具体含义。
下面参照图1-图3描述本发明实施例的振动破碎机。
该振动破碎机包括两组分别连接有电机1的激振器3、底座7以及弹性设置于底座上的机体9、所述机体内部具有空腔，且该空腔内容有若干破碎介质10；所述两组激振器3分别连接所述机体的两端；同组激振器3的转轴通过连接轴同步同转向连接，不同组的激振器对应的电机之间连接有同步器2，使得不同组的激振器同步反转向转动；所述机体的上部中央设置有入料口6，机体的底部设置有与所述入料口6相对的出料口4，所述入料口内设置有将待破碎物料扩散分布至整个空腔的物料散布器5；所述机体的横截面为U型，相应地该横截面也可以为矩形、底边短于上边的梯形、或者长轴纵向分布的椭圆形，所述机体位于两组激振器之间的长度与机体横截面的最大宽度之比小于2：1。
所述机体的下部与底座之间连接有弹簧8，从而使得所述机体弹性设置于底座上。所述弹簧可以是金属弹簧或空气弹簧或者是橡胶弹簧。
如图5所示，所述物料散布器呈中部向上隆起的曲面状，其底部边缘与所述机体内壁连接或通过一支架布置在入料口上方，其周侧面设置有若干供物料通过的孔洞或散布叶片。
如图4所示，所述同步器包括设置在底座上的两个互相啮合的传动齿12，并且两个传动齿分别通过一组链轮链条或皮带皮带轮13与不同组的激振器对应的电机转轴传动连接。
具体地，所述破碎介质具体为圆柱状的合金钢。
作为对比，图6是现有破碎机仓体示意图；图7是本发明实施例破碎机仓体示意图，通过对比可以看到两图中破碎介质堆积高度的对比。
图8、图9是现有振动磨或破碎机机体内物料分布示意图；图10是本实施例破碎机体内物料分布示意图，图中标记11为物料分布区域，通过两图的对比可以看到本新型与传统筒身物料分布的对比情况。
传统振动磨或其他振动动破碎机机体采用筒形设计其截面积为圆形如图6，其长径比在3：1左右，长径比往往较大(2：1以上)，不管是一边进料一边出料，还是中间进料两端出料，由于无法获得足够的破碎介质堆积，破碎效率低下，所以必须大大延长机体，增长破碎研磨路径，延长物料在破碎介质中停留的时间，以获得合格的出料粒度，这个过程大大降低了工作效率，且从图9可以看出，物料从入料口到出料口是梯度分布，破碎介质有很大一部分处于无物料工作状态，仓内50％左右的空间得不到有效利用，这种浪费的状态增加了破碎介质损耗、电力消耗，所以传统震动磨或破碎机都有产量和效率低下的缺点。
而改进后破碎机机体通过大大增加了破碎介质的堆积高度获得了充分的破碎能力，在保证出料粒度的情况下，可以大大缩短机体长度，使长径(或长宽)比可控制在2：1或以内，从图10可以看出较短的机体长度使物料进入后可以均匀分布，充分利用仓内所有空间和破碎介质，进一步提高破碎机使用效率，且较短的机体使物料行走路径大大缩短，显著提升破碎机效率。且同步器的使用消除了传统振动设备的低能区，使设备大型化成为可能，目前样机产量已可达到250-300吨/小时实验对比参照传统设计，破碎仓长度4米，直径1.3米，破碎介质填充率40％，即堆积高度520mm，处理能力为60吨/小时，装机容量为220KW；本新型设计试验机型破碎仓长度为2米，仓底直径1.3米(即仓宽1.3米)，破碎介质堆积高度1.3米，(填充率概念对于本设计已没有意义)，处理能力可达到120-150吨/小时，装机容量为180KW。数据证明，本设计破碎效率提高一倍，重量减少3-4吨，节能15％-20％左右。
传统破碎机的宽度尺寸(即机体直径)往往受到限制而无法随意扩大。从图7可以看出，传统振动磨或破碎机的圆桶形机体受形状所限，破碎介质的堆积高度受机体直径限制，当堆积高度超过40％时，仓壁开始阻碍振动运动降低破碎效率，这种现象随着破碎介质填充率的增大而增大，若填充率超过80％则机器几乎失去破碎能力。所以传统振动磨或破碎机填充率一般控制在50％以下，且由于低能区的存在使传统振动设备无法向大型化发展，台时产量很低；本发明中机体摆脱了机体直径限制，可以方便增加破碎介质堆积高度，图8中所示堆积高度可轻松增加一倍，破碎效率增加1.5-2倍左右，且无论破碎介质堆积高度多少，仓壁无任何振动阻力产生，对破碎介质填充率基本没有限制。改进的机体形状可以最大限度地发挥破碎介质的振动幅度，以产生最大的破碎能力，且有利于增加破碎介质的堆积高度，延长物料通过破碎介质的时间，破碎介质的堆积高度直接影响破碎效率。
在本说明书的描述中，参考术语“一个实施例”、“示例”、或“一些示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者特点包含于本发明的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不一定指的是相同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任何的一个或多个实施例或示例中以合适的方式结合。
尽管已经示出和描述了本发明的实施例，本领域的普通技术人员可以理解：在不脱离本发明的原理和宗旨的情况下可以对这些实施例进行多种变化、修改、替换和变型，本发明的范围由权利要求及其等同物限定。

Claims (6)

  1. 一种振动破碎机，其特征在于：包括两组分别连接有电机的激振器、底座以及弹性设置于底座上的机体、所述机体内部具有空腔，且该空腔内容有若干破碎介质；所述两组激振器分别连接所述机体的两端；同组激振器的转轴通过连接轴同步同转向连接，不同组的激振器对应的电机之间连接有同步器，使得不同组的激振器同步反转向转动；所述机体的上部中央设置有入料口，机体的底部设置有与所述入料口相对的出料口，所述入料口内设置有将待破碎物料扩散分布至整个空腔的物料散布器；所述机体的横截面为U型、矩形、底边短于上边的梯形、或者长轴纵向分布的椭圆形，所述机体位于两组激振器之间的长度与机体横截面的最大宽度之比小于等于2：1。
  2. 根据权利要求1所述的振动破碎机，其特征在于，，所述物料散布器呈中部向上隆起的曲面状，其底部边缘与所述机体内壁连接或通过一支架放置在入料口上部，其周侧面设置有若干供物料通过的孔洞或发散状的散布叶片。
  3. 根据权利要求1所述的振动破碎机，其特征在于，所述同步器包括设置在底座上的两个互相啮合的传动齿，并且两个传动齿分别通过一组链轮链条或皮带皮带轮与不同组的激振器对应的电机转轴传动连接。
  4. 根据权利要求1所述的振动破碎机，其特征在于，所述破碎介质具体为圆柱状的合金钢。
  5. 根据权利要求1所述的振动破碎机，其特征在于，所述机体的下部与底座之间连接有弹簧，从而使得所述机体弹性设置于底座上。
  6. 根据权利要求5所述的振动破碎机，其特征在于，所述弹簧为金属弹簧或空气弹簧或者为橡胶弹簧或者为复合弹簧。
PCT/CN2015/083323 2014-05-05 2015-07-03 一种振动破碎机 WO2015169267A1 (zh)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2015255410A AU2015255410A1 (en) 2014-05-05 2015-07-03 Vibrating crusher

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201420223827.4U CN204017965U (zh) 2014-05-05 2014-05-05 一种振动破碎机
CN201420223827.4 2014-05-05

Publications (1)

Publication Number Publication Date
WO2015169267A1 true WO2015169267A1 (zh) 2015-11-12

Family

ID=52057878

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2015/083323 WO2015169267A1 (zh) 2014-05-05 2015-07-03 一种振动破碎机

Country Status (3)

Country Link
CN (1) CN204017965U (zh)
AU (2) AU2015255410A1 (zh)
WO (1) WO2015169267A1 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117753533A (zh) * 2024-02-21 2024-03-26 河南广洋生物科技有限公司 一种肝素钠生产用粉碎设备

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN204017965U (zh) * 2014-05-05 2014-12-17 徐州乔鑫矿山机械制造有限公司 一种振动破碎机

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2224026Y (zh) * 1995-06-18 1996-04-10 洛阳矿山机械工程设计研究院 一种新型振动磨机
US5611495A (en) * 1995-11-06 1997-03-18 Williams; Robert M. Rotary shredding apparatus with anti-jam means
KR20100108960A (ko) * 2009-03-31 2010-10-08 수성산업(주) 건설 폐기물 진동 마쇄기
CN202683319U (zh) * 2012-08-03 2013-01-23 常州市众华建材科技有限公司 砂石破碎装置
CN203140079U (zh) * 2013-02-25 2013-08-21 北京合鼎巨德机械设备有限责任公司 双轴四驱动振动破碎机
CN204017965U (zh) * 2014-05-05 2014-12-17 徐州乔鑫矿山机械制造有限公司 一种振动破碎机

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2224026Y (zh) * 1995-06-18 1996-04-10 洛阳矿山机械工程设计研究院 一种新型振动磨机
US5611495A (en) * 1995-11-06 1997-03-18 Williams; Robert M. Rotary shredding apparatus with anti-jam means
KR20100108960A (ko) * 2009-03-31 2010-10-08 수성산업(주) 건설 폐기물 진동 마쇄기
CN202683319U (zh) * 2012-08-03 2013-01-23 常州市众华建材科技有限公司 砂石破碎装置
CN203140079U (zh) * 2013-02-25 2013-08-21 北京合鼎巨德机械设备有限责任公司 双轴四驱动振动破碎机
CN204017965U (zh) * 2014-05-05 2014-12-17 徐州乔鑫矿山机械制造有限公司 一种振动破碎机

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117753533A (zh) * 2024-02-21 2024-03-26 河南广洋生物科技有限公司 一种肝素钠生产用粉碎设备
CN117753533B (zh) * 2024-02-21 2024-05-10 河南广洋生物科技有限公司 一种肝素钠生产用粉碎设备

Also Published As

Publication number Publication date
AU2015255410A1 (en) 2016-12-22
CN204017965U (zh) 2014-12-17
AU2015101883A4 (en) 2017-05-04

Similar Documents

Publication Publication Date Title
CN101596474B (zh) 剪式锤片粉碎机
CN101954303B (zh) 双转子复合制砂机
CN106391182A (zh) 一种矿石粉碎装置
CN213761953U (zh) 一种倾斜偏心距偏心套的多缸圆锥破碎机
WO1998020977A1 (fr) Broyeur a marteaux
WO2015169267A1 (zh) 一种振动破碎机
CN207756227U (zh) 一种辊盘式碎磨机
CN102580814B (zh) 一种筛分破碎一体机
CN106000544A (zh) 连续进行冲击破碎和打击破碎的破碎方法
CN208302897U (zh) 一种化工用的粉碎机
CN212396822U (zh) 一种层压破碎腔
CN103100464A (zh) 节能环保型双转子破碎机
CN2516252Y (zh) 振动破碎机
CN108097387A (zh) 一种辊盘式碎磨机
CN101607222A (zh) 锤片粉碎机
CN104525308A (zh) 一种漂浮式的圆锥破碎机
CN109499657A (zh) 一种破碎机
CN201855715U (zh) 双转子复合制砂机
CN202096971U (zh) 一种双腔双动颚振动颚式破碎机
CN108325593B (zh) 一种圆锥破碎机用衬板结构
CN206965849U (zh) 一种硅粉粉碎机
CN206965831U (zh) 一种硅粉粉碎机
CN205570440U (zh) 一种磨腔内部研磨的立式振动磨机
CN104209173A (zh) 一种双质体近共振破(磨）机
CN201500548U (zh) 剪式锤片粉碎机

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 15789423

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 2015255410

Country of ref document: AU

Date of ref document: 20150703

Kind code of ref document: A

32PN Ep: public notification in the ep bulletin as address of the adressee cannot be established

Free format text: NOTING OF LOSS OF RIGHTS PURSUANT TO RULE 112(1) EPC (EPO FORM 1205A DATED 20/03/2017)

122 Ep: pct application non-entry in european phase

Ref document number: 15789423

Country of ref document: EP

Kind code of ref document: A1