WO2008012096A9 - Mécanisme de transmission pour un dispositif de concassage - Google Patents

Mécanisme de transmission pour un dispositif de concassage

Info

Publication number
WO2008012096A9
WO2008012096A9 PCT/EP2007/006656 EP2007006656W WO2008012096A9 WO 2008012096 A9 WO2008012096 A9 WO 2008012096A9 EP 2007006656 W EP2007006656 W EP 2007006656W WO 2008012096 A9 WO2008012096 A9 WO 2008012096A9
Authority
WO
WIPO (PCT)
Prior art keywords
power transmission
transmission device
drive
drive unit
absorber
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.)
Ceased
Application number
PCT/EP2007/006656
Other languages
German (de)
English (en)
Other versions
WO2008012096A3 (fr
WO2008012096A2 (fr
Inventor
Peter Roessler
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.)
Weima Maschinenbau GmbH
Original Assignee
Weima Maschinenbau 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 Weima Maschinenbau GmbH filed Critical Weima Maschinenbau GmbH
Publication of WO2008012096A2 publication Critical patent/WO2008012096A2/fr
Publication of WO2008012096A9 publication Critical patent/WO2008012096A9/fr
Publication of WO2008012096A3 publication Critical patent/WO2008012096A3/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • B02C18/00—Disintegrating by knives or other cutting or tearing members which chop material into fragments
    • B02C18/06—Disintegrating by knives or other cutting or tearing members which chop material into fragments with rotating knives
    • B02C18/16—Details
    • B02C18/24—Drives
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C17/00—Disintegrating by tumbling mills, i.e. mills having a container charged with the material to be disintegrated with or without special disintegrating members such as pebbles or balls
    • B02C17/18—Details
    • B02C17/24—Driving mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
    • F16D3/56—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic metal lamellae, elastic rods, or the like, e.g. arranged radially or parallel to the axis, the members being shear-loaded collectively by the total load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
    • F16D3/64—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic elements arranged between substantially-radial walls of both coupling parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
    • F16D3/64—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic elements arranged between substantially-radial walls of both coupling parts
    • F16D3/68—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic elements arranged between substantially-radial walls of both coupling parts the elements being made of rubber or similar material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
    • F16D7/02—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type
    • F16D7/024—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with axially applied torque limiting friction surfaces
    • F16D7/025—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with axially applied torque limiting friction surfaces with flat clutching surfaces, e.g. discs

Definitions

  • the invention relates to a power transmission device for a crushing device for transmitting a driving force from a drive unit to a crushing rotor, a crushing device.
  • Belt drives provided with a large gear ratios, which transmit the driving force of a drive unit to the crushing rotor.
  • Such belt drives take up much space relative to the entire crushing device.
  • such belt drives must be totally enclosed for safety reasons.
  • the belts are subject to significant wear, so that the belt drives significantly determine the maintenance of such shredding devices.
  • Object of the present invention is to provide a power transmission device of the type mentioned in such a way that the need for maintenance is reduced.
  • the power transmission device comprises at least one torsional vibration absorber and at least one torque-dependent working coupling element, which are connected in series.
  • a power transmission device which is preferably connected via a drive shaft with the drive unit and preferably via an output shaft with the crushing rotor.
  • the torsional vibration absorber has the function to absorb small-pitch angle shocks and corresponding torque fluctuations caused by the ever-changing resistance in crushing the material.
  • Such changes in resistance result from the fact that the material to be crushed is usually composed of bodies which differ in size, shape and / or strength. Besides, these bodies can be in different positions between the comminution tools of the comminution rotor and corresponding blades advised, whereby also different forces for crushing the body are required.
  • the load of the drive unit and the comminution rotor and thus the wear and the maintenance susceptibility is significantly reduced by the torsional vibration absorber.
  • the torque-dependent coupling element causes the comminution rotor to be at least partially uncoupled from the power pack and thus both components protected from destruction.
  • the crushing device can then be reversed, often releasing deadlocks, where it does not, it can also be stopped and the jammed material can then be manually removed. Since no components are destroyed, as is the case with the known overload protection with shear bolts, the crushing device can be restarted after only a brief interruption of work.
  • the rotary vibration absorber may have two coaxial absorber parts. - A -
  • the absorber parts may each comprise force transmission elements which mesh with play comb-like, and in at least one intermediate space between the force transmission elements may be arranged a coupling body.
  • the power transmission elements realize together with the coupling bodies a stable high torque transmitting connection.
  • recesses may be provided in the mutually facing, in particular closely spaced surfaces of the absorber parts, in which the coupling body is in each case arranged approximately in equal parts with respect to its cross section. Power transmission elements of the absorber parts are formed here by the walls of the recesses.
  • the recesses and the coupling body may be elongate prismatic and extend radially to the axes of the absorber parts. In this way, the forces occurring are distributed uniformly over the length of the coupling body.
  • the torque-dependent coupling element responds, and the drive unit and the drive shaft continue to rotate at least partially decoupled from the output shaft and the comminuting rotor, whereas the output shaft and the comminuting rotor lose speed, possibly stopping.
  • a sensor can be arranged in each case between the drive unit and the power transmission device and between the power transmission device and the comminution rotor, which sensor is connected via signal lines to a comparison device, in particular for comparing the angular positions or speeds in front of and behind the power transmission device, and from the sensor signals, in particular the angular positions or rotational speeds in front of and behind the power transmission device, a slip occurring in the region of the power transmission device can be determined.
  • the drive unit and the comminution rotor are at least partially decoupled by the torque-dependent coupling element, it is expedient to slow down or stop the drive unit, in order to prevent very high speeds of rotation occurring at short notice, which can also lead to damage.
  • the comparison device can be connected for this purpose via signal lines to a control unit for the drive unit.
  • the coupling element Since usually very large torques are required to drive the crushing rotor against the load, it is necessary to avoid that the coupling element triggers too early. As particularly efficient has been found here, when the coupling element is a spring-loaded friction clutch element, in which the triggering torque can be specified. Incidentally, with spring-biased friction clutch elements, even large torques can be transmitted slip-free as long as the static friction is not exceeded.
  • the drive unit may have a reduction gear, which is the least one drive motor downstream. This has the advantage that a significantly smaller dimensioned drive motor can be used and the drive unit still provides high torques.
  • the drive unit may comprise a plurality of electric motors, which are arranged in a motor housing and having drive pinions, which are arranged together symmetrically to a central drive gear, which is coupled to the power transmission device or optionally to the reduction gear.
  • This drive unit combines the drive power of several comparatively compact and easy to manufacture electric motors, which are arranged to save space around the common drive gear around. Embodiments of the invention will be explained in more detail with reference to the drawing; show it
  • Figure 1 shows schematically a partial section of a Zerklei ⁇ n réellesvorraum in the longitudinal direction
  • Figure 2 schematically shows a first embodiment of a torsional vibration absorber of the crushing device of Figure 1 in section perpendicular to a drive shaft.
  • Figure 3 schematically shows the torsional vibration absorber of Figure 2 in the axis-parallel section along the section line III-III there;
  • Figure 4 schematically shows a second to that shown in Figures 2 and 3 similar embodiment example of a torsional vibration absorber for a crushing device of Figure 1 perpendicular to the drive shaft cut;
  • Figure 5 schematically shows the torsional vibration absorber of Figure 4 in the axis-parallel section along the section line V-V;
  • Figure 6 schematically shows a drive unit for a crushing device according to Figure 1 seen in the direction of the drive shaft.
  • FIG. 1 a total provided with the reference numeral 10 crushing device is shown, with the crushed material, which is composed of bodies that may be different in size, shape and / or strength (eg beams wood waste from Window factories, plastic bumpers, plastic bags of stored blood, etc.), can be crushed.
  • the crushed material which is composed of bodies that may be different in size, shape and / or strength (eg beams wood waste from Window factories, plastic bumpers, plastic bags of stored blood, etc.), can be crushed.
  • the comminution device 10 has a drive unit 12, on the left in FIG. 1, with a reduction gear 14, a comminuting rotor 16, on the right in FIG. 1, and connected between these components via a power transmission device 18 for transmitting a drive force or a drive torque of FIG the drive unit 12 via the reduction gear 14 to the crushing rotor sixteenth
  • the drive unit 12 with the reduction gear 14 and the power transmission device 18 are housed in a housing 19 and 21, respectively.
  • the comminution rotor 16 is located in a machine housing, not shown, which forms a feed hopper for comminuted material and is provided with a feed opening for the material to be comminuted and a discharge opening for the comminuted material.
  • the adjacent housing 19, 20 (and the machine housing, not shown) have through openings for a drive shaft 20 and an output shaft 22 and are connected to each other via flange 24 separable.
  • the drive unit 12 which is shown in FIG. 6 in a section perpendicular to the output shaft 22, comprises four electric motors 26 which are arranged in the motor part of the housing 19.
  • the electric motors 26 each have a drive pinion 28.
  • the drive pinions 28 are arranged together symmetrically to a central drive gear 30 at the corners of a square.
  • the central drive gear 30 is mounted on an input side gear shaft 32 of the reduction gear 14.
  • the four electric motors 26 are three-phase asynchronous motors or synchronous motors, which are fed via a frequency-controllable frequency converter 27.
  • the speed of the electric motors 26 is so adjustable via a control unit 29 for the frequency converter 27.
  • a suitable coolant in particular cooling water for cooling, in particular the electric motors 26 is passed.
  • a power of 390 kW can be achieved in practice even with standard synchronous motors.
  • a maximum torque of up to 29800 Nm briefly a torque of up to 48000 Nm, can be generated.
  • the transmission of the torque from the reduction gear 14 to the power transmission device 18 is done by means of the drive shaft 20.
  • the output shaft 22 is provided accordingly.
  • the drive shaft 20 and the output shaft 22 extend coaxially with one another and with respect to an axis 34 of the comminution rotor 16.
  • the drive train of the comminution device 10 is constructed as a whole linearly.
  • the power transmission device 18 has a torsional vibration absorber 36 and a torque-dependent friction clutch element 38.
  • the rotary vibration absorber 36 and the slip clutch element 38 are arranged in series between the drive shaft 20 and the output shaft 22, wherein the torsional vibration absorber 36 on the drive unit 12 side facing, left in Figure 1, and the slip clutch element 38 on the crushing rotor 16 facing side, in Figure 1 right.
  • the internal components of the torsional vibration absorber 36 and the slip coupling element 38 are largely covered by a respective inner housing.
  • a first embodiment of a torsional vibration absorber 36 is shown in section perpendicular to the drive shaft 20 in Figure 2 and in the axis-parallel section in Figure 3.
  • the torsional vibration absorber 36 comprises two absorber parts 40 and 42 which are coaxial with the drive shaft 40 and the output shaft 42 and each have an approximately circular plate-shaped base body 44 and 45, respectively.
  • the Drive-side absorber part 40 which is shown on the left in FIG. 3, is fixedly mounted on the end of drive shaft 20 remote from reduction gear 14.
  • the drive shaft 20 extends perpendicular to the flat surfaces 48 of the main body 44th
  • the output-side absorber part 42 shown on the right in FIG. 3, is fastened correspondingly on a connecting shaft 46, which runs coaxially to the drive shaft 20 and the output shaft 22 and is connected to the slip-clutch element 38 with its end facing away from the torsional vibration absorber 36.
  • each four elongated webs 50 ⁇ ⁇ tion 52 arranged in a cross shape.
  • the longitudinal axes of the webs 50 extend radially from the edge of the main body 44 to the drive shaft 20, the longitudinal axes of the webs 52 from the edge of the main body 45 to the connecting shaft 46.
  • the webs 50 and 52 are integrally formed on the respective base body 44, 45.
  • All webs 50 and 52 each have a rectangular transverse cross-section.
  • the edge contour of the webs 52 is also rectangular seen in the axial direction.
  • Webs 50 of the drive-side absorber part 40 have, viewed axially, trapezoidal edge contour (FIG. 2).
  • the drive-side webs 50 and the output-side webs 52 have the same dimension in the axial direction of the torsional vibration absorber 36.
  • the drive-side absorber part 40 is 45 ° about the drive shaft 20 and the connecting shaft 46 offset relative to the output side absorber 42.
  • the ' drive-side webs 50 engage in a comb-like manner approximately centrally in the spaces between the driven side webs 52, such that in each case a substantially triangular gap 54 remains between a drive-side web 50 and its adjacent driven-side web 52, see FIG shows.
  • an elastic transverse transversely rectangular and in axial view trapezoidal coupling body 58 is arranged made of an elastomeric material which fills the gap 44 at least in the circumferential direction of the base body 44, 45 and at the approximately radially extending side surfaces of the adjacent Webs 50 and 52 is present.
  • the coupling bodies 58 are fastened on the surface 48 of the drive-side main body 44. Their extension in the direction of the drive shaft 20 is less than or equal to the corresponding extent of the drive-side webs 50.
  • the absorber parts 40 and 42 are connected to one another in a form-fitting manner by means of the elastic coupling bodies 58.
  • the coupling bodies 58 permit limited rotations of the two absorption parts 40 and 42 relative to one another about the axis of the drive shaft 20 or the connecting shaft 46 because of their elasticity, so as to avoid the torque fluctuations. ischenen.
  • torque fluctuations can be caused by the ever-changing resistance in crushing the material.
  • the changes in resistance are due to the fact that the material to be crushed is usually composed of bodies that differ in size, shape and / or strength.
  • the bodies to be crushed can come in different positions between the crushing tools of the crushing rotor 16 and corresponding housing-fixed Gegenmnesser, which also different forces for crushing the body are required.
  • the friction clutch element 38 which is not shown in detail, has two friction disks, which are pressed against one another with prestressed springs.
  • One of the friction plates is mounted on the connecting shaft 46, the other friction disc is mounted on the end of the output shaft 22 facing away from the comminution rotor 16.
  • the contact pressure of the springs on the friction disks is selected so that the slip clutch element 38 slips when a predetermined torque is exceeded, which is preferably about 44000 Nm at the above-mentioned maximum torque values, and thus the rigid coupling between drive shaft 20 (in fact the connecting shaft 46) and output shaft 22 lifts, so that a slip occurs.
  • a sensor S1 or S2 are arranged on the drive shaft 20 and on the output shaft 22 (cf., FIG. 1) with which the rotational speed of the respective shaft can be detected.
  • the sensors S 1 and S 2 comprise, for example, a pulse transmitter arranged close to the corresponding shaft, which cooperates, for example, inductively, with ten screws running with the shaft 20, 22 is. With each revolution of the shaft 20, 22, the pulse generator generates ten pulses.
  • the pulse generators are connected via signal lines with a comparator V.
  • the comparison device With the comparison device, the number of pulses to the drive shaft 20, that is, their speed, and the number of pulses on the output shaft 22 can be compared. From the difference of the pulse numbers, a slip occurring in the area of the power transmission device 18 is determined.
  • the comparator V As soon as the difference between the number of pulses before the power transmission device 18 and the pulse number behind the power transmission device 18 is more than two pulses, which corresponds to an angular offset of the drive shaft 20 to the output shaft 22 of about 70 °, the comparator V generates a corresponding control signal.
  • sensors S1 and S2 may be used which have a better angular resolution of, for example, 10 ° or 5 ° per pulse. This makes it possible to turn off the electric drive even faster when a fault occurs.
  • the comparison device V is connected to the control unit 29 for the frequency converter 27 of the drive unit 12, which modifies the possibly characteristic-modified or otherwise processed output signal of the comparator frequency control signal is transmitted. This can revert, slow down or stop the drive unit 12 in response to the control signal.
  • FIGS. 4 and 5 In a second embodiment of a torsional vibration absorber 36, shown in FIGS. 4 and 5, those elements that are functionally similar to those of the first embodiment described in FIGS. 2 and 3 are provided with the same reference numerals. With regard to their description, reference is made to the comments on the first embodiment.
  • the second embodiment differs from the first in that in the facing and closely spaced opposite surfaces 48 of the absorber 40 and 42 are each provided eight elongated profile in the semicircular prismatic recesses 65, 67, which in composite absorber parts 40 and 42 are pairwise opposite, and together give a cylindrical receptacle.
  • one of the cylindrical coupling body 58 is arranged, which is in each case half in one of the recesses 65, 67.
  • the recesses 65, 67 are arranged symmetrically about the drive shaft 20 or about the connecting shaft 46 and extend radially inwards or outwards almost to the edges of the absorber parts 40 and 42.
  • the positive elastic connection of the absorber 40, 42 comes in the second embodiment by the cooperation of the coupling body 58 with the pairwise opposite recesses 65, 67 state.
  • a drive unit 12 which achieves a smaller or greater maximum power than 390 kW. It is also possible to generate a smaller or a larger maximum torque than 29,800 Nm or, for a short time, 48,000 Nm.
  • the central drive gear 30 may be mounted directly on the drive shaft 20.
  • the drive unit 12 may also have only one or more than four electric motors 26.
  • the coupling bodies 58 may also have a different shape or be arranged differently.
  • individual matrix-like arranged coupling body 58 may be provided or the recesses may extend in the secant direction.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Food Science & Technology (AREA)
  • Crushing And Pulverization Processes (AREA)
  • Transmission Devices (AREA)

Abstract

L'invention concerne un mécanisme de transmission (18) pour un dispositif de concassage (10), permettant de transmettre la force motrice d'un groupe de propulsion (12) à un rotor de concassage (16). Le mécanisme de transmission (18) comporte au moins un amortisseur de vibrations torsionnelles (36) et au moins un élément d'accouplement (38) fonctionnant suivant un couple de rotation, qui, monté en série, est disposé entre le groupe de propulsion (12) et le rotor de concassage (16).
PCT/EP2007/006656 2006-07-27 2007-07-27 Mécanisme de transmission pour un dispositif de concassage Ceased WO2008012096A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200620011683 DE202006011683U1 (de) 2006-07-27 2006-07-27 Kraftübertragungseinrichtung für eine Zerkleinerungsvorrichtung
DE202006011683.4 2006-07-27

Publications (3)

Publication Number Publication Date
WO2008012096A2 WO2008012096A2 (fr) 2008-01-31
WO2008012096A9 true WO2008012096A9 (fr) 2008-05-22
WO2008012096A3 WO2008012096A3 (fr) 2008-08-21

Family

ID=37545436

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/006656 Ceased WO2008012096A2 (fr) 2006-07-27 2007-07-27 Mécanisme de transmission pour un dispositif de concassage

Country Status (2)

Country Link
DE (1) DE202006011683U1 (fr)
WO (1) WO2008012096A2 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008061734B4 (de) * 2008-12-12 2012-03-08 Vecoplan Ag Zerkleinerungsvorrichtung, insbesondere Trommelhacker
DE102011004113A1 (de) * 2011-02-15 2012-08-16 Universität Bielefeld Flexible Kupplung mit integrierter Messeinrichtung
JP5897316B2 (ja) * 2011-12-01 2016-03-30 株式会社マキタ 電動工具
DE202015101542U1 (de) * 2015-03-26 2016-06-30 Aradex Gmbh Zerkleinerer
CN106195200B (zh) * 2016-07-08 2018-08-10 中信重工机械股份有限公司 一种机械辅助齿式离合器对齿的慢速驱动装置
CN109027036A (zh) * 2018-09-13 2018-12-18 淮安信息职业技术学院 一种慢驱气动离合装置及其使用方法
CN112377423A (zh) * 2020-11-21 2021-02-19 越连机电有限公司 一种切割泵

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GB511010A (en) * 1938-11-24 1939-08-11 Joseph Elliott Kennedy Improvements in or relating to tube and the like mills
GB1190977A (en) * 1967-08-19 1970-05-06 Holset Engineering Co Flexible Coupling
DE2200228A1 (de) * 1972-01-04 1973-07-12 Kokemueller Erwin Antrieb fuer grosse abtriebsdrehmomente, insbesondere fuer rohrmuehlen
DE3612788A1 (de) * 1986-04-16 1986-09-11 Alois Zettler Elektrotechnische Fabrik GmbH, 8000 München Ueberlastungsschutz fuer geraet zum zerkleinern von blattfoermigem material
DE4342103A1 (de) * 1993-12-10 1995-06-14 Babcock Prozessautomation Gmbh Vorrichtung zum Regeln einer Strömungskupplung
DE9419129U1 (de) * 1994-11-29 1995-01-26 Westfalia Becorit Industrietechnik GmbH, 44534 Lünen Durchlaufbrecher, insbesondere Durchlauf-Backenbrecher
KR20010017883A (ko) * 1999-08-16 2001-03-05 이계안 차량용 충격 완화장치
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Also Published As

Publication number Publication date
WO2008012096A3 (fr) 2008-08-21
DE202006011683U1 (de) 2006-11-30
WO2008012096A2 (fr) 2008-01-31

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