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EP0340464B1 - Broyeur à cylindres à lit de matière - Google Patents

Broyeur à cylindres à lit de matière Download PDF

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Publication number
EP0340464B1
EP0340464B1 EP89105932A EP89105932A EP0340464B1 EP 0340464 B1 EP0340464 B1 EP 0340464B1 EP 89105932 A EP89105932 A EP 89105932A EP 89105932 A EP89105932 A EP 89105932A EP 0340464 B1 EP0340464 B1 EP 0340464B1
Authority
EP
European Patent Office
Prior art keywords
roller
spring
working
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.)
Expired - Lifetime
Application number
EP89105932A
Other languages
German (de)
English (en)
Other versions
EP0340464A3 (en
EP0340464A2 (fr
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.
  • a still further embodiment is known from US-A-2 765 731, which describes in particular with the aid of a sugar cane comminution mill how two fixed comminution rolls can be assigned a third roll provided in the gusset above it as an up and down movable loose roll.
  • the main issue is reliable lubrication and sealing in the area of the hydraulic piston for holding the idler roller, with a pressure accumulator in the form of a bladder accumulator (with a flexible wall) being connected to the upper hydraulic fluid space, while one filled with hydraulic fluid the lower annular space is connected via a tube to a vertical chamber, via which a scale indicator for the nip between the idler roller and an underlying fixed roller is created.
  • the invention is therefore based on the object of a material bed roller mill in the preamble of claim 1 to further develop the presupposed type in such a way that the grinding force can be adjusted in a simple manner even during operation and can be adapted to changed crushing conditions with relatively simple measures.
  • each working gas spring is divided into a central gas filling space (between the two pistons) and two hydraulic fluid spaces assigned to the two container end sections, which are essentially variable according to the operating pressures occurring on the part of the working cylinders.
  • the second piston of the working gas spring which delimits the second hydraulic fluid chamber, is assigned a displacement measuring device which responds to the respective reciprocating piston movement and whose measured quantity determines the pre-filling pressure of the hydraulic fluid with the same gas spring characteristic on both sides of the Loose roller (i.e. in both hydraulic gas spring systems) can be adjusted during operation.
  • the hydraulic fluid pre-filling pressure and thus also the grinding force in the grinding gap can thus be controlled via each working gas spring
  • the roller mill during the shredding operation can be adjusted in the desired manner using the path measuring device provided in such a way that the optimum grinding force and thus the optimum comminution of the roller mill are controlled or regulated. This can take place during the commissioning of the roller mill, when changing the regrind, when changing the regrind parameters (eg fine material content, moisture, etc.) or when the idler roller has to be adjusted if there is a large amount of grinding roller wear.
  • Such a readjustment of the grinding force can be carried out, for example, either directly by hand or also electromagnetically from a control station 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 which can be attributed to a horizontal movement of the idler roller, and independently of the position of the idler roller (e.g. inclined position) are, whereby the gas spring characteristic is essentially identical even after a new adjustment of the grinding force via the hydraulic pre-filling pressure in the working gas springs of the loose roller on both sides.
  • the load occurring via the grinding force can also be limited or set to a maximum permissibility without the roller mill having to be switched off.
  • the second hydraulic fluid chamber of the working gas spring there is a pressure relief valve for setting the maximum permissible grinding force in the grinding gap connected. This represents a particularly simple and at the same time effective
  • 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 distance 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 abut 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. 2, 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 basically be designed essentially 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 which 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 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 designed, for example, as a compressed gas bottle 38.
  • an auxiliary gas spring 42 is additionally hydraulically connected, 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 function of the hydraulic gas spring system for the loose roller 3 in particular: It is initially assumed that 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, for example if 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.
  • the grinding pressure (grinding force) can be controlled in grinding mode or regulated by comparing the actual and setpoint values of the specific shredding work.
  • 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)

Claims (5)

  1. Broyeur à cylindres ou rouleaux d'un lit de matière pour la fragmentation sous pression de matière friable, comprenant :
    a) deux rouleaux commandés (2, 3) formant entre eux un interstice de broyage (7) et dont l'un (2) est un rouleau stationnaire monté en position fixe et l'autre (3) est un rouleau déplaçable monté mobile perpendiculairement à l'interstice de broyage,
    b) deux systèmes de ressort pneumatique et hydraulique, dont chacun est affecté à un côté du rouleau déplaçable (3) et qui poussent élastiquement ce rouleau déplaçable sous forte pression vers le rouleau stationnaire (2), chacun de ces systèmes de ressort pneumatique et hydraulique comprenant au moins un cylindre hydraulique de travail (10, 11), un ressort pneumatique de travail (13) relié à ce cylindre de travail ainsi que des dispositifs commandés d'arrivée et de départ du liquide hydraulique et de gaz, les cylindres pneumatiques de travail de ces systèmes étant réglable à des pression de remplissage initial en gaz et en liquide hydraulique qui sont prédéterminables pour la caractéristique du ressort pneumatique et la force de broyage dans l'interstice correspondant (7) pour un interstice nul déterminant une distance minimale des rouleaux,
       caractérisé par les particularités suivantes :
    c) chaque ressort pneumatique de travail (13) comprend un récipient allongé (20) sensiblement fermé et deux pistons (21, 22) mobiles l'un par rapport à l'autre et dont chacun est disposé dans une extrémité du récipient, les côtés des pistons qui sont tournés l'un vers l'autre délimitant la chambre (23) remplie de gaz des ressorts pneumatiques de travail et les côtés de ces pistons tournés à l'opposé l'un de l'autre délimitant avec les cloisons correspondantes d'extrémités (20a, 20b) du récipient du ressort une première et une seconde chambres à liquide hydraulique (24, 25), la première chambre à liquide hydraulique (24) délimitée par le premier piston (21) communiquant par une canalisation hydraulique (14) avec le cylindre hydraulique de travail (10, 11) ;
    d) un dispositif (26) de mesure de déplacement, qui répond aux mouvements alternatifs du second piston (22) de chaque ressort pneumatique de travail (13) qui délimite la seconde chambre (25) à liquide de travail, est combiné avec ce piston, la mesure du déplacement détectée par ce dispositif (26) permettant de régler les pressions de remplissage initial en liquide hydraulique des ressorts pneumatiques de travail (13) des deux côtés du rouleau déplaçable avec une même caractéristique de ressort pneumatique ;
    e) un limiteur de pression (28) destiné au réglage d'une force maximale admissible de broyage dans l'interstice correspondant (7) est relié à la seconde chambre (25) à liquide hydraulique du récipient (20) du ressort.
  2. Broyeur à rouleaux d'un lit de matière selon la revendication 1, caractérisé en ce que le second piston (22) du ressort pneumatique de travail (13) comporte une tige (22a) qui ressort du récipient (20) du ressort par la cloison correspondante d'extrémité (20b) et qui coopère avec le dispositif (26) de mesure de déplacement.
  3. Broyeur à rouleaux d'un lit de matière selon la revendication 1, caractérisé en ce que le dispositif de mesure de déplacement qui est prévu est un dispositif de mesure à ultra-sons qui répond à chaque modification de position du second piston (22) dans le récipient (2o) du ressort.
  4. Broyeur à rouleaux d'un lit de matière selon la revendication 1, dans lequel plusieurs entretoises (8, 9) affectées aux deux rouleaux (2, 3) déterminent un interstice nul représentant une distance minimale entre rouleaux lorsqu'elles sont en appui les unes contre les autres, caractérisé en ce qu'en cas d'interruption de l'arrivée de matière dans l'interstice de broyage (7), le ressort pneumatique de travail (13) annule la pression qu'il exerce sur le rouleau déplaçable (3) et en ce qu'un ressort pneumatique auxiliaire (42) est raccordé à la canalisation hydraulique (14) menant de la première chambre (24) à liquide hydraulique du récipient (20) du ressort pneumatique de travail au cylindre de travail (10, 11), la force d'élasticité de ce ressort pneumatique auxiliaire (42) étant adaptée à la force de rappel du rouleau déplaçable (3) à la position d'interstice nul.
  5. Broyeur à rouleaux d'un lit de matière selon la revendication 1 et/ou 4, caractérisé en ce que chaque chambre (24, 25) à liquide hydraulique des ressorts pneumatiques de travail (13) est raccordée à une source (29) de liquide hydraulique par l'intermédiaire d'un distributeur (32, 35) à plusieurs courses et à plusieurs positions et d'une pompe commune (31) de liquide hydraulique et chaque chambre (23, 45) des ressorts pneumatiques (13, 42) qui est remplie de gaz est raccordée à une source commune (38) de gaz comprimé par l'intermédiaire d'un distributeur (40, 48) à plusieurs courses et plusieurs positions.
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 EP0340464A2 (fr) 1989-11-08
EP0340464A3 EP0340464A3 (en) 1990-08-29
EP0340464B1 true EP0340464B1 (fr) 1992-09-30

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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)

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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
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DE102016211276B4 (de) 2016-06-23 2018-03-15 Takraf Gmbh Zerkleinerungsvorrichtung zur druckbehandlung eines körnigen aufgabeguts
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US12097506B2 (en) 2021-10-22 2024-09-24 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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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

Also Published As

Publication number Publication date
EP0340464A3 (en) 1990-08-29
EP0340464A2 (fr) 1989-11-08
DE58902351D1 (de) 1992-11-05
US4973001A (en) 1990-11-27
ES2035405T3 (es) 1993-04-16
ZA892690B (en) 1989-12-27
DE3815002A1 (de) 1989-11-16

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