WO2009052640A1

WO2009052640A1 - Cardanic doctor blade

Info

Publication number: WO2009052640A1
Application number: PCT/CH2008/000407
Authority: WO
Inventors: Kurt Müntener
Original assignee: Bühler AG
Priority date: 2007-10-25
Filing date: 2008-10-02
Publication date: 2009-04-30
Also published as: EP2207621A1

Abstract

A device (101; 101a; 101b) for working dispersions has at least one elongated shearing tool (3), which is guided with respect to a working surface of a shearing plate (1; 1a, 1') to perform a shearing motion and driven by means of a drive shaft (111) to perform a rotating motion (16). The respective shearing tool (3) extends at an angle (e.g. -a, +a) transversely in relation to the axis (111a) of the drive shaft (111). In this case, the respective shearing tool (3) has on a shearing surface (3c) a shearing edge (3d) running substantially transversely in relation to the axis (111a) of the drive shaft (111). Furthermore, the respective shearing tool (3) is connected to the drive shaft (111) on one side by means of a cardan joint (10a). A loading device (6), in particular a spring, loads the shearing edge (3d) approximately in the region thereof or close to it against the shearing plate (1; 1a; 1'), while the shearing surface (3c) runs obliquely in relation to the shearing plate (1; 1a; 1'), forming a wedge angle (4), on account of the cardan joint (10a) on the one hand and the loading device (6a) on the other hand.

Description

Cardanic knife

The invention relates to a processing device according to the preamble of claim 1.

Such devices are used for dispersion layers in the electronics industry, for dye processing and for dispersions of solid particles in fat, so for example chocolates and chocolate-like masses. The processing involves grinding or comminution, but also rounding off the particles, homogenization, as well as the anodization or homogenization of the dispersion compounds.

The milling of dispersions is practically always a fine grinding. The term "fine grinding" means that at the end of a grinding process solid particles with a mean particle size of less than 20 μm are distributed in the liquid.Electron industry today even requires dispersions of solid particles in the nanometer range.The milling effect is used in most wet grinding processes (which of course The shearing forces are intended to tear and thus break up the individual grains.For liquid grinding, for example, stirred mills are also used in which the dispersion to be milled is sheared by moving balls.

Another example of the application of such shear forces are the so-called Reibwalzwerke in which under pressure abutting rollers rotate at different speeds and usually in the opposite direction of rotation. It is top priority that the shearing zone limiting, usually metallic parts do not touch each other, but in between a thin layer of the dispersion to be mated, the layer thickness also determines the achievable Komfeinheit. Therefore, any unevenness of the roll surfaces or any deviation from the parallelism of the rollers producing the shear or, in the case of other shear forces, prevents The same deviations from heavy tools to a shear surface, the achievement of the desired uniform grain sizes over the entire shear range or make therefore the process inefficient. In rolling mills, it is difficult to provide a uniform nip with roll shafts parallel to each other, especially at varying pressures. In addition, such rolling mills are relatively space consuming and expensive. In addition, in most cases they require pre-grinding of the coarsest particles of the dispersion.

The invention has for its object to provide a machine of the type mentioned in such a way that it can be produced inexpensively and used in many ways and still produces the desired products in excellent quality with high efficiency. According to the invention, this is achieved by the characterizing features of claim 1.

Characterized in that the respective shear tool extends at an angle transverse to the axis of the drive shaft, that is, in the ideal case extends radially and is guided against a shear surface by rotation of the drive shaft to a shearing motion, wherein the respective shear tool is a substantially transverse to the axis of the drive shaft However, it must be noted that on the one hand for manufacturing reasons due to distance and geometric tolerances per se can never be perfect parallelism. On the other hand, the friction - and thus the wear - over the length of the shearing edge or the radius of movement due to the radially outward continuously increasing peripheral speed is different. Because of the imperfect parallelism, the consequence is already from the outset a shearing gap of different lengths over the length of the shearing tool, which leads to a different particle size or a correspondingly wide particle size distribution (Gaussian distribution according to a bell curve). This changes over the operating time due to the different abrasion over the length of the shearing edge as well as due to the abrasion of the shear plate constantly the shear gap. The importance of this fact comes to light, considering that 1 second of angular deviation parallelism, corresponding to 0.0028 degrees, with only two rigidly attached to the drive shaft, in particular opposite each other, mounted shear tools, for example, each 150 mm in length and an outer Shear diameter of 400 mm already results in a deviation of the size of the shear gap of 19.4 microns, whereas the grain size should be smaller than this measure, that is about 15 microns, 10 microns or even 1 micron.

To compensate for all this, the respective shearing tool should be connected to the drive shaft via a universal joint, which allows an automatic adjustment of the optionally partially worn shear edge or shear surface to the coating surface, in particular in the interaction of all the heavy tool loading forces, such as the force of Loading device, which - together with the Kardanlagerung - a three-point support of the heavy tool on the, a counterforce impacting layer of the mass to be machined, as will be explained later.

This adaptation results in a well controllable way, especially when a loading device, in particular a spring, is provided, which approximately in the shear edge or near the shear edge against the shear surface loads, while the shear surface due to the universal joint on the one hand and the loading device on the other hand, forming a pull-in angle, oblique to the shear surface. Of course, the load device should and must exert the necessary pressure on the shear edge, and so strong that in the equilibrium state of the depressing force against the force of the back pressure of the mass of the desired large shear gap arises.

In this case, it is preferred if the shearing tool is guided on the end opposite the universal joint, preferably radially outward, by means of a guide arrangement substantially perpendicular to the direction of rotation or parallel to the axis of the drive shaft. In the preferred case, therefore, the universal joint is radially inward. Furthermore, the guide arrangement is preferably formed by an oblong hole on an arm protruding from the drive shaft, which can be configured differently. In an expedient embodiment, this guide arrangement, the shear tool, in particular attached thereto, optionally cylindrical pin, in the direction of rotation with game, for example, by the width of the elongated hole is greater than the diameter of the pin, so that for tilting movements about the universal joint even at maximum deviation from the parallelism or maximum abrasion of the shearing edge enough leeway remains. At the same time, the guide arrangement secures against the falling out of the universal joint from its joint socket.

Further details of the invention will become apparent with reference to the following description of exemplary embodiments shown schematically in the drawing. Show it:

1 A is a vertical section through a first embodiment of a processing machine according to the invention, to which

Fig. 1B is a plan view and a section along the line B-B of FIG. 1A below

Omission of the double wall of the container illustrated;

Fig. 2 is a detail section along the line H-II of Fig. 1B;

Fig. 3 is a view in the direction of the arrow III of Fig. 1 B;

Fig. 4 is a detail section along the line IV-IV of Fig. 1 B; the

Fig. 5, 7, 8 illustrate in several sections respectively along the line AA of Fig. 1B, the situation when shear and shear plate are parallel to each other (Fig. 5), in Figs. 7 and 8 each a situation with non-parallel position of this Parts, whereas the

Fig. 6 shows the shear tool in axonometric view; the

Figures 9, 10 illustrate two alternative embodiments for a four-bar device, each arm carrying at least one shear tool according to the invention; the

Fig. 11 A, 11 B show two other embodiments of a processing device according to the invention, of which

12 is a drawn in Fig. 1B section along the line XII-XII, Fig. 13 is a drawn in Fig. 1B section along the line XIII-XIII, and

Fig. 14 is a sectional view taken along the line XIV-XIV in Fig. 1B;

Fig. 15 is a plan view of a variant of the shear plate, the in

Fig. 16 in a section along the line XVI-XVI of Fig. 15 and in

Fig. 17 is shown in a section along the line XVII-XVII of Fig. 15, whereas Fig. 18 is a section along the line XVIII-XVIII of Fig. 15 and the

Fig. 19 is a perspective view of this shear plate, whereas the

Compare the

Fig. 20, the previously discussed with reference to FIGS. 12-14 embodiment of

Shear plate in a similar perspective view shows; on the basis of the perspective view of the

FIG. 21 is intended to explain the geometric and physical conditions of the cardanic mounting of a shearing tool; FIG. the

Figs. 22a-c illustrate the principle of a shear arrangement as could be used in devices of Figs. 11A and 11B, but without a universal joint, in which Fig. 22a is a sectional view taken along line aa of the plan view of Figs. 22c and 22b is a section along the line bb of Fig. 22a; on the basis of the perspective view of

Fig. 23 is the principle of the one-sided gimbal bearing of the heavy tool on the basis of a version with a substantially rectangular shear plate explained, which is mounted on a shortened arm by means of a ball joint; the 24 to 26 show the temperature control flow according to a particular embodiment in a shaft assembly according to the Fig. 11 A, wherein the Fig. 26 is approximately the upper part of Fig. 24, which is a section along the line XXIV-XXIV of FIG and Fig. 25 is a section along the line XXV-XXV of Fig. 24; the

Fig. 27 illustrates an axial section through another embodiment, to which

Fig. 28 shows an enlarged detail of the relative position and arrangement of two axially spaced-apart shear units, whereas the

29 to 31 a comparison of the respective drive shafts including shear units for the embodiments of FIGS. 1A, 1B on the one hand, the Fig. 11 A, 11 B on the other hand and Fig. 27 in perspective view.

A container 101 has a hopper 102, an upper cylindrical tube section 103 and a lower outlet section 104 with a discharge funnel. Between the upper tube portion 103 and the outlet portion 104, a shear plate 1 is inserted and by means of the flanges 105, 106 of the two sections 103 and 104 passing through, in Fig. 1A only dash-dotted lines indicated bolt 107 tightly screwed through corresponding holes (107a in Fig. 15 and 19, 20) protrude, with seals 108 are provided (see Fig .. 12-14).

Preferably, all sections of the container 101 are double-walled, in order to temper the mass located therein-generally a dispersion-via a gap-shaped space 109. The term "tempering" should be understood here as a generic term for a cooling or heating, because at the beginning of operation, so when the container 101 is still cold, it may be useful to heat the mass of a heating medium in the space 109, while at During operation, the resulting heat has to be dissipated via a cooling medium.If this is referred to as a gap-shaped space, it is understood that this design is different can be, for example with helical heating / cooling channels. Alternatively, of course, optional heating (eg, electrical windings) and cooling ducts could be provided, although this will generally be less preferred. In the present case, however, the space 109 may serve the flow of a temperature control medium and be provided for this purpose with corresponding terminals 118 (only one is shown) for supply and removal of this medium.

With the shear plate 1, a shear arrangement cooperates, the one to a rotation in the direction of the arrow 16 about its geometrical axis 111a drivable drive shaft 111 and seen from the top view in the direction of the line BB arms 18a to 18d (in the illustrated embodiment, there are four; see also Fig. 1B) for fixing plate-shaped, substantially oblong rectangular shear tools 3 with shear surface 3c (Fig. 6) and shear edge 3d has. The shear plate 1 takes the axis 111a at an angle 131, which for manufacturing reasons or due to mounting tolerances of exact 90 ° - will differ within a tolerance specification (although not intended). The details of this shear tool and its storage in cooperation with the shear plate 1 will be discussed below.

For the time being, however, the material flow in the processing machine 101 will be discussed in connection with FIG. 1A. A dispersion, such as, for example, a cocoa-containing dispersion in a fatty substance, is introduced through the top 102 of a container and passes by gravity and / or pumping into the region of the cutting tools 3 and the shear plate 1. The pumping can - as shown - several times done in a cycle. The shearing tools 3 occupy a predetermined angle 4 (Fig. 2) to the surface of the shear plate 1 and have a multiple effect:

> Due to their at least approximately radial orientation, starting from the shaft 111, they rub against the shear plate 1, so that the solid particles of the

, Dispersion are comminuted;

> the mass is homogenized and anointed.

Thus, after the machining has been carried out in this way at least in a first passage (in this case, the illustration of FIG. 1A shows only a shearing arrangement in the beginning). cooperate with a shear plate 1, although several waves 111 could also be arranged parallel to each other), the machined mass can pull off. This can be done in different ways; For example, it would be conceivable to provide at least one outlet opening radially on the outside of the shear plate 1 and / or in the wall of the section 103. In the present case, however, the shear plate 1 has at least one passage opening 112 for the machined mass, preferably a plurality of such openings 112, which are distributed over the surface of the shear plate 1, but preferably over the edge surface. In this way, the mass passes into the area bounded by the section 104 and (above) by the shear plate 1, from where it can be pumped off and / or recycled for further processing, as indicated by a line 113 shown schematically. For this purpose, Fig. 1A shows a pump 114 and a directional control valve 115, which can optionally be opened both to the line 113 and to the output line 116.

It should be mentioned here that the described material passage through the machine can also take place via at least two shearing plates 1 connected in series with associated shearing tools 3 in a similar manner, as will be described later with reference to FIG. 27 with reference to another embodiment.

In order that a smooth transfer of the machined mass from the upper tube section 103 into the underlying section 104 can take place, a vent tube 117 may be provided outside the path of movement of the arms 18a to 18d (see FIGS. 1A and 1B), which allows when flowing out of the mass from the outlet section 104 or during the flow of ground from above a fuss promoting air pressure compensation takes place.

As for the shearing tools 3, they are supported and guided on the arms in a manner as discussed particularly with reference to FIGS. 2-8 and FIG. 23, respectively. The bearing is preferably on one side of the universal joint, in particular on the radially inner side, whereas the other side, in particular the radially outer side, has a loose guide with clearance. The game is expediently so great that the pin 10b can move freely in the amount of horizontal relative movement as a result of rotation of the shear tool 3 about its on the basis of FIG. 23 described spatial diagonal 33 '. This bearing and guide thus comprises a universal joint 10a on the radially inner, the shaft 111 facing side and - preferably - a height movement or lateral movement permitting guide 18 ', 119 for movement at least in the extent h of Fig. 1A, ie perpendicular to the direction of rotation 16 of the shaft 111 and parallel to its axis 111a. The height movement within the mass h is advantageously dimensioned so that at maximum deviation from the parallelism or at maximum possible or tolerable abrasion of the cutting tools 3, the cylindrical pin 10b the upper or lower limit of the slot 119 as far as possible not yet reached.

Since the universal joint 10a or 10a 'provided according to the invention permits movement on all sides, it is expedient for the elongated hole 119 to have a certain play relative to the journal 10b. In this case, the slot 119 should be so wide that the pin 10b guided therein permits a movement transversely to the extension direction of the elongated hole 119 upon tilting of the shearing tool (as described about the diagonal 33 'on the basis of FIG. 23). This means that the shear tool 3 by the pressure 6 of the loading device instead of the position shown in solid lines, in which its plane through the points of the cardan joint (ball 10 a ') and the side edge of the tool 3 defining points (3-point storage ), which assumes the dot-dashed position in which the three points are determined by the universal joint 10a 'and the points defining the shear edge 3d.

This guide arrangement 18 ', 119 is preferably located on the radially sweeter end of the arm, although a guide at the inner end (see stops 39') will be explained with reference to FIG. This can be done in any case - regardless of any uneven mass wear facing the shear plate 1 shear edge of the cutting tools 3 - an automatic adjustment and adjustment. As can be seen, the arms 18a to 18d extend above the shearing tools 3 and engage over their entire length, so that the shearing tools 3 at its other, preferably radially outer, end by means of an apparent from Fig. 1B end plate 18 'then secured against falling out is when the universal joint according to FIGS. 5-8 is formed by a pin 10a with decreasing diameter towards the free end and not by a ball 10a 'as in Fig. 23. However, under the Invention, the universal joint should also be formed by a cylindrical pin, but which is in a bearing hole, which is wide enough to allow the desired gimbal movement.

The embodiment of the pin with a certain conicity according to FIGS. 5-8 has the advantage that the pin 10a can be easily inserted into its bearing hole and at the same time a stop in the horizontal direction radially inward, without the vertical movement or a hinder horizontal pivoting movement of the heavy tool 3. In contrast, different solutions would be possible with a ball and socket joint 10a ¹ according to FIG. 23: either the arm 18a 'is divided in a horizontal plane (referring to FIG. 23) and passing through the ball joint socket (indicated by the dot-dash line in FIG. so that the ball joint 10a 'first in the lower part of the arm 18a' inserted and then the upper part above it, in any manner, for example by means of clamping screws, is attached. Or the arm has an insertion hole, in which also the ball 10a 'is inserted, and on the inside of this hole an expandable joint socket, for example made of plastic, which receives the ball 10a' under widening and then snap together elastically.

In any case, Fig. 23 shows a preferred embodiment, although in a universal joint 10a ¹ , which thus prevents a displacement radially outward itself, as is the case with the ball joint 10a ', an embodiment without the guide assembly (see .Low 119 in FIG 3) is possible at the outer end of the arms 18.

However, such a guide (a movement of the pin with the ball 10 a 'leading vertical slot style with clearance) can also be provided at the radially inner end, such as by two parallel stops or by an L-shaped angle iron. This L-shaped stop 39 'with at the rear downwardly guided leg and under the bearing pin for the heavy tool 3 extending horizontal leg can be seen in Fig. 23, which the one-sided storage of the shear plate 3 in a ball joint 10a' at a - compared to the previous embodiments - shortened arm 18a illustrated. In any case, the leadership has the task of limiting the per se possible free movement of heavy tools 3 in the direction of rotation, forward and possibly also down. Due to the one-sided storage of the substantially rectangular shear plate 3 at a location remote from the shear edge 3d location, the shear plate 3 assumes the position shown in solid lines, in which it rests with its end points 29 and 30 on the shear plate 1. Due to the load in the direction of arrow 6, however, the shear plate 3 is tilted around the space diagonal 33 and pressed into the dot-dashed position in which their shear edge 3d in a desired manner along a straight line 32 between their end points 29 and 31 abuts the coating surface 1 or along this line 32 limits a shearing gap 15 (see Fig. 21).

Looking at the axonometric view of Fig. 6, it can be seen that the shearing tool 3 is composed of a support plate 3a and a wear plate 3b. The wear plate 3b can be connected in any manner with the support plate 3a, for example by means of a releasable holder, by gluing or the like. Accordingly, the wear plate 3b on the downwardly facing side has a shear surface 3c which terminates at a downwardly turned shear edge 3d. The storage of this cutting tool 3 takes place on one side in an approximately peg-shaped universal joint 10 a, which is arranged at a distance from the cutting edge 3d, wherein the universal joint preferably in a pin 10 b along a longitudinal axis O its continuation. This pin 10b is supported on the respective arm 18, as explained above, preferably so as to permit movement parallel to the axis of the drive shaft 111 (FIG. 1A), i. Advantageous in the already mentioned slot 119 within the apparent from Fig. 1B end plate 18 '. The accommodation and support of the elongated hole in the end plate 18 'is the advantage of a shear tool 3 over its entire (radial) length cross-arm 18. It is advantageous if the width 11a (Fig. 3) of the slot 119 is so much greater than the diameter of the pin 10b that a possible swiveling tangential movement of the pin 10b is not hindered. This slightly swinging tangential movement can be created by rotation of a rectangular shear tool 3 about its diagonal 33 '(FIG. 23) in the event of a change in the distance of the heavy edge 3d or 3d' and the axis O to the shear plate 1.

Incidentally, it can be seen from a comparison of FIG. 1A with FIGS. 2-4 that the shear plate 1, where heat which is to be dissipated during processing, is also conveyed over canals. Ie 120 can be tempered, which are provided with corresponding connections, such as the one shown in Fig. 1A connection 121. This, together with the other temperature control measures, allows a relatively accurate maintenance of an optimum temperature of the mass, for which purpose optionally at least one temperature sensor (not shown) is connected to a corresponding temperature control loop.

In order to counteract the dynamic buoyancy 8 (see FIG. 21), while maintaining the necessary shear gap 15 (generally <20 μm), a loading device, in particular a spring 6a (FIG. 4), is provided. As FIG. 4 shows, this spring 6a (or some other load) lies approximately above the region of the shearing edge 3d or near this shearing edge 3d and loads it against the shear plate 1 via loading bolts 6c, while the shearing surface 3c of the heavy tool 3 is grounded of the universal joint 10a on the one hand and the loading device 6a on the other hand, forming a pull-in angle 4 (FIG. 2), runs obliquely to the shear plate 1. It should be noted that in FIG. 1B, the through holes 112 are not shown for the convenience of illustration. The spring 6a is seated in each case in a spring housing 6b, and their pressure on the respective loading bolt 6c is optionally adjustable by means of an adjusting screw 122. The arrangement of the spring 6a, seen in the radial direction of the arm 18 and the underlying tool 3, is not critical. As can be seen from the arrow 6 of FIG. 21 or 23, a single loading device suffices per se. In the case of the embodiment according to FIG. 1B and the associated detailed figures, two such spring housings 6b are provided at a distance from one another per cutting tool 3, as is preferred. But it can also be distributed over the (radial) length of the cutting tool 3 more load devices of the same or different kind.

The effect of this arrangement is best seen in FIGS. 5 and 7, 8. Accordingly, the pin 10 a formed into a universal joint is accommodated in a bearing hole 10 b of an arm 18. In this case, the bearing hole 10b is preferably provided with a radius R permitting a clearance to facilitate the cardanic function at the inlet. The pin 10 a is just formed so that it can move and rotate in the bearing hole 10 b in all directions, in particular by rolling at the radius R, and thus exerts a Kardanfunktion. The above-mentioned longitudinal Slit 119 (Figure 3) prevents the pin 10a and its associated shear tool 3 in the direction of movement of the arm 18 is able to move so strong that the pin 10a could fall out of the bearing hole 10b. However, this movement limitation could also be done in other ways, for example on the side of the pin 10a, be it by a ball head (FIG. 23) or possibly also by a pin 10a surrounding, eg dome-shaped, flange, in the direction of the axis O through a holding part is held. In the parallel position of arm 18 and shear plate 1 shown in FIG. 5, the gimbal axis O and the axis O ¹ defined by the bearing hole 10b coincide, which is the case when the shear plate 1 is in an inclination to the shear edge 3d when two are opposite each other Arms 18 are at an angle of 90 ° transverse to the pitch axis, and provided that the shear plate 1 is still flat.

If, however, the shearing tool 3 or its shearing edge 3d (and / or the shear plate 1) becomes stronger at the radially outer end, then the situation according to FIG. 7 can arise in which the shafts O and O 'enclose an angle with one another. This Fig. 7 clearly shows that it really only depends on a relative movement, because while the universal joint with the pin 10a by the oblique position compensates for the wear of the shear surface or the shearing edge, theoretically, the shear plate 1 could be movably mounted to to make this possible. However, such a solution would be difficult because of the necessary tightness of the container 101 (see Fig. 1A) and demanded at least double-sided pivotally mounted shearing tools, as shown in Fig. 22a, whereas completely rigid shearing tools due to deviations of the planes of the arms in this case could not be enough. It is clear that such a solution is an invention independent of the present patent application.

The reverse case, namely that a special wear takes place on the radially inner side of the shearing tool 3, is shown with reference to FIG. 8. Again, then the axes O and O 'due to the gimbal bearing to each other at an angle, and accordingly - as shown - an adjustment of the position of the shear tool to its own wear automatically done so that below the shear edge 3d a small, but give even gap which ensures a uniform processing of the dispersion and a uniform grinding effect.

In order to illuminate the geometrical and physical conditions of the storage just discussed, briefly refer to FIG. 21, in which the corresponding arm supporting the cutting tool has been omitted for the sake of clarity. The shear plate 1, which is preferably flat, but also within the scope of the invention, e.g. can be curved in the manner of a cylinder (similar to a conch trough is the case), is shown here simplified. On this shear plate 1 will therefore be a certain dispersion layer 2, which is to be processed. About this shear plate 1 and the dispersion layer 2 lying thereon, the shearing tool 3 sweeps with its shear edge 3d. With regard to the principles of theological shear between dispersion layers, reference is made to DE-A-42 21 315. Of course, these principles also apply in the present case when it comes to shear.

In Fig. 21, the shear tool 3 is shown as a simple plate, although it may take various forms per se, whereas the gimbal bearing pin 10a and the guide pin 10b are indicated only by dash-dotted lines. Since the shearing tool 3 is pressed against the shear plate 1 by the arm 18 (see, for example, FIGS. 5 and 7, 8) via the loading device 6 (see bolt 6c) over the entire (radially extending) length of its shearing edge 3d (cf. to this also Fig. 23) and on the other hand, the center of the gimbal bearing 10 at a predetermined distance 9 to the shear plate 1, the already mentioned angle of attack results 4. Regardless of whether the shear plate 1 all around exactly at right angles to the drive axis 111a (Fig 1A), or whether the axis O is parallel to the shear plate 1, the shear edge 3d will abut the shear plate 1 over its entire length in each rotational position (in its non-moving state), whereas from the beginning of the rotation (arrow 5) the axis 111a is reached a dynamic state in which the edge is lifted by the buoyancy forces 8 of the mass so far that a constant shear gap 13 is formed. Because of the dynamics of the movement and the rheological-physical properties of the dispersion to be processed in the intake area 2 and in the intake gap 7 and due to the angle of attack 4, the shearing tool 3 of the shear plate 1 slightly lifting buoyancy force 8 will arise, which reduces the angle 4 slightly , The rotational speed 5 of the shear tool 3, together with the nip 7 and the physical properties of the material to be processed and the resulting state of equilibrium of the pressure forces 6 with the driving forces for the movement 66, as well as the gimbal bearing 10a retaining reaction forces, and the buoyancy forces 8 with the opposing forces of shear and back pressure 88 in the catchment room 2 under the cutting tool 3 ultimately determine the size of the shear gap 13 (distance 15 of the shear edge 3d of the shear plate 1). The desired size of this shear gap 13 or the distance 15, which determines the processing fineness of the dispersion, can be adjusted by the magnitude of the load 6 and preferably also vary. For all forces acting on the shearing tool 3 will ultimately be in a state of equilibrium with each other. For a grinding, this means that the maximum particle size of a dispersion to be milled after passing through the shear gap 13 is not greater than this itself.

So far, the arrangement, training and storage of each shear tool 3 has been discussed essentially. However, this can be driven in various ways relative to the shear plate 1. Because the problem at stake here is the processing of a mass or dispersion, such as chocolate, paints, coating compounds or the like. The arms 18 may protrude from the shaft approximately radially from her. Of course, it is not necessarily a construction with arms 18, because the shearing tools 3, for example, stored on a plate above them and can be driven by this, which covers them fully or only partially.

However, FIGS. 9 and 10 show two variants of the above-mentioned solution. In fact, if the shaft 111 rotates in the clockwise direction in the direction of the arrow 16, then it is possible to arrange it with a tangential to the direction of rotation 16 and arms opposite one another in the direction of rotation 16, which in FIG. 9 extends radially outwards to below, this time by 90 ° , Angle -α are directed backwards, unfold a pumping action in the manner of a centrifugal pump. This pumping action can be exploited, for example, to accelerate the machined mass radially outwards into a discharge opening arranged there or several thereof, which also means that the residence time in the respective reaction space is shortened. Conversely, it may be desirable to process the mass more intensively, and for this purpose, as seen in Fig. 10, the arms 18 may be directed radially outward at an angle + α forward to the direction of rotation 16 so as to counteract the centrifugal force and mass delayed to convey to the outside, ie to extend the residence time in the reaction space.

While Fig. 1A shows a machine 101 which is all in all specially designed for the intended purpose, Figs. 11A and 11B show machines which are known in their basics as mixers but for processing the mass or dispersion with the invention Shearing tools are provided. 11A shows a dash-dotted line of a mixing vessel 101a, which is flanged on its upper side to a drive with a motor M and motor shaft Mw and a hollow shaft 111 'mounted parallel thereto and driven by V-belt K with a housing 126 on the vessel 101a. This shaft 111 'rotates about a fixed axis 17 which on the upper side by means of the shape or wedge axis K1 and bolt 123 shown in detail in FIG. 26 rotatably, but axially displaceably mounted on a cover 124 and the shear plate at the bottom 1a bears. After loosening the nuts 140, the latter can be displaced relative to the shearing tools 3 by means of a relatively slight axial displacement of the wedge axis K1 which (according to FIG. 24) bears on the underside the shearing plate 1a, which means that the respective ones forming the loading device Springs 6 are compressed or relieved in the housings 6b. In this way, therefore, their pressure can be adjusted without having to actuate each individual adjustment screw 122 (FIG. 4). Thus, the device has two different pressure adjustment options, i. on the one hand individually on the adjusting screws 122 and on the other hand on the lifting or lowering of the wedge axis K1 on the nuts 140. But since the Gesamtverstellseinrichtung makes a Relatiwerstellung of shearing tools 3 and shear plate 1, it is understood that this could also be solved in reverse by the Shaft 111 'is height-displaceable with respect to the shear plate 1, but this will generally be less preferred.

Via connections 125 temperature control means can be supplied to the intermediate space between the shaft 111 'and the axis 17 or separate channels. The advantage of this solution lies not least in the fact that the mixing vessel 101a - after unscrewing the housing 126 - can also be used for other tasks. It can also - on Position of the housing 101 a to be placed such that a plurality of mutually parallel shafts 111 or 111 ', for example, with different tools, such dissolver tools for dissolving larger particles or Agglomera- th, by a common motor or driven separately.

The situation is similar in the case of Fig. 11B, but instead of a fixed to the container 101 a drive housing 126 (Fig. 11A) is provided via a lifting piston 127 in a stand 128 raised and lowered housing 126 a, so that Container 101a, after lifting out of the tool assembly or shaving unit 1, 18 shown in detail in Fig. 24 from the container, rolled away and can be replaced by another container. The drive unit of FIG. 11B can be designed substantially exactly as shown for FIG. 11A or in FIG. 26. In addition, it would be conceivable to operate the lifting device 127, 128 during the processing in the container 101a, so as to produce an up and down movement of the shaving unit 1, 18. Similarly, it may also be desirable in some embodiments for some applications to up and down the drive shaft 111 'during rotation in the container 101a and to provide a corresponding lifting device for it, although in both cases it is also possible to provide the same Up and down movement by raising and lowering the container 101a relative to the shaving unit 1, 18 to produce.

It should be noted that in the following the sections according to the lines XII-XII, XIII-XIlI and XlV-XIV of Fig. 1 B are to be discussed, but that the relevant embodiments in an analogous manner for a processing machine according to FIGS. 11 A or 11 B apply.

FIG. 12 shows an enlarged section along the line XII-XIII, which, however, also illustrates the connection 121 (FIG. 1A) and the tempering channel 120 together with the seals 108 in detail. Appropriately, in the illustrated embodiment with a tempering 120 further seals 129 are provided. This is advantageous if the shear plate 1 carries on its upper side a firing plate 1z, which, if desired, is easily replaceable after loosening the bolts 107. Fig. 13 shows the section along the line XII-XIII of Fig. 1B, but here one of the through holes 112 can be seen. As can be seen, the passage openings 112 are arranged so that no additional seal with respect to the tempering 120 is required.

Fig. 14 illustrates the arrangement of the vent tube 117 in a section along the line XIV-XIV of Fig. 1B. Also, this vent tube 117, which establishes the connection of the space above the shear plate 1 and the space below, is arranged so that no additional seal against the tempering 120 is required.

15 to 19 show a variant of a shear plate 1 ', in which for additional processing, in particular a more intensive grinding, the shear plate 1' with sharp edges 19 (see Fig. 16, 18, 19), preferably sawtooth, to the surface of the shear plate V or an interchangeable firing plate 1z 'are provided. During the movement of the shearing tools 3 (see previous figures) over the saw teeth with the edge 19, sudden up and down movements of the, preferably plate-shaped, shear tool 3, which - in addition to shearing - to a better grinding effect by additional smashing of the solid particles to lead. In this way, it may be possible to dispense with premilling coarser particles. In comparison, FIG. 20 shows a perspective view of the already explained shear plate 1.

While FIG. 21 has already been discussed above for clarification of the geometrical-physical conditions in the invention, FIGS. 22a to 22c show the theoretical case of a non-cardanic mounting of the shearing tools 3, which are each mounted here at their two ends, ie with per heavy tool 3 double-sided storage. This clearly shows the disadvantage that in the absence of parallelism of the arms 18 and the heavy tool 3 to the shear plate 1 (either by deviations within the geometric tolerance or due to deviations due to abrasion during operation) a one-sided widened and thus not parallel shear gap arises. Because it is clear that such an automatic adjustment to parallelism errors due to tolerances, assembly errors or wear is not possible; On the other hand, it is equally clear that the arrangement shown can easily be dungsgemäße could be converted by about the illustrated journal bearing is replaced on one side by a universal joint, for example, in the manner of Fig. 5-8, at the other end advantageous training either according to Fig. 3 or Fig. 23, possibly with appropriate guidance and / or holder against falling out of the Kardanzapfens from its storage hole, is provided.

In any case, of course, allows a fixed, two-fold storage of the shear tool with opposite journals parallelism only in the only possible position, so as to produce a everywhere uniform grinding gap or shear gap (see Fig. 13 in Fig. 21). Here it turns out that the universal joint provided according to the invention permits a dynamic adaptation over the entire revolution range of 360 ° and thus always a uniform shearing gap (13 in FIG. 21) is ensured.

Referring now to Fig. 22c, as may be the arrangement with two opposing arms and shearing tools (instead of four crosswise arranged arms corresponding to Fig. 1B), it should be noted here that with respect to the number of around the drive shaft 111 arranged shear tools per se, there is no restriction. For the sake of avoiding imbalance but it is expedient if the shearing tools are arranged at equal angular intervals around the shaft 111 and its axis 111 a. However, in some cases it may be desirable to attach only a single shear tool 3 to the shaft 111, and in that case it may be advantageous for such a shear tool to extend across the end of the shaft 111, so that it will be one End on one side of the shaft 111, the other end on the other side of the shaft 111 is located.

A version with a cooled shear plate 1a (see also FIGS. 11A, 11B) can be seen in FIGS. The arrangement and mounting of the shear tool 3 shown in FIG. 24 is the same as already described with reference to FIGS. 2-8. In this case, the drive shaft 111 ', mounted in a respective fixed bearing 28, 28' (Fig. 26), similarly as in Fig. 11A via a belt pulley 36 and the belt K driven, while in its hollow interior, the non-rotatable but advantageously axially displaceable , Double tube 17 (see also the connections 125 in Fig. 11A) is mounted, via which in the manner shown in Fig. 24 in the middle of a temperature control a supply channel 25 supplied and peripherally (see the arrows) is discharged from the temperature control 120 again. In this way, an intensive tempering and in particular a very effective removal of the resulting processing heat is possible.

FIG. 27 shows a variant embodiment in the form of an extruder 101b, but in which, instead of an extruder screw, the shearing tools 3 mounted on one side in a cardan manner are provided on arms. In the center of the arms 18, the form shaft or splined shaft 111 "is inserted in a driving sleeve 43 (FIGS. 28, 31) fixedly connected to the shear arm with a corresponding shape complementary to the external shape of the shaft 111", which expediently passes through an opening 111a "between continues the arms 18. The outer shape of the forming shaft 111 "may be arbitrary per se, as known in the art, for example as a splined shaft.

From Fig. 28 also seen that the arms 18 advantageously have a - in the direction of rotation - forward facing and against the shear tool 3 inclined surface 44, which thus on the one hand forms a streamlined profile in the mass to be processed, on the other hand, this mass against the deflects respective shear tool 3 out.

As can be seen from FIG. 27, the extruder housing 103a has a modular construction, wherein the individual modules are pressed together by clamping screws 37, which at the same time determines and generates the respective predicted force of the loading device (spring 6 in the spring housing 6b). This means that in itself the load is determined by the spring 6 respectively by the geometry or the length of the sleeves 43. Optionally, however, can provide a spreading device for adjusting the spring force between opposing sleeves (see Fig. 28), ie, for example, an eccentric or a cam, a toggle joint or the like. Each module comprises a temperature-controllable shear plate 1b and in between the housing 103a, which, as shown, is also tempered. As can be seen, the arms 18 are mounted axially displaceably on the drive shaft 111 '' with their sleeves 43, so that their free ends 130 abut against each other as shown in Fig. 28. In the uninstalled state, this defines the unloaded distance 131a (see Figs Distance 131 in Fig. 27) of the opposite shear edges 3d from the respective shear plate 1b (see Fig. 27, 28). 1b, 18 are located, advantageously temperable, intermediate plates 38, which force a deflection of the flow from the outside to (radially) inside.

In this way, the mass to be processed passes through the supply line 113 in a to the right (as seen in Fig. 27) sealed in a manner not shown annular space 40 around the shaft 111 "and is then from the radially inner side, if necessary supported 9, directed radially outward, as shown by the arrows in Fig. 27. In part, however, the mass already passes between the arms 18 and reaches a turn radially inward The gap 41 of the intermediate disks 38, from where it passes radially outward via the next shear plate 1b to the passage opening 112 of the next shear plate 1b, repeats itself arbitrarily, possibly conditioning conditioning chambers 42 which can be tempered on all sides a similar to the annulus 40 formed annular space 40a and a discharge line 109a again.

While Fig. 29 illustrates in perspective view that embodiment with a full drive shaft 111 and the arms 18 as used in the embodiment of Figs. 1A, 1B, Fig. 30 shows the hollow drive shaft 111 'which in the embodiment of Figs Figs. 11A and 11B is used.

It can be seen from the above variants that the invention can take on a wide variety of shapes, with only the gimbal bearing of the shearing tools 3 being of importance. These shearing tools 3 are preferably as rectangular as shown in Figs. 21 or 23, but other shapes are possible.

Claims

claims

1. Processing device (101, 101 a, 101 b) for processing dispersions having at least one surface guided against a shear surface of a shear plate (1, 1 a, 1 ') for a sweeping movement and via a drive shaft (111, 111', 111 ") to a rotary movement (16) driven elongate shearing tool (3), characterized in that the respective shearing tool (3) at an angle (eg -α, + α) transversely to the axis (111a) of the drive shaft (111; 111 ', 111 ) that the respective shearing tool (3) has a shearing edge (3 a) extending essentially transversely to the axis (111 a) of the drive shaft (111; 111 '; 111 "), that the respective shearing tool (3 ) is connected to the drive shaft (111) via a universal joint (10a), and that a loading device (6), in particular a spring, is provided, which approximately in the region of the shearing edge (3d) or close to the shearing edge (3d) against the shear plate (1, 1a, 1 ") loaded, while the shearing surface (3c) due to the universal joint (10a) on the one hand and the loading device (6a) on the other hand, forming a pull-in angle (4), obliquely to the shear plate (1; 1a; 1 ').

2. Device according to claim 1, characterized in that at least one of the following features is provided:

a) the shear plate (1, 1a, 1 ') is formed as a substantially flat disc or plate; b) the shearing tool (3) is substantially oblong rectangular, wherein preferably the universal joint (10 a) at a distance from the shearing edge (3d) is arranged; c) at least two shearing tools (3), eg four, are provided, which are preferably arranged at uniform angular intervals around the drive shaft (111, 111 ', 111 "); d) at least two loading devices (6) are each associated with an individual adjusting device (122) for adjusting the force, but preferably also a total adjusting device (17, 140).

3. Apparatus according to claim 1 or 2, characterized in that the shearing tool (3) on the universal joint (10 a) opposite, preferably radially outward end by means of a guide arrangement (119) substantially perpendicular to the direction of rotation or parallel to the axis of Drive shaft is guided, that preferably the guide assembly (119) of a slot on an extending from the drive shaft arm (18) is formed, and that expediently this guide assembly (119) the shearing tool (3), in particular attached thereto, optionally cylindrical , Pin (10), with play in the direction of rotation, for example, by the width of the elongated hole is greater than the diameter of the pin (10).

4. Device according to one of the preceding claims, characterized in that the universal joint (10a, 10a ') satisfies one of the following conditions:

a) it has a longitudinal axis (O) at a distance, in particular at the shear edge (3d) opposite, the width (11) of the shear tool (3) delimiting end of the shearing tool (3), of the shearing edge (3d) relative to the Axial (111a) of the drive shaft (111; 111 ', 111 ") extends approximately radially, preferably the drive shaft (111; 111';111") facing away from the end of the shear tool (3) a movement parallel to the axis (111a) of the drive shaft (111; 111 '; 111 ") allowing guide, preferably with a longitudinal slot (119) passing through journal (10), expediently the bearing in the direction of rotational movement (5) has a game b) it is with respect to the drive shaft ( 111, 111 ', 111 ") are arranged on the radially inner side; c) it comprises a pin (10a) attached to the shearing tool (3) with a diameter decreasing towards the free end.

5. Device according to one of the preceding claims, characterized in that the shear plate (1, 1a, 1 ') satisfies one of the following conditions:

a) it is formed as a substantially planar plate, which, however, is optionally formed in a sawtooth cross-section between the center and periphery; b) it has at least one passage opening (112) for the machined mass, preferably a plurality of such openings (112), which are distributed over at least a portion of the surface, in particular around a peripheral region thereof.

6. Device according to one of the preceding claims, characterized in that the respective shearing tool (3) by a longitudinally cross-arm (18) is supported - preferably by means of two opposing bearing or guide assemblies (10, 10 a), of one, in particular that of the drive shaft (111; 111 ', 111 ") closer, is formed by the universal joint (10a), and that the arm (18) preferably one - in the direction of rotation - forward facing and against the shearing tool ( 3) has an inclined surface.

7. Device according to one of the preceding claims, characterized in that the respective shearing edge (3d) to the of the axis (111a) of the drive shaft (111; 111 '; 111 ") outgoing radius at a deviating angle of 90 ° (-α , + α), in particular under one of the rotational direction (16) opposite, radially outwardly directed backwards and thus unfolding a pumping action angle (-α) and / or seen to a direction of rotation (16), radially outwardly to the front and so the centrifugal force counteracting angle (+ α).

8. Device according to one of the preceding claims, characterized in that the shear plate (1; 1a; 1 ") at least rotationally fixed, preferably substantially stationary, in a, for example, tube-like, container (101; 101a; 101 b) installed or in this by means of a lifting device (127) is einenkbar, and in that at least one tempering channel (25, 120) is preferably provided in the shear plate (1; 1a; 1 ').

9. Device according to one of the preceding claims, characterized in that at least two shear plates (1b) are arranged stationarily in a tubular housing (103a), wherein the associated cutting tools (3) facing away from a driving forming shaft (111 ") slidably but rotationally fixed , are preferably arranged by means of sleeves (43) fixedly connected to them, and that optionally the pressure of the loading device (6) is determined by the dimensions of mutually tensionable sections of the housing (103a).

10. Use of a device with at least one shearing tool (3) which is connected to the drive shaft (111) via a universal joint (10 a), according to one of the preceding claims for the processing of a dispersion, in particular a cocoa-containing mass.