Apparatus and method for grinding input material

Abstract

The invention relates to a rolling device (10) for grinding an output material (M), comprising: a fixedly mounted fixed roller (2) having a roller axis (y2) mounted at least approximately in a fixed position; a loosely mounted loose roller (3) having a roller axis (y3) that can be arranged in a variable position; a frame (11) that supports at least the fixed roller and optionally the loose roller; at least one force application unit (15) that acts on the loose roller at a force application point (P2); wherein the fixed roller and the loose roller can be mounted and positioned relative to each other to apply a grinding force (F); wherein the loose roller (3) having a positionally variable roller axis (y3) is mounted to pivot about a pivot axis (P3) in the form of a one-sided lever (16) so that the relative position of the loose roller relative to the fixed roller can be defined by the pivoting movement, the one-sided lever (16) being formed between the pivot axis (P3) and the force application point (P2). This not only brings advantages in terms of design. In addition, the invention also relates to a corresponding method for grinding an input material.

Description

Technical Field

[0001] The invention relates to an apparatus and a method for grinding raw materials, in particular an apparatus in the form of a roller mill, which has a fixed roller mounted in a fixed manner and a floating roller mounted in a floating manner, which can be displaced relative to the fixed roller. In this respect, the rollers can be mounted and supported on a frame, in particular mounted and supported together on a common frame. In particular, this relates to a roller press apparatus in the form of a material bed roller mill for raw materials in the form of mineral or extracted materials. In particular, this relates to a so-called roller press, which, for example, has a drive power in the range of at least 200 kW to 5000 kW. Background Art

[0002] Raw materials such as limestone, clinker, ore or similar rocks are ground, for example, by means of roller presses. The rollers are usually mounted fixedly on the one hand and displaced in translation on the other hand. The hydraulic force exerted on the floating rollers mounted in a floating manner in the direction of the grinding gap causes a translational displacement of the contact point relative to the rollers or generates a force effect in the grinding gap. In particular, the floating rollers act at least at two points in the translation direction, also in order to be able to prevent torques.

[0003] In other words: A roller press usually comprises a fixedly mounted roller and a floating roller mounted in a floating manner, wherein the floating roller can be displaced in a translational manner relative to the fixed roller and the roller is mounted and supported in a frame. For example, a lower frame part and an upper frame part are provided, on each of which a (translational) sliding bearing for the floating roller is provided. In addition to the hydraulic actuator for the relative positioning of the floating roller relative to the fixed roller, additional stabilizing actuators are usually required.

[0004] In particular, in the case of relatively large roller presses and large forces and moments or impacts, it is not easy in terms of design to design a roller press for the widest possible range of operating conditions or different raw materials. The question of how the reaction force can or should be transmitted from the roller to the frame and to the stand constitutes a large number of engineering attempts. In this regard, the design requirements are also particularly high for a high degree of continuous loading. Regardless of its size, the roller press must also be as strong as possible in terms of tilting operation, overload or similar adverse effects. For example, in the case of many roller types, the precise settability and precise relative alignment of the roller axis therefore also remain important factors in selecting a favorable overall design concept. In particular, it must be possible to position the axis of the roller press as accurately as possible within the smallest narrow tolerance range, especially relative to each other. In other words: high dynamic continuous loads combined with a narrow tolerance range for the relative position of the rollers are based on high design requirements.

[0005] Therefore, the costs that must be invested in the conceptual design of the frame (support structure) and the support of the force introduction points and the consideration of favorable force flow paths are also relatively high. In particular, due to the fluctuating, sometimes unknown composition and hardness of the raw materials, the roller presses and bearings used are subject to very high loads and stresses even if they are designed with a large safety factor. For example, in existing equipment, skew operation cannot be effectively avoided in all cases, or a certain degree of skew operation desired within the narrowest possible tolerance limits cannot be set accurately enough. For example, this is a problem of skew operation of one of the axes (especially the contact axis) in the range of 0 to 10 millimeters (mm) or at most 15 mm. On the one hand, it is likely that a smaller degree of tilting operation is required (especially to compensate for the irregular impact of the material on the roller), and on the other hand, the tilting operation should not become too large, especially since this may adversely affect the grinding efficiency. This example clearly shows that the highest requirements are placed on the quality of the design, support and installation, especially when the roller press is in the higher performance range.

[0006] The drive power of roller presses, which tend to be relatively large and heavy, is, for example, in the range of 2 x 150-200 kW, i.e., for example, a total of 350 kW, but can also be significantly higher, for example, 2 x 3000 kW. In this respect, the spatial dimensions in each of the three spatial directions can be, for example, 2 to 4 meters. However, significantly larger or smaller structures can also be implemented or used; in particular, they can be scaled individually for the respective application, depending on the raw material to be processed. The invention is scalable to a large extent, regardless of the respective roller type; in particular, the invention has a particularly advantageous effect in the case of relatively large roller presses.

[0007] DE 10 2015 114 992 A2 describes a roller press for grinding grinding material, wherein the rollers are mounted in such a way that they can be replaced more easily, in particular when the line of action of the operating forces generated extends in a half space within the support structure, wherein the floating roller interacts with a pivot device which pivots around a pivot bearing in the form of a two-sided lever.

[0008] Likewise, DE 10 2015 114 998 A2 describes a roller press for grinding grinding material, wherein the rollers are mounted to simplify the replacement of floating rollers, in particular with a pivot axis of two side levers advantageously arranged below the force application point at one end of the lever, and the axis of the floating roller is below the pivot axis.

[0009] The floating rollers of these roller presses are therefore not mounted in a purely translational manner, but can be pivoted.

[0010] DE 37 24 742 A1 discloses a roller crusher having a fixed roller and a floating roller.

[0011] DE 32 24 249 A1 discloses a roller mill having two rollers with an adjustable roller gap.

[0012] GB 2 103 107 A discloses a fixing device for a grinding roller.

[0013] DE 38 18 540 A1 discloses a roller mill with an adjustable roller gap.

[0014] CN 104 998 714A discloses a machine having a driving roller and a driven roller connected to the central part of the circle center connecting line. The ends of the driving roller and the driven roller are coaxially connected to the end shaft. The pivot arm is mounted on the rotating shaft via the pivot shaft. The rotating shaft is mounted on the pivot bearing seat. The output shaft is connected to the reduction gear mechanism mounted on the pivot arm. The pivot arm pressure plate is connected to the top part of the machine frame and inflates the compressed air bag.

[0015] DE 10 2013 010 220 A1 discloses a high-pressure roller press having a pendulum suspension.

[0016] DE 10 2015 110 033 A1 discloses a material bed roller mill having two counter-rotating rollers and two roller holders pivotably connected to a machine frame.

[0017] Taking these different configurations as a starting point, there is interest in even more convenient configurations, especially for relatively large, high-capacity roller devices. Summary of the invention

[0018] The object of the invention is to provide an apparatus and a method having the features described in the introduction which make it possible to further optimize the grinding of the raw material or to use individual rollers in combination with one another for grinding the raw material in a particularly advantageous manner. In particular, a further object is to provide a robust apparatus which, even in the case of relatively high reaction forces and heavy loads, has a structural design which is as simple and robust as possible, which also makes it possible to reduce or even largely avoid skew running or to at least define the extent of skew running within very narrow tolerance ranges. Furthermore, there is also an interest in a solution which is as cost-effective as possible and has the simplest possible robust, durable system technical design.

[0019] According to the invention, this object is achieved in particular by a roller pressing device which is configured for grinding raw material, for example, in the form of a mineral grinding material, in particular in the form of a roller mill, in particular a material bed roller mill, which has: a fixedly mounted fixed roller, which has a roller axis which is at least approximately fixedly mounted; a floating roller which is mounted in a floating manner, which has a roller axis which can be arranged variably in a predefinable relative position with respect to the fixed roller; a frame on which at least the fixed roller and optionally the floating roller are mounted; at least one force application unit which acts on the floating roller at a force application point; wherein, in order to apply the grinding In order to apply a grinding force (rolling force generated in the grinding gap) and to contact each other at the roller contact point or to define a grinding gap for the raw material, the fixed roller and the floating roller can be mounted and positioned relative to each other, in particular by means of a force application unit; and wherein the floating roller with a variable position roller axis can be mounted so that it can be pivoted about a pivot axis in the manner of a one-sided lever against the fixed roller, so that the relative position of the floating roller (or the variable position roller axis) relative to the fixed roller can be defined in order to apply a grinding force due to this one-sided pivoting movement about the pivot axis, wherein the one-sided lever is formed between the pivot axis and the force application point. This provides a robust arrangement on the one hand and enables a relatively stress-free, variable positioning of the rollers relative to each other. In particular, a high efficiency, in particular an energy efficiency, can also be ensured. In this case, particularly high design requirements can also be met in an elegant, simple manner.

[0020] It has been shown that the pivotable mounting of the floating roller also offers great advantages in terms of force introduction and force application, in particular in the case of very large rollers. In particular, the forces provided (in particular hydraulic forces) can be utilized efficiently and effectively. In particular, the amount of force required and thus ultimately also the required energy can be minimized. Not least, due to the optimized power flow path, the device as a whole can also be given a narrower design, i.e. with less expenditure in terms of material and costs and overall weight. Conversely, the hydraulic forces to be installed can also be minimized; the expenditure on hydraulic fittings, pressure-resistant lines and adapters can be significantly reduced. In other words: the variable-position roller axis can be pivotally positioned in the grinding gap with relatively small actuation forces. In this case, the pivot axis in particular also defines the fulcrum of a one-sided lever. Here, the fixed-position roller axis can also optionally be completely fixed in position without any displacement mechanism being provided, i.e. for all possible operating conditions or operating states.

[0021] In this respect, in a broader sense, floating rollers are to be understood as meaning rollers which can be actively positioned relative to fixed rollers and which are also mounted in a positionally displaceable manner for relative displacement. Likewise, in this respect, fixed rollers are similarly to be understood as meaning rollers which are mounted in a positionally fixed manner and are not intended to be displaced. In special cases, which are described further below, fixed rollers can also be mounted in pivot bearings. The terms fixed mounting and floating mounting chosen here are independent of any mechanical or kinematic requirements for static / dynamic provisions. The terms chosen here are primarily intended to illustrate the two different roller types.

[0022] According to the invention, the pivot axis is arranged on the tangents of the fixed roller and the floating roller at the roller contact point, as long as there is a roller contact point due to the direct contact of the fixed roller and the floating roller due to the grinding gap being zero. If the grinding gap is not zero, the pivot axis is arranged between the intersection points between the tangents of the fixed roller at the intersection of the connecting line between the positionally fixed roller axis and the positionally variable roller axis and the tangent of the floating roller at the intersection of the positionally fixed roller axis and the positionally variable roller axis. In the context of the invention, between the tangents also includes being located on at least one tangent, which results in particular in the special case of a grinding gap of zero, since in this special case the two tangents coincide and the pivot axis is therefore arranged on two coinciding tangents. However, even in the case of a non-zero grinding gap, the pivot axis can in particular be located on the tangent of the fixed roller at the intersection of the connecting line between the positionally fixed roller axis and the positionally variable roller axis, since this would allow a grinding gap variable from zero. In particular, the grinding gap is small compared to the diameter of the fixed roller and the diameter of the dancing roller, and as a result the tolerance may include the assumption that the grinding gap is zero.

[0023] In the special case of interlocking fixed and floating rolls, the grinding gap can also assume negative values ​​and in this case is limited at most to the interlocking depth of the rolls.

[0024] In particular, the device according to the invention also enables the advantageous use of a frame. In particular, conventional, proven configurations and designs of frames can also be used for the device according to the invention.

[0025] The device according to the invention is preferably configured for a drive power in the range of at least 200 kW to 5000 kW. The bearings used are particularly configured for intercepting and transmitting the impact and reaction forces exerted on the rollers and bearings by the grinding material in the form of minerals or stones, etc. during grinding. Measures that are advantageous or feasible in terms of system engineering, process engineering and design may be dictated or restricted by the field of application. The person skilled in the art must also find measures that are particularly suitable for the desired field of application.

[0026] Advantageously, in the roller arrangement according to the invention, a (pure) mechanical suppression of the tilting roll can be dispensed with. It is also possible to at least partially dispense with hydraulic measures for suppressing the tilting roll. In particular, the arrangement according to the invention also offers the advantage that the tilting roll can be effectively reduced or even completely avoided simply by the way the rollers are mounted relative to one another and by the pivoting movement of the floating roller.

[0027] In this respect, a one-sided lever or a one-sided lever arrangement is understood to mean an arrangement in which only one end of the lever pivots and the lever is arranged on the other side in a pivot bearing. The loading arm and the force application arm coincide. In the case of a one-sided lever, only one end of the lever has a force acting on it. There is only one point of force application and pivoting the lever does not result in forces acting on the other end of the lever or in torque being generated at the other end of the lever. Instead, a rotary bearing for pivoting the lever about the rotary bearing is arranged at the other end (fulcrum). The action point or interaction point or mechanical interface is arranged on the line segment between the pivot bearing and the end of the lever. In other words: there is no opposite pivoting movement. In contrast, in the case of a two-sided lever arrangement, the two ends of the lever pivot relative to each other, i.e. one end performs a relative pivoting movement and the other end also performs a relative pivoting movement, with the result that the relative lengths of the two lever arms are important.

[0028] Each force application point is arranged, for example, on the bearing ring of the floating roller or between the bearing rings of the floating roller, and in the case of force action between the bearing rings, the bearing rings are preferably coupled, in particular in such a way that the hydraulic force can be transmitted to the bearing rings via the coupling. For example, a bearing bushing, a roller bearing or a similar rotating bearing element can be provided as a bearing ring. The bearing ring is particularly used to accommodate the bearing and transmit the reaction force to the bearing. The coupling between two or more bearing rings is not necessary. However, if tilting operation is to be completely prevented, coupling the bearing rings may be particularly advantageous. In particular, the coupling can be achieved, for example, by two bearing rings and at least one component for coupling being composed of a cast part. The coupling can also be achieved by connecting a steel pipe / steel frame (for example by screws) to the bearing rings. When the bearing rings are coupled, the force application point can be, for example, located between the two bearing rings, or in any case one force application point is provided for each bearing ring.

[0029] It has been shown that the use of multiple (at least two) hydraulic cylinders is particularly advantageous in individual applications, in particular each hydraulic cylinder is coupled to a bearing ring, with the result that each side or each bearing ring defines a force application point. This makes it possible to dispense with coupling the bearing rings to one another.

[0030] The invention is also based on the concept of using a one-sided lever arrangement to ensure that the floating roller is positioned relative to the fixed roller only by translational actuation. Rotational actuation movements or, for example, even the use of an eccentric is not necessary. Thus, according to the invention, a relatively narrow, simple design with relatively few interacting parts and few relative movements can be provided. As a result, design adaptations or scaling can also be performed in a simple manner.

[0031] In this case, the terms "fixedly mounted" and "mounted in a floating manner" relate in particular to the operating conditions for grinding the stock. In other words: During grinding, the fixed roller is usually not moved, but it can nevertheless be mounted in such a way that it can be moved, for example for assembly purposes. In contrast, usually only the floating roller is positioned for the grinding operation. Alternatively, however, the concept of the invention can also be transferred to two rollers mounted in a floating manner relative to each other.

[0032] According to an exemplary embodiment, the roller pressing device is in the form of a material bed roller mill. It has been shown that the advantages according to the invention described here can also be achieved particularly advantageously in the case of a material bed roller mill.

[0033] In another embodiment of the invention, the distance r between the pivot axis and the connecting line between the fixed roller axis and the variably arranged roller axis, along the connecting line between the fixed roller axis and the variably arranged roller axis at right angles and passing through the pivot axis, is dist Corresponding to the fixed roller radius r fixed and the floating roller radius r floatxing at least 0.15 times the sum of the fixed roller radius r fixed and the floating roller radius r floating The sum is at most 1 times. So the result is:

[0034] 0.15·(r fixed +r floating )≤r dist ≤1·(r fixed +r floating )

[0035] This makes the construction compact and stable.

[0036] The distance r between the pivot axis and the connecting line between the fixed roller axis and the variably arranged roller axis, along the connecting line between the fixed roller axis and the variably arranged roller axis at right angles and passing through the pivot axis dist Particularly preferably corresponds to the fixed roller radius r fixed and the floating roller radius r floating at least 0.2 times the sum of the fixed roller radius r fixed and the floating roller radius r floatingThe sum is at most 0.8 times. So the result is:

[0037] 0.2·(r fixed +r floating )≤r dist ≤0.8·(r fixed +r floating )

[0038] The distance r between the pivot axis and the connecting line between the fixed roller axis and the variably arranged roller axis, along the connecting line between the fixed roller axis and the variably arranged roller axis at right angles and passing through the pivot axis dist Very particularly preferably corresponds to the fixed roller radius r fixed and the floating roller radius r floating at least 0.25 times the sum of the fixed roller radius r fixed and the floating roller radius r floating The sum is at most 0.75 times. So the result is:

[0039] 0.25·(r fixed +r floating )≤r dist ≤0.75·(r fixed +r floating )

[0040] The distance r between the pivot axis and the connecting line between the fixed roller axis and the variably arranged roller axis, along the connecting line between the fixed roller axis and the variably arranged roller axis at right angles and passing through the pivot axis dist Even more particularly preferably corresponds to the fixed roller radius r fixed and the floating roller radius r floating at least 0.25 times the sum of the fixed roller radius r fixed and the floating roller radius r floating The sum is at most 0.6 times. So the result is:

[0041] 0.25·(r fixed +r floating )≤r dist ≤0.6·(r fixed +r floating )

[0042] In another embodiment of the invention, the distance between the pivot axis and the point of force application corresponds to 1 to 5 times the distance between the pivot axis and the connecting line between the fixedly mounted roller axis and the variably arranged roller axis, along a straight line at right angles to the connecting line between the fixedly mounted roller axis and the variably arranged roller axis and passing through the pivot axis. In other words, the virtual lever between the point of force application and the pivot axis is 1 to 5 times longer than the distance between the roller contact point and the pivot axis.

[0043] In another preferred embodiment of the present invention, the distance between the pivot axis and the point of force application corresponds to 1.5 to 4 times the distance between the pivot axis and the connecting line between the fixed roller axis and the variably arranged roller axis, along a straight line that is at right angles to the connecting line between the fixed roller axis and the variably arranged roller axis and passes through the pivot axis.

[0044] In another preferred embodiment of the present invention, the distance between the pivot axis and the point of force application corresponds to 1.5 to 3 times the distance between the pivot axis and the connecting line between the fixed roller axis and the variably arranged roller axis, along a straight line that is at right angles to the connecting line between the fixed roller axis and the variably arranged roller axis and passes through the pivot axis.

[0045] In another preferred embodiment of the present invention, the distance between the pivot axis and the point of force application corresponds to 1.75 to 2.75 times the distance between the pivot axis and the connecting line between the fixed roller axis and the variably arranged roller axis, along a straight line that is at right angles to the connecting line between the fixed roller axis and the variably arranged roller axis and passes through the pivot axis.

[0046] In another preferred embodiment of the present invention, the distance between the pivot axis and the point of force application corresponds to 2 to 2.5 times the distance between the pivot axis and the connecting line between the fixed roller axis and the variably arranged roller axis, along a straight line that is at right angles to the connecting line between the fixed roller axis and the variably arranged roller axis and passes through the pivot axis.

[0047] In another preferred embodiment of the present invention, the angle between the vector between the pivot axis and the force application point and the angle between the pivot axis and the connecting line between the fixed roller axis and the variably arranged roller axis, and the angle between the vector along the straight line that is at right angles to the connecting line between the fixed roller axis and the variably arranged roller axis and passes through the pivot axis is between 80° and 100°, preferably between 85° and 95°, and particularly preferably, the angle is 90°.

[0048] In another embodiment of the present invention, the grinding gap is not zero. In particular, the grinding gap can be set to a minimum value x during the grinding operation. 0,min With the maximum value x 0,max In this embodiment, the shortest distance between the pivot axes is preferably set at a minimum value x 0,min Half of the maximum value x 0,max The minimum value x 0,min It may particularly preferably be zero.

[0049] In another embodiment of the invention, the one-sided lever comprises a straight connection line between the force application point and the pivot axis. In the context of the invention, included here should be understood to mean that the straight connection extends within the mechanical lever. Thus, the force is directly guided and passes through the one-sided lever along a straight line. In particular, the one-sided lever is therefore not U-shaped or parabolic, resulting in the omission of a direct connection line between the force application point and the pivot axis.

[0050] In a further embodiment of the invention, the positionally variable roller axis passes through the one-sided lever.

[0051] In another embodiment of the present invention, the variably positioned roller axis is spaced apart from the straight line connecting line between the force application point and the pivot axis by at most 0.1 times the length of the straight line connecting line between the force application point and the pivot axis; the variably positioned roller axis is particularly preferably spaced apart from the straight line connecting line between the force application point and the pivot axis by at most 0.02 times the length of the straight line connecting line between the force application point and the pivot axis.

[0052] In a further embodiment of the invention, the force acts at the force application point at an angle of 75° to 105° relative to the connecting line between the fixed roller axis and the variably arranged roller axis. The force preferably acts at the force application point at an angle of 85° to 95° relative to the connecting line between the fixed roller axis and the variably arranged roller axis; the force particularly preferably acts at the force application point at an angle of 90° relative to the connecting line between the fixed roller axis and the variably arranged roller axis. The force particularly preferably acts from the bottom to the top. As a result, a particularly compact design is possible.

[0053] According to an exemplary embodiment, the roller contact point is arranged in the section between the force application point and the pivot axis and / or at a distance from the pivot axis that is less than the length of the one-sided lever, wherein the roller contact point defines the load arm of the one-sided lever. In this respect, the contact point defined by the raw material can also be understood to mean the roller contact point, i.e. with a relatively large grinding gap. Here, the roller contact point can also be understood to mean the effective force transmission point in the grinding gap.

[0054] According to an exemplary embodiment, the variable position roller axis can be displaced relative to the fixed roller on a curved movement path, in particular on a circular path. This also makes it possible, for example, to adjust the relative roller position in the grinding gap. In this respect, the variable position roller axis can be positioned relative to the fixed roller by a rotational actuation movement about a pivot axis.

[0055] According to an exemplary embodiment, the position-variable roller axis is arranged in a lever section which extends from the pivot axis between the force application point and the pivot axis, in particular at a distance from the pivot axis that is less than or equal to half the lever length. This also makes it possible to ensure a favorable force distribution. The pivot axis and the force application point can form a lever arrangement, wherein the floating roller can be positioned around the pivot axis in the form of a one-sided lever, wherein the roller contact point is arranged at an effective lever distance from the pivot axis that is less than or equal to half the lever length between the force application point and the pivot axis. This makes it possible to achieve a good force effect at the grinding point, in particular with relatively low forces at the point acting thereon.

[0056] According to an exemplary embodiment, the pivot axis is aligned at least approximately parallel to the fixed roller axis. Optionally, the pivot axis is aligned exactly parallel to the fixed roller axis and / or the variable roller axis.

[0057] According to an exemplary embodiment, the position-variable roller axis can be pivoted on a circular path about the pivot axis, in particular with an accurate circular movement path about an instantaneous center (instantaneous center in a broad sense, since the pivot axis does not necessarily have to be displaceable) arranged on the pivot axis. Optionally, the pivot axis or the corresponding pivot bearing can also be displaced in an additional translational manner. Optionally, the movement path is not a circular path but a curve, which is flattened due to the superimposed translation. The translational displacement can provide further options for adjusting operating parameters or for the relative arrangement of the roller axis. However, with regard to the size of the grinding gap, it is generally sufficient if the grinding gap can be changed in the region of only a few millimeters, which can already be ensured simply by pivoting.

[0058] The variable roller axis can be pivoted about a pivot axis so that the variable roller axis can be positioned relative to the fixed roller axis in at least two spatial directions (x, z), in particular with different x and z coordinates (or x and z positions) from the fixed roller axis. The variation in the z direction also offers the advantage that not only the size of the grinding gap but also the geometry of the grinding gap can be varied. In particular, the grinding stock can be advantageously ground even if the grinding stock is very inhomogeneous.

[0059] In this respect, bearing rings that are not coupled to one another can, for example, also be pivoted to different degrees, in particular in order to be able to set a tilting run or an effect corresponding to a tilting run. As a result, a grinding gap can be produced which does not extend parallel but opens differently from one end of the roller to the other. As a result of this measure, even in the case of non-coupled bearing rings, a variation of the run-away effect can occur.

[0060] According to an exemplary embodiment, the floating roller is pivotably mounted in the frame (or on the inner side of the frame) and supported on the frame. This makes it possible, for example, that the frame can also at least partially provide a frame or an interface for a frame. In this context, an arrangement in the frame is also to be understood as meaning an arrangement in which the frame is only arranged on one side in the z-direction, in particular only on the bottom side of the roller. In this context, an arrangement in the frame is also to be understood as meaning an arrangement in which the frame completely overlaps the roller in at least one spatial direction. Here, the pivot axis can be arranged at a distance from at least one of the roller axes that is less than or equal to the distance between the fixed bearing of the fixed roller and the position-fixed roller axis. This facilitates support in the frame. In addition, a favorable force distribution can be ensured even in the case of relatively short lever lengths.

[0061] According to an exemplary embodiment, at least one of the rollers is supported and mounted on the frame independently of the other roller, in particular in a plane passing through the grinding gap. This also provides an advantageous arrangement in terms of power flow and relative movement paths.

[0062] According to an exemplary embodiment, at least one of the rollers is supported in a plane passing through the grinding gap. More importantly, this also provides good variability in the arrangement of the force application points or the direction of action of the forces.

[0063] According to an exemplary embodiment, when the rollers are in contact at the roller contact point, the roller axes are arranged relative to the pivot axis in such a way that the connecting lines passing through the three axes in a plane extending orthogonally thereto form a triangle, in particular preferably at least approximately an isosceles triangle, preferably each base angle on the connecting lines between the roller axes is less than 50 degrees, in particular less than 45 degrees, preferably less than 40 degrees, further preferably less than 35 degrees. In other words: the three axes advantageously define an at least approximately isosceles triangle arrangement, in particular with the pivot axis as the vertex pointing downwards. Such a symmetrical arrangement of the roller axes relative to the pivot axis, wherein the pivot axis is at the smallest possible distance from the roller axis, also provides an advantageous leverage ratio and can simplify the design, in particular also allowing a common mounting (although preferably independent of one another) on the same pivot axis or at least approximately at the same position on the frame.

[0064] In this respect, the base angle of the triangular arrangement (e.g., isosceles triangle) can also vary within a range of about 15°, preferably only 10° or only 5° around the values ​​mentioned here. In particular, the base angle of the respective application can also be selected individually within a value range of 45° plus or minus 15°.

[0065] Here, the alignment (pivot angle alignment) of the one-sided lever may be less than 90°, in particular less than 45°, for example in the range of 20° to 40° relative to the horizontal plane. According to a variant, the pivot angle alignment corresponds to the base angle of the triangular arrangement.

[0066] According to an exemplary embodiment, the pivot axis is arranged below the stationary roller axis, in particular at a distance of at most half the roller diameter (the maximum distance corresponds to the radius of the fixed roller and / or the floating roller). This also provides an advantageous arrangement with regard to the interaction of the effects of force and gravity.

[0067] The one-sided lever arrangement is advantageously configured in such a way that the gravity acting at the roller center of gravity or at the center of gravity of the entire pivotable arrangement reacts to the action of the force. In other words: the load arm of the one-sided lever is defined on the one hand by the reaction force at the roller contact point and on the other hand also by the gravity acting at the center of gravity. The floating roller is therefore mounted on one side about the pivot axis so that both the reaction force at the roller contact point and the gravity counteract the action of the force acting at the point (on the lever arm). This provides good responsiveness and can also improve the grinding conditions, in particular supporting the return movement under the action of gravity (the grinding gap becomes larger). In particular, since gravity resets the roller or tends to open the grinding gap rather than close it, a device for opening the gap can also be omitted (minimizing the expenditure on equipment engineering).

[0068] According to an exemplary embodiment, the floating roller is pivotably mounted and arranged in such a way that the weight force acting at the center of gravity of the floating roller acts on the load arm of the one-sided lever in the direction of the return movement, thereby enlarging the grinding gap. This also makes it possible to achieve a favorable grinding behavior. In particular, good reactivity can be ensured and blocking or clogging situations, for example in the case of particularly hard or large raw materials, can be effectively avoided.

[0069] According to an exemplary embodiment, the floating roller or the variable position roller is aligned at least approximately parallel to the fixed roller axis and is mounted in (at least) two bearing rings, wherein the bearing ring of the floating roller is fixed so that it can rotate at one point (in particular about the pivot axis) and is coupled at another point (coupling point or support point). This optional coupling of the bearing rings also enables it to operate particularly effectively against deflection. In this case, the further point (coupling point or support point) is preferably arranged spaced apart from the pivot axis.

[0070] In this case, the coupling can be realized mechanically or hydraulically, in particular by means of transverse struts, cast elements and / or torsion shafts (mechanical), or by means of transverse hydraulic cylinders (hydraulic).

[0071] According to an exemplary embodiment, a hydraulic cylinder (component of a force unit) acting or aligned in the longitudinal direction is provided for each bearing ring for subjecting the floating roller to a force. The hydraulic cylinder of the force unit acting on the bearing of each roller can be connected on the oil side. The force unit can include a hydraulic cylinder, which acts or is arranged between the two bearing rings of the floating roller. The bearing ring of the (each) roller can include a guide in the longitudinal direction of the bearing ring. The guide serves in particular to keep the bearing ring in a predetermined plane, in particular with regard to rotation, in particular in order to avoid twisting of the bearing ring (axial forces in the x-direction also act on the roller). In this regard, the guide can stabilize or strengthen the parallelogram arrangement of the bearing rings of the floating roller.

[0072] According to an exemplary embodiment, the floating roller can be hydraulically acted on one side tangentially around the floating roller at another point (force application point) above or below the roller axis, so that the hydraulic action causes a torque about the pivot axis and in the process defines the grinding / rolling forces.

[0073] According to an exemplary embodiment, the force application points and the pivot axis as well as the fixed bearing for the fixed roller are geometrically arranged so that the connecting line passing through these points or components or the enclosed area correspondingly defined by these points geometrically extends over a horizontal distance of up to twice the roller diameter of the roller (or the diameter of a relatively larger roller) and a vertical distance of up to 1.5 times the roller diameter of the roller, in particular up to 1.2 times the roller diameter of the roller, in particular the peripheral contour of the corresponding area orthogonal to the pivot axis in the connecting line (contour, profile) or cross section is in the form of a triangle or a quadrilateral, each having a corner angle of less than 180°.

[0074] This way of combining individual components in the frame (or at least laterally on one side of the frame) also provides a compact and robust design. However, with regard to the force introduction direction and the relative distances and lever ratios, a wide range of variations can still be ensured here, which is advantageous in this respect. In the case of a fixed roller mounted on a pivot axis, special cases can also occur in which the bounded area is almost linear (i.e. very flat) or, depending on the vertical arrangement of the pivot axis (vertical position), presents a very flat, wide triangular geometry with a base angle of only a few degrees. In other words: the introduction of forces and the interception and transmission of reaction forces can be kept locally within a very narrow area (in particular only on one side of the frame), or the area defined by the force points and the bearing points is at least very compact and can be reduced to an advantageous geometric basic shape, which allows a compact, stable frame.

[0075] Therefore, according to one of the practicable variants, the invention is also based on the concept of forming a force triangle with an advantageous lever length and having an advantageous arrangement of the force introduction points, wherein the supporting forces and the reaction forces are likewise transmitted to the force triangle. In this respect, the longest side of the force triangle can be provided by a one-sided lever extending between the pivot axis and the action of the force.

[0076] According to an exemplary embodiment, the roller contact point, the force application point and the pivot axis are arranged relative to one another in such a way that a leverage ratio of the distance between the force application point and the pivot axis to the distance between the force application point and the roller contact point can be set to at least 2 times. The variable position roller axis, the force application point and the pivot axis can be arranged relative to one another in such a way that a leverage ratio of the distance between the force application point and the pivot axis to the distance between the variable position roller axis and the pivot axis can be set to at least 2 times. In particular, this arrangement also provides for a high effectiveness and efficiency.

[0077] According to an exemplary embodiment, at least the floating roller is dimensioned and / or arranged in the frame in such a way that a free space is ensured relative to the frame in the z-direction. The size of the structure displaced with the floating roller in the z-direction can be smaller than the size of the fixed mounting structure of the fixed roller in the z-direction. This makes it possible, in particular, to also provide a free space that facilitates a wider range of movement / pivoting.

[0078] According to an exemplary embodiment, the floating roller is acted on at a single point of action or at least a single radial distance in a tangential direction about the roller axis and about the pivot axis, in particular in a (hydraulic) direction of action at least approximately orthogonal to the roller axis, in particular in a vertical (z) or horizontal (x) direction of action in the case of a horizontally aligned roller axis and a horizontally aligned plane (xy) passing through the roller axis.

[0079] According to an exemplary embodiment, the floating roller can be positioned so that it can be pivoted about a pivot axis relative to the fixed roller, in particular by setting a (preferably hydraulic) force at a point of action that is aligned at least approximately tangentially on one side. In other words: the force applied is inclined relative to the roller axis.

[0080] According to an exemplary embodiment, the floating roller can be freely positioned in the frame at least in one pivot direction, in particular at least relative to the frame part on the bottom side or additionally relative to the frame part on the top side of the frame. In particular, the frame part on the bottom side can be directly coupled to the frame.

[0081] According to an exemplary embodiment, the floating roller is mounted such that it can pivot about a pivot point (pivot axis) which is arranged in a plane directly below or directly above the roller contact point of the fixed roller and the floating roller, i.e. directly in the middle between the two roller axes. In other words: the pivot axis is arranged vertically with respect to the grinding gap. This also provides design advantages, especially with regard to the mounting of the fixed roller.

[0082] The roller pressing device is advantageously configured to initiate the pivoting movement only by translational actuation or force action, i.e. without torque or rotational actuation movement. In particular, the force is caused to act on the roller at least approximately in an orthogonal and / or parallel direction with respect to the reaction force (contact force). Not only that, this also provides relatively simple and robust kinematics.

[0083] According to an exemplary embodiment, the pivot axis is arranged in a plane extending parallel to the roller axis, in particular in a plane passing through the grinding gap or precisely through the roller contact point, in particular in a plane extending in the vertical direction. This arrangement, which is symmetrical at least in the x-direction with respect to the roller axis, offers advantages in terms of supporting the rollers and the flow of forces, in particular even in the case of rollers of at least approximately the same size. The z position in the vertical direction can be selected to a large extent freely, in particular with regard to a particularly advantageous frame design and / or an optional common support of the two rollers on the pivot axis.

[0084] Optionally, the floating roller can be positioned / positioned relative to the fixed roller such that the pivot axis is arranged in the x-portion between the grinding gap (or roller contact point) and the roller axis of the floating roller (i.e. offset in the x-direction towards the position-variable roller axis), in particular at an x-distance from the position-variable roller axis of at least 2 / 3 of the x-distance between the axis of the position-variable roller and the roller contact point or the grinding gap (in particular at an x-distance of at least 2 / 3 of the floating roller radius), preferably at least 3 / 4 of this x-distance. This also provides for advantageous force ratios. In other words: the symmetrical x-arrangement of the pivot axis in the grinding gap can also be optionally varied, in particular by means of an x-offset in the direction of the position-variable roller axis.

[0085] The force triangle that can be realized by the arrangement according to the invention is formed by the points P1, P2 and P3. The arrangement of the respective roller axes is not very important here. However, it can be mentioned that the area spanned by the force triangle preferably covers only the floating roller (or its cross-sectional area) and the roller axis of the floating roller is optionally surrounded by the force triangle. The dimensional aspects can also be taken into account when selecting the lever ratio. The larger the distance P2 / P3 is selected relative to the distance P1 / P3, the smaller the configuration of the hydraulic cylinder or force introduction actuator can be. However, in this case, the load at the point P3 also increases. A ratio of at least about 1 to 2 is preferred, especially if the number of cylinders (actuators) should be as low as possible (in particular, it should be half the number of the prior art, i.e., in particular in the case of translational actuation). In many cases, the cost aspect is also very important, so that the ratio of the distances can also be optimized in terms of cost. If the design costs of the mounting point P3 rise to a greater extent than the costs of the cylinders, the ratio is selected to be smaller (if any), and vice versa. In this respect, in individual cases, the ratio can also be selected, for example, in the range of 1:1 to 1:3, in particular 1:1.5 to 1:2.5, preferably 1:2. Depending on the preferred boundary conditions, a person skilled in the art will be able to find the optimal solution for the respective application based on the present disclosure.

[0086] It has been shown that the contact line of the two rollers (absence of stock in the grinding gap) or the center line (central longitudinal axis) of the grinding gap exhibits minimal changes in height when the pivot axis is arranged close to the grinding gap in the x-direction. This more or less rectilinear (in the z-direction) arrangement of the center of the grinding gap and the pivot axis makes it possible to keep the two roller axes at least approximately in the same vertical position, even when the gap width varies. In this case, the grinding gap thus opens as horizontally as possible, which is also advantageous for feeding material from above (stock fed under gravity).

[0087] According to an exemplary embodiment, the force is applied (preferably hydraulically) about the pivot axis by at least one plunger, in particular by a plunger with a tilting device, in particular by a plunger with a hydraulic adjuster as a tilting device. This also facilitates the adjustment of the hydraulic force and the most precise positioning possible. The force application unit may comprise, for example, at least one plunger or a plunger piston or a valve piston. In particular, in the case of a pivot mechanism, the plunger also offers the advantage of a particularly compact design. However, the cylinder type can be selected individually in each case in order to be optimized for the case of use.

[0088] According to an exemplary embodiment, the pivot axis is arranged on the frame, in particular in a pivot bearing integrated in the frame, in particular on the frame part on the bottom side. More importantly, this also provides design advantages and has a favorable effect on the force flow / torque flow.

[0089] The fixed roller can, for example, be mounted in at least one bearing having the same z-coordinate as the pivot axis.

[0090] According to an exemplary embodiment, the fixed roller is mounted, in particular fixedly mounted, at least on the frame part on the bottom side of the frame and optionally also on the frame part on the top side of the frame. In other words: Optionally, the fixed roller can also be supported only on one side in the z-direction. These possible variations, in particular compared to translational sliding bearings, also allow a single design concept for a variety of applications without restricting optimization measures.

[0091] According to an exemplary embodiment, the pivot axis is arranged at a distance (in particular the z-distance or vertical distance) from the fixed and / or variable roller axis in at least one spatial direction which is less than or equal to the radius of the fixed roller and / or the floating roller, in particular less than 0.8 times or less than 0.7 times the radius of the floating roller. This also provides an advantageous force distribution.

[0092] According to an exemplary embodiment, at least one fixed bearing of the fixed roller is arranged at the level of the pivot axis (same z-coordinate). It has been shown that this makes it possible to minimize moments, in particular forces in the x-direction (grinding forces or reaction forces in the grinding gap). This also facilitates an advantageous frame design.

[0093] According to an exemplary embodiment, the fixed roller is mounted in at least one bearing which has the same z-coordinate as the pivot axis, i.e. in the same vertical position. In particular, this provides an advantageous design arrangement even if the frame has only one side. The fixed bearing can also be configured in the manner of a stop for the pivoting movement or comprise a stop; in this case, the fixed bearing primarily serves as a stop.

[0094] The design configuration with fixed bearings arranged at the level of the pivot axis for generating reaction forces offers advantages in terms of force distribution and load on the frame. The horizontal grinding forces generate horizontal reaction forces on the bearing rings of the floating roller and the fixed roller. In the case of a design arrangement in which the bearing rings can be connected to each other at or close to the pivot points, these reaction forces can be offset or compensated at these points. This means that other components, such as the base frame, can be relieved of load or, optionally, can also be given a narrower configuration (with corresponding cost advantages).

[0095] In particular, the pivot axis is arranged in a pivot bearing formed by a bearing part, which is configured for a corresponding pivoting movement, in particular for a pivoting movement within an angular range that makes it possible to set the gap between the two rollers up to 200 mm, in particular for a maximum gap size in the range between 80 mm and 200 mm, depending on the type series. For example, a spacer is screwed onto the base frame. Bolts guided through the bearing holes connect the bearing parts of the floating roller and the fixed roller. The pivot bearing bearing is configured, for example, as a maintenance-free or in particular low-maintenance pivot bearing with a woven Teflon fabric coating. During operation, the floating roller moves, for example, in a relatively small angular range between + / -1 mm and + / -5 mm. In this respect, the pivot bearing can be optimized for a load operating range of pivot angles in the range from + / -1 mm to + / -5 mm. At least under load, a relatively large pivot angle is not necessarily required.

[0096] The maintenance-free pivot bearing is preferably mounted in a pivot bearing housing. The housing is for example fixed (in particular screwed, welded) to the base frame. The pivot bearing can also be mounted in a bearing ring. The pivot axis is fixed on one or both sides, for example, by a bearing ring in the base frame.

[0097] The fixed roller is supported or mounted on the frame, in particular in the frame part on the bottom side. The fixed roller can also be optionally supported or mounted on the frame part on the top side.

[0098] Below is a description of particularly advantageous aspects which relate to the action of forces at least approximately orthogonal to the direction of gravity. In this respect, for example, forces are caused to act precisely in the horizontal direction. In the case of this type of force introduction, existing concepts can also be used. In other words: frames and actuators which have been used hitherto for the translational displacement of the floating roller can also be used optionally for the pivot mounting according to the invention, or existing devices can be converted or retrofitted.

[0099] According to an exemplary embodiment, the force is made to act in the same direction as the grinding force / rolling force (contact force between the rollers) generated, in particular the force action point is at least approximately at an effective lever distance which is at least twice as large as the lever distance between the pivot axis and the contact point of the rollers. This also makes it possible to ensure good efficiency and fine force measurability.

[0100] According to an exemplary embodiment, the lever force (in particular the hydraulic force) applied at the force application point is aligned at least approximately in the direction of the grinding force, in particular precisely in the direction of the grinding force, in particular in the horizontal direction of action. This makes it possible to set and adjust the action at the contact point of the roller particularly well.

[0101] Optionally, the hydraulic force deviates from the direction of the grinding force (contact force on the roller) by at most 40°, preferably at most 35°, further preferably at most 30° in the direction of action, in particular at least approximately parallel to the direction of action of the grinding force, in particular in the horizontal direction of action. This variability is advantageous, for example, when a wide range of grinding gap sizes is to be set.

[0102] Particularly advantageous aspects are described below, which relate to the action of a force at least approximately counter to the direction of gravity (parallel to the direction of gravity), in particular vertically upward, in which case the corresponding actuator can be supported on the frame or on the bottom frame part for this purpose.

[0103] According to an exemplary embodiment, a one-sided lever between the force application point and the pivot axis is formed by the relative arrangement of the roller contact point and the pivot axis and the force application point, so that the lever distance between the force application point and the pivot axis is greater than 2 times the distance between the position-variable roller axis and the pivot axis. The effective lever distance between the force application point and the position-variable roller axis can be greater than or equal to the effective lever distance between the position-variable roller axis and the pivot axis, in particular, greater than at least 1.2 to 1.5 times, for example 2 times. This also provides a good lever effect.

[0104] According to an exemplary embodiment, the floating roller is mounted by the action of an upward force, in particular a vertical upward force, in particular a contact force orthogonal to the roller contact point, opposing the weight force acting on the floating roller. In particular, this also provides good responsiveness with regard to the positioning of the floating roller; this can also promote gentle mounting and a longer service life. In this case, the lever length of the one-sided lever or force application arm can be selected largely freely.

[0105] According to an exemplary embodiment, the force application unit is supported on the bottom side of the frame, in particular in the frame part on the bottom side. Not only that, this also brings design advantages. In this respect, support on the bottom side is to be understood as meaning support below the roller axis. The frame part on the bottom side can be coupled to the frame / is coupleable to the frame. This also provides an advantageous force flow directly out of the frame, and the frame can thus be given a relatively narrow configuration.

[0106] According to an exemplary embodiment, the action of the force, in particular the hydraulic force, is not aligned in the direction of the grinding / rolling force, but at an angle greater than 45°, in particular at least 50°, preferably at least 55°, further preferably at least 60°, offset in the direction of action from the grinding / rolling force, in particular at least approximately orthogonal to the direction of action of the grinding / rolling force, in particular in the vertical (z) direction of action. In this case, the force is made to act on the floating roller, in particular only at the point of force action below the roller axis. This also allows the individual components to be advantageously arranged relative to each other in terms of design.

[0107] Particularly advantageous aspects are described below, in particular with regard to the action of forces at least approximately counter to the direction of gravity, in particular with a frame open at the top and / or with fixed rollers (also) mounted on a pivot axis. In the case of such an arrangement, the advantages of relatively direct introduction of forces into the frame can also be combined with the advantages of a cost-effective frame and good accessibility.

[0108] According to an exemplary embodiment, the fixed roller is mounted on a pivot axis, in particular about the same pivot axis as the floating roller, wherein in this case the fixed roller is prevented from pivoting in at least one fixed bearing, in particular in a fixed bearing (stop) for transmitting the grinding forces / roller contact forces. This also makes it possible to achieve a particularly narrow design, in particular without frame parts on the top side. In this special case, the term "fixed roller" is therefore interpreted to mean that the fixed roller is a roller on which the reaction forces caused by the forces acting on the floating roller are exerted. In this case, the fixed roller should not be displaced; however, it may also be advantageous to mount the fixed roller in a pivot bearing, although this mounting is intended to transmit the reaction forces into the frame without requiring a relative movement of the fixed roller (in particular by means of a stop).

[0109] In order to transmit the grinding forces / roller contact forces, the fixed roller can be supported in at least one fixed bearing at the same vertical coordinate as the pivot axis. In particular, the fixed bearing is configured to withstand forces in a circumferential direction around the pivot axis. In particular, the fixed bearing can also include a stop.

[0110] The fixed roller can also be mounted on the pivot axis. Not only that, this also has advantages in terms of compensating for grinding forces and bearing forces.

[0111] According to an exemplary embodiment, the frame is configured without frame sections on the top side and in particular comprises only at least one frame section on the bottom side on which the rollers are supported and mounted. In this case, both the floating roller and the fixed roller can be supported and / or mounted in a frame section extending only below the roller axis. This also ensures a favorable force / torque flow.

[0112] The features of the invention mentioned above relate to concepts that can be implemented in different variants, in particular depending on the configuration of the frame and / or the direction of action of the forces. It has been shown that the combination of the features described below can ensure a particularly large number of the above-mentioned advantages.

[0113] According to the invention, the above object is also achieved in particular by a roller mill (10), in particular in the form of a roller mill, which is configured to grind a raw material (M), the roller mill having:

[0114] - a fixedly mounted fixed roller (2) having an at least approximately fixedly mounted roller axis (y2);

[0115] - a floating roller (3) mounted in a floating manner, which has a roller axis (y3) which can be arranged in a variable position relative to the fixed roller;

[0116] - a frame (11) on which at least the fixed roller and optionally the floating roller are mounted;

[0117] - at least one force application unit (15) acting on the floating roller at a force application point (P2);

[0118] wherein, for the purpose of applying a grinding force (F) and contacting each other at a roller contact point (P1) or defining a grinding gap (x0) for the raw material, the fixed roller and the loose roller can be mounted and positioned relative to each other, in particular by means of a force application unit; wherein the floating roller (3) has a positionally variable roller axis (y3), the floating roller (3) being mounted so that it can be pivoted about a pivot axis (P3) in the manner of a one-sided lever (16) so that the relative position of the floating roller relative to the fixed roller can be defined by the pivoting movement, wherein the one-sided lever (16) is formed between the pivot axis (P3) and the force application point (P2), wherein the roller contact point (P1) is arranged in a section between the force application point (P2) and the pivot axis (P3) and / or at a distance from the pivot axis that is less than the length of the one-sided lever, and wherein The roller contact point (P1) defines the load arm (16.2) of the one-sided lever, wherein when the rollers are in contact at the roller contact point, the roller axis is arranged relative to the pivot axis such that in a plane extending orthogonally thereto (side view) the connecting lines through the three axes form a triangle or a triangular arrangement, preferably each base angle on the connecting lines between the roller axes is less than 50 degrees, in particular less than 45 degrees, preferably less than 40 degrees, further preferably less than 35 degrees, wherein the pivot axis (P3) is arranged below the positionally fixed roller axis (y2), wherein the roller contact point (P1), the force application point (P2) and the pivot axis (P3) are arranged relative to each other such that a lever ratio of the distance between the force application point and the pivot axis to the distance between the force application point and the roller contact point can be set to at least 2 times. The combination of these features provides a large number of the above-mentioned advantages, in particular in the case of or also for a frame design provided for a floating roller that is usually displaced in translation. This combination of features can be combined with other features described herein. The force is preferably caused to act at least approximately in the same direction as the resulting rolling or grinding force (or in the opposite direction).

[0119] According to the invention, the above object is also achieved in particular by a roller mill (10), in particular in the form of a roller mill, which is configured to grind a raw material (M), the roller mill having:

[0120] - a fixedly mounted fixed roller (2) having an at least approximately fixedly mounted roller axis (y2);

[0121] - a floating roller (3) mounted in a floating manner, which has a roller axis (y3) which can be arranged in a variable position relative to the fixed roller;

[0122] - a frame (11) on which at least the fixed roller and optionally the floating roller are mounted;

[0123] - at least one force application unit (15) acting on the floating roller at a force application point (P2);

[0124] wherein the fixed roller and the floating roller can be mounted and positioned relative to each other, in particular by means of a force application unit, for the purpose of applying a grinding force (F) and contacting each other at a roller contact point (P1) or defining a grinding gap (x0) for the raw material; wherein the floating roller (3) has a positionally variable roller axis (y3), the floating roller (3) being mounted such that it can be pivoted about a pivot axis (P3) in the manner of a one-sided lever (16), such that the relative position of the floating roller relative to the fixed roller can be defined by the pivoting movement, wherein the one-sided lever (16) is formed between the pivot axis (P3) and the force application point (P2), wherein the force application is aligned at an angle of at least 75° or at least 80° relative to the grinding force, in particular at least approximately orthogonal to the direction of the grinding force, in particular in an at least approximately vertical plane, wherein the floating roller is at least partially, in particular completely, supported on the frame at the force application point. In other words: the floating roller is mounted on the pivot axis on the one hand and on the other hand supported on the frame at at least one force application point on the other side of its center of gravity, in particular on a corresponding frame part on the bottom side. The combination of these features provides a large number of the above advantages, in particular also with regard to large design-related and program variability and reliable support (in particular the coupling of forces to the machine frame), and also with regard to good responsiveness of the floating roller. This combination of features can also be combined with other features described here.

[0125] According to the invention, the above object is also achieved in particular by a roller mill (10), in particular in the form of a roller mill, which is configured to grind a raw material (M), the roller mill having:

[0126] - a fixedly mounted fixed roller (2) having an at least approximately fixedly mounted roller axis (y2);

[0127] - a floating roller (3) mounted in a floating manner, which has a roller axis (y3) which can be arranged in a variable position relative to the fixed roller;

[0128] - a frame (11) on which at least the fixed roller and optionally the floating roller are mounted;

[0129] - at least one force application unit (15) acting on the floating roller at a force application point (P2);

[0130] wherein, for the purpose of applying a grinding force (F) and contacting each other at a roller contact point (P1) or defining a grinding gap (x0) for the stock, the fixed roller and the floating roller can be mounted and positioned relative to each other, in particular by means of a force application unit; wherein the floating roller (3) has a positionally variable roller axis (y3), the floating roller (3) being mounted such that it can be pivoted about a pivot axis (P3) in the manner of a one-sided lever (16), such that the relative position of the floating roller relative to the fixed roller can be defined by the pivoting movement, wherein the one-sided lever (16) is formed between the pivot axis (P3) and the force application point (P2), wherein the force application is aligned at an angle of at least 75° or at least 80° relative to the grinding force, in particular at least approximately orthogonal to the direction of the grinding force, in particular in an at least approximately vertical plane, wherein the fixed roller is also mounted on the pivot axis. The combination of these features provides a number of the above-mentioned advantages, in particular with regard to a narrow frame design. This combination of features can also be combined with other features described herein.

[0131] According to the invention, the above object is also achieved in particular by a method for grinding a raw material, for example a ground material in the form of a mineral, in particular by a roller pressing device as described above, which method comprises the following steps: driving at least one fixedly mounted fixed roller with an at least approximately fixedly mounted roller axis and a floating roller with a positionally variable roller axis, which is mounted in a floating manner; subjecting the floating roller to a force in order to apply a grinding force and to position the floating roller relative to the fixed roller; wherein the floating roller with the positionally variable roller axis is pivoted about a pivot axis by the action of a force in the manner of a one-sided lever and in the process the relative position of the floating roller relative to the fixed roller is defined, wherein the force is caused to act at the force application point of the one-sided lever, in particular at a force application point which, in terms of the lever action, is spaced at least as far from the pivot axis as the positionally variable roller axis, preferably further away from the positionally variable roller axis. This provides the above-mentioned advantages.

[0132] It has been shown that a particularly advantageous force application concept with advantageous design options and advantageous kinematics can be achieved by using a one-sided lever to apply the force (or applying the force in a one-sided lever arrangement in which the load arm overlaps the force arm).

[0133] Here, the driving operation is described by taking two rollers as an example. Alternatively, only one roller is driven.

[0134] According to one embodiment, during the pivoting movement, the dancer moves in the direction of action of the force (direction of rotation). This also makes it possible to ensure a compact arrangement in a stable frame and to transmit the forces in an advantageous manner.

[0135] According to one embodiment, the force is applied to the force application arm of a one-sided lever, wherein the floating roller is pivoted relative to the fixed roller, so that the floating roller is in contact with the fixed roller in the section of the force application arm and the load arm is defined by the roller contact point or by the raw material / grinding material in contact therewith (in the case of a one-sided lever, the load arm coincides with the force application arm). This also allows for advantageous adjustability. Furthermore, the choice of the lever ratio also makes it possible to easily optimize the reactivity and / or force effectiveness of the device.

[0136] According to one embodiment, the force is caused to act at an angle of at least 60°, preferably at least 75° or at most 30°, preferably at most 15° relative to the grinding force (reaction force at the roller contact point), in particular at least approximately orthogonal to the grinding force or at least approximately in the direction of the grinding force or opposite to the grinding force (reaction force). In other words: when the force is caused to act at least approximately in the horizontal direction and / or at least approximately in the vertical direction, with reference to the arrangement of the two roller axes in the horizontal plane, the various advantages of the invention can also be achieved particularly well. This makes it possible to implement two advantageous force action concepts as alternatives or to combine them with each other, in particular in the case of at least approximately vertical and / or horizontal action of the force. In this case, different advantageous variants for the frame configuration can be achieved for the respective individual case.

[0137] It has been shown that the action of forces in at least approximately vertical direction, in particular by means of hydraulic cylinders, is particularly advantageous, in particular with regard to the direct transmission of forces (reaction forces of the rollers) into the machine frame. In other words: the mounting according to the invention about the pivot axis also enables a design concept in which forces are conducted directly from the grinding gap via the force action point into the machine frame, in particular at least approximately in vertical direction, as a result of which, in some frame parts, a force deflection from a horizontal force direction to a vertical force direction is no longer necessary or can be largely omitted.

[0138] According to one embodiment, the force is made to act at an angle of at least 60°, preferably at least 75° relative to the grinding force (reaction force at the roller contact point), in particular at least approximately orthogonal to the grinding force or at least approximately in a vertical direction, in particular vertically upwards. This also facilitates an advantageous realization of a narrow frame concept. Optionally, the frame can be open at the top.

[0139] According to one embodiment, the force is caused to act at an angle of at most 30°, preferably at most 15° relative to the grinding force (reaction force at the roller contact point), in particular at least approximately parallel to the grinding force or at least approximately in the horizontal direction. More importantly, this also facilitates the implementation of the roller concept according to the invention in conventional frames, in particular with a minimized number of actuators, in particular also without the risk of jamming or blocking on the translation guide, in particular when the forces are minimized by an advantageous lever ratio. In other words: the roller concept according to the invention can also be implemented, for example, by a relatively simple conversion of existing systems.

[0140] According to an exemplary embodiment, the force acts (in particular exclusively) at an angle of at most 15° or at most 10° relative to the grinding force, in particular at least approximately in the direction of the grinding force or against the grinding force, in particular in an at least approximately horizontal plane.

[0141] According to an alternative exemplary embodiment, the force is caused to act (particularly exclusively) at an angle of at least 75° or at least 80° relative to the grinding force, particularly at least approximately orthogonal to the direction of the grinding force, particularly in an at least approximately vertical plane.

[0142] According to one embodiment, the force is made to act in such a way that a force arm of the one-sided lever (effective lever distance between the pivot axis and the force application point) is achieved which is at least twice as long, in particular at least 2.5 or 3 times as long, as the load arm of the one-sided lever (effective lever distance between the pivot axis and the position-variable roller axis). This also makes it possible to achieve a good force effect; in particular, the energy required to provide a predetermined action can be effectively minimized.

[0143] According to one embodiment, the roller contact force is achieved by adjusting the action of the force at a single force action point at a single predetermined distance from the pivot axis. This also makes it possible to provide a particularly narrow arrangement.

[0144] According to one embodiment, the floating roller is positioned relative to the fixed roller only by a pivoting movement, that is to say without a translational displacement. In this respect, the pivoting movement can also be initiated only by a translational actuation or the action of a force, that is to say without a torque or without a rotational actuation movement. This enables the advantages according to the invention to be achieved particularly clearly.

[0145] According to one embodiment, the roller is mounted and supported in such a way that the reaction forces relative to the grinding forces are either directed into the frame in the same horizontal plane as the pivot axis and / or the force application point or at least approximately parallel to the reaction forces in the grinding gap or are transmitted into the frame in an at least approximately vertical direction and / or at least approximately orthogonal to the reaction forces in the grinding gap at the support of the floating roller. This also provides an advantageous force flow path or a compact or particularly stable frame arrangement. In particular, moments can be minimized. Forces in the x-direction can be directed into the frame substantially moment-free.

[0146] According to the invention, the above object is also achieved in particular by an open-loop / closed-loop control device configured to carry out the method as described above, wherein the open-loop / closed-loop control device is configured to control the drive of the fixed roll and / or the floating roll in an open-loop / closed-loop controlled manner and is configured to control the action of the force on the floating roll in an open-loop / closed-loop manner, wherein the open-loop / closed-loop control device communicates with a measuring device or comprises a measuring device, wherein the open-loop / closed-loop control device is configured to control the action of the force at the point of action of the force in an open-loop / closed-loop manner in a one-sided lever manner around the pivot axis of the floating roll, in particular by actuating and adjusting at least one force action unit with a hydraulic actuator, in particular in order to position the floating roll by a predetermined pivoting movement. This provides the above advantages.

[0147] According to the invention, the above-mentioned object is also achieved in particular by mounting a floating roller of the material bed roller mill relative to at least one further roller of the material bed roller mill, in particular relative to the fixed roller, using a pivot axis, by the action of a force about the pivot axis in the manner of a one-sided lever and by pivoting the floating roller on the force application arm of the one-sided lever, in particular mounting a floating roller of a roller pressing device as described above, in particular in the case of the above-mentioned method, in particular the pivot axis is arranged in the grinding gap (or in a straight line in a vertical plane through the grinding gap) or at least at the same x distance from the roller axis (i.e. in an at least approximately symmetrical x position between the roller axes). This provides the above-mentioned advantages. The pivot axis can be mounted in one or more pivot bearings, in particular on a common frame below the roller axis. BRIEF DESCRIPTION OF THE DRAWINGS

[0148] Other features and advantages of the present invention will be apparent from the description of at least one exemplary embodiment with reference to the accompanying drawings, and from the drawings themselves, in which:

[0149] FIG1 shows a rolling device according to the prior art;

[0150] Figure 2 A schematic diagram showing, in partial cross-sectional side view, a rolling apparatus according to an exemplary embodiment;

[0151] Figure 3A schematic diagram showing a rolling apparatus according to another exemplary embodiment in a partially cut-away side view;

[0152] Figure 4 A schematic diagram showing a rolling apparatus according to another exemplary embodiment in a partially cut-away side view;

[0153] Figure 5 A schematic diagram showing a rolling device having a triangular arrangement according to an exemplary embodiment;

[0154] Figure 6 A diagram showing a grinding gap of 0 is shown;

[0155] Figure 7 The diagram shows a grinding gap with >0. DETAILED DESCRIPTION

[0156] For reference numerals that are not explicitly described for a single figure, reference is made to the other figures. For the purpose of easier understanding, the figures are first described together with reference to all the reference numerals. Details or special features shown in the individual figures are described separately. Unless explicitly mentioned otherwise, the individual features of the individual exemplary embodiments can be combined with other exemplary embodiments.

[0157] The roller press or roller press device 10 for grinding the raw material M is arranged in / on a frame 1, 11 and comprises at least one fixed roller 2 and at least one floating roller 3. The floating roller is usually mounted in a translational manner in at least one sliding bearing 4. The frame 11 comprises, for example, a frame part 11a on the bottom side and a frame part 11b on the top side. The fixed roller is mounted in at least one (fixed) bearing 12.

[0158] According to one aspect of the invention, the floating bearing 13 for the floating roller is configured as a pivot bearing. In addition, a stop bearing 14 can be provided to absorb the reaction force, in particular comprising a stop, on which the fixed roller can be supported relative to the reaction force. A one-sided lever device 16 can be acted upon by a force application unit 15, which in particular has at least one hydraulic actuator (for example a plunger with a tilting device) for pivoting the floating roller about a pivot axis. The force is introduced at the force application arm 16.1 of the one-sided lever and transmitted to the fixed roller via a load arm 16.2. The load arm extends from the pivot axis in the same direction as the force application arm and is formed in particular between the pivot axis and the center of gravity of the floating roller or all components pivoting together with the floating roller. The open-loop / closed-loop control device 20 is coupled to a measuring device 21, which in particular comprises a pivot angle sensor. The individual (relative) distances and points of action are explained in more detail below; in particular, reference is made to the corresponding figures:

[0159] d1 effective distance or lever arm between the pivot axis and the position variable roller axis, in particular the distance orthogonal to the force direction in the x or z direction;

[0160] d2 effective distance or lever arm between the axis of the variable position roller and the point of force application, especially in the x or z direction;

[0161] d3 the lateral distance between the pivot axis and the axis of the variable position roller, in particular in the x direction;

[0162] d4 is the lateral distance between the pivot axis and the axis of the stationary roller, in particular in the x-direction;

[0163] D5 distance between the pivot axis and the frame or the frame part on the bottom side, in particular in the z direction;

[0164] F (vector) rolling force or roller contact force (grinding force) that produces a polarization vector in the grinding gap or at the contact point;

[0165] F1 (vector) is the polarized vector-equivalent (hydraulic) force exerted on the dancer roller, especially in the x-direction;

[0166] F2 (vector) is the (hydraulic) force of polarization vector exerted on the dancer roller, especially in the z direction against the direction of gravity;

[0167] P1 roller contact point or (theoretical) force transmission point in the grinding gap;

[0168] P2 (force) point of application, especially the hydraulic force used for introduction;

[0169] P3 pivot point or pivot axis;

[0170] X0 grinding gap, specifically the yz plane through the roller contact point

[0171] Y2 position fixed roller axis;

[0172] Y3 position variable roller axis;

[0173] Z0 is the free space (pivot cavity) for the floating roller relative to the frame;

[0174] x, y, z longitudinal, lateral and vertical axes or directions.

[0175] Now, with specific reference to the prior art (FIG. 1) and various exemplary embodiments of the present invention ( Figures 2 to 5 ),in, Figure 5 The roller arrangement or mounting according to the invention which can be implemented in all exemplary embodiments is schematically shown.

[0176] FIG. 1 shows a previously known roller press in which a floating roller is mounted in a translational manner in a sliding bearing at the top and bottom in a frame 1. The translational displacement of the floating roller relative to the fixed roller also generates reaction forces in the fixed bearing 12, in particular through the action of forces at at least two force introduction points. In this example, the forces are made to act at two points (above and below the center of gravity of the floating roller), in particular by means of cylinders, in particular in the horizontal direction corresponding to the direction of the translational displacement (or in the direction in which the translational sliding bearing extends). This type of force action is caused in particular by a force progression in the frame that is as symmetrical as possible. Therefore, the contact point of the rollers in the grinding gap is also at least approximately located in the center of the frame, at least with respect to the z-direction or with respect to the two force application points shown (force vector arrows F1, corresponding to the forces exerted on the floating roller).

[0177] Figure 2 A first variant for forming a one-sided lever device 16 according to the concept of the invention is shown. At point P2, the force is made to act essentially in the horizontal direction (in particular only at a single force application point), wherein the load arm is approximately half as long as the force arm (d1 is approximately equal to d2). The action of the force causes the floating roller to pivot. The pivot axis P3 (the turning point for the pivoting movement) is arranged at least approximately in the grinding gap X0 (d3 is approximately equal to d4), i.e. at the same x-coordinate. In this case, the force can be made to act selectively on only one point or on a plurality of points. In other words: in contrast to the construction according to FIG. 1 , a symmetrical arrangement of two force application cylinders is not required.

[0178] Figure 2 Also shown are the effective lever lengths (dashed lines) in a projection orthogonal to the force action, in particular the lever arm 16.1 (relatively narrow for illustration purposes) on the one hand, the length of which is defined by the position of the force action point P2, and the load arm 16.2 (relatively wide for illustration purposes) on the other hand, the length of which is defined by the force transmission point P1 or by the contact point of the rollers in the grinding gap. The pivoting movements are shown by the forward and backward arrows about the pivot axis P3, 13. Depending on the loading state and the size or particle spectrum of the raw material, the pivoting movements during operation can be more or less significant.

[0179] Thus, the dancer 3 is held between points P2 and P3 in the frame.Alternatively, forces are transmitted between the dancer and the frame only at these points and also indirectly via the contact point P1.

[0180] In this regard, at least one force acting unit 15 can also be configured to actuate (in particular tensile and compressive forces) in two acting directions (opposite pivoting directions). Optionally, only the fixed roller is actuated, especially since the floating roller can advantageously pivot back (purely) under the action of gravity. In particular, this also promotes a fast, reactive and thus low-load operating behavior, even in the case of relatively large and heavy rollers. In particular, it is also possible to relatively easily adjust or optimize the way in which the force acts in the grinding gap, especially depending on the raw material. In other words: compared to the translational mounting shown in FIG. 1, no large force is required to move the floating roller out of the grinding gap (to the left in FIG. 1). This can also provide advantages in terms of the design of the frame and / or the selection of the drive / actuator.

[0181] Examples of Figure 2 can also be used to describe the triangle of forces defined by points P1, P2 and P3. The corresponding roller axes are not very important here. The greater the distance P2 / P3 (especially in the z direction) relative to the distance P1 / P3, the smaller the design of the hydraulic cylinder or the force-introducing actuator. On the other hand, in the case of a large z distance P2 / P3, the load at point P3, i.e., the load acting on the pivot axis, also increases (especially large lever forces when the rollers are in contact). A ratio of P2 / P3 to P1 / P3 of at least about 1 to 2 is preferred, especially when the number of cylinders (force-acting actuators) should be as low as possible (based on the translational mounting: especially should be halved). In many cases, the cost aspect is also very important, so the ratio of the distances is also optimized in terms of cost. If the design cost of the mounting point P3 rises to a greater extent than the cost of the cylinders, the ratio is chosen to be smaller (if at all), and vice versa. In this regard, the ratio can also be selected in individual cases in the range from, for example, 1:1 to 1:3, especially 1:1.5 to 1:2.5, preferably 1:2.

[0182] Figure 3 Shows a second variant of the unilateral lever device 16 for forming according to the inventive concept. At point P2, the force acts essentially in the vertical direction or essentially orthogonally to the reaction force F at the roller contact point (in particular, also at least approximately orthogonally to the extension plane of the bottom frame part or the machine frame), and the load arm 16.2 is significantly shorter than half of the force arm 16.1 (z distance P1 to P3 < x distance P2 to P3). The pivot axis P3 is arranged in the grinding gap X0 (distance d3 is approximately equal to distance d4).

[0183] In this arrangement, the action of gravity is particularly effective. The floating roller can be mounted in a particularly reactive manner with respect to the return movement, and the pivot axis can at least partly relieve the load with respect to the gravity of the floating roller.

[0184] From a design perspective, in accordance with Figure 3 In the case of an arrangement of, the frame parts transversely to the outside of the floating roller can be given a relatively weak configuration or can be completely omitted. The forces can be transmitted from the floating roller to the frame, in particular also via diagonally connected supports or similar transverse members between the floating roller and the frame, in particular via frame supports 11.1 or struts, in particular with a directional specification of the force flow. Such transverse supports are advantageously connected directly or indirectly to the bottom side of the frame, or directly to the frame. The transmission of forces from the floating roller to the frame can be deflected in this way, in particular into the frame in a specific direction. Effect: forces can be transmitted with very low loads and the frame can be given a correspondingly narrow configuration.

[0185] Figure 4 A third variant for forming a one-sided lever arrangement 16 according to the concept of the invention is shown. Figure 4 A number of aspects are shown which may be advantageous in themselves but do not necessarily have to be implemented in combination with one another, in particular the following: an advantageous narrow structure; an advantageous force flow path; an advantageous force coupling to the frame (not shown; below the frame part 11a); coordinated support of the rollers, with particularly advantageous use of the pivot axis 13 as a common bearing axis (in particular to compensate for reaction forces).

[0186] At point P2, the force is caused to act essentially in the vertical direction or at least approximately orthogonally to the reaction force at the roller contact point, wherein the load arm 16.2 is approximately half the length of the force arm (d1 is approximately equal to d2). The pivot axis P3 is arranged in the grinding gap X0 (d3 is approximately equal to d4), i.e. at the same x position below the roller contact point. A special feature that should be emphasized is that the fixed roller can optionally be mounted around or on the same pivot axis P3 as the floating roller and rests on the support 14 relative to the reaction force around the pivot axis. Only the floating roller 3 is effectively positioned relatively. Optionally, however, the counter bearing 14 can also be a fixed bearing, to which the fixed roller is coupled in a fixed position (for example, a bearing ring 14 threaded to the frame). In other words: as the term "fixed roller" also makes clear, a relative movement of the fixed roller is not necessary, i.e. not even when the pivot axis is used as the bearing axis for the fixed roller. On the contrary, Figure 4 The design shown optionally also offers the design advantage that the pivot axis of the floating roller can also be used to mount the fixed roller, in particular with regard to the compensation of forces in the x-direction.

[0187] The frame 11 has only one frame part 11a arranged on the bottom side. It can advantageously be coupled directly to the machine frame (not shown), thereby promoting an advantageous transmission of forces, in particular in the case of very large roller arrangements. In particular, it is not necessary to introduce gravity components or reaction forces caused by the grinding operation laterally into the sides of the frame. In particular, Figure 4 It can also be seen in FIG. 1 that the configuration of the frame 11 without frame parts on the top side offers further advantages, for example with regard to general accessibility and / or with regard to the material supply M.

[0188] Figure 5 The relative arrangement of the axes (pivot axis and roller axis) relative to one another in a triangular arrangement (the triangular geometry of the triangle is located at its vertices) is described in general with reference to all exemplary embodiments according to the invention described above, the purely geometric illustrative dashed lines indicating the roller axes y2, y3, which are symmetrical relative to the pivot axis 13. An at least approximately isosceles triangle TR is defined by the respective axes y2, y3, 13 as corner points, the base angle α being advantageously as small as possible. The isosceles triangle arrangement TR is produced in particular when the rollers are in direct contact (the grinding gap is at least approximately zero or non-existent). If the rollers are spaced apart relative to one another, for example due to the stock in the grinding gap, the base angle will be correspondingly smaller.

[0189] In accordance with Figure 4 In the arrangement according to Figure 2 or Figure 3 In the case of an arrangement of (the pivot axis is relatively close to the roller contact point P1 in the z direction), the base angle α is relatively small, in particular in the range of about 25° to 35°. In other words: the pivot axis is advantageously arranged at a distance (z) from the roller axis that is less than half the roller axis diameter. Depending on the configuration of the frame and the mounting, the base angle α can assume a magnitude, for example, in the range of 20° to 50° (or in individual cases even up to 60°).

[0190] It has been shown that by means of such a triangular arrangement TR, a large number of advantages of the invention can generally be ensured in each of the different exemplary embodiments, independently of the specific case of use. Therefore, the design concept according to the invention can also be implemented particularly advantageously by means of such a triangular arrangement TR, in particular the size of the base angle or the relative arrangement of the pivot axis is respectively a design parameter. As explained above, the relative x position and / or the relative z position of the pivot axis can also be adapted individually, for example slightly offset relative to the axis of rotation of the floating roller and moved out of the grinding gap. The triangular arrangement TR is preferably an isosceles triangle arrangement. However, the triangular arrangement TR does not necessarily have to be an isosceles triangle arrangement only, but rather the two base angles are optimized within the scope of adaptation by experts in the field for the corresponding case of use at least within a narrow range of variation.

[0191] Figures 2 to 5 A one-sided lever (one-sided lever arrangement) 16 is schematically shown by a dashed line, which extends from the pivot axis 13 to the force application point P2. The corresponding effective lever length ( Figure 2) should be determined in absolute values, in particular orthogonal to the force direction. The applicant therefore opted for a representation based on dashed lines, since the part forming the one-sided lever therein can be defined individually depending on the specific selectable position of the force application point, the length of the lever and the length ratio between the force arm and the load arm. Regardless of this, the floating roller is arranged both in the region of the load arm and in the region of the force application arm, or these regions overlap (one-sided lever arrangement without a free load arm, i.e. without a rocker).

[0192] Figure 6 In a highly simplified manner, only the fixed roller 2 and the floating roller 3 are shown relative to the pivot axis P3. A connecting line is shown between the roller axis y2, which is mounted in a fixed position, and the roller axis y3, which is arranged in a variably position. This connecting line intersects the fixed roller 2 and the floating roller 3 at the roller contact point P1. The tangent lines of the fixed roller 2 and the floating roller 3 are orthogonal to this connecting line and extend through the pivot axis P3.

[0193] Figure 7 A very oversized grinding gap X0 is shown. In practice, the grinding gap X0 will be much smaller than the radius of the fixed roller 2 and the radius of the floating roller 3. The distance between the fixed roller 2 and the floating roller 3 now creates two spaced-apart tangent lines. In the example shown, the pivot axis P3 is arranged exactly in the center between the tangent lines.

[0194] Reference numerals list

[0195] 1 Framework

[0196] 2 Fixed rollers

[0197] 3 Floating rollers

[0198] 4 Sliding bearings

[0199] 10 Roller Pressing Equipment

[0200] 11 Framework

[0201] 11a Frame portion on bottom side

[0202] 11b Frame portion on top side

[0203] 11.1 Frame supports or struts

[0204] 12 (Fixed) bearings for fixed rollers

[0205] 13 Floating bearings for floating rollers, especially pivot bearings

[0206] 14 Counter bearing for reaction force

[0207] 15 Force acting units, in particular hydraulic actuators, in particular plungers with tilting devices

[0208] 16 One-sided lever or one-sided lever device

[0209] 16.1 Lever

[0210] 16.2 Load Arm

[0211] 20 Open-loop / closed-loop control device

[0212] 21 Measuring device, in particular with a pivot angle sensor

[0213] d1 Effective distance or lever arm between the pivot axis and the position-variable roller axis, in particular the distance orthogonal to the force direction in the x or z direction

[0214] d2 Effective distance or lever arm between the axis of the variable position roller and the point of force application, especially in the x or z direction

[0215] d3 Transverse distance between the pivot axis and the axis of the variable position roller, in particular in the x direction

[0216] d4 Transverse distance between the pivot axis and the axis of the stationary roller, in particular in the x direction

[0217] D5 Distance between the pivot axis and the frame or the frame part on the bottom side, in particular in the z direction

[0218] F Rolling force or roller contact force (grinding force) generated in the grinding gap or at the contact point

[0219] F1 (Hydraulic) force applied to the floating roller, especially in the x-direction

[0220] F2 (Hydraulic) force applied to the floating roller, especially in the z direction

[0221] M Raw Materials

[0222] P1 Roller contact point or (theoretical) force transmission point in the grinding gap

[0223] P2 (Force) point of application, especially for the hydraulic pressure introduced

[0224] P3 Pivot point or pivot axis

[0225] TR Isosceles triangle

[0226] α Base angle

[0227] β Alignment of the one-sided lever relative to the horizontal plane

[0228] X0 Grinding gap, specifically the yz plane through the roller contact point

[0229] y2 Position fixed roller axis

[0230] y3 variable position roller axis

[0231] Z0 Free space for the floating roller relative to the frame (pivot cavity)

[0232] x, y, z longitudinal, transverse and vertical axes or directions

Claims

1. A roller pressing device (10) configured to grind a raw material (M) in the form of a roller mill, the roller pressing device comprising: - a fixedly mounted fixed roller (2) having a roller axis (y2) which is mounted at least approximately in a fixed position; - a floating roller (3) mounted in a floating manner, which has a roller axis (y3) which can be arranged in a variable position relative to the fixed roller; - a frame (11), on which at least the fixed roller and the floating roller are mounted; - at least one force application unit (15) acting on the floating roller at a force application point (P2); wherein the fixed roller and the floating roller can be mounted and positioned relative to each other by means of the force application unit in order to apply a grinding force (F) and to contact each other at a roller contact point (P1) or to define a grinding gap (x0) for the raw material; wherein the floating roller (3) having a position-variable roller axis (y3) is mounted so that it can be pivoted about a pivot axis (P3) in the manner of a one-sided lever (16) so that the relative position of the floating roller with respect to the fixed roller can be defined by this pivoting movement, wherein the one-sided lever (16) is formed between the pivot axis (P3) and the force application point (P2), Characterized in that the pivot axis (P3) is arranged on a tangent to the fixed roller (2) and the floating roller (3) at the roller contact point (P1), or, in the case of a non-zero grinding gap (x0), the pivot axis (P3) is arranged between a tangent at the intersection of a connecting line between a roller axis (y2) of the fixed roller (2) and a roller axis (y3) of a variably arranged position and a tangent at the intersection of a roller axis (y2) of the floating roller (3) and a roller axis (y3) of the fixed roller (2); the fixed roller (2) is mounted around the same pivot axis (P3) as the floating roller (3) or on the same pivot axis (P3) as the floating roller (3).

2. Rolling device according to claim 1, characterized in that The distance between the pivot axis (P3) and the connecting line between the fixed roller axis (y2) and the variably arranged roller axis (y3), and along a straight line which is at right angles to the connecting line between the fixed roller axis (y2) and the variably arranged roller axis (y3) and passes through the pivot axis (P3) corresponds to at least 0.15 times the sum of the radius of the fixed roller (2) and the radius of the floating roller (3) and at most 1 times the sum of the radius of the fixed roller (2) and the radius of the floating roller (3).

3. Rolling device according to claim 1, characterized in that The distance between the pivot axis (P3) and the force application point (P2) corresponds to 1 to 5 times the distance between the pivot axis (P3) and the connecting line between the fixed roller axis (y2) and the variably arranged roller axis (y3), along a straight line that is at right angles to the connecting line between the fixed roller axis (y2) and the variably arranged roller axis (y3) and passes through the pivot axis (P3).

4. The rolling device according to any one of the preceding claims 1 to 3, characterized in that: The one-sided lever (16) includes a straight line connecting the force application point (P2) and the pivot axis (P3).

5. The rolling device according to claim 4, characterized in that: The positionally variable roller axis (y3) passes through the one-sided lever (16).

6. The rolling device according to claim 4, characterized in that: The positionally variable roller axis (y3) is spaced apart from a straight line connecting the force application point (P2) and the pivot axis (P3) by at most 0.1 times the length of the straight line connecting the force application point (P2) and the pivot axis (P3).

7. The rolling device according to any one of the preceding claims 1 to 3, characterized in that: The force acts at the force application point (P2) at an angle of 75° to 105° relative to a connecting line between the fixed roller axis (y2) and the variably arranged roller axis (y3).

8. The rolling device according to any one of the preceding claims 1 to 3, characterized in that: The roller contact point (P1) is arranged in a section between the force application point (P2) and the pivot axis (P3) and / or at a distance from the pivot axis that is less than the length of the one-sided lever, and wherein the roller contact point (P1) defines a load arm (16.2) of the one-sided lever.

9. The rolling device according to any one of the preceding claims 1 to 3, characterized in that: When the rollers are in contact at the roller contact points, the roller axes are arranged relative to the pivot axis such that a connecting line passing through the three axes in a plane extending orthogonally thereto forms a triangular arrangement.

10. Rolling device according to claim 9, characterized in that Each base angle on the connecting line between the roller axes is less than 50 degrees.

11. Rolling device according to claim 9, characterized in that Each bottom angle on the connecting line between the roller axes is less than 45 degrees.

12. Rolling device according to claim 9, characterized in that Each bottom angle on the connecting line between the roller axes is less than 40 degrees.

13. Rolling device according to claim 9, characterized in that Each base angle on the connecting line between the roller axes is less than 35 degrees.

14. The rolling device according to any one of the preceding claims 1 to 3, characterized in that The dancer roller is pivotably mounted and arranged such that the weight force acting at the center of gravity of the dancer roller acts on the load arm of the one-sided lever in the direction of the return movement in order to enlarge the grinding gap.

15. The rolling device according to any one of the preceding claims 1 to 3, characterized in that Acting about said pivot axis (P3) by at least one plunger.

16. Rolling device according to claim 15, characterized in that Acting about said pivot axis (P3) by at least one plunger having a tilting device.

17. Rolling device according to claim 15, characterized in that Acting about the pivot axis (P3) is accomplished by at least one plunger having a hydraulic adjuster as a tilting device.

18. A method for grinding a raw material (M) by means of a roller pressing device (10) according to any one of the preceding claims 1 to 17, the method comprising the following steps: - driving at least one fixedly mounted fixed roller (2) with an at least approximately positionally fixed mounted roller axis (y2) and a floatingly mounted floating roller (3) with a positionally variable arranged roller axis (y3); - applying a force to the floating roller (3) in order to apply a grinding force (F) and to position the floating roller relative to the fixed roller (2); Characterized in that the floating roller with a position-variable roller axis is pivoted about a pivot axis (P3) in the manner of a one-sided lever (16) by the action of a force and in the process defines the relative position of the floating roller with respect to the fixed roller, wherein the force acts at the force application point (P2) of the one-sided lever.

19. The method according to claim 18, characterized in that The force acts at a force application point which is spaced at least as far from the position-variable roller axis (y3) as the position-variable roller axis (y3) is spaced from the pivot axis (P3) in terms of leverage.

20. The method according to claim 18, characterized in that The force is caused to act at a force application point which is spaced further from the position-variable roller axis (y3) than the position-variable roller axis (y3) is spaced from the pivot axis (P3) in terms of leverage.

21. The method according to claim 18, characterized in that A force is applied to the lever arm of the one-sided lever, wherein the floating roller (3) is pivoted relative to the fixed roller (2) so that the floating roller contacts the fixed roller in a section of the lever arm and a load arm is defined by the roller contact point (P1) or by the contacted material (M).

22. The method according to any one of claims 18 and 21, characterized in that The floating roller (3) is positioned relative to the fixed roller (2) only by a pivoting movement, i.e. without a translational displacement; and / or wherein the pivoting movement is initiated only by a translational actuation or the action of a force, i.e. without a torque or a rotational actuation movement.

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