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WO2020174579A1 - Concasseur giratoire - Google Patents

Concasseur giratoire Download PDF

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Publication number
WO2020174579A1
WO2020174579A1 PCT/JP2019/007305 JP2019007305W WO2020174579A1 WO 2020174579 A1 WO2020174579 A1 WO 2020174579A1 JP 2019007305 W JP2019007305 W JP 2019007305W WO 2020174579 A1 WO2020174579 A1 WO 2020174579A1
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WO
WIPO (PCT)
Prior art keywords
eccentric sleeve
main shaft
bearing
peripheral surface
inner peripheral
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.)
Ceased
Application number
PCT/JP2019/007305
Other languages
English (en)
Japanese (ja)
Inventor
崇 木島
敦志 大山
章将 古賀
寿恭 佐藤
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.)
Earthtechnica Co Ltd
Original Assignee
Earthtechnica Co Ltd
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 Earthtechnica Co Ltd filed Critical Earthtechnica Co Ltd
Priority to JP2021501430A priority Critical patent/JP7208353B2/ja
Priority to AU2019431004A priority patent/AU2019431004B2/en
Priority to PCT/JP2019/007305 priority patent/WO2020174579A1/fr
Publication of WO2020174579A1 publication Critical patent/WO2020174579A1/fr
Anticipated expiration legal-status Critical
Priority to ZA2021/07136A priority patent/ZA202107136B/en
Ceased legal-status Critical Current

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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
    • 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

Definitions

  • the present invention relates to a rotary crusher for crushing rocks and the like.
  • a rotary crusher such as a gyre re-crusher or cone crusher has been used as a crusher for crushing large rough stones (rocks).
  • a hydraulic rotary crusher is known in which a main shaft provided with a mantle is rotatably supported by an upper bearing and a lower bearing, and the main shaft is hydraulically moved up and down (for example, Patent Document 1).
  • a hydraulic cone crusher will be taken as an example to explain the outline and crushing principle with reference to FIG.
  • a main shaft 5 is provided at the center of an internal space formed by a tubular upper frame 1 having a truncated cone shape and a lower frame 2 connected to the tubular upper frame 1.
  • the central axis L1 of the main shaft 5 is arranged to be inclined with respect to the central axis L2 of the upper frame 1.
  • the upper frame 1 and the lower frame 2 are collectively referred to as a frame 31.
  • the lower portion of the main shaft 5 has a cylindrical shape and is rotatably supported by the lower bearing 15.
  • the lower bearing 15 is provided with an eccentric sleeve 4 having a spindle fitting insertion hole 3 into which a lower end portion of a spindle 5 is rotatably fitted.
  • the eccentric sleeve 4 includes an eccentric sleeve support 32 that supports the eccentric sleeve 4 below the eccentric sleeve 4 so as to be relatively rotatable.
  • the eccentric sleeve support 32 is fixed to the lower frame 2.
  • the outer peripheral surface of the eccentric sleeve 4 is rotatably fitted in an eccentric sleeve fitting hole 27 formed in the outer cylinder 7 arranged in the lower frame 2.
  • the upper end of the main shaft 5 is rotatably supported by an upper bearing 17.
  • the upper bearing 17 is supported by a spider 18 connected to the upper frame 1.
  • the spider 18 forms a beam that passes through the center of the upper frame 1 and connects the upper end of the upper frame 1.
  • a hydraulic cylinder 30 for moving the main shaft 5 up and down by hydraulic pressure is provided below the lower bearing 15.
  • a hydraulic chamber 28 is formed on the inner peripheral side of a cylindrical partition plate 24 provided above the lower bearing 15. Securing smooth sliding between the lower end of the main shaft 5 and the inner peripheral surface of the main shaft fitting insertion hole 3, and between the outer peripheral surface of the eccentric sleeve 4 and the inner peripheral surface of the eccentric sleeve fitting insertion hole 27, Lubricating oil is supplied from the hydraulic chamber 28 in order to form an oil film for preventing abrasion of the sliding surface.
  • the eccentric sleeve 4 and the outer cylinder 7 of the lower bearing 15 function as a radial plain bearing.
  • the dust seal 25 is attached to the bottom surface of the mantulator 12 using a dust seal cover 26.
  • a bearing portion constituted by the outer peripheral surface of the main shaft 5 fitted into the main shaft fitting insertion hole 3 and the inner peripheral surface of the eccentric sleeve 4 (main shaft fitting insertion hole 3) is referred to as a main shaft bearing 10, and the eccentric sleeve 4
  • the bearing portion constituted by the outer peripheral surface of the outer cylinder 7 and the inner peripheral surface of the outer cylinder 7 (the eccentric sleeve fitting hole 27) may be referred to as an eccentric sleeve bearing 11.
  • the main shaft bearing 10 and the eccentric sleeve bearing 11 may be referred to as a lower bearing 15 without particularly distinguishing them.
  • a mantle cover 12 forming a frustoconical outer peripheral surface is firmly attached by shrink fitting.
  • a mantle 13 which is made of a wear-resistant material (for example, high manganese cast steel) and forms a frustoconical outer peripheral surface is attached to the outer peripheral surface of the mantle door 12.
  • the inner surface of the upper frame 1 is provided with a cone cave 14 made of a wear resistant material (for example, high manganese cast steel).
  • the crushing chamber 16 is formed by a space formed by the corn cave 14 and the mantle 13 and having a substantially wedge shape in which the lower portion is narrow in the vertical cross section.
  • the central axis L1 of the main shaft 5 and the central axis L2 of the upper frame 1 intersect at an intersection O in the upper space of the crusher.
  • the main shaft 5 is inclined with respect to the upper frame 1 in a plane including the central axis L1 of the main shaft 5 and the central axis L2 of the upper frame 1.
  • the eccentric sleeve 4 has a central axis L4 that is substantially the same as the central axis L2 of the upper frame 1 (upper bearing 17), and is arranged so as to be rotatable around the central axis L4.
  • the driven bevel gear is driven by a motor (not shown) provided outside the frame 31 via a power transmission mechanism such as the pulley 22, the horizontal shaft, and the bevel gear 19 (driving side bevel gear 20 and driven side bevel gear 21).
  • the eccentric sleeve 4 connected to 21 rotates about the central axis L2 of the upper frame 1 as the center of rotation.
  • the main shaft 5 performs an eccentric turning motion, that is, a so-called precession motion in the crushing chamber 16 with the intersection O as a fixed point in space.
  • the above behavior is ideal geometrical. In an actual device, the intersection O slightly changes due to a bearing gap in the upper bearing 17 or deformation of the casing during operation or the like. Along with that, the geometrical motion behavior of the spindle 5 may slightly change.
  • the distance between any position on the inner surface of the cone cave 14 in the crushing chamber 16 and the outer peripheral surface of the mantle 13 facing the position changes at the same cycle as the rotation of the spindle 5. That is, when the eccentric sleeve 4 is rotated to rotate the main shaft 5 in the crushing chamber 16, for example, the position of the shortest distance between the outer surface of the mantle 13 and the inner surface of the cone cave 14 at the lowermost vertical end of the crushing chamber 16 is shown in FIG. As shown, it changes as the main shaft 5 turns.
  • crushed object 9 The rock to be crushed (hereinafter referred to as “crushed object”) 9 is loaded from above the crusher and falls into the crushing chamber 16.
  • the distance between the cone cave 14 and the mantle 13 becomes narrower as it goes downward, and the width of the distance changes periodically as the main shaft 5 turns.
  • the crushed material 9 is crushed while repeating dropping and compression.
  • the crushed object 9 crushed to be smaller than the narrowest interval between the corn cave 14 and the mantle 13 is discharged from below and collected as a crushed product.
  • a crushing of the object 9 to be crushed in the mantle 13 causes a reaction force P1 of the spindle 5 from the crushing position to the inside of the frame 31 (see FIG. 2 described later). And the reaction force P2 from the crushing position to the outside of the frame 31 acts on the frame 31. Due to the reaction force P1 acting on the main shaft 5, the lower end of the main shaft 5 moves toward the inner peripheral surface of the main shaft fitting insertion hole 3 of the eccentric sleeve 4 (translational movement).
  • the parallelism between the central axis L1 of the main shaft 5 and the central axis L3 of the main shaft fitting hole 3 is impaired, and the central axis L1 of the main shaft 5 is lost. Tilts with respect to the central axis L3 of the spindle insertion hole 3 (rotational motion).
  • the minimum oil film may become thin on the upper end side or the lower end side, that is, a so-called one-side contact state may occur.
  • the outer peripheral surface of the lower end portion of the main shaft 5 and the inner peripheral surface of the main shaft fitting insertion hole 3 of the eccentric sleeve 4 are mixed from the fluid lubrication state through the fluid film with microscopic contact. It shifts to a lubricated state or a state in which solid surfaces slide while making contact with each other. As a result, the main shaft 5 and the eccentric sleeve 4 may cause so-called seizure.
  • the eccentric sleeve 4 is applied to the inner peripheral surface of the outer cylinder 7 opposite to the side on which the reaction force P1 acts. Move towards. Further, the center axis L4 of the eccentric sleeve 4 and the eccentric sleeve fitting hole 27 are formed by the displacement and deformation of the eccentric sleeve 4, the frame 31, etc. due to the reaction force P1 acting on the main shaft 5 etc. and the reaction force P2 acting on the frame 31 etc.
  • the central axis L4 of the eccentric sleeve 4 is inclined with respect to the central axis L5 of the eccentric sleeve fitting insertion hole 27.
  • the minimum oil film may become thin on the upper end side or the lower end side, that is, a so-called one-side contact state may occur.
  • the outer peripheral surface of the eccentric sleeve 4 and the inner peripheral surface of the eccentric sleeve fitting hole 27 of the outer cylinder 7 are mixed lubricated with microscopic contact from the fluid lubrication state via the fluid film.
  • the state or the state in which the solid surfaces are in contact with each other and sliding is brought about.
  • the main shaft 5 and the eccentric sleeve 4 may cause so-called seizure.
  • the upper bearing on the lower bearing 15 spindle bearing 10 or eccentric sleeve bearing 11
  • the lower bearing on the lower end is referred to as “lower contact.”
  • the lower bearing 15 varies depending on the state of the crusher such as the magnitude of the reaction force during the crushing operation, the oil film thickness of the lower bearing 15 (the size of the bearing gap), the deformation of the main shaft 5 and the eccentric sleeve 4. Both upper and lower hits may occur.
  • the rotary crusher has the feature that, due to the crushing principle described above, it is essentially easy for the bearing to partly hit.
  • rocks which are the main object of crushing by a rotary crusher, have various strengths and brittleness.
  • the reaction force received by the mantle 13 is very large, and the lower bearing 15 is worn or damaged in a short time. For this reason, it is necessary to adjust the lower bearing 15 or the like or check it by a test, select an appropriate rotary crusher, or select an appropriate one according to the type of the crushed object 9.
  • the handling of the rotary crusher is very complicated, and the cost and labor are great burdens.
  • the surface of the mantle 13 or the cone cave 14 gradually wears and the thickness becomes thin as the operation progresses, and the distance between the outer peripheral surface of the mantle 13 and the inner surface of the cone cave 14 becomes smaller. Change (widen). Therefore, it is necessary to change (adjust) the position of the upper frame 1 or the position of the main shaft 5 according to the change in the distance. As a result, even with the same type of crushable object 9, the crushing load or its reaction force changes, and the load conditions and the like for the lower bearing 15 also change.
  • the present invention has been made to solve the above-mentioned problems of the prior art, and is a hydraulic rotary crusher in which a main shaft is moved up and down by hydraulic pressure, with a simple configuration and high resistance to changes in load conditions.
  • An object is to provide a rotary crusher having robustness.
  • a rotary crusher is rotatably arranged inside a cone cave, and its central axis is inclined with respect to the central axis of the cone cave to cause an eccentric turning motion.
  • a main shaft an upper bearing that rotatably supports the upper end of the main shaft, a mantle provided on the main shaft, a lower bearing that rotatably supports the lower end of the main shaft, and a lower bearing below the lower bearing.
  • a hydraulic cylinder for moving the main shaft up and down by hydraulic pressure
  • the lower bearing has an eccentric sleeve having a main shaft fitting hole into which a lower end portion of the main shaft is rotatably inserted, and the eccentric sleeve rotates.
  • An outer cylinder having an eccentric sleeve insertion hole that is freely inserted and inserted, and at least one of an inner peripheral surface of the spindle insertion hole, an outer peripheral surface of the eccentric sleeve, and an inner peripheral surface of the eccentric sleeve insertion hole.
  • One of them has a taper shape in which at least a part of the region in the axial direction, the distance from the facing surface increases as it goes upward.
  • the taper shape as described above since the taper shape as described above is provided, the upper end of the inner peripheral surface of the main shaft and the lower bearing can be supported even if the crushing load is large and the conventional configuration is in an upper contact state.
  • the proximity to the section is suppressed. Therefore, it is possible to prevent the lower bearing from being in the upper contact state, and it is possible to prevent the minimum oil film thickness from decreasing. Therefore, it is possible to realize a rotary crusher having a simple structure, which prevents seizure or the like from occurring in the lower bearing and has high robustness against changes in load conditions.
  • the taper shape may include a first taper shape such that the inner peripheral surface of the spindle fitting hole is increased in diameter as it goes upward.
  • the taper shape may include a second taper shape in which the outer peripheral surface of the eccentric sleeve expands in diameter downward.
  • the taper shape may include a third taper shape in which the inner peripheral surface of the eccentric sleeve fitting hole has a diameter that increases as it goes upward.
  • the first tapered shape includes an upper end position in the axial direction of the inner peripheral surface of the main shaft fitting insertion hole, and has a length that is 1 ⁇ 3 or more of the axial length of the inner peripheral surface of the main shaft fitting insertion hole. May be formed in.
  • the third tapered shape includes the upper end position in the axial direction of the inner peripheral surface of the eccentric sleeve fitting insertion hole, and has a length of 1/3 or more of the axial length of the inner peripheral surface of the eccentric sleeve fitting insertion hole. It may be formed in a region having the same.
  • the robust area can be set relatively easily by adjusting the taper angle or the taper ratio of the taper shape.
  • the taper shape has an angle of 0 indicating the rate of change in the diameter Dt of the region with respect to the length in the center axis direction of the region where the taper shape is formed in the lower bearing in a cross-sectional view passing through the center axis of the main shaft. It may be formed to be 0.001° or more and 1° or less.
  • the lower bearing includes an eccentric sleeve support body that rotatably supports the eccentric sleeve below the eccentric sleeve, and the eccentric sleeve contacts a lower surface of the eccentric sleeve with an upper surface of the eccentric sleeve support.
  • the first eccentric sleeve support has a second thrust bearing surface that allows contact with the first thrust bearing surface on the upper surface of the eccentric sleeve support. As at least one of the thrust bearing surface and the second thrust bearing surface goes radially outward of the eccentric sleeve, the distance between the opposing first thrust bearing surface and the second thrust bearing surface increases. It may have a fourth tapered shape.
  • the fourth taper shape that allows the inclination of the eccentric sleeve is formed between the eccentric sleeve and the eccentric sleeve support. Therefore, the deformation of the eccentric sleeve or the eccentric sleeve support due to the inclination of the eccentric sleeve can be suppressed.
  • a rotary crusher according to another aspect of the present invention is rotatably arranged inside a cone cave, and a central axis of the main axis is inclined with respect to the central axis of the cone cave to perform an eccentric turning motion, and the main axis of the main axis.
  • An upper bearing that rotatably supports the upper end, a mantle provided on the main shaft, a lower bearing that rotatably supports the lower end of the main shaft, and a lower bearing provided below the lower bearing, and the main shaft is hydraulically operated.
  • a hydraulic cylinder for moving up and down, wherein the lower bearing has an eccentric sleeve having a spindle fitting insertion hole into which a lower end portion of the spindle is rotatably fitted, and an eccentric sleeve fitting into which the eccentric sleeve is rotatably fitted.
  • An outer cylinder having an insertion hole, and an eccentric sleeve support body that rotatably supports the eccentric sleeve below the eccentric sleeve, the eccentric sleeve being provided on the lower surface of the eccentric sleeve.
  • a first thrust bearing surface that allows contact with the upper surface of the eccentric sleeve support, and the eccentric sleeve support has a second thrust bearing surface that allows contact with the first thrust bearing surface on the upper surface of the eccentric sleeve support.
  • the taper shape as described above is provided, even if the crushing load is large and the conventional configuration is in the upper contact state, the main shaft and the eccentric sleeve have the main shaft fitting insertion holes. Proximity to the upper end of the inner peripheral surface is suppressed. Therefore, it is possible to prevent the lower bearing from being in the upper contact state, and it is possible to prevent the minimum oil film thickness from decreasing. Therefore, it is possible to realize a rotary crusher having a simple structure, which prevents seizure or the like from occurring in the lower bearing and has high robustness against changes in load conditions.
  • FIG. 1 is a sectional view showing the overall configuration of a rotary crusher according to Embodiment 1 of the present invention.
  • FIG. 2 is a plan view for explaining the crushing principle of the rotary crusher.
  • FIG. 3A is a diagram showing a case where the lower bearing of the rotary crusher is in a lower contact state.
  • FIG. 3B is a diagram showing a case where the lower bearing of the rotary crusher is in a uniform contact state.
  • FIG. 3C is a diagram showing a case where the lower bearing of the rotary crusher is in the upper contact state.
  • FIG. 4A is an enlarged vertical cross-sectional view of the lower bearing when the shaft in FIG. 3C is the main shaft.
  • FIG. 4B is an enlarged sectional view of the lower bearing when the shaft in FIG.
  • FIG. 3C is an eccentric sleeve.
  • FIG. 5 is a graph showing the change in the minimum oil film thickness of the bearing with respect to the change in the crushing load for the lower bearing of the specification A.
  • FIG. 6 is a graph showing the change in the inclination angle of the shaft with respect to the change in the crushing load for the lower bearing of the specification A.
  • FIG. 7 is a graph showing the change in the minimum oil film thickness of the bearing with respect to the change in the crushing load for the lower bearing of the specification B.
  • FIG. 8 is a graph showing the change in the inclination angle of the shaft with respect to the change in the crushing load for the lower bearing of the specification B.
  • FIG. 9 is a diagram showing the oil film pressure distribution of the lower bearing in the upper contact state.
  • FIG. 10 is a diagram showing the oil film pressure distribution of the lower bearing in the even contact state for the lower bearing having the same crushing load and specifications as in FIG. 9.
  • FIG. 11 is a diagram showing a comparison between a lower bearing having no robust characteristic and a lower bearing having robust characteristic.
  • FIG. 12 is a graph showing a schematic characteristic curve showing the robust characteristic for the lower bearing of the specification A.
  • FIG. 13 is a graph in which the robust characteristic curve shown in FIG. 12 is approximated by a quadratic function.
  • FIG. 14 is a graph in which the robust characteristic curve shown in FIG. 12 is approximated by a cubic function.
  • FIG. 15 is a graph showing a schematic characteristic curve showing the robust characteristic for the lower bearing of specification B.
  • FIG. 16 is a graph in which the robust characteristic curve shown in FIG.
  • FIG. 15 is approximated by a quadratic function.
  • FIG. 17 is a graph in which the robust characteristic curve shown in FIG. 15 is approximated by a cubic function.
  • FIG. 18 is an enlarged cross-sectional view near the lower bearing of the rotary crusher shown in FIG.
  • FIG. 19A is an enlarged cross-sectional view near the lower bearing of the rotary crusher according to Modification 1 of the present embodiment.
  • FIG. 19B is an enlarged cross-sectional view near the lower bearing of the rotary crusher according to Modification 2 of the present embodiment.
  • FIG. 19C is an enlarged cross-sectional view near the lower bearing of the rotary crusher according to Modification 3 of the present embodiment.
  • FIG. 19D is an enlarged cross-sectional view near the lower bearing of the rotary crusher according to Modification 4 of the present embodiment.
  • FIG. 20A is an enlarged cross-sectional view of the vicinity of the lower end portion of the eccentric sleeve in the rotary crusher according to Embodiment 2 of the present invention.
  • FIG. 20B is an enlarged cross-sectional view of the vicinity of the lower end portion of the eccentric sleeve in the rotary crusher according to the first modification of the second embodiment.
  • FIG. 20C is an enlarged cross-sectional view of the vicinity of the lower end portion of the eccentric sleeve in the rotary crusher according to Modification 2 of Embodiment 2.
  • FIG. 21 is an enlarged cross-sectional view of the vicinity of the lower bearing of the rotary crusher according to the third embodiment of the present invention.
  • FIG. 22 is a vertical cross-sectional view showing the overall configuration of an example of a conventional rotary crusher.
  • the basic configuration of the rotary crusher according to this embodiment is the same as that shown in FIG.
  • configurations similar to those illustrated in FIG. 22 are denoted by the same reference numerals as those in FIG. 22, and description thereof will be omitted.
  • a configuration different from the configuration shown in FIG. 22 will be mainly described.
  • a hydraulic cone crusher will be described as an example as in FIG.
  • the rotary crusher according to the present embodiment is not limited to the hydraulic cone crusher, and can also be applied to a gyre re-crusher and other types of rotary crushers. ..
  • FIG. 1 is a vertical cross-sectional view showing the overall configuration of a rotary crusher according to Embodiment 1 of the present invention.
  • the hydraulic cone crusher according to the present embodiment is arranged in a central portion (inside the cone cave 14) of an internal space formed by a tubular upper frame 1 having a truncated cone shape and a lower frame 2 connected thereto. It has a main shaft 5.
  • the central axis L1 of the main shaft 5 is arranged to be inclined with respect to the central axis L2 of the crusher (upper frame 1).
  • the upper end of the main shaft 5 is rotatably supported by the upper bearing 17.
  • the lower end of the main shaft 5 is rotatably supported by the lower bearing 15.
  • the lower bearing 15 is provided with an eccentric sleeve 4 having a spindle fitting insertion hole 3 into which a lower end portion of a spindle 5 is rotatably fitted.
  • the eccentric sleeve 4 includes an eccentric sleeve support 32 that supports the eccentric sleeve 4 below the eccentric sleeve 4 so as to be relatively rotatable.
  • the eccentric sleeve support 32 is fixed to the lower frame 2.
  • An outer peripheral surface of the main shaft 5 fitted into the main shaft fitting hole 3 and an inner peripheral surface of the eccentric sleeve 4 (main shaft fitting hole 3) constitute a radial slide bearing (main shaft bearing 10) having a predetermined gap. To do. Lubricating oil is supplied to the predetermined gap to form an oil film.
  • the outer peripheral surface of the eccentric sleeve 4 is rotatably fitted in an eccentric sleeve fitting hole 27 formed in the outer cylinder 7 arranged in the lower frame 2.
  • the outer peripheral surface of the eccentric sleeve 4 and the inner peripheral surface of the outer cylinder 7 (the eccentric sleeve fitting hole 27) constitute a radial slide bearing (eccentric sleeve bearing 11) having a predetermined gap. Lubricating oil is supplied to the predetermined gap to form an oil film.
  • the main shaft bearing 10 and the eccentric sleeve bearing 11 may be referred to as a lower bearing 15 without making a particular distinction.
  • the main shaft 5 is rotatably supported by the upper bearing 17 and the lower bearing 15, so that the central axis L1 is inclined with respect to the central axis L2 of the cone cave 14 so that the main shaft 5 can be eccentrically swung. ..
  • a hydraulic cylinder 30 is provided below the lower bearing 15.
  • the main shaft 5 is configured to be movable up and down by hydraulic pressure. The eccentric turning motion and the vertical movement of the main shaft 5 cause the crushed object 9 to be crushed in the crushing chamber 16 defined by the mantle 13 provided on the main shaft 5 and the cone cave 14.
  • the inner peripheral surface 4a of the spindle fitting hole 3 includes a first taper shape whose diameter increases as it goes upward. ..
  • the crushing load and, consequently, the reaction force may change the spindle 5 or
  • the frame 31 or the like is displaced or deformed.
  • the state of the lower bearing 15 changes.
  • FIG. 3A to 3C are diagrams for extracting and explaining the operation or behavior of the lower bearing 15, and show the state of the lower bearing 15 according to the magnitude of the bearing load F that changes according to the magnitude of the crushing load W.
  • FIG. 3 is a diagram schematically showing a relationship between the minimum oil film thickness T and the three states
  • FIG. 3A is a diagram showing a case where the lower bearing 15 of the rotary crusher is in a lower contact state.
  • FIG. 3B is a diagram showing a case where the lower bearing 15 of the rotary crusher is in a uniform contact state.
  • FIG. 3C is a diagram showing a case where the lower bearing 15 of the rotary crusher is in the upper contact state.
  • FIGS. 3A to 3C and FIGS. 4A to 4B show the lower bearing 15 that does not have a tapered shape for convenience of description. Further, the minimum oil film thickness in each state of lower hit, even hit and upper hit is respectively T1, T2 and T3.
  • the central axis of the shaft 41 is La and the central axis of the lower bearing 15 is Lb. 4A to 4B, the center axis of the main shaft 5 is L1, the center axis of the upper bearing 17 is L2, the center axis of the main shaft fitting hole 3 is L3, and the center axis of the eccentric sleeve 4 is L4.
  • the central axis of the insertion hole 27 is L5.
  • the main shaft bearing 10 and the eccentric sleeve bearing 11 will be individually described below.
  • the shaft 41 corresponds to the main shaft 5
  • the center axis La of the shaft 41 corresponds to the center axis L1 of the main shaft 5.
  • the central axis Lb of the bearing 15 corresponds to the central axis L3 of the main shaft fitting hole 3 (see FIG. 4A).
  • the center axis L1 of the spindle 5 corresponding to La is substantially parallel to the center axis L3 of the spindle fitting hole 3 corresponding to Lb, and Shows a state of approaching the inner surface on the right side.
  • FIG. 3B shows that the center axis L1 of the spindle 5 corresponding to La.
  • 3B is a state in which an oil film having a substantially uniform thickness is formed over the entire axial length direction (equal contact state).
  • the bearing load F increases/decreases as the crushing load increases/decreases.
  • the shaft 41 is elastically deformed to some extent by receiving the crushing load F 0 in the portion between the upper bearing 17 and the lower bearing 15 (the central axis La of the shaft 41 is the central portion of the shaft 41 to some extent). It can be said that it is bent).
  • the bearing load F is smaller than the bearing load F 0 that provides a uniform contact state, displacement and deformation of the main shaft 5 and the like are small.
  • the bending of the central axis La of the shaft 41 becomes smaller than that in the state of FIG. 3B. Therefore, compared with the state of FIG. 3B, the central axis L1 (La) of the lower end portion of the spindle 5 is inclined counterclockwise with respect to the central axis L3 (Lb) of the spindle insertion hole 3 toward the paper surface. As a result, as shown in FIG. 3A, the shaft 41 comes into a lower contact state in which the shaft 41 approaches the lower end portion of the lower bearing 15. On the contrary, when the bearing load F is larger than the bearing load F 0 in which the bearings F are evenly hit with reference to the state of FIG. 3B, the displacement and deformation of the main shaft 5 and the like are large.
  • the bending of the central axis La of the shaft 41 becomes larger than that in the state of FIG. 3B. Therefore, as compared with the state of FIG. 3B, the central axis L1 (La) of the spindle 5 is inclined clockwise with respect to the central axis L3 (Lb) of the spindle fitting hole 3 toward the paper surface. As a result, as shown in FIG. 3C, the shaft 41 comes into a top contact state in which the shaft 41 approaches the upper end portion of the lower bearing 15.
  • the main shaft 5 is pressed by the bearing load F toward the inner peripheral direction of the frame 31 (rightward of the paper surface in FIGS. 3A to 3C). Therefore, the region where the minimum oil film thickness occurs is generally on the inner peripheral side of the frame 31 in the main shaft bearing 10.
  • the positions where the minimum oil film thickness occurs in the main shaft bearing 10 in the lower contact state, the even contact state, and the upper contact state are opposite to the side on which the bearing load F acts.
  • the size of the minimum oil film thickness T decreases in the order of the lower hit state, the even hit state, and the upper hit state.
  • FIGS. 3A to 3C when it is considered that the lower bearing 15 is the eccentric sleeve bearing 11, the shaft 41 corresponds to the eccentric sleeve 4.
  • the center axis L4 of the eccentric sleeve 4 is substantially parallel to the center axis L5 of the eccentric sleeve fitting insertion hole 27 (see FIG. 4A), and the right side of the eccentric sleeve fitting insertion hole 27 (toward the paper surface) is shown.
  • the state of approaching the inner surface side is shown.
  • FIG. 3B shows a state in which an oil film having a substantially uniform thickness is formed over the entire axial direction (equal contact state).
  • the position where the minimum oil film thickness occurs and the magnitude of the minimum oil film thickness T in the lower contact state, the even contact state and the upper contact state are such that the shaft 41 is the main shaft bearing 10. It is similar to the case when it is considered to be present.
  • Table 1 summarizes the above three states of the lower bearing 15 due to the difference in the size of the crushing load.
  • the lower bearing 15 of the rotary crusher according to the present embodiment has the characteristics as described above, that is, the upper contact state increases as the crush load increases and the lower contact state decreases as the crush load decreases. This is mainly because the local contact position of the shaft 41 with respect to the lower bearing 15 shifts from the lower end to the upper end of the lower bearing 15. This transition of the contact position is that the main shaft 5 is deformed (elastically deformed) by the bearing load F acting on the intermediate portion between the lower bearing 15 and the upper bearing 17 with the lower bearing 15 and the upper bearing 17 as support points. Caused by.
  • the elastic deformation or displacement of the main shaft 5 strongly depends on the bearing center distance between the upper bearing 17 and the lower bearing 15 (main shaft bearing 10 or eccentric sleeve bearing 11) and the bending rigidity of the main shaft, which is determined by the diameter of the main shaft 5.
  • the crushing load is constant, for example, when the bearing center distance between the upper bearing 17 and the lower bearing 15 increases, the deformation or displacement of the main shaft 5 increases.
  • the diameter of the lower end portion of the spindle 5 fitted in the spindle fitting hole 3 or the diameter of the bottom surface of the mantle 13 increases, the deformation or displacement of the spindle 5 decreases.
  • the lower bearing 15 is apt to hit the upper structure structurally. Therefore, when seizure occurs in the lower bearing 15, it is often in the upper contact state.
  • the distance between the bearing centers with respect to the diameter of the main shaft structurally (the distance between the bearing center of the upper bearing 17 and the bearing center of the lower bearing 15 is structurally ) Becomes longer. Therefore, in the rotary crusher as described above, the lower bearing 15 is likely to be in a strong contact state with an increase in the crushing load.
  • the supporting point (reaction point) of the lower bearing 15 that receives the reaction force of the crushing load acting on (the middle portion of) the main shaft 5 of the lower bearing 15 is It changes from the lower end to the upper end. Therefore, the distance between the action point of the main shaft 15 on which the reaction force of the crushing load acts and the support point of the lower bearing 15 becomes short. Therefore, in the upper contact state, even if the reaction force of the crushing load acting on the main shaft 5 is the same, the bearing load acting on the lower bearing 15 tends to be larger than in the lower contact state and the even contact state. .. Therefore, the bearing is in a severe condition.
  • the inner peripheral surface of the lower bearing 15 has a tapered shape in which the diameter increases as it goes upward. More specifically, as described above, as shown in FIG. 1 and FIG. 18, which is an enlarged view of the vicinity of the lower bearing 15 in FIG. 1, the tapered shape is defined by the main shaft fitting insertion hole 3 provided in the eccentric sleeve 4.
  • the inner peripheral surface 4a includes a first tapered shape whose diameter increases as it goes upward.
  • the inner peripheral surface of the lower bearing 15 having such a tapered shape is shown by a broken line 42.
  • the broken line 42 in FIG. 3C and the inner peripheral surface 4a of the spindle insertion hole 3 in FIG. 1 and FIG. 18 are exaggerated in the taper angle for ease of viewing.
  • the shaft 41 and the lower portion The proximity of the inner peripheral surface 42 of the bearing 15 to the upper end portion is suppressed.
  • the minimum oil film thickness is the smallest among the states of FIGS. 3A to 3C.
  • the uniform contact state of FIG. 3B is obtained. The minimum oil film thickness that remains almost unchanged can be maintained.
  • tapered shape first tapered shape
  • the design range of the lower bearing 15 in the rotary crusher that can take the states shown in FIGS. 3A to 3C is as follows. That is, in general, the order of the Sommerfeld number S is about 0.0001 to 0.1 when the ratio of the bearing length to the shaft diameter (L/D) is about 0.5 to 2, and the minimum The oil film thickness is approximately several ⁇ m to several hundreds ⁇ m.
  • the Sommerfeld number S is a dimensionless quantity for evaluating the lubrication state of the slide bearing and the shaft (fluid lubrication) which are lubricated by oil or the like, and is an evaluation representative of the oil film characteristic of the fluid lubrication bearing. It is an index.
  • the Sommerfeld number S is calculated by the following equation (1).
  • ⁇ is a viscosity coefficient [Pa ⁇ s] of the lubricating oil
  • n is a shaft rotation speed [s ⁇ 1 ]
  • P is a bearing surface pressure [Pa]
  • r is a shaft diameter [m]
  • the above-mentioned taper shape is set to such a taper angle that a robust region described later is included in the change in the minimum oil film thickness of the lubricating oil with respect to the change in the crushing load.
  • the angle (taper angle) ⁇ t between the shaft 41 and the inner peripheral surface 42 of the lower bearing 15 is 0.001° or more and 1° or less in a cross-sectional view passing through the central axis L1 of the main shaft 5. Is.
  • the taper angle ⁇ t which indicates the ratio of the change in the diameter Dt of the region where the taper shape is formed to the length Lt in the central axis Lb direction of the region where the taper shape is formed in the lower bearing 15, is expressed as an angle. It is 0.001° or more and 1° or less. Converting into a taper rate indicating the rate of change of the diameter Dt of the region where the taper shape is formed with respect to the length Lt in the central axis direction of the region where the taper shape is formed in the lower bearing 15, it is 2/1000000 or more and 2/100 or less. is there. Note that, as shown in FIG.
  • the length Lt in the present embodiment is equal to the axial length of the eccentric sleeve 4.
  • the diameter Dt of the region where the tapered shape is formed is equal to the diameter of the inner peripheral surface 4 a of the spindle fitting hole 3.
  • the taper rate is represented by ⁇ Dt/Lt.
  • FIG. 5 is a graph showing the change of the minimum oil film thickness of the lower bearing 15 with respect to the change of the crushing load in the specification A.
  • the deformation or displacement of the structure such as the spindle 5 and the frame 31 (the upper frame 1 and the lower frame 2) in the specification A is determined by the structure such as FEM (finite element method) or BEM (boundary element method). It was determined by analysis. Further, using these values, the oil film thickness of the lower bearing 15 of the specification A was obtained by oil film analysis using the Reynolds equation based on the fluid lubrication theory, and the results were arranged and graphed.
  • FIG. 6 is a graph showing the change in the inclination angle of the lower bearing 15 with respect to the change in the crushing load in the specification A.
  • FIG. 7 is a graph showing the change in the minimum oil film thickness of the lower bearing 15 with respect to the change in the crushing load in the specification B.
  • FIG. 7 is a graph obtained by obtaining the oil film thickness in the same manner as in FIG. 5 in the specification B.
  • FIG. 8 is a graph showing the change in the inclination angle of the lower bearing 15 with respect to the crushing load in the specification B.
  • the rated load is a state in which a fed raw material (such as rock) is crushed at the rated output in a rotary crusher that can be operated at the rated output of the electric motor that drives the rotary crusher.
  • the crushing load that can be generated by a rotary crusher.
  • the rated output of the electric motor In a rotary crusher that cannot be operated at, the rated load means the crushing load corresponding to the maximum output that can safely continue the crushing process when the maximum output is regarded as the rated output.
  • cone crushers are generally designed assuming continuous crushing.
  • the gyre re-crusher used in the primary crusher, etc. is not only in the state where continuous crushing is continued, but also in the case of crushing single particles such as large-scale raw materials (specifically, stone etc.) or discontinuous. Crushing may be performed regularly. Even in a rotary crusher that operates discontinuously, such as a gyre crusher, the rated load shall be as defined above.
  • the minimum oil film thickness on the vertical axis in FIGS. 5 and 7 is normalized by setting the minimum oil film thickness of the lower bearing 15 to 1 when the crushing load is 100%.
  • the inclination angle of the vertical axis in FIGS. 6 and 8 is a positive direction with respect to the center axis L2 of the lower bearing 15 and a direction in which the shaft 41 inclines clockwise toward the paper surface (direction toward the upper contact state). There is. Further, the inclination angle of the vertical axis in FIGS. 6 and 8 is normalized with the absolute value of the inclination angle being 1 when the crushing load is 50%. Regarding the positive and negative signs related to the normalized tilt angle, negative ( ⁇ ) indicates a lower hit state, and positive (+) indicates an upper hit state.
  • the inclination angle of the lower bearing 15 generally increases monotonically so as to draw a substantially linear or gentle curve with an increase in the crushing load, as shown in FIGS. 6 and 8.
  • the minimum oil film thickness in the lower bearing 15 generally generally decreases monotonically with an increase in the crushing load, as shown in FIGS. 5 and 7.
  • the minimum oil film thickness in the lower bearing 15 has a smaller rate of change (decrease) with respect to the increase in the crushing load than in the range other than the specific range. Has become. More specifically, in the lower bearing 15 of the specification A shown in FIG. 5, the minimum oil film thickness decreases as the crush load increases from 50%, but the minimum oil film thickness decreases as the crush load increases.
  • the rate of decrease is gradually gradual. This tendency continues until the crushing load reaches about 105% and the ratio of the decrease in the minimum oil film thickness to the increase in the crushing load rapidly increases. Also in the lower bearing 15 of the specification B shown in FIG. 7, the minimum oil film thickness decreases as the crush load increases from 50%, but the minimum oil film thickness decreases continuously as the crush load increases. Becomes loose. This tendency continues until the crushing load becomes about 145% and the ratio of change in the minimum oil film thickness to the increase in the crushing load rapidly increases.
  • the rate of change (generally a decrease) of the minimum oil film thickness with respect to the increase of the crush load is small compared to the case where the crush load is outside the specified range, and the rate of change of the above-mentioned minimum oil film thickness
  • a specific range until a sharp increase is called “robust region”.
  • the property of the lower bearing 15 having such a robust region is referred to as “robust characteristic”. As shown in FIGS. 5 and 7, the change in the minimum oil film thickness with respect to the crushing load changes smoothly from the small crushing load to the upper limit value of the crushing load in the robust region. In many cases, the lower limit of can not be clearly specified.
  • the upper limit value of the crushing load in the robust region is specified by the feature that the ratio of the decrease in the minimum oil film thickness to the increase in the crushing load, which was moderate until then, increases sharply as described above.
  • the upper limit value of the crushing load in the robust region is about 105%.
  • the upper limit value of the crushing load in the robust region is about 145%. The mathematical specification method of the upper limit value of the crushing load in the robust area will be described later.
  • the inclination angle of the lower bearing 15 changes from negative to positive when the crushing load is about 100%. Therefore, in the specification A, it can be said that the contact is even when the load is about 105% of the crushing load. Therefore, when the crushing load is less than about 105%, the lower hit state is set, and when the crush load is greater than about 105%, the upper hit state is set.
  • the inclination angle of the lower bearing 15 changes from negative to positive when the crushing load is about 145%. Therefore, in the specification B, it can be said that the contact is even when the crushing load is about 145%. Therefore, when the crushing load is less than about 145%, the lower hit state is obtained, and when the crush load is greater than about 145%, the upper hit state is obtained.
  • FIG. 9 shows the analysis result of the oil film pressure distribution in the one-sided contact state.
  • FIG. 10 shows the analysis result of the oil film force distribution in the even contact state.
  • the specifications and bearing loads of the rotary crusher are the same.
  • the inclination angles of the shaft 41 in FIGS. 9 and 10 are 0.015 degrees and 0 degrees, respectively, and the scale of the pressure distribution is the same in both figures.
  • the pressure distribution in the even contact state has a distinct peak in the axial direction, and is a low and gentle distribution as a whole.
  • the lower bearing 15, that is, at least one of the main shaft bearing 10 and the eccentric sleeve bearing 11, is The hit state changes to a uniform hit state. Therefore, the position where the oil film thickness of the lubricating oil is minimum changes from the lower end portion of the bearing to the entire bearing vertical direction. That is, as the lower bearing 15 changes from the lower contact state to the even contact state, the oil film pressure distribution of the lower bearing 15 is a distribution that is biased toward the lower end side of the lower bearing 15 and that is smooth over the entire bearing vertical direction. Change to approach.
  • the bearing 15 changes to a hit state. Therefore, the position where the oil film thickness is minimum moves to the upper end of the lower bearing 15. As a result, the oil film pressure distribution is biased toward the upper end portion of the lower bearing 15 as shown in FIG. 9 from a distribution that becomes smooth over the entire bearing vertical direction as the uniform contact state changes to the upper contact state. It changes to a steep distribution.
  • the minimum oil film thickness in the one-sided contact state of FIG. 9 has decreased to about 13% of the minimum oil pressure thickness in the one-sided contact state of FIG.
  • the uniform contact state is advantageous in order to increase the minimum oil film thickness.
  • the minimum oil film thickness becomes small, so that the bearing becomes a severe condition.
  • the lower bearing 15 has a robust region that gradually changes from a light lower hitting state to an even hitting state as the lower bearing 15 increases in crushing load.
  • a change in the minimum oil film thickness with respect to a change in load is ensured to be insensitive compared to the case where the change is outside the range of the robust region. Therefore, the minimum oil film thickness is easily secured.
  • FIG. 11 is a diagram showing a comparison between a bearing having no robust characteristic and a bearing having robust characteristic.
  • the graph (a) in FIG. 11 shows the change in the minimum oil film thickness with respect to the change in the crushing load in each bearing.
  • the graph (b) in FIG. 11 shows the change of the inclination angle with respect to the change of the crushing load in each bearing.
  • the rated load is 100% for the crushing load
  • the minimum oil film thickness is 1 when the crushing load is 100% of the rated load for the minimum oil film thickness
  • the crushing load is for the inclination angle. Is normalized by setting the absolute value of the tilt angle when 20% of the rated load is 1.
  • the minimum oil film thickness and the inclination angle are simply expressed for easy description and understanding.
  • the upper limit value of the crushing load in the robust region of the bearing having the robust characteristic It is set to 120% of the crushing load.
  • the minimum oil film thickness decreases monotonically overall as the crushing load increases, regardless of whether the bearing has robust characteristics or not.
  • the crushing load is already in the upper contact state at 50%, and above that, the inclination angle becomes large, and the bearing shifts to the strong upper contact state.
  • the minimum oil film thickness monotonically decreases without changing the rate of change of the minimum oil film thickness with respect to an increase in crushing load.
  • the minimum oil film thickness decreases as the crush load increases from 50%, but the ratio of the change (generally a decrease) in the minimum oil film thickness as the crush load increases in the robust region. Shows a robust characteristic that becomes gradually continuous. In FIG.
  • the crushing load is in the range of about 80% to 120%, which is a robust region exhibiting such robust characteristics.
  • the change in the crushing load is associated with the state of one-side contact of the bearing.
  • the range from the slightly lower contact state to the even contact state is a robust region that exhibits robust characteristics with respect to the minimum oil film thickness. ing.
  • the robust area is formed in the range from the light hitting state to the even hitting state.
  • the bearing having no robust region has been described as an example of the bearing in which only the upper contact state is always generated. However, the same applies to a bearing in which only a relatively strong lower contact state is included, which does not include a light lower contact state. Can be said to have no robust region.
  • the ratio of the change in the minimum oil film thickness to the change in the crush load becomes the least sensitive (small) at the crush load, which is the upper limit value or a little smaller than the upper limit value in the robust region.
  • the change of the minimum oil film thickness with respect to the crushing load is monotonically decreasing, but the change rate may be 0 (zero) with a crushing load slightly smaller than the upper limit value of the robust region.
  • the minimum oil film thickness slightly increases with the increase of the crushing load, and when the crushing load exceeds the upper limit value, the minimum oil film is again detected. Thickness may start to decrease with increasing crushing load.
  • this behavior is minute and can occur only under limited conditions, it is considered that the change in the minimum oil film thickness with respect to the crushing load generally decreases monotonically and there is no problem.
  • the lower bearing 15 according to the present embodiment has robust characteristics regarding the minimum oil film thickness in the range from the slightly lower hit state to the even hit state.
  • the sliding mark is likely to be formed over the region from the lower end of the lower bearing 15 to the position of about 1/5 to about 1/3 of the axial length. Further, when the lower bearing 15 is in a uniform contact state, the sliding mark is located at a position of about 1/5 to 1/3 of the axial length from the lower end of the lower bearing 15 and from the upper end of the lower bearing 15 to about the axial length. It is likely to be continuously formed in the region between the positions of 1/5 to 1/3.
  • the lower bearing 15 shifts from the even contact state to the upper contact state, the lower bearing 15 exceeds the upper limit value of the robust region, and thus the robust characteristic is lost.
  • the bearing shifts to the upper contact state in this way, conversely, the minimum oil film is formed on the upper end of the lower bearing 15, and the oil film becomes thicker as it goes downward. Therefore, the sliding mark is likely to be formed over the region from the upper end of the lower bearing 15 to the position of about 1/5 to 1/3 of the axial length.
  • the lower bearing 15 having the robust characteristic even if the crushing load fluctuates or the like, seizure or the like due to the loss of the oil film or the like is unlikely to occur, and a smooth sliding mark in a relatively wide range in the axial direction. Tend to form.
  • the minimum oil film thickness T2 in the even contact state and the minimum oil film thickness T1 in the bottom contact state are the minimum in the upper contact state. It becomes larger than the oil film thickness T3. Therefore, in the lower bearing 15 having robust characteristics, the oil film state is better in the slightly lower contact state and the even contact state than in the upper contact state, and the sliding mark itself is less likely to be formed. Therefore, even if a sliding mark is formed on the lower bearing 15 having robust characteristics, the sliding mark may be relatively mild or may not be formed.
  • the bearing is in a lower hit state or an upper hit state with a relatively strong inclination.
  • a local sliding mark is formed near the lower end of the lower bearing 15.
  • a sliding mark is formed in the region from the upper end of the lower bearing 15 to the position of about 1/5 to 1/3 of the axial length.
  • the minimum oil film thickness is rapidly reduced with the progress of the upper contact state, and therefore the locally strong sliding mark is generated.
  • the sliding marks not only the sliding marks but also seizure or the like may occur due to the loss of the oil film.
  • the bearing having no robust characteristic has a bearing in the upper contact state or a relatively strong inclined lower contact state in the relation of the minimum oil film thickness to the crushing load in the lower bearing 15 having the robust characteristic. It can be said that the bearing.
  • the bearing that does not have robust characteristics can be said to be a bearing that does not fall in the range of a light under-contact state or a uniform contact state. Therefore, in such a bearing, only one of the features of the sliding mark outside the range of the robust region is provided, and a sliding trace peculiar to the case of having the robust region is not formed.
  • the normalized minimum oil film thickness is the same between the bearing having robust characteristics and the bearing having no robust characteristics. ing. However, considering the change rate of the minimum oil film thickness with respect to the change of the crushing load in the bearing that does not have robust characteristics, the actual minimum oil film thickness at the rated load is larger in the bearing that does not have robust characteristics. ..
  • the change in the minimum oil film thickness with respect to the crushing load clearly changes before and after the upper limit of the crushing load in the robust region.
  • the dots ( ⁇ ) in FIGS. 5 and 7 are values obtained by the oil film analysis, and the solid line is a line connecting the dots.
  • it is easy to specify the upper limit of the crushing load in the robust region by acquiring and analyzing the minimum oil film thickness at many crushing load points as shown in FIGS. 5 and 7. is there. About 105% in FIG. 5 and about 145% in FIG. 7 can be judged to be the upper limit value of the crushing load in the robust region.
  • FIG. 12 is a graph showing a schematic characteristic curve showing the robust characteristic of the bearing of specification A.
  • FIG. 12 is the same as the graph of FIG.
  • FIG. 13 is a graph in which the robust characteristic curve shown in FIG. 12 is approximated by a quadratic function.
  • FIG. 14 is a graph in which the robust characteristic curve shown in FIG. 12 is approximated by a cubic function. In the example of FIG.
  • FIG. 15 is a graph showing a schematic characteristic curve showing the robust characteristic for the bearing of specification B.
  • FIG. 15 is the same as the graph of FIG. 7.
  • FIG. 16 is a graph in which the robust characteristic curve shown in FIG. 15 is approximated by a quadratic function.
  • FIG. 17 is a graph in which the robust characteristic curve shown in FIG. 15 is approximated by a cubic function. In the example of FIG.
  • the upper limit value of the crushing load in the robust region obtained by obtaining the intersection of the approximated curves is 144.1%. Further, in the example of FIG. 17, the upper limit value of the crushing load in the robust region obtained by obtaining the intersection of the approximate curves is 145.4%.
  • the robust characteristics are relatively clear. If the difference between the change rate of the minimum oil film thickness with respect to the change of the crushing load in the robust area and the change rate outside the range of the robust area is small, the robust area becomes unclear. Even in such a case, the characteristic curve can be approximated by two approximation curves using a quadratic function or a cubic function. If the upper limit value of the crushing load in the robust region can be specified from the intersection of the two approximated curves, the bearing is considered to have robust characteristics.
  • the size of the crushing load in the robust region and the size of the range of the robust region are affected by the rigidity of the frame 31, the main shaft 5, the bearing support (outer cylinder 7, eccentric sleeve support 32) and the balance. Change. Therefore, the rigidity of each part is an important parameter in the robust area design together with the crushing load.
  • the wear amount of the upper bearing 17 is also an important parameter in the robust area design.
  • the bearing metal used for the upper bearing 17 wears over time.
  • the one-sided contact state of the lower bearing 15 changes to an upper contact state, so that the robust region changes from the initial state of design or a new state.
  • the robust region changes to a lower load side as compared to when the upper bearing 17 is new without wear.
  • the respective characteristic curves move leftward toward the paper surface.
  • the raw material may stay in the crushing chamber 16 formed by the mantle 13 and the cone cave 14 for some reason.
  • the crushing process or the discharging process is delayed, if the operation is to be continued, the raw material staying in the crushing chamber 16 impedes the rotary motion of the crusher.
  • the load applied to the rotary crusher may momentarily greatly exceed the rating.
  • a three-phase induction motor may generally generate a maximum torque of 160% or more of the rated load state.
  • a bearing load corresponding to the shaft torque may be applied to the bearing.
  • a crushing load of 160% or more may occur.
  • the rotary crusher is generally provided with some kind of safety device.
  • the upper limit of the crushing load is preferably at most 200% of the rated load of the rotary crusher.
  • the motor is overloaded. Therefore, the upper limit value of the crushing load is more preferably 160% or less.
  • the robust area may be intentionally set on the load side where the crush load is larger than the rated load. This ensures reliability in the unlikely event of a situation.
  • the normal load the crushing load that is normally used depending on the type or property of the raw material
  • the rated load is lower than the lower limit of the crushing load in the robust region. As described above, when the crushing load is small, it tends to be in a lower contact state. However, since the crushing load W (bearing load F) itself is small, as shown in FIGS. 5 and 7, it is easy to secure a sufficient minimum oil film thickness T1 in the first place.
  • rotary crushers are often operated under conditions where the crushing load is less than the rated load, for example, about 50% of the crushing load.
  • the reliability of the bearing during operation can be improved by setting the robust area to an area (range) where the crush load is low.
  • the rotary crusher By using the rotary crusher using the lower bearing 15 having the above characteristics, the type of the crushed object is changed or the operating conditions are changed (including the change of the crushing load due to the wear of the mantle 13 or the cone cave 14), etc. Therefore, even if the crushing load changes, the rotary crusher can be continuously used while preventing the occurrence of the one-side contact state. As a result, it is not necessary to adjust the lower bearing 15 or to check the lower bearing 15 or the like again according to the change in the crushing load. Further, it is not necessary to select an appropriate rotary crusher or to use it properly according to the change of the crushing load. Therefore, the labor or cost due to the change in the crushing load can be reduced, and the operating rate can be improved.
  • the crush load is almost proportional to the motor power (shaft torque), and in actual operation of the rotary crusher, the motor power is easier to measure and manage directly than the crush load. For this reason, it is more convenient to sort and grasp the relationship between the motor power and the minimum oil film thickness than using the relationship between the crushing load and the minimum oil film thickness.
  • the crushing load is normalized by the rated load (rated value)
  • the crushing load can be used as the motor power as it is (reread).
  • the upper limit value of the crushing load is preferably about 70% or more, about 80% or more, or about 100% or more of the rated value of the motor power.
  • the upper limit value of the crushing load is preferably about 200% or less, about 160% or less, or about 110% or less of the rated value of the motor power.
  • the present invention is particularly effective for a large rotary crusher. Specifically, it is particularly effective in a rotary crusher having an inlet size of the rotary crusher of 200 mm or more.
  • the inlet dimension is the distance between the inner surface of the cone cave 14 and the upper end of the mantle 13.
  • the inlet size defines the maximum size of raw material that can be fed to the rotary crusher.
  • the robust region can be set as described above by adjusting the taper angle or the taper ratio of the taper shape provided on the inner peripheral surface 42 of the lower bearing 15.
  • the taper angle ⁇ t of the taper shape is preferably 0.001° or more and 1° or less. Converted to a taper rate, it is 2/1000000 or more and 2/100 or less.
  • the tapered shape for avoiding the upper contact state the first tapered shape in which the inner peripheral surface 4a of the main shaft fitting insertion hole 3 has a diameter increasing toward the upper side is described.
  • the present invention is not limited to this.
  • the taper shape may include a second taper shape in which the outer peripheral surface 4b of the eccentric sleeve 4 expands in diameter downward.
  • the taper shape may include a third taper shape in which the inner peripheral surface 7a of the eccentric sleeve fitting insertion hole 27 of the outer cylinder 7 has a diameter that increases as it goes upward.
  • the taper angle ⁇ t for having the robust region is similar to the above range.
  • the central axial length Lt of the region where the tapered shape is formed in the lower bearing 15 is equal to the axial length of the outer cylinder 7.
  • the diameter Dt of the region where the tapered shape is formed is equal to the diameter of the outer peripheral surface 4b of the eccentric sleeve 4.
  • the central axis direction length Lt of the region where the tapered shape is formed in the lower bearing 15 is equal to the axial length of the outer cylinder 7.
  • the diameter Dt of the region where the tapered shape is formed is equal to the diameter of the inner peripheral surface 7 a of the eccentric sleeve fitting hole 27.
  • the shaft 41 in FIG. 3C corresponds to the eccentric sleeve 4.
  • the relative relationship between the shaft 41 and the lower bearing 15 also has a shape that avoids the upper contact state, as in FIG. 3C. Therefore, by having the second taper shape or the third taper shape, it is possible to prevent the lower bearing 15 from being in the upper contact state, and it is possible to prevent the minimum oil film thickness T3 from decreasing. .. Therefore, with a simple structure, it is possible to realize a rotary crusher that prevents seizure and the like from occurring in the lower bearing 15 and has high robustness against changes in load conditions.
  • the third taper shape is formed in the entire area of the inner peripheral surface 7a of the eccentric sleeve fitting insertion hole 27 in the axial direction.
  • a third taper shape may be formed in the region.
  • the third taper shape has an upper end position in the axial direction of the inner peripheral surface 7a of the eccentric sleeve fitting insertion hole 27 and an axial center position of the inner peripheral surface 7a of the eccentric sleeve fitting insertion hole 27.
  • the region 7a2 between the axial center position of the inner peripheral surface 7a of the eccentric sleeve fitting insertion hole 27 and the lower end position of the inner peripheral surface 7a of the eccentric sleeve fitting insertion hole 27 in the axial direction is tapered. It is a region that is not covered (the inner peripheral surface is along the axial direction).
  • the length Lt in the central axis direction of the region where the tapered shape is formed in the lower bearing 15 is equal to 1 ⁇ 2 of the axial length of the outer cylinder 7.
  • the third taper shape includes the upper end position in the axial direction of the inner peripheral surface 7a of the eccentric sleeve fitting insertion hole 27 and is 1 ⁇ 2 of the axial length of the inner peripheral surface 7a of the eccentric sleeve fitting insertion hole 27. It is formed in a region having a length.
  • the third taper shape when the third taper shape is formed in a part of the region in the axial direction, the third taper shape is not limited to the above example, and the third taper shape corresponds to the upper end position of the inner peripheral surface 7a of the eccentric sleeve fitting insertion hole 27 in the axial direction. It may be formed in a region having a length of 1/3 or more of the axial length of the inner peripheral surface 7a of the eccentric sleeve fitting insertion hole 27. For example, in the region 7a1 in which the third tapered shape has a length that is 1 ⁇ 3 of the axial length of the inner peripheral surface 7a of the eccentric sleeve fitting hole 27, the lower end position of the region is from the upper end position to the eccentric sleeve fitting hole.
  • the hole 27 is located at a position lower by 1/3 of the axial length of the inner peripheral surface 7a. Further, for example, in the region 7a1 in which the third taper shape has a length of 2 ⁇ 3 of the axial length of the inner peripheral surface 7a of the eccentric sleeve fitting insertion hole 27, the lower end position of the region is from the upper end position to the eccentric sleeve. It is located at a position that is 2 ⁇ 3 of the axial length of the inner peripheral surface 7a of the insertion hole 27 and is below the length.
  • the axial length of the region 7a1 in which the third tapered shape is formed is more preferably 1/2 or more of the axial length of the inner peripheral surface 7a of the eccentric sleeve fitting hole 27.
  • the first tapered shape is formed in the entire area of the inner peripheral surface 4a of the spindle fitting hole 3 in the axial direction.
  • the first tapered shape may be formed in a part of the region in the axial direction.
  • the first taper shape has an upper end position in the axial direction of the inner peripheral surface 4a of the main shaft fitting insertion hole 3 and an axial center position of the inner peripheral surface 4a of the main shaft fitting insertion hole 3. It is formed in the region 4a1 between them.
  • the central axis direction length Lt of the region where the tapered shape is formed in the lower bearing 15 is equal to 1 ⁇ 2 of the axial length of the eccentric sleeve 4.
  • the first tapered shape includes the upper end position in the axial direction of the inner peripheral surface 4a of the main shaft fitting insertion hole 3 and has a length that is 1 ⁇ 2 of the axial length of the inner peripheral surface 4a of the main shaft fitting insertion hole 3. Is formed in a region having.
  • the region in which the first taper shape is formed on the inner peripheral surface 4a of the spindle insertion hole 3 is made a part of the region in the axial direction, so that in both cases of low load and high load. Also, it is possible to prevent the minimum oil film thickness T3 from decreasing.
  • the first taper shape is not limited to the above example, and the first taper shape includes the upper end position of the inner peripheral surface 4a of the main shaft fitting hole 3 in the axial direction. It can be formed in a region having a length that is 1 ⁇ 3 or more of the axial length of the inner peripheral surface 4 a of the spindle fitting hole 3.
  • the axial length of the region 4a1 in which the first tapered shape is formed is more preferably 1/2 or more of the axial length of the inner peripheral surface 4a of the main shaft fitting insertion hole 3.
  • a plurality of first to third tapered shapes may be combined. That is, at least one of the inner peripheral surface 4a of the spindle fitting insertion hole 3, the outer peripheral surface 4b of the eccentric sleeve 4 and the inner peripheral surface 7a of the eccentric sleeve fitting insertion hole 27 is a distance from a surface facing the upper surface. It has only to have a tapered shape so that In any case, similarly to FIG. 1, it is possible to prevent the lower bearing 15 from being in the upper contact state, and it is possible to prevent the minimum oil film thickness T3 (FIG. 3C) from decreasing. .. Therefore, with a simple structure, it is possible to realize a rotary crusher that prevents seizure and the like from occurring in the lower bearing 15 and has high robustness against changes in load conditions.
  • the taper angle for having a robust region is the same as the above range.
  • the taper angle at this time is the sum of the taper angles of the combined tapered shapes.
  • the rotary crusher has a configuration in which the thrust bearing 33 between the eccentric sleeve 4 and the eccentric sleeve support 32 is provided with a tapered shape. You may have.
  • FIG. 20A is an enlarged cross-sectional view of the vicinity of the lower end portion of the eccentric sleeve in the rotary crusher according to the second embodiment of the present invention.
  • the eccentric sleeve 4 includes a first thrust bearing surface 23a that allows the lower surface of the eccentric sleeve 4 to come into contact with the upper surface of the eccentric sleeve support 32.
  • the eccentric sleeve support 32 is provided with a second thrust bearing surface 23b that allows contact with the first thrust bearing surface 23a on the upper surface of the eccentric sleeve support 32.
  • the first thrust bearing surface 23a and the second thrust bearing surface 23b constitute the thrust bearing 23 with respect to the eccentric sleeve support 32 (lower frame 2) of the lower bearing 15.
  • the first thrust bearing surface 23a has a fourth taper shape such that the distance between the first thrust bearing surface 23a and the second thrust bearing surface 23b facing each other increases as it goes radially outward of the eccentric sleeve 4. There is.
  • the spindle 5 and the eccentric sleeve 4 are fitted into the spindle even in a situation where the crushing load is large and the conventional configuration is in an upper contact state.
  • the proximity of the inner peripheral surface of the hole 3 to the upper end portion is suppressed. Therefore, it is possible to prevent the lower bearing 15 from being in the upper contact state, and it is possible to prevent the minimum oil film thickness from decreasing. Therefore, with a simple structure, it is possible to realize a rotary crusher that prevents seizure and the like from occurring in the lower bearing 15 and has high robustness against changes in load conditions.
  • the second thrust bearing surface 23b may have the fourth tapered shape as shown in FIG. 20B. Further, as shown in FIG. 20C, both the first thrust bearing surface 23a and the second thrust bearing surface 23b may have a fourth tapered shape.
  • the rotary crusher has a taper shape (at least one of the first taper shape to the third taper shape) in the first embodiment and a fourth taper shape (first thrust bearing surface 23a) in the second embodiment. And a tapered shape formed on at least one of the second thrust bearing surface 23b).
  • FIG. 21 is an enlarged sectional view of the vicinity of the lower bearing of the rotary crusher according to the third embodiment of the present invention.
  • the lower bearing 15 has a second taper shape formed on the outer peripheral surface 4b of the eccentric sleeve 4 and a third taper formed on the inner peripheral surface 7a of the eccentric sleeve fitting insertion hole 27 of the outer cylinder 7. It has a shape and a fourth tapered shape formed on each of the first thrust bearing surface 23a and the second thrust bearing surface 23b of the thrust bearing 23.
  • the second taper shape and the third taper shape formed in the lower bearing 15 may cause the eccentric sleeve 4 to have a larger inclination as compared with the conventional case (a structure without the second taper shape and the third taper shape). Can be acceptable. Therefore, the stress acting on the eccentric sleeve 4 and the eccentric sleeve support 32 due to the inclination of the eccentric sleeve 4 may be large.
  • a fourth tapered shape first thrust bearing surface 23a and second thrust bearing surface 23b
  • the combination of the first taper shape to the fourth taper shape is not limited to the above example.
  • the first taper shape and the third taper shape are provided, or all the first taper shape to the fourth taper shape are provided.
  • Various combinations such as configurations can be adopted.

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

Abstract

La présente invention concerne un concasseur giratoire pourvu : d'un arbre principal qui est disposé de manière rotative à l'intérieur d'une concavité et qui tourne de manière excentrique avec l'axe central de l'arbre principal selon une inclinaison par rapport à l'axe central de la concavité ; un palier supérieur qui supporte de manière rotative une section d'extrémité supérieure de l'arbre principal ; un palier inférieur qui supporte de manière rotative une section d'extrémité inférieure de l'arbre principal ; et un vérin hydraulique qui amène l'arbre principal à se déplacer verticalement sous l'effet de la pression de l'huile. Le palier inférieur est pourvu d'un manchon excentrique qui comporte un trou d'insertion d'ajustement d'arbre principal dans lequel la section d'extrémité inférieure de l'arbre principal est insérée pour s'ajuster de manière rotative, et un vérin externe qui a un trou d'insertion d'ajustement de manchon excentrique dans lequel le manchon excentrique est inséré pour s'ajuster de manière rotative. Au moins l'une d'une surface périphérique interne du trou d'insertion d'ajustement d'arbre principal, d'une surface périphérique externe du manchon excentrique, et d'une surface périphérique interne du trou d'insertion d'ajustement de manchon excentrique a une forme effilée dans au moins une région partielle de celle-ci dans la direction axiale de telle sorte que la distance à partir d'une surface telle que de telles faces de forme effilée devient supérieure à mesure que la forme effilée progresse vers le haut.
PCT/JP2019/007305 2019-02-26 2019-02-26 Concasseur giratoire Ceased WO2020174579A1 (fr)

Priority Applications (4)

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JP2021501430A JP7208353B2 (ja) 2019-02-26 2019-02-26 旋動式破砕機
AU2019431004A AU2019431004B2 (en) 2019-02-26 2019-02-26 Gyration-type crusher
PCT/JP2019/007305 WO2020174579A1 (fr) 2019-02-26 2019-02-26 Concasseur giratoire
ZA2021/07136A ZA202107136B (en) 2019-02-26 2021-09-23 Gyration-type crusher

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PCT/JP2019/007305 WO2020174579A1 (fr) 2019-02-26 2019-02-26 Concasseur giratoire

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Cited By (4)

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Publication number Priority date Publication date Assignee Title
CN114289444A (zh) * 2021-11-23 2022-04-08 浙江微盾环保科技股份有限公司 一种刀具集成式医疗废物灭菌处理筒
CN114289457A (zh) * 2021-11-23 2022-04-08 浙江微盾环保科技股份有限公司 一种具有防堵功能的医疗废物处理机
WO2022151513A1 (fr) * 2021-01-15 2022-07-21 南京悠维有机食品有限公司 Procédé de préparation de pulpe de fruit utilisant une rupture de paroi instantanée à haute pression (hpb)
WO2024194782A1 (fr) * 2023-03-17 2024-09-26 Flsmidth A/S Concasseur à cône à axe oblique

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JPS605437U (ja) * 1983-06-21 1985-01-16 株式会社神戸製鋼所 旋動形破砕機の軸支持構造
US20140306040A1 (en) * 2011-11-28 2014-10-16 Sandvik Intellectual Property Ab Method of controlling an inertia cone crusher
JP2017113739A (ja) * 2015-12-27 2017-06-29 株式会社アーステクニカ 旋動式破砕機

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JP2626844B2 (ja) * 1991-02-12 1997-07-02 宇部興産株式会社 旋動式破砕機のセット値測定装置

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Publication number Priority date Publication date Assignee Title
JPS605437U (ja) * 1983-06-21 1985-01-16 株式会社神戸製鋼所 旋動形破砕機の軸支持構造
US20140306040A1 (en) * 2011-11-28 2014-10-16 Sandvik Intellectual Property Ab Method of controlling an inertia cone crusher
JP2017113739A (ja) * 2015-12-27 2017-06-29 株式会社アーステクニカ 旋動式破砕機

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022151513A1 (fr) * 2021-01-15 2022-07-21 南京悠维有机食品有限公司 Procédé de préparation de pulpe de fruit utilisant une rupture de paroi instantanée à haute pression (hpb)
CN114289444A (zh) * 2021-11-23 2022-04-08 浙江微盾环保科技股份有限公司 一种刀具集成式医疗废物灭菌处理筒
CN114289457A (zh) * 2021-11-23 2022-04-08 浙江微盾环保科技股份有限公司 一种具有防堵功能的医疗废物处理机
CN114289457B (zh) * 2021-11-23 2023-01-10 浙江微盾环保科技股份有限公司 一种具有防堵功能的医疗废物处理机
CN114289444B (zh) * 2021-11-23 2023-01-10 浙江微盾环保科技股份有限公司 一种刀具集成式医疗废物灭菌处理筒
WO2024194782A1 (fr) * 2023-03-17 2024-09-26 Flsmidth A/S Concasseur à cône à axe oblique

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JP7208353B2 (ja) 2023-01-18
AU2019431004A1 (en) 2021-10-21
JPWO2020174579A1 (ja) 2021-12-16
ZA202107136B (en) 2023-11-29

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