Roller device for grinding feed material, in particular excavation material, and roller system
Patent Information
- Application Number
- PCT/EP2026/052717
- Authority / Receiving Office
- WO · WO
- Patent Type
- Applications
- Current Assignee / Owner
- Priority Date
- 2025-02-27
- Filing Date
- 2026-02-03
- Publication Date
- 2026-09-03
Smart Images
Figure EP2026052717_03092026_PF_FP_ABST
Abstract
Description
[0001] M / FLSM-016-PC FLSmidth A / S JK / PW
[0002] Roller device for grinding input material, in particular mining material, and roller system
[0003] Description
[0004] The invention relates to a roller device for grinding input material, in particular mining material, and a roller system. A roller device according to the preamble of claim 1 is, for example, made of the
[0005] WO 2021 / 144191 Al known.
[0006] To crush raw materials or extracted material containing rocks such as limestone, ore, or the like, roller mills can be used. These roller mills often have two essentially parallel rollers that define a grinding gap between them. The grinding gap is adjustable by mounting at least one of the rollers so that its position relative to the opposite roller can be adjusted. The known roller mills are also equipped with an actuating unit to move one of the two rollers towards the other during operation. Such roller mills can also be called roller presses.
[0007] From the aforementioned WO 2021 / 144191 Al, for example, a roller device of the type described above is known, comprising two parallel rollers with a grinding gap between them. Specifically, the roller device has a loose roller and a fixed roller, the loose roller being pivotably mounted about a pivot axis located between the roller rotation axes. This allows the loose roller to be pivoted towards the fixed roller during operation, particularly by means of an actuating unit, in order to build up contact pressure when grinding the feed material. In other words, the position of the loose roller relative to the fixed roller is relatively adjustable. Furthermore, the fixed roller, like the loose roller, can be mounted on the same pivot axis, with the fixed roller being a M / FLSM-016-PC 2
[0008] It features fixed bearings to absorb grinding and roller contact forces. The position of the fixed roller is not adjustable during operation.
[0009] The actuating unit of the roller device interacts with the loose roller via an angled lever to move it around the pivot axis. This allows for the adjustment of a grinding gap between the loose and fixed rollers, as well as a specific grinding force, during operation. However, a disadvantage of the roller device according to WO 2021 / 144191 Al is that, due to the position and length of the lever arm, in combination with the described direction of action of an actuating force introduced into the lever arm by the actuating unit, undesirable constraint forces prevail, particularly at the point of force application, on the lever arm, and on the pivot axis.
[0010] The invention is therefore based on the objective of providing a roller device for grinding feed material which has the simplest possible design, is cost-effective, and at least reduces undesirable constraint forces. The invention is further based on the objective of providing a roller system with such a roller device.
[0011] According to the invention, this problem is solved with regard to the roller device by the subject matter of claim 1. With regard to the roller system, the aforementioned problem is solved by the subject matter of claim 10.
[0012] Specifically, the task is accomplished by a roller device for grinding input material, in particular mining material:
[0013] - a first roller unit with a first roller, in particular a loose roller, and a second roller unit with a second roller, in particular a fixed roller, wherein the two rollers each have an axis of rotation; - at least one pivot bearing which pivotably supports the two roller units, wherein the pivot bearing has a pivot axis located between the axes of rotation of the two rollers, about which the rollers are movable; and
[0014] - at least one actuating unit which interacts with the first roller for movement about the pivot axis by means of at least one angle lever, wherein the angle lever comprises at least one force arm and at least one load arm, wherein the force arm extends from a force application point of the actuating unit to the pivot axis and the M / FLSM-016-PC 3
[0015] The load arm extends from the pivot axis to the axis of rotation of the first roller.
[0016] According to the invention, the force arm extends at an angle β to the load arm, which is less than or equal to 45 degrees. Additionally, the actuating unit is arranged and aligned such that an actuating force can be introduced into the force arm substantially orthogonally at the point of force application.
[0017] The invention offers several advantages. The alignment of the force arm at an angle β, less than or equal to 45 degrees from the load arm of the angle lever, allows for particularly flexible positioning and determination of the force application point on the force arm. Furthermore, it has been shown that this results in advantageous geometric freedom regarding the position of the force application point in relation to a roller contact point of the two rollers, the axis of rotation of the first roller (especially the loose roller), and the position of the pivot axis. The angular position of the force arm according to the invention allows for a generous and flexible spacing of the force application point, particularly from the pivot axis. This has a beneficial effect on the forces acting on one or more components of the roller assembly during operation. Moreover, this results in an optimized structural design of the roller assembly.
[0018] The angle β between the force arm and the load arm can be up to 45 degrees, in particular up to 40 degrees, up to 35 degrees, up to 30 degrees, up to 25 degrees, or up to 20 degrees. In other words, the angle β can lie within a range of 20 degrees to 45 degrees, in particular 25 degrees to 40 degrees or 30 degrees to 35 degrees. Other values for the angle β, within a range of, for example, 10 degrees to 45 degrees, are possible.
[0019] The bell crank, through which the actuating unit interacts with the first roller, has a force arm and a load arm that merge into each other at the pivot axis. The force arm and the load arm each form a specific segment of the bell crank. Crucially, the force arm and load arm of the bell crank have separate paths. In other words, the force arm and load arm of the bell crank do not overlap. Preferably, the force arm and load arm are straight. In other words, the force arm preferably forms a first straight line, particularly an imaginary line, from the point of force application of the actuating unit to the M / FLSM-016-PC 4
[0020] The pivot axis and the load arm form a second straight line, in particular an imaginary line, from the pivot axis to the axis of rotation of the first roller. The force arm and load arm preferably lie in one and the same plane, which is vertically oriented and orthogonal to the pivot axis.
[0021] A further advantage of the invention is that, due to the specific arrangement and orientation of the actuating unit, the actuating force introduced or to be introduced into the force arm at the point of force application acts essentially, and in particular approximately, orthogonally to the force arm. In other words, the actuating unit is designed such that the line of action of the introduced or to be introduced actuating force runs essentially orthogonally to the force arm. This applies preferably to an operating position of the first roller, in particular the loose roller, in which it is moved about the pivot axis depending on a grinding gap between the two rollers. The operating position can be an operating point at which a desired grinding gap is set with a specific diameter of the rollers.The actuating unit is adapted to perform a translational positioning movement such that the first roller, in particular the first roller unit, is moved about the pivot axis in the direction of the second roller.
[0022] Due to the essentially orthogonal application of the actuating force, the actuating force acts on the force arm with increased efficiency. In other words, the actuating force of the actuating unit, which counteracts a grinding force occurring in the grinding gap during operation, is minimized by the essentially orthogonal force application to the force arm. This has the significant advantage that only very small or no constraint forces act on the angle lever or the first roller unit, in particular a bearing housing, preferably a bearing block, of the first roller unit, and / or the pivot bearing. Due to the arrangement and orientation of the actuating unit according to the invention, components of a mechanical connection, e.g., bearings, bolts, material cross-sections, or the like, of the actuating unit to the first roller unit and of the first roller unit itself can be dimensioned smaller.Furthermore, it is advantageous that the force arm of the angle lever can be optimally designed according to requirements and geometric conditions. Consideration of the load arm is not necessary. M / FLSM-016-PC 5.
[0023] In the roller assembly according to the invention, both rollers, and in particular both roller units, are pivotable about the common pivot axis of the pivot bearing. However, the movement of the rollers about the pivot axis depends on the operating state of the roller assembly. The roller assembly is designed such that, during operation, the first roller, and in particular the first roller unit, is movable about the pivot axis relative to the second roller, and in particular the second roller unit. In other words, during operation, the first roller can be pivoted towards or away from the second roller about the pivot axis. Or, put another way, the position of the first roller, and in particular the first roller unit, can be changed during operation. This makes it possible, on the one hand, to adjust the grinding gap during operation and / or, on the other hand, to set a specific grinding force directed towards the second roller.For this purpose, the roller device has the actuating unit which is coupled to the first roller unit in a force-applying manner in order to introduce a certain actuating force into the force arm of the angle lever.
[0024] During operation, the second roller is fixed in position. This means that, unlike the first roller, the second roller cannot be moved during operation, particularly around its pivot axis. Due to its pivoting capability during operation, the first roller can be described as a floating roller, and the second roller as a fixed roller.
[0025] Operation is understood to mean that the rollers of the two roller units are driven, i.e., rotate around their axes. Preferably, the rollers rotate in opposite directions around their axes during operation, particularly rotating from above into the grinding gap. During a grinding process, the rollers each rotate in a direction leading towards the grinding gap to feed the material to be ground into the grinding gap and grind it. It is possible that at least one or both rollers rotate in opposite directions. This can occur, for example, if material to be ground becomes jammed between the rollers or if the rollers are blocked by material being ground, particularly to free the rollers. However, this is a special case that does not correspond to normal operation.
[0026] When the roller assembly is at rest, both the first and second rollers can be moved around the pivot axis. In other words, M / FLSM-016-PC 6
[0027] The roller assembly is designed such that the second roller, in particular the second roller unit, can pivot about the pivot axis. Thus, when stationary, the first and second rollers can preferably be repositioned. This function is provided, for example, during commissioning, maintenance, repair of the roller assembly, or replacement of at least one roller. Additionally or alternatively, the second roller can be moved about the pivot axis during adjustment procedures performed when stationary.
[0028] The roller device is preferably used for crushing or grinding input material, especially mining waste. The roller device is particularly preferably used as a roller mill, especially a roller press, for crushing or grinding mining waste. Such mining waste can include rock types of any kind, such as limestone, as well as minerals such as ores or the like.
[0029] Alternatively, it is conceivable that the roller device could not only be used as a large-scale plant for mining, but could also be scaled as needed to be used as a medium-sized or small-scale plant.
[0030] Preferred embodiments of the invention are specified in the dependent claims.
[0031] In a preferred embodiment, the actuating unit is arranged and aligned such that an actuating force can be applied at the point of force application at an angle of 80 to 100 degrees, in particular 85 to 95 degrees, preferably 89 to 91 degrees to the force arm. In other words, the actuating unit is arranged and aligned such that the line of action of the actuating force to be applied or already applied is essentially orthogonal to the force arm. This preferably applies to the position of the actuating unit during operation and / or when at standstill. The aforementioned advantageous angular ranges are specified to cover the entire operating range of the first roller, in which the first roller is moved about the pivot axis to adjust the grinding gap or a specific grinding force. This increases the variability of the roller assembly, particularly with regard to the orientation of the
[0032] Actuating unit.M / FLSM-016-PC 7
[0033] In a further preferred embodiment, the actuating unit comprises at least one cylinder, in particular a hydraulic cylinder, oriented essentially orthogonally to the force arm. The cylinder preferably includes a piston rod coupled to the first roller unit, in particular to a bearing housing, and adapted to perform a translational positioning movement, in particular a stroke. This provides a simple and cost-effective way to move the first roller about the pivot axis. At the same time, the cylinder can be easily integrated into the roller assembly, allowing it to remain compact. The cylinder can be a plunger piston cylinder or a reciprocating piston cylinder.Furthermore, this embodiment has the advantage that the force at the point of application, regardless of the stroke of the cylinder, remains approximately constant over the full swivel range of the first roller, and thus also the acting torque around the swivel axis, formed from the product of the actuating force and the length of the force arm.
[0034] Preferably, the roller device has at least one measuring device for displacement measurement, in particular stroke measurement, which is arranged on or integrated into the actuating unit. In the case of a cylinder, this allows the stroke of a piston rod to be measured. From this, the swivel angle and the swivel position of the first roller with respect to the swivel axis, and thus the size of the grinding gap, can be determined.
[0035] Complex and unreliable rotary encoders, as specified in WO 2021 / 144191 Al, are unnecessary here. The measuring device for position measurement on the actuating unit is cost-effective to implement and enables increased reliability for determining the roller position and the grinding gap.
[0036] It is generally known that any reduction in actuating force achieved by selecting a specific arm length ratio must be compensated for by a correspondingly long stroke of the actuating unit. It is advantageous for the force arm and the load arm to have a length ratio of 2:1 to 3:1. In other words, the force arm preferably has a length that is two to three times the length of the load arm. Larger arm length ratios are disadvantageous for the dimensioning of the pivot axis and the pivot bearing and require a large stroke of the actuating unit. Smaller arm length ratios may be possible for the first roller unit, but they necessitate an increased actuating force from the actuating unit and are difficult to implement in the already limited installation space. M / FLSM-016-PC 8
[0037] to integrate the roller direction. This embodiment thus covers the optimal range in which the length ratio of the force and load arm allows for improved coordination of the actuating force and stroke of the actuating unit.
[0038] In the roller assembly, no force application point for an actuating unit is provided for the second roller unit with the second roller, in particular the fixed roller. The roller assembly preferably includes a counter bearing to absorb and dissipate a reaction force from the actuating force introduced by the actuating unit and / or the grinding force occurring during operation. Depending on the selected position of this counter bearing relative to the pivot axis, ratios between the force arm length and the load arm length in the range of 1.5:1 to 3:1 can result. This must generally be taken into account when designing a synergistic force support, especially with regard to the pivot bearing.
[0039] Particularly preferably, the first roller unit has at least one roller bearing for rotatably mounting the first roller with a bearing housing, in particular a bearing block, wherein the bell crank, in particular the force and / or load arm, is an integral part of the bearing housing. In other words, the bell crank is part of a bearing housing, in particular the bearing block, of the first roller unit. In this embodiment, the actuating unit is connected to the bearing housing, in particular directly. The bearing housing thus represents a central component that encloses the bell crank. This embodiment has the advantage that the number of parts is reduced, since separate lever components are eliminated. The bearing housing therefore not only supports the first roller but also transmits the force from the actuating unit to the first roller. Additionally, the bearing housing is, for example,via a swivel arm, preferably connected to the swivel bearing, to mount the first roller in a pivotable manner.
[0040] In a preferred embodiment, the actuating unit is connected on one side to the bearing housing of the first roller unit and on the other side to a counter bearing that supports the actuating unit. In other words, the actuating unit comprises two joints which, depending on the operating position of the first roller, in particular the loose roller, transmit a substantially orthogonal force into the force arm of the angle lever M / FLSM-016-PC 9
[0041] This is made possible by the articulated connection of the actuating unit to the bearing housing, in particular a bearing block of the first roller unit. The orientation of the actuating unit changes depending on the stroke performed. This has the advantage that the actuating unit adapts its position to the position of the force arm, thus achieving optimal force transmission regardless of the operating position of the first roller.
[0042] It is further advantageous if the bearing housing of the first roller unit comprises a vertical median plane to which the pivot axis is orthogonal, with the point of force application on the force arm lying in the median plane. Here, it is advantageous that the force transmission from the point of force application to the first roller occurs in one and the same plane.
[0043] In one embodiment, the axes of rotation of the two rollers and the pivot axis are arranged such that their connecting lines, lying in a plane, particularly the median plane, form a triangle, wherein the vertical distance of the pivot axis to the connecting line between the two axes of rotation corresponds to 0.4 to 0.7 times, preferably 0.5 times, the diameter of the first and / or second roller. Preferably, the intersection of the pivot axis with the plane forms a first point that constitutes the apex of the triangle.
[0044] The axes of rotation of the two rollers are arranged opposite each other on the pivot axis. The intersection of each axis of rotation with the plane forms another (vertex) point of the triangle. Preferably, the triangle is symmetrical about a vertical line that lies on the pivot axis. The connecting line of the triangle, which runs from the axis of rotation of the first roller to the pivot axis, corresponds to the load arm of the bell crank. A base angle θ is enclosed between the connecting line of the axes of rotation and the load arm, which can be between 20 degrees and 50 degrees, in particular 25 degrees and 45 degrees or 30 degrees and 40 degrees. Other angles are conceivable.
[0045] Generally, a small base angle o is advantageous, although there are limits to determining the base angle. If the pivot axis is very close to the line connecting the axes of rotation, it may happen that a desired grinding gap or working gap between the rollers cannot be opened sufficiently wide. A working gap can be understood as either a grinding gap or a working gap. M / FLSM-016-PC 10
[0046] However, roller gaps that are larger than the intended grinding gap and are adjusted, for example, only for maintenance purposes, are also possible. In light of this, the limiting condition according to the equation is preferred.
[0047] V(a 2 +b 2 ) > d / 2+xl
[0048] This must be taken into account when selecting or determining the position of the pivot axis. The variables in the preceding equation are explained below.
[0049] a length of the load arm
[0050] b vertical distance between the pivot axis and the line connecting the rotation axes
[0051] d roller diameter
[0052] XL working gap, grinding gap
[0053] Compliance with the aforementioned limit condition does not yet account for a height offset at the roller contact point that occurs when the first roller, especially the loose roller, pivots around the pivot axis. To achieve the smallest possible height offset in the working gap, the length of the load arm should be chosen to be as large as possible. This, in turn, is countered by a very small base angle θ and / or a very small vertical distance between the pivot axis and the line connecting the axes of rotation. It has therefore been shown that a vertical distance of approximately 0.5 times the roller diameter of the first and / or second roller advantageously results in a small height offset.
[0054] It is possible that the vertical distance between the pivot axis and the line connecting the axes of rotation can be at least 0.4 times the diameter of the first and / or second roller. Alternatively, the vertical distance between the pivot axis and the line connecting the axes of rotation can be at least 0.6 times, and in particular 0.7, 0.8, or 0.9 times, the diameter of the first and / or second roller. The greater the vertical distance, the smaller the vertical displacement of the roller contact point caused by pivoting the first roller around the pivot axis.
[0055] In the roller device, the resultant of the grinding force acts approximately parallel or parallel to the axis-of-rotation connecting line of the two rollers imM / FLSM-016-PC 11
[0056] Roller contact point. The line connecting the axes of rotation is therefore preferably understood as the line of action of the grinding force. According to known displacement axioms, the grinding force can be shifted to the end of the load arm (assuming rigid bodies). This point coincides with the axis of rotation of the first roller. The actual effective length of the load arm corresponds to the vertical distance between the line connecting the axes of rotation and the pivot axis, since the grinding force acts orthogonally along this line. This applies to the case where the line connecting the axes of rotation runs horizontally.
[0057] The load moment on the load arm resulting from the grinding force then corresponds to the product of the grinding force and the distance. It should be noted that the actual effective length of the load arm is by no means constant over the swivel range of the first roller. Rather, the vertical distance from the swivel axis to the line connecting the rotation axes changes with the respective swivel position within a specific range, which depends on the set working gap or grinding gap.
[0058] According to a secondary aspect, the invention relates to a system with at least one roller device according to the invention, and at least one basic structure, in particular a base frame, a base plate or a base rack, and / or a foundation on which the roller device is attached, in particular by force and / or material connection, wherein the actuating unit for introducing an actuating force into the force arm of the angle lever is supported on the basic structure and / or the foundation.
[0059] The advantages of the system are described in relation to the advantages explained in connection with the roller device. In addition, the system may alternatively or additionally possess one or a combination of several of the features previously mentioned in relation to the roller device.
[0060] The invention is explained in more detail below with reference to the accompanying drawings. The illustrated embodiment represents an example of how the roller device or roller system according to the invention can be designed.
[0061] These show M / FLSM-016-PC 12
[0062] Fig. 1 shows a side view of a roller system with a roller device according to a preferred first embodiment of the invention in schematic representation; and
[0063] Fig. 2 shows a top view of the roller system with the roller device according to Fig. 1.
[0064] In the following description, the same reference numbers are used for identical or equivalent parts.
[0065] Figures 1 and 2 show a roller device 1 according to a preferred embodiment of the invention. The roller device 1 is designed as a roller mill and serves for crushing or grinding mined material, preferably in mining. Mined material can be understood to be any type of rock or mineral. For example, the mined material can include limestone, ore, and / or a variety of other materials.
[0066] As can be seen in Figures 1 and 2, the roller assembly 1 comprises a first roller unit 200 and a second roller unit 300. The first roller unit 200 includes a first roller 2, and the second roller unit 300 includes a second roller 3. The roller units 200 and 300 each have two roller bearings 100, which rotatably support the respective roller 2 and 3 about their axes of rotation 5 and 11. The roller bearings 100 movably accommodate the roller ends of the rollers 2 and 3. Each roller bearing 100 has a bearing housing 101, which is a bearing block 4 and 10. The bearing blocks 4 and 10 will be discussed in more detail later.
[0067] The roller assembly 1 further comprises a pivot bearing 400 for pivoting the two roller units 200, 300. The pivot bearing 400 has a pivot axis 6 located between the axes of rotation 5, 11 of the two rollers 2, 3. The two roller units 200, 300 are coupled to the pivot bearing 400 such that they are pivotable about the pivot axis 6. The roller units 200, 300, in particular the two rollers 2, 3, thus have the same pivot axis 6. This can be referred to as the common pivot axis 6 of the roller units 200, 300. The rollers 2, 3 are therefore arranged opposite each other on the pivot axis 6. M / FLSM-016-PC 13
[0068] Fig. 1 shows that the pivot axis 6 of the pivot bearing 400 is located below the rotation axes 5, 11 of the two rollers 2, 3 in the installed position of the roller device 1.
[0069] The first roller 2, in particular the entire first roller unit 200, is pivotable about the pivot axis 6 when the roller device 1 is in operation. This also applies when the roller device 1 is at rest. The second roller 3, in particular the entire second roller unit 300, however, is only pivotable about the pivot axis 6 when the roller device 1 is at rest. The first roller 2 is therefore adjustable about the pivot axis 6 during operation, while the second roller 3 is fixed in position during operation. Thus, only the position of the first roller 2 relative to the second roller 3 can be adjusted during operation. The first roller unit 200 is coupled to an actuating unit 9, which will be discussed in more detail later.
[0070] The first roller 2 can be referred to as a floating roller or free roller due to its pivotability during operation, and the second roller 3 as a fixed roller or free roller. For the sake of simplicity, the first roller 2 will be referred to as the floating roller and the second roller 3 as the fixed roller in the following. The floating roller 2 and the fixed roller 3 each have a floating bearing side 21 and a fixed bearing side 22, respectively, with the floating and fixed bearing sides 21, 22 being arranged opposite each other on the rollers 2, 3 in the direction of rotation.
[0071] Figure 2 shows that a first bearing block 4a, 10a of the rollers 2, 3 is arranged on a fixed bearing side 22 and a second bearing block 4b, 10b on a floating bearing side 21 of the rollers 2, 3. The two first bearing blocks 4a, 10a are arranged opposite each other, in particular directly, on the pivot axis 6. Furthermore, the two second bearing blocks 4b, 10b are arranged opposite each other, in particular directly, on the pivot axis 6.
[0072] The bearing blocks 4, 10 are each preferably formed in one piece. In other words, the bearing block 4, 10 is monolithic. Or, put another way, the bearing block 4, 10 is formed in one piece. The bearing block 4, 10 is preferably a casting. The bearing block 4, 10 is made of a metallic material. The bearing blocks 4 of the first rolling unit 200 are identical, and the bearing blocks 10 of the second rolling unit 300 are identical. It is possible that the bearing blocks 10 of the second rolling unit 300 can be identical to the bearing blocks 4 of the first rolling unit 200. M / FLSM-016-PC 14
[0073] As can be clearly seen in Figures 1 and 2, the bearing blocks 4, 10 of the roller bearings 100 have a pivot arm 18, 19 by which the bearing blocks 4, 10 are connected to the pivot bearing 400. Consequently, the rollers 2, 3 are coupled to the pivot bearing 400 by the pivot arms 18, 19 of the bearing blocks 4, 10. The pivot arm 18, 19 is an integral part of the bearing block 4, 10.
[0074] In Fig. 1, it is clearly visible that the pivot arms 18, 19 of the first and second bearing blocks 4, 10 extend between the axis of rotation 5, 11 of the associated rollers 2, 3 and the pivot axis 6. The pivot arms 18 of the bearing blocks 4a, 4b of the loose roller 2 and the pivot arms 19 of the bearing blocks 10a, 10b of the fixed roller 3 extend in opposite directions with respect to the pivot axis 6. Specifically, Fig. 1 shows that the pivot arms 18, 19 extend from the axes of rotation 5, 11 of the rollers 2, 3 towards the pivot axis 6 of the pivot bearing 400.
[0075] Fig. 2 shows a top view of the roller assembly 1, in which it can be seen that the rollers 2, 3 of the two roller units 200, 300 run parallel. In other words, the axes of rotation 5, 11 of the two rollers 2, 3 run parallel. The pivot axis 6 is also parallel to the axes of rotation 5, 11 of the rollers 2, 3.
[0076] Fig. 2 shows that the roller assembly 1 comprises an actuating unit 9 on each side 21, 22 of the first roller assembly 200. Specifically, a first actuating unit 9 is arranged on the floating bearing side 21 and a second actuating unit 9 on the fixed bearing side 22. The actuating units 9 are identical. In the following, one of the actuating units 9, its connection to the bearing housing 101 of the first roller assembly 200, and the force transmission via the bell crank 8 are described by way of example with reference to Fig. 1. The bell crank 8 is shown in dashed lines in Fig. 1.
[0077] Fig. 1 shows that the actuating unit 9 interacts with the loose roller 2 via an angle lever 8 to move the loose roller 2 about the pivot axis 6. The actuating unit 9 comprises a hydraulic cylinder 14, which transmits a stroke to the bearing block 4 of the second roller unit 200. For this purpose, the hydraulic cylinder 14 is connected to the bearing block 4. The hydraulic cylinder 14 serves to introduce a pressure force or actuating force F. B into the bearing block 4. Specifically, the hydraulic cylinder 14 engages at a force application point 7 on the M / FLSM-016-PC 15
[0078] Bearing block 4, on which the hydraulic cylinder 14 exerts an actuating force F B introduces into bearing stone 4.
[0079] As can be seen in Fig. 1, the axis of rotation 5 of the loose roller 2 is located horizontally between the point of force application 7 and the pivot axis 6. Furthermore, it can be seen that the point of force application 7 lies vertically between the axis of rotation 5 of the loose roller 2 and the pivot axis 6. The point of force application 7 lies on a vertically oriented median plane ME of the bearing block 4, which is oriented orthogonally to the pivot axis 6 and / or axis of rotation 5 of the loose roller 2.
[0080] Fig. 1 shows that the bell crank 8 has a force arm 12 and a load arm 13 that merge into one another at the pivot axis 6. The force arm 12 and the load arm 13 are straight. The force arm 12 extends from the point of force application 7, in particular transversely, to the pivot axis 6. The load arm 13 extends from the pivot axis 6, in particular transversely, to the axis of rotation 5 of the loose roller 2. The force arm 12 and the load arm 13 of the bell crank 8 have a length ratio of 2:1 to 3:1. In other words, the force arm 12 can have a length L F exhibiting lengths that are two to three times the length of the load arm 13.
[0081] An angle β of less than or equal to 45 degrees is enclosed between the force arm 12 and the load arm 13. The angle β between force and load arms 12, 13 can therefore be up to 45 degrees. Alternatively, the angle β could be up to 40 degrees, up to 35 degrees, up to 30 degrees, up to 25 degrees, or up to 20 degrees. In other words, the angle β can lie within a range of 20 degrees to 45 degrees, specifically 25 degrees to 40 degrees or 30 degrees to 35 degrees. Other values for the angle β, within a range of, for example, 10 degrees to 45 degrees, are also possible.
[0082] The angle lever 8 is an integral part of the bearing block 4. In other words, the angle lever 8 is not a separate lever, but is formed by the bearing block 4. The force and load arms 12, 13 run, at least partially, within the pivot arm 18 of the bearing block 4. The force arm 12 and the load arm 13 are shown as dotted lines in Fig. 1 to illustrate the path of the angle lever 8 within the bearing block 4. M / FLSM-016-PC 16
[0083] Fig. 1 further shows that the axes of rotation 5, 11 of the two rollers 2, 3 and the pivot axis 6 are arranged such that their connecting lines lying in the median plane ME form a triangle TR, wherein the vertical distance b of the pivot axis 6 to the line connecting the axes of rotation L running between the two axes of rotation 5, 11 wThis corresponds approximately to 0.5 times the roller diameter of the loose and fixed rollers 2, 3. It should be noted that Fig. 1 is a schematic representation of the roller assembly, not to scale.
[0084] The intersection of the pivot axis 6 with the median plane ME forms a first point PI, which is the apex of triangle TR. The axes of rotation 5, 11 of the two rollers 2, 3 are arranged opposite each other on the pivot axis 6. The intersection of each axis of rotation 5, 11 with the median plane ME forms a further vertex P2, P3 of triangle TR. Preferably, triangle TR is symmetrical about a vertical line that lies on the pivot axis 6. The connecting line LI of triangle TR, which runs from the axis of rotation 5 of the loose roller 2 to the pivot axis 6, corresponds to the load arm 13 of the bell crank 8.
[0085] Between the axis of rotation connecting line L wA base angle θ is included between the load arm 13 and the load arm 13, and this angle can be between 20 degrees and 50 degrees, in particular between 25 degrees and 45 degrees or between 30 degrees and 40 degrees. Other angles are conceivable. The sum of the base angle θ and the angle β is preferably less than 90 degrees. It is also possible for the sum of the base angle θ and the angle β to be equal to 90 degrees.
[0086] Fig. 1 further shows that a grinding force F occurring or applied during operation is located on the axis-connecting line L. wThe line connecting the axes of rotation Lw can therefore be considered the line of action of the grinding force F. Furthermore, a roller contact point PK is located on the line connecting the axes of rotation Lw, where the roller contact point PK is the point (which can also be linear) at which the rollers 2, 3 are in contact when the grinding gap xO or working gap xl is equal to 0. In Fig. 1, however, a grinding gap xO or working gap xl is shown, i.e., the rollers 2, 3 are separated from each other.
[0087] Fig. 1 further shows that the hydraulic cylinder 14 is arranged and aligned such that an actuating force F applied by the hydraulic cylinder 14 is present at the point of force application 7. B into the power arm 12 imM / FLSM-016-PC 17
[0088] The force is introduced essentially orthogonally. In other words, the hydraulic cylinder 14 is designed such that the line of action of the applied or to-be-applied actuating force F Bessentially runs orthogonally to the force arm 12. Since the loose roller 2 is moved about the pivot axis 6 by the hydraulic cylinder 14 during operation, in order to generate an actuating force F that counteracts the grinding force F, B To introduce into the force arm 12 and, on the other hand, to adjust the grinding gap xO or to maintain its presetting, it is possible for the hydraulic cylinder 14 to change its position so that the actuating force F B is initiated with a slight deviation. For example, the actuating force F B The force arm 12 is introduced at an angle of 80 to 100 degrees or 85 to 95 degrees, particularly preferably at an angle of 89 to 91 degrees.
[0089] The use of the hydraulic cylinder 14 as an actuating unit 9 has the advantage that a reliable and cost-effective position measuring device 21 can be used to determine the position of the loose roller 2 with respect to the pivot axis 6. The measuring device 15 can be integrated into the hydraulic cylinder 14 or arranged externally on the hydraulic cylinder 14.
[0090] The hydraulic cylinder 14 is connected on one side to the bearing block 4 of the loose roller 2 and on the other side to a counter bearing that supports the hydraulic cylinder 14. In other words, the hydraulic cylinder 14 comprises two joints which, depending on the operating position of the loose roller 2, enable a substantially orthogonal force transmission into the force arm 12 of the bell crank 8. Due to the articulated connection of the hydraulic cylinder 14 to the bearing block 4, the orientation of the hydraulic cylinder 14 changes depending on the stroke.
[0091] Figure 1 further shows that the roller assembly 1 has a counter bearing 17 on which the second roller unit 300 is supported. The counter bearing 12 serves to support the second roller unit 300 or the fixed roller 3. The counter bearing 17 is in turn connected to a foundation 500 to transfer the forces introduced by the second roller unit 300. The pivot bearing 400 is also mounted on the foundation 500. Preferably, the pivot bearings of the pivot bearing 400 are connected to the foundation 500 by force-fit and / or material bonding. Alternatively, the pivot bearings of the pivot bearing 400 can be connected to a base structure, e.g., a base frame, a base M / FLSM-016-PC
[0092] plate or a base frame, connected by force and / or material bonding, in particular screwed and / or welded, a.M / FLSM-016-PC
[0093] 19
[0094] List of references
[0095] 1 roller device
[0096] 2 first roller
[0097] 3 second roller
[0098] 4 bearing blocks of the first roller unit
[0099] 4a Bearing block of the first roller unit on the fixed bearing side 4b Bearing block of the first roller unit on the floating bearing side 5 Axis of rotation of the first roller
[0100] 6 swivel axes
[0101] 7 Force application point
[0102] 8 angle levers
[0103] 9 Actuating unit
[0104] 10 bearing blocks of the second roller unit
[0105] 10a Bearing block of the second roller unit on the fixed bearing side 10b Bearing block of the second roller unit on the floating bearing side 11 Rotation axis of the second roller
[0106] 12 Power arm
[0107] 13 Load arm
[0108] 14 cylinders
[0109] 15 Measuring device
[0110] 16 bearing housings
[0111] 17 counter bearings of the second roller
[0112] 18 swivel arms of the first roller unit
[0113] 19 swivel arms of the second roller unit
[0114] 21 Loose storage side
[0115] 22 Fixed bearing side
[0116] 100 roller bearings
[0117] 200 first roller unit
[0118] 300 second roller unit
[0119] 400 swivel bearing
[0120] 500 foundation
[0121] ME vertical mid-level
[0122] F B Actuating force
[0123] F MahlkraftM / FLSM-016-PC
[0124] 20
[0125] a base angle
[0126] β Angle between force arm and load arm
[0127] b vertical distance
[0128] L w Rotation axis connecting line of the rollers L F Length of the power arm
[0129] LI connecting line
[0130] PI first point
[0131] P2, P3 Key points
[0132] PK roller contact point
[0133] TR Triangle
Claims
M / FLSM-016-PC FLSmidth A / S JK / PW Roller device for grinding input material, in particular mining material, and roller system Claims 1. Roller device (1) for grinding input material, in particular mining material, comprising: a first roller unit (200) with a first roller (2), in particular a loose roller, and a second roller unit (300) with a second roller (3), in particular a fixed roller, wherein the two rollers (2, 3) each have an axis of rotation (5, 11); - at least one pivot bearing (400) which pivotably supports the two roller units (200, 300), wherein the pivot bearing has a pivot axis (6) located between the axes of rotation (5, 11) of the two rollers (2, 3), about which the rollers (2, 3) are movable; and - at least one actuating unit (9) which interacts with the first roller (2) by means of at least one bell crank (8) to move it about the pivot axis (6), wherein the bell crank (8) comprises at least one force arm (12) and at least one load arm (13), wherein the force arm (12) extends from a force application point (7) of the actuating unit (9) to the pivot axis (6) and the load arm (13) extends from the pivot axis (6) to the axis of rotation (5) of the first roller (2), characterized in that the force arm (12) extends at an angle β to the load arm (13) enclosed between the force arm and the load arm (13), which is less than or equal to 45 degrees, and the actuating unit (9) is arranged and aligned such that an actuating force (F) is applied at the point of force application (7). B ) can be introduced essentially orthogonally into the force arm (12). M / FLSM-016-PC 2 2. Roller device (1) according to claim 1, characterized by the fact that the actuating unit (9) is arranged and aligned such that an actuating force (F) is applied at the point of force application (7). B ) can be introduced at an angle of 80 degrees to 100 degrees, in particular 85 degrees to 95 degrees, preferably 89 degrees to 91 degrees to the force arm (12).
3. Roller device (1) according to claim 1 or 2, characterized by the fact that the actuating unit (9) comprises at least one cylinder (14), in particular a hydraulic cylinder, and is oriented essentially orthogonally to the force arm (12).
4. Roller device (1) according to one of the preceding claims, characterized in that at least one measuring device (15) for distance measurement, in particular stroke measurement, is provided, which is arranged on or integrated into the actuating unit (9).
5. Roller device (1) according to one of the preceding claims, characterized in that The force arm (12) and the load arm (13) have a longitudinal ratio of 2:1 to 3:
1.
6. Roller device (1) according to one of the preceding claims, characterized in that The first roller unit (200) has at least one roller bearing for rotatably supporting the first roller (2) with a bearing housing (16), in particular a bearing block, wherein the angle lever (8), in particular the force and / or load arm (12, 13), is an integral part of the bearing housing (16).
7. Roller device (1) according to one of the preceding claims, in particular according to claim 6, characterized by the fact that the actuating unit (9) on one side with a / the bearing housing (16)M / FLSM-016-PC 3 the first roller unit (200) and on the other hand is articulatedly connected to a counter bearing supporting the actuating unit (9).
8. Roller device (1) according to one of claims 6 or 7 characterized in that the bearing housing (16) of the first roller unit (200) comprises a vertical median plane (ME) to which the pivot axis (6) is orthogonal, with the point of force application (7) on the force arm (12) lying in the median plane (ME).
9. Roller device (1) according to one of the preceding claims, characterized in that the axes of rotation (5, 11) of the two rollers (2, 3) and the pivot axis (6) are arranged such that their connecting lines lying in a plane, in particular the median plane (ME), form a triangle, wherein the vertical distance (b) of the pivot axis (6) to the line connecting the axes of rotation (L) running between the two axes of rotation (5, 11) w) corresponds to 0.4 to 0.7 times, in particular 0.5 times, a roller diameter of the first and / or second roller (2, 3).
10. System comprising at least one roller device (1) according to one of the preceding claims, and at least one basic structure, in particular a base frame, a base plate or a base rack, and / or a foundation (500) on which the roller device (1) is attached, in particular by force and / or material bonding, wherein the actuating unit (9) is designed to introduce an actuating force (F B ) supports the force arm (12) of the angle lever (8) on the basic structure and / or the foundation (500).