• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Grinding machine (1) comprising: - a frame (2), - a tank (3), - a cone (5) placed inside the tank (3), the machine (1) further comprising a device (7) vibrating the vessel (3) relative to the frame (2); the machine (1) being characterized in that the device (7) for vibrating the tank (3) comprises at least two vibrators (8a, 8b, 8c, 8d) mounted on the frame (4), each vibrator ( 8a, 8b, 8c, 8d) being rotated about a longitudinal axis of the frame by a motor (10), each motor (10) controlling independently of each other the vibrator with which it is associated.
    公开号:FR3063234A1
    申请号:FR1751554
    申请日:2017-02-27
    公开日:2018-08-31
    发明作者:Jérôme PORTAL
    申请人:Fives FCB SA；Fives Solios SA；
    IPC主号:
    专利说明:

    063 234
    51554 ® FRENCH REPUBLIC
    NATIONAL INSTITUTE OF INDUSTRIAL PROPERTY © Publication number:
    (to be used only for reproduction orders)
    ©) National registration number
    COURBEVOIE © Int Cl 8 : B 02 C 2/04 (2017.01)
    PATENT INVENTION APPLICATION
    A1
    ©) Date of filing: 27.02.17. (© Applicant (s): FIVES SOLIOS Joint-stock company (© Priority: simplified - FR and FIVES FCB Société anonyme - FR. (© Inventor (s): PORTAL Jérôme. ©) Date of public availability of the request: 31.08.18 Bulletin 18/35. ©) List of documents cited in the report preliminary research: Refer to end of present booklet (© References to other national documents (® Holder (s): FIVES SOLIOS Joint stock company related: FIVES FCB Public limited company. ©) Extension request (s): © Agent (s): CABINET PLASSERAUD.
    ITxU CONE CRUSHING MACHINE AND CRUSHING METHOD USING SUCH A MACHINE.
    FR 3 063 234 - A1
    Grinding machine (1) comprising:
    - a frame (2),
    - a tank (3),
    - a cone (5) placed inside the tank (3), the machine (1) further comprising a device (7) for vibrating the tank (3) relative to the frame (2);
    the machine (1) being characterized in that the device (7) for vibrating the tank (3) comprises at least two vibrators (8a, 8b, 8c, 8d) mounted on the chassis (4), each vibrator ( 8a, 8b, 8c, 8d) being rotated about a longitudinal axis of the chassis by a motor (10), each motor (10) controlling the vibrator with which it is associated independently of each other.

    i
    Cone grinding machine and grinding method using such a machine
    The invention relates to the field of fragmentation machines, also called machines for grinding and / or crushing material, such as ores. More specifically, the invention relates to the field of grinding machines in which the material is ground between a cone and a frustoconical tank without bottom by setting the tank in motion relative to the cone.
    The operating principle of such a machine is described in the document FR. 2,687,080. The machine comprises a conical head, also called the cone, housed in a tank, a space being defined between the head and the tank. The conical head is in a fixed position relative to a frame, while the tank is positioned on a bearing structure, mounted floating relative to the frame. The supporting structure can be moved in a horizontal plane with respect to the frame by means of vibrators which are set in motion by suitable means. Thus, the material poured into the space between the cone and the tank is crushed by setting in motion in circular translation in the horizontal plane of the tank relative to the cone. The ground material then falls into a conduit located under the cone.
    Document EP 0 642 387 proposes two improvements. On the one hand, the conical head is mounted free to rotate about a vertical axis relative to the frame, in order to limit the phenomena of wear due to movements in a tangential plane between the tank and the head. On the other hand, the height of the cone relative to the tank can be adjusted, so as to adjust the minimum width of the space between the head and the tank, and therefore the maximum size of the ground products. In fact, by measuring the speed of rotation of the head, and knowing the maximum width of the grinding space, it is deduced therefrom the thickness of the layer of material, and therefore the maximum size of the ground products. By comparing this thickness with a set value, it is possible to adjust the machine parameters.
    Document EP 0 833 692 describes a system for vibrating the tank making it possible to limit vertical vibrations. To this end, several vertical vibrator shafts are mounted on a chassis supporting the tank, each shaft carrying a vibrator composed of two weights arranged on either side of a base of the chassis defining a horizontal plane. Thus, when the vibrators are rotated, the forces they exert are located in the horizontal plane of the base.
    In the examples presented above, the vibrating system comprises vibrator shafts, generally four, arranged in a square around the tank and the conical head. A first vibrator shaft is coupled to a motor, and the other shafts are driven from the first shaft by a set of pulleys and belt. The rotation of the vibrators must be synchronized to avoid the appearance of parasitic moments.
    When the machine starts, the vibrator shafts are rotated, their speed gradually increasing to a nominal speed. The material spilled between the head and the tank is then crushed. However, without special precautions, the vibrations of the tank pass through different frequencies, some of which may correspond to the resonant frequencies of the machine, which is detrimental to the machine.
    It is then known to set up a phase shift device for adjusting the angular offset of a group of vibrators with respect to the other group, in order to modify the amplitude of the result of the forces generated by the vibrators. Thus, at start-up, two vibrators are in phase opposition with respect to the other two vibrators so that the result of the forces generated by the vibrators is zero: the tank is stationary relative to the head. The phase opposition is maintained until the nominal speed is reached. Then, all the vibrators are put in phase, so that the result of the forces is maximum, and the tank is set in motion relative to the head to grind the material.
    For example, as presented in document EP 0 833 692, the amplitude can be modified by means of one or two rotary actuators making it possible to modify the phase shift of the vibrators of one group relative to those of the other group.
    Thus, the phase shift and the phasing of the vibrators relative to each other are based in particular on the transmission by the set of pulleys and belts, making the adjustment imprecise and unreliable. Indeed, the wear of the pulleys and belts as well as the tension in the belts must be monitored in order to maintain a fine adjustment. The belt can also "jump" on the notches of the pulleys, especially since the notches are subject to wear, shifting the angular position of the vibrators relative to each other.
    Furthermore, the set of pulleys and belts increases the number of parts on the machine, making it more complex, and making maintenance delicate. In particular, the hydraulic cylinders for pivoting the shafts of the vibrators require a robust seal, both vis-à-vis the pivoting of the shafts, but also vis-à-vis the vibrations of the machine. Many leakage problems can arise.
    In addition, during the operation of the machine, the hydraulic cylinders tend to pivot, in particular because of leaks which can be accentuated under the effect of the vibrations of the machine, so that their position becomes random. Hydraulic cylinders cannot reliably hold an intermediate position. Thus, the vibrators generally work on an all or nothing principle: either the vibrators are phase shifted, and the resultant of the forces is zero, or the vibrators are in phase, and the resultant is maximum. An intermediate position can only be held for a short period, exceptionally.
    However, it may be necessary to adapt the value of the maximum resultant as being a general process setting. As this value cannot be permanently adapted by maintaining the cylinders in an intermediate position, mechanical stops are manually installed in the cylinders to define a position giving the maximum result. The installation of the stops is tedious, and involves stopping the grinding machine during the installation operations. However, since the grinding machine is generally integrated into a more general process for treating the material, stopping the machine has an impact on the overall process.
    There is therefore a need for a new grinding and / or crushing machine notably overcoming the aforementioned drawbacks.
    To this end, according to a first aspect, the invention provides a grinding machine comprising:
    a frame, a tank forming an internal grinding track. The tank is mounted on a frame movable in translation at least in a transverse plane relative to the frame, a cone forming an external grinding track and placed inside the tank.
    The machine further comprises a device for vibrating the tank relative to the frame in a transverse plane, so that material is crushed between the internal track and the external grinding track by the relative movement of the tank with respect to to the cone.
    The device for vibrating the tank comprises at least two vibrators mounted on the chassis, each vibrator being rotated about a longitudinal axis of the chassis by a motor. Each motor independently controls the vibrator with which it is associated. The device for vibrating the tank further comprises a motor control system and a system for measuring the relative phase shift angle between the vibrators, so that the vibration device can take at least three positions:
    a so-called zero position, in which the phase shift angle between the vibrators is such that the vibrations of the tank are of minimum amplitude;
    a so-called maximum position, in which the phase shift angle between the vibrators is zero, so that the vibrations of the tank are of maximum amplitude;
    at least one so-called intermediate position, in which the phase angle between the vibrators is such that the vibrations of the tank are of intermediate amplitude between the maximum amplitude and the minimum amplitude, the control system being able to pass the vibration device from one position to another while maintaining the rotation of the vibrators.
    The vibrations for grinding the material can thus be adapted online, without stopping the machine, depending on the grinding power required to grind the material.
    According to one embodiment, each motor is mounted on the frame and comprises a motor shaft extending longitudinally. Each vibrator is mounted on a vibrator shaft, a connection between the motor shaft and the corresponding vibrator shaft comprising a rigid coupling in the transverse plane, so that the vibrator shaft is rotated by the motor shaft and a flexible coupling in the longitudinal direction, so that the vibrator shaft can move in the longitudinal direction relative to the motor shaft over a determined maximum stroke.
    The flexible connection between the motor shaft and the vibrator shaft helps preserve the machine while ensuring efficient transmission.
    For example, the connection between the drive shaft and the vibrator shaft may comprise a connecting rod comprising a constant velocity transmission joint between the driving shaft and the vibrating shaft, and may also comprise an intermediate part between the connecting rod and the 'engine shaft. The intermediate piece may comprise a strip of elastomeric material fixed astride two parts of a rigid body of the intermediate piece. More specifically, a first part can be fixed to one end of the motor shaft and a second part can be fixed to one end of the connecting rod. One of the first part and the second part may further comprise a lug projecting longitudinally cooperating with a longitudinal drilling of the other of the first part and the second part to guide the movement of the vibrator shaft according to the longitudinal direction relative to the motor shaft.
    This embodiment is inexpensive to set up and ensures transmission between the motor shaft and the vibrator shaft effectively.
    According to one embodiment, each motor comprises a motor mode, in which the motor consumes energy to rotate the associated vibrator, and a generator mode, in which the motor generates energy by braking the associated vibrator. For this purpose, for example, the engine control system may include a device for recovering and storing at least part of the energy generated by each engine in generator mode. As a variant or in combination, the engine control system can comprise a device for dissipating at least part of the energy generated by each engine in generator mode.
    The energy recovered thus makes it possible to reduce the operating costs of the machine. The recovered energy can thus be used either to control the machine or to power other devices.
    According to a second aspect, a grinding process is proposed using a grinding machine as presented above. The process then includes the following steps:
    placing the vibration setting device in the zero position; the determination by the control system of a grinding force as a function of at least one grinding parameter;
    increasing the speed of rotation of the vibrators to a value determined by the grinding force;
    placing the vibrators in relative position with a phase angle between the vibrators determined by the grinding force;
    the supply of material to be ground to the machine between the two grinding tracks.
    The method further comprises, the rotation of the vibrators being maintained:
    the detection of a modification of at least one grinding parameter; determining a new grinding effort;
    the modification of at least the phase shift angle between the vibrators as a function of the new force.
    According to a particular embodiment, a modified grinding parameter can be the particle size of the ground material leaving the grinding machine. Thus, by adjusting the grinding effort in line, the particle size characteristics of the material leaving the machine can be adapted as required.
    As a variant or in combination, a modified grinding parameter can be the particle size of the material feeding the grinding machine. The modification of the particle size of the material entering the grinding machine is commonly encountered. It is therefore particularly advantageous economically to adapt the grinding force to the particle size of the material to be ground.
    According to one embodiment, the grinding machine further comprises a sensor of the tank vibrations in the longitudinal direction, that is to say the vertical vibrations. The detection of a modification of the grinding parameter can then include:
    the determination of a reference spectrum of the longitudinal vibrations of the vessel, the comparison between the reference spectrum and a spectrum measured by the vibration sensor, the quantification of a difference between the reference spectrum and the spectrum measured if the difference quantified value exceeds a threshold value, the confirmation of the detection of a modification of at least one grinding parameter of the material feeding the grinding machine.
    The monitoring of vertical vibrations makes it possible in particular to monitor a failure of a machine, and to anticipate it to avoid breakage which would require a long stop of the machine for repair.
    According to one embodiment, the setting into the start position comprises the following steps:
    the vibrators being stopped, the recording of an initial position of the vibrators in which the phase difference between the vibrators corresponds to the zero position of the vibrating device;
    moving the vibrators;
    the rotation of the vibrators until the vibrators are in their initial position.
    This procedure for recording an initial position makes it possible to start the machine more quickly and automatically. For example, when a fault has required stopping the machine, the machine can be restarted from the stored initial position automatically.
    According to one embodiment, when a material supply cut-off occurs, the device for vibrating the tank is set to the zero position, in order to preserve the machine. As each vibrator is controlled independently of the others by a motor, the zero position is achieved very quickly, preserving the integrity of the machine.
    According to one embodiment, when an electrical supply cut to the motors occurs, the method can comprise the following steps:
    the placing in generator mode of at least one engine, the recovery and storage of at least part of the braking energy by the recovery and storage device;
    setting the tank vibration device to zero position using at least part of the energy recovered in the recovery and storage device to phase the vibrators, maintaining the zero position until stopped of the rotation of all the vibrators.
    Other effects and advantages will appear in the light of the description of embodiments of the invention accompanied by the figures in which:
    Figure 1 is a top sectional view of a grinding machine according to an embodiment of the invention in which four vibrators are controlled by four independent motors;
    Figure 2 is a view of the machine of Figure 1 along the section line II-II;
    Figure 3 is a schematic representation of an embodiment of the machine control of Figure 1;
    FIG. 4 is a view of detail IV of FIG. 2.
    In FIGS. 1 and 2, a machine 1 for vibration grinding is shown. The machine 1 includes in particular a frame 2, intended to rest on the ground.
    The machine 1 further comprises a tank 3, the internal surface of which forms an internal grinding track 3a. The tank 3 is mounted on a chassis 4 movable in translation relative to the frame 2 at least in a transverse plane, which in practice is substantially the horizontal plane. To this end, the chassis 4 is mounted on the frame 2 by means of elastic studs 4a, elastically deforming both transversely and longitudinally to limit the transmission of vibrations to the frame 2. A cone 5, the outer surface of which is shape substantially complementary to that of the inner surface of the tank 3 and which forms an external grinding track 5a is placed inside the tank 3. Preferably, the cone 5 is mounted on a shaft 6 extending along a longitudinal axis A, which in practice is substantially vertical, and supported by a secondary frame 2a. The secondary frame 2a is suspended from the chassis 4.
    The machine 1 finally comprises a device 7 for vibrating the tank 3 relative to the frame 2 in a transverse plane (FIG. 3). Thus, under the effect of the device 7 for vibrating, the tank 3 moves in a transverse plane relative to the cone 5, so that material is ground between the inner track 3a and the outer track 5a. The vibrating device 7 comprises at least two vibrators.
    According to an embodiment which is that of the figures, the device 7 for vibrating comprises four vibrators 8a, 8b, 8c, 8d distributed in a square on the frame 4. Each vibrator 8a, 8b, 8c, 8d can be formed of two parts called weights distributed on either side of a substantially transverse plane of the chassis 4, so that the vibrations of the tank 3 caused by the rotation of the vibrators 8a, 8b 8c, 8d remain substantially in this transverse plane. Each vibrator 8a, 8b, 8c, 8d is fixed on a shaft 9a, 9b, 9c, 9d with vibrator of longitudinal axis driven in rotation relative to the chassis 4 by a motor 10, including the motors 10 of the shafts 9a, 9b to vibrator are visible in Figure 2. Thus, when the vibrators are rotated, the tank 3 is vibrated and describes a circular translational movement in a transverse plane.
    ίο
    Each motor 10 controls the corresponding vibrator independently of the other vibrators. More precisely, each motor 10 controls the position and the speed of rotation of the corresponding vibrator. As will be explained below, each motor 10 is preferably a reversible motor, that is to say that it comprises a motor mode, in which it consumes energy to rotate the corresponding vibrator, and a generator mode in which it generates energy by braking the corresponding vibrator.
    More specifically, the device 7 for vibrating comprises a system 11 for controlling the motors 10 and a system 12 for measuring the relative phase shift between the vibrators 8a, 8b, 8c, 8d, that is to say the relative angle between the vibrators 8a, 8b, 8c, 8d, so that the vibration device 7 can take at least three positions:
    a so-called zero position, in which the phase shift angle between the vibrators 8a, 8b, 8c, 8d is such that the vibrations of the tank 3 are of minimum amplitude, or even zero;
    a so-called maximum position, in which the phase shift angle between the vibrators 8a, 8b, 8c, 8d is zero, so that the vibrations of the tank 3 are of maximum amplitude;
    at least one so-called intermediate position, in which the phase angle between the vibrators 8a, 8b, 8c, 8d is such that the vibrations of the tank 3 are of intermediate amplitude between the maximum amplitude and the minimum amplitude.
    In practice, the vibration device 7 can take a multitude of intermediate positions, so as to adjust the amplitude of the vibrations as a function of the required grinding power.
    According to the example presented in the figures, that is to say with four vibrators 8a, 8b, 8c, 8d, the phase shift of the vibrators is carried out in pairs. Thus, in the zero position, the diagonally opposite vibrators 8a, 8c are in phase with one another, just as the diagonally opposite vibrators 8b, 8d are in phase with each other, while the vibrators 8a, 8c are in phase opposition with respect to the vibrators 8b, 8d, that is to say that the phase shift angle is substantially 180 °. In the maximum position, the four vibrators 8a, 8b, 8c, 8d are in phase with each other. Finally, in the intermediate position, the vibrators 8a, 8c are phase shifted by an angle different from 180 ° relative to the vibrators 8b, 8d.
    More precisely, each vibrator 8a, 8b, 8c, 8d can be associated with a position sensor, enabling the position of each of the vibrators 8a, 8b, 8c, 8d to be known at all times.
    The control system 11 is thus able to pass the device 7 for vibrating from one position to the other while maintaining the rotation of the vibrators. Indeed, thanks in particular to the independence of the motors 10, at all times, the position of each vibrator, its speed of rotation and its phase shift relative to the other vibrators are known and can be regulated online, without the machine 1 not must be stopped.
    To this end, the control system 11 comprises a computer 13 which, from the knowledge of the speed of rotation and the position of each vibrator and of the phase difference between the vibrators 8a, 8b, 8c, 8d makes it possible to know at all instant the amplitude of the vibrations of the tank 3. By comparing the calculated value with a target value, the vibration setting device 7 can in particular regulate the phase shift between the vibrators 8a, 8b, 8c, 8d to regulate the amplitude of the vibrations of the tank 3 at any time, and thus regulate the grinding effort. Optionally, the control system 11 can also regulate the speed of rotation of the vibrators to regulate the grinding power.
    Thus, the intermediate position does not depend on the mechanical mounting, but can be adjusted online, without stopping the operation of the machine 1, by the engine control system 11 acting directly on the engines.
    Thanks to this new design of grinding machine 1 in which the vibrators 8a, 8b, 8c, 8d are each controlled by a motor 10 independently of each other, the machine 1 makes it possible to adapt the grinding force according to the characteristics of the incoming material and of the characteristics targeted for the material leaving the machine 1.
    Thus, to grind material, the device 7 for vibrating is previously placed in the zero position. An initial grinding power can be determined by the computer 13 as a function of at least one grinding parameter. The initial grinding power determines an initial speed of rotation and an initial phase shift of the vibrators 8a, 8b, 8c, 8d, this initial phase shift being able to correspond to the maximum position or to an intermediate position. The control system 11 then gradually increases the speed of rotation of the vibrators 8a, 8b, 8c, 8d until it reaches the initial value. The vibrating device 7 being in the zero position, the tank 3 has little or no transverse displacement relative to the cone 5. Thus, during the increase in rotational speed, it avoids passing through frequencies of resonance of machine 1 which could degrade it. Then, the control system 11 moves the vibrators so as to obtain the determined initial phase shift, and therefore the initial grinding power.
    As long as the grinding parameters are not modified, the grinding power can be maintained substantially equal to the initial grinding power: the speed of rotation of the vibrators and the phase shift are maintained.
    However, it may happen that a grinding parameter is modified during feeding of the material.
    By grinding parameter, here is meant any parameter which can influence the characteristics of the material leaving the grinding machine 1. Non-limiting mention may be made of the particle size of the granules, that is to say in particular the size, hardness, shape and porosity of the granules, the density of the incoming material, the targeted particle size of the granules leaving the material, the material flow. In practice, the particle size of the incoming material, and in particular the size of the granules, relative to the targeted particle size, and in particular the size of the granules, of the outgoing material constitute the most often used grinding parameters.
    By detecting the modification of a grinding parameter, a new grinding power can be calculated by the computer 13, and the phase angle of the vibrators can be modified to obtain the new grinding power, while maintaining the rotation of the vibrators . Here again, the phase angle of the vibrators can correspond to the maximum position or to an intermediate position.
    Indeed, the grinding power is directly related to the amplitude of the vibrations of the tank 3, which is determined by the phase difference between the vibrators. More precisely, it is the grinding effort which directly depends on the phase shift of the vibrators.
    However, the required grinding power can be determined in particular as a function of the characteristics of the incoming material and of the characteristics targeted for the outgoing material. For example, the greater the difference in size between the granules of the outgoing material and the incoming material, the greater the grinding power must be.
    An example of application relates to mineral processing, that is to say the crushing of ores. Depending on requirements, it may happen that the outgoing material has a proportion of granules of sizes smaller than a required size, called fines, which is too high. In fact, fine particles can be detrimental to downstream treatment processes. Thanks to the new machine 1 presented here, the grinding power is adjusted to avoid the production of fines.
    In general, thanks to the grinding machine 1 thus designed, and unlike the machines of the prior art, it is not necessary to stop the grinding machine 1 to change the phase difference between the vibrators 8a, 8b , 8c, 8d and maintain a new grinding power different from that initially determined when starting machine 1.
    The modification of a grinding parameter can be done upstream of the machine 1, for example by directly measuring the characteristics of the incoming material, or downstream of the machine 1, for example by measuring the characteristics of the outgoing material. According to one embodiment, the machine 1 further comprises a sensor of the longitudinal vibrations of the tank 3. By comparing the spectrum of the longitudinal vibrations measured by the sensor with a reference spectrum, it is possible to detect a modification of a parameter grinding. A difference between the measured spectrum and the reference spectrum is quantified. It may for example be a difference in amplitude, frequency or even a time difference. If the quantified difference exceeds a threshold value, the detection of a modification of a grinding parameter can be confirmed, for example by sending a signal to the vibration setting device 7, to consequently regulate the phase shift of the vibrators.
    Indeed, there may be situations in which the grinding power of the machine 1 is unsuitable. For example, the power may be insufficient, so that the granules of the incoming material are not ground, and cause a blockage. It can also happen that the grinding power is too high, so that the outer track 5a of the cone 5 comes into contact with the inner track 3a of the tank 3. In such situations, unwanted longitudinal vibrations appear, signaling that the grinding power must be adjusted.
    The machine 1 thus formed can be more reactive to changes in the grinding parameters than the grinding machines of the prior art. In particular, when a material supply cut-off occurs, it is quickly detected, and, thanks to the motors 10, the vibration setting device 7 can quickly set to zero position, to prevent the tank 3 from coming in contact with the cone 5 and that the grinding tracks 3a, 5a are not degraded. The reaction time is of the order of a few seconds between the detection of the material supply cut-off and the setting to zero position, while in the state of the pulley technique, the reaction time is several tens of seconds.
    The position of the vibrators is also precise, with generally an angular offset of less than 1 °. In addition, the position and speed of the vibrators 8a, 8b, 8c, 8d being known at all times, it is easy to set up predictive maintenance: when the power developed by a vibrator deviates too much from a power of reference or that of the other vibrators, a maintenance signal can be generated to indicate that an intervention, for example a lubrication operation, a diagnosis of the bearings or a visual inspection, must be carried out.
    According to an embodiment illustrated in particular in FIG. 4, the position sensor of each vibrator is of the encoder type. An operator places the vibrators 8a, 8b, 8c, 8d in an initial position in which the phase difference between the vibrators 8a, 8b, 8c, 8d corresponds to the zero position of the vibrating device 7. Each encoder then records the position of the associated vibrator. Thus, after the vibrators 8a, 8b, 8c, 8d have been moved from their initial position, to start the machine 1, the vibration device 7 should be returned to the zero position, in order to be able to increase the speed up to the speed determined by the grinding power required without generating vibrations. To this end, the motors 10 rotate the vibrators 8a, 8b, 8c, 8d until each vibrator 8a, 8b, 8c, 8d is returned to the initial position, before increasing their speed of rotation. Thus, the machine 1 can be stopped suddenly, the vibrators 8a, 8b, 8c, 8d being in a position with any relative phase shift; restarting the machine 1 is always done with the device 7 for vibrating in the zero position.
    As mentioned above, the motors 10 can be of the reversible type. Thus, according to one embodiment, the system 11 for controlling the motors 10 comprises a device 14 for recovering and storing at least part of the energy generated by each motor 10 in generator mode. Thus, when an electrical supply cut occurs, at least one motor 10, in practice all the motors 10, go into generator mode. The recovered energy can then be used by the control system 10 to put the vibration setting device 7 in the zero position, so that the vibrations of the tank 3 are almost zero. Thus, the speed of rotation of the vibrators 8a, 8b, 8c, 8d gradually decreases, the device 7 for vibrating being kept in the zero position, without passing through resonant frequencies of the machine 1 which could degrade it.
    Optionally, the control system 11 may further comprise a device 15 for dissipating at least part of the energy generated by each motor in generator mode, making it possible to evacuate the excess energy and avoiding an overload on the network.
    According to one embodiment, each motor 10 is mounted on the frame 2 and comprises a motor shaft 16, extending longitudinally, and connected to the shaft 9a, 9b, 9c, 9d with a corresponding vibrator using a link 17 for driving the shaft 9a, 9b, 9c, 9d with a vibrator in rotation. To this end, each shaft 9a, 9b, 9c, 9d with a vibrator being mounted in rotation about an axis parallel to the longitudinal axis of the chassis 4, the connection 17 between the motor shaft 16 and the shaft 9a, 9b , 9c, 9d with corresponding vibrator comprises a rigid coupling in the transverse plane. However, any longitudinal vibrations of the chassis 4 carrying the tank 3 can degrade the connection between the shafts. To avoid this, the connection also includes a flexible coupling in the longitudinal direction, so that the shaft 9a, 9b, 9c, 9d with vibrator can move in the longitudinal direction relative to the motor shaft 14 over a stroke maximum determined. This arrangement also makes it possible to have each motor 10 substantially in the longitudinal alignment of one of the vibrators 8a, 8b, 8c, 8d.
    For example, the link 17 between the motor shaft 16 and the shaft 9a, 9b, 9c, 9d with corresponding vibrator comprises a connecting rod 18 with constant velocity transmission joint. It is for example a connecting rod 18 with double universal joint. The link 17 further comprises a part 19 intermediate between one end of the connecting rod 18, for example the end on the motor side 10. This intermediate part 19 is formed in particular of a rigid body 20, for example metallic, in two parts 20a, 20b, and a band 21 of elastomeric material fixed astride the two parts 20a, 20b of the rigid body 20. More specifically, the strip 21 is of annular shape, each of its free edges being rigidly fixed on one of the parts 20a, 20b of the rigid body 20. A first part 20a of the rigid body 20 is rigidly fixed to one end of the motor shaft 10, and the second part 20b is fixed to the motor side end 10 of the connecting rod 18. The band 21 of elastomer is sufficiently elastic to be deform longitudinally, allowing a longitudinal relative movement over a determined stroke between the motor shaft 10 and the shaft 9a, 9b, 9c, 9d with corresponding vibrator. In order to guide this longitudinal displacement, one of the two parts, for example the first part 20a, comprises a lug 22 projecting longitudinally, and the other part, for example the second part 20b, comprises a longitudinal bore 23, complementary to the lug 22, in order to allow the guide 22 to slide in the bore 23 with guidance. The lug 22 can be attached by rigid fixing to the first part 20a, or be integral with the first part 20a. The second part 20b is for example made of steel, and a self-lubricated bronze ring is force-fitted into the bore 23.
    The link 17 thus allows flexibility in the transmission of rotation from the motor shafts 16 to the shafts 9a, 9b, 9c, 9d with a vibrator absorbing the vibrations of the tank 3 relative to the frame 2. Cooperation between the lug 22 and the bore 23 makes it possible to avoid transverse deflections detrimental to the mechanical strength of the link 17.
    权利要求:
    Claims (15)
    [1" id="c-fr-0001]
    1. Grinding machine (1) comprising: a frame (2), a tank (3) forming an internal grinding track (3a), the tank being mounted on a chassis (4) movable in translation at least in a transverse plane by relative to the frame, a cone (5) forming an external grinding track (5a) and placed inside the tank (3), the machine (1) further comprising a device (7) for vibrating the tank (3) relative to the frame (2) in a transverse plane, so that material is crushed between the inner track (3a) and the outer track (5a) of grinding by the relative movement of the tank (3) by relation to the cone (5); the machine (1) being characterized in that the device (7) for vibrating the tank (3) comprises at least two vibrators (8a, 8b, 8c, 8d) mounted on the chassis (4), each vibrator ( 8a, 8b, 8c, 8d) being rotated about a longitudinal axis of the chassis by a motor (10), each motor (10) controlling independently of each other the vibrator with which it is associated, the device (7) for vibrating the tank (3) further comprising a system (11) for controlling the motors (10) and a system (12) for measuring the relative phase shift angle between the vibrators (8a, 8b, 8c, 8d), so that the vibration device (7) can take at least three positions:
    a so-called zero position, in which the phase shift angle between the vibrators (8a, 8b, 8c, 8d) is such that the vibrations of the tank (3) are of minimum amplitude;
    a so-called maximum position, in which the phase shift angle between the vibrators (8a, 8b, 8c, 8d) is zero, so that the vibrations of the tank (3) are of maximum amplitude;
    at least one so-called intermediate position, in which the phase angle between the vibrators (8a, 8b, 8c, 8d) is such that the vibrations of the tank are of intermediate amplitude between the maximum amplitude and the minimum amplitude, the control system (11) being capable of passing the vibration device from one position to the other while maintaining the rotation of the vibrators (8a, 8b,
    8c, 8d).
    [2" id="c-fr-0002]
    2. Machine (1) according to claim 1, in which each motor (10) is mounted on the frame (2) and comprises a motor shaft (16) extending longitudinally, and in which each vibrator (8a, 8b, 8c , 8d) is mounted on a shaft (9a, 9b, 9c, 9d) with vibrator, a connection (17) between the motor shaft (16) and the shaft (9a, 9b, 9c, 9d) with corresponding vibrator comprising a rigid coupling in the transverse plane, so that the vibrator shaft (9a, 9b, 9c, 9d) is rotated by the drive shaft (16) and a flexible coupling in the longitudinal direction, so that the 'shaft (9a, 9b, 9c, 9d) vibrator can move in the longitudinal direction relative to the motor shaft (16) over a determined maximum stroke.
    [3" id="c-fr-0003]
    3. Machine (1) according to claim 2 wherein the connection (17) between the motor shaft (16) and the shaft (9a, 9b, 9c, 9d) includes a connecting rod (18) comprising a constant velocity transmission between the motor shaft (16) and the vibrator shaft (9a, 9b, 9c, 9d), and comprises a part (19) intermediate between the connecting rod (18) and the motor shaft (16), the intermediate piece (19) comprising a strip (21) of elastomer material fixed astride two parts (20a, 20b) of a rigid body (20) of the intermediate piece (19), a first part (20a) being fixed to one end of the motor shaft (16) and a second part (20b) being fixed to one end of the connecting rod (18), one of the first part (20a) and the second part (20b) further comprising a lug (22) projecting longitudinally cooperating with a longitudinal bore (23) on the other of the first part (20a) and the second part (20b) to guide the movement of the shaft e (9a, 9b, 9c, 9d) with vibrator in the longitudinal direction relative to the motor shaft (16).
    [4" id="c-fr-0004]
    4. Machine (1) according to any one of the preceding claims in which each motor (10) comprises a motor mode, in which the motor (10) consumes energy to rotate the vibrator (8a, 8b, 8c , 8d) associated, and a generator mode, in which the motor (10) generates energy by braking the vibrator (8a, 8b, 8c, 8d) associated.
    [5" id="c-fr-0005]
    5. Machine (1) according to claim 4, wherein the engine control system (11) comprises a device (14) for recovering and storing at least part of the energy generated by each engine (10) in generator mode.
    [6" id="c-fr-0006]
    6. Machine (1) according to claim 4 or claim 5, wherein the engine control system (11) comprises a device (15) for dissipating at least part of the energy generated by each engine (10 ) in generator mode.
    [7" id="c-fr-0007]
    7. Grinding process using a grinding machine (1) according to any one of the preceding claims, comprising:
    placing the vibration setting device (7) in the zero position; the determination by the control system (11) of a grinding force as a function of at least one grinding parameter;
    increasing the speed of rotation of the vibrators (8a, 8b, 8c, 8d) to a value determined by the grinding force;
    placing the vibrators (8a, 8b, 8c, 8d) in relative position with a phase shift angle between the vibrators (8a, 8b, 8c, 8d) determined by the grinding force;
    the supply of material to be ground to the machine (1) between the two grinding tracks (3a, 5a), the method further comprising, the rotation of the vibrators (8a, 8b, 8c, 8d) being maintained:
    the detection of a modification of at least one grinding parameter; determining a new grinding effort;
    modifying at least the phase shift angle between the vibrators (8a, 8b, 8c, 8d) as a function of the new force.
    [8" id="c-fr-0008]
    8. The method of claim 7, wherein a modified grinding parameter is the particle size of the ground material at the outlet of the grinding machine (1).
    [9" id="c-fr-0009]
    9. The method of claim 7 or claim 8, wherein a modified grinding parameter is the particle size of the material feeding the grinding machine (1).
    [10" id="c-fr-0010]
    10. The method as claimed in claim 9, in which the grinding machine (1) further comprises a tank vibration sensor (3) in the longitudinal direction, and in which the detection of a modification of the grinding parameter comprises:
    the determination of a reference spectrum of the longitudinal vibrations of the tank (3), the comparison between the reference spectrum and a spectrum measured by the vibration sensor, the quantification of a difference between the reference spectrum and the measured spectrum if the quantified difference exceeds a threshold value, confirmation of the detection of a modification of at least one grinding parameter of the material feeding the grinding machine (1).
    [11" id="c-fr-0011]
    11. Method according to the preceding claim, in which the placing in the starting position comprises:
    the vibrators (8a, 8b, 8c, 8d) being stopped, the recording of an initial position of the vibrators in which the phase difference between the vibrators (8a, 8b, 8c, 8d) corresponds to the zero position of the device (7) vibration;
    moving the vibrators (8a, 8b, 8c, 8d);
    the rotation of the vibrators (8a, 8b, 8c, 8d) until the vibrators (8a, 8b, 8c, 8d) are in their initial position.
    [12" id="c-fr-0012]
    12. Method according to any one of claims 7 to 11, when a material supply cut-off occurs, the device (7) for vibrating the tank (3) is set to the zero position.
    [13" id="c-fr-0013]
    13. Method according to any one of the preceding claims, in which the machine (1) is according to any one of claims 4 to 6, and
    10 in which when an electrical supply cut to the motors (10) occurs, it comprises:
    putting at least one engine (10) into generator mode, recovering and storing at least part of the braking energy by the device (
    [14" id="c-fr-0014]
    14) recovery and storage;
    [15" id="c-fr-0015]
    15 - setting the device (7) for vibrating the tank (3) to zero position using at least part of the energy recovered in the device (14) for recovery and storage to phase the vibrators (8a , 8b, 8c, 8d), maintaining the zero position until the rotation of all the vibrators (8a, 8b, 8c, 8d) has stopped.
    1/4
    类似技术:
    公开号 | 公开日 | 专利标题
    FR3063234A1|2018-08-31|CONE MILLING MACHINE AND MILLING METHOD USING SUCH A MACHINE
    EP1553324B1|2007-10-31|Bearing support with double stiffness
    EP0808701B1|2002-12-04|Wire saw
    EP1736587B1|2010-01-20|Needling machine for consolidating a web
    CA2505058C|2013-03-19|Process for closing a hole in a metal part by means of friction welding, use of a metal bar and a bearing bracket to carry out the process
    EP1939343A2|2008-07-02|Guided punching device and method
    EP0642387B1|1998-01-28|Cone-type vibrating crusher and method for adjusting operation of such crusher
    FR2901563A1|2007-11-30|NEEDLEFINER WHOSE FREQUENCY OF AT LEAST ONE CLEAN MODE OF VIBRATION IS ADJUSTABLE
    FR2557939A1|1985-07-12|BEARING LUBRICATION DEVICE
    FR2489460A1|1982-03-05|VARIATOR OF BELT SPEED
    FR2981417A1|2013-04-19|SYSTEM FOR GUIDING A VERTICAL SHAFT OF ROTATING MACHINE AND ENERGY CONVERTING PLANT INCORPORATING SUCH A SYSTEM
    FR2471257A1|1981-06-19|DEVICE FOR THE RECTIFICATION WITHOUT POINTS OF SYMMETRIC SURFACES OF REVOLUTION OF WORKPIECES
    EP3319749B1|2019-09-11|Vibratory system with an oscillating plate
    EP3204163B1|2020-07-29|Mill for crushing a bed of materials by compression
    FR2939843A1|2010-06-18|Oil delivering device for turbomachine i.e. jet engine, of aircraft, has nozzles positioned with respect to each other and relative to openings, so that oil blast from nozzles is passed in openings and is supplied to component
    EP0350345A1|1990-01-10|Method of and installation for continuous casting thin metallic products
    FR2475674A1|1981-08-14|Remotely controlled pressure vessel cap locking screw - uses rotation control motor connected to fluid lift cylinder to provide turning of piston in cylinder body
    FR3096603A1|2020-12-04|Cutting wire cutting device adopting the form of a closed loop
    BE1009776A3|1997-08-05|Direction valve.
    FR2901159A1|2007-11-23|Inertial shaker useful in paper manufacturing process, comprises fixed frame, rotating shafts of horizontal rotation axis fixed on movable frame and carries eccentric-weight, and unit for operating rotating shaft in synchronized rotation
    EP3067466A1|2016-09-14|Machine and method for compacting a ballast bed
    EP1658938A1|2006-05-24|Ultrasonic cutting tool and cutting device comprising said cutting tool
    BE380501A|
    FR2572774A1|1986-05-09|Pump with pistons with a barrel, especially for high pressure fluids
    FR3080454A1|2019-10-25|PURE FLEXION TEST MACHINE OF A TEST
    同族专利:
    公开号 | 公开日
    JP2020508218A|2020-03-19|
    US20200023372A1|2020-01-23|
    CA3052731A1|2018-08-30|
    EP3585518B1|2021-02-17|
    CN110446554A|2019-11-12|
    ZA201904890B|2020-12-23|
    RU2741635C1|2021-01-28|
    WO2018154222A1|2018-08-30|
    KR20190116317A|2019-10-14|
    AU2018225355A1|2019-08-22|
    FR3063234B1|2019-04-12|
    CN110446554B|2021-10-08|
    JP6976355B2|2021-12-08|
    DK3585518T3|2021-05-10|
    CN208679263U|2019-04-02|
    BR112019016260A2|2020-04-07|
    EP3585518A1|2020-01-01|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US5996915A|1995-06-13|1999-12-07|Fcb Societe Anonyme|Vibrating cone crusher|
    US20110155834A1|2009-12-30|2011-06-30|Fan Kung-Chi|Vibrating cone crusher|
    YU124388A|1988-06-27|1990-10-31|Jadrijevic Ante|Universal vibrational crusher|
    FR2687080B1|1992-02-06|1996-05-10|Drac Isere Concassage|FIXED CONE CRUSHER.|
    FR2702970B1|1993-03-24|1995-05-24|Fcb|Vibrating cone crusher and method for adjusting the speed of such a crusher.|
    RU2178339C2|1999-12-16|2002-01-20|Акционерное общество открытого типа "Механобр-техника"|Conic inertial grinder|
    RU2225257C2|2001-12-17|2004-03-10|Открытое акционерное общество "Механобр-Техника"|Inertia conic mill|
    US8091817B2|2009-12-11|2012-01-10|Flsmidth A/S|Milling device|
    RU136744U1|2013-08-22|2014-01-20|Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Санкт-Петербургский государственный архитектурно-строительный университет"|CONE VIBRATION CRUSHER|
    FR3063234B1|2017-02-27|2019-04-12|Fives Solios|CONE MILLING MACHINE AND MILLING METHOD USING SUCH A MACHINE|FR3063234B1|2017-02-27|2019-04-12|Fives Solios|CONE MILLING MACHINE AND MILLING METHOD USING SUCH A MACHINE|
    FR3078493B1|2018-03-02|2020-02-14|Fives Fcb|PROCESS FOR DISSOCIATING DIFFERENT CONSTITUENTS OF A HETEROGENEOUS ARTIFICIAL MATERIAL|
    CN110479412B|2019-08-27|2020-12-15|湖南柿竹园有色金属有限责任公司|High-efficient type cone crusher|
    RU208631U1|2021-09-21|2021-12-28|Акционерное общество «ГЕОСВИП»|Vibration exciter hydraulic cylinder with bimetallic bushings|
    法律状态:
    2018-01-22| PLFP| Fee payment|Year of fee payment: 2 |
    2018-08-31| PLSC| Publication of the preliminary search report|Effective date: 20180831 |
    2019-01-23| PLFP| Fee payment|Year of fee payment: 3 |
    2020-01-22| PLFP| Fee payment|Year of fee payment: 4 |
    2021-01-20| PLFP| Fee payment|Year of fee payment: 5 |
    2022-01-19| PLFP| Fee payment|Year of fee payment: 6 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1751554|2017-02-27|
    FR1751554A|FR3063234B1|2017-02-27|2017-02-27|CONE MILLING MACHINE AND MILLING METHOD USING SUCH A MACHINE|FR1751554A| FR3063234B1|2017-02-27|2017-02-27|CONE MILLING MACHINE AND MILLING METHOD USING SUCH A MACHINE|
    CN201721193898.4U| CN208679263U|2017-02-27|2017-09-18|Online adjustable vibration cone crusher|
    JP2019567401A| JP6976355B2|2017-02-27|2018-02-20|Cone crushing machines and crushing methods using such machines|
    PCT/FR2018/050391| WO2018154222A1|2017-02-27|2018-02-20|Cone crushing machine and crushing method using such a machine|
    CA3052731A| CA3052731A1|2017-02-27|2018-02-20|Cone crushing machine and crushing method using such a machine|
    BR112019016260A| BR112019016260A2|2017-02-27|2018-02-20|cone milling machine and milling process that employs such a machine|
    US16/489,007| US20200023372A1|2017-02-27|2018-02-20|Cone crushing machine and crushing method using such a machine|
    KR1020197024045A| KR20190116317A|2017-02-27|2018-02-20|Cone Shredding Machine and Shredding Method Using the Shredding Machine|
    RU2019130159A| RU2741635C1|2017-02-27|2018-02-20|Conical crusher and method of grinding using such crusher|
    AU2018225355A| AU2018225355A1|2017-02-27|2018-02-20|Cone crushing machine and crushing method using such a machine|
    DK18709673.0T| DK3585518T3|2017-02-27|2018-02-20|CONE GRINDING MACHINE AND METHOD OF GRINDING USING SUCH A MACHINE|
    CN201880013800.3A| CN110446554B|2017-02-27|2018-02-20|Cone crusher and crushing method using same|
    EP18709673.0A| EP3585518B1|2017-02-27|2018-02-20|Cone crushing machine and crushing method using such a machine|
    ZA2019/04890A| ZA201904890B|2017-02-27|2019-07-25|Cone crushing machine and crushing method using such a machine|
    [返回顶部]