EP4135900A1 - Procédé de régulation de l'amortissement du mouvement d'un rouleau presseur d'une presse à rouleaux haute pression et presse à rouleaux haute pression correspondante - Google Patents

Procédé de régulation de l'amortissement du mouvement d'un rouleau presseur d'une presse à rouleaux haute pression et presse à rouleaux haute pression correspondante

Info

Publication number
EP4135900A1
EP4135900A1 EP21716098.5A EP21716098A EP4135900A1 EP 4135900 A1 EP4135900 A1 EP 4135900A1 EP 21716098 A EP21716098 A EP 21716098A EP 4135900 A1 EP4135900 A1 EP 4135900A1
Authority
EP
European Patent Office
Prior art keywords
roller
damping
pressure
press
loose
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP21716098.5A
Other languages
German (de)
English (en)
Inventor
Niko Hachenberg
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
KHD Humboldt Wedag AG
Original Assignee
KHD Humboldt Wedag AG
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 KHD Humboldt Wedag AG filed Critical KHD Humboldt Wedag AG
Publication of EP4135900A1 publication Critical patent/EP4135900A1/fr
Pending legal-status Critical Current

Links

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
    • B02C4/00—Crushing or disintegrating by roller mills
    • B02C4/28—Details
    • B02C4/32—Adjusting, applying pressure to, or controlling the distance between, milling members
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C4/00—Crushing or disintegrating by roller mills
    • B02C4/02—Crushing or disintegrating by roller mills with two or more rollers

Definitions

  • the invention relates to a method for regulating the damping of the movement of a loose roll of a high-pressure roller press, the high-pressure roller press having a hydraulic system which presses the loose roller against a fixed roller and thus maintains a predetermined nip pressure in the nip between the loose roller and the fixed roller when the material to be ground passes the nip happened between the loose roller and the fixed roller.
  • the invention also relates to a high pressure roller press having such a control.
  • high pressure roller presses For crushing or compacting granular material, high pressure roller presses are often used, which consist of two counter-rotating, usually the same size, rotatably mounted press rollers that rotate at the same circumferential speed and form a narrow nip between them.
  • the ground material to be comminuted or compacted is drawn through this roller gap, the ground material being crushed or compacted under the high pressure prevailing in the roller gap.
  • the result of this treatment namely comminution or compression, is largely dependent on the material properties of the ground material to be comminuted.
  • the crushing in the roller gap described here was first used by Schönert et al.
  • High-pressure roller presses differ fundamentally from other presses that are used for size reduction.
  • high-pressure roller presses which are intended for crushing rock, cannot be compared with roller presses, for example for crushing grain.
  • Grain is ground in grain rollers.
  • Grain rollers have weights in the range of a maximum of 100 kg.
  • the entire apparatus structure of a grain roller is very different from high pressure roller presses.
  • Grain rollers also work with shear. In contrast, high pressure roller presses work without shear.
  • High pressure roller presses also differ significantly from belt rollers for rolling steel.
  • Steel belt rollers are characterized by their smooth running.
  • the steel between the belt rolls is either very ductile, because the steel to be rolled is hot-deformed, or the steel is cold-deformable.
  • the smoothness of running a steel roll is quite good due to the nature of the rolling process. It is thus possible to operate a belt roller with two rollers arranged horizontally one above the other, the nip pressure being generated by the rollers' own weight and also by hydraulic aids. Problems with vibration are not to be expected due to the ductility of the steel to be rolled.
  • strip rollers can reach a roller gap speed of up to 200 km / h.
  • the present invention is concerned with high-pressure roller presses for crushing brittle ground material such as rock and ores, the brittleness of the ground material being an essential prerequisite for the suitability of this grinding process for the respective ground material.
  • Belt rollers for steel work in the other operating extreme than high-pressure roller presses, namely with ductile steel, which deforms under the roller and does not break up spontaneously due to brittleness and thus evades the pressure in the roller gap.
  • the rollers lie horizontally next to each other and form a roller gap through which the ground material runs vertically.
  • High pressure roller presses have a nip pressure of 50 MPa and more.
  • the overall mechanical behavior of the high pressure roller press cannot be compared with the mechanical behavior of vertically stacked belt rollers, which also run smoothly and smoothly due to the ductility of the steel to be rolled.
  • the grinding material which is not always uniform, passes through the roller gap and due to the high pressure generated by hydraulic presses that move the rollers in a horizontal direction, a high-pressure roller press can tend to vibrate. The vibration can develop as a result of a slight change in the properties of the material to be ground. It can happen that dry, brittle regrind draws air with it when it is crushed in the roller gap.
  • the air trapped in the millbase can also escape spontaneously when the millbase is compressed before it is broken up spontaneously by brittle cracks, thus giving way to the nip pressure.
  • the vibration behavior of the high-pressure roller press can be influenced by non-linear forces, the description of which cannot be considered in the classic analysis of a damped vibration.
  • the natural frequencies of high-pressure roller presses are undesirably in the range of external excitation frequencies, such as the sudden yield in the event of a brittle fracture, the spontaneous escape of air from the highly compressed grist, the rotation of the grinding rollers and the loading with a bucket elevator.
  • high-pressure crushing depends on a number of parameters to be observed in the high-pressure roller press used for optimum, low-energy and low-wear crushing. For example, it is important that the rollers of the high-pressure roller press used rotate without relative slippage, so that the rollers do not grind by shearing movement of the material to be ground, but only press. Furthermore, it has been found that the correct amount of fresh good per unit of time fed to the nip of the high-pressure roller press used also plays a significant role for the optimal function of the high-pressure roller press used.
  • the high-pressure roller press works as a crusher, especially when using rollers equipped with hard reinforcement bodies, the granular material to be crushed being broken as fresh material by point loads. This type of comminution is less energy-efficient than high-pressure comminution and it does not lead to the desired fine product. If, on the other hand, the roller gap is filled with too much granular material as fresh material per unit of time, the regrind of fresh material and circulating material in the roller gap compresses too much, trapped air can no longer escape and the roller gap of the high-pressure roller press used tends to become clogged .
  • the resiliently mounted rollers give way in this case, the excess fresh material falls through the roller gap without being crushed and the high-pressure roller press then works again in the previous state until it has to repeatedly move to allow the excess fresh material to pass through the roller gap.
  • the roller press thus gets into a first type of oscillatory movement alongside other oscillatory movements and it begins to vibrate mechanically.
  • rollers can then show a combined oscillation, which consists of a back and forth movement of the rollers in the horizontal direction perpendicular to the extension of the nip and a rotational oscillation.
  • the rollers can also undergo a slight, oscillating change in position in which the respective roller rotates by very small amounts of angles about a vertical axis. During this movement, the roller is not shifted evenly with the two bearing blocks carrying it, but the two bearing blocks at each end of a roller change their position alternately.
  • mechanical vibration movements can occur within a high-pressure roller press when the high-pressure roller press is started, if the material to be ground is not yet in equilibrium in circulation or if the material in circulation is not yet in equilibrium. Has settlement. Mechanical vibratory movements also arise when using fresh food that is wet and fine-grained.
  • the entire system of the high pressure roller press is mechanically dampened due to its structure.
  • the damping is provided by the hydraulic system, in which the hydraulic fluid flows back and forth through the lines, which are fine in comparison with the diameters of the hydraulic rams or cylinders, at a high speed.
  • the viscosity of the hydraulic fluid causes strong and rather linear damping when flowing through the lines at high speed. Linear damping can be described by the classic description of a damped oscillation.
  • the movement of the bearing blocks on the slide rails of the loose rollers also absorbs a high level of mechanical energy in the form of friction, which dampens any oscillating movement.
  • the movement of the bearing blocks follows less of a linear damping, since the transition from static friction (no movement with slight surface deformation in the elastic range) to sliding friction occurs suddenly.
  • the sliding friction is also not linear.
  • the resistance to sliding friction decreases with speed. Due to the large number of possible vibrations, i.e. bending vibrations, torsional vibrations, vibrations whose damping is in accordance with static / sliding friction, vibrations that are dampened by the viscosity of the hydraulic fluid, and the large number of external vibration excitations, such as periodic loading of ground material through a bucket elevator, a large number of different natural vibrations, ie different resonance frequencies, can be observed in a high-pressure roller press.
  • the operating speed can also lead to a vibratory movement in the event of a beating bearing or in the event of a vertical runout of the rollers.
  • the high pressure roller press gets into an unwanted oscillation mode, it turns out that the high pressure roller press is no longer working in an energy-efficient manner and, moreover, is also subject to high mechanical loads.
  • the amount of fresh goods fed in per unit of time can be regulated by e.g. the high-pressure roller press will give less fresh material per unit of time to the roller gap through the feed device.
  • this has the disadvantage that a comparatively long follow-up time of the controlled system from the controlled feeding device to the detected oscillatory movements has to be accepted. It takes a certain amount of time until the changed loading of the roller gap with fresh material takes effect and ultimately the oscillation movement is reduced as a result. By then, considerable damage to the high-pressure roller press can already have occurred or accumulate if this type of control intervention is required more frequently.
  • cone crushers are described that are equipped with proximity sensors such as ultrasonic or laser sensors. By measuring the width of the exit gap, the width of the gap can be adjusted to the process conditions by raising or lowering the cone. thereby avoiding uneven rotations that can damage the cone.
  • US2004 / 0255679A1 describes a drum mill for comminuting minerals which has an acoustic sensor in the drum, with the aid of which excessive loads on the drum, e.g. from rock-like rock, can be detected.
  • DE10132067A1 discloses a method for acoustic monitoring of dangerous operating conditions, e.g. slip, in roller mills. For this purpose, the noises occurring in the roller mill or the sound level are recorded with a microphone and the frequency spectrum is evaluated.
  • DE102011018705A1 discloses a method for regulating the nip pressure as a function of an observed vibration of the high-pressure roller press. Depending on the operating status, the pressure in the hydraulic system is varied so that the high-pressure roller press can always be operated close to the maximum pressure.
  • German patent application DE 44 14366 A1 also teaches to reduce the pressure of the hydraulic system when measured vibration amplitudes exceed a predetermined value over a certain period of time and, conversely, to increase the pressure when predetermined vibration amplitudes are not exceeded.
  • the German patent DE 19647483 B4 discloses a high-pressure roller press which has a variable bladder accumulator in its hydraulic system, which absorbs pressure peaks in the hydraulic system. Pressure peaks are generated during the passage of material that cannot be comminuted by brittle fracture when the heavy roller presses are forced to make sudden and very rapid evasive movements while opening the roller gap when this material is passed.
  • the gas volume of the bladder accumulator changes, the spring constant of the buffer system is changed and thus the pressure increase when the volume in the hydraulic system changes. Through the Changing the gas volume in the bladder accumulator changes the hardness of the spring system.
  • the object of the invention is therefore to operate a generic high-pressure roller press in such a way that a mechanical vibration movement does not occur.
  • the object according to the invention is achieved in that the high-pressure roller press has adaptive damping in the hydraulic system.
  • a specific method for adaptive damping is given in claims 2-7.
  • the special feature of this control is that the high-pressure roller press can be operated with constant hydraulic pressure despite the vibration control. This protects the hydraulic pump, which is not subject to constant load changes and it enables the high pressure roller press to work more time in the ideal state and thus to be more efficient.
  • Equation of motion of an oscillating system can be described by assuming a harmonic oscillation behavior tfc At with x equal to the position coordinate, t equal to time, m equal to the moving mass, c equal to the damping coefficient and k equal to the restoring force.
  • the linear link is the restoring force k in the aforementioned equation.
  • the restoring force is changed. So k is changed in the equation of motion.
  • the idea of the invention provides for the damping to be adjusted by a control loop so that when a vibration is detected, the oscillation behavior of the loose roller of a high pressure roller press is such that the oscillation behavior corresponds to the aperiodic limit case of a damped one Schwingers corresponds as possible.
  • a leveling time or relaxation time is specified as a guide element, within which the system has returned to a non-oscillating state after a forced oscillation has occurred, for example when a regrind component that cannot be crushed by brittle fracture is passed or when the regrind composition changes and / or the regrind moisture content changes.
  • the forced vibration which is calculated by means of a vibration analysis and used as an actuating variable, enters the system as a disturbance variable. large is an attenuator in the control loop.
  • the coupling path of the control loop is the path of the forced oscillation of the loose roller, which is to be avoided ver, and the damping of the movement of the loose roller, both of which interact with one another. Since the loose roller can also be overdamped and if the damping is too strong, it can turn into the so-called and undesirable "creep case", the regulation is necessary which on the one hand avoids the creep case detectable by vibration analysis, but also avoids the vibration occurring if the damping is too low.
  • a high-pressure roller press can easily excite itself to oscillating states during operation.
  • the adaptive damping via the control enables the high-pressure roller press to run smoothly, which works outside the ideal operating parameter range of the roller gap in the shortest possible time.
  • the ideal operating parameters are the speed of the press rolls, the nip width, the nip pressure and the flow of regrind as the quotient of the amount of regrind fed per time.
  • the ideal operating parameters are intervened, namely the roller gap pressure, which can be adjusted via the hydraulic pressure and is proportional to it, and the roller gap width, which inevitably increases when the pressure drops .
  • the mean rotation frequency of the press roll can be assumed to be almost constant due to the large mass and the associated moment of inertia.
  • the millbase flow can also be assumed to be reasonably constant when appropriately regulated by a feed device.
  • the grinding stock behavior is not sufficiently constant, in particular with regard to the tendency of the grinding stock to trap air, and the homogeneity of the grinding stock.
  • the largest mean disturbance variables are therefore the variation in the properties of the regrind, followed by the uniformity of the regrind flow.
  • the method described here for regulating the damping of the movement of a loose roll of a high-pressure roller press can have the following steps in a specific embodiment of the method: measuring mechanical vibrations on the machine frame at at least one point and / or measuring pressure fluctuations in the hydraulic system at at least one point, and / or measuring electrical current fluctuations of the Electric power consumption of at least one drive motor as a first step, the at least one mechanical oscillation and / or the pressure fluctuation and / or the current fluctuation as at least one disturbance variable in a control loop of the control.
  • a vibration analysis is carried out as a mathematical operation in a process computer.
  • Such vibration analyzes can include: low-pass filtering, high-pass filtering or band-pass filtering.
  • a Fourier transformation can be carried out, in particular a fast Fourier transformation.
  • Statistical methods of smoothing the data can be carried out, such as singular value decomposition.
  • Mathematical Gaussian convolution and noise suppression systems can also be used.
  • mathematical lock-in amplifier simulations can also be used, in which the signals to be filtered are modulated with a periodic signal to filter signals. The person skilled in the art is free here to choose an ideal vibration analysis.
  • the damping constant is the constant in front of the first order differential term in an equation of motion for a harmonic, damped oscillator. Given a known vibration behavior, this damping constant allows conclusions to be drawn about the expected leveling behavior of the entire system. If the damping constant is too large, the loose roller of the high pressure roller press to be controlled would tend to creep, in which the high pressure roller press works outside of the ideal state and thus works inefficiently, but still consumes energy.
  • the damping is too low, the loose roll of the high pressure roller press would tend to mechanical vibrations, which cause severe damage to the high pressure roller press, the foundation and, in the worst case, to the environment, such as cracks in buildings due to vibrations transmitted via the ground to the foundation of a company building
  • the next control step is followed by a comparison of the at least one damping constant with a predetermined damping constant each, with each predetermined damping constant entering the control loop as a reference variable.
  • the damping constant indirectly describes the settling time or the relaxation time of the loose roller.
  • the result of the comparison is followed by the next step of the regulation, namely setting at least one adjustable throttle in the hydraulic system, the throttle position of the respective adjustable throttle being included in the control loop as a manipulated variable, and the respective adjustable throttle in the hydraulic system having a damping effect on the Movement of the loose roller exerts and thus the control loop is closed.
  • the step of comparing the determined damping constant with the target damping constant can also be done via a known PID control, a PI control, a PD control or an ID control where P stands for "proportional”, I for "integral” and d for "differential". This control strategy is well known to the measurement and control technician and reference is made to the relevant specialist literature.
  • the specification described above is particularly suitable for regulating a system of a high-pressure roller press in which a large number of forced oscillation states can be measured.
  • belt rolls which, due to the nature of the rolling process with ductile steel, have a rather calm, i.e.
  • high-pressure roll presses exhibit vibrations that originate, for example, from the following sources: higher-frequency vibrations through the use of so-called "stud lining" the equipment of the surface of a press roll with a large number of hard bodies, inhomogeneous grist quality, sudden brittle breakage of the grist to be shredded, frequency converter with industry-typical 400 Hz alternating current with very high current consumption in the vicinity of the system (so-called mains hum), the same with 50 Hz or 60 Hz, depending on the existing mains frequency. Further vibrations may generate beating bearings, the rotation of the press roll itself when it is washed out and may no longer be ideally cylindrical or shows the first surface damage as a sign of wear.
  • the machine frame shows all kinds of natural frequencies, be it bending vibrations from steel belts, torsional vibrations or longitudinal vibrations. With the very high loads, these vibrations can also occur as torsional vibrations of the shaft for driving the loose roller. Finally, unwanted bearing vibrations caused by the meshing of gears can also be found in an overall vibration pattern of a high-pressure roller press.
  • the attenuation constant can be determined by regression, the regression calculation being based on a linearized exponential function. So it is an exponential coefficient of a decay curve from computationally determined by statistical methods.
  • a very special type of damping is achieved through the use of an adjustable one-way flow control valve in the hydraulic system.
  • a Drossel Wegtschven valve is characterized by a fluid flow that is evenly throttled in both directions, whereby the strength of the throttling effect can be adjusted with an actuator.
  • the hydraulic system By regulating the high-pressure roller press with constant pressure, it is necessary that the hydraulic system has a switch and / or the loose roller has a stop in order to prevent the loose roller from reaching the fixed roller directly when idling. If the rollers touch each other under pressure, it is easier for the reinforcement of the surface with hard bodies to be damaged.
  • the hydraulic system has an automatic pressure switch-off, which is triggered when the loose roller comes closer than a predetermined value to the fixed roller, with a mechanical switch on the machine frame the approach of the loose roller to the fixed roller is detected.
  • a mechanical stop can also achieve a similar result.
  • 1 shows a high-pressure roller press with locations of strain gauges arranged by way of example
  • 2 shows an exemplary, unprocessed vibration diagram of a vibration detector
  • FIG. 3 shows the oscillation diagram from FIG. 2 after processing by a low-pass filter
  • FIG. 4 shows the processed oscillation diagram from FIG. 3 after Fourier transformation
  • FIG. 5 Selection of a Fourier coefficient from FIG. 4 as a representation over time
  • FIG. 6 shows a Fourier series from FIG. 4, which is selected via a threshold value
  • Fig. 10 shows the effect of excessive damping on the vibration behavior of the loose roller
  • FIG. 12 shows an embodiment of the high-pressure roller press according to the invention with a maximum number of vibration sensors and an optional one-way flow control valve
  • FIGS. 8, 9 and 10 shows diagrams from FIGS. 8, 9 and 10, but with the use of a one-way flow control valve.
  • a generic high-pressure roller press 1 is shown, wel che two counter-rotating press rollers as fixed roller 2 and loose roller 3, which are received in a machine frame 4, which in turn is equipped at different positions with sensors 20 for the detection of vibratory movements.
  • the two press rollers, fixed roller 2 and loose roller 3 of the high-pressure roller press 1 are pressed against one another via hydraulic rams 17 and 18, but without touching one another.
  • the ground material to be crushed is fed to the nip 7 of the high-pressure roller press 1 between the fixed roller 2 and the loose roller 3 and thereby crushed by the pressure prevailing between the two rotating press rollers, fixed roller 2 and loose roller 3.
  • the comminution takes place by brittle fracture while avoiding shearing stress.
  • strain gauges 20 are attached as Senso Ren for the detection of vibrational movements. The vibrations measured by the strain gauges 20 are passed on to an evaluation device (not shown here), where the amplitude and / or the frequency of the measured vibrational movement is compared with a previously determined nominal value.
  • the position of a throttle valve not shown in this drawing, is changed, whereby the damping of the movement is increased.
  • the damping is slowly reduced again by means of a control strategy, preferably according to the PID method, so that the roller press 1 always works in a damping range, which brings the mechanical vibratory movement of the loose roller as far as possible into the aperiodic borderline case of damped vibration.
  • the control strategy pursues a damping that corresponds as closely as possible to the movement pattern of the aperiodic limit case with an initial deflection in a first direction, a return with slight overshoots and slowly approaching the zero position.
  • FIG. 2 shows an example of a vibration diagram as Fi (t) (function 1 after time t), which can have been detected by almost any motion sensor.
  • the mechanical displacement D is shown on the abscissa and the time t is shown on the ordinate.
  • Particularly suitable sensors for vibration measurement are: Strain gauges 20 at various points on the machine frame 4. Strain gauges 20 can measure longitudinal vibrations of a metal belt of the machine frame 4 and also torsional vibrations of a drive shaft. Acceleration sensors at just as many points on the machine frame 4 can measure bending vibrations of the corresponding metal belt when it vibrates like a guitar string. Although this oscillation is only very small in terms of the spatially resolved amplitude, usually in the range of a few pm, it is sufficient to measure characteristic oscillations.
  • Acceleration sensors can also measure when the entire high-pressure roller press 1 performs a corresponding countermovement in space due to the loose roller 3 oscillating back and forth.
  • the pressure absorption in the hydraulic system 8 and also the measurement of the power consumption of the drive motors are suitable as further sources of measurement.
  • Each vibration source has its own and typical superimpositions of negligible vibrations, such as the very high mains frequency or converter frequency when measuring current consumption, the rotation frequency and its harmonics when measuring accelerations by acceleration sensors, and again the mains frequency when measuring Longitudinal vibrations and the frequency that arises from the brittle breaking of the grist rather than gray noise, i.e. not Gaussian noise with hard signal peaks.
  • An acceleration sensor directly on a bearing block an actual vibration of the loose roller is received as the dominant vibration.
  • the aim of the invention is to regulate the damping state with detected vibrations before the high-amplitude back and forth movements of the loose roller 3 occur.
  • the signal for the first time it can be subjected to low-pass filtering, which suppresses gray noise and the line frequency.
  • the result of the low-pass filtering is shown in FIG. 3, the low-pass filtered signal of the deflection-time diagram from FIG. 2 as F2 (t) (function 2 after time t).
  • F2 (t) function 2 after time t.
  • two oscillations with different frequencies can be seen here, namely a dominant fundamental oscillation and a harmonic and traces of higher harmonics.
  • FIG. 4 shows the Fourier transform, which can be interpreted as a frequency filtering of a signal in parallel channels a) ... b) ... n).
  • the Fourier transformation converts the signal from FIG. 3 into a frequency-time diagram, with the frequency from channel a) as a function F a (f, t) (function a) after the frequency f and after the time t), channel b) as a function Fb (f, t) (function b) after the frequency f and after the time t) and channel n) as a function Fn (f, t) (function n) after the frequency f and after the Time t) is shown.
  • the dominant oscillation in channel a) is selected here and is shown in FIG. 5 as a map of a) over time t.
  • the coefficient x (a) of the damping part e (x (a) * l) of the oscillation is suitable for regression analysis to determine a damping coefficient with which the damping control can be carried out.
  • a regression analysis of the time course of the coefficient F a (f, t) allows a value x (a) to be determined, assuming a negative-exponential course. It is an observation in the invention that the swinging up of the loose roller 3, which is to be prevented, can already be recognized prematurely by typical Fre quenzmustern that can be found in the natural oscillation frequencies of the machine frame of the high pressure press.
  • the upper oscillation is shown as the deflection D (displacement) of the frequency with the coefficient a) over time t).
  • the lower oscillation diagram shows the displacement D of the frequency with the coefficient b) over time t).
  • the control strategy now determines a coefficient x (a) for the damping of the equation of motion for a telltale vibration in the machine frame 4 of a high-pressure roller press 1 from the decay of the vibration in, for example in FIG. 7 via a continuous signal (FIG. 5) Signal is the feedback signal into the control loop. If the damping is too strong, thus the coefficient x (a) is too large, the damping of the movement of the loose roller 3 is reduced by partially opening a throttle slide of a throttle in the Hydraulic system 8 of a high pressure roller press 1 and vice versa.
  • the different control states are shown in FIGS. 8 (damping too low), FIG. 9 (damping ideal) and FIG. 10 (damping too strong).
  • the loose roller 3 can, in the event of an externally forced oscillation, for example by rotating the loose roller 3 at a predetermined number of revolutions, roll gap pressure which is proportional to the hydraulic pressure of the hydraulic rams 17 and 18 and one to it Material properties of the grist that do not match, level off only after a few oscillation cycles. If a 1001 heavy roller vibrates back and forth with a frequency significantly greater than 1 Hz, the impacts transmitted to the ground can cause damage in the immediate vicinity. It has already been observed that an improperly operated and unsupervised high-pressure roller press caused cracks in the foundation of a nearby company building. This state of affairs must be avoided as a matter of urgency. If the damping is too great, the high pressure roller press 1 runs smoothly.
  • the roller gap is too large and the material that passes through is not shredded, but rather broken into large pieces.
  • the hatched area under the curve in FIG. 10 shows the deflection over time. The greater the deflection D (displacement), the more inefficiently the high-pressure roller press 1 works of the one-time overshoot at time tmax is again in the equilibrium state and thus in the ideal operating point.
  • a high pressure roller press from the PRIOR ART is shown in FIG. 11, having a fixed roller 2 and a loose roller 3.
  • the loose roller 3 is pressed against the fixed roller 2 by hydraulic rams 17 and 18.
  • Hydraulic fluid from a reservoir 23 is used to exert force by means of a hydraulic Lik pump 19 is pumped into the pistons of hydraulic rams 17 and 18.
  • a bladder accumulator 14 is provided which has a pressurized air cushion against which the hydraulic fluid can expand when it is caused by a jerky movement of the loose roller 3 is pushed intermittently from the piston of the hydraulic ram 17 and 18 back into the Lei processing system of the hydraulic system.
  • FIG 12 an embodiment of the high pressure roller press according to the invention is shown.
  • the essential element here is an adjustable throttle 15 or an adjustable throttle check valve 16 between the hydraulic system 8 and the bladder accumulator 14. If it is a one-way flow control valve 16, hydraulic fluid can expand rapidly and undamped through the bypass 16.2 in the direction of the bladder accumulator flow 14 and expand there in the event of an abrupt displacement of the idler roller 3.
  • the return flow from the pressurized Bla sen amid 14 is damped by the throttle 16.1, because the free cross-section for the flow of hydraulic fluid is limited by the throttle 16.1.
  • the viscosity of the hydraulic fluid thus generates a counterforce that is opposite to the flow velocity of the hydraulic fluid.
  • the high-pressure roller press 1 has various vibration sensors, each of which generates an individual vibration diagram as a disturbance variable 13. These are strain gauges 20 at various points on the machine frame 4, acceleration sensors at precisely these points, a digital manometer 21 in the hydraulic system 8 for the detection of pressure fluctuations and a digi tal ammeter 22 for the detection of vibrations in the power consumption of the electric drive motors. All of these sensors provide a vibration diagram that can be processed as described above. From a determined damping coefficient, which is representative of the vibration behavior of the loose roller 3, the control device determines, for example according to the PID Control strategy a control value for the throttle 16.1. The throttle 16.1 acts on the vibration behavior of the idler roller 3 and thus the control loop is closed.
  • FIGS. 13 and 14 the different effects of a throttle 15 and a throttle check valve 16 on the settling time (relaxation time) of the loose roller 3 are shown.
  • FIG. 13 is merely a repetition of FIGS. 8, 9 and 10.
  • FIG. 14 shows in the middle example that a one-way flow control valve 16 leads to a significant reduction in the settling time (relaxation time) tmax to tmax, new.
  • the loose roller 3 can retract with little or no damping, opening the roller gap 7, which is shown in the middle diagram of FIG. 14 with an arrow on the far left in bold to the right.
  • the arrow in bold stands for a fast and unrestrained or undamped movement.
  • the loose roller 3 moves again undamped (right, bold arrow to the right) by the force of the compressed grist back into the ideal position.
  • the return is faster when a one-way flow control valve 16 is used than in the case of damping in both directions with a throttle 15 acting identically in both flow directions the floch pressure roller press 1 is operated only in a very short period of time outside of its optimal operating point.

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

Abstract

L'invention concerne un procédé de régulation de l'amortissement du mouvement d'un rouleau libre (3) d'une presse à rouleaux haute pression (1), la presse à rouleaux haute pression (1) présentant un système hydraulique (8) qui presse le rouleau libre (3) contre un rouleau fixe (2) et maintient ainsi une pression d'écartement entre rouleaux prédéfinie dans l'écartement entre rouleaux (7) entre le rouleau libre (3) et le rouleau fixe (2), lorsque la matière broyée franchit l'écartement entre rouleaux (7) entre le rouleau libre (3) et le rouleau fixe (2). L'invention se caractérise par l'utilisation d'une régulation d'amortissement adaptative qui contrôle l'amortissement d'un mouvement d'oscillation du rouleau libre. L'invention concerne en outre une presse à rouleaux haute pression comportant une telle régulation d'amortissement adaptative.
EP21716098.5A 2020-04-17 2021-03-25 Procédé de régulation de l'amortissement du mouvement d'un rouleau presseur d'une presse à rouleaux haute pression et presse à rouleaux haute pression correspondante Pending EP4135900A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020110468.5A DE102020110468A1 (de) 2020-04-17 2020-04-17 Verfahren zur Regelung der Dämpfung der Bewegung einer Presswalze einer Hochdruckwalzenpresse und korrespondierende Hochdruckwalzenpresse
PCT/EP2021/057691 WO2021209236A1 (fr) 2020-04-17 2021-03-25 Procédé de régulation de l'amortissement du mouvement d'un rouleau presseur d'une presse à rouleaux haute pression et presse à rouleaux haute pression correspondante

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EP4135900A1 true EP4135900A1 (fr) 2023-02-22

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EP21716098.5A Pending EP4135900A1 (fr) 2020-04-17 2021-03-25 Procédé de régulation de l'amortissement du mouvement d'un rouleau presseur d'une presse à rouleaux haute pression et presse à rouleaux haute pression correspondante

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EP (1) EP4135900A1 (fr)
CN (1) CN115734822A (fr)
DE (1) DE102020110468A1 (fr)
WO (1) WO2021209236A1 (fr)

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CN116969449B (zh) * 2023-09-22 2023-12-08 云南欣城防水科技有限公司 一种石墨烯压延设备

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2708053C3 (de) 1977-02-24 1986-05-07 Schönert, Klaus, Prof. Dr.-Ing., 7500 Karlsruhe Verfahren zur Fein- und Feinstzerkleinerung von Materialien spröden Stoffverhaltens
DE3743141A1 (de) * 1987-12-18 1989-06-29 Krupp Polysius Ag Gutbett-walzenmuehle
FR2692171B1 (fr) * 1992-06-16 1996-05-15 Broyeurs Poittemill Sa Perfectionnements aux procedes et dispositifs de broyage de matieres solides, tels que des minerais.
DE4414366A1 (de) 1994-04-25 1995-10-26 Krupp Polysius Ag Verfahren zur Regelung des Hydraulikdrucks
DE19647483B4 (de) 1996-11-16 2007-05-24 Khd Humboldt Wedag Gmbh Zweiwalzenmaschine und Verfahren zu ihrem Betrieb
DE10106856A1 (de) * 2001-02-14 2002-09-05 Koeppern & Co Kg Maschf Verfahren zum Betrieb von Gutbettzerkleinerungs-Hochdruckwalzenpressen
DE10132067A1 (de) 2001-07-05 2003-01-16 Buehler Ag Verfahren zur Betriebszustandsüberwachung von Walzenstühlen
CA2456566C (fr) 2003-01-31 2008-12-02 Universidad Tecnica Federico Santa Maria Dispositif et methode de mesure et de classement des chocs dans un broyeur rotatif pour mineraux
RU2337756C1 (ru) 2007-01-31 2008-11-10 Константин Евсеевич Белоцерковский Способ управления технологическими параметрами конусной дробилки
DE102007059072A1 (de) 2007-12-07 2009-06-10 Khd Humboldt Wedag Gmbh Rollenpresse mit zwei Losrollen
DE102011018705C5 (de) 2011-04-26 2020-03-26 Khd Humboldt Wedag Gmbh Verfahren zur Regelung des Walzenspaltdrucks einer Rollenpresse und Rollenpresse

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WO2021209236A1 (fr) 2021-10-21
CN115734822A (zh) 2023-03-03
DE102020110468A1 (de) 2021-10-21

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