EP0340464A2 - Broyeur à cylindres à lit de matière - Google Patents

Broyeur à cylindres à lit de matière Download PDF

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Publication number
EP0340464A2
EP0340464A2 EP89105932A EP89105932A EP0340464A2 EP 0340464 A2 EP0340464 A2 EP 0340464A2 EP 89105932 A EP89105932 A EP 89105932A EP 89105932 A EP89105932 A EP 89105932A EP 0340464 A2 EP0340464 A2 EP 0340464A2
Authority
EP
European Patent Office
Prior art keywords
roller
gas spring
spring
hydraulic
hydraulic fluid
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.)
Granted
Application number
EP89105932A
Other languages
German (de)
English (en)
Other versions
EP0340464B1 (fr
EP0340464A3 (en
Inventor
Gerhard Dipl.-Ing. Kästingschäfer
Reinhold Dipl.-Ing. Gebbe
Gerhard Dipl.-Ing. Arensmeier
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.)
ThyssenKrupp Industrial Solutions AG
Original Assignee
Krupp Polysius AG
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 Krupp Polysius AG filed Critical Krupp Polysius AG
Publication of EP0340464A2 publication Critical patent/EP0340464A2/fr
Publication of EP0340464A3 publication Critical patent/EP0340464A3/de
Application granted granted Critical
Publication of EP0340464B1 publication Critical patent/EP0340464B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • B02C4/00—Crushing or disintegrating by roller mills
    • B02C4/28—Details
    • B02C4/32—Adjusting, applying pressure to, or controlling the distance between, milling members

Definitions

  • the invention relates to a material bed roller mill for pressure comminution of brittle regrind, according to the preamble of claim 1.
  • Gutbett roll mills are generally known from DE-C-27 08 053 and allow considerable energy savings in the pressure reduction of brittle regrind, such as. B. cement clinker, ores, etc.
  • brittle regrind such as. B. cement clinker, ores, etc.
  • two horizontally arranged, driven rollers are pressed against one another at high pressure.
  • the material is largely crushed as it passes through the grinding gap formed between the two rollers, agglomerates (so-called slugs) being formed which contain a high proportion of fine or finished goods and which are then broken down in a downstream unit with low energy consumption.
  • one roller is designed as a stationary fixed roller and the other as a loose roller movably mounted transversely to the grinding gap, the loose roller being pressed with high pressure in the direction of the fixed roller in order to reduce the pressure described above To bring ground material.
  • a combined hydraulic gas spring system to each side of the idler roller, in which at least one hydraulic working cylinder is provided for each side of the idler roller, ie for each knuckle of the idler roller cooperates with a working gas spring.
  • the optimum setting, in particular of the grinding force is made above all by several tests, various settings of the gas and hydraulic fluid pre-filling pressures being made, for which purpose the roller mill is then switched off and the pre-filling pressures are reset.
  • the working gas spring in each hydraulic gas spring system is first filled with gas to a predetermined gas pre-pressure during the operating setting, and then hydraulic oil is supplied to a predetermined pre-pressure to adjust the grinding force at a so-called zero gap, i.e. when the force flow between the two rollers is above runs several spacers through which a minimum roller distance is maintained.
  • the gas spring characteristics and the grinding force behavior during the grinding of the material to be ground are determined by the gas and oil pre-filling pressures.
  • the invention is therefore based on the object to further develop a material bed roller mill of the type required in the preamble of claim 1 in such a way that the grinding force can be adjusted in a simple manner even during operation and modified grinding conditions can thereby be adapted with relatively simple measures.
  • each working gas spring is divided into a central gas filling space (between the two pistons) and into two hydraulic liquid spaces assigned to the two container edge sections, which are essentially variable to the operating pressures occurring on the part of the working cylinders.
  • the second piston of the working gas spring delimiting the second hydraulic fluid space is assigned a displacement measuring device which responds to the piston movement and via which the pre-filling pressure of the hydraulic fluid with the same gas spring characteristic on both sides of the idler roller (i.e. in both hydraulic gas spring systems) can be adjusted during operation.
  • the hydraulic fluid pre-filling pressure can thus be obtained via each working gas spring and thus also the grinding force in the grinding nip of the roller mill can be adjusted in the desired manner in the desired way in such a way that the optimum grinding force and thus the optimum comminution of the roller mill are controlled or regulated.
  • This can happen during commissioning of the roller mill, when changing the regrind, when changing the regrind parameters (e.g. fine material content, moisture, etc.) and also when the idler roller has to be adjusted if the grinding roller wears down a lot.
  • Such readjustment of the grinding force can, for. B. both directly by hand or approximately electromagnetically from a control center or via a control loop.
  • the previously described control or regulation of the grinding force (via the pre-filling pressure of the hydraulic fluid) can be carried out independently of fluctuations in each hydraulic gas spring system that can be attributed to a horizontal movement of the idler roller, and independently of the position of the idler roller (e.g. Inclination) are carried out, whereby the gas spring characteristic is essentially identical even after readjusting the grinding force via the hydraulic pre-filling pressure in the working gas springs of the idler roller on both sides.
  • a pressure relief valve for setting the maximum permissible grinding force in the grinding gap is connected to the second hydraulic fluid chamber of the working gas spring.
  • This material bed roller mill contains, in a stationary mill housing 1, two horizontally arranged rollers 2, 3, which are driven by drive mechanisms (not shown), of which the roller 2 is designed as a fixed roller and the roller 3 as a loose roller.
  • the fixed roller 2 is mounted via its two steering knuckles 2a in two associated bearing blocks 4 in a stationary manner in the mill housing 1, while the two steering knuckles 3a of the floating roller 3 are mounted in two associated floating bearing blocks 5, which can be moved within the mill housing 1 together with the loose roller 3 in accordance with the double arrow 6 are so that the latter is movable or displaceable relative to the fixed roller 2.
  • a grinding gap (roll gap) 7 is formed between the two rolls 2, 3. Since the loose roller 3 is movable in the direction of the double arrow 6, it is also movable transversely to the grinding gap 7, ie the width of this grinding gap 7 can be changed accordingly by the mobility of the loose roller 3.
  • a plurality of spacers in the form of spacers 8, 9 are attached, which determine the minimum roller spacing of the two rollers 2, 3 when they are in mutual contact; this minimum roller spacing ensures that when the roller mill is idling, that is to say if there is little or no supply of regrind, the two rollers 2, 3 do not lie against one another with their roller surfaces, thereby preventing unnecessary wear.
  • This minimum roll distance represents the so-called zero gap.
  • a hydraulic gas spring system is provided for each side of the loose roller 3, each of which has two hydraulic working cylinders 10, 11, one in the exemplary embodiment illustrated in FIG. 1 Contains hydraulic pump 12 and a working gas spring 13, which is connected by a hydraulic line 14 to the two working cylinders 10, 11.
  • a first throttle 15, to which a first check valve 16 lies in series can be arranged in the hydraulic line 14.
  • a second throttle 17, to which a second check valve 18 lies in series can be arranged parallel to this series connection. This arrangement of the two throttles 15, 17 and the two check valves 16, 18 prevents the occurrence of disturbing resonance vibrations.
  • FIG. 2 The detailed details of one of the associated hydraulic gas spring systems of the material bed roller mill according to FIG. 1 are explained below with reference to the flow diagram of FIG. 2, in which, for the sake of simplicity, only one working cylinder, for example the working cylinder 10 and the loose roller 3 with an associated loose bearing block 5 (on one side or on a steering knuckle 3a of the loose roller 3) is illustrated.
  • the mobility of the loose roller 3 with the aid of its loose bearing blocks 5 is again illustrated by the double arrow 6, while the grinding force required for comminuting the material to be ground is indicated in the grinding gap between the two rollers by an arrow 19 directed against the loose roller.
  • the hydraulic gas spring system shown on the one side of the idler roller working gas spring 13, which through the line 14 with the working cylinders, for. B. 10, is connected, has an elongated spring container 20 approximately in the manner of a cylinder, which is essentially closed at both end sections by an end wall 20a, 20b - apart from sealed line bushings or the like. Furthermore, this working gas spring 13 has two pistons 21, 22 which are movable relative to one another and which are each assigned to a container end section within the spring container 20. As can be seen in Fig.
  • the opposing limits Piston sides of these two pistons 21, 22 define a central gas filling space 23 of the gas spring 13, while the respectively opposite piston sides with the associated end walls 20a and 20b of the spring container 20 delimit a first hydraulic fluid space 24 and a second hydraulic fluid space 25.
  • the first hydraulic fluid chamber 24 delimited by the first piston 21 is connected via the hydraulic line 14 to the hydraulic working cylinders, e.g. B. 10, in connection.
  • the two pistons 21 and 22 can in principle essentially be designed in the form of a piston plate or a piston body.
  • the second piston 22 is assigned a displacement measuring device which responds to the piston movements in one direction or the other and is generally designed in any suitable manner and This second piston 22 can be assigned to respond to each of the reciprocating piston movements and measure their sizes.
  • One possibility for the formation of such a path measuring device is indicated at 26 in FIG. 2.
  • the second piston 22 has a piston rod 22a which projects through the associated end wall 20b of the spring container 20 and which cooperates with the displacement measuring device 26 for the precise determination of the respective change in position of the piston 22 in the spring container 20.
  • a structurally particularly simple design of the displacement measuring device which can be used very favorably in terms of control and regulation technology can consist in the design as an ultrasonic measuring device which responds to any change in position of the second piston 22 in the spring container 20.
  • a transmitter and receiver can be provided in or on the associated end wall 20b of the spring container 20 in such a way that corresponding signals are reflected by the piston 22, from which the exact relative position of the piston 22 in the spring container 20 can be derived.
  • the hydraulic fluid pre-filling pressure of the working gas spring 13 can then be measured and during milling operation with approximately the same gas spring characteristic on both sides of the idler roller 3 and thus at the same time the grinding force in the grinding gap 7 can be set, as will be explained in more detail below.
  • a pressure limiting valve 28 is also connected to the second hydraulic fluid chamber 25 of the spring container 20 via a line 27, via which a maximum permissible grinding force in the grinding gap 7 can be set or controlled.
  • the outflow side of this pressure relief valve 28 is connected to a hydraulic fluid tank 29. It should be emphasized in this connection that any suitable hydraulic fluid can be used; however, this is preferably hydraulic oil.
  • a partial line 30 is also connected, which is connected to the oil tank 29 via an oil feed pump 31 and in which a multi-way / multi-position valve which enables hydraulic fluid chamber 25 to be supplied and removed 32 and a manometer 33 are arranged.
  • a branch line 34 is also connected to the hydraulic line 14 connected to the first hydraulic fluid chamber 24 of the spring container 20, in which a further multi-way / multi-position valve 35 which permits the supply and discharge of hydraulic fluid and a manometer 36 are arranged and which are likewise via the oil feed pump 31 communicates with the oil tank 29.
  • the supply of gas into the gas filling space 23 of the spring container 22 can be done in any suitable manner.
  • the piston rod 22a can be designed as a hollow rod and connected to a gas supply line 37.
  • a spiral or helically wound supply hose which can be arranged within the second hydraulic fluid space 25 without hindering the relative movements of the second piston 22.
  • a piston rod led out of the spring container can be dispensed with, which is favored, for example, by using an ultrasound measuring device for the distance measurement.
  • the gas supply line 37 is provided and is connected, for example, via a pressure gauge 39 and a further multi-way / multi-position valve 40 and a simple shut-off valve 41 to a compressed gas source, for example, a compressed gas bottle 38.
  • an auxiliary gas spring 42 is also connected hydraulically, the spring force of which is adapted to the restoring force for the idler roller 3 in the zero gap position determined by the spacers 8, 9; this additional auxiliary gas spring is therefore referred to below as the zero gap gas spring 42.
  • the zero gap gas spring 42 can be made significantly simpler than the working gas spring 13. It has a substantially closed, preferably cylindrical spring container 43 and a simple piston (e.g. plate or membrane piston) arranged axially movably therein, which divides the container interior into a gas filling chamber 45 and a hydraulic fluid chamber or oil chamber 46.
  • the oil space 46 is connected to the hydraulic line 14 via a connecting line 14a, while the gas filling space 45 is also connected to the compressed gas bottle 38 via a gas line 47.
  • a multi-way / multi-position valve 48 and a pressure gauge 49 are installed in the gas line 47.
  • This zero gap gas spring 42 is designed and arranged in a special way for interaction with the working gas spring 13 provided here. For this purpose, it is provided that if the supply of grinding material to the grinding gap 7 is interrupted, the rollers 2, 3 on the part the working gas spring 13 are relieved of pressure. In this pressure-relieved idling state, the two rollers 2, 3 are to be brought together again in their starting position, that is to say in the zero gap position, in that the loose roller 3 is guided against the fixed roller 2 via its loose bearing blocks 5 until the spacers 8, 9 abut one another.
  • the zero gap gas spring 42 is effective, the spring force of which only has to be so great that the corresponding frictional forces are overcome and the floating bearing blocks 5 together with the loose roller 3 can be reset.
  • This simple measure entails that the corresponding components of the roller mill can be considerably reduced in terms of both their weight and their processing costs compared to the previously known mills, and that, in the event of interruptions or idling conditions, no undesirable large impacts on the corresponding components of the mill are exercised and that due to these relatively low loads, an increased service life, in particular of the associated bearings (spherical roller bearings) and, if appropriate, of the jewels can be achieved.
  • the gas and oil priming pressures are set at the zero gap position (spacers 8, 9 abut one another). If one looks at the flow diagram in FIG. 2, the valves 32, 35 are first opened and the gas pre-filling pressure in the gas filling chamber 23 of the working gas spring 13 via the gas supply line 37 and the valve 40 and the pressure gauge 39 and then the gas pressure in the zero gap gas spring 42 via gas line 47, valve 48 and pressure gauge 49 are set to the respectively required pressure.
  • the gas pre-filling pressure of the working gas spring 13 is generally significantly higher than that in the zero-gap gas spring 42 (e.g.
  • the gas pre-filling pressure in the working gas spring 13 can be approximately 40 bar and the gas pressure in the zero-gap gas spring 42 can be approximately 8 bar).
  • the two oil valves 32, 35 are then temporarily closed.
  • the oil prefill pressure in the second hydraulic fluid chamber 25 of the working gas spring 13 is first set via the oil valve 32 and then the oil prefill pressure in the oil chamber 46 of the zero-point gas spring 42 via other oil valve 35, the oil prefill pressure in the second hydraulic fluid chamber 25 being significantly higher than that of the oil space 46 of the zero gap gas spring 42 will lie.
  • the oil pre-filling pressure in the oil space 46 of the zero gap gas spring 42 must be lower than the gas or oil pre-filling pressure in the working gas spring 13. The hydraulic gas spring system is then ready to start.
  • the oil pre-filling pressure and thus the grinding force during operation of the roller mill can be adjusted in a defined manner by means of the path measuring device 26 explained with each working gas spring 13, which in turn optimally controls or regulates the grinding force in the grinding gap 7 can.
  • the mean pressure at the two floating bearing blocks 5 can be optimally set under different loads across the width of the rollers 2, 3, the initially set oil pre-pressures for the working gas springs 13 on both loose roller sides changing identically.
  • the grinding force can always be readjusted in each operating phase if, for example, the grinding conditions in the roller mill have changed due to changes in the grinding material parameters or when the loose roller 3 is adjusted in the event of excessive grinding roller wear.
  • each working gas spring 13 provides a manipulated variable, namely the respective position of the second piston 22 in the spring container 20 (displacement measurement), with which the oil pre-pressures in the associated hydraulic gas spring system can be adjusted uniformly on the corresponding loose roller side in the grinding operation. This means that the gas spring characteristics after a readjustment in both hydraulic gas spring systems (on both loose roller sides) are the same.
  • the spring characteristics are the same even after adjusting the two working gas springs in the two hydraulic gas spring systems.
  • the grinding pressure can be controlled in grinding mode or regulated by comparing the actual and setpoint values of the specific shredding work. This means that with the newly created manipulated variable, the material bed roller mill with always identical spring characteristics of the working gas springs 13 of both hydraulic gas spring systems on the basis of the optimal operating point (specific Shredding) can be regulated.
  • the pressure-limiting valve 28 explained above which limits the maximum grinding force and thus prevents overloading of the roller mill, can be installed particularly advantageously in each hydraulic gas spring system. After this pressure limiting valve 28 has responded (when the oil pre-filling pressure changes), the oil pre-filling pressure can be reset to the optimum value by means of the actual and setpoint comparison mentioned above, without the roller mill having to be switched off after the pressure relief valve has responded.

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  • Engineering & Computer Science (AREA)
  • Food Science & Technology (AREA)
  • Crushing And Grinding (AREA)
EP89105932A 1988-05-03 1989-04-05 Broyeur à cylindres à lit de matière Expired - Lifetime EP0340464B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3815002A DE3815002A1 (de) 1988-05-03 1988-05-03 Gutbett-walzenmuehle
DE3815002 1988-05-03

Publications (3)

Publication Number Publication Date
EP0340464A2 true EP0340464A2 (fr) 1989-11-08
EP0340464A3 EP0340464A3 (en) 1990-08-29
EP0340464B1 EP0340464B1 (fr) 1992-09-30

Family

ID=6353493

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89105932A Expired - Lifetime EP0340464B1 (fr) 1988-05-03 1989-04-05 Broyeur à cylindres à lit de matière

Country Status (5)

Country Link
US (1) US4973001A (fr)
EP (1) EP0340464B1 (fr)
DE (2) DE3815002A1 (fr)
ES (1) ES2035405T3 (fr)
ZA (1) ZA892690B (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4234481A1 (de) * 1992-10-13 1994-04-14 Krupp Polysius Ag Walzenmühle
FR2734176A1 (fr) * 1995-05-17 1996-11-22 Krupp Foerdertechnik Gmbh Concasseur a cylindres
DE19522251A1 (de) * 1995-05-17 1996-12-05 Krupp Foerdertechnik Gmbh Walzenbrecher
WO1998053913A1 (fr) * 1997-05-30 1998-12-03 Bühler AG Procede et dispositif pour regulation de fente hydro-electrique
WO2008068120A1 (fr) * 2006-12-08 2008-06-12 Polysius Ag Broyeur avec système presseur
CN114100773A (zh) * 2021-11-24 2022-03-01 林德岗 一种艾绒制备除杂装置
CN115780018A (zh) * 2022-12-09 2023-03-14 中材建设有限公司 一种预粉磨破碎装置

Families Citing this family (14)

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Publication number Priority date Publication date Assignee Title
DE4219886A1 (de) * 1992-06-17 1993-12-23 Krupp Polysius Ag Verfahren zum Betrieb einer Gutbett-Walzenmühle
DE4226158C2 (de) * 1992-08-07 2003-04-10 Kloeckner Humboldt Wedag Verfahren und Anlage zur Druckbehandlung körnigen Gutes
DE4320668A1 (de) * 1993-06-22 1995-01-05 Krupp Polysius Ag Walzenmühle
EP0654434B1 (fr) * 1993-11-19 2000-04-05 Ferag AG Dispositif de pressage pour des articles imprimés pliés tels que journaux, magazines et des parties de ceux-ci
DE202005004663U1 (de) * 2005-03-22 2006-08-03 Köppern Entwicklungs-GmbH Walzenpresse
DE202010012495U1 (de) * 2010-09-13 2011-12-16 Hugo Vogelsang Maschinenbau Gmbh Zerkleinerungsvorrichtung mit Verschleißanzeige
DE102013110981A1 (de) * 2013-10-02 2015-04-02 Thyssenkrupp Industrial Solutions Ag Verfahren zum Betreiben einer Anlage mit wenigstens einem Aggregat, das eine rotierende Oberfläche aufweist
US20160199841A1 (en) * 2015-01-12 2016-07-14 Kwok Fai Edmund SO Ceramic material granulator
CN104772186B (zh) * 2015-03-30 2019-07-16 南京梅山冶金发展有限公司 一种四辊破碎机开机前辊缝保持且无阻力启动的控制方法
DE102016211276B4 (de) 2016-06-23 2018-03-15 Takraf Gmbh Zerkleinerungsvorrichtung zur druckbehandlung eines körnigen aufgabeguts
US12036637B2 (en) * 2018-04-24 2024-07-16 Cold Jet, Llc Particle blast apparatus
US12097506B2 (en) 2021-10-22 2024-09-24 Metso Outotec USA Inc. Roller crusher and method for operating thereof
US11925942B2 (en) 2021-10-22 2024-03-12 Metso Outotec USA Inc. Roller crusher and method for operating thereof
US12076729B2 (en) * 2021-10-22 2024-09-03 Metso Outotec USA Inc. Roller crusher and method for arrangement thereof

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DE665343C (de) * 1937-01-12 1938-09-22 Auguste Frerotte Vorrichtung zur Regelung des Anpressdruckes, insbesondere der Mahlwalzen von Walzenstuehlen
US2204434A (en) * 1937-07-16 1940-06-11 Joseph J Munson Rolling mill
US2765731A (en) * 1952-03-28 1956-10-09 Edwards Eng Corp Hydraulic ram caps for crushing and pressing rolls
US2862360A (en) * 1954-05-31 1958-12-02 Alsacienne Constr Meca Hydraulic control of an elastic load
US3417928A (en) * 1966-11-14 1968-12-24 T J Gundlach Company Gas-hydraulic system for crushers
US3527159A (en) * 1968-03-27 1970-09-08 Du Pont Nip roll apparatus
FR2110734A5 (fr) * 1970-10-28 1972-06-02 Spidem Ste Nle
US3938732A (en) * 1974-09-16 1976-02-17 Iowa Manufacturing Company Adjustment means for roll crushers with gas hydraulic springs
DE2623492C3 (de) * 1976-05-26 1981-06-04 Küsters, Eduard, 4150 Krefeld Vorrichtung zur Drucksteuerung für Walzeinrichtungen
DE2655925A1 (de) * 1976-12-09 1978-06-15 Bauermeister Hermann Maschf Nahrungsmittel-walzvorrichtung
US4161885A (en) * 1977-05-27 1979-07-24 Sack Gmbh Measuring apparatus for measuring the roll gap in gauge-controlled roll stands
GB2043250A (en) * 1979-02-23 1980-10-01 Davy Loewy Ltd Ultrasonic transducer arrangement for indicating position of a piston
DE2943644A1 (de) * 1979-10-29 1981-05-07 Küsters, Eduard, 4150 Krefeld Walzenanordnung zur druckbehandlung von warenbahnen
IT1147385B (it) * 1981-07-16 1986-11-19 Giacomo Ferrero Cilindraia o mulino a cilindri a regolazione e sicurezza idrauliche

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4234481A1 (de) * 1992-10-13 1994-04-14 Krupp Polysius Ag Walzenmühle
FR2734176A1 (fr) * 1995-05-17 1996-11-22 Krupp Foerdertechnik Gmbh Concasseur a cylindres
DE19522251A1 (de) * 1995-05-17 1996-12-05 Krupp Foerdertechnik Gmbh Walzenbrecher
US5722605A (en) * 1995-05-17 1998-03-03 Krupp Fordertechnik Gmbh Roll crusher
WO1998053913A1 (fr) * 1997-05-30 1998-12-03 Bühler AG Procede et dispositif pour regulation de fente hydro-electrique
WO2008068120A1 (fr) * 2006-12-08 2008-06-12 Polysius Ag Broyeur avec système presseur
CN114100773A (zh) * 2021-11-24 2022-03-01 林德岗 一种艾绒制备除杂装置
CN115780018A (zh) * 2022-12-09 2023-03-14 中材建设有限公司 一种预粉磨破碎装置
CN115780018B (zh) * 2022-12-09 2023-10-20 中材建设有限公司 一种预粉磨破碎装置

Also Published As

Publication number Publication date
DE3815002A1 (de) 1989-11-16
US4973001A (en) 1990-11-27
DE58902351D1 (de) 1992-11-05
ES2035405T3 (es) 1993-04-16
EP0340464B1 (fr) 1992-09-30
EP0340464A3 (en) 1990-08-29
ZA892690B (en) 1989-12-27

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