EP3271076A1

EP3271076A1 - Comminuting device

Info

Publication number: EP3271076A1
Application number: EP16704429.6A
Authority: EP
Inventors: Felix Scharfe; Oscar SCHARFE
Original assignee: PMS Handelskontor GmbH
Current assignee: PMS Handelskontor GmbH
Priority date: 2015-03-18
Filing date: 2016-02-11
Publication date: 2018-01-24
Anticipated expiration: 2036-02-11
Also published as: CL2017002365A1; US10639639B2; ES2735436T3; WO2016146306A1; CN107708867B; CA2982538A1; US20180243747A1; MX2017011961A; BR112017019974A2; PT3271076T; AU2016232614B2; JP6563026B2; RU2667753C1; PL3271076T3; WO2016146307A1; DE102015104078A1; BR112017019974B1; JP2018508357A; EP3271076B1; CA2982538C

Abstract

The invention relates to a comminuting device comprising a cylinder casing which surrounds a comminuting chamber, in which several rotors (30, 32, 34) can be operated independently from each other with individual drives, said rotors being driven by concentric shafts (14, 16, 18) which are arranged concentrically to the central axis (z) of the comminuting chamber, said concentric shafts having a central shaft (14) and at least one outer hollow shaft (16, 18) surrounding said central shaft. At least one lubricant line for connecting to a lubricant supply (66) is arranged in the central shaft (14) and/or in a shaft casing, said said lubricant line being connected by means of at least one radial lubricant through guide (68) to at least one bearing (22, 26, 28) of the rotors.

Description

comminution device

Technical area

The present invention relates to a crushing apparatus comprising a cylinder shell surrounding a cylindrical crushing chamber. In the crushing chamber a plurality of rotors are driven via mutually concentric waves and operated independently of each other. The rotors are arranged concentrically to the central axis of the crushing chamber. The concentric shafts comprise a central shaft and at least one outer hollow shaft surrounding it. Such a comminution device is known, for example, from DE 10 2013 110 352 A. As in the present invention also in this prior art impact tools are connected to at least two of the rotors. One of the rotors can also be a fan rotor. The crushing of the materials creates splinters and dust, which can affect the bearings of the coaxial shafts or reduce their lifetime.

It is an object of the invention to provide a crushing device that allows a longer life of the rotors and their bearings. This object is achieved by a crushing device with the features of claim 1. Advantageous developments of the invention are the subject of the dependent claims. Further developments of the invention are also described in the description and illustrated in the drawings. Presentation of the invention

According to the invention, at least one lubricant line for connection to a lubricant supply is arranged in the central shaft and / or in a shaft casing, which lubricant line is connected to at least one bearing of the rotors via at least one radial lubricant feedthrough.

The invention thus makes it possible to transport lubricant via longitudinal bores arranged in the shafts to the shaft bearings. These longitudinal bores extend in the axial direction of the shafts and act as a lubricant conduit to produce a lubricant, i. E. to supply an oil and / or grease to the axial areas in which the shaft bearings are arranged. Of course, a plurality of separate longitudinal bores, ie lubricant lines for different shaft bearings may be provided in order to be able to supply an individual lubricant quantity and / or an individual lubricant pressure to the individual shaft bearings. Of course, the lubricant line can, for example, pass seamlessly into the lubricant feedthrough, if these z. B. at the end where the shaft bearing is bent outwards. Of course, the lubricant line could also be inclined slightly outwards so that it exits the shaft jacket exactly in the axial bearing area. Here, the lubricant line and the lubricant feedthrough would be integrated, for example, by an inclined arrangement of a hole in the shaft jacket. Usually, however, the lubricant line are formed by an axial bore in the shaft jacket and the lubricant feedthrough through a radial bore in the shaft jacket. If a primarily axially extending but slightly inclined bore is provided in the shaft jacket, the lubricant line and the lubricant feedthrough is integrated in a bore in the shaft jacket.

The lubricant feedthrough can z. B. directly into the warehouse, however, would require a processing of the bearing here, e.g. the provision of lubricant supply holes in the bearing outer shell. Therefore, the lubricant feedthrough preferably opens into an annular region, on / in which a shaft bearing is arranged. The lubricant is thus supplied to the shaft bearing of he open side.

Of course, shaft bearings can be supplied with lubricant, which lie radially outside and radially inside the lubricant feedthrough. Thus, the lubricant bushing z. B. extend through the entire thickness of the shaft jacket and then opens into an axial region within and outside of the shaft jacket. In this way, for. B. two bearings can be supplied directly with lubricant. In an advantageous embodiment of the invention, the annular region is formed in a first axial direction by a bearing and in the opposite second axial direction by a lubricant seal. The lubricant seal then forces the lubricant in the ring area towards the bearing, where it can effectively contribute to the lubrication of the shaft bearing. The lubricant seal is preferably gas-permeable. This has the advantage that a pressurized gas loading of the shaft assembly can pass the lubricant seal, whereby the pressurized gas, e.g. Compressed air can pass through the bearings to the outside into the crushing chamber. In this way, the storage area can be effectively kept free of dust from the crushing chamber.

Preferably, the lubricant line is connected to the end face of the rotors with a ring feed space, so that the lubricant line, the lubricant can be fed regardless of the rotational position of the waves. Preferably, a lubricant line is arranged in the central shaft or in the intermediate space, which is connected to at least one bearing. In this way, the bearing or the bearings are not only flowed around with air, so that no material dust can penetrate into them, but the bearings also lubricant is supplied, whereby their lubrication is ensured during operation. The lubricant is preferably supplied to the bearings via radial lubricant feedthroughs formed in the shrouds. This measure, too, considerably increases the life of the bearings and thus cooperates with the gas supply in a symbiotic manner, because the gas ensures that the lubricant is not contaminated by material particles formed during comminution, in which case the dirty lubricant acts as an abrasive would.

Preferably, the central shaft is formed as a hollow shaft and the lubricant line extends in the cavity of the central shaft, which for connection to a

Lubricant supply is designed. In this way, the bearings are supplied with the lubricant through the cavity in the central shaft. Thus, not only the bearings between the shafts can be lubricated, but also a bearing between the central shaft and a fixed structure of the comminution device with respect to the motor / bearing block.

Preferably, at least one shaft has in its shaft jacket a radial lubricant feedthrough from the inside of the shaft to the outside of the shaft, which lubricant feedthrough is connected to a bearing arranged there. In this way, the lubricant can be easily distributed from the central shaft to the surrounding bearings between the central shaft and the outer shaft or between the plurality of outer hollow shafts.

When referred to in this application of "radial", this means that the orientation has a radial component. The direct radial alignment of the corresponding component is only a preferred embodiment.

In an advantageous development of the invention, at least one shaft in the region of its lubricant feedthrough contains a radially extending lubricant channel which bears against the wall of the adjacent shaft in the region of a lubricant feedthrough arranged in the latter. The lubricant channel is rotatably connected to the shaft. In this way it is achieved that per revolution of the lubricant channel is aligned at a once with the lubricant passage of the adjacent shaft, wherein the lubricant can be transmitted in accordance with radial. Thus, the lubricant can be guided radially outward or inward so that the lubricant once per Rotation passes through a lubricant feedthrough of a radially further outward or inward shaft.

The lubricant channel then preferably has a contact material which is slidable with respect to the material of the shaft, at least in the region abutting against the wall.

Preferably, the crushing device has means for determining the position of each individual shaft. It is then preferably provided an electronic control in which a lubricating position of the mutually concentric shafts is stored, in which the lubricant channel is aligned with the lubricant passage of the adjacent shaft. In this lubrication position then the lubrication of the bearings can be done when the short-term alignment of the lubricant channel with the lubricant passage during normal operation is not sufficient to ensure a lubricant supply to the radially remote bearings.

Preferably, the lubricant channel at least in the voltage applied to the wall of the adjacent shaft region with respect to the material of the shaft slidable contact material, whereby the lubricant channel easily and without significant friction d. H. Heat generation during operation can slide along the wall of the adjacent wave. Between the lubricant channel and the wall of the adjacent shaft, such a small distance, d. H. Gap, be provided that leakage of lubricant from this gap to a significant extent is not possible. Preferably, the radial lubricant passage extends into an annular region which is sealed in a first axial direction by a bearing and in the opposite second axial direction by a lubricant seal, which is in particular annular. In this way, it is avoided that the lubricant is supplied to the entire space, but essentially only the bearing. In the remaining space can thus be supplied, for example, gas to keep the bearings free of material dust.

Preferably, the lubricant seal is gas-permeable so as to prevent lubricant from entering the rest of the space from the area of the bearing, but on the other hand allowing passage of gas from the clearance to the bearing and lubricated area.

In an advantageous embodiment of the invention, an interior space and / or between the waves at least one intermediate space is formed in the central shaft, which inner / intermediate space at least partially as a gas supply space for connection to a Gas supply is formed, which gas supply space is connected to at least one arranged between the shafts shaft bearing. In this way, the bearings not only the lubricant but also gas, eg air supplied to keep the bearings dust-free. This has the synergistic effect that also the lubricant supplied to the bearings is not mixed with dust, which could cause an unfavorable emery effect. The shaft bearings thus remain both clean (dust-free) and lubricated.

Preferably, the space is connected to an end piece rotatably mounted thereon, which has a gas supply opening for connection to a gas supply. In this way we control the gas supply regardless of the rotational position of the waves.

Preferably, at least one of the shafts has a gas passage extending radially in the shaft jacket, which is connected to a shaft bearing. These allow the gas to be distributed easily in the radial direction.

In an advantageous development of the invention, the gas feedthrough opens into a first gas ring area which is formed in a first axial direction by a bearing and in the opposite second axial direction by an annular gas seal. About this gas ring area, the gas can be supplied to the shaft bearing very effective large area from the side. In addition, modifications of the bearing, e.g. the provision of Gaszuführöffnungen in the bearing outer shell are not necessary.

Preferably, the central shaft has an axially extending cavity or inner space, which is connected on the one hand via a radially extending in the shaft jacket gas passage with the gap and on the other hand designed for connection to a gas supply. In this way, the gas from the central gas supply from the interior in the central shaft can be effectively supplied to the spaces between the waves. All shaft bearings are flushed with gas between several coaxial shafts.

In an advantageous development of the invention, the gas supply is formed by a fan, which is easy to implement. Preferably, all gaps between the shafts are connected to the gas supply, so that all shaft bearings of the comminution device are flushed with gas and thus have a long service life. In the gas supply, the space between the concentric shafts is preferably used to supply air or any other gas to the bearings interposed between the shafts and possibly also a bearing between the central shaft and a fixed structure of the crusher to remove the dust from crushing Keep away dust from these warehouses. The gas supply may in this case be, for example, a fan which supplies the ambient air, possibly filtered, to the bearings. The gas supply may also be connected to a cavity in the central shaft, by means of which the supplied air or the supplied gas is passed to the gaps between the waves via radial gas passages.

This solution according to the invention has the advantage that the bearings for the rotors are exposed to significantly lower wear, the shafts themselves need only be minimally changed. Thus, only small radial through holes in the shrouds are necessary to be passed as a gas feedthrough to more outboard spaces, for example between the central shaft and the first outer shaft or between the first outer shaft and a second outer shaft surrounding it , It must be drilled in the shrouds no axial gas lines, which would be associated with a relatively high cost. Thus, the invention allows a very easy to implement protection of the bearings of the rotors of a crushing device.

Needless to say, the concentric shafts on at least one side are driven by drive motors, e.g. a combined motor / bearing block, are connected, over which they are driven independently. These motors are preferably arranged on an end face of the shafts. On this page, the shafts in the engine / bearing block are also mounted on the engines. On the opposite side is preferably at least the central shaft to a fixed structure, for. B. frame or end wall of the crushing chamber stored. Preferably, the gas feedthrough opens into an annular region of a gap, which is formed on the one hand by a bearing and on the other side by an annular gas seal. In this way, the gas is not supplied to the entire gap, but only a limited axial area of the gap between the gas seal and the bearing.

Preferably, the central shaft has an axial hollow / inner space which is used in conjunction with a gas supply as a gas supply to the gap. The axial cavity of the central shaft is connected on the one hand via a radially extending in the shaft jacket gas passage with the gap and on the other hand, it is designed for connection to a gas supply, for example a fan. This is done in this way the supply of the gas, in particular the air, over the axial cavity in the central shaft and is from there into the space between the central shaft and a first outer hollow shaft and possibly from there into further spaces between other outer hollow shafts. The number of waves preferably corresponds to the number of rotors, wherein the number of rotors, that is, the concentric waves is preferably between two and five.

Preferably, the gap and / or the cavity of the central shaft is connected to an end piece rotatably mounted thereon which has a gas supply opening for connection to a gas supply. In this way, the gas can be supplied to the annular gap / cavity of the central shaft in a simple manner.

The gas supply may be formed by a blower in a simple embodiment, but it can also other compressed gas devices, eg. B. pressure pumps or compressed gas storage can be used. The simplest gas is the atmospheric air. In the case of certain materials, however, it may be useful to supply inert gases, such as CO ₂ or nitrogen, to prevent oxidation or ignition of materials during comminution. In this way, not only the bearings are kept dust-free, but the crushing chamber can also be flushed with a desired gas, which is important for the crushing process itself.

In one embodiment of the invention, all intermediate spaces between the shafts are connected to the gas supply, which has the advantage that all bearings between all concentric shafts are flushed with the gas supplied and thus remain free of crushed material.

The following expressions are used synonymously: shaft bearings - bearings; Longitudinal bore - Lubricant line; Cavity - interior - lubrication line; The embodiments of the invention described above can be combined with one another in any desired manner, as long as several features are not technically contradictory.

The invention will be described below by way of example with reference to the schematic drawing. In this show:

Fig. FIG. 1 is a first partially sectioned view of a shredder with three rotors and three concentric shafts with combined gas and lubricant supply. FIG. Ways to carry out the invention

In the figures, identical or functionally identical parts are described with the identical reference numerals.

Fig. FIG. 1 shows a comminution device 10 in a very diagrammatic partially sectioned view along its longitudinal axis z. The cylinder jacket and the entire bottom portion of the crushing device are not shown. The comminuting device 10 comprises a motor / bearing block 12 which rotatably supports and drives three shafts concentric with each other, namely a central hollow shaft 14, a first outer hollow shaft 16 surrounding it, and a second outer hollow shaft 18 surrounding the first outer hollow shaft 16. The three hollow shafts 14, 16, 18 are arranged concentrically about the central axis Z of the crushing chamber. At least one, preferably two, in particular each concentric shaft 14, 16, 18 carries impact tools 20 for crushing top fed material (e.g., mineral conglomerates). The three shafts 14, 16, 18 are individually controllable via three separate motors in the motor / bearing block 12, so that they are each driven in opposite directions and with increasing speed. In this way, a very effective crushing of the supplied material can be achieved. Not shown in the drawing is a cylinder jacket, which surrounds the rotors 14, 16, 18 and defines a crushing chamber in its interior. The central hollow shaft 14 is mounted at its lower end to the motor / bearing block 12 and at the opposite upper end by means of a first bearing 22 to a fixed structure 24 of the crushing device 10, for example a wall. The first outer hollow shaft 16 is supported radially relative to the central hollow shaft 14 with a second bearing 26 and centered. The second outer hollow shaft 18 is radially supported and centered with respect to the first outer hollow shaft 16 with a third bearing 28. The three bearings 22, 26, 28 ensure that the concentric waves remain concentrically aligned when crushing material. The sections of the concentric shafts 14, 16, 18 which are not covered on the outside form rotors 30, 32, 34 to which the striking tools 20 are anchored in a manner not described in greater detail. Preferably, the

Impact tools 20 on the rotors 30, 32, 34 held interchangeable. The striking tools 20 may be rods or chains or the like per se known functional elements, as they are known from DE 10 2013 110 352 A. When crushing materials, especially mineral-containing materials, a lot of dust is generated, which could quickly affect or destroy the bearings of the waves.

In order to lubricate the bearings well, there is a lubricant supply to the bearings 22, 26, 28. In the crushing device 10 shown here, the central cavity 62 of the central hollow shaft 14 is formed as a lubricant line, which via a lubricant supply line 64 with a lubricant supply 66, for example one Pressure lubrication device is connected. In the region of the first bearing 22, the central cavity 62 has a first radial lubricant feedthrough 68 which leads directly to the first bearing 22 and thus leads to a lubrication of the first bearing 22. A second lubricant passage 68 leads into an inner annular space 70, which is formed between the second bearing 26 and an annular lubricant seal 72. The lubricant seal 72 causes the lubricant is supplied only to the inner annular space 70 and thus the bearing 26 and not into the underlying first gap 44. In the central hollow shaft 14, a further lubricant passage 68 is also provided, which opens into a lubricant channel 74, which is fixed radially on the outside of the central hollow shaft 14. On the outside, the lubricant channel 74 bears against the inner wall 76 of the first outer hollow shaft 16 and is arranged at a height in which the lubricant channel 74 can be aligned with an outer lubricant passage 78 in the first outer hollow shaft 16. As a result, the lubricant channel 74 in a certain rotational position of the central hollow shaft 14 relative to the first outer hollow shaft 16 with the outer lubricant passage 78 of the first outer hollow shaft 16 are aligned. Thus, an outer annulus 80 is supplied between the first outer hollow shaft 16 and the second outer hollow shaft 18 lubricant, which outer annulus 80 is limited downwardly by an annular lubricant seal 72 and upward through the third bearing 28. In this way is also the third outermost bearing 28 supplied enough lubricant. If the short alignment of the lubricant channel 74 with the outer lubricant passage 78 is too short to supply enough lubricant to the outer annular space 80 and thus to the third bearing 28, it may be provided that an electronic control transfers the position of the shafts 14, 16, 18 to each other determined corresponding sensors and the central hollow shaft 14 and the first outer

Hollow shaft 16 in a lubricant position can position relative to each other so that the lubricant passage 74 is aligned with the outer lubricant passage 78. In this position, the third bearing 28 can then be lubricated. If it is not aligned with the outer lubricant passage 78, the lubricant passage 74 is closed by the inner wall 76 of the first outer hollow shaft 16. The lubricant channel 74 can either easily slide along the inner wall 76 of the first outer hollow shaft 16 or has a minimal distance to this, which prevents the escape of lubricant.

In addition, the central cavity 62 is connected to a third lubricant feedthrough 68, which supplies lubricant to the uppermost bearing 22. Thus, all bearings 22, 26, 28 are supplied via the central cavity 62 and the lubricant passages 68 lubricant.

Additionally or alternatively to the central cavity 62, a lubricant line 63 (shown in phantom) may be arranged in a shaft wall 14, for. B. in the form of a axial bore, which is connected to the, preferably with all lubricant passages 68. In this way, then, for example, the central cavity 62 can be used for a gas supply. This alternative can also be used if the central shaft 14 has no central cavity 62.

The first intermediate space 44 is connected via a gas line 38 to a gas supply 40, for example a blower. The lubricant seal 72 between the central hollow shaft 14 and the first outer hollow shaft 16 and between the first outer hollow shaft 16 and the second outer hollow shaft 18 are gas-permeable. In addition, in the first outer hollow shaft 16, a gas passage 42 through which a gas supplied from a gas supply 40, e.g. Air, also the second gap 52 between the first outer hollow shaft 16 and the second outer hollow shaft 18 is supplied. As a result, the second bearing 26 and the third bearing 28 are supplied with gas. In this embodiment, therefore, the two bearings 26, 28 are supplied not only with lubricant, but also with a gas, for example, atmospheric air, so that they are not contaminated with dust of the crushed material and thus have a very long life.

At the free end of the central hollow shaft 14, a central cover 46 is arranged, which closes the central cavity 36 towards the free end. At the end of the first outer hollow shaft 16, a first annular cover 48 is arranged, which is spaced around a first gap 50 with respect to the central hollow shaft 14. This first ring cover 46 on the one hand causes a mechanical barrier against the ingress of dust from the crushing chamber. On the other hand, due to the narrowing of the exit in the first gap 50 between the central hollow shaft 14 and the first ring cover 48, the available flow space is extremely reduced, which results in the gas exiting there at a correspondingly increased speed. The protection of the second bearing 26 against the ingress of dust is thereby significantly improved. In the first outer hollow shaft 16, a radial gas passage 42 is arranged, so that the gas is guided into a second intermediate space 52, which is arranged between the first outer hollow shaft 16 and the second outer hollow shaft 18. From there, the gas is supplied to the third bearing 28 and passes through a second gap 54 between the first outer hollow shaft 16 and a second ring cover 49 in the crushing chamber. In the second gap 54, in turn, the gas velocity is increased, so that this provides a very good protection against the ingress of dust and larger material grains in the third bearing 28.

The first bearing may be located outside the crushing chamber, in which case gas purging is not necessarily required. The present invention is not limited to the described embodiments, but may be varied as desired within the scope of the appended claims.

LIST OF REFERENCE NUMBERS

10 crushing device (first embodiment)

12 engine / storage block

14 central hollow shaft

16 first outer hollow shaft

18 second outer hollow shaft

20 striking tools

22 first camp

24 solid structure

26 second camp

28 third camp

30 first rotor

32 second rotor

34 third rotor

36 central cavity

38 gas line

40 gas supply

42 gas passage

44 first gap

46 central cover

48 first ring cover

49 second ring cover

50 first gap

52 second gap

54 second gap

60 crushing device (second embodiment)

62 central cavity

64 lubricant supply line

66 Lubricant supply

68 lubricant feedthrough

70 inner annulus

72 lubricant seal

74 lubricant channel

76 inner wall of the first outer hollow shaft

78 outer lubricant feedthrough

80 outer annulus

Claims

claims

1. Crushing device comprising a cylinder jacket surrounding a crushing chamber in which a plurality of rotors (30, 32, 34) are independently operable with their own drives, which rotors are driven via shafts (14, 16, 18) concentric with one another, which are arranged concentrically to the central axis (z) of the crushing chamber, which concentric waves have a central shaft (14) and at least one surrounding outer hollow shaft (16, 18), characterized in that in the central shaft (14) and / or at least one lubricant line for connection to a lubricant supply (66) is arranged in a shaft jacket, which lubricant line is connected to at least one bearing (22, 26, 28) of the rotors via at least one radial lubricant feedthrough (68).

2. Crushing device according to claim 1, characterized in that the lubricant feedthrough (68) opens into an annular region (70, 80), on / in which a shaft bearing is arranged.

3. Crushing device according to claim 2, characterized in that the annular region in a first axial direction by a bearing (26, 28) and in the opposite translated second axial direction by a lubricant seal (72) is formed.

4. crushing device according to claim 3, characterized in that the lubricant seal (72) is gas-permeable.

5. Crushing device according to one of the preceding claims, characterized in that at least one shaft (14, 16, 18) in the region of its lubricant passage (68) has a radially extending lubricant channel (74) on the wall (76) of the adjacent shaft in the region of a arranged in this lubricant feedthrough (78).

6. Crushing device according to claim 5, wherein the lubricant channel (74) at least in the area adjacent to the wall (76) has a region with respect to the material of the shaft slidable contact material.

7. Crushing device according to one of the preceding claims, characterized in that the lubricant line is connected to the end face of the rotors with a ring feed space.

8. Crushing device according to one of the preceding claims, character- ized in that in the central shaft an interior and / or between the waves at least one intermediate space (44, 52) is formed, which inner / intermediate space is formed at least partially as a gas supply space for connection to a gas supply (40), which gas supply space is connected to at least one shaft bearing (26, 28) arranged between the shafts.

A crushing apparatus according to claim 8, characterized in that the gas supply space is connected to a tail piece rotatably mounted thereon, which has a gas supply opening for connection to a gas supply (40).

10. Crushing device according to claim 8 or 9, characterized in that at least one of the shafts (14, 16, 18) has a radially extending in the shaft jacket gas passage (42) which is connected to a shaft bearing (26).

11. Crushing device according to claim 10, characterized in that the gas passage (42) opens into a first gas ring area, which in a first axial

Direction is formed by a bearing and in the opposite second axial direction by an annular gas seal.

12. Crushing device according to one of the preceding claims, character- ized in that the central shaft (14) has an axial cavity (36), on the one hand via a radially extending in the shaft jacket gas passage (42) with the intermediate space (44, 52). is connected and on the other hand designed for connection to a gas supply (40).

13. Crushing device according to one of the preceding claims, characterized in that the gas supply (40) is formed by a blower.

14. Crushing device according to one of the preceding claims, characterized in that all intermediate spaces (44, 52) between the shafts (14, 16, 18) are connected to the gas supply (40).