LU502855B1 - Roller crusher with adjustable crushing gap - Google Patents

Abstract

The invention relates to a roller crusher (1) with a machine frame (2), with a rotatable roller (4), with a rocker (8) mounted on a rocker axis (6) on the machine frame (2), with a crushing chamber (9) between the roller (4) and the rocker (8), wherein an adjustable crushing gap (BS) is formed between the roller (4) and the rocker (8) at a lower end of the crushing chamber. The roller (4) is loosely mounted on the machine frame (2). The roller crusher (1) has a roller adjustment device (30) for adjusting the roller (4) perpendicular to its axis of rotation (5) in the direction of the rocker (8) to adjust the crushing gap (BS). The invention further relates to a method.

Description

Iron freight feeder

LU502855

Munich, 29 September 2022

Our reference: TM 5999-02LU FEG/bki

Applicant/Owner: thyssenkrupp Mining Technologies GmbH

Official reference number: New registration thyssenkrupp Mining Technologies GmbH

Thyssenkrupp Allee 1, 45143 Essen, DE

Roller crusher with adjustable crushing gap

Description

The invention relates to a roller crusher with a machine frame, with a rotatable roller, with a bearing mounted on a swing axle on the machine frame.

Swing arm, with a crushing chamber between the roller and the swing arm, with a lower

At the end of the crushing chamber, an adjustable crushing gap is formed between the roller and the rocker. The invention further relates to a method for operating a roller crusher.

Such a roller crusher can be designed in particular as an eccentric roller crusher or as a roller crusher with a directly driven roller.

Eccentric roller crushers, also known as "Rotex crushers", are, for example, from the magazine "Aufbereitungs-Technik, Zeitschrift für die Aufbereitung fester

Raw materials", Volume 5 (1964), Issue 5, pages 242 to 247 and "Processing technology,

Journal for the processing of solid raw materials", Volume 6 (1966), Issue 3, pages 166 to 174. In the known designs of eccentric roller crushers, the swing arm is suspended diagonally above the roller and can be swivelled in order to be able to adjust both the inlet gap and the outlet gap (also called the crushing gap). During operation of the roller crusher, however, the swing arm is fixed in its position in order to be able to crush the crushed material, particularly rock. In order to adjust the gap, a gap adjustment device is initially provided. In addition, it can also happen during operation that foreign substances that are too hard and cannot be crushed get into the crushed material. There is then a risk that the crushing gap 0H) 0 0 0 OD R00 *2022660715*

? LU502855 clogged or even the roller with the crushing jaws and the swing arm with the crushing jaws can be damaged. It is therefore known to equip eccentric roller crushers with an overload protection device, which is arranged between the swing arm and an abutment fixed to the housing frame. The pre-tensioning force of the springs is selected so that they do not spring back under normal crushing load. If, on the other hand, the crushing jaws are at risk of being overloaded, the swing arm can retreat against the force of the springs and thus expand the crushing space in order to be able to eject foreign bodies if necessary. However, it has proven to be disadvantageous that very large, stable

Springs must be used for support, which do not spring back under normal crushing stress. Furthermore, the transition area is difficult to adjust due to the typical spring characteristics. There is also the disadvantage that very large spring forces continue to act during the spring back, so that damage cannot be ruled out. Finally, when using springs, there may also be an undefined transition area in which the springs are only partially compressed, which then results in an undefined operating state, which can, for example, lead to an incorrect grain size of the crushed material over a longer period of time.

The present invention is not limited to a design of the roller crusher as an eccentric roller crusher. US 1 141 643 and DE 1 077 037 show roller crushers of this type with a directly rotating driven roller. This roller works together with a rocker which is held by an upper load safety device equipped with springs.

An eccentric roller crusher of the present applicant is disclosed, for example, in WO 2014/067882 A2. There, it is proposed to adjust the rocker via an adjustment device that has a wedge that can be moved between a first position and a second

Position can be moved back and forth. The wedge itself is driven and moved mechanically or hydraulically. An overload protection can also be provided, which can be done via a bypass valve or a pressure relief valve in the case of hydraulic actuation of the wedge, or via a

Adjusting spindle, through a mechanical predetermined breaking point. The counter bearing for the wedge on the machine frame side can be rotated around an axis in order to compensate for the rotation of the swing arm when adjusting the swing arm.

This type of adjustment has proven itself because, on the one hand, the wedge achieves a ratio between the driving force for the wedge and the deflection of the swing arm, such that

’ LU502855 that no excessive forces act on the drive device for the wedge. In the event of a

Overload, for example due to too large a crushed material in the crushing chamber or too hard a material, the wedge can still be moved by the swing arm and the

Trigger overload protection. If the overload protection is triggered, the swing arm can continue

Open and the non-crushed material is removed from the crushing chamber.

Further eccentric roller crushers are disclosed in WO 2014/067858 A1, WO 2014/067867

A1, WO 2019/134864 A1 and DE 10 2019 204 836 B3.

The object of the present invention is to provide a roller crusher of the type mentioned

Art to further improve, especially with regard to damage caused by overload.

The invention solves the problem of a roller crusher of the type mentioned at the beginning according to the invention by the features of claim 1. In particular, it is provided that the roller is loosely mounted on the machine frame and that the roller crusher has a roller

Adjustment device for adjusting the roller perpendicular to its axis of rotation in the direction of

Swing arm for adjusting the crushing gap.

The roller crusher of the present invention thus departs from the path of the stationary rotating roller and movable rocker taken by the prior art, in that the roller itself is loosely mounted and thus displaceably mounted on the machine frame relative to its axis of rotation. The roller can be either a directly driven roller or an eccentric roller, which rotates in a stationary manner but the roller body itself is provided with an eccentricity. The roller can be adjusted essentially horizontally or at an angle, in particular on a curved path. The roller adjustment device is preferably designed in such a way that at least a minimal crushing gap is present, but this can be widened, in particular to remove crushed material that is too large or foreign bodies. The widening of the crushing gap can take place purely passively, due to reaction forces when the crushed material or foreign bodies in the crushing chamber are too large, or actively by an actuator provided for this purpose.

In a preferred development, the roller crusher has a swing arm adjustment device which is arranged at a distance from the swing arm axis between the swing arm and a swing arm abutment which is fixed to the machine frame in order to enable rotation of the swing arm about the swing arm axis. Preferably, it is provided that the swing arm adjustment device has a swing arm wedge arranged between the swing arm and the swing arm abutment which has a gap

* LU502855 between a contact surface arranged on the rear side of a swing arm and a

The swing arm abutment is bridged by a counter surface assigned to the swing arm abutment, wherein in a second position of the swing arm wedge in the gap the crushing gap is larger than in a first position, wherein the swing arm abutment is formed by a rotation axis on which a

Swing counter element with the counter surface shown on it can rotate freely. This

The design is essentially based on the disclosure WO 2014/067882 A2, whose

The content is incorporated herein by reference in its entirety. Preferably, the swing

Adjustment device according to one or more features of the adjustment device according to

WO 2014/067882 A2. A floating bearing unit can be provided, wherein the

Roller is accommodated in the floating bearing unit, and wherein the roller adjustment device acts on the floating position unit to adjust the roller. The floating bearing unit can be mounted as a structural unit on the machine frame, in particular in a sliding manner. Alternatively, the floating bearing unit can also consist of two separate first and second bearings, wherein a shaft journal, which extends axially on the roller on opposite sides, is accommodated in the first and second floating bearings. A sliding bearing is preferably provided between the floating bearing unit or the floating bearings of the floating bearing unit and the machine frame in order to enable the roller to be moved and thus adjusted. This sliding bearing can be oil-lubricated in order to enable it to run smoothly.

In one embodiment, the roller adjustment device comprises at least a first

Roller wedge which bridges a gap between a contact surface arranged on the rear side of the bearing and a counter surface assigned to a roller abutment, wherein in a second position of the roller wedge in the gap the crushing gap is larger than in a first position. In the event that the floating bearing unit has two separate floating bearings for the

Shaft ends of the roller, two roller wedges can also be provided, with a first roller wedge being connected to a first floating bearing and a second roller wedge being connected to a second

The floating bearing unit can be assigned to a floating bearing. The at least first roller wedge can be designed similarly or identically to the swing wedge and is preferably not self-locking. The roller abutment is preferably formed by a rotation axis on which a roller counter element with a counter surface formed thereon can rotate freely. In this way, certain displacements of the roller can be compensated.

In a preferred development, the roller crusher has a synchronizing device for the roller, which is designed to limit misalignment to a predetermined level. This is particularly preferred if the floating bearing unit has two separate

Floating bearings for the two shaft ends of the roller. The synchronization device allows

° LU502855 to a certain degree an independent displacement of the first and second floating bearings, which can then cause a misalignment of the roller, that is to say a twisting of the roller perpendicular to the axis of rotation and perpendicular to the direction of the adjustment device. A certain misalignment within a certain range can be preferred, especially when a high load only occurs on one side of the roller. By a certain

If misalignment is permitted, the roller can also easily deviate on one side and thus prevent overloading. A synchronizing device that can be used advantageously within the scope of the invention and can limit misalignment to a predetermined level is known from WO 2021/023643 A1 of the present applicant, the disclosure content of which is fully incorporated herein by reference. In particular, the synchronizing device of the present invention can comprise one or all features of the synchronizing device from WO 2021/023643.

In a preferred development, it is provided that the roller adjustment device has at least one first spring, wherein the crushing gap is adjusted against the force of the first

Spring is expandable. Preferably, a second spring is provided, the first spring being assigned to the first floating bearing and the second spring being assigned to the second floating bearing. The first and second springs are preferably designed in such a way that they do not flex under normal load and only flex under a force that can lead to an overload and thus expand the crushing gap. In order to completely prevent misalignment, a mechanical coupling of the first and second springs can be provided, for example via a linearly guided plate.

Additionally or alternatively, the roller adjustment device may comprise at least a first

Hydraulic or pneumatic pistons for adjusting the crushing gap. While the spring only allows passive adjustment based on the reaction force, the crushing gap can be actively adjusted to a certain desired size using a hydraulic or pneumatic piston. In this way, not only can wear be compensated, but a target grain size of the roll crusher can also be set. It should be understood that a roll adjustment device that has a first hydraulic or

Pneumatic piston, can also have a first spring. In this context, the spring can then function as an overload protection, while the first hydraulic or pneumatic piston is used to set a nominal size of the crushing gap.

It is further preferred that the roller adjustment device has at least one first spindle drive for adjusting the crushing gap. The first spindle drive can also

° LU502855 can be used as an alternative or in addition to the hydraulic or pneumatic piston and/or as an alternative in addition to the spring. A nominal breaking gap can also be set using a spindle drive.

Furthermore, it is preferred that the roller adjustment device, in the event that it has a

Roller wedge, at least one roller counterweight, wherein the crushing gap can be expanded against the weight of the roller counterweight. The roller wedge is preferably designed so that it is not self-locking. The roller counterweight can act on the crushing gap, for example via a deflection roller, and the

Pull the roller wedge into a position and hold it that corresponds to a certain crushing gap. Because the roller wedge is not self-locking, the roller can then deflect against a crushing force and move the wedge, thereby raising the roller counterweight. In this way, an alternative design to the spring can be achieved that does not result in an increasing force with increasing deflection, as is the case with springs due to the spring constant.

In order to further prevent overloading, the roller adjustment device can have at least one roller overload protection. This is preferably selected in accordance with the corresponding actuator or passive elements. An overload protection can, for example, comprise a predetermined breaking point, a mechanical spring, a bypass valve, a pressure relief valve, a counterweight. In certain embodiments, for example, the roller counterweight described above can act as an overload protection, while a nominal crushing gap is set by means of a hydraulic piston. It can also be provided that a nominal crushing gap is set by a spindle drive, while overload protection is provided via a pressure relief valve of a pneumatic piston. It should be understood that all conceivable combinations and variants are included herein.

The swing adjustment device can also be driven in various ways. Examples include: spring, hydraulic piston, pneumatic piston, spindle drive, swing counterweight, which can preferably be designed in accordance with the roller counterweight described above.

In a second aspect, the invention solves the problem in a method of the type mentioned at the outset with the features of claim 14. It should be understood that the

Roller crusher according to the first aspect of the invention, the method according to the second

! LU502855 aspect of the invention have the same and similar sub-aspects as are particularly laid down in the dependent claims. In this respect, preferred

Further developments of the method according to the second aspect of the invention refer in full to the above description of the first aspect of the invention. The method according to the second aspect of the invention preferably comprises the steps: conveying

Crushed material to the roller crusher; screening of crushed material below a predetermined

Grain size; feeding of crushed material above the predetermined grain size to the

crushing chamber, and adjusting the roller to expand the crushing gap in case

Crushed material of an unsuitable grain size and/or made of an unsuitable material in the

According to the method, it can also be provided that the rocker is also or alternatively adjusted to expand the crushing gap in the event that

Crushed material of an unsuitable grain size and/or made of an unsuitable material in the

crushing chamber.

Alternatively or in addition to the step of adjusting the roller and/or rocker to expand the crushing gap, one or more of the following steps can also be carried out. Preferably, a crushing gap is first created by adjusting the

Swing arm and/or roller. A fixed nominal crushing gap can be set, which then determines the size of the resulting crushed material. In this case, the roller and/or swing arm should be stationary during operation and only actively or passively deflected in the event of an impending overload. It is also conceivable and preferred that a certain pressure in the crushing gap is set by adjusting the swing arm and/or roller. In this case, it is not a gap that is set and regulated if necessary, but a pressure between the roller and swing arm that is used to crush the

material is used. If the pressure increases due to large amounts of material in the crushing chamber, the roller and/or rocker are adjusted or move away until the pressure is balanced again. Such a control is particularly easy to implement in variants with hydraulic, pneumatic or force-based adjustment of

Roller and/or swing arm. Adjustment is also possible if a larger resulting product is desired during the crushing process. It is also preferable to adjust the roller and/or swing arm to compensate for wear, especially on the crushing jaws.

The invention thus offers the possibility of not only adjusting the rocker as is known in the prior art, but also of adjusting the roller. In the case of unsuitable

Material in the crushing chamber or for maintenance purposes, either the roller can be moved or the swing arm can be moved or both the roller

9 LU502855 the swing arm is also moved. If both the roller and the swing arm are moved, the crushing space is expanded to the maximum, which can also simplify maintenance.

In a further aspect, a roller crusher is disclosed which only has a swing

Adjustment device according to one of the embodiments disclosed herein, but no roller adjustment device. Furthermore, it should be understood that each of the embodiments of the swing adjustment device disclosed herein can be used with each of the embodiments disclosed herein.

Designs of the roller adjustment device can be combined. Each of the swing adjustment devices disclosed herein can be used with and without swing overload protection, and each roller adjustment device disclosed herein can be implemented with and without roller overload protection. It is also conceivable and preferred that a swing adjustment device and a roller overload protection or a roller adjustment device and a swing overload protection are used. Such embodiments are also part of the disclosure.

Embodiments of the invention will now be described below with reference to the drawings. These are not necessarily intended to show the embodiments to scale; rather, the drawings are in a schematic and/or slightly distorted form where this is useful for explanation. With regard to additions to the teachings immediately apparent from the drawings, reference is made to the relevant state of the art.

Technology. It should be noted that a wide variety of modifications and changes can be made to the form and detail of an embodiment without deviating from the general idea of the invention. The features of the invention disclosed in the description, in the drawings and in the claims can be essential for the development of the invention both individually and in any combination. In addition, all combinations of at least two of the features disclosed in the description, the drawings and/or the claims fall within the scope of the invention. The general idea of the invention is not limited to the exact

Form or detail of the preferred embodiments shown and described below or limited to an object that would be limited in comparison to the object claimed in the claims. In the case of specified dimension ranges, values within the stated limits should also be disclosed as limit values and can be used and claimed as desired. For the sake of simplicity, the same reference numerals are used below for identical or similar parts or parts with identical or similar functions.

Further advantages, features and details of the invention emerge from the following description of the preferred embodiments and from the drawings, which show:

Fig. 1 is a schematic longitudinal section of a roller crusher in a first

embodiment;

Fig. 2 shows a schematic longitudinal section of a V-roller crusher in a second

embodiment;

Fig. 3 is a schematic cross-section of the roll crusher according to Fig. 2;

Fig. 4 is a schematic longitudinal section of a roll crusher in a third

embodiment;

Fig. 5 is a schematic longitudinal section of a roll crusher in a fourth

embodiment;

Fig. 6 is a schematic longitudinal section of a roller crusher in a fifth

embodiment;

Fig. 7 is a schematic longitudinal section of a roll crusher in a sixth

embodiment; and in

Fig. 8 is a schematic longitudinal section of a roller crusher in a seventh

Example of implementation.

A roller crusher 1, which is designed here as an eccentric roller crusher, comprises a machine frame 2, a rotatable roller 4, a swing arm 8 mounted on a swing arm axis 6 on the machine frame 2, a crushing chamber 9 between roller 4 and swing arm 8 and a screening chamber 7. At the lower end of the crushing chamber 9, between

A crushing gap BS is formed between the rocker 8 and the roller 4, which defines the smallest distance between the roller 4 and the rocker 8. During operation, the roller 4 rotates about an axis of rotation 5, whereby the roller 4 is designed with an eccentricity so that the roller body 4 rotates eccentrically about the axis of rotation 5. When the roller 4 rotates eccentrically, the distance between the roller 4 and the rocker 8 changes so that the crushed material which is fed into the crushing chamber 9 can be crushed.

The swing arm 8 is provided with a swing arm adjustment device 10, which, as shown in

WO 2014/067882 A2. Specifically, the swing arm adjustment device 10 comprises a swing arm wedge 12 which is arranged in a gap between a

The rocker arm is arranged on a contact surface 13 formed on the rear side of the rocker arm and a counter surface 15 associated with a rocker arm abutment 14. The rocker arm wedge 12 can be positioned within the gap with a rocker arm wedge drive 16 of the rocker arm adjustment device 10 in order to change the distance between the rocker arm 8 and the roller 4 and thus the effective crushing gap BS. When the rocker arm wedge 12 is moved downwards in the direction of its second position with reference to Fig. 1, the distance between the roller 4 and the rocker arm 8 increases. When the rocker arm wedge 12 is moved upwards in the direction of

towards its first position P1, the crushing gap BS between

Roller 4 and swing arm 8.

The swing wedge 12, the contact surface 13 and the counter surface 15 are aligned with each other in such a way that the swing wedge 12 is pushed downwards, i.e. in the direction of the second position P2, by the forces acting on the swing arm 8. The geometry of the

contact surface 13, the counter surface 15 and the swing wedge 12 is selected so that the

Swing wedge 12 is not self-locking, that is, no self-locking occurs. In particular, the swing wedge 12 can be designed to move automatically downwards in the direction of the second

Position. The counter surface 15 is formed on a counter holder 17, which forms a fixed bearing, but is arranged so as to be rotatable about the abutment 14, which is designed as an axle pin. In this way, the counter surface 15 can rotate about the abutment 14 when the swing wedge 12 is adjusted. This takes into account the fact that the swing 8 rotates about the swing axis 6 when the swing wedge 12 is adjusted.

In the embodiment shown here (Fig. 1), the swing wedge drive 16 comprises a hydraulic or pneumatic drive 18, with a hydraulic or pneumatic cylinder 19, which is firmly connected to the swing 8, and a hydraulic or pneumatic piston 20, which is connected in an articulated manner to the swing wedge. By appropriate

Applying hydraulic or pneumatic pressure inside the hydraulic or

Pneumatic cylinder 19 allows the hydraulic or pneumatic piston 20 to be moved up or down with reference to Fig. 1 in order to adjust the swing wedge.

The swing arm adjustment device 10 also comprises a swing arm overload protection 22, which here comprises a pressure relief valve 23, such that hydraulic or pneumatic fluid

Overload of the swing arm 8 can be released from the pressure relief valve 23 in order to

Swing wedge 12 is moved to a lower position and thus the crushing gap BS is widened.

In addition to the swing arm adjustment device 10, the embodiment shown here (Fig. 1) of the roller crusher 1 comprises a roller adjustment device 30. The roller adjustment device 30 serves to adjust the roller 4 perpendicular to its axis of rotation 5 in the direction of the swing arm 8 in order to adjust the crushing gap BS. In order to prevent deflection of the roller 4 with

Referring to Fig. 1, this is loosely mounted. In the

In the embodiment shown in Fig. 1, the roller adjustment device 30 is purely passive and comprises at least a first spring 32. The compression spring 32 is supported against a support 34 which is connected to the machine frame 2. The first spring 32 can act directly on a first shaft shoulder 36 of the roller 4, or (as will be described in detail later with reference to Figs. 2 and 3) on a first

Bearing housing of the first shaft shoulder 36. The spring 32 is preferably dimensioned such that it does not deflect during normal operation, but only deflects when a

Force in the crushing chamber 9 would exceed a load limit of the roller crusher 1 and thus there is a risk of damage to the roller crusher 1.

The spring 32 can be pre-tensioned for this purpose. Additionally or alternatively, a second spring (not shown) can also be provided on the other side of the roller 4, not shown in Fig. 1, on the second shaft shoulder (not shown in Fig. 1). It can also be provided that only a first spring is provided, which then acts on both the first and the second shaft shoulder via a holding mechanism. It can also be provided that the first and the second spring are coupled to one another, so that a

Synchronous running of the roller 4 is ensured. The support 34 can also be attached to the machine frame 2 in an articulated manner so that no moments are introduced into the machine frame 2.

In Fig. 1 it can also be seen that a screening device 40 is provided above the roller 4, which is supported on the one hand on a stationary abutment 42 on the machine frame 2 and on the other hand on a support surface of the roller 4. A movement of the

Roller 4 causes a shaking movement on the support surface between the screening device 40 and roller 4. The screening device 40 can also rotate around the abutment 42 so that the screening device 40 can compensate for an eccentric rotation of the roller 4. The screening device 40 is designed so that crushed material below a predetermined size falls through the screen and, with reference to Fig. 1, is on the left at the

Roller 4 can be guided past, that is, does not enter the fracture chamber 9. Only

Crushed material with a size above the predetermined size, i.e. crushed material that cannot pass through the screening device 40, is fed to the crushing chamber 9.

The screening device 40 is preferably designed in accordance with WO 2014/067867 and can have one or all of the features of the screening device described therein. In particular, it can be provided that the screening device 2 comprises a finger screen and/or sliding shoes are provided and/or elastic damping elements and/or rubber buffers.

The roller crusher 1 also has a guide element 44 which is separate from the rocker 8 and which is attached to the machine frame 2. The guide element 44 is separate from the rocker 8 and stationary and does not move together with the rocker 8, neither when adjusting the crushing gap nor during any overload compensation movement of the rocker 8. The guide element 44 is preferably formed in accordance with WO 2014/067858 A1 and has one or all of the features of the guide element according to WO 2014/067858 A1.

Both the rocker 8 and the guide element 44 and the roller 4 are fitted with crushing jaws 45, 46, 47. The crushing jaws 45, 46, 47 are wear parts that can be replaced. The crushing jaws 45, 46 on the rocker 8 and the guide element 44 are profiled, the crushing jaw 45 on the rocker 8 is wave-shaped or has a convex-concave shape, particularly in the lower area of the crushing gap. The crushing jaws 47 of the roller 4 are arranged in a circle around the roller 4.

Fig. 2 now shows a second embodiment of the roller crusher 1. Identical and similar elements are provided with the same reference numerals, so that reference is made in full to the above description of the first embodiment (Fig. 1). In

In the following, the differences to the first embodiment are particularly highlighted.

The main difference between the second embodiment (Fig. 2) and the first embodiment (Fig. 1) is that the roller adjustment device 30 is designed differently. Firstly, a floating bearing unit 35 is provided for the roller 4, which here is on the first

Shaft shoulder 36 comprises a first bearing housing 37 which is mounted in a first bearing guide 48 on the machine frame 2. The first bearing guide 48 can, for example, comprise a side guide for the first bearing housing 37 which is formed, for example, in the form of a groove or dovetail guide. The first bearing guide 48 can be oil-lubricated and is designed in particular as a plain bearing. With

Referring to Fig. 2 to the right, that is in the direction of the rocker 8, the first

Bearing guide 48 preferably has a stop so that displacement of the roller 4 in

Direction of the rocker 8 is limited so that contact between the rocker 8 and the roller 4 is prevented.

Another difference to the first embodiment is that instead of the

Spring 32, a hydraulic actuator 50 is now provided. The hydraulic actuator 50 is supported on the one hand on the support 34, and on the other hand acts against the first bearing housing 37 in order to adjust and load it towards the rocker 8. It is preferably provided that a piston 51 of the hydraulic actuator 50 does not have to absorb any moments, but is connected to the first bearing housing 37 without moments, for example via a spherical cap. The hydraulic actuator 50 can have an overload protection in the form of a pressure relief valve or bypass valve. In particular, in the embodiment shown in Fig. 2, it can be provided that only an overload protection, either the

Overload protection 22 or the overload protection is provided on the roller adjustment device 30. Preferably, however, a separate overload protection is provided for both the swing adjustment device 10 and the roller adjustment device 30. In this

In this way, the safety of the roller crusher 1 can be further improved.

Fig. 3 shows a schematic cross section through the roller crusher 1 according to Fig. 2 perpendicular to the view in Fig. 2. Fig. 3 shows the roller crusher 1 with the roller 4 and the rocker 8 opposite. Between the roller 4 and the rocker 8 is the crushing gap

BS. The roller 4 has first and second shaft shoulders 36, 38 which extend at opposite axial ends of the roller. The first shaft shoulder 36 is rotatably received in a first bearing housing 37 by means of a ball bearing, as basically described with reference to Fig. 2. The second shaft shoulder 38 is rotatably supported by means of a

Ball bearing is rotatably housed in a second bearing housing 39.

As shown in Fig. 2, the first hydraulic actuator 50 engages the first bearing housing 37, and a second hydraulic actuator 52 is provided on the second bearing housing 39. The hydraulic actuators 50, 52 each serve to apply a breaking force in the direction of the rocker 8 to the roller 4, which is mounted in the floating bearing unit 35. The hydraulic actuators 50, 52 are each supported with one end on the first and second bearing housings 37, 39 and with their opposite end on the

Machine frame 2. A movement of the respective bearing housing 37, 39 of the floating bearing unit 35 results in a corresponding movement of the respective

Hydraulic actuator 50, 52. Each hydraulic actuator 50, 52 preferably has a cylinder and a piston movably attached thereto, wherein under the movement of the

For example, in the case of a hydraulic actuator, this means moving the piston within the cylinder.

In the embodiment shown here, the roller crusher 1 also has a synchronizing device 54, which is connected to the hydraulic actuators 50, 52 via hydraulic lines 56, 58. The synchronizing device 54 serves to couple, in particular to synchronize, the movement of the hydraulic actuators 50, 52, so that the bearing housings 37, 39 move in a coupled or equal manner and in particular a misalignment of the roller 4 is avoided or preferably limited. The synchronizing device 54 is preferably designed such that a movement of one of the hydraulic actuators 50, 52 results in a corresponding movement of the other of the hydraulic actuators 50, 52.

The synchronization device 54 has a plurality of hydraulic cylinders 60, 62, 64, 66.

In the detailed view at the bottom left in Fig. 3, four hydraulic cylinders 60, 62, 64, 66 are shown, which are arranged in a housing 68, for example. It is also conceivable and preferred to provide only two hydraulic cylinders, six, eight or, for example, ten hydraulic cylinders. Half of the hydraulic cylinders 60 - 66 are preferably connected exclusively to one of the hydraulic actuators 50, 52. For example, one, two or more hydraulic actuators 50, 52 are attached to each bearing housing 37, 39 of the floating bearing unit 35, with half of the hydraulic cylinders 60 - 66 of the

Synchronization device 54 is preferably hydraulically connected exclusively to the hydraulic actuators 50, 52 of a bearing housing 37, 39. For example, each

Hydraulic cylinders 60 - 66 of the synchronization device 54 are connected to exactly one hydraulic actuator 50, 52.

A piston 70, 72 protrudes from each of the hydraulic cylinders 60 - 66 with one end protruding from the respective hydraulic cylinder 60 - 66, wherein the end of the piston 70, 72 protruding from the hydraulic cylinder is attached to a mechanical coupling 74. The mechanical coupling 74 is, for example, a plate to which the pistons 70, 72 are attached. The pistons 70, 72 are preferably aligned parallel to one another and orthogonal to the mechanical coupling 62, preferably the plate. Hydraulic cylinders 60 - 66 are connected to the hydraulic actuators 50, 52 via the hydraulic lines 56, 58. The roller crusher preferably has two hydraulic lines 56, 58, wherein one hydraulic line 56 is connected to the hydraulic actuators 52 of a

Bearing housing 39 of the floating bearing unit 35 and the other hydraulic line 58 is connected to the hydraulic actuators 50 of the other bearing housing 37 of the floating bearing unit 35. Preferably, each of the hydraulic lines 56, 58 is connected exclusively to one half of the hydraulic cylinders 60 - 66 of the synchronization device 54.

By way of example, the mechanical coupling 74 in the embodiment of Fig. 3 is

Piston, the synchronizing device 54 having a cylinder 76 with a gas chamber 78, which is preferably filled with a compressible gas, such as nitrogen. The gas chamber 78 is delimited by the mechanical coupling 74, which also acts as a piston here, and a further piston 80, the further piston 80 separating the gas chamber 78 from a hydraulic chamber 82. The hydraulic chamber 82 is preferably filled with a non-compressible hydraulic oil and in particular is connected to a hydraulic pump (not shown) via a hydraulic line.

In the embodiment of Fig. 3, between the synchronizing device 54 and each

A buffer unit 84, 86 is arranged in each case for each hydraulic actuator 50, 52. The buffer units 84, 86 are each connected to the synchronization device 54 and the hydraulic actuators 50, 52 via one of the hydraulic lines 56, 58. The buffer units 84, 86 are preferably designed to be essentially identical. Each buffer unit 84, 86 is designed in particular as a single-acting hydraulic cylinder and each has a cylinder with a piston 88 which separates a gas chamber 90 from a hydraulic chamber 92 and is movable within the cylinder. The gas chamber 90 is preferably filled with a compressible gas such as nitrogen, the hydraulic chamber 92 being filled with a non-compressible hydraulic oil and being connected to the respective hydraulic line 56, 58 so that hydraulic oil can flow from the respective hydraulic line 56, 58 into the hydraulic chamber 92. The buffer units 84, 86 serve as buffers between the synchronization device 54 and the hydraulic actuators 50, 52, so that the hydraulic actuators 50, 52 are at least partially decoupled from the synchronization device 54 if the movement of the hydraulic actuators 50, 52 does not exceed a certain travel limit value. The travel limit value is preferably a

Deviation of the position of the hydraulic actuator 50, 52 relative to a zero position, which corresponds to the desired size of the crushing gap BS. In this way, a limited misalignment can be made possible and in particular one-sided forces that act on the

roller. In this respect, the buffer units 84, 86 also act as

Roller overload protection and allow roller 4 to partially avoid the movement. The

Gas chamber 78 serves as overload protection and allows the roller 4 as a whole to deflect via the synchronization device 54.

As an alternative to the first and second hydraulic actuators 50, 52, a mechanical coupling for the first and second bearing housings 37, 39 can also be provided directly, which then only interacts with a single or several hydraulic actuators, and in this respect always causes a coupling of the first and second bearing housings 37, 39.

It should also be understood that the buffer units 84, 86 are only optional.

When considering actuators for adjusting the roller 4 below, it should be understood that these are always mounted either on the bearing housing 37, 39 as with reference to

Fig. 3 or in a common mechanism that connects the bearing housings 37, 39, such as a separate bearing housing that uniformly accommodates the first and second shaft shoulders 36, 38.

In addition, instead of the synchronizing device 54, as described in Fig. 3, a

Synchronization device as described in WO 2021/023643, in particular alternative designs of both the synchronization device and the buffer units described therein.

The embodiment of the roller crusher 1 shown in Fig. 4 is in turn based on the embodiment of the roller crusher 1 shown in Figs. 1 and 2, wherein again identical and similar elements are provided with the same reference numerals. In this respect, reference is made in full to the above description of Figs. 1 and 2.

A significant difference to the first and second embodiments (Fig. 1, 2, 3) lies in the design of the roller adjustment device 30. This is purely mechanical and comprises a roller counterweight 94, which, via a traction cable 96, which is connected via a first deflection 97 to the machine frame 2 and a second deflection 98, also to the machine frame 2, acts on a support element 99, which in turn loads the roller 4 in the direction of the rocker 8. The support element 99 is in a

Guide is slidably mounted on the machine frame 2 and can be connected either directly to the

Roller 4 or a shaft shoulder 36, 38 or as described with reference to Fig. 3, with the first or second bearing housing 37, 39. A separate roller counterweight 94 can be provided for the first and second shaft shoulder 36, 38, or a roller counterweight 94 is provided for the roller 4 as a whole. If two separate roller counterweights are provided, a

By coupling these counterweights, a synchronization device can also be realized.

In this way, a passive roller adjustment device 30 is realized, which can also function as overload protection. The roller counterweight 94 can, for example, be selected so that it is only raised by deflection of the roller 4 when an overload threatens.

A fourth embodiment shown in Fig. 5 is essentially based on the third embodiment shown in Fig. 4 and identical and similar elements are again provided with the same reference numerals. In this respect, reference is made in full to the above description of Fig. 4. The roller adjustment device 30 according to the fourth embodiment (Fig. 5) again uses the roller counterweight 94, which, however, in the embodiment shown here does not act on the support element 99, but on a

Roller wedge 100. The roller wedge 100 bridges a gap between a contact surface 102 arranged on the rear side of the bearing and a counter surface 104 assigned to a roller abutment 34, wherein in a second position P2 of the roller wedge 100 in the gap the crushing gap BS is larger than in a first position P1. The second position

P2 is a lower position with reference to Fig. 5, while position P1 is an upper position. In the embodiment shown in Fig. 5, the contact surface 102 is not arranged directly on the bearing housing 37, but on a support element 99. The

Support element 99 can be integral or otherwise connected to the bearing housing 37, or the contact surface 102 is arranged directly on the bearing housing.

Furthermore, both the contact surface 102 and the counter surface 104 are arranged at an angle, which is not absolutely necessary. In particular, it can be provided that only the contact surface 102 or the counter surface 104 are arranged at an angle. Furthermore, a stop 106 is provided, which can be adjusted by means of one or more spacers and which prevents the roller wedge 100 from coming out in the vertical direction. In this way, a displacement of the roller 4 in the direction of the rocker 8 can be limited.

This dimension can be limited by inserting certain spacers.

The other embodiments shown in Fig. 6 to 8 are initially based on the

Essentially on the embodiment shown in Fig. 1, wherein the

Swing arm adjustment device 10 is designed differently. Again, identical and similar elements are provided with the same reference numerals and reference is made in full to the above description.

In the fifth embodiment (Fig. 6), the swing wedge drive 16 comprises instead of a

Hydraulic or pneumatic drive 18 a mechanical drive, for example a

Spindle drive 108, with a nut 109 which is rotatably arranged within a nut housing and rotates about an axially movable, but not rotating spindle 110.

The spindle 110, like the hydraulic or pneumatic piston 20 (Fig. 1), is connected in an articulated manner to the swing wedge 12 and can drive it. A predetermined breaking point 112 is provided here as a swing overload protection 22, which is formed on the spindle 110 and breaks at a certain tensile load so that the swing 8 can open.

It should be understood that the swing arm adjustment device 10 according to the fifth

Embodiment (Fig. 6) can also be combined with each of the roller adjustment devices 30 according to the embodiments 1, 2, 3 and 4. Furthermore, the swing adjustment device 10 according to the fifth embodiment can be used both with and without overload protection. The same also applies to all roller adjustment devices disclosed herein, which are each preferred and possible with and without overload protection.

In a sixth embodiment, the roller crusher 1 is again based on the first embodiment according to Fig. 1 and identical and similar elements are provided with the same reference numerals. In this respect, reference is made in full to the above description.

Reference is made. Again, in the sixth embodiment (Fig. 7), the swing arm adjustment device 10 is different, which here comprises a swing arm wedge drive 16 that uses a swing arm counterweight 114 and thus uses the same principle that was already described with reference to Figs. 4 and 5. The swing arm counterweight 114 is connected to a cable 116 that is guided over a first swing arm-side deflection roller 117 and is connected at the other end to the swing arm wedge 12, so that the weight of the swing arm counterweight 114 loads the swing arm wedge 12 into the first, upper position. As already described with reference to Fig. 5, a stop 118 is also provided in the embodiment according to Fig. 7, which limits movement of the swing arm wedge 12 in the vertical direction. The effect of the stop 118 can also be adjusted, in particular by using one or more washers, spacers or the like.

Here again, the swing arm adjustment device 10 is designed according to the sixth

embodiment can be combined with all roller adjustment devices 30 of the previous embodiments. The combination with the

Roller adjustment devices 30 according to Fig. 4 and 5. A seventh embodiment (Fig.

8) is based on the fifth embodiment (Fig. 6) and identical and similar elements are again provided with the same reference numerals. In contrast to the fifth embodiment according to Fig. 6, in the seventh embodiment according to Fig. 8 no predetermined breaking point 112 is provided as overload protection 22, but a spring 120. This has the

The advantage is that when the overload protection 22 is triggered, the spindle 110 does not have to be replaced, but only the spring 120 is deflected.

List of reference symbols (part of the description) 1 Roll crusher 2 Machine frame 4 Roller 6 Swing arm axle 7 Screening chamber 8 Swing arm 9 Crushing chamber 10 Swing arm adjustment device 12 Swing arm wedge 13 Contact surface on the rear of the swing arm 14 Abutment 15 Counter surface 16 Swing arm wedge drive 17 Swing arm counter element 18 Hydraulic or pneumatic drive 19 Hydraulic or pneumatic cylinder 20 Hydraulic or pneumatic piston 22 Swing arm overload protection 23 Pressure relief valve

Roller adjustment device 32 first spring 34 support 30 35 floating bearing unit 36 first shaft shoulder 37 first bearing housing 38 first shaft shoulder 39 second bearing housing

Sieving device

42 stationary abutment 44 guide element 45,46,47 crushing jaws 48 first bearing guide 50 first hydraulic actuator 51 piston 52 second hydraulic actuator 54 synchronization device 56 hydraulic line 58 hydraulic line 60, 62, 64, 66 hydraulic cylinder 68 housing 70,72 piston 74 mechanical coupling 76 cylinder 78 gas chamber 80 further piston 82 hydraulic chamber 84 first buffer unit 86 second buffer unit 88 piston of the buffer unit 90 gas chamber of the buffer unit 92 hydraulic chamber of the buffer unit 94 roller counterweight 96 traction cable 97 first deflection roller 98 second deflection roller 99 support element 100 roller wedge 102 contact surface 104 counter surface 106 stop 108 spindle drive 109 nut 110 spindle 112 predetermined breaking point 114 swing counterweight

116 Rope 117 Pulley 118 Stop 120 Spring

BS crushing gap

P1 first position

P2 second position

Claims (15)

Patent claims 1. Roll crusher (1) with a machine frame (2), with a rotatable roll (4), with a rocker (8) mounted on a rocker axis (6) on the machine frame (2), with a crushing chamber (9) between the roll (4) and the rocker (8), wherein an adjustable crushing gap (BS) is formed between the roll (4) and the rocker (8) at a lower end of the crushing chamber, wherein the roll (4) is loosely mounted on the machine frame (2), and with a roll adjustment device (30) for adjusting the roll (4) perpendicular to its axis of rotation (5) in the direction of the rocker (8) to adjust the crushing gap (BS). 2. Roll crusher according to claim 1, comprising a swing arm adjustment device (10) which is arranged at a distance from the swing arm axis (6) between the swing arm (8) and a swing arm abutment (14) fixed to the machine frame (2) in order to enable rotation of the swing arm (8) about the swing arm axis (6). 3. Roll crusher according to claim 2, wherein the swing arm adjusting device (10) has a swing arm wedge (12) arranged between the swing arm (8) and the swing arm abutment (14), which bridges a gap between a contact surface (13) arranged on a swing arm rear side and a counter surface (15) assigned to the swing arm abutment (14), wherein in a second position (P2) of the swing arm wedge (12) in the gap the crushing gap (BS) is larger than in a first position (P1), wherein the swing arm abutment (14) is formed by a rotation axis on which a swing arm counter element (17) with the counter surface (15) formed thereon is freely rotatable. 4. Roller crusher according to one of the preceding claims, comprising a floating bearing unit, wherein the roller (4) is accommodated in a floating bearing unit (35), and wherein the roller adjustment device (30) engages the floating bearing unit (35) for adjusting the roller (4). 5. Roll crusher according to one of the preceding claims, wherein the roll adjusting device (30) has at least one first roll wedge (100) which forms a gap between a contact surface (102) arranged on a rear side of the bearing and a Roller abutment (34) associated counter surface (104) is bridged, wherein in a second position (P2) of the roller wedge (100) in the gap the crushing gap (BS) is larger than in a first position (P1). 6. Roller crusher according to one of the preceding claims, comprising a synchronizing device (54) for the roller (4), which is designed to limit skew to a predetermined amount. 7. Roller crusher according to one of the preceding claims, wherein the roller adjusting device (30) has at least one first spring (32), wherein the crushing gap (BS) can be expanded against the force of the first spring (32). 8. Roller crusher according to one of the preceding claims, wherein the roller adjusting device (30) has at least one first hydraulic or pneumatic actuator (50, 52) for adjusting the crushing gap (BS). 9. Roller crusher according to one of the preceding claims, wherein the roller adjusting device (30) has at least a first spindle drive for adjusting the crushing gap. 10. Roller crusher according to one of the preceding claims, wherein the roller adjustment device (30) has at least one roller counterweight (94), wherein the crushing gap (BS) can be expanded against the weight of the roller counterweight (94). 11. Roller crusher according to one of the preceding claims, wherein the roller adjustment device (30) has at least one roller overload protection. 12. A roller crusher according to claim 11, wherein the roller overload protection comprises at least one of the following: predetermined breaking point, mechanical spring, bypass valve, pressure relief valve, counterweight. 13. Roll crusher according to claim 2 or 3, wherein the swing arm adjustment device (10) comprises at least one of the following: spring (120), hydraulic piston (18), pneumatic piston, spindle drive (108), swing arm counterweight (114). 14. Method for operating a roller crusher (1), preferably according to one of the preceding claims, comprising the steps: - conveying crushed material to the roller crusher (1); - screening crushed material below a predetermined grain size; - feeding crushed material above the predetermined grain size to the crushing chamber (9); - adjusting the roller (4) to widen the crushing gap (BS) in the event that crushed material of an unsuitable grain size and/or made of an unsuitable material enters the crushing chamber (9). 15. Method according to claim 14, comprising the step: - adjusting the rocker (8) to widen the crushing gap (BS) in the event that crushed material of an unsuitable grain size and/or made of an unsuitable material enters the crushing chamber (9).