EP0598705B1 - Device for milling and/or compacting food or fodder components - Google Patents

Abstract

In an apparatus for grinding and/or compacting food and fodder components, there is provided, on a roller stand (1, 2), at least one pair of rollers which has a fixed and a movable roller (145, 146). Furthermore, a setting device (163 - 180) for the distance between the axes of the pair of rollers and a foreign-body protection device (168 - 174) for rapidly increasing the roller spacing in the event of entry of a foreign body into the grinding gap are provided. The bearing housings (147, 149; 157, 159) of the two rollers (145, 146) are combined to form a jointed frame forming a roller stack (4, 5, 6) by means of connections (155, 156; 163 - 174) situated above and below the roller axes, in one of which connections the setting device (163 - 180) and the foreign-body protection device (168 - 174) are contained. At one end of the connection containing the setting device (163 - 180) and the foreign-body protection device (168 - 174), there is provided an eccentric (165) which alters the length of this connection in the case of rotation and has an actuating lever (175) which is supported, via an adjusting arrangement (176, 177) which extends away from the actuating lever (175) at an angle, is of variable length and is formed by a threaded spindle (177) and a swivelling journal (176) having a female screw thread arranged on the latter, on a fixed bearing part, provided on the opposite side of the axle end (151, 162), on the axle journal (156). <IMAGE>

Description

The invention relates to a device for grinding and / or pressing food or feed components according to the preamble of patent claim 1.

Storage of the rollers of milling roller mills is already known (DE-PS 426 907), in which a bearing shell for the other roller is pivotably mounted on a bearing base containing the fixed roller and fastened to the roller stand to create a first connection between the two rollers . On the opposite side of the swivel bearing of the stub axle of these rollers there is a further connection of the bearing housing, which has a foreign body protection device and, as an adjusting device for the distance between the two rollers, a threaded rod on which a nut designed as a handwheel is arranged.

The arrangement of the pivotable bearing shell directly on the bearing base for the bearing of the other roller has the advantage that the path of the grinding forces within the joint frame is made as short as possible. A disadvantage of the known arrangement, however, is that the fine adjustment can only be carried out manually by means of a nut-spindle arrangement which acts directly on the connection between the two bearing housings; this means that the required accuracy cannot be maintained and the threads have to absorb the full grinding pressure. Furthermore, a release device provided with an eccentric is provided, the adjustment linkage of which is supported on the roller stand and thus transmits part of the power flow and vibrations to the roller stand.

Furthermore, a pressing device for the rolling of roller mills is already known (CH-PS 97 418), in which the fixed roller directly in the roller stand and the movable roller in a lever bearing pivotably arranged on the roller stand are rotatably mounted so that the power flow and vibrations are transmitted to the roll stand. The end of the lever bearing facing away from the pivot axis is held on the roller stand via a connection containing a foreign body lock and an eccentric, so that the rollers are held at a defined distance. The eccentric has an actuating lever which can be pivoted in a defined manner via a length-adjustable adjustment arrangement, as a result of which the roller spacing can be adjusted.

The aim of the present invention is to provide a device of the type mentioned at the outset, which can be attached to other parts without disturbing the flow of force or being transmitted to these parts.

To achieve this object, the features of the characterizing part of claim 1 are provided.

According to the invention, the fine adjustment of the roller spacing is carried out by means of an eccentric provided at one end of the adjusting device, the special feature being that the actuating arrangement for the eccentric is located on a fixed bearing part, ie on a part of the bearing base which carries the roller attached to the roller stand, supports. This ensures, on the one hand, the fine adjustment characteristic of an eccentric with a high power transmission capacity and, on the other hand, that no adjustment forces or vibrations are transmitted to the roller stand even via the variable-length actuating arrangement for the eccentric. Above all, the setting device is made an integral part of the roller package in a simple manner while maintaining the principle of fine adjustment by means of an eccentric, so that it can be completely prefabricated and attached to other lines.

Fig. 1

die erfindungsgemäße Vorrichtung in Gestalt einer Malzschrotmühle in schematisierter Schnittdarstellung,

Fig. 2

die Malzschrotmühle gemäß Fig. 1 in Ansicht bei abgenommener Verkleidung des Mittelteils, ebenfalls in stark vereinfachter Darstellungsweise,

Fig. 3

ein Detail aus Fig. 2 in vergrößerter Darstellung,

Fig. 4

einen Schnitt längs der Linie IV - IV in Fig. 3,

Fig. 5

einen Schnitt V - V in Fig. 4,

The invention is described below, for example with reference to the drawing; in this shows:

Fig. 1

the device according to the invention in the form of a malt grist in a schematic sectional view,

Fig. 2

1 in view with the covering of the middle part removed, likewise in a greatly simplified representation,

Fig. 3

3 shows a detail from FIG. 2 in an enlarged representation,

Fig. 4

4 shows a section along the line IV-IV in FIG. 3,

Fig. 5

4 shows a section V - V in FIG. 4,

The malt grist mill shown in FIGS. 1 and 2 consists essentially of two supporting columns 2 of the machine housing 3 projecting from a base plate 1, between which three roller packages 4, 5 and 6 formed as self-contained units by indicated screw connections 4 ', 5', 6 'are fastened (see also FIG. 2) and from two screen units 7, 8 arranged between the second roll package 5 and the lowermost roll package 6 with a counter-rotating drive 9.

The sieve units 7, 8 are symmetrical and each have two inclined, double-bottomed sieve compartments 10, 11 and 12, 13, respectively, in which two sieve frames 14, 14 'and 15, 15' are contained. Each sieve unit 7, 8 is articulated in the region of its side walls by means of a total of four articulation levers on supporting parts of the machine housing 3, so that they are activated by the drive 9 in the direction indicated by the arrows 16, 17 Can swing back and forth while doing sieving or separating work.

In operation, the material to be ground is fed to the roller package 4 via a feed roller 18 and a baffle plate 19, where it is - as in the subsequent roller package 5 - crushed. The meal is evenly distributed by a distribution device 20 to the two sieve units 7 and 8 or their sieve compartments 10 and 12, where semolina and flour portions are already sieved, while the husks remain above the sieve surface. This process continues in the lower sieve compartments 11 and 13, after which flour is finally drawn off through the outlet shafts 21 and 22 and through the shafts 23 and 24 husks. The semolina reaches the lowest roller pack 6 via guide devices 25, 26, where they are also ground to flour.

The arrangement of the sieve units is such that the sieve unit 7 is arranged on the one hand on two identical link levers, which in turn are firmly connected to corresponding drive levers 27 'and are pivotably mounted in an enlarged area 2' of the columns 2 of the machine housing 3; on the other hand, the sieve unit is supported by two further articulation levers 29 such that it can swing in relation to support arms (not shown) extending from the extended area 2 'of the columns 2 (not shown). The articulation of the sieve unit 8 is designed in an analogous manner, that is to say with corresponding articulation levers and drive levers 31 ′ assigned to them and articulated levers 33 arranged “standing”.

The center of gravity of each of the sieve units 7, 8 is approximately the same distance from all of their articulation points and in one plane with them. All of these levers have, due to their storage in rubber spring elements, to be described, restoring forces which, in the rest position, that is to say when the drive 9 is not switched on, bring about a vertical position of all the levers. The two-sided deflection from this rest position is relatively small due to the design of the drive 9 or the opposite oscillating movement generated by it; in connection with the likewise short effective lengths of all articulation levers, which is preferably only about eight to ten times the vibration range of the sieve units, this leads to a practically horizontal oscillating movement of the sieve units 7 and 8, so that disturbing vertical forces practically do not occur at all.

The drive 9 which causes the oscillating movement of the sieve units 7, 8 essentially consists of a drive shaft which is equipped at both ends with two eccentrics, so that the two sieve units 7, 8 execute an opposite oscillating movement.

The enlarged detail in FIGS. 3, 4 and 5 shows the roller package 4 designed as a closed structural unit with the roller pair 145, 146, which is described as representative of the roller packages 5 and 6 of the same design.

The roller package 4 containing the rollers 145, 146 has a bearing base 147 which forms the one bearing shell for the roller 146. A removable bearing shell 149 is fixedly connected to this by screws 148. A spherical roller bearing 150 (FIGS. 4 and 5) is clamped between the two, in which the stub shaft end 151 of the roller 146 is rotatably mounted. The spherical roller bearing 150 is secured laterally by a lock nut 152 and covered by bearing covers 153, 154 screwed together. At the opposite, invisible end, the second stub shaft of the roller 146 is mounted in the same way. The roller 146 is therefore removed by loosening the screws 148 and removing the bearing shell 149, whereupon the roller is free to be removed horizontally to one side of the column 2. The spherical roller bearing 150, the bearing caps 153, 154 and the lock nut 152 can then be removed from the stub shaft 151. The bearing base 147 overlaps the column 2 against the movable roller 145 with a bracket 155 and has an axle journal 156 on the free bracket end, to which a movable bearing shell 157 is articulated, in such a way that it can be pivoted against the bearing base 147 or away from it . A bearing shell 159 is detachably fastened to this movable bearing shell 157 by means of screws 158. Is between the removable bearing shell 157 and the bearing shell 159 (As already described with reference to the roller 146), a spherical roller bearing 160 is clamped, which is laterally covered by bearing caps 161. The stub axle 162 of the roller 145 is rotatably mounted in the spherical roller bearing 160. At the invisible end, the rollers 145, 146 are mounted in the same way and are also equipped with drive means which drive them at different speeds.

For the drive, each pair of rollers 145, 146 has a drive pulley on the axis of the high-speed, fixed roller 146. The overdrive from the roller 146 to the slow-moving, movable roller 145 is effected by chain drives or spur gears.

In order to engage or disengage the two rollers 145, 146 or to adjust the grinding gap, the bearing base 147 has a bearing eye 163 at both ends of the roller, in which a shaft 164 with an eccentric pin 165 is freely rotatably mounted. A clamp 166 is pivotally mounted on the eccentric pin 165, in which a screw 167 is firmly clamped with the screw head 168. The screw 167 passes through a nut 169 which is rotatably mounted in a bearing head 170 of the bearing shell 157. A nut 171, which is supported against the nut 169, is screwed onto the screw 167. A spring 174 is located between a spring bearing 172 bearing against the screw head 168 and a spring bearing 173 supported on the bearing head 170. The pretensioning of the spring 174 is set by adjusting the nut 171. This serves as an overload protection if a hard foreign body gets between the rollers 145 and 146 during the grinding process. In this case, the bearing shell 157 together with the roller 145 can pivot outwards against the action of the spring 174, thereby preventing mechanical damage to the pair of rollers.

The roller 145 is installed and removed in the same way as for the roller 146. After the screws 158 have been loosened, the bearing shells 159 are removed at both roller ends and the stub axles 162 are exposed. The roller can then be removed horizontally (away from column 2).

The roller gap is adjusted at both roller ends by rotating the shaft 164. For this purpose, the end of a lever 175 is articulated on the eccentric pin 165, in the other forked end of which a pivot pin 176 is rotatably mounted. A nut thread runs diametrically in the pivot pin 176, into which a spindle 177 is screwed. The lower end of the spindle is freely rotatably mounted in a bearing 178 which is firmly connected to the journal 156, so that the spindle 177 can be pivoted with the journal 156. The spindle 177 is non-rotatably and axially connected to the output shaft of an angular gear 179, which is flanged to a brake motor 180 on the drive side. The angular gear 179 is supported by a torque arm 181. On the one hand it can follow a pivoting movement of the spindle 177 and on the other hand the torque generated by the brake motor 180 is compensated for by the machine housing. By rotating the spindle 177 by means of the brake motor 180, the pivot pin 176 follows an arc around the center of the shaft 164 and rotates it. With the eccentric pin 165, the clamp 166 and the screw 167 move and pivot the bearing shell 157 or the roller 145 about the axle pin 156 at both roller ends.

The bearing base 147 has a comparatively large extension in the vertical direction of the column 2 and forms a long lever parallel to the column 2. At their upper and lower ends there is a screw connection 4 'with which they are attached to the column 2 is. The connecting straight line of the two screw connections 4 'runs essentially parallel to the column 2 and is roughly approximated centrally between the rollers 145, 146. The distance between the fastening points is preferably equal to or greater than the center distance of the rollers 145, 146 Roller drive and the forces transmitted by the rollers 145, 146 rotating at different speeds to the column 2 are comparatively small, and the smaller the greater the mutual distance between the screw connections 4 ', that is, the longer the effective lever is. The arrangement of the rollers 145, 146 on opposite sides of the column 2 also causes (at least in rough approximation) a symmetrical loading of the column 2, so that it can be made slim and light. In the case of multiple roller mills (as shown in FIGS. 1 and 2), in which the roller packs 4, 5, 6 lie vertically one above the other, the tab 155 with the journal 156 are preferably arranged alternately in the bearing housing of the fixed rollers 146, what also favors a symmetrical loading of the columns 2. Such multiple roller mills also have the advantage that each roller can be unhindered by other machine parts and removed to the side.

The bearings of the roller packs 4, 5, 6 each form a closed joint frame within which the forces and bending moments that occur during grinding are in equilibrium. These are therefore not to be taken up by the columns 2. They are only subjected to a load due to the weight of the roller packs and the drive torques. However, this burden is largely evenly distributed on both sides. Since the rollers 145 and 146 are mounted identically at both ends the parallel positioning of the rollers 145, 146 in the horizontal direction with the screw 167 by screwing it (at both roller ends) more or less into the clamp 166. The spring preload is always retained since the nut 171 is secured to the screw 167 with a stud screw.

The axes of rotation of the rollers 145 and 146 are leveled by pivoting the bearing housing about the lower screw of the screw connection 4 ', 5' or 6 ', with subsequent fixing of the bearing base 147 by tightening both screws. The parallelism of the rollers 145, 146 is achieved by screwing the screw 167 more or less into the clamp 166.

When the spring bearing 173 bears against the bearing head 170, the spring 174 pulls the screw 167 with the nut 171 against the nut 169, which is thereby pressed in its bearing in the bearing head 170 against the side facing the spring bearing 173. Since the grinding forces run in the same direction, there is play-free mounting of the nut 169 in the bearing head 170, with the advantage that the screw forces (= grinding forces) always run through the center of the nut 169 when the bearing shell 157 is pivoted.

Due to the motorized adjustment of the roller spacing, there is a risk that the rollers 145, 146 can run empty on one another due to incorrect control of the electronics. This can cause significant damage when the rollers 145, 146 are running. To prevent this is on both. An adjustable stop screw 182 is screwed into the bearing base 33 at the ends of the rollers and cooperates with a stop plate 183 which is fixedly arranged on the movable bearing shell 157 in such a way that it moves together the rollers are mechanically prevented. In addition, a stationary safety switch 184 is connected to the column 2 and can be actuated by a sensor 185 attached to the movable bearing shell 157. The switching point is adjustable by means of a micrometer screw 186. These safety switches 182 are at their switching point below the grinding gap but above the roller contact, so that the rollers are stopped before they can touch each other.

The shaft 164 is provided with a rotational position indicator 187 which interacts with a fixed (i.e. firmly connected to the column 2) reference switch 188. The reference switch 188 and the rotational position indicator 187 are matched to one another in such a way that the latter closes a switching contact in the first with a switching accuracy of ± 2/100 millimeters when the movable roller 145 reaches its disengaged position. When the rollers disengage, the reference switch 188 signals that the defined disengagement path has been reached within the tolerance mentioned. If this signal is missing at the end of the disengagement process, there may be an adjustment and the rollers will switch off automatically.

Claims (15)

1. Apparatus for the grinding and/or pressing of foodstuff and animal feed constituents, having at least one roller pair on a roller stand (1, 2) comprising a stationary and a movable roller (145, 146), and having an adjustment device (163-180) for the inter-axes spacing of the pair of rollers, also having a safety device (168- 174) against foreign bodies for rapidly increasing the inter-axes spacing when a foreign body enters the grinding gap, wherein the bearing housings (147, 149; 157, 159) of the two rollers (145, 146) are combined, by connections (155, 156; 163-174) which are situated above and below the roller axes and in one of which the adjustment device (163-180) as well as the foreign body safety device (168-174) is contained, to constitute an articulated frame which forms a roller set (4, 5, 6) and in which the normal forces occurring between the rollers (145, 146) during the grinding operation are accepted, and wherein each stub shaft (151) of one roller (146) is rotatably mounted in a bearing (150) arranged in a bearing base (147) secured on the roller stand (1, 2), and each stub shaft (162) of the other roller (145) in a bearing (160) which is arranged in a bearing shell (157) mounted pivotably by means of a pivot pin (156) on a strap (155) of the bearing base (147), whereby thereby there is provided the connection of the two bearing housings (147, 149; 157, 159) which is opposite relatively to the connection containing the adjustment device (163-180) and the foreign body safety device (168-174), characterised in that at one end of the connection containing the adjustment device (163-180) and the foreign body safety device (168-174) there is arranged an eccentric (165) varying the length of this connection at rotational movement, and having an actuating lever (175, which, through the agency of an adjustment arrangement (176, 177) which extends away therefrom at an angle and is variable in length and is formed more particularly by a screwthreaded spindle (177) and a female-threaded swivel pin (176) arranged thereon, is supported on a stationary bearing part (strap 155) provided at the opposite side of the stub shafts (151, 162), advantageously on the pivot pin (156).
2. Apparatus according to claim 1, characterised in that the roller stand has a bed plate (1) and two vertically disposed parts (2) for securing the bearing base (147) which pivotably bears the movable bearing shells (157).
3. Apparatus according to claim 1 or 2, characterised in that the bearings (150, 160) are held releasably, by releasably arranged bearing shells (149, 159), on each bearing base (147) and each movable bearing shell (157).
4. Apparatus according to one of the preceding claims, characterised in that the vertically disposed parts of the roller stand or of the housing (191) containing the rollers (145, 146) are two columns (2) on which the bearing base (147) of the stationary roller (146) is secured, and that the columns (2) are situated between the end-situated stub shafts (151, 162) of the rollers (145, 146), and preferably a plurality of roller pairs (145, 146) are secured on the columns (2).
5. Apparatus according to one of the preceding claims, characterised in that the spindle (177) of the nut-and-spindle arrangement (176, 177) is driven via a bevel gearing (179) by a braking motor (180), and the bevel gearing (179) and the braking motor (180) are arranged on that end of the spindle (177) which is remote from the region at which it bears on the stationary bearing part (strap 155).
6. Apparatus according to claim 5, characterised in that the bevel gearing is supported by a torque bearing (181).
7. Apparatus according to one of the preceding claims, characterised in that the stub shafts (151) of the roller (146) arranged on the bearing base (147) are situated at one side of the points (4', 5', 6') at which the bearing base (147) is secured on the roller stand (1, 2), and the stub shafts (162) of the roller (145) arranged on the pivotably arranged bearing shell (157) are situated at the other side of these securing points (4', 5', 6').
8. Apparatus for the grinding and/or pressing of foodstuff and animal feed constituents, having at least one roller pair on a roller stand (1, 2) comprising a stationary and a movable roller (145, 146), and having an adjustment device (163-180) for the inter-axes spacing of the pair of rollers, also having a safety device (168-174) against foreign bodies for rapidly increasing the inter-axes spacing when a foreign body enters the grinding gap, wherein the bearing housings (147, 149; 157, 159) of the two rollers (145, 146) are combined, by connections (155-156; 163-174) which are situated above and below the roller axes and in one of which the adjustment device (163-180) as well as the foreign body safety device (168-174) is contained, to constitute an articulated frame which forms a roller set (4, 5, 6) and in which the normal forces occurring between the rollers (145, 146) during the grinding operation are accepted, and wherein each stub shaft (151) of one roller (146) is rotatably mounted in a bearing (150) arranged in a bearing base (147) secured on the roller stand (1, 2), and each stub shaft (162) of the other roller (145) in a bearing (160) which is arranged in a bearing shell (157) mounted pivotably by means of a pivot pin (156) on a strap (155) of the bearing base (147), whereby the connection is provided of the two bearing housings (147, 149; 157, 159) which is opposite relatively to the connection containing the adjustment device (163-180) and also the foreign body safety device (168-174), more particularly according to one of the preceding claims, characterised in that the bearing base (147) is secured to the roller stand (1, 2) by two screwing fastenings (4'; 4', 5', 5', 6', 6') which are vertically spaced-apart.
9. Apparatus according to claim 8, characterised in that the spacing between the fastening points (4', 4'; 5', 5'; 6', 6') is equal to or greater than the inter-axes spacing of the rollers (145, 146).
10. Apparatus according to claim 8 or 9, characterised in that the axes of rotation of the rollers (145, 146) are adjustable in their horizontal attitude by pivoting the bearing housings (147, 149; 157, 159) about the lower screw of the screwing connections (4', 4'; 5', 5'; 6', 6').
11. Apparatus according to claim 10, characterised in that the bearing base (147) is subsequently fixable by tightening the two screws.
12. Apparatus according to one of the preceding claims, characterised in that the rollers (145, 146) are mechanically prevented from running on to one another by a pair of abutments (182, 183) secured on the bearing base (147) and the movable bearing shell (157) respectively.
13. Apparatus according to one of the preceding claims, characterised in that in the event of approach below the grinding gap but above roller contact the rollers (145, 146) are stoppable by a pair of safety sensor switches (184, 185) which are effective between the roller stand (1, 2) and the movable bearing shell (157).
14. Apparatus according to one of the preceding claims, characterised in that the eccentric shaft (164) is provided with a rotation position indicator (187) which cooperates with a stationary reference switch (188).
15. Apparatus according to claim 14, characterised in that at disengagement of the rollers (145, 146) the reference switch (188) signals that the defined disengagement distance within the tolerance limit has been reached.

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