阅读说明：本技术 用于破碎设备的螺旋齿轮箱 (Helical gearbox for a crushing plant ) 是由 D.斯温森 M.丹尼尔 M.O.林德奎斯特 N.L.米勒 于 2018-11-16 设计创作，主要内容包括：一种用于破碎机(1)的新颖齿轮箱(200)的特征在于,凹部(210)包括具有高点(212A)和低点(212B)的螺旋非均匀深度凹部。齿轮箱(200)的特征还在于,凹部(210)的底板(211)不是延伸到锐角过渡(112)且然后延伸到正交侧壁(126),而是与邻近低点(212B)的小齿轮间隙底板(222)相交或融合。螺旋非均匀深度凹部(210)优选地配置成用于提高齿轮箱(200)的强度和/或配置成用于减轻齿轮箱(200)内的油起泡,但不限于此。(A novel gearbox (200) for a crusher (1) is characterized in that the recess (210) comprises a helical non-uniform depth recess having a high point (212A) and a low point (212B). The gearbox (200) is further characterized in that the floor (211) of the recess (210) does not extend to the acute angle transition (112) and then to the orthogonal side wall (126), but intersects or merges with the pinion clearance floor (222) adjacent the low point (212B). The helical non-uniform depth recess (210) is preferably configured for increasing the strength of the gearbox (200) and/or configured for mitigating oil foaming within the gearbox (200), but is not limited thereto.)

1. A gearbox (200) for a crusher (1) substantially as shown and described.

2. A gearbox (200) for a crusher (1), comprising:

a body (206);

a recess (210) configured to be positioned adjacent to a driven gear (15) of an eccentric (4), wherein the recess (210) comprises a bottom plate (211); and

a pinion clearance floor (222);

the method is characterized in that:

the recess (210) comprises a helical non-uniform depth recess having a high point (212A) and a low point (212B); and is

Rather than extending to the acute angle transition (112) and then to the orthogonal sidewall (126), the floor (211) of the recess (210) intersects or merges with the pinion clearance floor (222) adjacent the low point (212B);

wherein the helical non-uniform depth recess (210) is configured to increase the strength of the gearbox (200) or mitigate oil blistering within the gearbox (200).

3. The gearbox (200) for a crusher (1) according to claim 2, wherein the angular distance theta (θ) representing the angular span of the recess (210) about the centerline axis (206) of the gearbox (200) and extending between a low point (212B) of the recess (210) and a high point (212A) of the recess (210) is greater than 45 degrees but less than 335 degrees.

4. The gearbox (200) for a crusher (1) according to claim 2 or 3, wherein the angular distance theta (θ) representing the angular span of the recess (210) around the centre line axis (206) of the gearbox (200) and extending between the low point (212B) of the recess (210) and the high point (212A) of the recess (210) is greater than 90 degrees but less than 270 degrees.

5. The gearbox (200) for a crusher (1) according to any one of claims 2-4, wherein the angular distance theta (θ) representing the angular span of the recess (210) about the centreline axis (206) of the gearbox (200) and extending between a low point (212B) of the recess (210) and a high point (212A) of the recess (210) is greater than 135 degrees but less than 225 degrees.

6. The gearbox (200) for a crusher (1) according to any one of claims 2-5, wherein the angular distance theta (θ) representing the angular span of the recess (210) around the centreline axis (206) of the gearbox (200) and extending between a low point (212B) of the recess (210) and a high point (212A) of the recess (210) is 180 degrees.

7. A crusher (1) comprising:

a cone (20) supported by the shaft (16) and forming a first crushing surface;

a mantle (19) positioned adjacent to the cone (20) and forming a second crushing surface;

the shaft (16) is arranged within an eccentric (4) operatively coupled to the driven gear (15) and within the gearbox (100);

a gear box (200) is provided with: a body (206); a recess (210) configured to be positioned adjacent to the driven gear (15) of the eccentric (4); and a pinion clearance floor (222); wherein the recess (210) comprises a floor (211);

characterized in that the crusher (1) comprises a gearbox (200) according to any of the preceding claims 2-6.

8. A method of installing a gearbox (100) into a crusher (1), comprising:

removing a gearbox (100) with a part-annular recess (110) from the crusher (1);

providing a replacement gearbox (200), the replacement gearbox (200) having: a body (206); a recess (210) configured to be positioned adjacent to the driven gear (15) of the eccentric (4); and a pinion clearance floor (222); wherein the recess (210) comprises a floor (211); and

installing a replacement gearbox (200) into the crusher (1);

characterized in that the replacement gearbox (200) comprises a gearbox (200) according to any of the preceding claims 2-6.

Technical Field

The present disclosure relates generally to the field of crushing and to industrial crushing equipment suitable for use in the mining and aggregate industries.

In particular, a novel apparatus for facilitating gear lubrication in a crusher while minimizing the potential for oil bubbling is disclosed.

More particularly, an improved helical recess design for a gearbox component of a cone crusher is disclosed. The helical recess design is intended to reduce stress concentrations in the casting, mitigate oil bubbling and improve the overall robustness and effectiveness of the gearbox.

Background

Conventional cone crushers 1 and related crushing devices typically employ an externally threaded bowl 3, a complementary internally threaded adjusting ring 9 around a lower portion of the bowl 3, and a complementary internally threaded clamping ring 2 located above the adjusting ring 9 also around the bowl 3.

During normal crushing operation, the clamping ring 2 remains fixed to the adjusting ring 9 and stationary relative thereto, with the external thread of the bowl 3 fixed therebetween, so that the bowl 3 also remains stationary relative to the adjusting ring 9 and the clamping ring 2.

To remove the bowl 3 from the crushing device 1 for maintenance, either the bowl 3 is installed into the crushing device 1 or the gap size between the mantle 19 and the cone 20 is adjusted in situ (which in turn sets the material crushing size), the bowl 3 is rotated via a peripheral drive motor 13, which peripheral drive motor 13 turns a ring gear 11 attached to the bowl 3 via a web 10. The bowl 3 is rotated while the clamp ring 2 and the adjustment ring 9 remain in a vertically stationary configuration, thus causing simultaneous linear vertical and rotational movement/displacement of the bowl 3. The displacement of the bowl 3 sets the crushing gap distance between the mantle 19 and the cone 20 and thus the size of the crushed product.

As shown in fig. 1, the cone crusher 1 may have a clamping ring 2 connected to the adjusting ring 9 via a fastening device 14. The inner diameter portions of clamp ring 2 and adjustment ring 9 may each include female threads, which may include exaggerated flanks (e.g., buttress threads), but are not so limited. The threads of each component may be similar or identical and they may be complementary to the external threads of the bowl 3, but are not limited thereto.

The outer diameter portion of the bowl 3 may include male threads (i.e., the bowl 3 may be externally threaded). As shown in fig. 1, the external threads of the bowl 3 may correspond to threads provided on each of the adjusting ring 9 and the clamping ring 2. The bowl 3 may be provided with a web 10 or other flange-like member which serves as a connection to the outer ring gear 11. Alternatively, the ring gear 11 may be connected directly to the bowl 3.

A drive motor 13 provided with a pinion gear 12 may cooperatively engage the ring gear 11 to drive/rotate the ring gear 11 and rotate the bowl 3. By means of the drive motor 13 rotating both the pinion 12 and the ring gear 11, the web 10 and the bowl 3 rotate together in common relative to the crushing device 1, the adjusting ring 9 and the clamping ring 2. As the bowl 3 rotates, the surfaces between the threads of the bowl 3 and the threads of the clamping ring 2 move relative to each other.

The ring gear 11 may include external teeth that mate with complementary teeth on the pinion gear 12. It is contemplated that other drive mechanisms (e.g., worm gears, helical gears, spur gears, and the like) may be equally employed between the drive motor 13 and the bowl 3, but are not so limited.

To facilitate mounting of the bowl 3 on the crushing device 1, either the bowl 3 is removed from the crushing device 1, or the vertical movement of the bowl 3 relative to the crushing device 1 (i.e. in order to set or adjust the crushing size or to open/close the crushing gap between the mantle 19 and the cone 20), the fastening means 14 connecting the clamping ring 2 to the adjusting ring 9 may be loosened to make it easier for the drive motor 13 to rotate the bowl 3 via the pinion 12 and the ring gear 11. In order to set a fixed crushing gap size for the crushing operation, the clamping ring 2 may be fixed to the adjusting ring 9 via re-engagement of the fastening means 14.

As shown, the fastening means 14 may comprise a fastener passing through the clamping ring 2 and threadingly engaging the adjustment ring 9. By securing the clamping ring 2 to the adjusting ring 9 by means of the fastening means 14, the bowl 3 is prevented from rotating and vertical movement relative to the clamping ring 2 and the adjacent adjusting ring 9.

Traditionally, industrial crushers such as the cone crusher 1 also have a gearbox 100 comprising a main body 106 and a part annular recess 110 of uniform depth. The part-annular recess 110 generally comprises a non-helical part-annular floor (which may be planar, frustoconical or tapered radially inwardly as shown). The conventional gearbox 100 is typically configured to receive an annular driven gear 15 (e.g., which is typically provided as a helical or bevel gear).

Conventionally, the large cutout 120 extends downwardly from a portion of the partial annular recess 110 at a steep right angle or similar angle, thereby forming an acute angle transition 112 between the generally horizontally oriented partial annular recess floor 111 and the substantially vertical wall 126 of the large cutout 120. The large cutout 120 serves to provide sufficient clearance space for the drive pinion 18 to be seated and rotate unimpeded — the purpose of the drive pinion 18 is to move the driven gear 15. The large cutout 120 is generally configured as a substantially rectangular cavity, as shown in fig. 2-5.

A drive motor (not shown or labeled) rotates a drive shaft 17 provided with a drive pinion 18 at its distal end. The drive pinion 18 in turn drives/rotates a driven gear 15, which may be integrally provided or attached to an eccentric 4 having a central opening. The shaft 16 may pass through the eccentric 4, the driven gear 15 and the body 106 of the gearbox 100. The central opening 128 in the gearbox 100 may be tapered and act as a thrust bearing for supporting the shaft 116, as shown in fig. 1, 4 and 5.

Generally, the sharp transition 112 between the partial annular recess 110 and the rectangular cavity 120 may cause a significant increase in stress concentration during operation and may be a common failure mode of the gearbox 100 (e.g., via cracking). The thin wall portions adjacent the acute transition 112 may be present from castings formed by the present methods and designs; and over time even ductile gearbox 100 castings may begin to see signs of hairline cracks and stress fracture formation from near the sharp transition 112.

Another problem with this acute transition or corner 112 is that the oil lubricating the gear pairs 15, 18 becomes turbulent as it flows from the floor 111 of the partial annular recess 110, through the acute transition 112, past the vertical sidewall 126. Such an "overflow" or "waterfall" may lead to undesirable foaming in the power train of the crusher 1.

Disclosure of Invention

It is therefore an object of the present invention to overcome the above mentioned drawbacks associated with the prior art gear boxes of crushers.

It is another object of some non-limiting embodiments of the present invention to extend the use and/or service life of a gearbox, but is not so limited.

It is a further object of some non-limiting embodiments of the present invention to improve the hydrodynamic performance of gearboxes and reduce oil foaming during continuous operation, but not limited thereto.

These and other objects of the present invention will be apparent from the drawings and description herein. While it is believed that each of the objects of the invention is achieved by at least one embodiment of the invention, there is not necessarily any one embodiment of the invention that achieves all of the objects of the invention.

A gearbox 200 for a crusher 1 is disclosed. According to some preferred embodiments, the gearbox 200 may include a body 206, a recess 210, and a pinion clearance bottom plate 222. The recess 210 is preferably configured to be positioned adjacent the driven gear 15 of the eccentric 4. The recess 210 also includes a floor 211. The gearbox 200 is characterized in that its recess 210 comprises a helical non-uniform depth recess having a high point 212A and a low point 212B (and a distance along the Z-axis or centerline axis 206 of the gearbox 200 separating the high point 212A from the low point 212B). Thus, rather than extending to the acute angle transition 112 and then to the orthogonal side wall 126 as in prior art designs, the helical floor 211 of the improved helical recess 210 intersects or merges with the pinion clearance floor 222 adjacent the low point 212B (e.g., without the vertical side wall 126 and/or without the acute angle transition 112). The helical non-uniform depth recess 210 may be configured to improve the strength of the gearbox 200 by eliminating the sharp transitions 112 and stress risers associated with using right angle thin walls in the casting. Alternatively or in addition, the helical recess 210 may be configured to reduce or mitigate oil foaming within the gearbox 200.

According to some embodiments, the angular distance theta (θ), representing the angular span of the recess 210 about the centerline axis 206 of the gearbox 200 and extending between the low point 212B of the recess 210 and the high point 212A of the recess 210, may be greater than 45 degrees but less than 335 degrees, but is not limited thereto. In other words, the helical/spiral path of the recess 210 is less than one revolution about the axis 206.

For example, according to some embodiments, the angular distance theta (θ) representing the angular span of the recess 210 about the centerline axis 206 of the gearbox 200 and extending between the low point 212B of the recess 210 and the high point 212A of the recess 210 may be greater than 90 degrees but less than 270 degrees, but is not limited thereto.

As another example, in some embodiments, the angular distance theta (θ) representing the angular span of the recess 210 about the centerline axis 206 of the gearbox 200 and extending between the low point 212B of the recess 210 and the high point 212A of the recess 210 may be greater than 135 degrees but less than 225 degrees, but is not limited thereto.

As yet another example, in some embodiments, and as shown in exemplary and non-limiting FIGS. 6-9, the angular distance theta (θ) representing the angular span of the recess 210 about the centerline axis 206 of the gearbox 200 and extending between the low point 212B of the recess 210 and the high point 212A of the recess 210 may be about 180 degrees, but is not limited thereto.

A crusher 1 is also disclosed. The crusher 1 may comprise a cone 20 supported by the shaft 16, the cone 20 forming a first crushing surface. The crusher 1 may further comprise a mantle 19 positioned adjacent to the cone 20, the mantle 19 forming a second crushing surface. The shaft 16 may be arranged inside the eccentric 4 and supported by the gearbox. The eccentric 4 may be operably coupled to a driven gear 15. The driven gear 15 may be located within or adjacent to the recess 210 of the gearbox 100.

The gear box 200 may have: a main body 206; a recess 210 configured to be positioned adjacent to the driven gear 15 associated with the eccentric 4; and a pinion clearance floor 222. Further, the recess may include a floor 211, which may be configured to convey oil.

The crusher 1 is characterized in that the floor 211 of the recess 210 in the gearbox 200 is preferably helical in nature (i.e. in the form of a spiral, a coil, a helix, etc.), as shown in fig. 6-9. In other words, the gearbox 200 may be characterized in that it includes a helical non-uniform depth recess having a high point 212A and a low point 212B that does not exist in the same plane along the Z-axis or centerline axis 106 as in the prior art design of FIGS. 2-5. A vertical distance along the Z-axis or a distance along the centerline axis 206 separates the high point 212A from the low point 212B. Thus, rather than extending to acute angle transition 112 and then to orthogonal side wall 126, floor 211 of recess 210 according to the present embodiment intersects or merges with pinion clearance floor 222 adjacent low point 212B.

The helical non-uniform depth recess 210 may be configured to increase the strength of the gearbox 200. Alternatively or in addition, the recess 210 may be configured to reduce or mitigate oil bubbling within the gearbox 200.

According to some embodiments, the gearbox 200 with the helical non-uniform depth recess 210 described above may be installed into the crusher 1. The steps may include: providing a replacement gearbox 200 as described above and having: a main body 206; a recess 210 configured to be positioned adjacent to the driven gear 15 of the eccentric 4; pinion clearance bottom plate 222; and a bottom plate 211 provided to the recess 210. The steps may also include removing the gearbox 100 with the part annular recess 110 from the crusher 1 and installing a replacement gearbox 200 into the crusher 1, but are not limited thereto.

Drawings

To supplement the description made and to help a better understanding of the characteristics of the invention, in the present description there is attached a set of drawings showing, as an integral part thereof, a new and novel gearbox device for improving a crusher, in which the following description is given with illustrative and non-limiting characteristics. It should be understood that the same reference numerals (if used) may be used in the drawings to identify the same elements.

Fig. 1 shows a crusher 1 according to the prior art, which may benefit from embodiments of the present invention.

Fig. 2 shows an enlarged partial cross-sectional view of a conventional gearbox 100 found in the crusher 1 shown in fig. 1.

Fig. 3 shows a side view of the gearbox 100 shown in fig. 1 and 2.

FIG. 4 illustrates a side cross-sectional view of the gearbox 100 shown in FIG. 3.

Fig. 5 is an isometric cross-sectional view of the gearbox 100 shown in fig. 1-4.

FIG. 6 illustrates an enlarged partial cross-sectional view of a gearbox 200 according to some exemplary non-limiting embodiments, which may be used to retrofit the crusher shown in FIG. 1.

FIG. 7 illustrates a side view of the gearbox 200 shown in FIG. 6.

FIG. 8 illustrates a side cross-sectional view of the gearbox 200 shown in FIG. 7.

Fig. 9 is an isometric cross-sectional view of the gearbox 200 shown in fig. 6-8.

Fig. 10 is a schematic diagram illustrating a possible exemplary range of angular spans for the helical recess 210, according to some non-limiting embodiments.

FIG. 11 presents a method for installing a gearbox 200 according to some embodiments.

Hereinafter, the present invention will be described in more detail with reference to the accompanying drawings in conjunction with exemplary embodiments.

Detailed Description

Although the present invention has been described herein using an exemplary embodiment of a gearbox 200 for a crusher 1 and a method of mounting the same, it is to be understood that many variations and modifications will be apparent to those of ordinary skill in the art in light of the teachings provided herein.

The detailed description shown and described in the text and drawings should not be construed as limiting in scope; rather, all provided embodiments should be considered exemplary in nature. Accordingly, the invention is not to be restricted except in light of the attached claims.

The disclosure of each patent, patent application, and publication cited, listed, named, or mentioned herein is hereby incorporated by reference in its entirety for any and all purposes as if fully set forth herein.

Although the subject matter has been disclosed with reference to specific embodiments, it is apparent that other embodiments and modifications can be devised by others skilled in the art without departing from the true spirit and scope of the subject matter described herein. The appended claims may encompass some, but not all, such embodiments and equivalent variations.

The described embodiments are to be considered in all respects only as illustrative and not restrictive. The scope of the invention is, therefore, indicated and limited only by the appended claims rather than by the foregoing description. All embodiments that come within the meaning and range of equivalency of the claims are to be embraced within their scope.

The inventors have recognized a novel and heretofore unappreciated design of a gearbox 200 for a crushing device 1-particularly those for a cone crusher drive train, but not limited thereto.

Turning now to prior art fig. 1, a crusher 1 (e.g., a cone crusher) may include an internally threaded clamp ring 2 and an externally threaded bowl 3 threadedly engaged with the clamp ring 2. The bowl 3 operatively engages a cover 19 forming an upper crushing surface. An internally threaded adjustment ring 9 is also threadedly engaged with the bowl 3. A web 10 may extend from the bowl 3 and connect the bowl 3 to the outer ring gear 11. The outer ring gear 11 may communicate with a pinion gear 12 driven by a peripheral drive motor 13.

Upon powering the peripheral drive motor 13, the pinion gear 12 rotates, thereby rotating the outer ring gear 11, the web 10 and the connected bowl 3. During the rotational movement of the bowl 3, the crushing gap (i.e. the distance between the mantle 19 and the cone 20) can be adjusted, thereby changing the size of the produced crushed product.

A fastening device 14 may be provided between the adjusting ring 9 and the clamping ring 2 to prevent relative movement between the parts 2, 9, 3 of the crusher 1 during operation. The fastening means 14 may be loosened or removed to allow removal or adjustment of the parts 2, 9, 3 of the crusher 1.

On the lower inner part of the crusher 1, a cone 20 forming the lower crushing surface is supported by a shaft 16, which shaft 16 is guided by an eccentric 4 surrounding the shaft 16. The eccentric 4 is coupled to a driven gear 15 (e.g., at a lower portion of the eccentric 4). The driven gear 15 may alternatively be formed integrally with the eccentric 4. A drive shaft 17 configured to be coupled to a drive motor/transmission output (not shown) powers the crusher 1 by rotating a drive pinion 18 thereon. The drive pinion 18 is in contact with the driven gear 15. The driven gear 15 and the drive pinion 18 are typically of the helical or bevel gear type, but are not limited thereto.

A conventional gearbox 100 (such as the gearbox shown in fig. 2-5) may be placed below the eccentric 4 and may support the eccentric 4 and/or serve as a lower support bearing (e.g., thrust bearing) for the shaft 16, but is not so limited. The bearings may allow relative rotational movement between the eccentric 4 and the conventional gearbox 100. The conventional gearbox 100 includes a first drive shaft bearing 102 (e.g., a sleeve, journal, or race), a second drive shaft bearing 103 (e.g., a sleeve, journal, or race), and an opening 124 therebetween to support the drive shaft 17 and provide lubrication or reduce friction between portions of the conventional gearbox 100 and the drive shaft 17.

The body 106 of the conventional gearbox 100 is provided with a partial annular recess 110 of non-helical uniform depth having a partial annular recess floor 111. Points along the partial annular recess floor 111 may be defined as a series of polar coordinates that share a similar radius and fall in substantially the same horizontally oriented plane along the height axis of the crusher or centerline axis 106 of the conventional gearbox 100. In other words, if points along the partial annular recess floor 111 share similar radial positions, they may share similar elevation or "Z-axis" positions in the crusher 1. In other words, in prior gearboxes 100, two separate points on the floor 111 of the recess 110 that are equidistant from the centerline axis 106 would also share a common location along the centerline axis 106, but are not so limited.

There is a junction/interruption in the partial annular recess 110 of non-helical uniform depth, where there is a conventional acute angle transition 112 to a substantially vertical sidewall 126 forming part of the large cutout 120. The macro cutout 120 also includes a floor 122 that provides clearance for the drive pinion 18. The large cutout 120 may at least partially serve as a groove for lubricating oil for driving the pinion gear 18 and the driven gear 15. As shown, the side walls 126 and the floor 111 are generally perpendicular/orthogonal to each other and joined at their intersection by an acute angle transition 112.

A problem with the prior art gearbox 100 design shown in fig. 1-5 is that high stresses within the gearbox 100 may cause cracks along or adjacent to the conventional sharp-angled transition 112, which often includes thin walls of cast iron.

Another problem with the prior art gearbox 100 design shown in fig. 1-5 is that oil contained on the surface of the driven gear 15 falls to the top surface of the partial annular recess 110 and, due to the small gaps therebetween, the oil may be agitated by the teeth of the driven gear 15 as the driven gear 15 rotates. Moreover, the agitated oil may further bubble due to high turbulence as it progresses at the acute angle transition 112 and splashes into the catch basin formed by the macro cutout 120, the side walls 126, and the pinion clearance floor 122.

Turning now to fig. 6-9, an improved gearbox 200 according to some embodiments may similarly include a first drive shaft bearing 202 (e.g., a sleeve, journal, or race) and a second drive shaft bearing 204 (e.g., a sleeve, journal, or race) configured to support the drive shaft 17 and drive pinion 18 thereon. The opening 224 may extend therebetween.

The driven gear 15, with which the pinion 18 engages to rotate the eccentric 4, is configured to rotate freely within a helical recess 210 of substantially non-uniform depth. As shown, the helical recess 210 may include a helical recess floor 211 that merges with a pinion clearance floor 222 that underlies and provides clearance for the drive pinion 18. As shown, spiral recess floor 211 extends from a high point 212A (e.g., at the beginning of spiral recess 210) to a low point 212B (e.g., at the end of spiral recess 210). The helical recess 210 removes the sharp transition 112 and the large vertical wall 126 and instead merges the recess 210 into a large cutout area configured to receive the pinion gear 18.

By means of the inclined bottom plate 211, the oil lubricating the drive pinion 18 and the driven gear 15 can slide down via gravity with little turbulence and re-lubricate the drive pinion 18. Oil may accumulate adjacent the pinion within the groove area formed by the pinion clearance floor 222. Subsequently, as the pinion gear 18 rotates, oil received by the surface of the drive pinion gear 18 may contact the driven gear 15, thereby lubricating the gear pairs and the tooth surfaces therebetween. The floor 211 of the helical recess 210 may thus be configured to reduce foaming of the lubricating oil, as the gearbox 200 replaces the prior art features 110, 111, 112, 126 which allow oil to splash inside the crusher 1 (e.g. onto the conventional acute angle transition 112 between the conventional part annular recess floor 111 and the side wall 126 of the conventional large cut-out 120).

Furthermore, due to the helical design, the overall strength of the gearbox 200 may be increased, and as the recess 210 traverses about the centerline axis 206, the clearance between the accumulated oil and the rotating teeth of the driven gear 15 may be increased due to the gradual increase in spacing between the high point 212A and the low point 212B.

Turning now to FIG. 10, it is to be understood that the helical non-uniform depth recess 210 described herein may begin at a high point 212A and extend to a low point 212B as it traverses around the gearbox 200, but is not so limited. The shortest angular distance between high point 212A and low point 212B may be set to be slightly more or greater than the width of drive pinion 18 in order to configure notch 220 to provide sufficient clearance for rotation of drive pinion 18 while maximizing the circumferential length/span of helical recess 210. By making the spiral recess 210 longer, the slope thereof can become more gentle. By making the helical recess 210 shorter, its slope can become steeper. It should be understood that the upstroke (e.g., relative slope, grade, steepness) of the floor 211 of the spiral recess 210 may be constant as shown, or it may vary at different angular positions about the axis 206. Accordingly, embodiments of the gearbox 200 in which the recess 210 includes a "compound" or "variable pitch" helical geometry are well within the scope of the present disclosure.

The angular distance theta (theta) may represent the angular span of the helical recess 210 of the gearbox 200 according to some embodiments of the present invention. This theta angle may be conceptualized as the circular distance that the helical recess 210 circumferentially spans or travels in its spiral/helical path about the centerline axis 206 of the gearbox 200. Theta angle may alternatively be conceptualized as the circular distance traveled or circumferentially spanned by helical recess 210 about Z-axis or centerline axis 206. As shown, theta angles may be expressed in degrees relative to polar coordinates for the purposes of this disclosure, but are not limited thereto; where zero degrees may represent the intersection between the spiral recess floor 211 and the pinion clearance floor 222.

As shown, the most preferred contemplated embodiments within the scope of the present disclosure may have a theta angle (e.g., absolute theta angle) greater than about 90 degrees but less than about 270 degrees, such as 180 degrees, but are not limited thereto.

In the non-limiting embodiment shown in fig. 6-9, the helical recess 210 is shown extending 180 degrees around the gearbox 200, where theta may be about 180 degrees. This is because the high point 212A of the spiral recess floor 211 is located at a polar angular coordinate comprising 180 degrees, while the low point 212B of the spiral recess floor 211 is located at a polar angular coordinate comprising zero degrees, so that the two points 212A, 212B are polar opposite.

It should be noted that the two points 212A, 212B do not share the same position along the central centerline axis 206 of the gearbox and therefore also have different vertical positions within the crusher 1 along the Z-axis. Thus, the disclosed spiral recess 210 encourages less turbulent downward flow of oil via gravity along the floor 211 surface and into the large chamber sump area defined by the pinion gap floor 222. In this regard, the pinion gear 18 may maintain good lubrication without the negative effects of oil bubbling that are common with conventional gearboxes 100.

FIG. 9 shows that theta may exceed 180 degrees (e.g., about 335 degrees) or be less than 180 degrees in certain preferred embodiments; however, embodiments contemplated within the scope of the present disclosure include theta angles that are not close to 360 degrees. A preferred embodiment of the gearbox 200 may include a theta angle of at least 90 degrees but no greater than 270 degrees. For example, a theta angle that is too small may cause the helical recess 210 to be too steep, thereby reducing the effectiveness of the light reducing oil to bubble.

In some embodiments, a method of installing the gearbox 200 may be performed. In some embodiments, the method may comprise assembling parts of the crusher 1 together with the gearbox 200 described herein to form an improved crusher 1 comprising a gearbox 200 with a helical recess 210.

Turning now to fig. 11, in some embodiments, a method of retrofitting a crusher 1 with a gearbox 200 according to embodiments of the invention described herein may be performed. As shown in the figures, the method may comprise removing an old gearbox 100 having a part-annular recess 110 of non-helical uniform depth from the crusher 1 (e.g., the gearbox 100 as shown and described in prior art fig. 2-5) and then replacing it with a gearbox 200 as described herein (e.g., the gearbox 200 as shown and described in fig. 6-9) to form an improved crusher 1 comprising a gearbox 200 having a helical recess 210.

A contractor or other entity may provide a gearbox 200 as substantially described herein, or may practice any of the methods or method steps described herein, but is not limited to such. Further, a contractor or other entity may provide portions or components of the gearbox 200 as substantially described herein, or may practice one or more of the method steps described herein, but is not limited thereto. The contractor may modify an existing gearbox 100 by welding, machining, additive, fusion casting, or using other manufacturing techniques to implement a gearbox 200 according to the present embodiment.

A contractor or other entity may provide a crushing device 1, such as a cone crusher, comprising a gearbox 200 according to embodiments described herein. Alternatively, it may be operated in whole or in part by a contractor or other entity, such as a customer, consumer or user of the crusher 1. The contractor or other entity may install the gearbox 200 according to embodiments described herein into the crusher 1, but is not limited thereto.

A contractor or other entity may receive bid requests for items related to designing, manufacturing, delivering, installing, operating, performing maintenance of the gearbox 200 disclosed herein, but is not so limited. A contractor or other entity may offer to design or provide processes or services related to similar systems, devices, or equipment for a customer. The contractor or other entity may propose to modify an existing gearbox 100 or may actually modify it using any one or more of the components or physical features described herein (e.g., but not limited to, the helical recess 210, the inclined floor 211, the high point 212A and the low point 212B, etc.) to manufacture a modified gearbox 200 for the crusher 1 or to modify or retrofit the crusher 1. It is further contemplated that a contractor or other entity may offer, but is not limited to, selling, delivering, and/or installing one or more gearboxes 200 described herein to an end user, customer, or consumer in accordance with the inventive concepts and teachings described herein.

Although the invention has been described in terms of particular embodiments and applications, it is to be understood that other embodiments and modifications may be devised in light of this teaching by those skilled in the art without departing from the spirit or exceeding the scope of the claimed invention.

List of reference numerals

1. Crushing machine

2. Internal thread clamping ring

3. External thread bowl

4. Eccentric wheel

9. Internal thread adjusting ring

10. Web plate

11. Outer ring gear

12. Pinion gear

13. Peripheral driving motor

14. Fastening device

15. Driven gear

16. Shaft

17. Drive shaft

18. Drive pinion

19. Cover

20. Cone body

100. Gear case (conventional)

102. First drive shaft bearing (e.g. sleeve, journal or race)

103. Second drive shaft bearing (e.g. sleeve, journal or race)

106. Main body (conventional)

108. Centerline axis (conventional)

110. Non-helical part annular recess (conventional, e.g. "of uniform depth")

111. Partial ring recess floor of non-spiral uniform depth (conventional)

112. Acute transition (conventional)

120. Big cut (conventional)

122. Pinion clearance baseboard (conventional)

124. Opening of the container

126. Side wall of large incision (conventional)

128. Tapered opening/thrust bearing (conventional)

200. Gear box

202. First drive shaft bearing (e.g. sleeve, journal or race)

204. Second drive shaft bearing (e.g. sleeve, journal or race)

206. Center line axis

210. Spiral recess (i.e. "non-uniform" depth)

211. Spiral recess bottom plate

212A. high spot (e.g. start of spiral non-uniform depth recess)

212B. Low Point (e.g. end of spiral non-uniform depth recess)

222. Pinion clearance bottom plate

224. Opening of the container

228. Tapered split/thrust bearing