AU2015368587B2

AU2015368587B2 - Oil supply structure, oil supply method, and gyratory crusher

Info

Publication number: AU2015368587B2
Application number: AU2015368587A
Authority: AU
Inventors: Shoji Inomata; Takashi Kijima; Akimasa Koga; Masahiko Nishi; Atsushi Oyama; Yoshichika Sato; Hirotoshi Takanami; Hiroshi Takata
Original assignee: Earthtechnica Co Ltd
Current assignee: Earthtechnica Co Ltd
Priority date: 2014-12-24
Filing date: 2015-12-22
Publication date: 2020-12-24
Anticipated expiration: 2035-12-22
Also published as: WO2016104503A1; ZA201705031B; AU2015368587A1

Abstract

[Problem] To provide a gyratory crusher serviced through an opening at the top for excellent serviceability, in which the amount of oil supplied can be controlled to maintain a sound oil film in a bearing portion; also to provide an oil supply structure and an oil supply method for such a gyratory crusher. [Solution] An oil supply structure (30) is a structure for supplying lubricating oil to both a first bearing part (41) and a second bearing part (42), the oil supply structure having an annular thrust seal (33) arranged on the inner side of a lower frame assembly (13) and supporting the bottom end of an inner cylinder bush part (14a) from below, a first oil supply inlet (31) opening in the bottom part of the lower frame assembly (13) so as to supply oil to the first bearing part (41), and a second oil supply inlet (32) opening in the inner peripheral surface of an outer cylinder bush part (13a) so as to supply oil to the second bearing part (42). The thrust seal (33) separates the flow channel of lubricating oil supplied from the first oil supply inlet (31) to the first bearing part (41), and the flow channel of lubricating oil supplied from the second oil supply inlet (32) to the second bearing part (42).

Description

DESCRIPTION

Title of Invention OIL SUPPLY STRUCTURE, OIL SUPPLY METHOD, AND GYRATORY CRUSHER

Technical Field

[0001] The present invention relates to a gyratory crusher in which a material to be crushed, such as raw ore or rough stones, is supplied to between a gyrated mantle and a concave and is crushed, and to an oil supply structure and an oil supply method for such a gyratory crusher.

Background Art

[0002] A gyratory type crusher, such as a cone crusher or a gyratory crusher, is a machine provided with a crushing chamber formed between a funnel-shaped mantle which is fixed to an upper portion of a main shaft assembly gyrated and a concave which is provided so as to cover the mantle.

[0003] A bottom shell assembly having a bottom shell bush section is disposed under the concave, and an eccentric bush section of an eccentric sleeve assembly is fitted to the bottom shell bush section of the bottom shell assembly. The eccentric bush section is formed at an eccentric position with a hole extending in a direction inclined relative to a rotational axis of the eccentric bush section, and the main shaft assembly to which the mantle is fixed is fitted in the hole in the eccentric bush section. In addition, a flange section extending to outside of the bottom shell bush section is fixed to an end portion of the eccentric bush section, and a rotational power transmission system is connected to the tip of the flange section. The flange section and the eccentric bush section are rotated as one body about the rotational axis of the eccentric bush section by rotational power from the rotational power transmission system, whereby the main shaft assembly and the mantle are gyrated as one body around the rotational axis of the eccentric bush section.

[0004] Besides, a bottom shell assembly having the bottom shell bush section is disposed under the concave, and a sleeve section of the eccentric sleeve assembly is fitted to the bottom shell bush section of the bottom shell assembly. The sleeve section is formed with a hole extending in a direction inclined relative to a rotational axis of the eccentric sleeve assembly, and the eccentric bush section is fitted in the hole extending in the inclined direction. In addition, the main shaft assembly to which the mantle is fixed is fitted in an eccentric hole in the eccentric bush section. Besides, the flange section extending to outside of the bottom shell bush section extends at an upper portion or a lower portion of the sleeve section, and the rotational power transmission system is connected to the tip of the flange section. With the eccentric sleeve assembly rotated by the rotational power from the rotational power transmission system, the main shaft assembly and the mantle are gyrated as one body about the rotational axis of the eccentric hole in the eccentric bush section.

[0005] When raw ore or rough stones are supplied into the crushing chamber through a hopper provided at an upper portion of the gyratory crusher, the raw ore or rough stones trapped between the gyrated mantle and the concave are crushed under pressure to a predetermined grain size, and discharged.

[0006] Meanwhile, in regard of the positional relationship between the eccentric bush section and the flange section of the eccentric sleeve assembly, there are known a type in which the flange section is fixed to an upper portion of the eccentric bush section (hereinafter referred to as the type serviced through an opening at the top) and a type in which the flange section is fixed to a lower portion of the eccentric bush section (hereinafter referred to as the type serviced through an opening at the bottom). For example, Patent Document 1 discloses a gyratory crusher of the type serviced through an opening at the top, while Patent Document 2 discloses a gyratory crusher of the type serviced through an opening at the bottom.

[0007] In addition, in regard of the positional relationship between the sleeve section and the flange section of the eccentric sleeve assembly, there are known a type in which the flange section extends at an upper portion of the sleeve section (hereinafter referred to as the type serviced through an opening at the top) and a type in which the flange section extends at a lower portion of the sleeve section (hereinafter referred to as the type serviced through an opening at the bottom). For instance, Patent Document 1 discloses a gyratory crusher of the type serviced through an opening at the top, while Patent Document 2 discloses a gyratory crusher of the type serviced through an opening at the bottom.

[0008] The gyratory crusher of the type serviced through an opening at the top is excellent in serviceability but involves difficulty in controlling the quantities of oil supplied for maintaining sound oil films in bearing sections. On the other hand, the gyratory crusher of the type serviced through an opening at the bottom makes it easy to control the quantities of oil supplied for maintaining sound oil films in bearing sections but is low in serviceability.

Citation List Patent Literature

[0009] Patent Document 1: Japanese patent application publication No. 05-345136 Patent Document 2: Japanese patent application publication No. 2014-108390

Summary of Invention

[0010] The present invention has been made inconsideration of the aforementioned points. It is an object of the present invention to overcome one or more disadvantages of the prior art by, for example, providing an oil supply structure for a gyratory crusher, an oil supply method and a gyratory crusher, of the type serviced through an opening at the top for excellent serviceability, in which the quantities of oil supplied can be controlled for maintaining sound oil films in bearing sections.

[0011] One aspect of the present invention is directed to an oil supply structure for a gyratory crusher, the gyratory crusher comprising: a bottom shell assembly having a bottom shell bush section; an eccentric sleeve assembly that has an eccentric bush section fitted to the bottom shell bush section and rotated and a flange section fixed to an upper portion of the eccentric bush section; a main shaft assembly holding a mantle that is fitted to the eccentric bush section and gyrated; and a rotational power transmission system that transmits rotational power to the flange section, wherein a material to be crushed is crushed between the gyrated mantle and a concave, the oil supply structure being for supplying lubricating oil to afirst bearing section between the main shaft assembly and the eccentric bush section and to a second bearing section between the eccentric bush section and the bottom shell bush section, the oil supply structure comprising: an annular thrust seal that is disposed inside the bottom shell assembly and supports a lower end portion of the eccentric bush section from below; a first oil supply inlet that opens in a bottom portion of the bottom shell assembly so as to enable oil supply to the first bearing section; and a second oil supply inlet that opens in an inner peripheral surface of the bottom shell bush section so as to enable oil supply to the second bearing section, wherein the thrust seal separates a flow channel for the lubricating oil supplied from the first oil supply inlet to the first bearing section from a flow channel for the lubricating oil supplied from the second oil supply inlet to the second bearing section.

[0012] In the oil supply structure according to the mode mentioned above, a thrust bearing that supports the flange section from below may be provided at an upper end portion of the bottom shell bush section.

[0013] In the oil supply structure according to the mode mentioned above, a thrust bearing that supports the flange section from below may not be provided at an upper end portion of the bottom shell bush section.

[0014] In the oil supply structure according to the mode mentioned above, a stepped portion may be projectingly provided on an outer diameter side of the thrust seal, and an inner peripheral surface of the stepped portion may surround an outer peripheral surface of a lower end portion of the eccentric bush section.

[0015] According to another mode of the present invention, there is provided a gyratory crusher crushing comprising: a bottom shell assembly having a bottom shell bush section; an eccentric sleeve assembly that has an eccentric bush section fitted to the bottom shell bush section and rotated and a flange section fixed to an upper portion of the eccentric bush section; a main shaft assembly holding a mantle that is fitted to the eccentric bush section and gyrated; and a rotational power transmission system that transmits rotational power to the flange section, wherein a material to be crushed is crushed between the gyrated mantle and a concave, the gyratory crusher further comprises an oil supply structure for supplying lubricating oil to a first bearing section between the main shaft assembly and the eccentric bush section and to a second bearing section between the eccentric bush section and the bottom shell bush section, the oil supply structure comprises: an annular thrust seal that is disposed inside the bottom shell assembly and supports a lower end portion of the eccentric bush section from below; a first oil supply inlet that opens in a bottom portion of the bottom shell assembly so as to enable oil supply to the first bearing section; and a second oil supply inlet that opens in an inner peripheral surface of the bottom shell bush section so as to enable oil supply to the second bearing section, and the thrust seal separates a flow channel for the lubricating oil supplied from the first oil supply inlet to the first bearing section from a flow channel for the lubricating oil supplied from the second oil supply inlet to the second bearing section.

[0015a] An aspect of the present invention provides an oil supply method for a gyratory crusher, the gyratory crusher comprising: a bottom shell assembly having a bottom shell bush section; an eccentric sleeve assembly that has a sleeve section holding an eccentric bush section fitted to the bottom shell bush section and rotated and a flange section extending at an upper portion of the sleeve section; a main shaft assembly holding a mantle that is fitted to the eccentric bush section and gyrated; and a rotational power transmission system that transmits rotational power to the flange section, wherein a material to be crushed is crushed between the gyrated mantle and a concave, the oil supply method being for supplying lubricating oil to a first bearing section between the main shaft assembly and the eccentric bush section and to a second bearing section between the sleeve section and the bottom shell bush section, wherein both the lubricating oil for the first bearing section and the lubricating oil for the second bearing section are supplied from an oil supply inlet that opens in a bottom portion of the bottom shell assembly, wherein a partition plate is provided between a lower end portion of the sleeve section and a bottom portion of the bottom shell assembly, and flow rate of the lubricating oil supplied from the oil supply inlet to the first bearing section and flow rate of the lubricating oil supplied from the oil supply inlet to the second bearing section are controlled

6a

[0016] According to another mode of the present invention, there is provided an oil supply structure for a gyratory crusher, the gyratory crusher comprising: a bottom shell assembly having a bottom shell bush section; an eccentric sleeve assembly that has a sleeve section holding an eccentric bush section fitted to the bottom shell bush section and rotated and a flange section extending at an upper portion of the sleeve section; a main shaft assembly holding a mantle that is fitted to the eccentric bush section and gyrated; and a rotational power transmission system that transmits rotational power to the flange section, a material to be crushed being crushed between the gyrated mantle and a concave, the oil supply structure being for supplying lubricating oil to a first bearing section between the main shaft assembly and the eccentric bush section and to a second bearing section between the sleeve section and the bottom shell bush section, the oil supply structure comprising: a first oil supply inlet that opens in a bottom portion of the bottom shell assembly so as to enable oil supply to the first bearing section; a second oil supply inlet that opens in a circumferential surface of the bottom shell bush section so as to enable oil supply to the second bearing section; and an annular seal forming section that is provided inside the bottom shell assembly and has a non-contact surface facing an end face of a lower end portion of the sleeve section, wherein a gap between the non-contact surface of the seal forming section and the end face of the lower end portion of the sleeve section is sealed with the lubricating oil, a partition plate is disposed at an outer periphery of the annular seal forming section, and an annular oil sump section is formed between the partition plate and an outer peripheral surface of the lower end portion of the sleeve section.

[0017] In the oil supply structure according to the mode mentioned above, the oil sump section may be formed at a position above the gap.

[0018] According to another mode of the present invention, there is provided a gyratory crusher comprising: a bottom shell assembly having a bottom shell bush section; an eccentric sleeve assembly that has a sleeve section holding an eccentric bush section fitted to the bottom shell bush section and rotated and a flange section fixed to an upper portion of the eccentric bush section; a main shaft assembly holding a mantle that is fitted to the eccentric bush section and gyrated; and a rotational power transmission system that transmits rotational power to the flange section, wherein a material to be crushed is crushed between the gyrated mantle and a concave, the gyratory crusher further comprises an oil supply structure for supplying lubricating oil to a first bearing section between the main shaft assembly and the eccentric bush section and to a second bearing section between the sleeve section and the bottom shell bush section, the oil supply structure comprises: a first oil supply inlet that opens in a bottom portion of the bottom shell assembly so as to enable oil supply to the first bearing section; a second oil supply inlet that opens in a circumferential surface of the bottom shell bush section so as to enable oil supply to the second bearing section; and an annular seal forming section that is provided inside the bottom shell assembly and has a non-contact surface facing an end face of a lower end portion of the sleeve section, a gap between the non-contact surface of the seal forming section and the end face of the lower end portion of the sleeve section is sealed with the lubricating oil, a partition plate is disposed at an outer periphery of the annular seal forming section, and an annular oil sump section is formed between the partition plate and an outer peripheral surface of the lower end portion of the sleeve section.

[0019] According to another mode of the present invention, there is provided an oil supply method for a gyratory crusher, the gyratory crusher comprising: a bottom shell assembly having a bottom shell bush section; an eccentric sleeve assembly that has a sleeve section holding an eccentric bush section fitted to the bottom shell bush section and rotated and a flange section extending at an upper portion of the sleeve section; a main shaft assembly holding a mantle that is fitted to the eccentric bush section and gyrated; and a rotational power transmission system that transmits rotational power to the flange section, wherein a material to be crushed is crushed between the gyrated mantle and a concave, the oil supply method being for supplying lubricating oil to a first bearing section between the main shaft assembly and the eccentric bush section and to a second bearing section between the sleeve section and the bottom shell bush section, wherein both the lubricating oil for the first bearing section and the lubricating oil for the second bearing section are supplied from an oil supply inlet that opens in a bottom portion of the bottom shell assembly.

[0020] In the oil supply method according to the mode mentioned above, the eccentric bush section, the sleeve section or the bottom shell bush section may be provided with a longitudinal groove section, thereby to control flow rate of the lubricating oil supplied from the oil supply inlet to the first bearing section and flow rate of the lubricating oil supplied from the oil supply inlet to the second bearing section.

[0021] In the oil supply method according to the mode mentioned above, a partition plate may be provided between a lower end portion of the sleeve section and a bottom portion of the bottom shell assembly, thereby to control flow rate of the lubricating oil supplied from the oil supply inlet to the first bearing section and flow rate of the lubricating oil supplied from the oil supply inlet to the second bearing section.

[0022] According to another mode of the present invention, there is provided an oil supply structure for a gyratory crusher, the gyratory crusher comprising: a bottom shell assembly having a bottom shell bush section; an eccentric sleeve assembly that has a sleeve section holding an eccentric bush section fitted to the bottom shell bush section and rotated and a flange section extending at an upper portion of the sleeve section; a main shaft assembly holding a mantle that is fitted to the eccentric bush section and gyrated; and a rotational power transmission system that transmits rotational power to the flange section, wherein a material to be crushed is crushed between the gyrated mantle and a concave, the oil supply structure being for supplying lubricating oil to a first bearing section between the main shaft assembly and the eccentric bush section and to a second bearing section between the sleeve section and the bottom shell bush section, the oil supply structure comprising an oil supply inlet that opens in a bottom portion of the bottom shell assembly, wherein the oil supply inlet is configured so as to supply both the lubricating oil for the first bearing section and the lubricating oil for the second bearing section.

[0023] In the oil supply structure according to the mode mentioned above, the eccentric bush section, the sleeve section or the bottom shell bush section may be provided with a longitudinal groove section, thereby to control flow rate of the lubricating oil supplied from the oil supply inlet to the first bearing section and flow rate of the lubricating oil supplied from the oil supply inlet to the second bearing section.

[0024] In the oil supply structure according to the mode mentioned above, a partition plate for controlling flow rate of the lubricating oil supplied from the oil supply inlet to the first bearing section and flow rate of the lubricating oil supplied from the oil supply inlet to the second bearing section may be provided between a lower end portion of the sleeve section and a bottom portion of the bottom shell assembly.

[0024a] An aspect of the present invention provides an oil supply structure for a gyratory crusher, the gyratory crusher comprising: a bottom shell assembly having a bottom shell bush section; an eccentric sleeve assembly that has a sleeve section holding an eccentric bush section fitted to the bottom shell bush section and rotated and a flange section extending at an upper portion of the sleeve section; a main shaft assembly holding a mantle that is fitted to the eccentric bush section and gyrated; and a rotational power transmission system that transmits rotational power to the flange section, wherein a material to be crushed is crushed between the gyrated mantle and a concave, the oil supply structure being for supplying lubricating oil to a first bearing section between the main shaft assembly and the eccentric bush section and to a second bearing section between the sleeve section and the bottom shell bush section, the oil supply structure comprising an oil supply inlet that opens in a bottom portion of the bottom shell assembly, wherein the oil supply inlet is configured so as to supply both the lubricating oil for the first bearing section and the lubricating oil for the second bearing section; and a partition plate for controlling flow rate of the lubricating oil supplied from the oil supply inlet to the first bearing section and flow rate of the lubricating oil supplied from the oil supply inlet to the second bearing section is provided between a lower end portion of the sleeve section and a bottom portion of the bottom shell assembly

[0024b] An aspect of the present invention provides a gyratory crusher comprising: a bottom shell assembly having a bottom shell bush section; an eccentric sleeve assembly that has a sleeve section holding an eccentric bush section fitted to the bottom shell bush section and rotated and a flange section extending at an upper portion of the sleeve section; a main shaft assembly holding a mantle that is fitted to the eccentric bush section and gyrated; and a rotational power transmission system that transmits rotational power to the flange section, wherein a material to be crushed is crushed between the gyrated mantle and a concave, the gyratory crusher further comprises an oil supply structure for supplying lubricating oil to a first bearing section between the main shaft assembly and the eccentric bush section and to a second bearing section between the sleeve section and the bottom shell bush section, the oil supply structure has an oil supply inlet that opens in a bottom portion of the bottom shell assembly, the oil supply inlet is configured so as to supply both the lubricating oil for the first bearing section and the lubricating oil for the second bearing section; and a partition plate for controlling flow rate of the lubricating oil supplied from the oil supply inlet to the first bearing section and flow rate of the lubricating oil supplied from the oil supply inlet to the second bearing section is provided between a lower end portion of the sleeve section and a bottom portion of the bottom shell assembly

[0025] According to another mode of the present invention, there is provided an gyratory crusher comprising: a bottom shell assembly having a bottom shell bush section; an eccentric sleeve assembly that has a sleeve section holding an eccentric bush section fitted to the bottom shell bush section and rotated and a flange section extending at an upper portion of the sleeve section;

a main shaft assembly holding a mantle that is fitted to the eccentric bush section and gyrated; and a rotational power transmission system that transmits rotational power to the flange section, wherein a material to be crushed is crushed between the gyrated mantle and a concave, the gyratory crusher further comprises an oil supply structure for supplying lubricating oil to a first bearing section between the main shaft assembly and the eccentric bush section and to a second bearing section between the sleeve section and the bottom shell bush section, the oil supply structure has an oil supply inlet that opens in a bottom portion of the bottom shell

11a

assembly, and the oil supply inlet is configured so as to supply both the lubricating oil for the first bearing section and the lubricating oil for the second bearing section.

Advantageous Effects of Invention

[0026] According to preferred embodiments of the present invention, in the type serviced through an opening at the top for excellent serviceability, the quantities of oil supplied can be controlled for maintaining sound oil films in bearing sections.

BRIEF DESCRIPTION OF DRAWINGS

[0027] [FIG. 1]

FIG. 1 is a vertical sectional view of a gyratory crusher according to an embodiment of the present invention.

[FIG. 2]

FIG. 2 is a schematic view showing in an enlarged form an oil supply structure in the gyratory crusher of FIG. 1.

[FIG. 3]

FIG. 3 is a schematic view showing a comparative example of the oil supply structure in a top opening type gyratory crusher.

[FIG. 4]

FIG. 4 is a vertical sectional view of a gyratory crusher 20 according to an embodiment of the present invention.

[FIG. 5]

FIG. 5 is a schematic view showing in an enlarged form an oil supply structure in the gyratory crusher of FIG. 4.

11b

[FIG. 6]

FIG. 6 is a horizontal sectional view showing an oil film formed at a first bearing section of the gyratory crusher of FIG. 4.

[FIG. 7]

FIG. 7 is a graph showing pressure of the oil film of FIG. 6.

[FIG. 8]

FIG. 8 is a graph showing outflow (inflow) quantity distribution of lubricating oil in a gap between a seal forming section and a sleeve section.

[FIG. 9]

FIG. 9 is a schematic view showing a comparative example of an oil supply structure of a top opening type gyratory crusher.

[FIG. 10]

FIG. 10 is a vertical sectional view of a gyratory crusher according to an embodiment of the present invention.

[FIG. 11] FIG. 11 is a schematic view showing in an enlarged form an oil supply structure in the gyratory crusher of FIG. 10.

[FIG. 12] FIG. 12 is a horizontal sectional view of a bearing section of the gyratory crusher of FIG. 10, for explaining a longitudinal groove section.

[FIG. 13] FIG. 13 is a schematic view showing a modification of an oil supply structure, which is a drawing corresponding to FIG. 11.

[FIG. 14] FIG. 14 is a schematic view showing a comparative example of an oil supply structure of a top opening type gyratory crusher.

Description of Embodiments

[0028] Embodiments of the present invention will be described specifically below, referring to the drawings. Note that in the attached drawings, for convenience of easy illustration and understanding, reduction scale and vertical/horizontal dimensional ratio and the like are exaggerated by changing them from the actual ones, as required.

[0029]

[First Embodiment] FIG. 1 is a vertical sectional view of a gyratory crusher according to an embodiment of the present invention.

[0030] As shown in FIG. 1, a gyratory crusher 10 according to this embodiment includes following components: a top shell assembly 11 that holds a concave 12; a bottom shell assembly 13 having a bottom shell bush section 13a that is disposed under the top shell assembly 11; an eccentric sleeve assembly 14 rotated inside the bottom shell bush section 13a; a main shaft assembly 15 holding a mantle 17 that is fitted to the eccentric sleeve assembly 14 and gyrated; and a rotational power transmission system 20 that transmits rotational power to the eccentric sleeve assembly 14.

[0031] Of these components, the eccentric sleeve assembly 14 has an eccentric bush section 14a that is fitted to the bottom shell bush section 13a of the bottom shell assembly 13 and rotated, and a flange section 14b that is fixed to an upper portion of the eccentric bush section 14a. The flange section 14b extends from an upper portion of the eccentric bush section 14a into a gear space 40 outside the bottom shell bush section 13a, and is supported from below by a thrust bearing 19 provided at an upper end portion of the bottom shell bush section 13a. In this embodiment, the flange section 14b is fixed to an upper portion of the eccentric bush section 14a, which ensures that the eccentric sleeve assembly 14 can be drawn out upward from the bottom shell assembly 13. A bevel gear 21a is fixed to a tip portion of the flange section 14b. The bevel gear 21a is disposed coaxially with a rotational axis of the eccentric bush section 14a.

[0032] The rotational power transmission system 20 has a pinion shaft 22 connected to a driving motor (not shown), and a bevel pinion 21b fixed to one end portion of the pinion shaft 22. The pinion shaft 22 is orientated in a direction perpendicular to the rotational axis of the eccentric bush section 14a. The bevel pinion 21b fixed to one end of the pinion shaft 22 is disposed in such a manner as to mesh with the bevel gear 21a fixed to the flange section 14b. When the pinion shaft 22 and the bevel pinion 21b are rotated as one body by rotational power of the driving motor, the rotational power is transmitted from the bevel pinion 21b to the bevel gear 21a, so that the bevel gear 21a, the flange section 14b, and the eccentric bush section 14a are driven to rotate as one body about the rotational axis of the eccentric bush section 14a.

[0033] The eccentric bush section 14a is formed at an eccentric position therein with a through-hole extending in a direction inclined relative to the rotational axis of the eccentric bush section 14a, and the main shaft assembly 15 is inserted in the through-hole in the eccentric bush section 14a. A funnel-shaped mantle 17 is fixed to an upper portion of the main shaft assembly 15.

[0034] In the example illustrated, the gyratory crusher 10 is a so-called hydraulic cone crusher, in which an upper end portion of the main shaft assembly 15 is supported by a bearing 23 held by the top shell assembly 11. On the other hand, a main shaft step 15a having a convex spherical surface is fixed to a lower end portion of the main shaft assembly 15, and a step washer 13c having a concave spherical surface and a plain bearing 13b supporting the back surface of the step washer 13c are disposed in a stacked state under the main shaft step 15a. The Plain bearing 13b is fixed to a bottom portion of the bottom shell assembly 13, more specifically to a ram of a hydraulic cylinder assembly disposed under the bottom shell assembly 13. The convex spherical surface of the main step 15a and the concave spherical surface of the step washer 13c form a sliding section which slides.

[0035] When the flange section 14b and the eccentric bush section 14a of the eccentric sleeve assembly 14 are rotated as one body by the rotational power transmission system 20, the main shaft assembly 15 is put into precession around the rotational axis of the eccentric bush section 14a, with the bearing 23 as a fulcrum. The mantle 17 is put into precession relative to the concave 12 according to the precession of the main shaft assembly 15, thereby crushing a material to be crushed which is supplied into a crushing chamber 18 defined between the mantle 17 and the concave 12.

[0036] During operation of the gyratory crusher 10, sound oil films should be maintained by supplying appropriate quantities of lubricating oil to a first bearing section 41 between the main shaft assembly 15 and the eccentric bush section 14a and a second bearing section 42 between the eccentric bush section 14a and the bottom shell bush section 13a, in order to ensure smooth precession of the main shaft assembly 15 on which a high load is exerted. For this reason, the gyratory crusher 10 is provided with an oil supply structure 30 for supplying the lubricating oil to the first bearing section 41 and to the second bearing section 42.

[0037] FIG. 2 is a schematic view showing the oil supply structure 30 in an enlarged form. In FIG. 2, arrows indicate directions in which the lubricating oil flows.

[0038] As shown in FIG. 2, the oil supply structure 30 includes following components: an annular thrust seal 33 that is disposed inside the bottom shell assembly 13 and supports from below a lower end portion of the eccentric bush section 14a; a first oil supply inlet 31 opening in a bottom portion of the bottom shell assembly 13, more specifically in a ram central portion of the hydraulic cylinder assembly, so as to supply the lubricating oil to the first bearing section 41; and a second oil supply inlet 32 opening in an inner peripheral surface of the bottom shell bush section 13a so as to supply the lubricating oil to the second bearing section 42.

[0039] Specifically, the thrust seal 33 is, for example, a metallic annular ring (circular ring) having a parallel plate-shaped vertical section. In the illustrated example, an annular thrust seal fitting frame 34 is fixed to a bottom portion of the bottom shell assembly 13, in such a manner as to surround the outside of the first oil supply inlet 31. An annular stepped portion 35 is projectingly provided at an upper end portion of the thrust seal fitting frame 34, and the thrust seal 33 is fitted to an inner diameter side of the stepped portion 35 and is supported from below. A lower end face of the eccentric bush section 14a is pressed against and in surface contact with an upper surface of the thrust seal 33, due to the weight of the eccentric sleeve assembly 14. The lower end face of the eccentric bush section 14a is preferably chamfered or worked to be flat, for enlarging the area of contact thereof with the upper surface of the thrust seal 33.

[0040] In the illustrated example, a through-hole 36 is formed to penetrate a central portion of the plain bearing 13b and a central portion of the step washer 13c, and the first oil supply inlet 31 opens to the inside of the through-hole 36. As shown in FIG. 2, the lubricating oil introduced through the first oil supply inlet 31 into the through-hole 36 flows into an inner diameter side end portion of the sliding section between the plain bearing 13b and the step washer 13c and into an inner diameter side end portion of the sliding section between the step washer 13c and the main shaft step 15a, and lubricates each of the sliding sections. The lubricating oil having passed each sliding section flows out from an outer diameter side end portion of each sliding section into an annular space 37 outside a lower end portion of the main shaft assembly 15, and flows through the annular space 37 into a lower end portion of the first bearing section 41, to lubricate the first bearing section 41. The lubricating oil having passed the first bearing section 41 flows out from an upper end portion of the first bearing section 41 into a gear accommodating space 40 outside the bottom shell bush section 13a, and the lubricating oil collecting on a floor of the gear accommodating space 40 is recovered through an oil supply outlet 39 depicted in FIG. 1.

[0041] On the other hand, part of the lubricating oil introduced through the second oil supply inlet 32 into the second bearing section 42 flows into that region of the second bearing section 42 which is on the lower side of the second oil supply inlet 32, to lubricate the lower region. Then, the lubricating oil having passed the lower region of the second bearing section 42 flows out from a lower end portion of the second bearing section 42 into an annular space 38 provided thereunder, and the lubricating oil collecting on a floor of the annular space 38 is recovered through the oil supply outlet 39 depicted in FIG. 1. In addition, the remaining portion of the lubricating oil introduced directly from the second oil supply inlet 32 into the second bearing section 42 flows into that region of the second bearing section 42 which is on the upper side of the second oil supply inlet 32, to lubricate the upper region. Then, the lubricating oil having passed the upper region of the second bearing section 42 flows out from an upper end portion of the second bearing section 42 into the gear accommodating space 40 outside the bottom shell bush section 13a, and the lubricating oil collecting on a floor of the gear accommodating space 40 is recovered through the oil supply outlet 39 depicted in FIG. 1.

[0042] Meanwhile, FIG. 3 is a schematic view showing a comparative example of the oil supply structure in a top opening type gyratory crusher. In FIG. 3, arrows indicate directions in which the lubricating oil flows. In a gyratory crusher serviced through an opening at the top as shown in FIG. 3, a flange section 114b is supported from below by a thrust bearing 119 provided at an upper end portion of a bottom shell bush section 113a, but a thrust seal is not disposed at a lower end portion of an eccentric bush section 115a, and a flow channel for lubricating oil supplied from a first oil supply inlet 131 to a first bearing section 141 and a flow channel for lubricating oil supplied from a second oil supply inlet 132 to a second bearing section 142 are structurally not separated from each other. Particularly, an oil supply outlet side 152 of the second bearing section 142 and an oil supply inlet side 151 of the first bearing section 141 communicate with each other. For this reason, the quantities of lubricating oil distributed to the bearing sections 141 and 142 are instable, and, particularly under bad conditions, it may be difficult to maintain sound oil films.

[0043] On the other hand, in this embodiment, as illustrated in FIG. 2, the lower end face of the eccentric bush section 14a is in surface contact with the upper surface of the thrust seal 33, whereby the annular space 37 outside the lower end portion of the main shaft assembly 15 and the annular space 38 provided under the lower end portion of the second bearing section 42 are structurally separated from each other. This ensures that the flow channel for the lubricating oil supplied from the first oil supply inlet 31 to the first bearing section 41 and the flow channel for the lubricating oil supplied from the second oil supply inlet 32 to the second bearing section 42 are substantially separated from each other, resulting in that it is possible to control oil supply quantities for maintaining sound oil films in the first bearing section 41 and the second bearing section 42.

[0044] In addition, in this embodiment, an inner peripheral surface of the stepped portion 35 projectingly provided on the outer diameter side of the thrust seal 33 surrounds an outer peripheral surface of the lower end portion of the eccentric bush section 14a supported by the thrust seal 33. It is preferable that the gap between the inner peripheral surface of the stepped portion 35 and the outer peripheral surface of the lower end portion of the eccentric bush section 14a is narrow. For the lubricating oil wetting between the lower end face of the eccentric bush section 14a and the upper surface of the thrust seal 33, the stepped portion 35 projectingly provided on the outer diameter side of the thrust seal 33 functions as a resistance to flow. Therefore, even when the lubricating oil wetting between the lower end face of the eccentric bush section 14a and the upper surface of the thrust seal 33 receives exerted thereon an outward force attendant on an eccentric motion of the main shaft assembly 15, the lubricating oil can be restrained from jetting toward the outside.

[0045] Now, an operation of the gyratory crusher 10 according to this embodiment will be described below.

[0046] First, the lubricating oil is supplied through the first oil supply inlet 31 to the first bearing section 41, and the lubricating oil is supplied from the second oil supply inlet 32 to the second bearing section 42. In this embodiment, the thrust seal 33 structurally separates the flow channel for the lubricating oil supplied to the first bearing section 41 and the flow channel for the lubricating oil supplied to the second bearing section 42; therefore, the lubricating oil can be supplied independently to the first bearing section 41 and to the second bearing section 42, and the quantities of the lubricating oil supplied can be controlled in such a manner as to maintain sound oil films respectively in the first bearing section 41 and the second bearing section 42.

[0047] Next, rotational power is transmitted from the rotational power transmission system 20 to the flange section 14b of the eccentric sleeve assembly 14, and the flange section 14b and the eccentric bush section 14a are rotated as one body about the rotational axis of the eccentric bush section 14a. Attendant on the rotation of the eccentric bush section 14a, the main shaft assembly 15 fitted to the eccentric bush section 14a is put into precession, with the bearing 23 as a fulcrum. The mantle 17 fixed to the main shaft assembly 15 is put into precession relative to the concave 12 according to the precession of the main shaft assembly 15, and the gap between the mantle 17 and the concave 12 is changed to be wider and narrower in accordance with each revolution.

[0048] Subsequently, a material to be crushed, such as raw ore or rough stones, is charged through a hopper 25 at an upper portion of the top shell assembly 11. The material to be crushed thus charged drops into the crushing chamber 18 defined between the mantle 17 and the concave 12, and is trapped between the mantle 17 and the concave 12. When the mantle 17 is gyrated and the gap between the mantle 17 and the concave 12 is narrowed, the material to be crushed is crushed under pressure.

[0049] Thereafter, when the gap between the mantle 17 and the concave 12 is widened, the material to be crushed drops into that part of the inside of the crushing chamber 18 at which the gap between the mantle 17 and the concave 12 is wider, and, when the gap between the mantle 17 and the concave 12 is again narrowed, the material is crushed further finely under pressure. The material to be crushed is gradually made finer through repetition of the dropping and crushing under pressure, to be a product having a predetermined grain size, which drops through the gap between the mantle 17 and the concave 12 onto the floor, to be discharged to the exterior of the machine through an opening in the floor.

[0050] During the operation of the gyratory crusher 10, the quantities of the lubricating oil supplied are controlled so as to maintain sound oil films in the first bearing section 41 and the second bearing section 42, whereby the frequency of replacement of the lubricating oil is reduced, and the bearing sections 41 and 42 can be prevented from being broken due to seizure or the like.

[0051] According to this embodiment as above, the flange section 14b of the eccentric sleeve assembly 14 is fixed to an upper portion of the eccentric bush section 14a, so that the eccentric sleeve assembly 14 can be drawn out upward from the bottom shell assembly 13. Thus, in the case where the bearing sections 41 and 42 or the gears 21a and 21b are broken, servicing operations for the bearing sections 41 and 42 or the gears 21a and 21b can be performed by drawing out the eccentric sleeve assembly 14 upward. Therefore, it is unnecessary to disassemble the hydraulic cylinder assembly disposed under the bottom shell assembly 13. In addition, a dangerous work to be performed by a worker situated under a suspended load is not needed. Thus, superior serviceability can be obtained as compared to the type serviced through an opening at the bottom.

[0052] Besides, according to this embodiment, the annular thrust seal 33 disposed inside the bottom shell assembly 13 and supporting the lower end portion of the eccentric bush section 14a from below separates the flow channel for the lubricating oil supplied from the first oil supply inlet 31 to the first bearing section 41 and the flow channel for the lubricating oil supplied from the second oil supply inlet 32 to the second bearing section 42, so that it is possible to control the quantities of the lubricating oil supplied so as to maintain sound oil films in the first bearing section 41 and the second bearing section 42. Accordingly, the frequency of replacement of the lubricating oil is reduced, and the bearing sections 41 and 42 can be prevented from being broken due to seizure or the like.

[0053] In addition, according to this embodiment, the inner peripheral surface of the stepped portion 35 surrounds the outer peripheral surface of the lower end portion of the inner cylinder section 14a, so that, for the lubricating oil wetting between the lower end face of the eccentric bush section 14a and the upper surface of the thrust seal 33, the stepped portion 35 functions as a resistance to flow. Therefore, even when the lubricating oil wetting between the lower end face of the eccentric bush section 14a and the upper surface of the thrust seal 33 receives exerted thereon an outward force attendant on the eccentric motion of the main shaft assembly 15, the lubricating oil can be restrained from jetting toward the outside.

[0054] Besides, according to this embodiment, the thrust bearing 19 supporting the flange section 14b from below is provided at the upper end portion of the outer cylinder section 13a, so that the load of the eccentric sleeve 14 is dispersed to the thrust seal 33 and the thrust bearing 19. This makes it possible to retard wear of the thrust seal 33.

[0055] Note that the thrust bearing 19 may not necessarily be provided at the upper end portion of the outer cylinder section 13a. In other words, the thrust bearing 19 can be omitted from the upper end portion of the outer cylinder section 13a.

[0056] In a mode in which the thrust bearing 19 is provided at the upper end portion of the outer cylinder section 13a, the load exerted on the upper surface of the thrust seal 33 from the lower end face of the inner cylinder section 14a may become insufficient, or a gap may be generated between the lower end face of the inner cylinder section 14a and the upper surface of the thrust seal 33 due to assembly tolerance.

[0057] On the other hand, in a mode in which the thrust bearing 19 is omitted from the upper end portion of the outer cylinder section 13a, a sufficient load is exerted on the upper surface of the thrust seal 33 from the lower end face of the inner cylinder section 14a, so that the separation between the flow channel for the lubricating oil supplied to the first bearing section 41 and the flow channel for the lubricating oil supplied to the second bearing section 42 can be ensured more reliably.

[0058] Note that while the gyratory crusher 10 has been a so-called hydraulic cone crusher in the example shown in FIG. 1, this is not restrictive. For example, the oil supply structure 30 according to this embodiment is also applicable to a mechanical (Symons) cone crusher.

[0059]

[Second Embodiment] FIG. 4 is a vertical sectional view of a gyratory crusher according to an embodiment of the present invention.

[0060] As shown in FIG. 4, a gyratory crusher 210 according to this embodiment includes following components: a top shell assembly 211 holding a concave 212; a bottom shell assembly 213 that has a bottom shell bush section 213a disposed under the top shell assembly 211; an eccentric sleeve assembly 214 rotated inside the bottom shell bush section 213a; a main shaft assembly 215 holding a mantle 217 that is fitted to the eccentric sleeve assembly 214 and gyrated; and a rotational power transmission system 220 that transmits rotational power to the eccentric sleeve assembly 214.

[0061]

Of these components, the eccentric sleeve assembly 214 has a sleeve section 214c that holds an eccentric bush section 214a fitted to the bottom shell bush section 213a of the bottom shell assembly 213 and rotated, and a flange section 214b that is fixed to an upper portion of the sleeve section 214c. The flange section 214b extends from an upper portion of the sleeve section 214c into a gear accommodating space 240 formed outside the bottom shell bush section 213a, and is supported from below by a thrust bearing 219 provided at an upper end portion of the bottom shell bush section 213a. In this embodiment, since the flange section 214b extends at an upper portion of the sleeve section 214c, the eccentric sleeve assembly 214 can be drawn out upward from the bottom shell assembly 213. A bevel gear 221a is fixed to a tip portion of the flange section 214b. The bevel gear 221a is disposed coaxially with a rotational axis of the bottom shell bush section 213a.

[0062] The rotational power transmission system 220 has a pinion shaft 222 connected to a driving motor (not shown), and a bevel pinion 221b fixed to one end portion of the pinion shaft 222. The pinion shaft 222 is oriented in a direction perpendicular to the rotational axis of the bottom shell bush section 213a. The bevel pinion 221b fixed to one end of the pinion shaft 222 is disposed in such a manner as to mesh, in the gear accommodating space 240, with the bevel gear 221a fixed to the flange section 214b. When the pinion shaft 222 and the bevel pinion 221b are rotated as one body by rotational power of the driving motor, the rotational power is transmitted from the bevel pinion 221b to the bevel gear 221a, whereby the eccentric sleeve assembly 214 is driven to rotate about the rotational axis of the bottom shell bush section 213a.

[0063] The sleeve section 214c is formed therein with a through-hole extending in a direction inclined relative to the rotational axis of the bottom shell bush section 213a, and the eccentric bush section 214a is fitted in the through-hole extending in the inclined direction. The main shaft assembly 215 is inserted in the eccentric bush section 214a. A funnel-shaped mantle 217 is fixed to an upper portion of the main shaft assembly 215.

[0064] In the illustrated example, the gyratory crusher 210 is a so-called hydraulic cone crusher, and an upper end portion of the main shaft assembly 215 is supported by a bearing 223 held by the top shell assembly 211. On the other hand, a main shaft step 215a having a convex spherical surface is fixed to a lower end portion of the main shaft assembly 215, and a step washer 213c having a concave spherical surface and a plain bearing 213b supporting a back surface of the step washer 213c are disposed in a stacked state under the main shaft step 215a. The Plain bearing 213b is fixed to a bottom portion of the bottom shell assembly 213, more specifically to a ram of a hydraulic cylinder assembly disposed under the bottom shell assembly 213. The convex spherical surface of the main shaft step 215a and the concave spherical surface of the step washer 213c form a sliding section that slides.

[0065] When the eccentric sleeve assembly 214 is rotated by the rotational power transmission system 220, the main shaft assembly 215 is put into precession about the rotational axis of the eccentric bush section 214a, with the bearing 223 as a fulcrum. The mantle 217 is put into precession relative to the concave 212 according to the precession of the main shaft assembly 215, whereby a material to be crushed which is supplied into a crushing chamber 218 defined between the mantle 217 and the concave 212 is crushed.

[0066] During the operation of the gyratory crusher 210, sound oil films should be maintained by supplying appropriate quantities of the lubricating oil to the first bearing section 241 between the main shaft assembly 215 and the eccentric bush section 214a and to the second bearing section 242 between the sleeve section 214c and the bottom shell bush section 213a, in order to ensure smooth precession of the main shaft assembly 215 on which a high load is exerted. For this reason, the gyratory crusher 210 is provided with an oil supply structure 230 for supplying the lubricating oil to the first bearing section 241 and to the second bearing section 242.

[0067] FIG. 5 is a schematic view showing the oil supply structure 230 in an enlarged form. In FIG. 5, arrows indicate directions in which the lubricating oil flows.

[0068] As shown in FIG. 5, the oil supply structure 230 includes following components: a first oil supply inlet 231 opening in a bottom portion of the bottom shell assembly 213, more specifically in a ram central portion of the hydraulic cylinder assembly so as to supply the lubricating oil to the first bearing section 241; a second oil supply inlet 232 opening in an inner peripheral surface of the bottom shell bush section 213a so as to supply the lubricating oil to the second bearing section 242; and an annular seal forming section 234 that is provided inside bottom shell assembly 213 and has a non-contact surface facing an end face of a lower end portion of the sleeve section 214c.

[0069] In the illustrated example, the seal forming section 234 is provided to project upward from an inner surface of the bottom shell assembly 213, and is provided with the non-contact surface at an upper end portion thereof. Since the flange section 214b of the eccentric sleeve assembly 214 is supported from below by the thrust bearing 219, the sleeve section 214c of the eccentric sleeve assembly 214 is positioned at a predetermined-height position, whereby a gap 233 having a predetermined spacing is formed between the non-contact surface of the seal forming section 234 and the end face of the lower end portion of the sleeve section 214c.

[0070] The gap 233 formed between the non-contact surface of the seal forming section 234 and the end face of the lower end portion of the sleeve section 214c is sealed with the lubricating oil, and is adjusted to such a spacing as to prevent the lubricating oil supplied through the first oil supply inlet 231 from flowing into the second bearing section 242. Specifically, the spacing of the gap 233 is, for example, about 0.5 to 1.0 mm, but is not limited to a value in this range.

[0071] As shown in FIG. 5, a partition plate 235 is disposed at an outer periphery of the annular seal forming section 234. The partition plate 235 is provided so as to surround an outer peripheral surface of a lower end portion of the sleeve section 214c under the second bearing section 242, and an annular oil sump section 250 is formed between an inner peripheral surface of the partition plate 235 and the outer peripheral surface of the lower end portion of the sleeve section 214c. Part of the lubricating oil flowing out from a lower end portion of the second bearing section 242 is collected in the oil sump section 250. The oil sump section 250 communicates with the gap 233 between the non-contact surface of the seal forming section 234 and the end face of the lower end portion of the sleeve section 214c.

[0072] An operation of the oil sump section 250 attendant on the rotation of the eccentric sleeve assembly 214 will be described below, referring to FIGS. 6 to 8.

[0073] FIG. 6 is a horizontal sectional view showing an oil film formed in the first bearing section 241 of the gyratory crusher 210. In FIG. 6, in regard of phase of the eccentric sleeve assembly 214, a phase at which the spacing between the outer peripheral surface of the main shaft assembly 215 and the inner peripheral surface of the eccentric bush section 214a is maximized is assumed to be e = 00, whereas a phase at which the spacing is minimized is assumed to be e= 1800, and the clockwise direction is assumed to be a positive direction.

[0074] In FIG. 6, the eccentric sleeve assembly 214 is rotating clockwise, whereby a part at which the spacing between the outer peripheral surface of the main shaft assembly 215 and the inner peripheral surface of the eccentric bush section 214a is minimized (a part corresponding to the phase of 6 = 1800) is also rotated clockwise. Since the part at which the spacing between the outer peripheral surface of the main shaft assembly 215 and the inner peripheral surface of the eccentric bush section 214a is minimized (the part corresponding to the phase of e= 1800) is rotated clockwise, the lubricating oil supplied to the first bearing section 241 is pushed out clockwise while being press-held between the outer peripheral surface of the main shaft assembly 215 and the inner peripheral surface of the eccentric bush section 214a. As a result, as shown in FIG. 6, at the first bearing section 241 between the outer peripheral surface of the main shaft assembly 215 and the inner peripheral surface of the eccentric bush section 214a, an oil film is formed ranging from the vicinity of the part corresponding to the phase of 6 = 1800 to the part corresponding to the phase of6 = 0°.

[0075] FIG. 7 shows pressure distribution in the oil film. In that region of the first bearing section 241 which is adjacent in the clockwise direction to the phase of e= 1800, the eccentric sleeve assembly 214 is rotated clockwise, whereby the oil film is pressed flat between the outer peripheral surface of the main shaft assembly 215 and the inner peripheral surface of the eccentric bush section 214a, so that the pressure of the oil film increases.

[0076] As a result, as shown in FIG. 8, in that region of the gap 233 between the non-contact surface of the seal forming section 234 and the end face of the lower end portion of the sleeve section 214c which corresponds to the phase ranging from the vicinity of e= 1800 to 3600, the lubricating oil in the gap 233 receives a pressure from the oil film formed at the first bearing section 241, whereby a flow of the lubricating oil in a direction for flowing out from the gap 233 to the oil sump section 250 is generated.

[0077]

On the other hand, though not shown in FIG. 7, in that region of the first bearing section 241 which is adjacent in a counterclockwise direction to the phase of 6 = 1800, due to clockwise rotation of the eccentric sleeve assembly 214, the oil film is lost and the gap between the outer peripheral surface of the main shaft assembly 215 and the inner peripheral surface of the eccentric bush section 214a is widened, so that a negative pressure is generated in that space.

[0078] As a result, as shown in FIG. 8, in that region of the gap 233 between the non-contact surface of the seal forming section 234 and the end face of the lower end portion of the sleeve section 214c which corresponds to the phase ranging from e = 0° to the vicinity of 1800, the lubricating oil in the gap 233 receives the negative pressure generated in the first bearing section 241, whereby a flow of the lubricating oil in a direction for flowing from the gap 233 into the first bearing section 241 is generated.

[0079] Here, as a comparative example, a mode in which the oil sump section 250 is not formed outside the gap 233 is considered. In this mode, when the flow of the lubricating oil in the direction for flowing from the gap 233 into the first bearing section 241 is generated by the rotation of the eccentric sleeve assembly 214, if air in the annular space 238 is sucked into the gap 233 and air bubbles are mixed into the lubricating oil, there is a high possibility of generation of oil film breakage, which is one of causes of bearing breakage, in the inside of the first bearing section 241.

[0080] On the other hand, in this embodiment, since the oil sump section 250 is formed outside the gap 233, when the flow of the lubricating oil in the direction for flowing from the gap 233 into the first bearing section 241 is generated by the rotation of the eccentric sleeve assembly 214, the lubricating oil collected in the oil sump section 250 is sucked into the gap 233. As a result, a situation in which air in the annular space 238 is sucked into the gap 233 with the result of mixing of air bubbles into the lubricating oil is effectively prevented.

[0081] As illustrated in the drawing, the oil sump section 250 is preferably formed at a position higher than the gap 233. In this case, since the lubricating oil collected in the oil sump section 250 is collected to the gap 233 side due to gravity, it is ensured that the lubricating oil collected in the oil sump section 250 is sucked into the gap 233 when the flow of the lubricating oil in the direction for flowing from the gap 233 into the first bearing section 241 is generated by the rotation of the eccentric sleeve assembly 214. Consequently, air in the annular space 238 can be more reliably prevented from being sucked into the gap 233.

[0082] In the illustrated example, a through-hole 236 is formed to penetrate a central portion of the plain bearing 213b and a central portion of the step washer 213c, and the first oil supply inlet 231 opens inside the through-hole 236. As shown in FIG. 5, the lubricating oil introduced through the first oil supply inlet 231 into the through-hole 236 flows into an inner diameter side end portion of the sliding section between the plain bearing 213b and the step washer 213c and into an inner diameter side end portion of the sliding section between the step washer 213c and the main shaft step 215a, to lubricate each of the sliding sections. Then, the lubricating oil having passed each sliding section flows out from an outer diameter side end portion of each sliding section into the annular space 237 outside the lower end portion of the main shaft assembly 215, and flows through the annular space 237 into a lower end portion of the first bearing section 241, to lubricate the first bearing section 241. Subsequently, the lubricating oil having passed the first bearing section 241 flows out from an upper end portion of the first bearing section 241 into the gear accommodating space 240 outside the bottom shell bush section 213a, and the lubricating oil collecting on a floor of the gear accommodating space 240 is recovered through the oil supply outlet 239 depicted in FIG. 4.

[0083] On the other hand, part of the lubricating oil introduced through the second oil supply inlet 232 into the second bearing section 242 flows into that region of the second bearing section 242 which is on the lower side of the second oil supply inlet 232, to lubricate the lower region. Then, the lubricating oil having passed the lower region of the second bearing section 242 flows out from a lower end portion of the second bearing section 242, to be collected in the oil sump section 250 provided thereunder. The lubricating oil flowing over from the oil sump section 250 flows into the annular space 238 on the outside thereof, and the lubricating oil collecting on the floor of the annular space 238 is recovered through the oil supply outlet 239 depicted in FIG. 4. In addition, the remaining portion of the lubricating oil introduced directly into the second bearing section 242 from the second oil supply inlet 232 flows into that region of the second bearing section 242 which is on the upper side of the second oil supply inlet 232, to lubricate the upper region. Then, the lubricating oil having passed the upper region of the second bearing section 242 flows out from an upper end portion of the second bearing section 242 into the gear accommodating space 240 outside the bottom shell bush section 213a, and the lubricating oil collecting on a floor of the gear accommodating space 240 is recovered through the oil supply outlet 239 depicted in FIG. 4.

[0084] Meanwhile, FIG. 9 is a schematic view showing a comparative example of an oil supply structure in a top opening type gyratory crusher. In FIG. 9, arrows indicate directions in which lubricating oil flows. In the gyratory crusher of the type serviced through an opening at the top as shown in FIG. 9, a flow channel for the lubricating oil supplied from a first oil supply inlet 2131 to a first bearing section 2141 and a flow channel for the lubricating oil supplied from a second oil supply inlet 2132 to a second bearing section 2142 are structurally not separated from each other. Particularly, an oil supply outlet side 2152 of the second bearing section 2142 and an oil supply inlet side 2151 of the first bearing section 2141 communicate with each other, so that the lubricating oil supplied from the first oil supply inlet 2131 flows into not only the first bearing section 2141 but also into the second bearing section 2142. Therefore, the quantities of the lubricating oil distributed to the bearing sections 2141 and 2142 are instable, and, particularly under bad conditions, it may be difficult to maintain sound oil films.

[0085] On the other hand, in this embodiment, as shown in FIG. 5, the seal forming section 234 is provided inside the bottom shell assembly 213, and the gap 233 between the non-contact surface of the seal forming section 234 and the end face of the lower end portion of the sleeve section 214c is sealed with the lubricating oil, so that the lubricating oil can be independently supplied to the first bearing section 241 and to the second bearing section 242. Therefore, the quantities of the lubricating oil supplied can be controlled in such a manner that sound oil films are maintained in the first bearing section 241 and the second bearing section 242.

[0086] An operation of the gyratory crusher 210 according to this embodiment will be described below.

[0087] First, the lubricating oil is supplied through the first oil supply inlet 231 to the first bearing section 241, and the lubricating oil is supplied through the second oil supply inlet 232 to the second bearing section 242. In addition, rotational power is transmitted from the rotational power transmission system 220 to the flange section 214b of the eccentric sleeve assembly 214, and the eccentric sleeve assembly 214 is rotated about a rotational axis of the bottom shell bush section 213a.

[0088] In this embodiment, during the rotation of the eccentric sleeve assembly 214, the lubricating oil supplied from the first oil supply inlet 231 is prevented from flowing into the second bearing section 242, by the gap 233 between the non-contact surface of the seal forming section 234 and the end face of the lower end portion of the sleeve section 214c. Therefore, by controlling the quantities of the lubricating oil supplied to the bearing sections 241 and 242, it is possible to maintain sound oil films in the first bearing section 241 and the second bearing section 242.

[0089] Attendant on the rotation of the eccentric sleeve assembly 214, the main shaft assembly 215 fitted to the eccentric bush section 214a is put into precession, with the bearing 223 as a fulcrum. The mantle 217 fixed to the main shaft assembly 215 is put into precession relative to the concave 212 according to the precession of the main shaft assembly 215, and the gap between the mantle 217 and the concave 212 is changed to be wider and narrower in accordance with each revolution.

[0090] Next, a material to be crushed, such as raw ore or rough stones, is charged through a hopper 25 at an upper portion of the top shell assembly 211. The material to be crushed thus charged drops into the crushing chamber 218 defined between the mantle 217 and the concave 212, and is trapped between the mantle 217 and the concave 212. When the mantle 217 is gyrated and the gap between the mantle 217 and the concave 212 is narrowed, the material to be crushed is crushed under pressure.

[0091] Thereafter, when the gap between the mantle 217 and the concave 212 is widened, the material to be crushed drops into that part of the inside of the crushing chamber 218 at which the gap between the mantle 217 and the concave 212 is wider, and, when the gap between the mantle 217 and the concave 212 is again narrowed, the material to be crushed is further finely crushed under pressure. The material to be crushed becomes gradually finer through repetition of the crushing under pressure and dropping, to be a product having a predetermined grain size, which drops through the gap between the mantle 217 and the concave 212 onto a floor, and is discharged to the exterior of the machine through an opening in the floor.

[0092]

During the operation of the gyratory crusher 210, the quantities of the lubricating oil supplied which are sufficient for maintaining sound oil films at the first bearing section 241 and the second bearing section 242 can be controlled stably and independently, so that the bearing sections 241 and 242 can be prevented from being broken due to seizure or the like.

[0093] According to this embodiment as above, since the flange section 214b of the eccentric sleeve assembly 214 extends at an upper portion of the sleeve section 214c, the eccentric sleeve assembly 214 can be drawn out upward from the bottom shell assembly 213, and, in the case where the bearing sections 241 and 242 or the gears 221a and 221b are broken, servicing work for the bearing sections 241 and 242 or the gears 221a and 221b can be performed by drawing out the eccentric sleeve assembly 214 upward. Therefore, it is unnecessary to disassemble the hydraulic cylinder assembly disposed under the bottom shell assembly 213, and a dangerous work to be performed by a worker situated under a suspended load is not needed. Thus, it is possible to obtain better serviceability as compared to the type serviced through an opening at the bottom.

[0094] In addition, according to this embodiment, since the gap 233 between the non-contact surface of the seal forming section 234 and the end face of the lower end portion of the sleeve section 214c is sealed with the lubricating oil, it is possible to control the quantities of the lubricating oil supplied, for maintaining sound oil films in the first bearing section 241 and the second bearing section 242. As a result, the bearing sections 241 and 242 can be prevented from being broken due to seizure or the like.

[0095] Besides, according to this embodiment, the partition plate 235 is provided so as to surround the outer peripheral surface of the lower end portion of the sleeve section 214c, and the annular oil sump section 250 defined between the inner peripheral surface of the partition plate 235 and the outer peripheral surface of the lower end portion of the sleeve section 214c communicates with the gap 233. When the flow of the lubricating oil in a radially inward direction is generated in the gap 233 by the rotation of the eccentric sleeve assembly 214, therefore, the lubricating oil collected in the oil sump section 250 is sucked into the gap 233. As a result, a situation in which air in the annular space 238 is sucked into the gap 233 with the result of mixing of air bubbles into the lubricating oil can be prevented.

[0096] In addition, according to this embodiment, since the oil sump section 250 is formed at a position higher than the gap 233, the lubricating oil collected in the oil sump section 250 is collected to the gap 233 side due to gravity. When the flow of the lubricating oil in a radially inward direction is generated in the gap 233 by the rotation of the eccentric sleeve assembly 214, therefore, it is ensured that the lubricating oil collected in the oil sump section 250 is sucked into the gap 233, whereby air in the annular space 238 can be reliably prevented from being sucked into the gap 233.

[0097] Note that in the example illustrated in FIG. 4, the gyratory crusher 210 has been the so-called hydraulic cone crusher, but this is not restrictive. For example, the oil supply structure 230 according to this embodiment is also applicable to, for example, a mechanical (Symons) cone crusher.

[0098]

[Third Embodiment] FIG. 10 is a vertical sectional view of a gyratory crusher according to an embodiment of the present invention.

[0099] As shown in FIG. 10, a gyratory crusher 310 according to this embodiment includes following components: a top shell assembly 311 that holds a concave 312; a bottom shell assembly 313 that has a bottom shell bush section 313a disposed under the top shell assembly 311; an eccentric sleeve assembly 314 that is rotated inside the bottom shell bush section 313a; a main shaft assembly 315 holding a mantle 317 that is fitted to the eccentric sleeve assembly 314 and gyrated; and a rotational power transmission system 320 that transmits rotational power to the eccentric sleeve assembly 314.

[0100] Of these components, the eccentric sleeve assembly 314 has a sleeve section 314c that holds an eccentric bush section 314a fitted to the bottom shell bush section 313a of the bottom shell assembly 313 and rotated, and a flange section 314b that extends at an upper portion of the sleeve section 314c. The flange section 314b extends from the upper portion of the sleeve section 314c into a gear accommodating space 340 formed outside the bottom shell bush section 313a, and is supported from below by a thrust bearing 319 provided at an upper end portion of the bottom shell bush section 313a. In this embodiment, since the flange section 314b extends at the upper portion of the sleeve section 314c, the eccentric sleeve assembly 314 can be drawn out upward from the bottom shell assembly 313. A bevel gear 321a is fixed to a tip portion of the flange section 314b. The bevel gear 321a is disposed coaxially with a rotational axis of the bottom shell bush section 313a.

[0101] The rotational power transmission system 320 has a pinion shaft 322 connected to a driving motor (not shown), and a bevel pinion 321b fixed to one end portion of the pinion shaft 322. The pinion shaft 322 is oriented in a direction perpendicular to the rotational axis of the bottom shell bush section 313a. The bevel pinion 321b fixed to one end of the pinion shaft 322 is disposed in such a manner as to mesh, in the gear accommodating space 340, with the bevel gear 321a fixed to the flange section 314b. When the pinion shaft 322 and the bevel pinion 321b are rotated as one body by rotational power of the driving motor, the rotational power is transmitted from the bevel pinion 321b to the bevel gear 321a, whereby the eccentric sleeve assembly 314 is driven to rotate about the rotational axis of the bottom shell bush section 313a.

[0102] The sleeve section 314c is formed therein with a through-hole extending in a direction inclined relative to the rotational axis of the bottom shell bush section 313a, and the eccentric bush section 314a is fitted in the hole extending in the inclined direction. The main shaft assembly 315 is inserted in the eccentric bush section 314a. A funnel-shaped mantle 317 is fixed to an upper portion of the main shaft assembly 315.

[0103] In the illustrated example, the gyratory crusher 310 is a so-called hydraulic cone crusher, and an upper end portion of the main shaft assembly 315 is supported by a bearing 323 held by the top shell assembly 311. On the other hand, a main shaft step 315a having a convex spherical surface is fixed to a lower end portion of the main shaft assembly 315, and a step washer 313c having a concave spherical surface and a plain bearing 313b supporting a back surface of the step washer 313c are disposed in a stacked state under the main shaft step 315a. The plain bearing 313b is fixed to a bottom portion of the bottom shell assembly 313, more specifically to a ram of a hydraulic cylinder assembly disposed under the bottom shell assembly 313. The convex spherical surface of the main shaft step 315a and the concave spherical surface of the step washer 313c form a sliding section that slides.

[0104] When the eccentric sleeve assembly 314 is rotated by the rotational power transmission system 320, the main shaft assembly 315 is put into precession around the rotational axis of the eccentric bush section 314a, with the bearing 323 as a fulcrum. The mantle 317 is put into precession relative to the concave 312 according to the precession of the main shaft assembly 315, whereby a material to be crushed which is supplied into a crushing chamber 318 defined between the mantle 317 and the concave 312 is crushed.

[0105] During the operation of the gyratory crusher 310, sound oil films should be maintained by supplying appropriate quantities of the lubricating oil to a first bearing section 341 between the main shaft assembly 315 and the eccentric bush section 314a and to a second bearing section 342 between the sleeve section 314c and the bottom shell bush section 313a, for ensuring smooth precession of the main shaft assembly 315 on which a high load is exerted. For this reason, the gyratory crusher 310 is provided with an oil supply structure 330 for supplying the lubricating oil to the first bearing section 341 and to the second bearing section 342.

[0106] FIG. 11 is a schematic view showing the oil supply structure 330 in an enlarged form. In FIG. 11, arrows indicate directions in which lubricating oil flows.

[0107] As shown in FIG. 11, the oil supply structure 330 has an oil supply inlet 331 which opens in a bottom portion of a bottom shell assembly 313, more specifically in a ram central portion of a hydraulic cylinder assembly. The oil supply inlet 331 is for supplying the lubricating oil to a first bearing section 341 and supplying the lubricating oil to a second bearing section 342.

[0108] FIG. 12 is a horizontal sectional view of the bearing sections 341 and 342 of the gyratory crusher 310.

[0109] In this embodiment, as illustrated in FIGS. 11 and 12, longitudinal groove sections 351 and 352 for respectively controlling flow rate of the lubricating oil supplied from the oil supply inlet 331 to the first bearing section 341 and flow rate of the lubricating oil supplied from the oil supply inlet 331 to the second bearing section 342 are provided in an inner peripheral surface of an eccentric bush section 314a and an outer peripheral surface of a sleeve section 314c.

[0110] The longitudinal groove section 351 provided in the inner peripheral surface of the eccentric bush section 314a is exposed to the first bearing section 341, while the longitudinal groove section 352 provided in the outer peripheral surface of the sleeve section 314c is exposed to the second bearing section 342.

[0111] As the sectional area and number of the longitudinal groove section or sections 351 exposed to the first bearing section 341 are larger, the flow channel section for the first bearing section 341 is larger, in other words, the flow rate distributed to the first bearing section 341 is higher. Also, as the sectional area and number of the longitudinal groove section or sections 352 exposed to the second bearing section 342 are larger, the flow channel section for the second bearing section 342 is larger, in other words, the flow rate distributed to the second bearing section 342 is higher. Therefore, by appropriately regulating the sectional areas and numbers of the longitudinal groove sections 351 and 352 exposed respectively to the bearing sections 341 and 342, it is possible to adjust the relative proportions of the flow rates distributed to the bearing sections 341 and 342, and, as a result, it is possible to easily control the quantities of the lubricating oil supplied through the oil supply inlet 331 to the bearing sections 341 and 342.

[0112] In the illustrated example, a through-hole 336 is formed so as to penetrate a central portion of a plain bearing 313b and a central portion of a step washer 313c, and the oil supply inlet 331 opens into the inside of the through-hole 336. As shown in FIG. 11, the lubricating oil introduced into the through-hole 336 through the oil supply inlet 331 flows into an inner diameter side end portion of a sliding section between the plain bearing 313b and the step washer 313c and into an inner diameter side end portion of a sliding section between the step washer 313c and a main shaft step 315a, to lubricate the sliding sections. Then, the lubricating oil having passed each of the sliding sections flows out from an outer diameter side end portion of each sliding section into an annular space 337 outside a lower end portion of the main shaft assembly 315.

[0113] Part of the lubricating oil having flowed out into the annular space 337 flows into a lower end portion of the first bearing section 341, to lubricate the first bearing section 341. Then, the lubricating oil having passed the first bearing section 341 flows out from an upper end portion of the first bearing section 341 into a gear accommodating space 340 outside the bottom shell bush section 313a, and the lubricating oil collecting on a floor of the gear accommodating space 340 is recovered through an oil supply outlet 339 depicted in FIG. 10.

[0114] On the other hand, the remaining portion of the lubricating oil having flowed out into the annular space 337 flows under the sleeve section 314c into a lower end portion of the second bearing section 342, to lubricate the second bearing section 342. Then, the lubricating oil having passed the second bearing section 342 flows out from an upper end portion of the second bearing section 342 into the gear accommodating space 340 outside the bottom shell bush section 313a, and the lubricating oil collecting on the floor of the gear accommodating space 340 is recovered through the oil supply outlet 339 depicted in FIG. 10.

[0115] Meanwhile, FIG. 14 is a schematic view showing a comparative example of an oil supply structure in a top opening type gyratory crusher. In FIG. 14, arrows indicate directions in which lubricating oil flows. In the gyratory crusher of the type serviced through an opening at the top as shown in FIG. 14, the lubricating oil for a first bearing section 3141 is supplied through a first oil supply inlet 3131 opening in a bottom portion of a bottom shell assembly 3113, whereas the lubricating oil for a second bearing section 3142 is supplied through a second oil supply inlet 3132 opening in a circumferential surface of a bottom shell bush section 3113a.

[0116] In this oil supply structure, however, a flow channel for the lubricating oil supplied from the first oil supply inlet 3131 to the first bearing section 3141 and a flow channel for the lubricating oil supplied from the second oil supply inlet 3132 to the second bearing section 3142 are structurally not separated from each other; particularly, an oil supply outlet side 3152 of the second bearing section 3142 and an oil supply inlet side 3151 of the first bearing section 3141 communicate with each other. Therefore, the lubricating oil supplied from the first oil supply inlet 3131 would flow not only into the first bearing section 3141 but also into the second bearing section 3142. For this reason, in that region of the second bearing section 3142 which is on the lower side of the second oil supply inlet 3132, a downward flow and an upward flow are mixedly present, so that failure in lubrication may occur. As a result, the quantities of the lubricating oil distributed to the bearing sections 3141 and 3142 become instable, and, particularly under bad conditions, it may be difficult to maintain sound oil films.

[0117] In addition, in the example shown in FIG. 14, since the lubricating oil is supplied from two parts, namely, the first oil supply inlet 3131 and the second oil supply inlet 3132, it is necessary that a piping material (not shown) for supplying the lubricating oil should be connected to the two parts, namely, the first oil supply inlet 3131 and the second oil supply inlet 3132, which leads to complicated piping.

[0118] On the other hand, in this embodiment, as illustrated in FIG. 11, the oil supply inlet 331 opening in the bottom portion of the bottom shell assembly 313 supplies the lubricating oil to be supplied to the first bearing section 341 and the lubricating oil to be supplied to the second bearing section 342. Therefore, only an upward flow is formed in each of the bearing sections 341 and 342, so that there is no possibility of failure in lubrication. As a result, the quantities of the lubricating oil distributed to the bearing sections 341 and 342 become stable, and the quantities of the lubricating oil supplied can be controlled in such a manner that sound oil films are maintained in the first bearing section 341 and the second bearing section 342.

[0119] Besides, in this embodiment, since the lubricating oil is supplied from one part, namely, the oil supply inlet 331, it is sufficient that a piping material (not shown) for supplying the lubricating oil is connected to one part, namely, the oil supply inlet 331, which leads to simple piping.

[0120] An operation of the gyratory crusher 310 according to this embodiment will now be described below.

[0121] First, the lubricating oil is supplied through the oil supply inlet 331 to both the first bearing section 341 and the second bearing section 342. In this embodiment, since the lubricating oil for the first bearing section 341 and the lubricating oil for the second bearing section 342 are both supplied from the oil supply inlet 331 opening in the bottom portion of the bottom shell assembly 313, the quantities of the lubricating oil distributed to the bearing sections 341 and 342 are stable, and the quantities of the lubricating oil supplied can be controlled in such a manner that sound oil films are maintained in the first bearing section 341 and the second bearing section 342.

[0122] In addition, in this embodiment, the longitudinal groove sections 351 and 352 for controlling the flow rate of the lubricating oil supplied from the oil supply inlet 331 to the first bearing section 341 and the flow rate of the lubricating oil supplied from the oil supply inlet 331 to the second bearing section 342 are provided in the inner peripheral surface of the eccentric bush section 314a and the outer peripheral surface of the sleeve section 314c. Therefore, the quantities of the lubricating oil supplied can be easily controlled in such a manner that sound oil films are maintained in the first bearing section 341 and the second bearing section 342.

[0123] Next, rotational power is transmitted from the rotational power transmission system 320 to the flange section 314b of the eccentric sleeve assembly 314, whereby the eccentric sleeve assembly 314 is rotated about the rotational axis of the bottom shell bush section 313a. Attendant on the rotation of the eccentric sleeve assembly 314, the main shaft assembly 315 fitted to the eccentric bush section 314a is put into precession, with the bearing 323 as a fulcrum. The mantle 317 fixed to the main shaft assembly 315 is put into precession relative to the concave 312 according to the precession of the main shaft assembly 315, whereby the gap between the mantle 317 and the concave 312 is changed to be wider and narrower in accordance with each revolution.

[0124] Subsequently, a material to be crushed, such as raw ore or rough stones, is charged through the hopper 325 at an upper portion of the top shell assembly 311. The material to be crushed which has thus been charged drops into the crushing chamber 318 defined between the mantle 317 and the concave 312, and is trapped between the mantle 317 and the concave 312. When the mantle 317 is gyrated and the gap between the mantle 317 and the concave 312 is narrowed, the material to be crushed is crushed under pressure.

[0125] Thereafter, when the gap between the mantle 317 and the concave 312 is widened, the material to be crushed drops into that part of the inside of the crushing chamber 318 at which the gap between the mantle 317 and the concave 312 is wider, and, when the gap between the mantle 317 and the concave 312 is again narrowed, the material to be crushed is further finely crushed under pressure. The material to be crushed becomes gradually finer through repetition of the crushing under pressure and dropping, to be a product having a predetermined grain size, which drops through the gap between the mantle 317 and the concave 312 onto a floor, and is discharged to the exterior of the machine through an opening in the floor.

[0126]

During the operation of the gyratory crusher 310, the quantities of the lubricating oil which are sufficient for maintaining sound oil films in the first bearing section 341 and the second bearing section 342 can be controlled, whereby the bearing sections 341 and 342 can be prevented from being broken due to seizure or the like.

[0127] According to this embodiment as above, since the flange section 314b of the eccentric sleeve assembly 314 extends at the upper portion of the sleeve section 314c, the eccentric sleeve assembly 314 can be drawn out upward from the bottom shell assembly 313, and, in the case where the bearing sections 341 and 342 or the gears 321a and 321b are broken, a servicing work for the bearing sections 341 and 342 or the gears 321a and 321b can be performed by drawing out the eccentric sleeve assembly 314 upward. Therefore, it is unnecessary to disassemble the hydraulic cylinder assembly disposed under the bottom shell assembly 313, and a dangerous work to be performed by a worker situated under a suspended load is not needed. Consequently, better serviceability as compared to the type serviced through an opening at the bottom can be obtained.

[0128] In addition, according to this embodiment, since both the lubricating oil for the first bearing section 341 and the lubricating oil for the second bearing section 342 are supplied through the oil supply inlet 331 opening in the bottom portion of the bottom shell assembly 313, the quantities of the lubricating oil distributed to the bearing sections 341 and 342 are stable, and the quantities of the lubricating oil supplied can be controlled in such a manner that sound oil films are maintained in the first bearing section 341 and the second bearing section 342. Consequently, the bearing sections 341 and 342 can be prevented from being broken due to seizure or the like.

[0129] Besides, according to this embodiment, both the supply of the lubricating oil to the first bearing section 341 and the supply of the lubricating to the second bearing section 342 are conducted through one part, namely, the oil supply inlet 331, it is sufficient that a piping material (not shown) for supplying the lubricating oil is connected to one part, namely, the oil supply inlet 331, which leads to simple piping.

[0130] In addition, according to this embodiment, the longitudinal groove sections 351 and 352 for controlling the flow rate of the lubricating oil supplied from the oil supply inlet 331 to the first bearing section 341 and the flow rate of the lubricating oil supplied from the oil supply inlet 331 to the second bearing section 342 are provided in the inner peripheral surface of the eccentric bush section 314a and the outer peripheral surface of the sleeve section 314c. For this reason, by appropriately regulating the sectional areas or numbers of the longitudinal groove sections 351 and 352 exposed to the bearing sections 341 and 342, the quantities of the lubricating oil supplied can be easily controlled in such a manner that sound oil films are maintained in the bearing sections 341 and 342.

[0131] Note that while the longitudinal groove sections 351 and 352 have been provided in both the inner peripheral surface of the eccentric bush section 314a and the outer peripheral surface of the sleeve section 314c in this embodiment, this is not restrictive. The longitudinal groove section or sections may be provided in only one of the inner peripheral surface of the eccentric bush section 314a and the outer peripheral surface of the sleeve section 314c. Besides, the longitudinal groove section or sections 352 may be provided in an inner peripheral surface of the bottom shell bush section 315a.

[0132] Note that while the gyratory crusher 310 has been the so-called hydraulic cone crusher in the example shown in FIG. 10, this is not restrictive. For example, the oil supply structure 330 according to this embodiment is also applicable to, for example, a mechanical (Symons) cone crusher.

[0133] Various modifications may be applied to this embodiment as above. Exemplary modifications will now be described below, referring to the drawings. In the following description and in the drawings used in the following description, the parts configured in the same manner as in this embodiment described above are denoted by the same reference symbols as used above, and overlapping descriptions thereof are omitted. In addition, where it is clear that the advantageous effects obtained in the embodiment above can be obtained also in the modifications, the descriptions thereof may be omitted.

[0134] FIG. 13 is a schematic view showing a modification of an oil supply structure 330.

[0135] In the oil supply structure 330 shown in FIG. 13, a partition plate 353 for controlling the flow rate of the lubricating oil supplied from an oil supply inlet 331 to a first bearing section 341 and the flow rate of the lubricating oil supplied from the oil supply inlet 331 to a second bearing section 342 is disposed between a lower end portion of a sleeve section 314c and a bottom portion of a bottom shell assembly 313.

[0136] In the illustrated example, the partition plate 353 has a hollow cylindrical shape, and is fixed to a bottom portion of the bottom shell assembly 313 in such a manner as to surround an annular space 337. A gap having a predetermined size is formed between an upper end portion of the partition plate 353 and a lower end portion of the sleeve section 314c. Since a flange section 314b of an eccentric sleeve assembly 314 is supported from below by a thrust bearing 319, the sleeve section 314c of the eccentric sleeve assembly 314 is positioned at a predetermined height position, whereby the gap between the upper end portion of the partition plate 350 and the lower end portion of the sleeve section 314c is maintained at a predetermined spacing. The lubricating oil supplied to the second bearing section 342 through the oil supply inlet 331 flows into the second bearing section 342 after passing the gap between the upper end portion of the partition plate 353 and the lower end portion of the sleeve section 314c.

[0137] According to the mode illustrated in FIG. 13, by regulating the size of the gap between the upper end portion of the partition plate 353 and the lower end portion of the sleeve section 314c, it is possible to easily control the flow rate of the lubricating oil supplied from the oil supply inlet 331 to the first bearing section 341 and the flow rate of the lubricating oil supplied from the oil supply inlet 331 to the second bearing section 342.

[0138] Note that the invention disclosed is not to be limited by the individual embodiments described above. The embodiments can be appropriately combined with one another within such a range as not to cause contradiction between the contents of treatment.

Reference Signs List

[0139] 10 Gyratory crusher 11 Top shell assembly 12 Concave 13 Bottom shell assembly 13a Bottom shell bush section 13b Plain bearing 13c Step washer 14 Eccentric sleeve assembly 14a Eccentric bush section 14b Flange section 15 Main shaft assembly 15a Main shaft step 17 Mantle 18 Crushing chamber 19 Thrust bearing 20 Rotational power transmission system

21a Bevelgear 21b Bevel pinion 22 Pinion shaft 23 Bearing 25 Hopper 30 Oil supply structure 31 First oil supply inlet 32 Second oil supply inlet 33 Thrust seal 34 Thrust seal fitting frame 35 Stepped portion 36 Through-hole 37 Annular space 38 Annular space 39 Oil supply outlet 40 Gear space 41 First bearing section 42 Second bearing section 210 Gyratory crusher 211 Top shell assembly 212 Concave 213 Bottom shell assembly 213a Bottom shell bush section 213b Plain bearing 213c Step washer 214 Eccentric sleeve assembly 214a Eccentric bush section 214b Flange section 214c Sleeve section 215 Main shaft assembly 215a Main shaft step 217 Mantle 218 Crushing chamber 219 Thrust bearing 220 Rotational power transmission system 221a Bevelgear

221b Bevel pinion 222 Pinion shaft 223 Bearing 225 Hopper 230 Oil supply structure 231 First oil supply inlet 232 Second oil supply inlet 233 Gap 234 Seal forming section 235 Partition plate 236 Through-hole 237 Annular space 238 Annular space 239 Oil supply outlet 240 Gear accommodating space 241 First bearing section 242 Second bearing section 250 Oil sump section 310 Gyratory crusher 311 Top shell assembly 312 Concave 313 Bottom shell assembly 313a Bottom shell bush section 313b Plain bearing 313c Step washer 314 Eccentric sleeve assembly 314a Eccentric bush section 314b Flange section 314c Sleeve section 315 Main shaft assembly 315a Main shaft step 317 Mantle 318 Crushing chamber 319 Thrust bearing 320 Rotational power transmission system 321a Bevelgear

321b Bevel pinion 322 Pinion shaft 323 Bearing 325 Hopper 330 Oil supply structure 331 Oil supply inlet 336 Through-hole 337 Annular space 339 Oil supply outlet 340 Gear accommodating space 341 First bearing section 342 Second bearing section 351 Longitudinal groove section 352 Longitudinal groove section 353 Partition plate

Claims

CLAIMS:

1. An oil supply structure for a gyratory crusher, the gyratory crusher comprising: a bottom shell assembly having a bottom shell bush section; an eccentric sleeve assembly that has an eccentric bush section fitted to the bottom shell bush section and rotated and a flange section fixed to an upper portion of the eccentric bush section; a main shaft assembly holding a mantle that is fitted to the eccentric bush section and gyrated; and a rotational power transmission system that transmits rotational power to the flange section, wherein a material to be crushed is crushed between the gyrated mantle and a concave, the oil supply structure being for supplying lubricating oil to afirst bearing section between the main shaft assembly and the eccentric bush section and to a second bearing section between the eccentric bush section and the bottom shell bush section, the oil supply structure comprising: an annular thrust seal that is disposed inside the bottom shell assembly and supports a lower end portion of the eccentric bush section from below; a first oil supply inlet that opens in a bottom portion of the bottom shell assembly so as to enable oil supply to the first bearing section; and a second oil supply inlet that opens in an inner peripheral surface of the bottom shell bush section so as to enable oil supply to the second bearing section, wherein the thrust seal separates a flow channel for the lubricating oil supplied from the first oil supply inlet to the first bearing section from a flow channel for the lubricating oil supplied from the second oil supply inlet to the second bearing section.

2. The oil supply structure according to claim 1, wherein a thrust bearing that supports the flange section from below is provided with an upper end portion of the bottom shell bush section.

3. The oil supply structure according to claim 1, wherein a thrust bearing that supports the flange section from below is not provided with an upper end portion of the bottom shell bush section.

4. The oil supply structure according to any one of claims I to 3, wherein a stepped portion is projectingly provided on an outer diameter side of the thrust seal, and an inner peripheral surface of the stepped portion surrounds an outer peripheral surface of a lower end portion of the eccentric bush section.

5. A gyratory crusher crushing comprising: a bottom shell assembly having a bottom shell bush section; an eccentric sleeve assembly that has an eccentric bush section fitted to the bottom shell bush section and rotated and a flange section fixed to an upper portion of the eccentric bush section; a main shaft assembly holding a mantle that is fitted to the eccentric bush section and gyrated; and a rotational power transmission system that transmits rotational power to the flange section, wherein a material to be crushed is crushed between the gyrated mantle and a concave, the gyratory crusher further comprises an oil supply structure for supplying lubricating oil to a first bearing section between the main shaft assembly and the eccentric bush section and to a second bearing section between the eccentric bush section and the bottom shell bush section, the oil supply structure comprises: an annular thrust seal that is disposed inside the bottom shell assembly and supports a lower end portion of the eccentric bush section from below; a first oil supply inlet that opens in a bottom portion of the bottom shell assembly so as to enable oil supply to thefirst bearing section; and a second oil supply inlet that opens in an inner peripheral surface of the bottom shell bush section so as to enable oil supply to the second bearing section, and the thrust seal separates a flow channel for the lubricating oil supplied from the first oil supply inlet to the first bearing section from a flow channel for the lubricating oil supplied from the second oil supply inlet to the second bearing section.

6. An oil supply structure for a gyratory crusher, the gyratory crusher comprising: a bottom shell assembly having a bottom shell bush section; an eccentric sleeve assembly that has a sleeve section holding an eccentric bush section fitted to the bottom shell bush section and rotated and a flange section extending at an upper portion of the sleeve section; a main shaft assembly holding a mantle that is fitted to the eccentric bush section and gyrated; and a rotational power transmission system that transmits rotational power to the flange section, a material to be crushed being crushed between the gyrated mantle and a concave, the oil supply structure being for supplying lubricating oil to a first bearing section between the main shaft assembly and the eccentric bush section and to a second bearing section between the sleeve section and the bottom shell bush section, the oil supply structure comprising: a first oil supply inlet that opens in a bottom portion of the bottom shell assembly so as to enable oil supply to thefirst bearing section; a second oil supply inlet that opens in a circumferential surface of the bottom shell bush section so as to enable oil supply to the second bearing section; and an annular seal forming section that is provided inside the bottom shell assembly and has a non-contact surface facing an end face of a lower end portion of the sleeve section, wherein a gap between the non-contact surface of the seal forming section and the end face of the lower end portion of the sleeve section is sealed with the lubricating oil, a partition plate is disposed at an outer periphery of the annular seal forming section, and an annular oil sump section is formed between the partition plate and an outer peripheral surface of the lower end portion of the sleeve section.

7. The oil supply structure according to claim 6, wherein the oil sump section is formed at a position higher than the gap.

8. A gyratory crusher comprising: a bottom shell assembly having a bottom shell bush section; an eccentric sleeve assembly that has a sleeve section holding an eccentric bush section fitted to the bottom shell bush section and rotated and a flange section fixed to an upper portion of the eccentric bush section; a main shaft assembly holding a mantle that is fitted to the eccentric bush section and gyrated; and a rotational power transmission system that transmits rotational power to the flange section, wherein a material to be crushed is crushed between the gyrated mantle and a concave, the gyratory crusher further comprises an oil supply structure for supplying lubricating oil to a first bearing section between the main shaft assembly and the eccentric bush section and to a second bearing section between the sleeve section and the bottom shell bush section, the oil supply structure comprises: a first oil supply inlet that opens in a bottom portion of the bottom shell assembly so as to enable oil supply to thefirst bearing section; a second oil supply inlet that opens in a circumferential surface of the bottom shell bush section so as to enable oil supply to the second bearing section; and an annular seal forming section that is provided inside the bottom shell assembly and has a non-contact surface facing an end face of a lower end portion of the sleeve section, a gap between the non-contact surface of the seal forming section and the end face of the lower end portion of the sleeve section is sealed with the lubricating oil, a partition plate is disposed at an outer periphery of the annular seal forming section, and an annular oil sump section is formed between the partition plate and an outer peripheral surface of the lower end portion of the sleeve section.

9. An oil supply method for a gyratory crusher, the gyratory crusher comprising: a bottom shell assembly having a bottom shell bush section; an eccentric sleeve assembly that has a sleeve section holding an eccentric bush section fitted to the bottom shell bush section and rotated and a flange section extending at an upper portion of the sleeve section; a main shaft assembly holding a mantle that is fitted to the eccentric bush section and gyrated; and a rotational power transmission system that transmits rotational power to the flange section, wherein a material to be crushed is crushed between the gyrated mantle and a concave, the oil supply method being for supplying lubricating oil to a first bearing section between the main shaft assembly and the eccentric bush section and to a second bearing section between the sleeve section and the bottom shell bush section, wherein both the lubricating oil for the first bearing section and the lubricating oil for the second bearing section are supplied from an oil supply inlet that opens in a bottom portion of the bottom shell assembly, wherein a partition plate is provided between a lower end portion of the sleeve section and a bottom portion of the bottom shell assembly, and flow rate of the lubricating oil supplied from the oil supply inlet to the first bearing section and flow rate of the lubricating oil supplied from the oil supply inlet to the second bearing section are controlled.

10. The oil supply method according to claim 9, wherein a longitudinal groove section is provided with the eccentric bush section, the sleeve section or the bottom shell bush section, and flow rate of the lubricating oil supplied from the oil supply inlet to the first bearing section and flow rate of the lubricating oil supplied from the oil supply inlet to the second bearing section are controlled.

11. An oil supply structure for a gyratory crusher, the gyratory crusher comprising: a bottom shell assembly having a bottom shell bush section; an eccentric sleeve assembly that has a sleeve section holding an eccentric bush section fitted to the bottom shell bush section and rotated and a flange section extending at an upper portion of the sleeve section; a main shaft assembly holding a mantle that is fitted to the eccentric bush section and gyrated; and a rotational power transmission system that transmits rotational power to the flange section, wherein a material to be crushed is crushed between the gyrated mantle and a concave, the oil supply structure being for supplying lubricating oil to a first bearing section between the main shaft assembly and the eccentric bush section and to a second bearing section between the sleeve section and the bottom shell bush section, the oil supply structure comprising an oil supply inlet that opens in a bottom portion of the bottom shell assembly, wherein the oil supply inlet is configured so as to supply both the lubricating oil for the first bearing section and the lubricating oil for the second bearing section; and a partition plate for controlling flow rate of the lubricating oil supplied from the oil supply inlet to the first bearing section and flow rate of the lubricating oil supplied from the oil supply inlet to the second bearing section is provided between a lower end portion of the sleeve section and a bottom portion of the bottom shell assembly.

12. The oil supply structure according to claim 11, wherein a longitudinal groove section for controlling flow rate of the lubricating oil supplied from the oil supply inlet to the first bearing section and flow rate of the lubricating oil supplied from the oil supply inlet to the second bearing section is provided with the eccentric bush section, the sleeve section or the bottom shell bush section.

13. A gyratory crusher comprising: a bottom shell assembly having a bottom shell bush section; an eccentric sleeve assembly that has a sleeve section holding an eccentric bush section fitted to the bottom shell bush section and rotated and a flange section extending at an upper portion of the sleeve section; a main shaft assembly holding a mantle that is fitted to the eccentric bush section and gyrated; and a rotational power transmission system that transmits rotational power to the flange section, wherein a material to be crushed is crushed between the gyrated mantle and a concave, the gyratory crusher further comprises an oil supply structure for supplying lubricating oil to a first bearing section between the main shaft assembly and the eccentric bush section and to a second bearing section between the sleeve section and the bottom shell bush section, the oil supply structure has an oil supply inlet that opens in a bottom portion of the bottom shell assembly, the oil supply inlet is configured so as to supply both the lubricating oil for the first bearing section and the lubricating oil for the second bearing section; and a partition plate for controlling flow rate of the lubricating oil supplied from the oil supply inlet to the first bearing section and flow rate of the lubricating oil supplied from the oil supply inlet to the second bearing section is provided between a lower end portion of the sleeve section and a bottom portion of the bottom shell assembly.

Kabushiki Kaisha Earthtechnica

Patent Attorneys for the Applicant/Nominated Person

SPRUSON&FERGUSON