WO2022019315A1 - 潤滑状態推定装置及び方法、滑り軸受装置、機械装置、並びに旋動式破砕機 - Google Patents

潤滑状態推定装置及び方法、滑り軸受装置、機械装置、並びに旋動式破砕機 Download PDF

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WO2022019315A1
WO2022019315A1 PCT/JP2021/027231 JP2021027231W WO2022019315A1 WO 2022019315 A1 WO2022019315 A1 WO 2022019315A1 JP 2021027231 W JP2021027231 W JP 2021027231W WO 2022019315 A1 WO2022019315 A1 WO 2022019315A1
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Prior art keywords
index
lubrication
lubrication state
bearing
sliding surface
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PCT/JP2021/027231
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English (en)
French (fr)
Japanese (ja)
Inventor
寿恭 佐藤
健介 木本
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川崎重工業株式会社
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Priority to JP2022538030A priority Critical patent/JP7506748B2/ja
Publication of WO2022019315A1 publication Critical patent/WO2022019315A1/ja

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C2/00—Crushing or disintegrating by gyratory or cone crushers
    • B02C2/02—Crushing or disintegrating by gyratory or cone crushers eccentrically moved
    • B02C2/04—Crushing or disintegrating by gyratory or cone crushers eccentrically moved with vertical axis
    • B02C2/06—Crushing or disintegrating by gyratory or cone crushers eccentrically moved with vertical axis and with top bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
    • F16C17/24—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with devices affected by abnormal or undesired positions, e.g. for preventing overheating, for safety
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N29/00—Special means in lubricating arrangements or systems providing for the indication or detection of undesired conditions; Use of devices responsive to conditions in lubricating arrangements or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N29/00—Special means in lubricating arrangements or systems providing for the indication or detection of undesired conditions; Use of devices responsive to conditions in lubricating arrangements or systems
    • F16N29/04—Special means in lubricating arrangements or systems providing for the indication or detection of undesired conditions; Use of devices responsive to conditions in lubricating arrangements or systems enabling a warning to be given; enabling moving parts to be stopped
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M13/00—Testing of machine parts
    • G01M13/04—Bearings

Definitions

  • the present disclosure relates to a technique for estimating the lubrication state of the sliding surfaces of two relative moving objects.
  • Patent Documents 1 and 2 propose a technique for preventing abnormal wear and seizure in a bearing device.
  • Patent Document 1 in a slide bearing composed of a bearing metal on which a lubricating film is formed and a bearing support portion that holds the bearing metal, a temperature sensor detects the temperature around the bearing metal, and the temperature rise is based on the temperature rise. It is disclosed to know the poor lubrication.
  • Patent Document 2 describes shaft vibration by an overcurrent type sensor, bearing box vibration by a piezoelectric type acceleration sensor, and a rotating shaft as a method for determining the presence or absence of rubbing (contact between a rotating part and a stationary part) in a slide bearing or the like. It is disclosed that an acoustic signal or the like generated when the bearing comes into contact with the bearing is used. Further, in Patent Document 2, the waveform data representing the acceleration of vibration generated during the operation of the sliding bearing and the axial rotation cycle of the sliding bearing are detected, and the acceleration waveform data is Fourier transformed to obtain the acceleration spectrum in the frequency domain. It is disclosed that the presence or absence of an abnormality in a sliding bearing is determined based on waveform data obtained by cepstrum analysis of an acceleration spectrum.
  • the Stribeck curve is used to explain the lubrication state between two surfaces having relative motion.
  • the Stribeck curve exemplified in FIG. 1 shows the friction coefficient f, the viscosity ⁇ of the lubricating film, the sliding speed v of the sliding surface, and the pressing load of the sliding surface on the sliding surfaces of two objects that move relative to each other.
  • the relationship with the physical quantity S * (S * ⁇ v / F), which is a combination of the three elements of F, is shown.
  • the Stribeck curve shows how the characteristics of the friction coefficient change as the lubrication state changes from fluid lubrication to boundary lubrication through mixed lubrication.
  • a lubricating film that is sufficiently thicker than the surface roughness is interposed between the sliding surfaces, and the sliding surfaces are completely separated by a continuous lubricating film.
  • the lubricating film becomes thinner than fluid lubrication, and the convex portions of the sliding surface come into local contact with each other.
  • boundary lubrication the lubricating film is thinner than that in mixed lubrication, and the convex portions of the sliding surfaces are brought into contact with each other via the molecular level lubricating film.
  • the present disclosure has been made in view of the above circumstances, and the purpose of the present disclosure is to estimate the lubrication state of the sliding surfaces of two objects that move relative to each other, thereby preventing seizure of the sliding surfaces. There is something in it.
  • the inventors of the present application have determined the positive and negative of the time change rate of the friction coefficient f of the sliding surface and the time change rate of the physical quantity S * after the lubrication state changes from fluid lubrication to mixed lubrication and before the transition to boundary lubrication.
  • the lubrication state estimation device is a lubrication state estimation device that estimates the lubrication state of the sliding surfaces of two objects that move relative to each other.
  • It comprises at least one memory in which a program executed by the processor is stored.
  • the friction coefficient of the sliding surface or an index that correlates with the friction coefficient is used as the first index.
  • S * ⁇ v / F (where ⁇ is the viscosity of the lubricant intervening in the sliding surface, v is the sliding speed of the sliding surface, and F is the pressing load of the sliding surface) .
  • the index that correlates with the physical quantity S * is used as the second index.
  • the processor acquires the first index and the second index, and based on the correlation between the positive / negative of the time change rate of the first index and the positive / negative of the time change rate of the second index, the sliding surface of the sliding surface. It estimates the lubrication state.
  • the lubrication state estimation method is a lubrication state estimation method for estimating the lubrication state of the sliding surfaces of two objects having relative motions.
  • F is a physical quantity S * or the physical quantity S * an index correlated with second indicator represented by pressing load) of the sliding surface, Acquiring the first index and the second index, and It includes estimating the lubrication state of the sliding surface based on the correlation between the positive / negative of the time change rate of the first index and the positive / negative of the time change rate of the second index.
  • the correlation between the positive / negative of the time change rate of the first index and the positive / negative of the time change rate of the second index differs depending on whether the lubrication state of the sliding surface is fluid lubrication or mixed lubrication.
  • fluid lubrication is performed based on the change in the correlation between the positive / negative of the time change rate of the first index and the positive / negative of the time change rate of the second index.
  • the lubrication state of the moving surface can be estimated. Then, by using this estimation result, it is possible to grasp the sign before the lubrication state shifts to the boundary lubrication and seizure or the like occurs. Then, by performing a process for preventing seizure or the like at the timing when a sign of seizure or the like is caught, seizure or the like can be prevented in advance.
  • the above lubrication state estimation device and method it is sufficient to know the positive and negative of the time change rate for the first index and the second index, so that the exact values of the first index and the second index are not required. Therefore, according to the above-mentioned lubrication state estimation device and method, it is possible to estimate the lubrication state of the sliding surface of two objects having relative motion in an actual machine in which it is difficult to measure an exact value.
  • the lubrication state estimation device is a lubrication state estimation device that estimates the lubrication state of the sliding surface between the rotating shaft and the bearing.
  • It comprises at least one memory in which a program executed by the processor is stored.
  • the shaft torque of the rotating shaft or an index that correlates with the shaft torque is used as the third index
  • the pressing load of the sliding surface or the index that correlates with the pressing load is used as the fourth index.
  • the processor acquires the third index and the fourth index, and plots the acquired third index and the fourth index on a chart in which the vertical axis represents the third index and the horizontal axis represents the fourth index.
  • the lubrication state estimation method is a lubrication state estimation method for estimating the lubrication state of the sliding surface between the rotating shaft and the bearing, and is the shaft torque of the rotating shaft or the shaft.
  • the index that correlates with the torque is used as the third index
  • the pressing load on the sliding surface or the index that correlates with the pressing load is used as the fourth index
  • the third index and the fourth index are acquired
  • the vertical axis is used.
  • the slope of the tangent line of the TF line is substantially constant or decreases as the pressing load F increases, and the intercept of the tangent line of the TF line is 0 or a positive value.
  • the slope of the tangent line of the TF line increases as the pressing load F increases (that is, the ratio of boundary lubrication in the mixed lubrication increases), and the intercept of the tangent line of the TF line becomes 0 or negative. It is known to be the value of.
  • the lubrication state of the sliding surface is estimated based on the inclination of the tangent line of the TF line and the section of the tangent line, and before seizure occurs. You can catch the sign. Then, by performing a process for preventing seizure or the like at the timing when a sign of seizure or the like is caught, seizure or the like can be prevented in advance.
  • the above-mentioned lubrication state estimation device and method it is sufficient to know the positive / negative of the slope of the tangent of the TF line and the positive / negative of the intercept of the tangent of the TF line. No value is required. Therefore, according to the above-mentioned lubrication state estimation device and method, it is possible to estimate the lubrication state of the sliding surface between the rotating shaft and the bearing in an actual machine in which it is difficult to measure an exact value.
  • the rotary crusher is a rotary crusher. Concave and With the spindle placed inside the concave, The mantle provided on the spindle and An eccentric sleeve in which the lower part of the spindle is rotatably inserted, With the boss into which the eccentric sleeve is rotatably inserted, A drive shaft that rotationally drives the eccentric sleeve, A drive motor that rotates and drives the drive shaft, A hydraulic cylinder that supports the spindle so that it can be raised and lowered, A first fluid lubricated bearing formed between the spindle and the eccentric sleeve, A second fluid lubricated bearing formed between the eccentric sleeve and the boss, Boundary lubrication bearings formed between the spindle and the hydraulic cylinder, A function that correlates with ⁇ the shaft power of the drive shaft or an index that correlates with the shaft power / the cylinder pressure of the hydraulic cylinder or the index that correlates with the cylinder pressure ⁇ is
  • a function that correlates with ⁇ 1 / the cylinder pressure or an index that correlates with the cylinder pressure ⁇ is used as the sixth index, and at least one sixth index measuring instrument that measures the sixth index. It is provided with a lubrication state estimation device that estimates the lubrication state of the first fluid lubrication bearing, the second fluid lubrication bearing, and the boundary lubrication bearing based on the rate of change of the fifth index with respect to the sixth index.
  • a concave, a main shaft arranged inside the concave, a mantle provided on the main shaft, and a lower portion of the main shaft are rotatable.
  • the inserted eccentric sleeve, the boss into which the eccentric sleeve is rotatably inserted, the drive shaft for rotationally driving the eccentric sleeve, the drive motor for rotationally driving the drive shaft, and the spindle are movably supported.
  • the function that correlates with ⁇ the shaft power of the drive shaft or the index that correlates with the shaft power / the cylinder pressure of the hydraulic cylinder or the index that correlates with the cylinder pressure ⁇ is used as the fifth index.
  • the function that correlates with ⁇ 1 / the cylinder pressure or the index that correlates with the cylinder pressure ⁇ is used as the sixth index.
  • Lubrication of the first fluid lubricated bearing, the second fluid lubricated bearing, and the boundary lubricated bearing based on the acquisition of the fifth index and the sixth index and the rate of change of the fifth index with respect to the sixth index. It involves estimating the state.
  • the lubrication state of the fluid lubrication bearing and the boundary lubrication bearing can be estimated individually by one device, and thereby it is possible to estimate where the seizure sign is occurring. ..
  • the lubrication state of the fluid lubrication bearing and the boundary lubrication bearing is estimated individually in a series of processes, and thereby, where the seizure sign is generated is estimated. be able to. That is, it is not necessary to individually estimate the lubrication state of the fluid-lubricated bearing and the boundary-lubricated bearing.
  • FIG. 1 is a Stribeck diagram.
  • FIG. 2 is a diagram showing a journal slide bearing model used in Verification 1.
  • FIG. 3 is a chart showing the results of verification 1.
  • FIG. 4 is a diagram showing a thrust slide bearing model used in verification 2.
  • FIG. 5A is a chart showing the results of the simulation of verification 2.
  • FIG. 5B is a chart showing the results of the element test of verification 2.
  • FIG. 6 is a block diagram showing a schematic configuration of the lubrication state estimation system according to the first embodiment of the present disclosure.
  • FIG. 7 is a flowchart illustrating a processing flow of the lubrication state estimation device.
  • FIG. 8 is a flowchart illustrating a modified example of the processing flow of the lubrication state estimation device.
  • FIG. 7 is a flowchart illustrating a processing flow of the lubrication state estimation device.
  • FIG. 9 is a conversion of the Stribeck diagram shown in FIG. 1 into a TF diagram.
  • FIG. 10 is a chart showing the results of verification 3.
  • FIG. 11 is a chart showing the change in the slope of the tangent line of the curve drawn in the chart of FIG.
  • FIG. 12 is a chart showing changes in the values of the sections of the curves drawn in the chart of FIG.
  • FIG. 13 is a block diagram showing a schematic configuration of the lubrication state estimation system according to the second embodiment of the present disclosure.
  • FIG. 14 is a flowchart illustrating a processing flow of the lubrication state estimation device.
  • FIG. 15 is a third index-4th index diagram in which the third index and the fourth index are plotted.
  • FIG. 16 is a diagram showing a plain bearing device including a lubrication state estimation system.
  • FIG. 17 is a diagram showing a mechanical device including a lubrication state estimation system.
  • FIG. 18 is a diagram showing a schematic configuration of a rotary crusher used in an actual machine simulated test.
  • FIG. 19 is a chart showing the results of an actual machine mock test.
  • FIG. 20A is a 5th index-6th index diagram of the lower bearing.
  • FIG. 20B is a 5th index-6th index diagram of the spindle thrust bearing.
  • FIG. 21 is a block diagram showing a schematic configuration of the lubrication state estimation system according to the third embodiment of the present disclosure.
  • FIG. 22 is a flowchart illustrating a processing flow of the lubrication state estimation device.
  • the sliding conditions of the sliding surface change with the passage of time. For example, it is assumed that the load F applied to the sliding surface increases, the sliding speed v of the sliding surface decreases, or the viscosity ⁇ of the lubricant decreases with the passage of time.
  • the physical quantity S * gradually decreases with time as the sliding conditions. That is, if the rate of change of the physical quantity S * with the change of the sliding condition is negative, the lubrication state of the sliding surface advances on the Stribeck curve toward the left side of the chart with the passage of time.
  • the time change rate of the physical quantity S * is negative (decrease)
  • the time change rate of the friction coefficient f is negative (decrease).
  • Such matching between the positive and negative of the time change rate of the friction coefficient f and the positive and negative of the time change rate of the physical quantity S * is hereinafter referred to as "positive correlation”.
  • the time change rate of the physical quantity S * is negative (decrease)
  • the time change rate of the friction coefficient f is positive (increase).
  • Such a positive / negative of the time change rate of the friction coefficient f and a positive / negative of the time change rate of the physical quantity S * are hereinafter referred to as “negative correlation”.
  • Table 1 shows the correlation between the positive / negative of the time change rate of the friction coefficient f and the positive / negative of the time change rate of the physical quantity S * (hereinafter, simply referred to as “correlation between the friction coefficient f and the physical quantity S *”).
  • the friction coefficient f may be replaced with the first index (friction coefficient f or an index correlating with the friction coefficient), and the physical quantity S * may be replaced with the second index (physical quantity S * or an index correlating with the S *).
  • the change in the lubrication state of the sliding surface can be similarly detected from the change in the correlation between these two indexes.
  • the correlation of the "correlation index” may be either a positive correlation or a negative correlation.
  • Tables 2 to 5 show the correlation between the positive / negative of the time change rate of the first index and the positive / negative of the time change rate of the second index (hereinafter, simply referred to as "correlation between the first index and the second index"). ..
  • the first index may be the friction coefficient f and the second index may be the physical quantity S * .
  • Table 3 is applicable, for example, when the first index is the friction coefficient f and the second index is ⁇ 1 / physical quantity S * ⁇ .
  • Table 4 applies, for example, to the case where the first index is ⁇ 1 / friction coefficient f ⁇ and the second index is the physical quantity S *.
  • Table 5 is applicable, for example, when the first index is ⁇ 1 / friction coefficient f ⁇ and the second index is ⁇ 1 / physical quantity S * ⁇ .
  • FIG. 2 is a diagram showing a journal plain bearing model used in the simulation of verification 1.
  • a rotating shaft 41 is inserted into the journal sliding bearing 42, and a lubricating film 43 made of a lubricant is formed between the inner circumference of the journal sliding bearing 42 and the outer periphery of the rotating shaft 41.
  • the rotary shaft 41 is rotated under the condition that the rotational speed of the rotary shaft 41 is constant and the viscosity ⁇ of the lubricant decreases with time as the temperature of the lubricant rises. Further, the friction coefficient f and the change with time of the bearing load when the pressing load F on the bearing was changed with time were obtained by simulation.
  • the rotation speed of the rotating shaft 41 is a physical quantity corresponding to the sliding speed v of the sliding surface
  • the bearing load is a physical quantity corresponding to the pressing load F of the sliding surface.
  • the correlation between the positive and negative of the time change rate of the friction coefficient f and the positive and negative of the time change rate of the pressing load F (hereinafter, simply referred to as "correlation between the friction coefficient f and the pressing load F") is negative. Show the correlation.
  • the pressing load F and the friction coefficient f fluctuate periodically under mixed lubrication, and the cycles are equal and have the same phase. More specifically, under mixed lubrication, the friction coefficient f increases while the pressing load F increases, and the friction coefficient f decreases while the pressing load F decreases. That is, under mixed lubrication, the correlation between the friction coefficient f and the pressing load F shows a positive correlation.
  • the first index (friction coefficient f) is the second index with respect to the time change rate.
  • Relative ratio of the time change rate of the second index time change rate of the second index / time change rate of the first index
  • the relative ratio of the amplitude of the second index to the amplitude of the first index amplitude of the second index / the first index.
  • the relative ratio of the time change rate of the second index to the time change rate of the first index, and The relative ratio of the amplitude of the second index to the amplitude of the first index changes in the increasing direction. Further, as the ratio of boundary lubrication increases, the relative ratio of the time change rate of the second index to the time change rate of the first index and the relative ratio of the amplitude of the second index to the amplitude of the first index become smaller again. It changes in the direction of becoming.
  • FIG. 4 is a diagram showing a thrust slide bearing model used in the element test and simulation of verification 2.
  • a lubricating film 46 made of a lubricant is formed between a thrust bearing 45 and a rotating disk 44 supported by the thrust bearing 45.
  • the rotational speed of the rotating disk 44 is kept constant
  • the viscosity ⁇ of the lubricant is kept constant by temperature control
  • the pressing load F on the bearing is changed periodically while increasing. The changes over time in the friction coefficient f and the pressing load F at the time were obtained.
  • the rotation speed of the rotating disk 44 is a physical quantity corresponding to the sliding speed v of the sliding surface
  • the bearing load is a physical quantity corresponding to the pressing load F of the sliding surface.
  • the chart (simulation result) of FIG. 5A shows the change over time in the pressing load F (bearing load) on the sliding surface and the change over time in the friction coefficient f. From this chart, it can be read that the pressing load F and the friction coefficient f fluctuate periodically under fluid lubrication, the periods are equal, and the phase difference is half a period. More specifically, under fluid lubrication, the coefficient of friction f decreases while the pressing load F increases, and the coefficient of friction increases while the pressing load F decreases. That is, under fluid lubrication, the correlation between the friction coefficient f and the pressing load F shows a negative correlation.
  • the pressing load F and the friction coefficient f fluctuate periodically under mixed lubrication, and the cycles are equal and have the same phase. More specifically, under mixed lubrication, the friction coefficient f increases while the pressing load F increases, and the friction coefficient f decreases while the pressing load F decreases. That is, under mixed lubrication, the correlation between the friction coefficient f and the pressing load F shows a positive correlation.
  • FIG. 5B is a chart of the results of the element test. Similar to the simulation result of FIG. 5A, it was confirmed that the correlation between the friction coefficient f and the pressing load F was established in the element test. In the element test, there are no sliding marks (wear marks) on the sliding surface in fluid lubrication, and in the test conditions where the pressing load F is increased until mixed lubrication, the sliding marks (wear) remaining on the sliding surface. By confirming the marks), the actual sliding state was judged, and the validity of the simulation was confirmed.
  • the first index (friction coefficient f) is the second index with respect to the time change rate.
  • the relative ratio of the time change rate of (pressing load F) and the relative ratio of the amplitude of the second index to the amplitude of the first index change in a smaller direction.
  • the relative ratio of the time change rate of the second index to the time change rate of the first index, and The relative ratio of the amplitude of the second index to the amplitude of the first index changes in the increasing direction.
  • the relative ratio of the time change rate of the second index to the time change rate of the first index and the relative ratio of the amplitude of the second index to the amplitude of the first index can be estimated, and the ratio of boundary lubrication to mixed lubrication can be estimated under mixed lubrication.
  • the lubrication state of the sliding surface is estimated based on whether the correlation between the friction coefficient f and the physical quantity S * is a positive correlation or a negative correlation. However, it is regarded as a sign of seizure of the sliding surface.
  • Lubrication state estimation may include estimation of fluid lubrication or mixed lubrication. To estimate the lubrication state, it is estimated that the lubrication state has changed from fluid lubrication to mixed lubrication based on the change in the correlation between the friction coefficient f and the physical quantity S * from a positive correlation to a negative correlation. May be included.
  • the estimation of the lubrication state may include estimating the degree of fluid lubrication and mixed lubrication.
  • FIG. 6 is a block diagram showing a schematic configuration of the lubrication state estimation system 50 according to the first embodiment of the present disclosure.
  • the lubrication state estimation system 50 shown in FIG. 6 includes an index measuring device 51 including a first index measuring device 51a for measuring the first index and a second index measuring device 51b for measuring the second index, and a lubrication state estimating device 53. including.
  • the index measuring device 51 includes at least one type of measuring device for measuring the first index, the second index, or the physical quantity which is a component thereof.
  • the first index measuring instrument 51a and the second index measuring instrument 51b may include a common measuring instrument.
  • the first index measuring instrument 51a and the second index measuring instrument 51b are appropriately selected from various instruments according to the physical quantity to be measured.
  • the first index is an index that correlates with the friction coefficient f or the friction coefficient f of the sliding surfaces of two objects that make relative motion.
  • the "index that correlates with the friction coefficient f" is an index that corresponds to the positive and negative of the friction coefficient f and the time change rate.
  • the positive and negative of the time change rate correspond includes the case where the positive and negative of the time change rate match and the case where the positive and negative of the time change rate are opposite.
  • the first index may be an index composed of one kind of physical quantity or an index composed of a combination of two or more kinds of physical quantities. As the first index, it is sufficient to know the positive or negative of the time change rate, so a quantitative and accurate value is not required.
  • the second index is the physical quantity of the sliding surfaces of the two objects to the relative movement S *, or is an index correlated with the physical quantity S *.
  • the "index that correlates with the physical quantity S * " is an index in which the positive and negative of the physical quantity S * and the time change rate correspond to each other.
  • the components of the second index include the viscosity ⁇ of the lubricant intervening in the sliding surface, the sliding speed v of the sliding surface, the pressing load F of the sliding surface, or the physical quantity correlating with them. good.
  • the second index it is sufficient to know the positive or negative of the time change rate, so a quantitative and accurate value is not required. Therefore, the viscosity ⁇ of the lubricant may be replaced by the temperature of the lubricant, or the sliding speed v of the sliding surface may be replaced by the rotation speed.
  • the lubrication state estimation device 53 is a so-called computer, and includes at least one processor and at least one memory in which a program executed by the processor is stored. In addition to the program executed by the processor, various fixed data and the like are stored in the memory.
  • the processor sends and receives data to and from an external device.
  • the processor reads and executes software such as a program stored in the memory, so that the process described later is performed.
  • the lubrication state estimation device 53 may execute each process by centralized control by a single computer, or may execute each process by the cooperation of a plurality of computers.
  • FIG. 7 is a flowchart illustrating a processing flow of the lubrication state estimation device 53.
  • the lubrication state estimation device 53 acquires the first index and the second index from the index measuring device 51 (step S1). Then, the lubrication state estimation device 53 determines the correlation between the positive / negative of the time change rate of the first index and the positive / negative of the time change rate of the second index (hereinafter, simply referred to as "correlation between the first index and the second index"). Obtain (step S2).
  • the lubrication state estimation device 53 determines whether the lubrication state of the sliding surface is fluid lubrication or mixed lubrication based on whether the correlation between the first index and the second index is a positive correlation or a negative correlation (step). S3).
  • the lubrication state estimation device 53 estimates the degree of fluid lubrication. Specifically, the lubrication state estimation device 53 relates to the relative ratio of the time change rate of the second index to the time change rate of the first index, and the amplitude of the first index when the second index changes periodically. At least one of the relative ratios of the amplitudes of the second index is obtained (step S4). The lubrication state estimation device 53 evaluates the soundness of fluid lubrication based on the obtained relative ratio (step S5).
  • the lubrication state estimation device 53 estimates the lubrication film thickness based on the obtained relative ratio, compares the estimated lubrication film thickness with a predetermined threshold value, and if the lubrication film thickness is equal to or greater than the threshold value. Evaluate that the fluid lubrication is sound. Information for specifying the relationship between the relative ratio and the lubrication film thickness is stored in advance in the lubrication state estimation device 53, and the lubrication state estimation device 53 can estimate the lubrication film thickness from the relative ratio using this information. .. Further, the threshold value regarding the lubrication film thickness may be appropriately set according to the sliding surface.
  • step S5 If the fluid lubrication is sound (YES in step S5), the process returns to S1 and is repeated. If the fluid lubrication is not sound (NO in step S5), the lubrication state estimation device 53 outputs a warning from the connected alarm device (not shown) (step S6), and returns the process to step S1. It should be noted that this warning does not notify the detection of a sign of seizure, but merely notifies that the thickness of the lubricating film forming the fluid lubrication is decreasing (approaching mixed lubrication). However, the worker can receive the warning and take appropriate measures.
  • the lubrication state estimation device 53 estimates the degree of mixed lubrication. Specifically, the lubrication state estimation device 53 relates to the relative ratio of the time change rate of the second index to the time change rate of the first index, and the amplitude of the first index when the second index changes periodically. At least one of the relative ratios of the amplitudes of the second index is obtained (step S11). Then, the lubrication state estimation device 53 determines whether or not the seizure risk is low based on the obtained relative ratio (step S12).
  • the lubrication state estimation device 53 estimates the ratio of boundary lubrication to the mixed lubrication based on the obtained relative ratio, compares the ratio of boundary lubrication with a predetermined threshold value, and the ratio of boundary lubrication is the threshold value. If it is larger, it is judged that the seizure risk is high, and if the boundary lubrication ratio is below the threshold, it is judged that the seizure risk is low.
  • Information for specifying the relationship between the relative ratio and the ratio of boundary lubrication to mixed lubrication is stored in advance in the lubrication state estimation device 53, and the lubrication state estimation device 53 uses this information to calculate the ratio of boundary lubrication from the relative ratio. Can be estimated.
  • the threshold value regarding the ratio of boundary lubrication is a value at which seizure does not occur and a value that can secure a sufficient time until seizure occurs is appropriately set according to the sliding surface. It's okay.
  • the threshold value regarding the ratio of boundary lubrication in this way, the sign of seizure is not detected in the light mixed lubrication, and misdiagnosis can be avoided.
  • light mixed lubrication has sufficient margin for seizure, and it may not be necessary to take immediate action. Therefore, by setting the threshold value in consideration of the operating condition of two objects including the sliding surface (for example, shaft and bearing) and the influence when damage occurs, processing to prevent seizure etc. is performed. It is possible to determine when to start.
  • the lubrication state estimation device 53 determines that the seizure risk is low (YES in step S12), it outputs a warning from the connected alarm device (not shown) (step S13), and returns the process to step S1. It should be noted that this warning does not notify the detection of a sign of seizure, but merely notifies that the lubrication state is mixed lubrication, but the operator may receive the warning and take appropriate measures. can.
  • the lubrication state estimation device 53 determines that the seizure risk is high (NO in step S12), it detects it as a sign of seizure (step S14) and outputs an alarm from the connected alarm device (not shown). (Step S15). This alarm notifies the detection of a sign of seizure. Further, the lubrication state estimation device 53 outputs a command signal for operating the machine to perform a predetermined process after detecting a sign of seizure, or displays and outputs the content of the process on a monitor (not shown). (Step S16), the process may be terminated.
  • the predetermined treatment may include the addition of a lubricant, the reduction of the pressing load F, and the suspension of relative motion at least one of them.
  • FIG. 8 is a flowchart illustrating a modified example of the processing flow of the lubrication state estimation device 53.
  • step S4 and step S5 are omitted and it is determined in step S3 that fluid lubrication is performed, the process returns to S1 and is repeated.
  • step S13 is omitted and it is determined in step S12 that the seizure risk is low, the process returns to S1 and is repeated, which is different from the process flow shown in FIG. 7. Due to these differences, the processing flow shown in FIG. 8 is simpler than the processing flow shown in FIG. 7, and the sign of seizure is detected only when the mixed lubrication is clearly in progress. Will be done.
  • the lubrication state estimation device 53 includes at least one processor and at least one memory in which a program executed by the processor is stored, and the processor is a first index and a first index.
  • the second index is acquired, and the sliding surface is based on the correlation between the first index and the second index (that is, the positive / negative of the time change rate of the first index and the positive / negative of the time change rate of the second index).
  • the first index is an index that correlates with the friction coefficient f of the sliding surface or the friction coefficient f
  • the viscosity of the agent v is the sliding speed of the sliding surface
  • F is an index correlated with the physical quantity S * or the physical quantity S * represented by pressing load) of the sliding surface.
  • the sliding surface is obtained based on the acquisition of the first index and the second index and the correlation between the first index and the second index. Includes estimating the lubrication state of.
  • the correlation between the positive / negative of the time change rate of the first index and the positive / negative of the time change rate of the second index differs depending on whether the lubrication state of the sliding surface is fluid lubrication or mixed lubrication.
  • the lubrication state of the sliding surface is determined based on the correlation between the positive / negative of the time change rate of the first index and the positive / negative of the time change rate of the second index. Whether it is fluid lubrication or mixed lubrication, and its transition can be estimated. Then, by using this estimation result, it is possible to catch the sign before seizure or the like occurs. Then, by performing a process for preventing seizure or the like at the timing when a sign of seizure or the like is caught, seizure or the like can be prevented in advance.
  • the lubrication state estimation device 53 and the method it is sufficient to know the positive and negative of the time change rate for the first index and the second index, so that the exact values of the first index and the second index are not required. Therefore, according to the lubrication state estimation device 53 and the method, it is possible to estimate the lubrication state of the sliding surface of two objects having relative motion in an actual machine in which it is difficult to measure an exact value.
  • the processor estimates that the sliding surface is fluid lubrication
  • the relative ratio of the time change rate of the second index to the time change rate of the first index the relative ratio of the time change rate of the second index to the time change rate of the first index
  • the soundness of the fluid lubrication of the sliding surface is evaluated based on at least one of the relative ratios of the amplitude of the second index to the amplitude of the first index when the second index changes periodically.
  • the processor estimates that the sliding surface is mixed lubrication
  • the relative ratio of the time change rate of the second index to the time change rate of the first index is estimated based on at least one of the relative ratios of the amplitude of the second index to the amplitude of the first index when the second index changes periodically.
  • the relative ratio of the time change rate of the second index to the time change rate of the first index when the sliding surface is estimated to be fluid lubrication under mixed lubrication, the relative ratio of the time change rate of the second index to the time change rate of the first index.
  • the integrity of fluid lubrication of sliding surfaces based on at least one of the relative ratios of the amplitude of the second index to the amplitude of the first index when the second index changes periodically.
  • the relative ratio of the time change rate of the second index to the time change rate of the first index and the second index when the sliding surface is estimated to be mixed lubrication, the relative ratio of the time change rate of the second index to the time change rate of the first index and the second index. Further includes estimating the ratio of boundary lubrication to the mixed lubrication of the sliding surface based on at least one of the relative ratios of the amplitude of the second index to the amplitude of the first index when the number changes periodically.
  • the soundness of (thickness) can be evaluated, and the ratio of boundary lubrication to mixed lubrication can be estimated under mixed lubrication. Therefore, by estimating the soundness of the fluid lubrication of the sliding surface and the ratio of the boundary lubrication to the mixed lubrication based on the above relative ratio, the operation of two objects including the sliding surface (for example, a shaft and a bearing) can be operated. It is possible to determine the timing to start the process for preventing seizure, etc., in consideration of the condition and the influence when damage occurs.
  • FIG. 9 is a conversion of the Stribeck diagram shown in FIG. 1 into a TF diagram under conditions where the viscosity ⁇ and the sliding speed v are constant.
  • the vertical axis represents the shaft torque T
  • the horizontal axis represents the pressing load F.
  • a TF line showing the relationship between the shaft torque T and the pressing load F is drawn.
  • the slope of the tangent line of the TF line decreases or is almost constant with increasing pressing load F (see FIGS. 9 and 7), and the intercept of the tangent line of the TF line. Is 0 or a positive value and increases as the pressing load F increases.
  • the slope of the tangent to the TF line increases and the intercept decreases from positive to negative.
  • the slope of the tangent line of the TF line increases as the pressing load F increases (that is, the ratio of boundary lubrication in the mixed lubrication increases), and the intercept of the tangent line of the TF line becomes negative. It is a value of and decreases as the pressing load F increases.
  • the thickness of the lubricating film decreases as the pressing load F increases.
  • the ratio of boundary lubrication in mixed lubrication increases as the pressing load F increases.
  • Table 7 The characteristics of such TF lines are shown in Table 7 below.
  • FIG. 11 is a chart showing the change in the inclination of the tangent line of the line (T'-F line) drawn in the chart of FIG. 10
  • FIG. 12 is a chart showing the line (T'-F) drawn in the chart of FIG. It is a chart showing the change of the value of the intercept of the tangent line of the line).
  • the T'-F line obtained in Verification 3 is consistent with the ideal TF line shown in FIG. That is, when the lubrication state is fluid lubrication, the slope of the tangent line of the T'-F line is generally constant or decreases with respect to the increase in the pressing load F, and the intercept of the tangent line of the T'-F line is 0 or positive. It is a value of and is constant or increases as the pressing load F increases.
  • the slope of the tangent line of the T'-F line increases as the pressing load F increases, and the intercept of the tangent line of the T'-F line has a negative value and the pressing load F increases. It decreases remarkably according to. In this way, it was confirmed that the relationship between the index correlating with the shaft torque T (sliding drag force of the thrust bearing 45) and the pressing load F is also established in the element test.
  • the lubrication state estimation system 50A estimates the lubrication state of the sliding surface between the rotating shaft and the bearing by utilizing the characteristics of the TF line as described above.
  • the lubrication state estimation system 50A according to the present embodiment has at least one third index measuring instrument 51c for measuring the third index and at least one fourth index measuring device for measuring the fourth index. It is provided with an index measuring device 51 including the device 51d, and a lubrication state estimation device 53 that acquires a third index and a fourth index from the index measuring device 51 and estimates the lubrication state of the sliding surface using these.
  • the third index measuring instrument 51c and the fourth index measuring instrument 51d are appropriately selected from various instruments according to the physical quantity to be measured.
  • the third index measuring instrument 51c and the fourth index measuring instrument 51d may include a common measuring instrument.
  • the third index T' is an index that correlates with the shaft torque T or the shaft torque T of the rotating shaft.
  • the "index that correlates with the shaft torque T" is an index that corresponds to the positive and negative of the shaft torque T and the time change rate.
  • the fourth index F' is an index that correlates with the pressing load F or the pressing load F on the sliding surface of the rotating shaft and the bearing.
  • the "index that correlates with the pressing load F" is an index in which the positive and negative of the pressing load F and the time change rate correspond to each other.
  • Indexes that correlate with the pressing load F include, for example, the control value of the pressing load (bearing load), the hydraulic value of the hydraulic equipment that receives the pressing load F, and the drive current value of the motor that gives rotational power to the drive shaft that drives the rotary shaft. and so on.
  • the lubrication state estimation device 53 acquires the third index T'and the fourth index F'from the third index measuring device 51c and the fourth index measuring device 51d, and the vertical axis represents the third index T'and the horizontal axis represents the third index T'. Plot the acquired third index T'and fourth index F'on the T'-F'line diagram representing the fourth index F'is repeated at least twice, and the tangent line of the T'-F' line appearing in the chart. The slope of and the intercept of the tangent line are obtained. Then, the lubrication state estimation device 53 estimates the lubrication state of the sliding surface based on the combination of the inclination of the tangent line of the T'-F'line and the section of the tangent line.
  • the soundness of the fluid lubrication may be evaluated when it is estimated to be fluid lubrication, or the ratio of boundary lubrication to the mixed lubrication may be estimated when it is estimated to be mixed lubrication.
  • FIG. 14 is a flowchart illustrating a processing flow of the lubrication state estimation device 53.
  • the lubrication state estimation device 53 acquires the third index and the fourth index (or their components) from the index measuring device 51 (step S21). Then, in the lubrication state estimation device 53, the measured value of the third index T'and the fourth index F'are shown in a log-log graph in which the vertical axis represents the third index T'and the horizontal axis represents the fourth index F'. Plot the measured values (step S22).
  • a third index-fourth index line T'-F' line
  • FIG. 15 shows an example of the third index-4th index diagram.
  • the lubrication state estimation device 53 obtains the slope of the tangent line of the T'-F'line and the intercept of the tangent line (step S23). The lubrication state estimation device 53 determines whether or not the lubrication state of the sliding surface is fluid lubrication based on the combination of the inclination of the tangent line of the T'-F'line and the section of the tangent line (step S24). In order to determine whether or not the lubrication state of the sliding surface is fluid lubrication, the relationship between the T'-F'line and the lubrication state as shown in Table 7 stored in advance in the lubrication state estimation device 53 is used. Lubrication.
  • the lubrication state estimation device 53 estimates the degree of fluid lubrication. Specifically, the lubrication state estimation device 53 evaluates the soundness of fluid lubrication based on the value of the section of the tangential line of the T'-F'line (step S25). Here, the lubrication state estimation device 53 estimates the lubrication film thickness from the value of the section of the tangent line, compares the estimated lubrication film thickness with a predetermined threshold value, and if the lubrication film thickness is equal to or more than the threshold value, fluid lubrication is performed. Is evaluated as healthy.
  • Information for specifying the relationship between the value of the tangent section and the lubrication film thickness is stored in advance in the lubrication state estimation device 53, and the lubrication state estimation device 53 uses this information to obtain the lubrication film thickness from the value of the tangent section. Can be estimated. Further, the threshold value regarding the lubrication film thickness may be appropriately set according to the sliding surface.
  • step S25 If the fluid lubrication is sound (YES in step S25), the process returns to S21 and is repeated. If the fluid lubrication is not sound (NO in step S25), the lubrication state estimation device 53 outputs a warning from the connected alarm device (not shown) (step S26), and returns the process to step S21. It should be noted that this warning does not notify the detection of a sign of seizure, but merely notifies that the thickness of the lubricating film forming the fluid lubrication has decreased, but the operator warns the warning. It can be received and appropriate measures can be taken as needed.
  • the lubrication state estimation device 53 estimates the degree of mixed lubrication. Specifically, the lubrication state estimation device 53 determines whether or not the seizure risk is low based on the value of the tangential section of the TF line (step S27). Specifically, the lubrication state estimation device 53 estimates the ratio of boundary lubrication to the mixed lubrication based on the value of the section of the tangent line, compares the ratio of boundary lubrication with a predetermined threshold value, and determines the ratio of boundary lubrication.
  • the threshold value When it is larger than the threshold value, it is judged that the seizure risk is high, and when the ratio of boundary lubrication is less than the threshold value, it is judged that the seizure risk is low.
  • Information for specifying the relationship between the value of the tangent section and the ratio of boundary lubrication to the mixed lubrication is stored in advance in the lubrication state estimation device 53, and the lubrication state estimation device 53 uses this information to store the value of the tangent section.
  • the ratio of boundary lubrication can be estimated from.
  • the threshold value regarding the ratio of boundary lubrication is a value at which seizure does not occur and a value that can secure a sufficient time until seizure occurs is appropriately set according to the sliding surface. It's okay.
  • the threshold value regarding the ratio of boundary lubrication By setting the threshold value regarding the ratio of boundary lubrication in this way, the sign of seizure is not detected in the light mixed lubrication, and misdiagnosis can be avoided. In addition, light mixed lubrication has sufficient margin for seizure, and it may not be necessary to take immediate action. Therefore, by setting the threshold value in consideration of the operating condition of two objects including the sliding surface (for example, shaft and bearing) and the influence when damage occurs, processing to prevent seizure etc. is performed. It is possible to determine when to start.
  • the lubrication state estimation device 53 determines that the seizure risk is low (YES in step S27), it outputs a warning from the connected alarm device (not shown) (step S28), and returns the process to step S21. It should be noted that this warning does not notify the detection of a sign of seizure, but merely notifies that the lubrication state is mixed lubrication, but the operator may receive the warning and take appropriate measures. can.
  • the lubrication state estimation device 53 determines that the seizure risk is high (NO in step S27), it detects this as a sign of seizure (step S29) and outputs an alarm from the connected alarm device (not shown). (Step S30). This alarm notifies the detection of a sign of seizure. Further, the lubrication state estimation device 53 outputs a command signal for operating the machine to perform a predetermined seizure prevention process after detecting a sign of seizure, or displays the content of the process on a monitor (not shown). It may be output (step S31).
  • the predetermined treatment may include at least one of additional reduction of lubricant, reduction of pressing load F, and suspension of rotational motion.
  • the lubrication state estimation device 53 estimates the lubrication state of the sliding surface between the rotating shaft and the bearing, and is executed by at least one processor and the processor.
  • the third index T' is provided with at least one memory in which the program is stored, and the shaft torque of the rotating shaft or the index correlating with the shaft torque is set as the third index T', and the pushing load of the sliding surface or the index correlating with the pushing load is the third index.
  • the processor acquires the 3rd index T'and the 4th index F', and the vertical axis represents the 3rd index T'and the horizontal axis represents the 4th index F'.
  • Estimate the state To estimate the lubrication state, estimate whether it is fluid lubrication or mixed lubrication, evaluate the soundness of fluid lubrication when it is estimated to be fluid lubrication, and when it is estimated to be mixed lubrication. At least one of estimating the ratio of boundary lubrication to mixed lubrication may be included.
  • the lubrication state estimation method is a lubrication state estimation method for estimating the lubrication state of the sliding surface between the rotating shaft and the bearing, and obtains the shaft torque of the rotating shaft or an index that correlates with the shaft torque.
  • the third index T' is used, the pressing load on the sliding surface or the index that correlates with the pressing load is used as the fourth index F', and the third index T'and the fourth index F'are acquired, and the vertical axis is Plot the acquired third index T'and fourth index F'on the chart representing the third index T'and the horizontal axis representing the fourth index F'is repeated at least twice, and the line (T-) appearing in the chart.
  • the lubrication state of the sliding surface is estimated based on the inclination of the tangent line of the T'-F'line and the section of the tangent line, and the lubrication state is estimated before seizure occurs. You can catch the signs. Then, by performing a process for preventing seizure or the like at the timing when a sign of seizure or the like is caught, seizure or the like can be prevented in advance.
  • the lubrication state estimation device 53 and the method it is sufficient to know the positive / negative of the slope of the tangent of the TF line and the positive / negative of the intercept of the tangent of the TF line. No value is required. Therefore, according to the lubrication state estimation device 53 and the method, it is possible to estimate the lubrication state of the sliding surface between the rotating shaft and the bearing in an actual machine in which it is difficult to measure an exact value. In addition, the soundness of fluid lubrication can be evaluated when it is estimated to be fluid lubrication, and the ratio of boundary lubrication to mixed lubrication can be estimated when it is estimated to be mixed lubrication.
  • the lubrication state estimation systems 50 and 50A according to the first and second embodiments can be applied to, for example, a slide bearing device 60.
  • the slide bearing device 60 exemplified in FIG. 16 is a lubrication state estimation system that estimates the lubrication state of the bearing member 62 that supports the rotary shaft 61 via the lubricating film 63 and the sliding surfaces of the rotary shaft 61 and the bearing member 62. 50 (and / or lubrication state estimation system 50A) is provided.
  • the slide bearing device 60 exemplified in FIG. 16 is a journal slide shaft, it may be a thrust slide bearing.
  • the lubrication state estimation systems 50 and 50A according to the first and second embodiments can be applied to, for example, a mechanical device 65 including a set of sliding members 66 and 67.
  • the mechanical device 65 exemplified in FIG. 17 has a set of sliding members 66, 67 that move relative to each other while being in contact with each other via a lubricating film 68, and a lubrication state of the sliding surfaces of the set of sliding members 66, 67.
  • the lubrication state estimation system 50 (and / or the lubrication state estimation system 50A) for estimating the above is provided.
  • the lubrication state estimation systems 50 and 50A are not limited to the slide bearing device 60, and the lubrication state of the sliding surfaces of two objects that perform curved motion, linear motion, or reciprocating motion. Can be widely used to estimate.
  • FIG. 18 is a diagram showing a schematic configuration of the rotary crusher 100 used in the actual machine simulated test.
  • the rotary crusher 100 shown in FIG. 18 is a gyre crusher or cone crusher provided with a spindle 5 rotatably provided in a crushing chamber 16 formed inside the frames 31 and 32, and estimates the lubrication state.
  • the configuration of the crusher 100 itself excluding the system 50 is known.
  • the rotary crusher 100 is arranged in a central portion of an internal space formed by an upper frame 31 and a lower frame 32 connected to the upper frame 31, with a central axis inclined with respect to the central axis of the crusher 100.
  • the main shaft 5 is provided.
  • the lower part of the spindle 5 is rotatably inserted into the eccentric sleeve 4.
  • the eccentric sleeve 4 is rotatably fitted into the boss 7 formed on the lower frame 32.
  • the lower portion of the eccentric sleeve 4 is supported by a thrust slide bearing 23 provided in the lower frame 32.
  • the lower end of the spindle 5 is supported by the spindle thrust bearing 2 provided in the piston of the hydraulic cylinder 6 for raising and lowering the spindle.
  • the upper end of the spindle 5 is rotatably supported by an upper bearing 17 provided on a spider 18 attached to the upper end of the upper frame 31.
  • a hydraulic chamber 27 is formed above the eccentric sleeve 4 and the boss 7 on the inner peripheral side of the cylindrical partition plate 24.
  • Lubricant is supplied between the outer peripheral surface of the main shaft 5 and the inner peripheral surface of the eccentric sleeve 4, and between the outer peripheral surface of the eccentric sleeve 4 and the inner peripheral surface of the boss 7.
  • the journal plain bearing formed between the outer peripheral surface of the spindle 5 and the inner peripheral surface of the eccentric sleeve 4 is referred to as a "spindle bearing 10", and is between the outer peripheral surface of the eccentric sleeve 4 and the inner peripheral surface of the boss 7.
  • the journal sliding bearing formed in the above is referred to as a "sleeve bearing 11".
  • the multiple bearing formed by the spindle bearing 10 and the sleeve bearing 11 is referred to as a "lower bearing 15".
  • the upper part of the main shaft 5 constitutes a mantle 12 whose outer peripheral surface forms a conical surface.
  • a mantle 13 whose outer surface forms a conical surface is attached to the outside of the mantle 12.
  • a concave 14 is provided on the inner surface of the upper frame 31. The inner surface of the concave 14 and the outer surface of the mantle 13 form a crushing chamber 16 having a wedge-shaped vertical cross section.
  • Power is transmitted from the drive shaft 8a driven by the drive motor 8 provided outside the machine to the eccentric sleeve 4 via the power transmission mechanism 20 including the pulley 22, the horizontal shaft, and the bevel gear 19.
  • the eccentric sleeve 4 rotates, the spindle 5 performs an eccentric turning motion, that is, a so-called precession motion, with respect to the upper frame 31.
  • the distance between the outer surface of the mantle 13 and the inner surface of the concave 14 changes according to the turning position of the spindle 5.
  • the crushed material that has fallen into the crushing chamber 16 is crushed between the concave 14 and the mantle 13, and is collected as a crushed product from below the lower frame 32.
  • the rotary crusher 100 having the above configuration includes a cylinder pressure measuring device 55 that measures the cylinder pressure of the hydraulic cylinder 6 for raising and lowering the spindle, and a shaft power measuring device that measures the shaft power (output) of the drive shaft 8a of the drive motor 8.
  • a lubrication state estimation system 50 (and / or a lubrication state estimation system 50A) including a lubrication state estimation device 53 and a lubrication state estimation device 53 is provided.
  • the cylinder pressure measuring device 55 may be a hydraulic sensor provided in the hydraulic cylinder 6 for raising and lowering the spindle.
  • the shaft power measuring instrument 56 may be a power meter or a torque sensor provided in the drive motor 8.
  • the cylinder pressure measuring device 55 and the shaft power measuring device 56 correspond to the index measuring device 51.
  • ⁇ shaft power / cylinder pressure ⁇ is used as the first index that correlates with the friction coefficient f of the sliding surface in the lower bearing 15
  • ⁇ cylinder pressure ⁇ is used as the second index that correlates with the physical quantity S * in the lower bearing 15. board.
  • the loss of the lower bearing 15 is expressed by ⁇ friction coefficient f x cylinder pressure x coefficient ⁇ .
  • friction coefficient f x cylinder pressure x coefficient ⁇ Approximately the energy balance during load operation of the rotary crusher 100, the shaft power of the drive shaft 8a, the crushing work, the loss of the lower bearing 15, the transmission loss of the power transmission mechanism 20, the mechanical loss of the drive motor 8, And, the sum of the losses of the bearings excluding the lower bearing 15 is balanced.
  • the rotation speed of the spindle 5 is kept substantially constant. Under conditions where the load is sufficiently large and steep load fluctuations can be ignored, the coefficient of friction f of the lower bearing 15 correlates with ⁇ shaft power / cylinder pressure ⁇ .
  • ⁇ shaft power / cylinder pressure ⁇ can be used as the first index that correlates with the friction coefficient f of the lower bearing 15.
  • an index that correlates with the shaft power may be used instead of the shaft power, or an index that correlates with the cylinder pressure may be used instead of the cylinder pressure.
  • the positive / negative of the time change rate of the physical quantity S * of the lower bearing 15 corresponds to the positive / negative of the time change rate of the bearing load of the lower bearing 15 (that is, the pressing load F of the sliding surface).
  • the bearing load of the lower bearing 15 is expressed by ⁇ cylinder pressure ⁇ coefficient ⁇ . From the above, ⁇ cylinder pressure ⁇ can be used as the second index that correlates with the physical quantity S *.
  • an index that correlates with the cylinder pressure may be used instead of the cylinder pressure.
  • the vertical axis of this chart represents the first index or the second index, and the horizontal axis represents the elapsed time.
  • the correlation between the first index and the second index shows a negative correlation under fluid lubrication, but eventually changes to a positive correlation at a certain timing.
  • the lubrication state estimation system 50 included in the rotary crusher 100 the lubrication state changes at the timing when the correlation between the first index and the second index changes from a negative correlation to a positive correlation. It is possible to detect the transition from fluid lubrication to mixed lubrication.
  • the concave 14 and the main shaft 5 arranged inside the concave 14, the mantle 13 provided on the main shaft 5, and the lower part of the main shaft 5 are included.
  • the eccentric sleeve 4 rotatably inserted, the boss 7 into which the eccentric sleeve 4 is rotatably inserted, the drive shaft 8a for rotationally driving the eccentric sleeve 4 via the power transmission mechanism 20, and the drive shaft 8a for rotational drive.
  • the drive motor 8 is provided, a hydraulic cylinder 6 for supporting the spindle 5 so as to be able to move up and down, at least one slide bearing device, and lubrication state estimation systems 50 and 50A for estimating the lubrication state of the sliding surface in the slide bearing device. ..
  • lubrication state estimation system 50, 50A at least one of the lubrication state estimation systems 50, 50A according to the first embodiment and the second embodiment may be applied to the rotary crusher 100.
  • the lubrication state estimation systems 50 and 50A are formed between the journal sliding bearing (spindle bearing 10) formed between the spindle 5 and the eccentric sleeve 4, and between the eccentric sleeve 4 and the boss 7.
  • the double bearing (lower bearing 15) made of the journal sliding bearing (sleeve bearing 11) the lubrication state of the sliding surface is estimated.
  • the lubrication state estimation systems 50 and 50A estimate the lubrication state of the sliding surface of the lower bearing 15, but the lubrication state estimation systems 50 and 50A are other sliding surfaces included in the rotary crusher 100. It may be configured to estimate the lubrication state of. That is, the lubrication state estimation systems 50 and 50A include the spindle bearing 10, the sleeve bearing 11, the spindle thrust bearing 2 formed between the spindle 5 and the hydraulic cylinder 6, the thrust slip bearing 23 of the eccentric sleeve 4, and the spindle 5. At least one of the journal sliding bearings (upper bearing 17) supporting the upper part of the bearing may be configured to estimate the lubrication state of the sliding surface.
  • the lubrication state estimation systems 50 and 50A use the cylinder pressure measuring device 55 for measuring the cylinder pressure of the hydraulic cylinder 6 and the drive motor 8 as the index measuring device 51.
  • the shaft power measuring device 56 for measuring the shaft power is included.
  • the cylinder pressure measuring device 55 is included in the index measuring device of the first index (correlated with f), the second index ( correlated with S * ), and the fourth index (correlated with F).
  • the shaft power measuring instrument 56 is included in the index measuring instrument of the first index (correlated with f) and the third index (correlated with T).
  • the lubrication state estimation system 50 correlates with ⁇ an index that correlates with the shaft power or the shaft power / an index that correlates with the cylinder pressure or the cylinder pressure ⁇ , assuming that the rotation speed of the eccentric sleeve 4 and the viscosity of the lubricating oil are constant.
  • the function that correlates with ⁇ the index that correlates with the cylinder pressure or the cylinder pressure ⁇ is used as the second index, and these indexes are used for estimating the lubrication state of the sliding surface.
  • the lubrication state estimation system 50A assumes that the rotational speed of the eccentric sleeve 4 and the viscosity of the lubricating oil are constant, and uses a function that correlates with ⁇ an index that correlates with axial power or axial power ⁇ as a third index, and ⁇ cylinder. An index that correlates with pressure or cylinder pressure ⁇ is used as the fourth index, and these indexes are used to estimate the lubrication state of the sliding surface.
  • the first index, the second index, and the third index are used by using the process data which is relatively easy to measure during the operation of the rotary crusher 100. Since the index and the fourth index are obtained, the lubrication state estimation systems 50 and 50A can be easily applied to the rotary crusher 100. Further, since the lubrication state estimation systems 50 and 50A can constantly and continuously estimate the lubrication state of bearings such as the lower bearing 15, it is possible to estimate the secular change of the bearing in addition to the lubrication state of the bearing. can.
  • the shaft power and the cylinder pressure of the rotary crusher 100 are measured, and the measured values of the shaft power and the cylinder pressure are estimated.
  • the lubrication state of the sliding bearing (lower bearing 15 in this embodiment).
  • other physical quantities that can be used as the first to fourth indicators may be used.
  • the first index may be a measured value including work, bearing loss, and other losses as long as it is a physical quantity that correlates with the friction coefficient f of the slide bearing to be estimated.
  • the second index may be a measured value including work, bearing loss, and other losses as long as it is an index that correlates with the physical quantity S * to be estimated.
  • the third index may be a measured value including work, bearing loss, and other losses as long as it is an index that correlates with the shaft torque.
  • the fourth index may be a measured value including work, bearing loss, and other losses as long as it is an index that correlates with the load on the bearing sliding surface (pressing load F).
  • the shaft power of the drive motor 8 the shaft power obtained from the shaft torque and the rotation speed of the spindle 5, the motor power obtained from the current and the voltage applied to the drive motor 8, and the like may be used.
  • the shaft torque may be substituted by the strain of the spindle 5 or the stress of the spindle 5.
  • the output torque of the drive motor 8 shaft torque of the drive shaft 8a
  • the displacement amount of the cylinder may be used instead of the cylinder pressure.
  • one spindle 5 is supported by both a lower bearing 15 which is a journal sliding bearing and a spindle thrust bearing 2 which is a thrust sliding bearing.
  • the lower bearing 15 is a so-called “fluid lubrication bearing” in which the normal lubrication state is fluid lubrication. In a fluid-lubricated bearing, the lubrication state changes from fluid lubrication to boundary lubrication via mixed lubrication.
  • the spindle thrust bearing 2 is a so-called "boundary lubrication bearing” in which the normal lubrication state is boundary lubrication.
  • the viscosity ⁇ and the sliding speed v are constant.
  • ⁇ the shaft power of the drive shaft 8a (or the index that correlates with the shaft power) / the cylinder pressure of the hydraulic cylinder 6 (or the index that correlates with the cylinder pressure) ⁇ is used as the fifth index.
  • ⁇ 1 / cylinder pressure of the hydraulic cylinder 6 (or an index correlating with the cylinder pressure) ⁇ is used as the sixth index.
  • FIG. 20A is a 5th index-6th index diagram of the lower bearing 15.
  • the fifth index-6th index diagram is a log-log graph in which the vertical axis represents the fifth index and the horizontal axis represents the sixth index.
  • the slope of the tangent of the fifth index-6th index line (that is, the rate of change of the fifth index with respect to the sixth index) is positive.
  • the inclination of the tangent line of the fifth index-6th index line is negative.
  • FIG. 20B is a 5th index-6th index diagram of the spindle thrust bearing 2.
  • the scales on the horizontal axis of FIGS. 20A and 20B correspond to each other.
  • the lubrication state of the spindle thrust bearing 2 is boundary lubrication
  • the inclination of the tangent line of the fifth index-6th index line is almost 0.
  • the slope of the tangent line of the fifth index to the sixth index line is negative.
  • the lubrication state of the spindle thrust bearing 2 is higher than the inclination of the tangent of the fifth index-6th index line when the lubrication state of the lower bearing 15 is mixed lubrication.
  • the slope of the tangent of the 5th index-6th index line when the scuffing phenomenon is occurring is steeper.
  • the rate of change R1 of the fifth index with respect to the sixth index when the lubrication state of the lower bearing 15 is mixed lubrication is the fifth index with respect to the sixth index when the lubrication state of the spindle thrust bearing 2 is mixed lubrication. Larger than the rate of change R2.
  • Both R1 and R2 are negative values.
  • the lubrication state estimation system 50B has at least one fifth index measuring instrument 51e for measuring the fifth index and at least one for measuring the sixth index.
  • the lower bearing 15 (fluid lubrication bearing) and the spindle thrust bearing 2 are obtained based on the 6th index measuring instrument 51f and the measured values of the 5th index and the 6th index, and the rate of change R of the 5th index with respect to the 6th index.
  • a lubrication state estimation device 53 for estimating the lubrication state of the (boundary lubrication bearing) is provided.
  • the fifth index measuring instrument 51e may include the shaft power measuring instrument 56 and the cylinder pressure measuring instrument 55 described in the third embodiment of the first and second embodiments.
  • the sixth index measuring device 51f may include the cylinder pressure measuring device 55 described in the third embodiment of the first and second embodiments.
  • FIG. 22 is a flowchart illustrating a processing flow of the lubrication state estimation device 53.
  • the lubrication state estimation device 53 acquires the measured value of the fifth index from the fifth index measuring device 51e, and acquires the measured value of the sixth index from the sixth index measuring device 51f (step S51). ).
  • the lubrication state estimation device 53 obtains the rate of change R of the fifth index with respect to the sixth index (step S52). If the rate of change R is a positive value (YES in step S53), the lubrication state estimation device 53 considers that the lubrication state of the lower bearing 15 and the spindle thrust bearing 2 is normal, and returns the process to step S51.
  • the lubrication state estimation device 53 compares the rate of change R with the predetermined first threshold value ⁇ 1 (step S54).
  • the first threshold value ⁇ 1 is a value smaller than 0.
  • the lubrication state estimation device 53 estimates that a scuffing phenomenon has occurred in the spindle thrust bearing 2 (boundary lubrication bearing) when the rate of change R is equal to or less than the first threshold value ⁇ 1 (YES in step S54).
  • An alarm for notifying the abnormality of the spindle thrust bearing 2 is output from the illustrated alarm device (step S55).
  • the lubrication state estimation device 53 compares the rate of change R with the predetermined second threshold value ⁇ 2 (step S56).
  • the second threshold value ⁇ 2 is a value larger than the first threshold value ⁇ 1 and smaller than 0 (0> ⁇ 2> ⁇ 1).
  • the lubrication state estimation device 53 occupies the mixed lubrication in the lower bearing 15 (fluid lubrication bearing).
  • the ratio of boundary lubrication is equal to or higher than a predetermined ratio, and an alarm for notifying an abnormality of the lower bearing 15 is output from an alarm device (not shown) (step S57).
  • the "predetermined ratio” is a value such that seizure of the sliding surface does not occur, but seizure of the sliding surface may occur in the near future if sliding is continued.
  • step S56 If the rate of change R is larger than the second threshold value ⁇ 2 in step S56 (NO in step S56), the lubrication state estimation device 53 outputs a warning regarding the lubrication state of the lower bearing 15 from an alarm device (not shown) (step). S58), the process is returned to step S51. This warning only warns that the thickness of the lubricating film has decreased, but the operator can receive the warning and take appropriate measures.
  • the concave, the main shaft 5 arranged inside the concave 14, the mantle 13 provided on the main shaft 5, and the lower part of the main shaft 5 are included.
  • a lower bearing 15 composed of a sleeve bearing 11 which is a second fluid lubricated bearing, a spindle thrust bearing 2 which is a boundary lubricated bearing formed between the spindle 5 and the hydraulic cylinder 6, and at least 1 for measuring the fifth index.
  • One fifth index measuring instrument 51e at least one sixth index measuring instrument 51f for measuring the sixth index, and a first fluid lubrication bearing and a second fluid lubrication based on the rate of change R of the fifth index with respect to the sixth index.
  • the bearing and the boundary lubrication bearing are provided with a lubrication state estimation device 53 for estimating the lubrication state of the bearing.
  • the fifth index and the sixth index are measured, and the first fluid is based on the rate of change of the fifth index with respect to the sixth index. It includes estimating the lubrication state of the lubrication bearing, the second fluid lubrication bearing and the boundary lubrication bearing.
  • the lubrication state estimation device 53 estimates that a scuffing phenomenon occurs in the spindle thrust bearing 2 (boundary lubrication bearing) when the rate of change R is smaller than 0 and equal to or less than a predetermined first threshold value ⁇ 1. do.
  • the lubrication state estimation method when the step of estimating the lubrication state is equal to or less than a predetermined first threshold value ⁇ 1 in which the rate of change R is smaller than 0, the scuffing phenomenon occurs in the spindle thrust bearing 2 (boundary lubrication bearing). Includes estimating what is happening.
  • the lubrication state estimation device 53 has a lower bearing 15 (first fluid lubrication bearing) when the rate of change R is greater than or equal to the first threshold value ⁇ 1 and smaller than 0 by a predetermined second threshold value ⁇ 2 or less. It is estimated that the ratio of boundary lubrication to the mixed lubrication in (at least one of the second fluid lubrication bearings) is equal to or higher than the predetermined ratio.
  • the lubrication state estimation method when the lubrication state is estimated when the rate of change R is larger than the predetermined first threshold value ⁇ 1 smaller than 0 and smaller than the predetermined second threshold value ⁇ 2 smaller than 0. , Including estimating that the ratio of boundary lubrication to the mixed lubrication in the lower bearing 15 (at least one of the first fluid lubrication bearing and the second fluid lubrication bearing) is equal to or more than a predetermined ratio.
  • the lubrication state of the lower bearing 15 which is a fluid lubrication bearing and the spindle thrust bearing 2 which is a boundary lubrication bearing is individually estimated by one system. However, from this, it is possible to estimate where the sign of seizure is occurring.
  • the lubrication state estimation method according to the present embodiment the lubrication state of the fluid lubrication bearing and the boundary lubrication bearing is individually estimated in a series of processes, and by this, a seizure sign is generated. Can be estimated. That is, it is not necessary to individually estimate the lubrication state of the fluid-lubricated bearing and the boundary-lubricated bearing.
  • the number of devices included in the rotary crusher 100 for estimating the lubrication state of both the fluid-lubricated bearing and the boundary-lubricated bearing can be reduced.
  • the parts to be replaced can be specified without stopping the operation of the rotary crusher 100 and disassembling it.
  • the functions of the lubrication state estimation device 53 disclosed herein include general-purpose processors, dedicated processors, integrated circuits, ASICs (Application Specific Integrated Circuits), conventional circuits, which are configured or programmed to perform the disclosed functions. And / or can be performed using a circuit containing a combination thereof or a processing circuit.
  • a processor is considered a processing circuit or circuit because it includes transistors and other circuits.
  • a circuit, unit, or means is hardware that performs the listed functions.
  • the hardware may be the hardware disclosed herein, or it may be other known hardware that is programmed or configured to perform the listed functions. If the hardware is a processor considered to be a type of circuit, the circuit, means, or unit is a combination of hardware and software, and the software is used to configure the hardware and / or processor.
  • the lubrication state estimation device 53 which is a component of the lubrication state estimation systems 50, 50A, 50B, and various index measuring instruments do not have to be provided at the same place.
  • various index measuring instruments may be provided incidentally to the rotary crusher 100, and at least a part of the functions of the lubrication state estimation device 53 may be provided at a remote location from the rotary crusher 100.
  • the value of the index detected by various index detectors is transmitted to the lubrication state estimation device 53 through the communication network, and the lubrication state estimation device 53 transmits the calculated lubrication state estimation result to the rotary crusher through the communication network. It may be a control device of 100 or the like.
  • the function of the lubrication state estimation device 53 may be provided by the cloud service.
  • the cloud server accessed from the computer may function as the lubrication state estimation device 53 by executing a predetermined program, and may return the failure sign diagnosis result to the computer.
  • the lubrication state estimation device 53 may store the estimation result of the lubrication state in the cloud storage.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Food Science & Technology (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Sliding-Contact Bearings (AREA)
PCT/JP2021/027231 2020-07-20 2021-07-20 潤滑状態推定装置及び方法、滑り軸受装置、機械装置、並びに旋動式破砕機 WO2022019315A1 (ja)

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5395663A (en) * 1977-02-01 1978-08-22 Yaskawa Denki Seisakusho Kk Detecting apparatus for abnormal state of bearings
JP2004519325A (ja) * 2001-03-23 2004-07-02 メッツオ ミネラルズ （タンペレ） オサケイシテヨ 破砕機の軸受状態を監視する方法及びその破砕機
WO2019045042A1 (ja) * 2017-08-31 2019-03-07 株式会社アーステクニカ 旋動式破砕機
JP2019202245A (ja) * 2018-05-21 2019-11-28 株式会社アーステクニカ 旋動式破砕機及びその制御方法

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5395663A (en) * 1977-02-01 1978-08-22 Yaskawa Denki Seisakusho Kk Detecting apparatus for abnormal state of bearings
JP2004519325A (ja) * 2001-03-23 2004-07-02 メッツオ ミネラルズ （タンペレ） オサケイシテヨ 破砕機の軸受状態を監視する方法及びその破砕機
WO2019045042A1 (ja) * 2017-08-31 2019-03-07 株式会社アーステクニカ 旋動式破砕機
JP2019202245A (ja) * 2018-05-21 2019-11-28 株式会社アーステクニカ 旋動式破砕機及びその制御方法

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