Gear well for crusher and crusher comprising same

Abstract

The present disclosure relates to a geared well (100) for a crusher, comprising: a hub surrounding portion (110) arranged to surround at least a portion of a hub of the crusher, and comprising a groove (112) having first and second side walls (114, 116) and a groove base (118); a pinion recess (120) having a bottom (122); and a transition region (130) extending between an end (110a) of the hub surrounding portion (110) and the pinion recess (120), where the transition region (130) provides a stepped transition of the groove (112) from the hub surrounding portion (110) to a bottom (122) of the pinion recess (120). A crusher comprising such a gear well (100) is also disclosed.

Description

Technical Field

[0001] The present disclosure relates to a gear well for a crusher and a crusher including the gear well. Background Art

[0002] Crushers are well known in the art. They are commonly used to reduce rocks and stones to a desired size in applications such as aggregate, recycling and mining. Gyratory crushers or cone crushers are suitable for reducing and shaping the material downstream of the crushing circuit. The material size is reduced by continuous compression between a fixed element, called a bowl liner, and a moving element, called a cover. In addition, the crusher includes a head assembly, which includes a crushing head that rotates about a vertical axis in a bowl attached to the frame of the crusher. The crushing head is assembled around an eccentric member that rotates about an axis to impart a gyratory motion to the crushing head, which crushes the rock, stone or other material as it passes through the crushing gap between the crushing head and the bowl. The crushed material leaves the crusher through the bottom of the crushing gap. The eccentric member can be driven by a variety of power drive devices (such as additional gears driven by a pinion and countershaft assembly) and a variety of mechanical power sources such as an electric motor or an internal combustion engine. A crusher typically includes a gear well (gear slot) configured to lubricate the gear and / or pinion and layshaft assembly.

[0003] A problem with existing gear wells is that they include a sharp transition, which may be called a precipice, along which the lubricating oil flows. The disadvantage of this precipice is that it generates large stresses in the castings of the crusher, which, among other things, reduces the service life of the gear well.

[0004] Conventional gear wells involve a number of drawbacks. Therefore, there is a need in the art for an improvement to reduce stress in the castings, improve oil distribution, and extend the useful life of the gear well. Summary of the invention

[0005] The object of the present disclosure is to mitigate, alleviate or eliminate one or more of the above-mentioned deficiencies and disadvantages in the art, individually or in combination, and to at least solve the above-mentioned problems.

[0006] According to a first embodiment, a gear well for a crusher is provided, comprising:

[0007] a hub enclosure portion, arrangeable to enclose at least a portion of a hub of a crusher and comprising a recess having a first sidewall and a second sidewall and a recess base;

[0008] a pinion recess having a bottom; and

[0009] A transition zone extending between the end of the hub surround and the pinion recess,

[0010] Therein, the transition zone provides a step-like transition of the groove from the hub surrounding part to the bottom of the pinion recess.

[0011] In this case, the hub surrounding part and the pinion recess are arranged at a distance from each other as seen along the center axis of the crusher hub, wherein the transition zone extends between the hub surrounding part and the pinion recess.The hub may be surrounded by the hub surrounding part, the pinion recess and the transition zone.

[0012] Preferably, the gear well comprises two transition zones, wherein one transition zone extends between a first end of the hub enclosing part and the pinion recess, and the other transition zone extends between an opposite second end of the hub enclosing part and the pinion recess. In this way, the hub can be surrounded by the hub enclosing part, the pinion recess and the two transition zones.

[0013] The hub enclosure portion may have a hub enclosure angular distance extending between a first end of the hub enclosure portion and a second end of the hub enclosure portion, the hub enclosure angular distance being between 250 degrees ± 25 degrees.

[0014] The pinion recess may have a pinion recess angular distance extending between a first end of the pinion recess and an opposing second end of the pinion recess, the pinion recess angular distance being between 20 degrees ±5 degrees.

[0015] Each transition zone may have a transition zone angular distance extending between a first end of the transition zone and an opposite second end of the transition zone, the transition zone angular distance being between 45 degrees ± 10 degrees. Preferably, the two transition zones have the same transition zone angular distance.

[0016] When referred to herein, the term "step transition" generally refers to a transition formed by at least one step, thereby forming a non-continuous transition between the end of the hub surrounding portion and the pinion recess. Therefore, the step transition area includes at least one step for providing a step transition.

[0017] The hub enclosure may be configured to be located adjacent to a driven gear for the eccentric. The pinion recess may be configured to receive a pinion and layshaft assembly. A gear well is provided to facilitate lubrication of gears in the crusher. The gear well of the present disclosure has an advantage over conventional gear wells in that it reduces overall stress in the casting of the crusher. Providing a gear well may also facilitate uniform stress distribution. By being able to reduce overall stress and provide uniform stress distribution, the strength of the gear well is improved, thereby increasing the useful life of the gear well.

[0018] The gear well has the following advantages: due to the reduction of overall stress and the improvement of stress distribution, the gear well has higher fatigue strength both in crushing load cases and in casting simulations. The inventors unexpectedly found that by providing a gear well with a stepped transition as described herein, the maximum principal stress range can be reduced by up to a range of 35-40% compared to the gear well of the prior art.

[0019] The gear well also has the advantage that the above features / advantages can be achieved without challenging the external shape of the gear well. This is advantageous because it allows the disclosed gear well to replace an existing gear well in a crusher without modifying or redesigning the crusher. Thus, the disclosed gear well can be used as a retrofit component for existing crushers. In other words, the disclosed gear well has a novel and creative internal structure, which facilitates providing the above advantages without challenging the external shape of the gear well.

[0020] The gear well also has the advantage of preventing or at least reducing failures during use. Furthermore, providing the gear well with a stepped transition improves the casting process because the stresses in the casting are better distributed.

[0021] Another advantage of the gear well is that it allows for reduced foaming or bubbling of the oil in the gear well and efficient oil lubrication of the gears. Foam is an efficient insulator and therefore the temperature of the oil may be difficult to control. Problems caused by foaming may involve oil pressure fluctuations, oil pump cavitation, oil loss through the breather valve and dipstick, and reduced lubrication and cooling efficiency.

[0022] According to some embodiments, the transition zone includes: an angled portion that is angled relative to a plane that passes through the central axis; and a first vertical portion, wherein the angled portion extends between an end of the hub surrounding portion and the first vertical portion, and the first vertical portion extends between the angled portion and the pinion recess. In other words, the angled portion is inclined at an angle relative to a transverse axis that passes through the central axis of the hub.

[0023] This has the advantage of allowing overall stress reduction in the casting during production of the gear well.

[0024] According to some embodiments, the transition zone includes at least two steps for providing a stepped transition. This has the advantage of allowing each step of the transition zone to be smaller, i.e., having a smaller height along the central axis than when only one step is provided. By being able to provide a smaller step, the path of the oil can be smoother, thereby reducing the foaming of the oil. This also has the advantage of allowing the overall stress of the gear well to be reduced, thereby increasing the durability of the gear well and extending the service life.

[0025] According to some embodiments, the at least two steps are arranged at different angular positions relative to a central axis of the hub.

[0026] When mentioned herein, the term "arranged at different angular positions relative to the central axis of the hub" generally means that each step has a main radial extension in a radial direction which is different from the radial direction of another step having a main radial extension.

[0027] This has the advantage of allowing a seamless transition in the transition zone between the hub surround and the bottom of the pinion recess. It also has the advantage of allowing a more uniform wall thickness. In other words, compared to conventional gear wells, there is no drastic wall thickness variation, which helps reduce the likelihood of casting defects.

[0028] According to some embodiments, the transition zone includes an inclined portion, a first vertical portion, and a second vertical portion, wherein the second vertical portion connects the end of the hub surrounding portion with the inclined portion, the inclined portion extends between the second vertical portion and the first vertical portion, and the first vertical portion extends between the inclined portion and the pinion recess.

[0029] When referred to herein, the term "connected" generally refers to the second vertical portion extending at least between the end of the hub surrounding portion and the angular portion. However, in some embodiments, at least a portion of the second vertical portion may also extend to the first vertical portion and / or the pinion recess. Therefore, the second vertical portion can be designed in different ways.

[0030] This has the advantage of allowing a two-step transition area to be formed, thereby obtaining an improved gear well. Also as previously mentioned, the two-step transition area allows oil to be supplied in the gear well in a smooth manner while reducing overall stress in the casting.

[0031] According to some embodiments, the first vertical portion has an extension in the axial direction and an extension in the radial direction of the hub, and the second vertical portion has an extension in the axial direction and an extension in the tangential direction of the hub.

[0032] The axial direction is parallel to the central axis of the hub.The radial direction is preferably radial with respect to the extension of the hub.

[0033] This has the advantage that it allows the transition zone to be arranged based on the outer geometry of the gear well, for example allowing the transition zone to surround a portion of the hub and extend between an end of the hub surrounding portion and the pinion recess.

[0034] According to some embodiments, the axial extension of the first vertical portion is uniform, whereas the axial extension of the second vertical portion is non-uniform. This provides an effective step-like transition zone.

[0035] According to some embodiments, the axial extension of the first vertical portion is in the range of 5 to 120 mm, such as 10 to 115 mm.

[0036] The axial extension of the second vertical portion may be in the range of 5 to 250 mm, for example 25 to 150 mm. Again, as previously mentioned, the axial extension of the second vertical portion is non-uniform, so that the axial extension of the vertical portion varies along the axial extension in the range of 5 to 250 mm, for example 25 to 150 mm.

[0037] According to some embodiments, the inclined portion has an extension in radial direction and an extension in tangential direction of the hub. Again, as previously mentioned, this has the advantage of allowing an improved structure of the gear well, providing a more robust gear well, without requiring changes to its outer shape or geometry.

[0038] According to some embodiments, the tangential extension of the inclined portion is equal to the tangential extension of the second vertical portion. In other words, the length of the tangential extension of the inclined portion is the same as the length of the tangential extension of the second vertical portion. Within the scope of the present disclosure, it can also be provided that the tangential extension of the inclined portion is shorter than the tangential extension of the second vertical portion, or the tangential extension of the inclined portion is longer than the tangential extension of the second vertical portion. It should be understood by those skilled in the art that the tangential direction of the hub is a direction tangential to a portion of the hub. Therefore, in some embodiments, the inclined portion has a tangential extension in a tangential direction of a portion of the hub, which is different from the tangential direction of another portion of the hub, and the second vertical portion has a tangential extension in the tangential direction of the other portion of the hub.

[0039] According to some embodiments, the inclined portion has a downward slope towards the pinion recess.

[0040] This has the advantage that it facilitates the transition zone to extend between the end of the hub surrounding part and the pinion recess in a smooth and ideal manner, so that the hub surrounding part and the pinion recess can be connected via the transition zone.

[0041] According to some embodiments, the angle between the bottom of the pinion recess and the downward slope of the inclined portion is between 130 and 175 degrees, such as between 145 and 160 degrees.

[0042] This has the advantage that it avoids the need to include steep corners in the gear well as included in conventional gear wells.

[0043] According to some embodiments, the at least two steps have rounded transitions.

[0044] An advantage of this is that the rounded transition provides increased gear strength due to reduced overall stress in the casting compared to a gear well with a sharp transition.

[0045] The transition zone may include a rounded transition. The hub surround may include a rounded transition. The pinion recess may also include a rounded transition. Thus, in some embodiments, all portions present in the gear well have a rounded transition. Advantageously, the overall stress in the gear well is reduced and a more uniform stress distribution is provided in the casting.

[0046] According to some embodiments, the transition zone comprises more than one angular portion and more than two vertical portions, wherein each angular portion extends between two vertical portions.

[0047] Preferably, the gear well comprises a number of vertical portions which is one greater than the number of angular portions, so as to form a stepped transition.

[0048] According to a second aspect of the present disclosure, these and other objects are also fully or at least partially achieved by a crusher including the above-mentioned gear well.

[0049] The effects and features of the second solution are largely similar to those described above in conjunction with the first solution. The embodiments described in connection with the first solution are also applicable to the second solution to a large extent. It is further noted that, unless explicitly stated, the disclosed concept relates to all possible combinations of features.

[0050] Other application scopes of the present disclosure can be clearly understood from the specific embodiments given below. However, it should be understood that although the specific embodiments and specific examples show preferred embodiments of the present disclosure, these are only for illustration, because those skilled in the art will understand various modifications and variations within the scope of the present disclosure from the specific embodiments.

[0051] Therefore, it should be understood that the present disclosure is not limited to the specific components of the described equipment or the steps of the described method, because the equipment and method can be different. It should also be understood that the terms used herein are only used for the purpose of describing specific embodiments and are not limiting. It should also be noted that the words "one", "a kind of", "the" and "said" used in this specification and the appended claims are intended to indicate the presence of one or more elements, unless the context clearly indicates otherwise. Therefore, for example, mentioning "a unit" or "said unit" can include multiple devices, etc. In addition, the words "comprise", "include", "contain" and similar words do not exclude the presence of other elements or steps. BRIEF DESCRIPTION OF THE DRAWINGS

[0052] The present disclosure will be described in more detail, by way of example, with reference to the accompanying drawings, which show currently preferred embodiments of the disclosure.

[0053] Figure 1 A perspective view of a gear well known in the prior art is shown.

[0054] Figure 2 Shows Figure 1 A cross-sectional view of a gear well known in the prior art is shown.

[0055] Figure 3 A cross-sectional view of a gear well is shown according to an embodiment of the present disclosure.

[0056] Figure 4a-4b The present invention shows an embodiment of Figure 3 A detailed view of the transition zone to the gear well is shown.

[0057] Figure 5a-Figure 5b A detailed view of a transition zone of a gear well is shown according to an embodiment of the present disclosure.

[0058] Figure 6 A detailed view of a transition zone of a gear well is shown according to an embodiment of the present disclosure.

[0059] Figure 7 A detailed view of a transition zone of a gear well is shown according to an embodiment of the present disclosure.

[0060] Figure 8 A detailed view of a transition zone of a gear well is shown according to an embodiment of the present disclosure. DETAILED DESCRIPTION

[0061] The present disclosure will be described more fully below in conjunction with the accompanying drawings, in which the currently preferred embodiments of the present disclosure are shown. However, the present disclosure may have many different forms and should not be construed as being limited to the described embodiments; on the contrary, these embodiments are provided to more fully and completely describe the scope of the present disclosure to the skilled person.

[0062] Figure 1 and Figure 2 A gear well 10 as known in the prior art is shown. The gear well 10 is configured to lubricate gears in a crusher such as a gyratory crusher or a cone crusher as known in the prior art. Although the crusher is not shown, it will be understood by those skilled in the art that the gear well is configured to be arranged in a crusher as known in the prior art. A gyratory crusher or a cone crusher is suitable for size reduction and shaping of material downstream of a crushing circuit. The size of the material is reduced by continuous compression between a fixed element, called a bowl liner, and a moving element, called a cover. In addition, the crusher includes a head assembly, which includes a crushing head that revolves around a vertical axis in a bowl attached to the main frame of the crusher. The crushing head is assembled around an eccentric that rotates around an axis to impart a gyratory motion to the crushing head, which crushes rocks, stones or other materials as they pass through a crushing gap between the crushing head and the bowl. The crushed material leaves the crusher through the bottom of the crushing gap. The eccentric assembly may be driven by a variety of power drive means, such as additional gears driven by a pinion and layshaft assembly, and a variety of mechanical power sources such as an electric motor or internal combustion engine.

[0063] The gear well 10 includes a hub surrounding portion 11, a pinion recess 12, and two transition zones 13. The hub surrounding portion 11 has a first side wall 14 and a second side wall 16, defining a groove extending between the two side walls. The pinion recess 12 has a bottom 22. Each transition zone 13 extends between the end of the hub surrounding portion 11 and the pinion recess 12. Each transition zone 13 has a sharp transition (also called a cliff) at which the groove transitions to the pinion recess by a sharp increase in groove depth.

[0064] Figure 3A cross-sectional view of a gear well 100 according to an embodiment of the present disclosure is shown. The gear well 100 may be used in a crusher (e.g., a gyratory crusher or a cone crusher) for lubricating gears in the crusher. The gear well 100 includes a hub surrounding portion 110, a pinion recess 120, and two transition zones 130. However, it should be noted that the gear well 100 may include only one transition zone 130. Thus, the gear well 100 may include at least one or two transition zones 130. The hub surrounding portion 110 surrounds at least a portion of a crusher hub (not shown). The hub surrounding portion 110 extends from one transition zone 130 to another transition zone 130. The pinion recess 120 extends between the two transition zones 130. Thus, each transition zone 130 extends between a respective end of the hub surrounding portion 110 and a respective end of the pinion recess 120. The pinion recess 120 has a pinion bottom 122. The pinion recess 120 is configured to receive a pinion and countershaft assembly. The pinion recess 120 has an extension d2 in the radial direction RD. The extension d2 ranges from 100 to 300 mm, preferably from 145 to 225 mm. The pinion recess 120 has an extension d3 in the axial direction AD. The extension d3 ranges from 30 to 100 mm, preferably from 50 to 80 mm. The extensions d2, d3 can be selected based on the geometry of the pinion and countershaft assembly.

[0065] The transition zone 130 has respective extensions d1 and d1' in the radial direction RD. The extension d1 ranges from 50 to 150 mm and the extension d1' ranges from 50 to 150 mm. Preferably, the extension d1 is equal to the extension d1', so as to form a uniform gear well.

[0066] An angle α is formed between the two transition areas 130. The angle α ranges from 90 to 130 degrees, preferably from 100 to 120 degrees.

[0067] Figure 4a and Figure 4b In further detail Figure 3 The gear well 100 is shown in FIG. Figure 4a The conceptual design of the gear well 100 is shown, and Figure 4b The basic shape of the gear well 100 is shown. Figure 3 As discussed above, the hub enclosure 110 includes a groove 112 having a first sidewall 114, a second sidewall 116, and a groove base 118. The hub enclosure 110 is configured to receive lubricating oil that may be supplied into the gear well 100 to lubricate the gears of the crusher.

[0068] Figure 4a and Figure 4b Shows Figure 3However, it should be noted that the geometries of the two transition zones 130 are preferably mirror images, so that Figure 4a and Figure 4b The features of the transition zone 130 shown in the figure can be applied to another transition zone 130 in the same manner. The transition zone 130 provides a stepped transition of the groove 112 from the hub surrounding portion 110 to the bottom 122 of the pinion recess 120. In the present exemplary embodiment, the transition zone 130 includes two steps for providing the stepped transition. The transition zone 130 includes an inclined portion 132, a first vertical portion 134, and a second vertical portion 136, thereby forming a two-step stepped transition. The second vertical portion 136 extends between the end 110a of the hub surrounding portion 110 and the inclined portion 132, so that the second vertical portion 136 connects the end 110a of the hub surrounding portion 110 with the inclined portion 132. The inclined portion 132 extends between the second vertical portion 136 and the first vertical portion 134. The first vertical portion 134 extends between the inclined portion 132 and the pinion recess 120. Thus, the transition area 130 forms a transition between the end 110 a of the hub surrounding portion 110 and the pinion recess 120 .

[0069] like Figure 6 As best shown in FIG. 1 , the inclined portion 132 has an extension REA in the radial direction RE and an extension TEA in the tangential direction TD. The first vertical portion 134 has an extension AE1 in the axial direction AD and an extension RE1 in the radial direction RD. The second vertical portion 136 has an extension AE2 in the axial direction AD and an extension TE2 in the tangential direction TD.

[0070] Return to reference Figure 4a and Figure 4b , relative to the conventional gear well, the hub surrounding portion 110, the pinion recess 120 and the transition zone 130 are all designed without changing the outer geometry of the gear well 100. The inclined portion 132 has a downward slope toward the pinion recess 130. Therefore, the inclined portion 132 has an upper end and a lower end, which are arranged at a distance from each other along the central axis CA. In addition, in order to make the transition zone 130 follow the outer geometry of the hub, the two steps (especially the two vertical portions 134 and 136) are respectively arranged at different angular positions relative to the central axis CA of the hub.

[0071] like Figure 4a As best shown, the transition region 130 includes a rounded transition. In other words, each portion 132, 134, and 136 of the transition region 130 includes a rounded transition, Figure 1 and Figure 2The illustrated prior art shows the opposite of the sharp transitions in the gear wells known therefrom. Typically, the fillet transitions may have a minimum radius of 5 mm and above. In addition, the hub surround 110 and the pinion recess 120 also include fillet transitions. Thus, an improved stress distribution and overall stress reduction of the casting is achieved.

[0072] refer to Figure 4b , the transition region 110 is shown without including a rounded transition, primarily for illustration purposes. Figure 4b It is also shown that the second vertical portion 136 has a smaller axial extension AE2 than the first vertical portion 134. However, it is also possible in another way, for example, an embodiment in which the first vertical portion 134 has a smaller axial extension AE1 than the second vertical portion 136 can also be realized within the scope of the concept of the present disclosure. It is also possible that the first vertical portion 134 and the second vertical portion 136 have the same axial extensions AE1 and AE2.

[0073] The gear well 100 also includes a pinion housing 140 configured to receive a pinion and layshaft assembly.

[0074] refer to Figure 5a and Figure 5b , shows another embodiment of the present disclosure, wherein the arrangement of the inclined portion 132 , the first vertical portion 134 , and the second vertical portion 136 of the transition zone is different relative to the previously described transition zone 130 . Figure 5a A conceptual diagram of a gear well 100 is shown. Figure 5b The basic shape of the gear well 100 is shown.

[0075] In this example embodiment, the second vertical portion 136 extends between the end 110a of the hub surrounding portion 110 and the inclined portion 132. The inclined portion 132 extends between the second vertical portion 136 and the first vertical portion 134. The first vertical portion 134 extends between the inclined portion 132 and the bottom 122 of the pinion recess 120. Figure 5a and Figure 5b As shown, the first vertical portion 134 has a uniform axial extension AE1, while the second vertical portion 136 has a non-uniform axial extension AE2. This allows the transition zone 130 to be changed relative to gear wells known in the art without affecting the outer shape or geometry of the gear well 100.

[0076] The inclined portion 132 has a downward slope toward the pinion recess 120. An angle β between the bottom 122 of the pinion recess 120 and the downward slope of the inclined portion 132 is shown. The angle β is preferably in the range of 130 to 175 degrees, for example, 145 to 160 degrees. Figure 5b, the angle β is about 145 degrees. The downward slope of the inclined portion 132 depends on the axial extension of the first vertical portion 134 and the second vertical portion 136. Thus, the angle β indirectly depends on the downward slope of the inclined portion 132.

[0077] refer to Figure 6 , shows another embodiment of the present disclosure, in which the arrangement of the inclined portion 132, the first vertical portion 134, and the second vertical portion 136 of the transition zone 130 is different from the previously described transition zone 130. Figure 5a and Figure 5b Compared with the first vertical portion 134 of the embodiment shown in Figure 6 In the embodiment shown, the first vertical portion 134 has a greater axial extension AE1. Figure 5a and Figure 5b Compared to the second vertical portion 136 of the embodiment shown in , the second vertical portion 136 has a smaller axial extension AE2. Figure 6 The angle β depicted in FIG. 1 is about 160 degrees in the present embodiment. Generally, as the axial extension AE1 of the first vertical portion 134 increases and the axial extension AE2 of the second vertical portion 136 remains constant, the downward slope of the inclined portion 132 decreases and the angle β increases.

[0078] It should be noted that Figure 6 The basic shape of the gear well 100 is shown. However, although not shown, the angular transitions of the transition area 130 and the angular transitions of the hub surrounding portion 110 and the pinion recess can all be rounded transitions for the reasons discussed above.

[0079] refer to Figure 7 , shows yet another embodiment according to the present disclosure, in which the arrangement of the inclined portion 132 , the first vertical portion 134 , and the second vertical portion 136 of the transition zone 130 is different from the previously described embodiments.

[0080] In this example embodiment, the second vertical portion 136 connects the end 110a of the hub surrounding portion 110 with the inclined portion 132. In addition, the second vertical portion 136 extends partially between the end 110a of the hub surrounding portion 110 and the inclined portion 110, and partially between the end 110a of the hub surrounding portion 110 and the pinion recess 120.

[0081] It should be noted that Figure 7 The basic shape of the gear well 100 is shown. However, although not shown, the angular transitions of the transition area 130 and the angular transitions of the hub surrounding portion 110 and the pinion recess may also preferably be rounded for the reasons discussed above.

[0082] refer to Figure 8, shows yet another embodiment according to the present disclosure, in which the arrangement of the inclined portion 132, the first vertical portion 134 and the second vertical portion 136 is different from the previously described embodiments.

[0083] exist Figure 8 In the illustrated embodiment, the second vertical portion 136 extends between the end 110a of the hub surrounding portion 110 and the inclined portion 132. The inclined portion 132 extends between the first vertical portion 134 and the second vertical portion 136. The first vertical portion 134 extends between the inclined portion 132 and the pinion recess 120. Since the axial extensions AE1 and AE2 of the first vertical portion 134 and the second vertical portion 136 in the axial direction AD are shorter, the inclined portion 132 is slightly bent around a portion of the hub here.

[0084] It should be noted that Figure 8 The basic shape of the gear well 100 is shown. Providing the angular transitions of the transition area 130 and the angular transitions of the hub surround 110 and the pinion recess as rounded transitions may also fall within the concepts of the present disclosure and may be preferred for reasons discussed herein.

[0085] Those skilled in the art will appreciate that the present disclosure is by no means limited to the preferred embodiments described above. Instead, numerous modifications and variations are possible within the scope of the appended claims.

[0086] For example, the transition zone 130 may include only the inclined portion 132 and the first vertical portion 134. In this case, the inclined portion 132 extends between the end 110a of the hub surrounding portion 110 and the first vertical portion 134. The first vertical portion 134 extends between the inclined portion 132 and the pinion recess 120. For other examples, the transition zone 130 may include more than two vertical portions and one inclined portion. In one example, the transition zone 130 includes one more vertical portion than the number of angular portions to form a stepped transition.

[0087] Additionally, numerous variations to the disclosed embodiments can be understood and effected by those skilled in the art through a study of the drawings, the disclosure, and the appended claims.

Claims

1. A gear well (100) for a crusher, comprising: a hub enclosure (110) configurable to enclose at least a portion of a hub of the crusher and comprising a recess (112) having first and second side walls (114, 116) and a recess base (118); a pinion recess (120) having a bottom (122); as well as a transition zone (130) extending between an end (110a) of the hub surrounding portion (110) and the pinion recess (120), The transition zone (130) provides a stepped transition of the groove (112) from the hub surrounding portion (110) to the bottom (122) of the pinion recess (120).

2. The gear well (100) according to claim 1, wherein the transition zone (130) includes an inclined portion (132) which is angled relative to a plane transverse to the center axis (CA); and a first vertical portion (134), wherein the inclined portion (132) extends between an end portion (110a) of the hub surrounding portion (110) and the first vertical portion (134), and the first vertical portion (134) extends between the inclined portion (132) and the pinion recess (120).

3. The gear well (100) according to claim 1 or 2, wherein the transition zone (130) includes a step to provide the stepped transition.

4. The gear well (100) according to any one of claims 1 to 3, wherein the transition zone (130) comprises at least two steps for providing the stepped transition.

5. The gear well (100) according to claim 4, wherein the at least two steps are arranged at different angular positions relative to the central axis (CA) of the hub.

6. The gear well (100) according to any one of claims 4 to 5, wherein the transition zone (130) includes an inclined portion (132), a first vertical portion (134) and a second vertical portion (136), wherein the second vertical portion (136) connects the end (110a) of the hub surrounding portion (110) with the inclined portion (132), the inclined portion (132) extends between the second vertical portion (136) and the first vertical portion (134), and the first vertical portion (134) extends between the inclined portion (132) and the pinion recess (120).

7. The gear well (100) according to claim 6, wherein the first vertical portion (134) has an extension (AE1) in an axial direction (AD) and an extension (RE1) in a radial direction (RD) of the hub, and the second vertical portion (136) has an extension (AE2) in an axial direction (AD) and an extension (TE2) in a tangential direction (TD) of the hub.

8. The gear well (100) according to claim 7, wherein the axial extension (AE1) of the first vertical portion (134) is uniform, and the axial extension (AE2) of the second vertical portion (136) is non-uniform.

9. The gear well (100) according to claim 7 or 8, wherein the axial extension (AE1) of the first vertical portion (134) is in the range of 5 to 120 mm, for example 10 to 115 mm.

10. The gear well (100) according to any one of claims 2 to 9, wherein the inclined portion (132) has an extension (REA) in a radial direction and an extension (TEA) in a tangential direction (TD) of the hub.

11. The gear well (100) according to claim 10, wherein a tangential extension (TEA) of the inclined portion (132) is equal to a tangential extension (TE2) of the second vertical portion (136).

12. The gear well (100) according to any one of claims 2 to 11, wherein the inclined portion (132) has a downward slope toward the pinion recess (120).

13. The gear well (100) according to claim 12, wherein the angle β between the bottom (122) of the pinion recess (120) and the downward slope of the inclined portion (132) is 130 to 175 degrees, for example 145 to 160 degrees.

14. The gear well (100) according to any one of the preceding claims, wherein the stepped transition (130) has a rounded transition.

15. The gear well (100) according to any one of the preceding claims, wherein the transition zone (130) includes more than one angular portion and more than two vertical portions, wherein each angular portion extends between two vertical portions.

16. A crusher comprising a gear well (100) according to any one of the preceding claims.

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