WO2016104503A1 - Oil supply structure, oil supply method, and gyratory crusher - Google Patents

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

Lubrication structure, lubrication method and rotary crusher

[Technical Field] The present invention relates to a rotary crusher for supplying a material to be crushed such as a rough stone between a rotating mantle and a corn cave and crushing, and an oil supply structure and an oil supply method of such a rotary crusher.

A rotary crusher such as a cone crusher or a gyratory crusher is formed between a funnel-shaped mantle fixed to the upper part of the main spindle assembly to be rotated and a cone cave provided to cover the mantle. A machine equipped with a crushing chamber.

A lower frame assembly having an outer cylinder bush portion is disposed below the cone cave, and an inner cylinder bush portion of an eccentric sleeve assembly is fitted to the outer cylinder bush portion of the lower frame assembly. At the eccentric position of the inner cylinder bush part, a hole extending in a direction inclined with respect to the rotation axis of the inner cylinder bush part is formed, and the spindle assembly with the mantle fixed is fitted into the hole of the inner cylinder bush part Has been. Further, a flange portion extending outward from the outer cylinder bush portion is fixed to the end portion of the inner cylinder bush portion, and a rotational power transmission system is connected to the tip of the flange portion. The main shaft assembly and the mantle are integrally rotated around the rotation axis of the inner cylinder bush portion by rotating the flange portion and the inner cylinder bush portion integrally around the rotation axis of the inner cylinder bush portion by the rotational power from the rotational power transmission system. It is turned around.

Also, a lower frame assembly having an outer cylinder bush portion is disposed below the cone cave, and an eccentric sleeve assembly sleeve portion is fitted to the outer cylinder bush portion of the lower frame assembly. The sleeve portion is formed with a hole extending in a direction inclined with respect to the rotational axis of the eccentric sleeve assembly, and the inner cylinder bush portion is fitted in the hole extending in the inclined direction. Further, the main shaft assembly to which the mantle is fixed is fitted into the eccentric hole of the inner cylinder bush portion. Further, a flange portion extending outward of the outer cylinder bush portion extends at the upper portion or the lower portion of the sleeve portion, and a rotational power transmission system is connected to the tip of the flange portion. When the eccentric sleeve assembly is rotated by the rotational power from the rotational power transmission system, the main shaft assembly and the mantle are integrally rotated around the rotational axis of the eccentric hole of the inner cylinder bush portion.

When the rough is supplied to the crushing chamber from the hopper provided at the top of the rotary crusher, the rough captured between the rotating mantle and the corn cave is crushed to a predetermined particle size and discharged.

By the way, regarding the positional relationship between the inner cylinder bush part and the flange part of the eccentric sleeve assembly, the type in which the flange part is fixed to the upper part of the inner cylinder bush part (hereinafter referred to as the upper open maintenance type), the flange part is the inner cylinder. A type fixed to the lower portion of the bush portion (hereinafter referred to as a lower open maintenance type) is known. For example, Patent Literature 1 discloses an upper open maintenance type rotary crusher, and Patent Literature 2 discloses a lower open maintenance type rotational crusher.

In addition, regarding the positional relationship between the sleeve portion and the flange portion of the eccentric sleeve assembly, the flange portion extends to the upper portion of the sleeve portion (hereinafter referred to as the upper open maintenance type), and the flange portion extends to the lower portion of the sleeve portion. The existing type (hereinafter referred to as the lower open maintenance type) is known. For example, Patent Literature 1 discloses an upper open maintenance type rotary crusher, and Patent Literature 2 discloses a lower open maintenance type rotational crusher.

The upper open maintenance type rotary crusher is excellent in maintainability, but it is difficult to control the amount of oil supplied to maintain a healthy oil film in each bearing part. On the other hand, the lower open maintenance type rotary crusher is easy to control the amount of oil supplied to maintain a healthy oil film in each bearing portion, but has low maintainability.

JP-A-5-345136 JP 2014-108390 A

The present invention has been made in consideration of such points. An object of the present invention is to provide a lubrication structure, a lubrication method, and a rotation type of a crushing crusher capable of controlling a lubrication amount for maintaining a healthy oil film in a bearing portion while being an open top maintenance type having excellent maintainability. To provide a crusher.

An oil supply structure according to an aspect of the present invention includes:
A lower frame assembly having an outer cylinder bush portion, an eccentric sleeve assembly having an inner cylinder bush portion fitted into the outer cylinder bush portion and rotated, and a flange portion fixed to the upper portion of the inner cylinder bush portion; A spindle assembly that holds a mantle that is rotated by being fitted to the inner cylinder bush portion, and a rotational power transmission system that transmits rotational power to the flange portion, and between the rotating mantle and the cone cable In a rotary crusher for crushing an object to be crushed, a first bearing part between the main shaft assembly and the inner cylinder bush part and a second bearing part between the inner cylinder bush part and the outer cylinder bush part Each of which has a lubricating structure for supplying lubricating oil,
An annular thrust seal that is installed inside the lower frame assembly and supports the lower end of the inner cylinder bushing from below;
A first refueling inlet that opens at a bottom of the lower frame assembly to refuel the first bearing portion;
A second oil supply inlet that opens on an inner peripheral surface of the outer cylinder bush portion so as to supply oil to the second bearing portion;
Have
The thrust seal includes a flow path of lubricating oil supplied from the first oil supply inlet to the first bearing portion, and a flow path of lubricating oil supplied from the second oil supply inlet to the second bearing portion. It is separated.

In the fuel supply structure of the above-described aspect, a thrust bearing that supports the flange portion from below may be provided at an upper end portion of the outer cylinder bush portion.

In the fuel supply structure according to the above aspect, the upper end portion of the outer cylinder bush portion may not be provided with a thrust bearing that supports the flange portion from below.

In the fuel supply structure of the above aspect, a stepped portion is provided on the outer diameter side of the thrust seal, and the inner peripheral surface of the stepped portion surrounds the outer peripheral surface of the lower end portion of the inner cylinder bushing portion. May be.

A rotary crusher according to another aspect of the present invention includes:
A lower frame assembly having an outer cylinder bush part;
An eccentric sleeve assembly having an inner cylinder bush part that is fitted and rotated in the outer cylinder bush part and a flange part fixed to the upper part of the inner cylinder bush part;
A spindle assembly that holds a mantle that is fitted to the inner cylinder bushing and rotated,
A rotational power transmission system for transmitting rotational power to the flange portion;
With
A rotary crusher that crushes objects to be crushed between a rotating mantle and a corn cave,
And an oil supply structure for supplying lubricating oil to the first bearing portion between the main shaft assembly and the inner cylinder bush portion and the second bearing portion between the inner cylinder bush portion and the outer cylinder bush portion, respectively. Prepared,
The oil supply structure is
An annular thrust seal that is installed inside the lower frame assembly and supports the lower end of the inner cylinder bushing from below;
A first refueling inlet that opens at a bottom of the lower frame assembly to refuel the first bearing portion;
A second oil supply inlet that opens on an inner peripheral surface of the outer cylinder bush portion so as to supply oil to the second bearing portion;
Have
The thrust seal includes a flow path of lubricating oil supplied from the first oil supply inlet to the first bearing portion, and a flow path of lubricating oil supplied from the second oil supply inlet to the second bearing portion. It is separated.

An oil supply structure according to another aspect of the present invention includes: a lower frame assembly having an outer cylinder bush part; a sleeve part that holds the inner cylinder bush part that is rotated by being fitted to the outer cylinder bush part; and an upper part of the sleeve part An eccentric sleeve assembly having a flange portion extending to the main shaft assembly, a main shaft assembly that holds a mantle that is rotated by being fitted to the inner cylinder bush portion, and a rotational power transmission system that transmits rotational power to the flange portion. A rotary crushing machine for crushing an object to be crushed between a rotating mantle and a cone cave, a first bearing part between the main shaft assembly and the inner cylinder bush part, the sleeve part, and the An oil supply structure for supplying lubricating oil to each of the second bearing portions between the outer cylinder bush portion and a first oil supply inlet that opens at the bottom of the lower frame assembly so as to supply oil to the first bearing portion When A second oil supply inlet that opens on a circumferential surface of the outer cylinder bushing so as to supply oil to the second bearing portion; and a non-facing portion that is provided inside the lower frame assembly and that faces the end surface of the lower end portion of the sleeve portion. An annular seal forming portion having a contact surface, and a gap between the non-contact surface of the seal forming portion and an end surface of the lower end portion of the sleeve portion is sealed with the lubricant, and the annular seal A partition plate is disposed on the outer periphery of the forming portion, and an annular oil reservoir is formed between the partition plate and the outer peripheral surface of the lower end portion of the sleeve portion.

In the oil supply structure according to the above-described aspect, the oil reservoir portion may be formed at a position higher than the gap.

A rotary crusher according to another aspect of the present invention includes a lower frame assembly having an outer cylinder bush portion, a sleeve portion that holds the inner cylinder bush portion that is rotated by being fitted to the outer cylinder bush portion, and the sleeve. An eccentric sleeve assembly having a flange portion extending at the top of the portion, a main shaft assembly that holds a mantle that is rotated by being fitted to the inner cylinder bush portion, and a rotational power that transmits rotational power to the flange portion A rotary crushing machine for crushing an object to be crushed between a rotating mantle and a cone cave, the first bearing part between the main shaft assembly and the inner cylinder bush part, The lower frame is further provided with an oil supply structure for supplying lubricating oil to each of the second bearing portions between the sleeve portion and the outer cylinder bush portion, and the oil supply structure supplies oil to the first bearing portion. Bottom of assembly A first oil supply inlet that opens, a second oil supply inlet that opens on a circumferential surface of the outer cylinder bush portion so as to supply oil to the second bearing portion, and an inner side of the lower frame assembly, An annular seal forming portion having a non-contact surface facing the end surface of the lower end portion, and the gap between the non-contact surface of the seal forming portion and the end surface of the lower end portion of the sleeve portion is the lubricating oil A partition plate is disposed on the outer periphery of the annular seal forming portion, and an annular oil reservoir portion is formed between the partition plate and the outer peripheral surface of the lower end portion of the sleeve portion.

An oil supply method according to another aspect of the present invention includes: a lower frame assembly having an outer cylinder bush part; a sleeve part holding the inner cylinder bush part rotated by being fitted to the outer cylinder bush part; and an upper part of the sleeve part An eccentric sleeve assembly having a flange portion extending to the main shaft assembly, a main shaft assembly that holds a mantle that is rotated by being fitted to the inner cylinder bush portion, and a rotational power transmission system that transmits rotational power to the flange portion. A rotary crushing machine for crushing an object to be crushed between a rotating mantle and a cone cave, a first bearing part between the main shaft assembly and the inner cylinder bush part, the sleeve part, and the An oil supply method for supplying lubricating oil to each of the second bearing portions between the outer cylinder bush portions, wherein both the lubricating oil of the first bearing portion and the lubricating oil of the second bearing portion are supplied to the lower portion. Frame assembly Supplied from the fuel supply inlet opening in the bottom.

In the oil supply method according to the above aspect, a longitudinal groove is provided in the inner cylinder bush part, the sleeve part or the outer cylinder bush part, and the flow rate of the lubricating oil supplied from the oil supply inlet to the first bearing part, The flow rate of the lubricating oil supplied from the oil supply inlet to the second bearing portion may be controlled.

In the oil supply method according to the above aspect, a partition plate is provided between the lower end portion of the sleeve portion and the bottom portion of the lower frame assembly, and the flow rate of the lubricating oil supplied from the oil supply inlet to the first bearing portion; You may control the flow volume of the lubricating oil supplied to the said 2nd bearing part from the said oil supply inlet.

An oil supply structure according to another aspect of the present invention includes: a lower frame assembly having an outer cylinder bush part; a sleeve part that holds the inner cylinder bush part that is rotated by being fitted to the outer cylinder bush part; and an upper part of the sleeve part An eccentric sleeve assembly having a flange portion extending to the main shaft assembly, a main shaft assembly that holds a mantle that is rotated by being fitted to the inner cylinder bush portion, and a rotational power transmission system that transmits rotational power to the flange portion. A rotary crushing machine for crushing an object to be crushed between a rotating mantle and a cone cave, a first bearing part between the main shaft assembly and the inner cylinder bush part, the sleeve part, and the An oil supply structure for supplying lubricating oil to each of the second bearing portions between the outer cylinder bush portion and an oil supply inlet that opens at a bottom of the lower frame assembly. bearing Has both lubricating oils and lubricating oil of the second bearing portion adapted to supply.

In the oil supply structure according to the above-described aspect, the inner cylinder bush portion, the sleeve portion, or the outer cylinder bush portion includes a flow rate of lubricating oil supplied from the oil supply inlet to the first bearing portion, and the oil supply inlet from the oil supply inlet. A longitudinal groove for controlling the flow rate of the lubricating oil supplied to the second bearing portion may be provided.

In the oil supply structure according to the above aspect, between the lower end portion of the sleeve portion and the bottom portion of the lower frame assembly, the flow rate of the lubricating oil supplied from the oil supply inlet to the first bearing portion, and the oil supply inlet A partition plate for controlling the flow rate of the lubricating oil supplied to the second bearing portion may be provided.

A rotary crusher according to another aspect of the present invention includes a lower frame assembly having an outer cylinder bush portion, a sleeve portion that holds the inner cylinder bush portion that is rotated by being fitted to the outer cylinder bush portion, and the sleeve. An eccentric sleeve assembly having a flange portion extending at the top of the portion, a main shaft assembly that holds a mantle that is rotated by being fitted to the inner cylinder bush portion, and a rotational power that transmits rotational power to the flange portion A rotary crushing machine for crushing an object to be crushed between a rotating mantle and a cone cave, the first bearing part between the main shaft assembly and the inner cylinder bush part, An oil supply structure for supplying lubricating oil to each of the second bearing parts between the sleeve part and the outer cylinder bush part is further provided, and the oil supply structure has an oil supply inlet opening at the bottom of the lower frame assembly. And said Oil inlet is adapted to supply both the lubricating oil in the lubricating oil and the second bearing portion of the first bearing portion.

According to the present invention, it is possible to control the amount of oil supplied for maintaining a healthy oil film in the bearing portion, while being an upper open maintenance type excellent in maintainability.

FIG. 1 is a longitudinal sectional view showing a rotary crusher according to an embodiment of the present invention. FIG. 2 is an enlarged schematic view showing an oil supply structure in the rotary crusher of FIG. FIG. 3 is a schematic view showing a comparative example of an oil supply structure in an upper open type rotary crusher. FIG. 4 is a longitudinal sectional view showing a rotary crusher according to an embodiment of the present invention. FIG. 5 is an enlarged schematic view showing an oil supply structure in the rotary crusher of FIG. 6 is a cross-sectional view showing an oil film formed on the first bearing portion of the rotary crusher of FIG. FIG. 7 is a graph showing the pressure of the oil film of FIG. FIG. 8 is a graph showing the distribution (inflow) amount of lubricating oil in the gap between the seal forming portion and the sleeve portion. FIG. 9 is a schematic diagram showing a comparative example of an oil supply structure in an upper open type rotary crusher. FIG. 10 is a longitudinal sectional view showing a rotary crusher according to an embodiment of the present invention. FIG. 11 is an enlarged schematic view showing an oil supply structure in the rotary crusher of FIG. 12 is a view for explaining the longitudinal groove portion, and is a cross-sectional view of a bearing portion of the rotary crusher of FIG. FIG. 13 is a diagram corresponding to FIG. 11, and is a schematic diagram illustrating a modified example of the oil supply structure. FIG. 14 is a schematic diagram showing a comparative example of an oil supply structure in an upper open type rotary crusher.

Hereinafter, specific examples of embodiments of the present invention will be described with reference to the drawings. In the drawings attached to the present specification, for the sake of illustration and ease of understanding, the scale, the vertical / horizontal dimension ratio, and the like are appropriately changed and exaggerated from those of the actual ones.

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

As shown in FIG. 1, the rotary crusher 10 according to the present embodiment includes an upper frame assembly 11 that holds a cone cable 12 and a lower frame that includes an outer cylinder bush portion 13 a that is disposed below the upper frame assembly 11. The assembly 13, the eccentric sleeve assembly 14 that is rotated inside the outer cylinder bush portion 13 a, the main shaft assembly 15 that holds the mantle 17 that is fitted and rotated in the eccentric sleeve assembly 14, and the eccentric sleeve assembly 14 rotates. And a rotational power transmission system 20 that transmits power.

Among these, the eccentric sleeve assembly 14 includes an inner cylinder bush portion 14a that is rotated by being fitted to the outer cylinder bush portion 13a of the lower frame assembly 13, and a flange portion 14b that is fixed to the upper portion of the inner cylinder bush portion 14a. Have. The flange part 14b extends from the upper part of the inner cylinder bush part 14a to the gear space 40 outside the outer cylinder bush part 13a, and is supported from below by a thrust bearing 19 provided at the upper end part of the outer cylinder bush part 13a. Has been. In the present embodiment, the eccentric sleeve assembly 14 can be pulled upward from the lower frame assembly 13 by fixing the flange portion 14b to the upper portion of the inner cylinder bush portion 14a. A bevel gear 21a is fixed to the distal end portion of the flange portion 14b. The bevel gear 21a is disposed coaxially with the rotation axis of the inner cylinder bush portion 14a.

Rotational power transmission system 20 has a horizontal shaft 22 connected to a drive motor (not shown), and a bevel pinion 21b fixed to one end of horizontal shaft 22. The horizontal shaft 22 is oriented in a direction perpendicular to the rotation axis of the inner cylinder bush portion 14a. The bevel pinion 21b fixed to one end of the horizontal shaft 22 is disposed so as to mesh with the bevel gear 21a fixed to the flange portion 14b. When the horizontal shaft 22 and the bevel pinion 21b are rotated together by the rotational power of the drive motor, the rotational power is transmitted from the bevel pinion 21b to the bevel gear 21a, and the bevel gear 21a, the flange portion 14b, and the inner cylinder bush portion 14a. It is integrally driven to rotate around the rotation axis of the inner cylinder bush portion 14a.

A through-hole extending in a direction inclined with respect to the rotation axis of the inner cylinder bush portion 14a is formed at an eccentric position of the inner cylinder bush portion 14a, and the main shaft assembly 15 is inserted into the through hole of the inner cylinder bush portion 14a. Has been. A funnel-shaped mantle 17 is fixed to the upper part of the main shaft assembly 15.

In the illustrated example, the rotary crusher 10 is a so-called hydraulic cone crusher, and the upper end of the spindle assembly 15 is supported by a bearing 23 held by the upper frame assembly 11. On the other hand, a spindle step 15a having a convex spherical surface is fixed to the lower end portion of the spindle assembly 15. Under the spindle step 15a, a step washer 13c having a concave spherical surface and wear for supporting the back surface of the step washer 13c. Plates 13b are stacked and arranged. The wear plate 13 b is fixed to the bottom of the lower frame assembly 13, more specifically, to the ram of the hydraulic cylinder assembly installed below the lower frame assembly 13. A sliding portion is formed in which the convex spherical surface of the main spindle step 15a and the concave spherical surface of the step washer 13c slide.

When the flange portion 14b of the eccentric sleeve assembly 14 and the inner cylinder bush portion 14a are integrally rotated by the rotational power transmission system 20, the main shaft assembly 15 moves around the rotation axis of the inner cylinder bush portion 14a with the bearing 23 as a fulcrum. The difference is exercised. The mantle 17 is precessed with respect to the cone cave 12 according to the precession of the main shaft assembly 15 so as to crush the object to be crushed supplied to the crushing chamber 18 sandwiched between the mantle 17 and the cone cave 12. It has become.

During the operation of the rotary crusher 10, the first bearing portion 41 and the inner cylinder bush between the main shaft assembly 15 and the inner cylinder bush portion 14a are used to smoothly precess the main spindle assembly 15 that is subjected to a large load. It is necessary to supply a proper amount of lubricating oil to the second bearing portion 42 between the portion 14a and the outer cylinder bush portion 13a to maintain a healthy oil film. Therefore, the rotary crusher 10 is provided with an oil supply structure 30 for supplying lubricating oil to the first bearing portion 41 and the second bearing portion 42, respectively.

FIG. 2 is a schematic view showing the oil supply structure 30 in an enlarged manner. In FIG. 2, the arrow indicates the direction in which the lubricating oil flows.

As shown in FIG. 2, the oil supply structure 30 is installed inside the lower frame assembly 13 and supplies oil to the first thrust bearing portion 41 and the annular thrust seal 33 that supports the lower end portion of the inner cylinder bush portion 14 a from below. Open to the bottom of the lower frame assembly 13, more specifically, the first oil inlet 31 that opens to the center of the ram of the hydraulic cylinder assembly, and the inner peripheral surface of the outer cylinder bush portion 13 a to supply oil to the second bearing portion 42. And a second refueling inlet 32.

Specifically, the thrust seal 33 is, for example, a metal ring (ring) having a parallel plate-like longitudinal section. In the illustrated example, an annular thrust seal mounting frame 34 is fixed to the bottom of the lower frame assembly 13 so as to surround the outside of the first oil supply inlet 31. An annular step 35 is protruded from the upper end of the thrust seal mounting frame 34, and the thrust seal 33 is fitted to the inner diameter side of the step 35 and supported from below. The lower end surface of the inner cylinder bush portion 14 a is pressed against the upper surface of the thrust seal 33 by the weight of the eccentric sleeve assembly 14 and is in surface contact. The lower end surface of the inner cylinder bush portion 14a is preferably chamfered or planarized in order to increase the contact area with the upper surface of the thrust seal 33.

In the illustrated example, a through hole 36 is formed so as to penetrate the central portion of the wear plate 13b and the central portion of the step washer 13c, and the first oil supply inlet 31 is opened inside the through hole 36. Yes. As shown in FIG. 2, the lubricating oil introduced into the through hole 36 from the first oil supply inlet 31 is the inner diameter side end of the sliding portion between the wear plate 13b and the step washer 13c, the step washer 13c and the main spindle step. It flows into the inner diameter side end of the sliding part between 15a and lubricates each sliding part. Then, the lubricating oil that has passed through each sliding portion flows out from the outer diameter side end portion of each sliding portion into the annular space 37 outside the lower end portion of the spindle assembly 15, and from the annular space 37, the first bearing portion 41. The first bearing portion 41 is lubricated. The lubricating oil that has passed through the first bearing portion 41 flows out from the upper end portion of the first bearing portion 41 into the gear housing space 40 outside the outer cylinder bush portion 13a, and the lubricating oil that accumulates on the floor of the gear housing space 40 is 1 is recovered from the fuel supply outlet 39 shown in FIG.

On the other hand, a part of the lubricating oil introduced from the second oil supply inlet 32 to the second bearing portion 42 flows into a region below the second oil supply inlet 32 in the second bearing portion 42 and lubricates the lower region. Let Then, the lubricating oil that has passed through the lower region of the second bearing portion 42 flows out from the lower end portion of the second bearing portion 42 into the annular space 38 provided below, and the lubricating oil that accumulates on the floor of the annular space 38 is 1 is recovered from the fuel supply outlet 39 shown in FIG. Further, the remaining portion of the lubricating oil introduced directly from the second oil supply inlet 32 to the second bearing portion 42 flows into a region above the second oil supply inlet 32 in the second bearing portion 42, and the upper region Lubricate. Then, the lubricating oil that has passed through the upper region of the second bearing portion 42 flows out from the upper end portion of the second bearing portion 42 into the gear housing space 40 outside the outer cylinder bush portion 13a and accumulates on the floor of the gear housing space 40. The lubricating oil is recovered from the oil supply outlet 39 shown in FIG.

Incidentally, FIG. 4 is a schematic view showing a comparative example of an oil supply structure in an upper open type rotary crusher. In FIG. 4, the arrow indicates the direction in which the lubricating oil flows. In the upper open maintenance type rotary crusher as shown in FIG. 4, the flange portion 114b is supported from below by a thrust bearing 119 provided at the upper end portion of the outer cylinder bush portion 113a. A thrust seal is not installed at the lower end of 115a, and is supplied from the first oil supply inlet 131 to the first bearing part 141 and from the second oil supply inlet 132 to the second bearing part 142. The lubricating oil flow path is not structurally separated. In particular, the oil supply outlet side 152 of the second bearing portion 142 and the oil supply inlet side 151 of the first bearing portion 141 communicate with each other. Therefore, the oil distribution amount to each bearing part 141 and 142 is unstable, and it may be difficult to maintain a healthy oil film especially under adverse conditions.

On the other hand, as shown in FIG. 2, in the present embodiment, the lower end surface of the inner cylinder bush portion 14 a is in surface contact with the upper surface of the thrust seal 33, so that the annular space 37 outside the lower end portion of the spindle assembly 15 The annular space 38 provided below the lower end portion of the second bearing portion 42 is structurally separated. Thereby, the flow path of the lubricating oil supplied from the first oil supply inlet 31 to the first bearing portion 41 and the flow path of the lubricating oil supplied from the second oil supply inlet 32 to the second bearing portion 42 are substantially reduced. As a result, the oil supply amount control for maintaining a healthy oil film in the first bearing portion 41 and the second bearing portion 42 is possible.

Further, in the present embodiment, the inner peripheral surface of the step portion 35 protruding from the outer diameter side of the thrust seal 33 surrounds the outer peripheral surface of the lower end portion of the inner cylinder bush portion 14 a supported by the thrust seal 33. Yes. The gap between the inner peripheral surface of the step portion 35 and the outer peripheral surface of the lower end portion of the inner cylinder bush portion 14a is preferably narrow. For the lubricating oil that has infiltrated between the lower end surface of the inner cylinder bush portion 14 a and the upper surface of the thrust seal 33, the stepped portion 35 protruding from the outer diameter side of the thrust seal 33 functions as a flow resistance. Therefore, even if an outward force is applied to the lubricating oil infiltrated between the lower end surface of the inner cylinder bush portion 14a and the upper surface of the thrust seal 33 with an eccentric motion of the main shaft assembly 15, the lubricating oil is ejected to the outside. This can be suppressed.

Next, the operation of the rotary crusher 10 according to this embodiment will be described.

First, the lubricating oil is supplied from the first oil supply inlet 31 to the first bearing portion 41, and the lubricating oil is supplied from the second oil supply inlet 32 to the second bearing portion 42. In the present embodiment, since the thrust seal 33 structurally separates the flow path of the lubricating oil supplied to the first bearing portion 41 and the flow path of the lubricating oil supplied to the second bearing portion 42, The first bearing portion 41 and the second bearing portion 42 can be independently lubricated, and the amount of lubrication is controlled so that a healthy oil film is maintained in the first bearing portion 41 and the second bearing portion 42. Is possible.

Next, rotational power is transmitted from the rotational power transmission system 20 to the flange portion 14b of the eccentric sleeve assembly 14, and the flange portion 14b and the inner cylinder bush portion 14a are integrally rotated around the rotation axis of the inner cylinder bush portion 14a. . Along with the rotation of the inner cylinder bush portion 14a, the main shaft assembly 15 fitted to the inner cylinder bush portion 14a is precessed about the bearing 23 as a fulcrum. The mantle 17 fixed to the main shaft assembly 15 is precessed with respect to the cone cave 12 according to the precession of the main shaft assembly 15, and the gap between the mantle 17 and the cone cave 12 is changed in a wide and narrow manner with each rotation. .

Next, an object to be crushed such as a rough stone is fed from the hopper 25 at the upper part of the upper frame assembly 11. The thrown object to be crushed falls into a crushing chamber 18 formed between the mantle 17 and the corn cave 12 and is captured between the mantle 17 and the corn cave 12. When the mantle 17 is rotated and the gap between the mantle 17 and the corn cave 12 becomes narrow, the object to be crushed is crushed.

Thereafter, when the gap between the mantle 17 and the corn cave 12 is widened, the material to be crushed falls in the crushing chamber 18 to a portion where the gap between the mantle 17 and the corn cave 12 becomes wider, and the mantle 17 and the corn cave 12. When the gap between is narrowed again, it is further crushed. The material to be crushed gradually becomes fine by repeating crushing and dropping, becomes a product of a predetermined particle size, falls to the floor through the gap between the mantle 17 and the corn cave 12, and is discharged from the opening of the floor to the outside of the machine. Is done.

During operation of the rotary crusher 10, the oil supply amount is controlled so that a healthy oil film is maintained in the first bearing portion 41 and the second bearing portion 42, thereby reducing the replacement frequency of the lubricating oil. At the same time, the bearing portions 41 and 42 can be prevented from being damaged due to seizure or the like.

According to the present embodiment as described above, since the flange portion 14b of the eccentric sleeve assembly 14 is fixed to the upper portion of the inner cylinder bush portion 14a, the eccentric sleeve assembly 14 can be pulled upward from the lower frame assembly 13. If the bearing portions 41 and 42 and the gears 21a and 21b are damaged, the eccentric sleeve assembly 14 can be pulled upward to perform maintenance work on the bearing portions 41 and 42 and the gears 21a and 21b. it can. Therefore, it is not necessary to disassemble the hydraulic cylinder assembly arranged below the lower frame assembly 13, and there is no need for a dangerous work performed by an operator under the suspended load, which is superior to the lower open maintenance type. Maintainability.

Further, according to the present embodiment, the annular thrust seal 33 that is installed inside the lower frame assembly 13 and supports the lower end portion of the inner cylinder bush portion 14a from below is provided from the first oil supply inlet 31 to the first bearing portion. Since the flow path of the lubricating oil supplied to 41 and the flow path of the lubricating oil supplied from the second oil supply inlet 32 to the second bearing portion 42 are separated, the first bearing portion 41 and the second bearing Oil supply amount control for maintaining a healthy oil film in the unit 42 is possible. As a result, the replacement frequency of the lubricating oil is reduced, and the bearing portions 41 and 42 can be prevented from being damaged due to seizure or the like.

Further, according to the present embodiment, the inner peripheral surface of the step portion 35 surrounds the outer peripheral surface of the lower end portion of the inner cylinder portion 14 a, and between the lower end surface of the inner cylinder bush portion 14 a and the upper surface of the thrust seal 33. The step portion 35 functions as a flow resistance for the lubricating oil infiltrated into. Therefore, even if an outward force is applied to the lubricating oil infiltrated between the lower end surface of the inner cylinder bush portion 14a and the upper surface of the thrust seal 33 with the eccentric motion of the main shaft assembly 15, the lubricating oil jets outward. This can be suppressed.

In addition, according to the present embodiment, since the thrust bearing 19 that supports the flange portion 14b from below is provided at the upper end portion of the outer cylinder portion 13a, the load of the eccentric sleeve 14 causes the thrust seal 33 and the thrust bearing 19 to load. And distributed. Thereby, the wear of the thrust seal 33 can be delayed.

In addition, it is not necessarily essential that the thrust bearing 19 is provided at the upper end portion of the outer cylinder portion 13a. That is, the thrust bearing 19 can be omitted from the upper end portion of the outer cylinder portion 13a.

In the aspect in which the thrust bearing 19 is provided at the upper end portion of the outer cylinder portion 13a, in some cases, the load applied from the lower end surface of the inner cylinder portion 14a to the upper surface of the thrust seal 33 may become insufficient, or the inner tolerance may increase due to assembly tolerances. There is a possibility that a gap may be formed between the lower end surface of the cylindrical portion 14a and the upper surface of the thrust seal 33.

On the other hand, in a mode in which the thrust bearing 19 is omitted from the upper end portion of the outer cylinder portion 13a, a sufficient load is applied from the lower end surface of the inner cylinder portion 14a to the upper surface of the thrust seal 33, so that the first bearing portion 41 is supplied. It can be ensured more reliably that the flow path of the lubricating oil and the flow path of the lubricating oil supplied to the second bearing portion 42 are separated.

In the example shown in FIG. 1, the rotary crusher 10 is a so-called hydraulic cone crusher, but is not limited thereto. For example, the oil supply structure 30 according to the present embodiment can also be applied to a mechanical (Simons) cone crusher.

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

As shown in FIG. 4, the rotary crusher 210 according to the present embodiment includes an upper frame assembly 211 that holds a cone cave 212 and a lower frame that has an outer cylinder bush portion 213 a disposed below the upper frame assembly 211. The assembly 213, the eccentric sleeve assembly 214 rotated inside the outer cylinder bush portion 213a, the spindle assembly 215 holding the mantle 217 fitted and rotated in the eccentric sleeve assembly 214, and the eccentric sleeve assembly 214 rotated. And a rotational power transmission system 220 that transmits power.

Among these, the eccentric sleeve assembly 214 includes a sleeve portion 214c that holds the inner cylinder bush portion 214a that is rotated by being fitted to the outer cylinder bush portion 213a of the lower frame assembly 213, and a flange portion that is fixed to the upper portion of the sleeve portion 214c. 214b. The flange portion 214b extends from the upper portion of the sleeve portion 214c to a gear accommodating space 240 formed outside the outer cylinder bush portion 213a, and is lowered by a thrust bearing 219 provided at the upper end portion of the outer cylinder bush portion 213a. It is supported from. In the present embodiment, since the flange portion 214b extends above the sleeve portion 214c, the eccentric sleeve assembly 214 can be pulled out upward from the lower frame assembly 213. A bevel gear 221a is fixed to the distal end portion of the flange portion 214b. The bevel gear 221a is disposed coaxially with the rotation axis of the outer cylinder bush portion 213a.

The rotational power transmission system 220 has a horizontal shaft 222 connected to a drive motor (not shown), and a bevel pinion 221b fixed to one end of the horizontal shaft 222. The horizontal shaft 222 is oriented in a direction perpendicular to the rotation axis of the outer cylinder bush portion 213a. The bevel pinion 221b fixed to one end of the horizontal shaft 222 is disposed in the gear housing space 240 so as to mesh with the bevel gear 221a fixed to the flange portion 214b. When the horizontal shaft 222 and the bevel pinion 221b are rotated together by the rotational power of the drive motor, the rotational power is transmitted from the bevel pinion 221b to the bevel gear 221a, and the eccentric sleeve assembly 214 rotates around the rotational axis of the outer cylinder bush portion 213a. Is driven to rotate.

The sleeve portion 214c is formed with a through hole extending in a direction inclined with respect to the rotation axis of the outer cylinder bush portion 213a, and the inner cylinder bush portion 214a is fitted into the hole extending in the inclination direction. . The main shaft assembly 215 is inserted into the inner cylinder bush portion 214a. A funnel-shaped mantle 217 is fixed to the upper part of the main shaft assembly 215.

In the illustrated example, the rotary crusher 210 is a so-called hydraulic cone crusher, and the upper end portion of the spindle assembly 215 is supported by a bearing 223 held by the upper frame assembly 211. On the other hand, a spindle step 215a having a convex spherical surface is fixed to the lower end portion of the spindle assembly 215. Under the spindle step 215a, a step washer 213c having a concave spherical surface and wear for supporting the back surface of the step washer 213c. Plates 213b are stacked and arranged. The wear plate 213b is fixed to the bottom of the lower frame assembly 213, more specifically, to a ram of a hydraulic cylinder assembly installed below the lower frame assembly 213. A sliding part is formed in which the convex spherical surface of the main spindle step 215a and the concave spherical surface of the step washer 213c slide.

When the eccentric sleeve assembly 214 is rotated by the rotational power transmission system 220, the main shaft assembly 215 is precessed around the rotation axis of the inner cylinder bush portion 214a with the bearing 223 as a fulcrum. The mantle 217 is precessed with respect to the cone cave 212 according to the precession of the main shaft assembly 215 so as to crush the object to be crushed supplied to the crushing chamber 218 sandwiched between the mantle 217 and the cone cave 212. It has become.

During the operation of the rotary crusher 210, the first bearing portion 241 and the sleeve portion 214c between the main shaft assembly 215 and the inner cylinder bush portion 214a are used in order to smoothly precess the main shaft assembly 215 to which a large load is applied. It is necessary to supply a proper amount of lubricating oil to the second bearing portion 242 between the outer cylinder bush portion 213a and maintain a healthy oil film. Therefore, the rotary crusher 210 is provided with an oil supply structure 230 for supplying lubricating oil to the first bearing portion 241 and the second bearing portion 242, respectively.

FIG. 5 is a schematic diagram showing the refueling structure 230 in an enlarged manner. In FIG. 5, the arrow indicates the direction in which the lubricating oil flows.

As shown in FIG. 5, the oil supply structure 230 includes a first oil supply inlet 231 that opens to the bottom of the lower frame assembly 213, more specifically, the ram center of the hydraulic cylinder assembly, so as to supply oil to the first bearing portion 241. The second oil supply inlet 232 that opens to the inner peripheral surface of the outer cylinder bush portion 213a so as to supply oil to the second bearing portion 242 and the inner side of the lower frame assembly 213 are opposed to the end surface of the lower end portion of the sleeve portion 214c. And an annular seal forming portion 234 having a non-contact surface.

In the illustrated example, the seal forming portion 234 is provided so as to protrude upward from the inner surface of the lower frame assembly 213, and a non-contact surface is provided at the upper end portion thereof. Since the flange portion 214 b of the eccentric sleeve assembly 214 is supported from below by the thrust bearing 219, the sleeve portion 214 c of the eccentric sleeve assembly 214 is positioned at a certain height position, and thereby the non-contact surface of the seal forming portion 234. A gap 233 with a constant interval is formed between the sleeve portion 214c and the end surface of the lower end portion of the sleeve portion 214c.

A gap 233 formed between the non-contact surface of the seal forming portion 234 and the end surface of the lower end portion of the sleeve portion 214c is sealed with lubricating oil, and the lubricating oil supplied from the first oil supply inlet 231 is second. The interval is adjusted so as to prevent inflow into the bearing portion 242. Specifically, the gap 233 is, for example, about 0.5 mm to 1.0 mm, but is not limited to a value within this range.

As shown in FIG. 5, a partition plate 235 is disposed on the outer periphery of the annular seal forming portion 234. The partition plate 235 is provided below the second bearing portion 242 so as to surround the outer peripheral surface of the lower end portion of the sleeve portion 214c, and the inner peripheral surface of the partition plate 235 and the outer peripheral surface of the lower end portion of the sleeve portion 214c. An annular oil reservoir 250 is formed between the two. A part of the lubricating oil flowing out from the lower end portion of the second bearing portion 242 is stored in the oil reservoir portion 250. The oil reservoir 250 is communicated with a gap 233 between the non-contact surface of the seal forming portion 234 and the end surface of the lower end portion of the sleeve portion 214c.

Hereinafter, with reference to FIGS. 6 to 8, the operation of the oil reservoir 250 accompanying the rotation of the eccentric sleeve assembly 214 will be described.

FIG. 6 is a cross-sectional view showing an oil film formed on the first bearing portion 241 of the rotary crusher 210. In FIG. 6, among the phases of the eccentric sleeve assembly 214, θ = 0 ° is the phase at which the distance between the outer peripheral surface of the spindle assembly 215 and the inner peripheral surface of the inner cylinder bush portion 214 a is maximum, and the phase at which the interval is minimum. θ = 180 °, and clockwise is the positive direction.

In FIG. 6, the eccentric sleeve assembly 214 rotates clockwise, whereby the portion (θ = 180) in which the distance between the outer peripheral surface of the main shaft assembly 215 and the inner peripheral surface of the inner cylinder bush portion 214a is minimized. The part corresponding to the phase of °) also rotates clockwise. The portion where the distance between the outer peripheral surface of the spindle assembly 215 and the inner peripheral surface of the inner cylinder bush portion 214a is the minimum (the portion corresponding to the phase of θ = 180 °) rotates clockwise, so that the first The lubricating oil supplied to the bearing portion 241 is pushed clockwise while being sandwiched between the outer peripheral surface of the main shaft assembly 215 and the inner peripheral surface of the inner cylinder bush portion 214a. As a result, the first bearing portion 241 between the outer peripheral surface of the spindle assembly 215 and the inner peripheral surface of the inner cylinder bush portion 214a has a vicinity of a portion corresponding to a phase of θ = 180 ° as shown in FIG. An oil film is formed over a portion corresponding to the phase of θ = 0 °.

FIG. 7 shows the pressure distribution of this oil film. In the region adjacent to the first bearing portion 241 in the clockwise direction with respect to the phase of θ = 180 °, the eccentric sleeve assembly 214 rotates clockwise, so that the outer peripheral surface of the spindle assembly 215 and the inner cylinder bush portion Since the oil film is crushed between the inner peripheral surface of 214a, the pressure of the oil film increases.

As a result, as shown in FIG. 8, in the gap 233 between the non-contact surface of the seal forming portion 234 and the end surface of the lower end portion of the sleeve portion 214c, a region corresponding to a phase of around θ = 180 ° to 360 °. Then, when the lubricating oil in the gap 233 receives pressure from the oil film formed in the first bearing portion 241, the lubricating oil flows in a direction that flows out from the gap 233 to the oil reservoir 250.

On the other hand, although not shown in FIG. 7, the eccentric sleeve assembly 214 rotates clockwise in the region adjacent to the first bearing portion 241 in the counterclockwise direction with respect to the phase of θ = 180 °. Thus, the oil film is lost, and the space between the outer peripheral surface of the main shaft assembly 215 and the inner peripheral surface of the inner cylinder bush portion 214a is widened, so that negative pressure is generated in the space.

As a result, as shown in FIG. 8, in the gap 233 between the non-contact surface of the seal forming portion 234 and the end surface of the lower end portion of the sleeve portion 214c, a region corresponding to a phase around θ = 0 ° to 180 °. Then, when the lubricating oil in the gap 233 receives the negative pressure generated in the first bearing portion 241, the lubricating oil flows in a direction flowing from the gap 233 to the first bearing portion 241.

Here, as a comparative example, a mode in which the oil reservoir 250 is not formed outside the gap 233 is considered. In this aspect, when the flow of the lubricating oil flows in the direction from the clearance 233 to the first bearing portion 241 due to the rotation of the eccentric sleeve assembly 214, the air in the annular space 238 is sucked into the clearance 233 and bubbles are generated in the lubricating oil. Is mixed, there is a high possibility that an oil film breakage, which is one of the causes of bearing damage, occurs inside the first bearing portion 241.

On the other hand, in the present embodiment, since the oil reservoir 250 is formed outside the gap 233, the lubricating oil directed to flow into the first bearing portion 241 from the gap 233 by the rotation of the eccentric sleeve assembly 214 is used. When the flow occurs, the lubricating oil stored in the oil reservoir 250 is sucked into the gap 233. As a result, air in the annular space 238 is effectively prevented from being sucked into the gap 233 and bubbles being mixed into the lubricating oil.

As shown in the figure, the oil reservoir 250 is preferably formed at a position higher than the gap 233. In this case, since the lubricating oil stored in the oil reservoir 250 is gathered near the gap 233 due to gravity, the flow of the lubricating oil flowing in the direction from the gap 233 to the first bearing portion 241 is caused by the rotation of the eccentric sleeve assembly 214. When it occurs, it is guaranteed that the lubricating oil stored in the oil reservoir 250 is sucked into the gap 233, and the air in the annular space 238 can be more reliably prevented from being sucked into the gap 233.

In the illustrated example, a through hole 236 is formed so as to penetrate the central portion of the wear plate 213b and the central portion of the step washer 213c, and the first oil supply inlet 231 is opened inside the through hole 236. Yes. As shown in FIG. 5, the lubricating oil introduced into the through hole 236 from the first oil supply inlet 231 is the inner diameter side end portion of the sliding portion between the wear plate 213b and the step washer 213c and the step washer 213c and the main spindle step. Each of the sliding portions is lubricated by flowing into the inner diameter side end portion of the sliding portion between 215a. Then, the lubricating oil that has passed through each sliding portion flows out from the outer diameter side end portion of each sliding portion into the annular space 237 outside the lower end portion of the spindle assembly 215, and from the annular space 237 to the first bearing portion 241. The first bearing portion 241 is lubricated. The lubricating oil that has passed through the first bearing portion 241 flows out from the upper end portion of the first bearing portion 241 to the gear housing space 240 outside the outer cylinder bush portion 213a, and the lubricating oil that accumulates on the floor of the gear housing space 240 is These are recovered from the fuel supply outlet 239 shown in FIG.

On the other hand, a part of the lubricating oil introduced into the second bearing portion 242 from the second oil supply inlet 232 flows into a region below the second oil supply inlet 232 in the second bearing portion 242 and lubricates the lower region. Let Then, the lubricating oil that has passed through the lower region of the second bearing portion 242 flows out from the lower end portion of the second bearing portion 242 and is stored in the oil reservoir 250 provided below the lubricating oil. Lubricating oil overflowing from the oil reservoir 250 flows into the outer annular space 238, and the lubricating oil remaining on the floor of the annular space 238 is recovered from the oil supply outlet 239 shown in FIG. Further, the remaining portion of the lubricating oil introduced directly from the second oil supply inlet 232 to the second bearing portion 242 flows into a region above the second oil supply inlet 232 in the second bearing portion 242, and the upper region Lubricate. Then, the lubricating oil that has passed through the upper region of the second bearing portion 242 flows out from the upper end portion of the second bearing portion 242 to the gear accommodating space 240 outside the outer cylinder bush portion 213a and accumulates on the floor of the gear accommodating space 240. Lubricating oil is collect | recovered from the oil supply exit 239 shown in FIG.

Incidentally, FIG. 9 is a schematic view showing a comparative example of an oil supply structure in an upper open type rotary crusher. In FIG. 9, the arrow indicates the direction in which the lubricating oil flows. In the upper open maintenance type rotary crusher as shown in FIG. 9, the flow path of the lubricating oil supplied from the first oil supply inlet 2131 to the first bearing portion 2141 and the second bearing portion 2142 from the second oil supply inlet 2132. Is not structurally separated from the flow path of the lubricating oil supplied to. In particular, the oil supply outlet side 2152 of the second bearing portion 2142 and the oil supply inlet side 2151 of the first bearing portion 2141 communicate with each other, and the lubricating oil supplied from the first oil supply inlet 2131 is not only the first bearing portion 2141 but also the first oil. It also flows into the two bearing portions 2142. Therefore, the amount of oil distribution to the bearings 2141 and 2142 is unstable, and it may be difficult to maintain a healthy oil film particularly under adverse conditions.

On the other hand, as shown in FIG. 5, in the present embodiment, a seal forming portion 234 is provided inside the lower frame assembly 213, and the non-contact surface of the seal forming portion 234 and the end surface of the lower end portion of the sleeve portion 214c. Since the gap 233 between them is sealed with lubricating oil, the first bearing portion 241 and the second bearing portion 242 can be independently supplied with oil. Therefore, the amount of oil supply can be controlled so that a healthy oil film is maintained in the first bearing portion 241 and the second bearing portion 242.

Next, the operation of the rotary crusher 210 according to this embodiment will be described.

First, the lubricating oil is supplied from the first oil supply inlet 231 to the first bearing portion 241, and the lubricating oil is supplied from the second oil supply inlet 232 to the second bearing portion 242. Further, rotational power is transmitted from the rotational power transmission system 220 to the flange portion 214b of the eccentric sleeve assembly 214, and the eccentric sleeve assembly 214 is rotated about the rotational axis of the outer cylinder bush portion 213a.

In the present embodiment, during the rotation of the eccentric sleeve assembly 214, the lubricating oil supplied from the first oil supply inlet 231 by the gap 233 between the non-contact surface of the seal forming portion 234 and the end surface of the lower end portion of the sleeve portion 214c. Is prevented from flowing into the second bearing portion 242. Therefore, a healthy oil film can be maintained in the first bearing portion 241 and the second bearing portion 242 by controlling the amount of oil supplied to the bearing portions 241 and 242.

As the eccentric sleeve assembly 214 rotates, the spindle assembly 215 fitted to the inner cylinder bush portion 214a is precessed about the bearing 223 as a fulcrum. The mantle 217 fixed to the main shaft assembly 215 is precessed with respect to the cone cave 212 in accordance with the precession of the main shaft assembly 215, and the gap between the mantle 217 and the cone cave 212 is changed widely with each rotation. .

Next, an object to be crushed such as a rough stone is fed from the hopper 25 at the upper part of the upper frame assembly 211. The thrown object to be crushed falls into the crushing chamber 218 formed between the mantle 217 and the corn cave 212 and is captured between the mantle 217 and the corn cave 212. When the mantle 217 is rotated and the gap between the mantle 217 and the corn cave 212 is narrowed, the object to be crushed is crushed.

Thereafter, when the gap between the mantle 217 and the corn cave 212 is widened, the material to be crushed falls in the crushing chamber 218 to a portion where the gap between the mantle 217 and the corn cave 212 becomes wider, and the mantle 217 and the corn cave 212 are dropped. When the gap between is narrowed again, it is further crushed. The material to be crushed gradually becomes finer by repeated crushing and dropping, becomes a product of a predetermined particle size, falls to the floor through the gap between the mantle 217 and the corn cave 212, and is discharged from the opening of the floor to the outside of the machine. Is done.

During operation of the rotary crusher 210, a sufficient amount of oil can be stably and independently controlled so that a healthy oil film is maintained in the first bearing portion 241 and the second bearing portion 242. The bearing portions 241 and 242 can be prevented from being damaged due to seizure or the like.

According to the present embodiment as described above, since the flange portion 214b of the eccentric sleeve assembly 214 extends above the sleeve portion 214c, the eccentric sleeve assembly 214 can be pulled upward from the lower frame assembly 213. When the bearing parts 241 and 242 and the gears 221a and 221b are damaged, the eccentric sleeve assembly 214 can be pulled upward to perform maintenance work on the bearing parts 241 and 242 and the gears 221a and 221b. . Therefore, it is not necessary to disassemble the hydraulic cylinder assembly arranged below the lower frame assembly 213, and there is no need for dangerous work performed by the operator under the suspended load, which is superior to the lower open maintenance type. Maintainability.

Further, according to the present embodiment, since the gap 233 between the non-contact surface of the seal forming portion 234 and the end surface of the lower end portion of the sleeve portion 214c is sealed with the lubricating oil, the first bearing portion 241 and the first The oil supply amount control for maintaining a healthy oil film in the two bearing portions 242 is possible. This can prevent the bearing portions 241 and 242 from being damaged due to seizure or the like.

Further, according to the present embodiment, the partition plate 235 is provided so as to surround the outer peripheral surface of the lower end portion of the sleeve portion 214c, and the inner peripheral surface of the partition plate 235 and the outer peripheral surface of the lower end portion of the sleeve portion 214c Since the annular oil reservoir 250 formed between the gaps 233 communicates with the gap 233, when the eccentric sleeve assembly 214 rotates, the lubricating oil in the gap 233 generates a radially inward flow. Thus, the lubricating oil stored in is sucked into the gap 233. As a result, air in the annular space 238 can be prevented from being sucked into the gap 233 and bubbles being mixed with the lubricating oil.

Further, according to the present embodiment, since the oil reservoir 250 is formed at a position higher than the gap 233, the lubricating oil stored in the oil reservoir 250 is gathered near the gap 233 by gravity. This ensures that the lubricating oil stored in the oil reservoir 250 is sucked into the gap 233 when the eccentric sleeve assembly 214 rotates to cause the lubricating oil in the gap 233 to flow inward in the radial direction. The air of 238 can be reliably prevented from being sucked into the gap 233.

In the example shown in FIG. 4, the rotary crusher 210 is a so-called hydraulic cone crusher, but is not limited to this. For example, the oil supply structure 230 according to the present embodiment can also be applied to a mechanical (Simons type) cone crusher.

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

As shown in FIG. 10, the rotary crusher 310 according to the present embodiment includes an upper frame assembly 311 that holds a cone cave 312 and a lower frame that has an outer cylinder bush portion 313 a disposed below the upper frame assembly 311. The assembly 313, the eccentric sleeve assembly 314 rotated inside the outer cylinder bushing 313a, the spindle assembly 315 holding the mantle 317 fitted and rotated in the eccentric sleeve assembly 314, and the eccentric sleeve assembly 314 rotated. And a rotational power transmission system 320 that transmits power.

Among them, the eccentric sleeve assembly 314 includes a sleeve portion 314c that holds the inner cylinder bush portion 314a that is rotated by being fitted to the outer cylinder bush portion 313a of the lower frame assembly 313, and a flange portion that extends above the sleeve portion 314c. 314b. The flange portion 314b extends from the upper portion of the sleeve portion 314c to a gear housing space 340 formed outside the outer cylinder bush portion 313a, and is lowered by a thrust bearing 319 provided at the upper end portion of the outer cylinder bush portion 313a. It is supported from. In the present embodiment, the flange portion 314b extends above the sleeve portion 314c, so that the eccentric sleeve assembly 314 can be pulled upward from the lower frame assembly 313. A bevel gear 321a is fixed to the tip of the flange portion 314b. The bevel gear 321a is disposed coaxially with the rotation axis of the outer cylinder bush portion 313a.

Rotational power transmission system 320 has a horizontal shaft 322 connected to a drive motor (not shown), and a bevel pinion 321b fixed to one end of horizontal shaft 322. The horizontal shaft 322 is oriented in a direction perpendicular to the rotation axis of the outer cylinder bush portion 313a. The bevel pinion 321b fixed to one end of the horizontal shaft 322 is disposed in the gear housing space 340 so as to mesh with the bevel gear 321a fixed to the flange portion 314b. When the horizontal shaft 322 and the bevel pinion 321b are rotated together by the rotational power of the drive motor, the rotational power is transmitted from the bevel pinion 321b to the bevel gear 321a, and the eccentric sleeve assembly 314 rotates around the rotational axis of the outer cylinder bush portion 313a. Is driven to rotate.

The sleeve portion 314c is formed with a through hole extending in a direction inclined with respect to the rotation axis of the outer cylinder bush portion 313a, and the inner cylinder bush portion 314a is fitted in the hole extending in the inclination direction. . The main shaft assembly 315 is inserted into the inner cylinder bush portion 314a. A funnel-shaped mantle 317 is fixed to the upper portion of the main shaft assembly 315.

In the illustrated example, the rotary crusher 310 is a so-called hydraulic cone crusher, and the upper end portion of the spindle assembly 315 is supported by a bearing 323 held by the upper frame assembly 311. On the other hand, a spindle step 315a having a convex spherical surface is fixed to the lower end portion of the spindle assembly 315. Under the spindle step 315a, a step washer 313c having a concave spherical surface and wear for supporting the back surface of the step washer 313c. Plates 313b are stacked and arranged. The wear plate 313b is fixed to the bottom of the lower frame assembly 313, more specifically, to a ram of a hydraulic cylinder assembly installed below the lower frame assembly 313. A sliding part is formed in which the convex spherical surface of the main spindle step 315a and the concave spherical surface of the step washer 313c slide.

When the eccentric sleeve assembly 314 is rotated by the rotational power transmission system 320, the main shaft assembly 315 is precessed around the rotation axis of the inner cylinder bush portion 314a with the bearing 323 as a fulcrum. The mantle 317 is precessed with respect to the cone cave 312 according to the precession of the main shaft assembly 315 so as to crush the object to be crushed supplied to the crushing chamber 318 sandwiched between the mantle 317 and the cone cave 312. It has become.

During the operation of the rotary crusher 310, the first bearing portion 341 and the sleeve portion 314c between the main shaft assembly 315 and the inner cylinder bush portion 314a are used for smoothly precessing the main shaft assembly 315 which is subjected to a large load. It is necessary to supply an appropriate amount of lubricating oil to the second bearing portion 342 between the outer cylinder bush portion 313a and the outer cylinder bush portion 313a to maintain a healthy oil film. Therefore, the rotary crusher 310 is provided with an oil supply structure 330 for supplying lubricating oil to the first bearing portion 341 and the second bearing portion 342, respectively.

FIG. 11 is a schematic diagram showing the refueling structure 330 in an enlarged manner. In FIG. 11, the arrow indicates the direction in which the lubricating oil flows.

As shown in FIG. 11, the oil supply structure 330 has an oil supply inlet 331 that opens to the bottom of the lower frame assembly 313, more specifically, to the center of the ram of the hydraulic cylinder assembly. The oil supply inlet 331 supplies both the lubricating oil for the first bearing portion 341 and the lubricating oil for the second bearing portion 342.

FIG. 12 is a cross-sectional view of the bearing portions 341 and 342 of the rotary crusher 310.

In the present embodiment, as shown in FIGS. 11 and 12, the inner peripheral surface of the inner cylinder bush portion 314a and the outer peripheral surface of the sleeve portion 314c are supplied from the oil supply inlet 331 to the first bearing portion 341, respectively. Vertical groove portions 351 and 352 for controlling the flow rate of the lubricating oil and the flow rate of the lubricating oil supplied from the oil supply inlet 331 to the second bearing portion 342 are provided.

The vertical groove portion 351 provided on the inner peripheral surface of the inner cylinder bush portion 314a is exposed to the first bearing portion 341, and the vertical groove portion 352 provided on the outer peripheral surface of the sleeve portion 314c is provided on the second bearing portion 342. Exposed.

The larger the cross-sectional area and the number of the longitudinal groove portions 351 exposed to the first bearing portion 341, the larger the cross section of the flow path of the first bearing portion 341, that is, the flow distribution to the first bearing portion 341 increases. Further, the larger the cross-sectional area and the number of the longitudinal groove portions 352 exposed to the second bearing portion 342, the larger the flow path cross section of the second bearing portion 342, that is, the flow rate distribution to the second bearing portion 342 increases. Therefore, by appropriately adjusting the cross-sectional area and number of the longitudinal groove portions 351 and 352 exposed to the bearing portions 341 and 342, the relative proportion of the flow distribution of the bearing portions 341 and 342 can be adjusted. As a result, the amount of oil distribution from the oil supply inlet 331 to each of the bearing portions 341 and 342 can be easily controlled.

In the illustrated example, a through hole 336 is formed so as to penetrate the central portion of the wear plate 313b and the central portion of the step washer 313c, and the oil supply inlet 331 is opened inside the through hole 336. As shown in FIG. 11, the lubricating oil introduced into the through hole 336 from the oil supply inlet 331 includes the inner diameter side end of the sliding portion between the wear plate 313b and the step washer 313c, the step washer 313c, the main spindle step 315a, Each of the sliding parts is lubricated by flowing into the inner diameter side end part of the sliding part between. Then, the lubricating oil that has passed through each sliding portion flows out from the outer diameter side end portion of each sliding portion into the annular space 337 outside the lower end portion of the spindle assembly 315.

Part of the lubricating oil that has flowed out into the annular space 337 flows into the lower end portion of the first bearing portion 341 and lubricates the first bearing portion 341. The lubricating oil that has passed through the first bearing portion 341 flows out from the upper end portion of the first bearing portion 341 to the gear housing space 340 outside the outer cylinder bush portion 313a, and the lubricating oil that accumulates on the floor of the gear housing space 340 is These are recovered from the fuel supply outlet 339 shown in FIG.

On the other hand, the remaining portion of the lubricating oil that has flowed out into the annular space 337 flows under the sleeve portion 314c and into the lower end portion of the second bearing portion 342, and lubricates the second bearing portion 342. The lubricating oil that has passed through the second bearing portion 342 flows out from the upper end portion of the second bearing portion 342 into the gear housing space 340 outside the outer cylinder bush portion 313a, and the lubricating oil that accumulates on the floor of the gear housing space 340 is These are recovered from the fuel supply outlet 339 shown in FIG.

Incidentally, FIG. 14 is a schematic view showing a comparative example of an oil supply structure in an upper open type rotary crusher. In FIG. 14, the arrow indicates the direction in which the lubricating oil flows. In the upper open maintenance type rotary crusher as shown in FIG. 14, the lubricating oil of the first bearing portion 3141 is supplied from the first oil supply inlet 3131 opening at the bottom of the lower frame assembly 3113, whereas the second The lubricating oil of the bearing portion 3142 is supplied from a second oil supply inlet 3132 that opens on the circumferential surface of the outer cylinder bush portion 3113a.

However, in this oil supply structure, a flow path of the lubricating oil supplied from the first oil supply inlet 3131 to the first bearing portion 3141 and a flow path of the lubricating oil supplied from the second oil supply inlet 3132 to the second bearing portion 3142 are provided. The lubricating oil supplied from the first oil supply inlet 3131 is not structurally separated, and in particular, the oil supply outlet side 3152 of the second bearing portion 3142 and the oil supply inlet side 3151 of the first bearing portion 3141 communicate with each other. Flows into not only the first bearing portion 3141 but also the second bearing portion 3142. Therefore, in the region below the second oil supply inlet 3132 in the second bearing portion 3142, there is a possibility that a downward flow and an upward flow are mixed and poor lubrication occurs. As a result, the amount of oil distribution to the bearing portions 3141 and 3142 becomes unstable, and it may be difficult to maintain a healthy oil film particularly under adverse conditions.

Further, in the example shown in FIG. 14, in order to supply oil from two locations of the first oil supply inlet 3131 and the second oil supply inlet 3132, piping materials (not shown) for supplying lubricating oil are used as the first oil supply inlet 3131 and It is necessary to connect to two places of the 2nd oil supply inlet 3132, and piping is complicated.

On the other hand, as shown in FIG. 11, in the present embodiment, the oil supply inlet 331 that opens to the bottom of the lower frame assembly 313 supplies both the lubricating oil of the first bearing portion 341 and the lubricating oil of the second bearing portion 342. It is supposed to be. Therefore, only the upward flow is formed in each of the bearing portions 341 and 342, and there is no possibility that poor lubrication will occur. As a result, the distribution amount of oil supply to the bearing portions 341 and 342 is stabilized, and the oil supply amount can be controlled so that a healthy oil film is maintained in the first bearing portion 341 and the second bearing portion 342.

Further, in this embodiment, since oil is supplied from one place of the oil supply inlet 331, a piping material (not shown) for supplying the lubricant need only be connected to one place of the oil supply inlet 331, and the piping is simple. It is.

Next, the operation of the rotary crusher 310 according to this embodiment will be described.

First, lubricating oil is supplied from the oil supply inlet 331 to both the first bearing portion 341 and the second bearing portion 342. In the present embodiment, since both the lubricating oil of the first bearing portion 341 and the lubricating oil of the second bearing portion 342 are supplied from the oil supply inlet 331 that opens to the bottom of the lower frame assembly 313, the bearing portions 341 and 342 are provided. The amount of oil distribution to the is stable, and the amount of oil supply can be controlled so that a healthy oil film is maintained in the first bearing portion 341 and the second bearing portion 342.

Further, in the present embodiment, the flow rate of the lubricating oil supplied from the oil supply inlet 331 to the first bearing portion 341 and the oil supply inlet 331 to the inner peripheral surface of the inner cylinder bush portion 314a and the outer peripheral surface of the sleeve portion 314c. 2 Since the longitudinal groove portions 351 and 352 for controlling the flow rate of the lubricating oil supplied to the bearing portion 342 are provided, a healthy oil film is maintained in the first bearing portion 341 and the second bearing portion 342. The amount of oil supply can be easily controlled.

Next, rotational power is transmitted from the rotational power transmission system 320 to the flange portion 314b of the eccentric sleeve assembly 314, and the eccentric sleeve assembly 314 is rotated about the rotational axis of the outer cylinder bush portion 313a. Along with the rotation of the eccentric sleeve assembly 314, the main shaft assembly 315 fitted to the inner cylinder bush portion 314a is precessed about the bearing 323 as a fulcrum. The mantle 317 fixed to the main shaft assembly 315 is precessed with respect to the cone cave 312 in accordance with the precession of the main shaft assembly 315, and the gap between the mantle 317 and the cone cave 312 is changed widely with each rotation. .

Next, an object to be crushed, such as a rough stone, is fed from the upper hopper 325 of the upper frame assembly 311. The input crushed material falls into a crushing chamber 318 formed between the mantle 317 and the corn cave 312 and is captured between the mantle 317 and the corn cave 312. When the mantle 317 is rotated and the gap between the mantle 317 and the corn cave 312 is narrowed, the object to be crushed is crushed.

Thereafter, when the gap between the mantle 317 and the corn cave 312 widens, the object to be crushed falls in the crushing chamber 318 to a portion where the gap between the mantle 317 and the corn cave 312 becomes wider, and the mantle 317 and the corn cave 312. When the gap between is narrowed again, it is further crushed. The material to be crushed gradually becomes fine by repeating crushing and dropping, becomes a product of a predetermined particle size, falls to the floor through the gap between the mantle 317 and the corn cave 312, and is discharged out of the machine from the floor opening. Is done.

During operation of the rotary crusher 310, a sufficient oil supply amount is controlled so that a healthy oil film is maintained in the first bearing portion 341 and the second bearing portion 342, so that the bearing portion 341, 342 can be prevented from being damaged.

According to the present embodiment as described above, since the flange portion 314b of the eccentric sleeve assembly 314 extends to the upper portion of the sleeve portion 314c, the eccentric sleeve assembly 314 can be pulled upward from the lower frame assembly 313. When the bearing portions 341 and 342 and the gears 321a and 321b are damaged, the eccentric sleeve assembly 314 can be pulled upward to perform maintenance work on the bearing portions 341 and 342 and the gears 321a and 321b. . Therefore, it is not necessary to disassemble the hydraulic cylinder assembly arranged below the lower frame assembly 313, and there is no need for dangerous work performed by an operator under the suspended load, which is superior to the lower open maintenance type. Maintainability.

Further, according to the present embodiment, both the lubricating oil of the first bearing portion 341 and the lubricating oil of the second bearing portion 342 are supplied from the oil supply inlet 331 that opens at the bottom of the lower frame assembly 313. The oil distribution amount to the parts 341 and 342 is stable, and the oil supply amount can be controlled so that a healthy oil film is maintained in the first bearing part 341 and the second bearing part 342. This can prevent the bearing portions 341 and 342 from being damaged due to seizure or the like.

In addition, according to the present embodiment, since both the first bearing portion 341 and the second bearing portion 342 are supplied from one place of the oil supply inlet 331, a piping material for supplying lubricating oil (not shown). Need only be connected to one location of the oil supply inlet 331, and the piping is simple.

Further, according to the present embodiment, the flow rate of the lubricating oil supplied from the oil supply inlet 331 to the first bearing portion 341 and the oil supply inlet 331 on the inner peripheral surface of the inner cylinder bush portion 314a and the outer peripheral surface of the sleeve portion 314c. Since the vertical groove portions 351 and 352 for controlling the flow rate of the lubricating oil supplied to the second bearing portion 342 are provided, the cross-sectional areas of the vertical groove portions 351 and 352 exposed to the bearing portions 341 and 342 are By appropriately adjusting the number, the oil supply amount can be easily controlled so that a healthy oil film is maintained in each of the bearing portions 341 and 342.

In the present embodiment, the longitudinal groove portions 351 and 352 are provided on both the inner peripheral surface of the inner cylinder bush portion 314a and the outer peripheral surface of the sleeve portion 314c. It may be provided only on either the inner peripheral surface of the portion 314a or the outer peripheral surface of the sleeve portion 314c. Moreover, the vertical groove part 352 may be provided in the internal peripheral surface of the outer cylinder bush part 315a.

In the example shown in FIG. 10, the rotary crusher 310 is a so-called hydraulic cone crusher, but is not limited to this. For example, the oil supply structure 330 according to the present embodiment can also be applied to a mechanical (Simons) cone crusher.

It is possible to add various changes to the above-described embodiment. Hereinafter, modified examples will be described with reference to the drawings. In the following description and the drawings used in the following description, the same reference numerals as those used for the corresponding parts in the above embodiment are used for the parts that can be configured in the same manner as the above embodiment. The duplicated explanation is omitted. In addition, when it is clear that the operational effects obtained in the above-described embodiment can be obtained in the modified example, the description thereof may be omitted.

FIG. 13 is a schematic view showing a modified example of the oil supply structure 330.

In the oil supply structure 330 shown in FIG. 13, between the lower end portion of the sleeve portion 314 c and the bottom portion of the lower frame assembly 313, the flow rate of the lubricating oil supplied from the oil supply inlet 331 to the first bearing portion 341, and the oil supply inlet 331 A partition plate 353 for controlling the flow rate of the lubricating oil supplied to the second bearing portion 342 is installed.

In the illustrated example, the partition plate 353 has a cylindrical shape and is fixed to the bottom of the lower frame assembly 313 so as to surround the annular space 337. A gap of a predetermined size is formed between the upper end portion of the partition plate 353 and the lower end portion of the sleeve portion 314c. Since the flange portion 314b of the eccentric sleeve assembly 314 is supported from below by the thrust bearing 319, the sleeve portion 314c of the eccentric sleeve assembly 314 is positioned at a certain height position, whereby the upper end portion of the partition plate 350 and the sleeve A gap between the lower end portion of the portion 314c is maintained at a constant interval. The lubricating oil of the second bearing portion 342 supplied from the oil supply inlet 331 passes through the gap between the upper end portion of the partition plate 353 and the lower end portion of the sleeve portion 314c, and then flows into the second bearing portion 342. It has become.

According to the aspect shown in FIG. 13, the lubrication supplied from the oil supply inlet 331 to the first bearing portion 341 is adjusted by adjusting the size of the gap between the upper end portion of the partition plate 353 and the lower end portion of the sleeve portion 314 c. It is possible to easily control the flow rate of the oil and the flow rate of the lubricating oil supplied from the oil supply inlet 331 to the second bearing portion 342.

Note that the disclosed invention is not limited to the individual embodiments described above. Each embodiment can be appropriately combined as long as the processing contents do not contradict each other.

DESCRIPTION OF SYMBOLS 10 Rotating type crusher 11 Upper frame assembly 12 Cone cave 13 Lower frame assembly 13a Outer cylinder bush part 13b Wear plate 13c Step washer 14 Eccentric sleeve assembly 14a Inner cylinder bush part 14b Flange part 15 Spindle assembly 15a Spindle step 17 Mantle 18 Crushing chamber 19 Thrust bearing 20 Rotational power transmission system 21a Bevel gear 21b Bevel pinion 22 Horizontal shaft 23 Bearing 25 Hopper 30 Oil supply structure 31 First oil inlet 32 Second oil inlet 33 Thrust seal 34 Thrust seal mounting frame 35 Step portion 36 Through hole 37 Annular space 38 annular space 39 oil supply outlet 40 gear space 41 first bearing portion 42 second bearing portion 210 rotative crusher 211 upper frame assembly 212 cone cave 213 lower frame assembly 213a outer cylinder bush portion 213 Wear plate 213c Step washer 214 Eccentric sleeve assembly 214a Inner cylinder bush portion 214b Flange portion 214c Sleeve portion 215 Main shaft assembly 215a Main shaft step 217 Mantle 218 Crushing chamber 219 Thrust bearing 220 Rotational power transmission system 221a Bevel gear 221b Bevel pinion 222 Horizontal shaft 223 Bearing 225 Hopper 230 Oiling structure 231 First oiling inlet 232 Second oiling inlet 233 Clearance 234 Seal forming portion 235 Partition plate 236 Through hole 237 Annular space 238 Annular space 239 Oiling outlet 240 Gear housing space 241 First bearing portion 242 Second bearing portion 250 Oil sump part 310 Rotating crusher 311 Upper frame assembly 312 Cone cable 313 Lower frame assembly 313a Outer cylinder bush part 313b Wear plate 313c Step Push washer 314 Eccentric sleeve assembly 314a Inner cylinder bush portion 314b Flange portion 314c Sleeve portion 315 Main shaft assembly 315a Main shaft step 317 Mantle 318 Crushing chamber 319 Thrust bearing 320 Rotational power transmission system 321a Bevel gear 321b Bevel pinion 322 Horizontal 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 housing space 341 First bearing portion 342 Second bearing portion 351 Vertical groove portion 352 Vertical groove portion 353 Partition plate

Claims (15)

1. A lower frame assembly having an outer cylinder bush portion, an eccentric sleeve assembly having an inner cylinder bush portion fitted into the outer cylinder bush portion and rotated, and a flange portion fixed to the upper portion of the inner cylinder bush portion; A spindle assembly that holds a mantle that is rotated by being fitted to the inner cylinder bush portion, and a rotational power transmission system that transmits rotational power to the flange portion, and between the rotating mantle and the cone cable In a rotary crusher for crushing an object to be crushed, a first bearing part between the main shaft assembly and the inner cylinder bush part and a second bearing part between the inner cylinder bush part and the outer cylinder bush part Each of which has a lubricating structure for supplying lubricating oil,
   An annular thrust seal that is installed inside the lower frame assembly and supports the lower end of the inner cylinder bushing from below;
   A first refueling inlet that opens at a bottom of the lower frame assembly to refuel the first bearing portion;
   A second oil supply inlet that opens on an inner peripheral surface of the outer cylinder bush portion so as to supply oil to the second bearing portion;
   Have
   The thrust seal includes a flow path of lubricating oil supplied from the first oil supply inlet to the first bearing portion, and a flow path of lubricating oil supplied from the second oil supply inlet to the second bearing portion. Oiling structure characterized by being separated.
2. The oil supply structure according to claim 1, wherein a thrust bearing for supporting the flange portion from below is provided at an upper end portion of the outer cylinder bush portion.
3. The oil supply structure according to claim 1, wherein a thrust bearing that supports the flange portion from below is not provided at an upper end portion of the outer cylinder bush portion.
4. The step portion is provided on the outer diameter side of the thrust seal, and the inner peripheral surface of the step portion surrounds the outer peripheral surface of the lower end portion of the inner cylinder bush portion. 4. The oil supply structure according to any one of 1 to 3.
5. A lower frame assembly having an outer cylinder bush part;
   An eccentric sleeve assembly having an inner cylinder bush part that is fitted and rotated in the outer cylinder bush part and a flange part fixed to the upper part of the inner cylinder bush part;
   A spindle assembly that holds a mantle that is fitted to the inner cylinder bushing and rotated,
   A rotational power transmission system for transmitting rotational power to the flange portion;
   With
   A rotary crusher that crushes objects to be crushed between a rotating mantle and a corn cave,
   And an oil supply structure for supplying lubricating oil to the first bearing portion between the main shaft assembly and the inner cylinder bush portion and the second bearing portion between the inner cylinder bush portion and the outer cylinder bush portion, respectively. Prepared,
   The oil supply structure is
   An annular thrust seal that is installed inside the lower frame assembly and supports the lower end of the inner cylinder bushing from below;
   A first refueling inlet that opens at a bottom of the lower frame assembly to refuel the first bearing portion;
   A second oil supply inlet that opens on an inner peripheral surface of the outer cylinder bush portion so as to supply oil to the second bearing portion;
   Have
   The thrust seal includes a flow path of lubricating oil supplied from the first oil supply inlet to the first bearing portion, and a flow path of lubricating oil supplied from the second oil supply inlet to the second bearing portion. A rotary crusher characterized by separation.
6. An eccentric sleeve having a lower frame assembly having an outer cylinder bush part, a sleeve part holding the inner cylinder bush part rotated by being fitted to the outer cylinder bush part, and a flange part extending above the sleeve part An assembly, a main shaft assembly that holds a mantle that is rotated by being fitted to the inner cylinder bush portion, and a rotational power transmission system that transmits rotational power to the flange portion. In a rotary crushing machine for crushing an object to be crushed, a first bearing part between the spindle assembly and the inner cylinder bush part and a second bearing between the sleeve part and the outer cylinder bush part An oil supply structure for supplying lubricating oil to each part,
   A first refueling inlet that opens at a bottom of the lower frame assembly to refuel the first bearing portion;
   A second oil supply inlet opening in a circumferential surface of the outer cylinder bush portion so as to supply oil to the second bearing portion;
   An annular seal forming portion provided inside the lower frame assembly and having a non-contact surface facing the end surface of the lower end portion of the sleeve portion;
   Have
   The gap between the non-contact surface of the seal forming portion and the end surface of the lower end portion of the sleeve portion is sealed with the lubricating oil, and a partition plate is disposed on the outer periphery of the annular seal forming portion. An oil supply structure in which an annular oil reservoir is formed between the plate and the outer peripheral surface of the lower end of the sleeve portion.
7. The oil supply structure according to claim 6, wherein the oil reservoir is formed at a position higher than the gap.
8. A lower frame assembly having an outer cylinder bush part;
   An eccentric sleeve assembly having a sleeve portion that holds an inner cylinder bush portion that is rotated by being fitted to the outer cylinder bush portion, and a flange portion that is fixed to an upper portion of the inner cylinder bush portion;
   A spindle assembly that holds a mantle that is fitted to the inner cylinder bushing and rotated,
   A rotational power transmission system for transmitting rotational power to the flange portion;
   With
   A rotary crusher that crushes objects to be crushed between a rotating mantle and a corn cave,
   An oil supply structure for supplying lubricating oil to the first bearing part between the main shaft assembly and the inner cylinder bush part and the second bearing part between the sleeve part and the outer cylinder bush part, respectively.
   The oil supply structure is
   A first refueling inlet that opens at a bottom of the lower frame assembly to refuel the first bearing portion;
   A second oil supply inlet opening in a circumferential surface of the outer cylinder bush portion so as to supply oil to the second bearing portion;
   An annular seal forming portion provided inside the lower frame assembly and having a non-contact surface facing the end surface of the lower end portion of the sleeve portion;
   Have
   The gap between the non-contact surface of the seal forming portion and the end surface of the lower end portion of the sleeve portion is sealed with the lubricating oil, and a partition plate is disposed on the outer periphery of the annular seal forming portion. A rotary crusher characterized in that an annular oil reservoir is formed between the plate and the outer peripheral surface of the lower end of the sleeve.
9. An eccentric sleeve having a lower frame assembly having an outer cylinder bush part, a sleeve part holding the inner cylinder bush part rotated by being fitted to the outer cylinder bush part, and a flange part extending above the sleeve part An assembly, a main shaft assembly that holds a mantle that is rotated by being fitted to the inner cylinder bush portion, and a rotational power transmission system that transmits rotational power to the flange portion. In a rotary crushing machine for crushing an object to be crushed, a first bearing part between the spindle assembly and the inner cylinder bush part and a second bearing between the sleeve part and the outer cylinder bush part An oil supply method for supplying lubricating oil to each part,
   Both the lubricating oil of the said 1st bearing part and the lubricating oil of the said 2nd bearing part are supplied from the oil supply inlet opened to the bottom part of the said lower frame assembly, The oil supply method characterized by the above-mentioned.
10. A longitudinal groove is provided in the inner cylinder bush part, the sleeve part or the outer cylinder bush part, and the flow rate of lubricating oil supplied from the oil supply inlet to the first bearing part, and the second bearing part from the oil supply inlet. The oil supply method according to claim 9, wherein the flow rate of the lubricating oil supplied to the oil is controlled.
11. A partition plate is provided between a lower end portion of the sleeve portion and a bottom portion of the lower frame assembly, and a flow rate of lubricating oil supplied from the oil supply inlet to the first bearing portion, and from the oil supply inlet to the second bearing. The oil supply method according to claim 9 or 10, wherein the flow rate of the lubricating oil supplied to the section is controlled.
12. An eccentric sleeve having a lower frame assembly having an outer cylinder bush part, a sleeve part holding the inner cylinder bush part rotated by being fitted to the outer cylinder bush part, and a flange part extending above the sleeve part An assembly, a main shaft assembly that holds a mantle that is rotated by being fitted to the inner cylinder bush portion, and a rotational power transmission system that transmits rotational power to the flange portion. In a rotary crushing machine for crushing an object to be crushed, a first bearing part between the spindle assembly and the inner cylinder bush part and a second bearing between the sleeve part and the outer cylinder bush part An oil supply structure for supplying lubricating oil to each part,
    A refueling inlet opening at the bottom of the lower frame assembly;
    The oil supply inlet is configured to supply both the lubricating oil of the first bearing portion and the lubricating oil of the second bearing portion.
13. The inner cylinder bush part, the sleeve part or the outer cylinder bush part is supplied with the flow rate of lubricating oil supplied from the oil supply inlet to the first bearing part and supplied from the oil supply inlet to the second bearing part. The oil supply structure according to claim 12, wherein a longitudinal groove portion for controlling a flow rate of the lubricating oil is provided.
14. Between the lower end portion of the sleeve portion and the bottom portion of the lower frame assembly, the flow rate of the lubricating oil supplied from the oil supply inlet to the first bearing portion and the oil supply inlet supplied to the second bearing portion. The oil supply structure according to claim 12 or 13, wherein a partition plate for controlling a flow rate of the lubricating oil is provided.
15. A lower frame assembly having an outer cylinder bush part;
    An eccentric sleeve assembly having a sleeve portion that holds the inner cylinder bush portion that is rotated by being fitted to the outer cylinder bush portion, and a flange portion that extends above the sleeve portion;
    A spindle assembly that holds a mantle that is fitted to the inner cylinder bushing and rotated,
    A rotational power transmission system for transmitting rotational power to the flange portion;
    With
    A rotary crusher that crushes objects to be crushed between a rotating mantle and a corn cave,
    An oil supply structure for supplying lubricating oil to the first bearing part between the main shaft assembly and the inner cylinder bush part and the second bearing part between the sleeve part and the outer cylinder bush part, respectively.
    The oil supply structure is
    A refueling inlet opening at the bottom of the lower frame assembly;
    The oil supply inlet is configured to supply both the lubricating oil of the first bearing portion and the lubricating oil of the second bearing portion.

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