EP3271076B1 - Zerkleinerungsvorrichtung - Google Patents

Zerkleinerungsvorrichtung Download PDF

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Publication number
EP3271076B1
EP3271076B1 EP16704429.6A EP16704429A EP3271076B1 EP 3271076 B1 EP3271076 B1 EP 3271076B1 EP 16704429 A EP16704429 A EP 16704429A EP 3271076 B1 EP3271076 B1 EP 3271076B1
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EP
European Patent Office
Prior art keywords
lubricant
shaft
gas
bearing
comminution device
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP16704429.6A
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German (de)
English (en)
French (fr)
Other versions
EP3271076A1 (de
Inventor
Felix Scharfe
Oscar SCHARFE
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
PMS Handelskontor GmbH
Original Assignee
PMS Handelskontor GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by PMS Handelskontor GmbH filed Critical PMS Handelskontor GmbH
Priority to PL16704429T priority Critical patent/PL3271076T3/pl
Publication of EP3271076A1 publication Critical patent/EP3271076A1/de
Application granted granted Critical
Publication of EP3271076B1 publication Critical patent/EP3271076B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
    • B02C13/26—Details
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C13/00—Disintegrating by mills having rotary beater elements ; Hammer mills
    • B02C13/20—Disintegrating by mills having rotary beater elements ; Hammer mills with two or more co-operating rotors
    • B02C13/205—Disintegrating by mills having rotary beater elements ; Hammer mills with two or more co-operating rotors arranged concentrically

Definitions

  • the present invention relates to a crushing apparatus comprising a cylinder shell surrounding a cylindrical 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 crushing device is for example from the DE 10 2013 110 352 A known.
  • 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.
  • WO-2008/122691-A1 discloses a crushing device according to the preamble of claim 1.
  • the crushing device has the features of claim 1.
  • 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 line to supply a lubricant, ie an oil and / or grease, to the axial regions in which the shaft bearings are arranged.
  • 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.
  • the lubricant line may also be e.g. transition smoothly into the lubricant feedthrough, if e.g. at the end, where the shaft bearing is located, is bent outwards.
  • the lubricant line could also be inclined slightly outwards so that it exits the shaft jacket exactly in the axial bearing area.
  • the lubricant line and the lubricant feedthrough would be integrated, e.g. by an inclined arrangement of a bore in the shaft jacket.
  • 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 may be e.g. directly into the warehouse, however, would require machining of the warehouse, 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.
  • shaft bearings can be supplied with lubricant, which lie radially outward as well as radially within the lubricant feedthrough.
  • the lubricant feedthrough may be e.g. 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, e.g. two bearings are supplied directly with lubricant.
  • 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 permeable to gas. 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.
  • 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.
  • a lubricant line is arranged in the central shaft or in the intermediate space, which is connected to at least one bearing.
  • 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.
  • the central shaft is formed as a hollow shaft and the lubricant line extends in the cavity of the central shaft, which is designed for connection to a lubricant supply.
  • the bearings are supplied with the lubricant through the cavity in the central shaft.
  • 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.
  • 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.
  • 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.
  • 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, at least in the region bearing against the wall, a contact material that is slidable with respect to the material of the shaft.
  • 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.
  • the lubricant channel has a contact material which is slidable with respect to the material of the shaft, whereby the lubricant channel is easily and without appreciable friction, i. Heat generation during operation can slide along the wall of the adjacent wave.
  • a small distance, i. Gap be provided that leakage of lubricant from this gap to a significant extent is not possible.
  • 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.
  • a lubricant seal which is in particular annular.
  • 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.
  • 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.
  • 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.
  • the gap is connected to an end piece rotatably mounted thereon having a gas supply port for connection to a gas supply. In this way we control the gas supply regardless of the rotational position of the waves.
  • 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.
  • the gas feedthrough opens into a first gas ring region which is formed in a first axial direction by a bearing and in the opposite second axial direction by an annular gas seal.
  • the gas can be supplied to the shaft bearing very effective large area from the side.
  • modifications of the bearing e.g. the provision of Gaszu Technologyö réelleen in the bearing outer shell are not necessary.
  • the central shaft has an axially extending cavity or interior, 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.
  • 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.
  • the gas supply is formed by a fan, which is easy to implement.
  • 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.
  • 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.
  • only small radial through holes in the shrouds are necessary to be routed as a gas passage to more outward gaps, 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.
  • the invention allows a very easy to implement protection of the bearings of the rotors of a crushing device.
  • 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.
  • the shafts in the engine / bearing block are also mounted on the engines.
  • the central shaft is attached to a fixed structure, e.g. Frame or front wall of the crushing chamber stored.
  • 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.
  • 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.
  • 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.
  • the gap and / or the cavity of the central shaft is connected to an end piece rotatably mounted thereon which has a gas supply port for connection to a gas supply.
  • the gas can be supplied to the annular gap / cavity of the central shaft in a simple manner.
  • the gas supply can be formed in a simple embodiment by a fan, but it can also be used other compressed gas devices, such as pressure pumps or compressed gas storage.
  • the simplest gas is the atmospheric air.
  • 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.
  • all the spaces between the shafts are connected to the gas supply, which has the advantage that all bearings between all concentric waves are flushed with the gas supplied and thus remain free of crushed material.
  • Fig. 1 shows a crushing device 10 in a very schematic 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 in order to crush material supplied from above (eg 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.
  • 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 outside uncovered portions of the concentric shafts 14, 16, 18 form rotors 30, 32, 34, to which the impact tools 20 are anchored in unspecified manner.
  • the impact tools 20 are held interchangeably on the rotors 30, 32, 34.
  • 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 are known.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the central cavity 62 is connected to a third lubricant passage 68 which supplies lubricant to the uppermost bearing 22.
  • all bearings 22, 26, 28 are supplied via the central cavity 62 and the lubricant passages 68 lubricant.
  • a lubricant line 63 (shown by dashed lines) can be arranged in a shaft wall 14, for example in the form of a shaft axial bore, which is connected to the, preferably with all lubricant passages 68.
  • 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.
  • 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.
  • 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.
  • a gas supplied from a gas supply 40 e.g. Air
  • the second bearing 26 and the third bearing 28 are supplied with gas.
  • 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.
  • a central cover 46 is arranged, which closes the central cavity 36 towards the free end.
  • 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.
  • 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.
  • 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Food Science & Technology (AREA)
  • Sliding-Contact Bearings (AREA)
  • Crushing And Pulverization Processes (AREA)
  • Accessories For Mixers (AREA)
  • Crushing And Grinding (AREA)
  • Reciprocating Pumps (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Rolling Contact Bearings (AREA)
EP16704429.6A 2015-03-18 2016-02-11 Zerkleinerungsvorrichtung Active EP3271076B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL16704429T PL3271076T3 (pl) 2015-03-18 2016-02-11 Mechanizm rozdrabniający

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015104078.6A DE102015104078A1 (de) 2015-03-18 2015-03-18 Zerkleinerungsvorrichtung
PCT/EP2016/052939 WO2016146307A1 (de) 2015-03-18 2016-02-11 Zerkleinerungsvorrichtung

Publications (2)

Publication Number Publication Date
EP3271076A1 EP3271076A1 (de) 2018-01-24
EP3271076B1 true EP3271076B1 (de) 2019-06-12

Family

ID=55349834

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16704429.6A Active EP3271076B1 (de) 2015-03-18 2016-02-11 Zerkleinerungsvorrichtung

Country Status (15)

Country Link
US (1) US10639639B2 (ru)
EP (1) EP3271076B1 (ru)
JP (1) JP6563026B2 (ru)
CN (1) CN107708867B (ru)
AU (1) AU2016232614B2 (ru)
BR (1) BR112017019974B1 (ru)
CA (1) CA2982538C (ru)
CL (1) CL2017002365A1 (ru)
DE (1) DE102015104078A1 (ru)
ES (1) ES2735436T3 (ru)
MX (1) MX2017011961A (ru)
PL (1) PL3271076T3 (ru)
PT (1) PT3271076T (ru)
RU (1) RU2667753C1 (ru)
WO (2) WO2016146306A1 (ru)

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Publication number Priority date Publication date Assignee Title
DE102013110352A1 (de) * 2013-09-19 2015-03-19 Pms Handelskontor Gmbh Zerkleinerungsvorrichtung
CN112128121B (zh) * 2020-09-11 2023-01-13 佛山市创联科技有限公司 一种空气压缩装置

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Also Published As

Publication number Publication date
CA2982538A1 (en) 2016-09-22
US20180243747A1 (en) 2018-08-30
BR112017019974B1 (pt) 2021-06-29
CA2982538C (en) 2019-02-26
AU2016232614B2 (en) 2019-02-07
ES2735436T3 (es) 2019-12-18
JP2018508357A (ja) 2018-03-29
MX2017011961A (es) 2018-06-07
DE102015104078A1 (de) 2016-09-22
RU2667753C1 (ru) 2018-09-24
JP6563026B2 (ja) 2019-08-21
BR112017019974A2 (pt) 2018-06-19
AU2016232614A1 (en) 2017-11-02
US10639639B2 (en) 2020-05-05
WO2016146307A1 (de) 2016-09-22
CL2017002365A1 (es) 2018-03-09
CN107708867B (zh) 2020-10-16
EP3271076A1 (de) 2018-01-24
PT3271076T (pt) 2019-07-23
WO2016146306A1 (de) 2016-09-22
CN107708867A (zh) 2018-02-16
PL3271076T3 (pl) 2019-10-31

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