DD147567A5 - ROTARY MACHINING MACHINE, ESPECIALLY FOR MACHINING VISCOSER PLASTIC OR POLYMERMATERIALS - Google Patents

Abstract

The invention relates to a rotary processing machine, in particular for processing viscous or koerniger plastic or polymer materials. By the invention is to be achieved, that regardless of the pressure occurring in the processing channels of the rotor deflection of the rotor or the drive shaft is avoided, at the same time escape or Ausflieszen the materials to be processed at high or low pressures between the coaxial Umfangsflaechen both between adjacent as well as frontally located processing channels is to be prevented. Therefore, according to the present invention, a dynamic seal has a plurality of channels arranged so that liquid material is penetratable into the sealing channel, the width I of the circumferential surface carrying the sealing channels, the number, angle and geometry of the sealing channel being chosen. That is, the outward penetration of the pressurized fluid into the gap and into the sealing channel is directed counter to the inward force exerted on the liquid in the sealing channels.

Description

Berlin / 9. 5. 1980 ί 7 24 4 "* ~ AP F 16 ϋ / 217 244

GZ 56 617 27

Rotary processing machine, in particular for processing viscous plastic or polymeric materials

The invention relates to a rotary processing machine, in particular for processing viscous plastic or polymeric materials or granular plastic or polymeric materials, having a rotor with a circumferential surface carrying at least one processing channel and a stationary housing having a circumferential surface complementary to the circumferential surface of the rotor is separated from the peripheral surface of the rotor by a narrow gap and is operatively connected to the processing channel to form an enclosed annular processing passage with the processing channel, wherein the stationary housing also has an inlet port for feeding the material to the processing passage, an outlet opening of the inlet opening is provided at a distance, taking into account a larger part of the circumference of the processing channel, to discharge material from the processing passage, and associated with a component which in the processing channel is arranged and a surface forming the liquid material collects or * gathers ₅ to inhibit this or to limit, and means for rotating the rotor is provided in a direction that leads from the inlet opening to the material limiting surface so that the rotor and the surface of the component which restricts the material which has been entrained cooperate, and a pressure is built up along the length of the path of the processing channel in the direction of the material restricting surface,

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- 2 «·

Known rotary processing machines for processing viscous plastic or polymeric materials include a rotor having at least one annular processing channel and a stationary component having a coaxial circumferential surface which cooperates with the processing channel to form an enclosed processing passage. The stationary member has an inlet port for supplying material to the processing passage and an outlet port provided at a distance from the inlet port taking into account a greater part of the circumference of the processing passage to discharge processed material from the processing passage another member is disposed on the stationary member to form a surface of an end wall which collects liquid material. This member is disposed in the machining passage in the vicinity of the outlet port to inhibit movement of the material fed into the machining passage and to cooperate with the rotating sidewalls of the processing channels to effect relative movement between the material and the inner surfaces of the sidewalls of the processing channels that are rotated toward the outer aperture ". This cha a characteristic co-operation allows only liquid material to come into contact with the inner surfaces of the rotating processing channel to be pulled forward to the surface of the liquid material collecting end wall to be selectively processed and / or unloaded

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become.

The essential components of the rotary processing machine are arranged so that the rotor carrying the rotary machining channel, can be rotated in a stationary housing or a stationary chamber "The processing channel and described, preferably a plurality of processing channels are respectively" in the cylindrical circumferential surface of a rotor The stationary housing or chamber has an inner cylindrical peripheral surface which has a co-operating coaxial circumferential surface which, together with the annular member (s), is formed with each of the processing channels having opposite side walls extending inwardly from the peripheral surface of the rotor Machining channels forms one or more enclosed machining passages.

These arrangements are useful to convey solid bodies, to melt or plasticize plastic or polymeric materials, to convey, pump or pressurize viscous liquid material to mix, mix, disperse, or disperse material distribute and homogenize, and to volatilize and / or about molecular or microscopic or macroscopic structure changes by chemical _reactions} ^ such as polymerization to cause "

Due to the versatility and affordability of the basic individual processing operation, a variety of them are generally employed to generally form rotary processing machines having one or more processing passes involving various operations

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 - 4 -

or perform functions. For example, a single processing channel or multiple individual processing channels may receive and transport material from one processing pass to another. It may also be a single processing channel or multiple individual processing channels may melt, mix or volatilize polymer or plastomer material or materials, or discharge polymer or plastomer material or materials. The particular function assigned to a single machining pass essentially determines the printing characteristics of the machining pass. For example, some assigned functions, such as melting or discharging, can result in the generation of very large pressures. Other functions, such as volatilization, may involve the generation of low pressures, while mixing processes are associated with mediocre pressures. Also, the pressure distribution along the circumference of each machining passage may change depending on the function assigned to the machining passage or the operation assigned to the machining passage . For some functions, the pressure may increase linearly along the entire circumference or only along part of the circumference. Some functions may provide pressure characteristics that include one or more pressure increases followed by one or more sharp debris along the circumference. In addition, often basic individual processing passes having particular pressure characteristics, such as high pressure, are arranged or provided adjacent or between units having completely different pressure characteristics, such as low pressure.

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7244-5-

In most instances, it is desirable to effect an effective seal for one or all of the individual machining passes a rotary processing machine with several machining passages to prevent unwanted escape of material from entering from at least one of the machining passes "In this unwanted escape or _e outflow For example, it may be an external outflow of one or both finishing passes of a multi-pass rotary processing machine. But it can also be an undesirable leakage internally occur between adjacent individual processing passages "In all examples, a leakage primarily occurs at a gap which is necessary between the peripheral surface of the rotary cylindrical side walls of the processing channels and the stationary inner coaxial annular peripheral surface, in particular on the parts of the machining passage where high pressures have been generated

For example, the problems associated with external and internal outflow are particularly complicated in multi-unit rotary processing machines, due to the radial differential pressures usually generated along the circumference (s). For example, the pressure at the entrance of the passage is generally small while the pressure at the part forming the surface of the material collecting end wall can be extremely high. In fact, the different radial pressures may be large enough to cause a deflection of the rotor or the drive shaft, whereby an undesired restriction of the available tolerances for the required distance between the peripheral surface of the or "the rotatable cylindrical channel walls, and

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the stationary, inner coaxial, annular periphery is effected flat.

Ziel'der invention is independent of whether an extreme pressure occurs in an odor more of the internal processing channels and / or one or both outer processing channels of the rotor to avoid bending of the rotor and aer drive shaft, can be reached at the same time that Escape or flow out of the materials to be processed at high or low pressures between the substantially coaxial circumferential surfaces both between adjacent processing channels as well as from the frontally located processing channels to the outside avoided or prevented.

The invention has for its object to provide a rotary processing machine, in particular for the processing of viscous plastic or polymer materials, in which by arranging and forming a seal, the machining channels having the rotor or the housing is to be assigned, the outflow of material between them relative to prevent each other moving complementary arranged to form a gap surfaces is prevented.

According to the invention this is achieved in that a dynamic seal for preventing the leakage of pressurized material at the gap a plurality of sealing channels on the cylindrical inner Umfanasflache or

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on the outer circumferential surface, which are arranged such that liquid material is penetrated into the sealing channels, wherein the width of the cylindrical inner circumferential surface or the outer circumferential surface carrying the sealing channels, the number, the angle and the geometry of the sealing channels is selected in that the outward penetration of the pressurized liquid into the gap and into the sealing channels is in the opposite direction to the inward force exerted on the liquid in the sealing channels when the cylindrical inner peripheral surface and the outer peripheral surface are moved relative to each other Resist the extent of penetration of the pressurized liquid in each of the sealing channels resistance.

Here, the liquid-containing part of the rotor a zone of minimum pressure to _0. Conveniently, further comprising a scraper is provided which projects into the gap to or liquid of which the sealing channels carrying outer circumferential surface to eliminate the cylindrical inner circumferential surface, so that the Liquid contact is interrupted at least during part of the rotation of the rotor. The part of the rotor which contains a liquid advantageously has a region of a first pressure, while a region with a greater pressure is provided circumferentially at a distance.

The length of the sealing channels is selected in a further embodiment so that during operation of the rotary processing machine, the extent of penetration of the liquid does not exceed the length of each sealing channel The arrangement of the sealing channels is preferably helical, but they can also be arranged so that they ver at least obliquely -

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"The pitch angle of each sealing channel should be 20 or less, but it could also be 15 or less, and is particularly favorable on this scale.

The sealing channels can be arranged according to a further feature of the invention so that either the plurality of sealing channels supporting cylindrical inner peripheral surface stationary or the plurality of sealing channels bearing outer peripheral surface is rotatable. The aer provided between the cylindrical inner peripheral surface and the outer circumferential surface of the gap should be 2.5 mn or less, but it may also be expedient if, this is 1.25 mm or less, so that the effectiveness of the gap is increased by " Regardless of whether the sealing channels are helical or inclined, they must always be arranged so that they run parallel to each other «

An improved seal in conjunction with the adjacent circumferential surface, especially with larger deflections of the drive shaft, ie larger gap, is achieved when the dynamic seal contains a truncated conical component made of a stiffly resilient material, the truncated conical component near the outer free edges has a surface closest to the processing channel to be displaceable by the pressure, means is provided for holding the inner edges of the truncated conical member against pressure displacement such that the outer free edges engage the cylindrical inner peripheral surface of the Housing form a seal, and the sealing channels formed either in the cylindrical inner Umfangsf.lache or in the outer free edges

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While in the rotary processing machine according to the invention is substantially the outer peripheral surface of the rotor of the peripheral surface areas, the cylindrical inner peripheral surface of the housing is formed with respect to the dynamic seal only by a part of the cylindrical inner peripheral surface of the housing.

But it can also be made an arrangement of the dynamic seal, wherein the rotor has an outer surface in the region of the dynamic seal, which is annular and formed in the. Region of the outer peripheral surface is respectively disposed on the end side of the rotor and in which this outer surface facing a stationary annular member having a stationary surface and is fixedly disposed on the stationary cylindrical inner Umfangsflächc of the housing.

Regardless of the design of the dynamic seal, the sealing channels may be disposed on each side of the processing channel. In principle, however, the rotor has a plurality of processing channels, each processing channel having a dynamic seal of the most varied embodiment assigned to it »

In order to further deflect away from the cylindrical inner peripheral surface or, the outer peripheral surface liquid, finally, in a further embodiment of the invention, the scraper on a surface facing the flow, which extends over the cylindrical inner peripheral surface or * the outer circumferential surface and a - Angle to the direction of movement of the cylindrical inner peripheral surface or »the outer peripheral surface is inclined relative to the scraper«

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- 10 -

In this rotation machining machine according to the invention may well be connected to the outlet of a processing channel with the inlet of a further processing channel the outlet.

AusführunqebeisDiel

The invention will be explained in more detail below with reference to several embodiments. In the accompanying drawings:

It is a side view of the rotary processing machine in which parts have been omitted to visualize a rotor, processing channels, and an annular coaxial circumferential surface;

Fig. 2; a section of Figure 1 on an enlarged scale.

Fig. 3 is a schematic view showing further relationships between the circumferential surfaces forming the dynamic seal;

Fig. 4 is a schematic representation of the cylindrical inner peripheral surface of one of the peripheral surfaces shown in Figs. 2 and 3 in a plane having a plurality of helical sealing channels;

Fig. 5: the graphical representation of the along the

Scope of a typical machining pass of a rotary machining

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- 11 -

ren sealing channels according to the Figure 1 developed pressure profile;

FIG. 6: a graphic representation of the penetration length of liquid calculated in the pressure profile of FIG. 5 into the helical sealing channels; FIG.

7 is a partially sectional side view of an end wall of a processing passage of a multi-pass-through rotary processing machine showing the relationship between a stationary scraper and a rotating cylindrical inner peripheral surface having a plurality of helical seal passages.

Fig. 7a is a plan view of the end wall and the scraper of Fig. 7;

Fig, 7b is a section 7B-7B through the end wall and the scraper of FIG _e 7a;

FIG _e 8 is a partially sectioned side view of the inner side walls of adjacent sealing channels of a · rotary processing machine with several machining passages, showing the relationship between a stationary scraper and a rotating cylindrical inner peripheral surface having a-plurality of helical sealing channels;

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* 12 -

Fig. 5 is a plan view of the side wall and scraper of Fig. 8;

Fig. 8b shows a section 8b-8b of the side wall and the scraper of Fig. 8a;

Fig. 9; a graphic representation of the along the

Circumference of a typical machining channel of a rotary machining machine having a plurality of machining passages according to the developed pressure profile;

Fig. 10t is a graphical representation of the liquid penetration length into the helical sealing channels calculated for the pressure profile of Fig. 9 and the effect of the periodic scraping of liquid from the peripheral surfaces to the penetration length of the liquid in a dynamic seal according to the invention;

11 shows a section of a processing channel in connection with a further embodiment of the dynamic seal;

Fig. 11a is a side view of one of the dynamic ones

Sealing the surfaces forming in the embodiment shown in FIG.

Fig. 11 is a partially sectioned plan view of the dynamic seal of Fig. 11 showing the relationship of a stationary scraper and a rotating surface having a plurality of

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7244

shows helical sealing channels;

Fig. 12: a view similar to Fig. 11, showing a

shows another embodiment of the dynamic seal;

Fig. 12a: a side view of one of the dynamic

Sealing the surfaces forming in the further embodiment shown in Figure 12;

Fig. 12b is a partially sectioned plan view of the dynamic seal of Fig. 12 showing the relationship of a scraper to a stationary surface having a plurality of helical sealing channels;

Fig. ₀ 13: shows the part of a section of a further embodiment of the dynamic seal on an enlarged scale;

Fig. 14

and Fig. 14a: similar to Figs. 3 and 4, another embodiment of the dynamic seal;

Fig. 15.

and Fig. 15as similar to Figs. 3 and 4 a possibility

another form of training the dynamic

Poetry;

Fig. 16

and Figure 17 is a partial section of further embodiments of the dynamic seal on an enlarged scale;

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- 14 -

Fig. 18, 19

and 20: graphs showing the penetration of the liquid into a plurality of helical sealing channels depending on various conditions such as the number and angle of the helical sealing channels and the Drehgeschvvindigkeit which the sealing channels supporting surface respectively, the circumferential surface _s

The invention will be described in relation to its use in a rotary processing machine having multiple feed passages. It will be appreciated, however, that the described dynamic seals are useful in connection with other applications in which a seal is required between rotating circumferential surfaces.

The rotary processing machine shown in Fig. 1 comprises a rotatable member having a rotor 10 rotatably disposed in a housing 12 provided with a cylindrical inner peripheral surface. The rotor 10 is supported by the drive shaft 16 which is supported in end walls 18 of the housing 12. The rotor 10 has a plurality of processing channels 20, each of which is bounded by opposite side walls 24 in fixed relation to one another stand. In addition, the rotor 10 outer peripheral fish 26 which is coaxial with oer stationary cylindrical inner peripheral surface 14 of the housing 12 at each side of each processing channel 20 and to the cylindrical inner peripheral surface 14 are spaced slightly * Oeder processing channel 20, which is rotatable, and the stationary cylindrical inner surface 14 of the housing 12 form a basic working

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7244

- 15 -

tion passage, is introduced into the material for processing through an inlet port 28. The movement of the processing channel 20 pulls material in contact with the sidewalls 24 to a portion forming an end wall surface, not shown, for collecting material. Collected machined material is discharged through the outlet port 29 in the housing 12. "As the material on the sidewalls 24 draws toward the material collecting surface of the end wall 18, a pressure is created such that the processing passage 20 becomes a high pressure area which increases in the direction of rotation «.

As shown in FIG. 1, there is a narrow gap 50 between the outer peripheral surface 26 and the stationary cylindrical inner peripheral surface 14 of the housing 12. In the ideal case, the gap 50 is about 2.5 mm or less, where preferably in a range of 0.75 to 1.5 mm. In general, the gap 50 should be substantially constant around the outer circumference of the rotor 10. The maintenance of such a narrow and constant gap 50, however, may be hampered by the radial differential pressures generated along the circumference of the processing channel 20. This imbalance in radial pressures may be sufficient to cause deflection of the drive shaft 16 or rotor 10 from a region of high pressure toward a region of low pressure. It will be understood that any deflection will affect the maintenance of the desired tight and constant gap 50, because additional clearance must be created to compensate for the amount of any deflection "

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The flow of the material to be processed controlling units may radially be arranged opposite, so that the radial pressures that are generated in part of a machining pass or with a group of passages are _s balanced by heat generated in another part of radial pressures "While the control of the deflection of a drive shaft a leak or "can reduce losses due to leakage", it is often desirable to provide an auxiliary seal, or an additional seal, a leakage to the greatest possible extent to verraindern _e the present invention relates to a new dynamic seal to control the leakage between them ara or in the vicinity of the gap 50 relative to each other moving peripheral surfaces,

An embodiment of a dynamic seal according to the present invention is shown in Figs. 3 and 4, in which a plurality of helical sealing channels 27 are formed on the outer peripheral surface 26 of the rotor 10 between the side walls 24 of the processing channels 20 and / or supported by the outer peripheral surface 26 to provide a dynamic seal between = see the outer peripheral surface 26 and the stationary cylindrical inner peripheral surface 14 of the housing 12 to form «the 'oblique or helical Dichtksnäle 21 are closely spaced and parallel. As shown _ff , the oblique or helical sealing channels 27 are preferably cut on the outer peripheral surface 26 and move relative to the smooth cylindrical inner peripheral surface 14 of the housing 12 * The most significant relationships between the various design or design parameters of the dyna according to the invention

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* - 17 -

mix seal are shown in Figures 3 and 4, _e and it is noted in the following description and the following explanation of the dynamic seal of the invention to these figures ·

As already mentioned, the dynamic seal described above is substantially achieved in that one of two circumferentially moving relative to each other with a gap 50, namely a cylindrical inner peripheral surface 14 and an outer peripheral surface 26, a plurality of oblique or _e helical sealing channels having 27 * In fact, works each oblique or _c helical sealing channel 27 as a segment of a conveyor screw of an extruder, wherein the stationary cylindrical inner peripheral surface 14 respectively for the plurality of oblique _ß helical sealing channels 27 (or the plurality of segments of the conveyor screw of the extruder) than tube Accordingly, the net flow q of a liquid across the width 1 of the outer peripheral surface 26 can be determined by the same analysis applied to a screw conveyor. The net flow q therefore corresponds to the difference between the dragline q _Q in one direction and the pressure flow q in the opposite direction or

q = q _D - q _p "(Equation A)

in which? q_. the theoretical entrainment and q the theoretical pressure flow

mean,.

For purposes of illustration, the dynamic seal is the

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££ $ 4 - 18 .-

FIG * 2 to 4 graphically in Fig _fl 4 relative to a constant pressure shown and eggs total net flow q sq under equilibrium conditions zero or _D = q "The Mitschleppfluß q _D is merely a function of the geometry of the oblique or _e helical sealing channel 27 and the Operating speed * For a given pressure, the pressure flow q is inversely proportional to the length of penetration of the liquid into the oblique or helical sealing channel 27, d _e h _o to the length of the oblique or helical sealing channel 27 filled with liquid Therefore, equilibrium is achieved as shown in FIGS. 3 and 4 as soon as the liquid has penetrated the oblique or helical sealing channels 27 to a length which attempts to move the pressure flow ( attempting to move the liquid into the oblique or helical sealing channel 27) ) is reduced to a value equal to the q Mitschleppfluß is "When measured in the axial direction length of the penetration is less than the length of the inclined or" helical sealing channel 27, no liquid over the width 1 of the or the oblique "helical sealing channels will expire 27 carrying outer circumferential surface 26 '

However, the dynamic seal according to the invention does not work under the conditions of constant pressure, as explained in connection with aer Figure "4 * instead shows the FIG _s 5 shows a typical pressure profile developed along the circumference of a Bearbeitungedurchgangs a Rotationsbearbeitungssnaschin ©" After During a period of relatively low pressure, the pressure in the processing passage gradually increases, reaches a maximum throw at the end of the processing pass, and then suddenly falls behind an obstruction, such as a channel block.

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to the original low level zurücke The dynamic seal of the present invention thus operates normally to a variable pressure, which periodically during each rotation of the side walls 24 der.Bearbeitungskanäle 20 repeats "The length of penetration of the liquid in the oblique or" helical sealing channels 27 was calculated for the * 5 shown in Fig pressure profile by a suitable dynamic model and is compared with the pressure profile plotted in FIG _e 6 * It can be seen that as soon as the pressure drops suddenly "or the length of penetration of the liquid in a slanting "helical sealing channel 27 is gradually reduced to a point, opposite to about the point at which the pressure increases again from there to the penetration of the liquid rises in a sloping or _e helical sealing channel 27 again to" It can be said in general, that the net flow ß (Equation A) never reached equilibrium during any revolution due to the time required for emptying the fluid from an oblique or helical sealing channel 27 when the pressure is at its lowest or the time required to reach the oblique or to fill the helical sealing channel 27 again with liquid, when the pressure is greatest, approaches the length of penetration of the liquid in a slanting or * helical sealing channel 27 the pressure profile before or nache After displayed dor FIG _o 5 sudden pressure drop occurs, for «B _e only a gradual reduction in the length of liquid penetration into an oblique or "helical sealing channel 27" However, by making the length of each oblique or helical sealing channel 27 long enough so that the length of penetration of the liquid never the length the one or the oblique or «

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- 20 -

exceeds screw-shaped sealing channels 27, is achieved that an undesirable leakage over the width of one of a plurality of oblique or helical sealing channels 27 bearing outer peripheral surface 26 can not occur «

The preferred dynamic seals of the present invention have multiple threads and have oblique helical sealing channels 27 with a relatively small helix angle Q _0. The small helix angle θ is desirable to provide helical sealing channels 27, the minimum penetration lengths for the one helical sealing channel 27 carrying outer peripheral surface 26 having a relatively small width 1 "The pitch angle Θ, which are below about 20 °, are particularly suitable for dynamic seals according to the invention.

The number of helical sealing channels 27 used to make the dynamic seal of the present invention is a very significant one. Because the side walls 24 of the processing channels 20 have a relatively large outer diameter, one is a plurality of oblique or helical sealing channels 27 carrying outer peripheral surface 26 particularly desirable _s because the pitch or, "pitch L of the oblique sealing channel 27 is greater than the width of the outer peripheral surface 26 _{e e} Accordingly, a plurality of oblique or 'helical sealing channels 27 is formed to an effective dynamic seal There is another reason that speaks for the use of a plurality of oblique or helical sealing channels 27. For a net flow q equal to zero, the pressure flow must q and q Mitschleppfluß _D

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-21 -

be the same size "However, if the ratio of the depth H of the inclined or" helical sealing channel 27 (Fig * 3) to the width W of the oblique or "helical sealing channel 27 (FIG _e 4) rises, d * h", if the width V / of the inclined or helical sealing channel 27 decreases, the value of the pressure flow takes q in the equation A faster, than the value of Mitschleppflusses q in the equation A faster, than the value of Mitschleppflusses q _Q * is from the above equation A it can be seen that under these circumstances, namely for the decrease in the width W of the sealing channel 27, the seal becomes more efficient, which means that a net flow q of zero is achieved with smaller or smaller penetration lengths of liquid in the oblique or helical sealing channel 27 It can also be seen from the equation for the width VV of the oblique or helical sealing channel 27 (FIG. 4) that an increasing number of de r oblique or helical sealing channels 27 to a reduction of the width W of the oblique or _e helical sealing channels 27 led Narrower widths VV the oblique or "helical sealing channels 27 are particularly desirable because of the radial differential pressures in the practice of the present invention around the periphery to meet the processing passage around are "by using a plurality of oblique or" helical sealing channels 27 with a narrow width W of the oblique or "helical sealing channels 27, the pressure changes or to each oblique will act" helical sealing channel 27 at any one time, on held a small value and each oblique or "parallel sealing channel 27 acts independently"

The Eindringgrenze the liquid shown in FIG _e 6

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- 22 -

speed represents the Boreich over which the oblique or helical sealing channels 27 are filled during a complete revolution of the oblique or "helical sealing channels 27 outer circumferential surface 26. This area also corresponds to the area of the stationary cylindrical inner peripheral surface 14, which with liquid in communication _e This fluid contact with the oblique or "helical sealing channel 27 carrying outer peripheral surface 26 and with the cylindrical inner peripheral surface 14 generates a shear which produces the desirable Mitschleppfluß q _Q, the very recite the extent of penetration of the liquid into the or However, shear also creates an undesirable power loss of the dynamic seal because energy is converted to heat or is consumed as heat.

According to a particularly preferred embodiment of the present invention, energy loss of the dynamic seals can be thereby significantly reduced that the fluid contact between the dynamic seal is interrupted during a part of each revolution of one of the surfaces of the dynamic seal producing * This embodiment is illustrated in Figures " , 7; 7a; 7b ι 8j 8a ί 8b j 9 and 10 shown, as in Figures 7; 7a; 7b, a scraper 30 is disposed on the inlet side of a channel block 19 (FIG. 7a) to remove liquid from the outer peripheral surface 26 carrying the oblique sealing channel 27, which is a dynamic seal thus designed is that an external outflow from the finishing pass is a rotation processing »

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- 23 -

Machine is avoided · The game between the scraper 30 and the outer. Preferably, this clearance should be small enough to allow most of the outer peripheral surface 26 supporting the oblique or helical sealing channel 27 and the stationary, cylindrical, inner circumferential surface 14 Accordingly, after scraping, the liquid contact between the outer peripheral surface 26 supporting the oblique screw-shaped sealing channels 27 and the cylindrical inner peripheral surface 14 is interrupted, and the oblique or screw-shaped sealing channels 27 remain liquid with liquid filled extent that they were filled in front of the scraping * power losses resulting from energy consumption in the dynamic seal are therefore reduced after scraping and does not rise again until sufficient fluid in the pumped or _e oblique or helical sealing channels 27 is to restore the fluid contact between the cylindrical inner peripheral surface 14 and the outer peripheral surface 26 of the dynamic seal «. From the oblique or "helical sealing channels 27 carrying outer peripheral surface 26 scraped liquid material is discharged at low pressure into the inlet *

FIGS. 8a and 8b show a scraper 31 which cooperates with another form of dynamic seal according to the invention, which is created between the cylindrical inner peripheral surface 14 defining the gap 50 and the cylindrical outer peripheral surface 26. As shown, two sets of intersecting oblique

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benförmigen sealing channels 27 and 27a disposed on the outer peripheral surface 25 between the side walls 24 of adjacent machining passages, wherein the slopes of the oblique or helical sealing channels 27 of each set are opposite * The scraper 31 is disposed on the inlet side of the channel block 19 (Fig * 8a) and is maintained in a close scraping relationship with the outer circumferential surface 26 supporting the oblique sealing channels 27 to interrupt fluid contact between the dynamic seal producing cylindrical inner peripheral surface 14 and outer peripheral surface 26 and the scraped liquid material into the inlet to unload «

The advantages of breaking of liquid contact between the cylindrical inner peripheral surface 14 and Oer outer peripheral surface 26 of the dynamic seals of the invention also shown in Figs _e 9 and 10, "FIG * 9 (as Figs * 5} shows a typical pressure profile The calculated length of penetration of the liquid in the oblique or helical sealing channels 27 for the pressure profile of FIG. 9, but which has a scraper 301, which coincides with that of the oblique or helical sealing channels 27 bearing outer circumferential surface 26 cooperates, as previously described and shown, as illustrated in FIG "IO is shown there, the scraping is at the inlet or at or near the low-pressure region of the processing passage made eliminating, so scraping, interrupts the Fl fluid contact between the cylindrical inner peripheral surface 14 and the outer peripheral

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£ I / £ 4 4 - 25 -.

However, because the layer that creates fluid contact between the cylindrical inner peripheral surface 14 and the outer unifangle surface 26 of the dynamic seal removes the oblique or helical sealing channels 27 filled with liquid to a level However, if there is a decrease in power loss and a very small liquid penetration into the area extending from the back of scraper 30 or 31 to about point 13 on the graph of Fig. 10, however, once the pressure increases The length of the liquid penetration immediately and very closely follows the pressure profile, with maximum penetration appearing fairly close to the pressure maximum. "A comparison of Figs. 10 with Fig. 5 shows that the range of maximum liquid penetration of Fig. 10 is considerably smaller is the maximum liquid intrinsic area of the F ig ", 5 _β A scraper 30; 31 therefore produces reduced power losses without degrading the efficiency of the dynamic seal «

In the previously described embodiments of the invention, the dynamic seals between the cylindrical inner peripheral surface 14 and the outer circumferential surface 26 are erected _s or "generated that determine the gap 50 (FIG _e 2 and 3)" The present invention, however, relates to dynamic seals between other surfaces, which lie in the vicinity of the gap 50 "Figs _e Hi 11a; lib j 12; 12a; 12b show such further embodiments of the invention. FIG. 11 shows a dynamic seal in which a part of the outer surface 32 of the rotor 10 is provided with a multiplicity of sealing channels 35 * extending along the outer surface.

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4 4 - 26 ~

ren surface 32 extend obliquely extend * "The part of the outer surface 32 which supports the plurality of sealing channels 35, has a width 1 (Fig * 11 and Ha) in" The outer surface 32 which carries the seal channels 35, moves during the rotation relative to the stationary surface 33 which is of the sealing channels 35 carrying outer surface 32 separated by a narrow gap 51, which may be the same as the gap 50 and may be larger or smaller than the gap 50, in general, however, is about 2.5 mm or less. "The stationary surface 33 is formed by a stationary annular member 34 fixedly attached to the stationary cylindrical inner peripheral surface 14 of the housing 12. FIG. 11 shows a view the outer surface 32 of the rotor 10, which has a plurality of sealing channels 35 in the width 1, which are arranged spirally and around the outer peripheral portions of the outer surface 32 extend. While the sealing channels 35 are shown in a curved spiral shape in FIG. 1 a, they may also be arranged straight and oblique without leaving the frame of the present invention. FIG _e 11b shows a view As shown the relationship between the outer surface 32 and stationary surface 33 forming the dynamic seal of Fig * 11 and a scraper 36 show ", the scraper 36 is fixed in the stationary ring - Shaped member 34 and extends from the stationary surface 33 outwardly to interrupt the liquid contact between the outer surface 32 and the stationary surface 33. The scraper 36 extends at least across the width 1 and is at the inlet or in near the inlet (not shown) of the machining

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217 24 4 - 27 -

arranged through the passage of passage *

The figure * 12; 12a and 12b show another alternative form in which the dynamic seal between the surfaces in the vicinity of the gap 50 is realized. In the illustrated embodiment, a plurality of helical sealing channels 37 are provided on a stationary surface 38 of a stationary annular member 39 which is secured to the cylindrical inner circumferential surface 14 of the housing 12. The width 1 of the helical or oblique sealing channels FIG. 12a shows a schematic side view of the stationary annular member 39 having a plurality of sealing channels 37 which are within the width 1 of the stationary surface 38 are provided. Rig ₆ 12b illustrates a view showing the relationship between the surfaces forming the dynamic seal of FIG. 12, namely the stationary surface 38 and the external surface, and a scraper 41. The scraper 41 is fixed in the stationary annular member 39 arranged and is held by this ^ It extends from the stationary surface 38 outwardly to interrupt a fluid communication between the stationary surface 38 and the external surface 40 "As shown in Figure" 12, the scraper extending 41 at least across the width of 1 and, as in the cases of all previously described scraper 30; 31 is the case, at the inlet (not shown) or in the vicinity of the inlet or in a low pressure region of the processing passage arranged

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Mä - 28 -

The dynamic seal, in Figs _e 12; 12a and 12b, somewhat different from the dynamic seals described above, in which the plurality of oblique or "helical sealing channels 27 bzw.," the sealing channels 35, which are also arranged helically, in the rotor 10 is included, because in the dynamic Referring now to Fig. 12, 12a and 12b, when the plurality of helical sealing channels 37 formed in a stationary surface 38 have already been discussed, the penetration length of a liquid in each of the sloped ones carried by a rotating cylindrical outer peripheral surface 26 changes or "helical sealing channel 27 progressively during each revolution, due to the differential pressures encountered along the circumference of the machining passage" This is shown graphically in Figures 5; 6; 9 and 10 * This change in length of the penetration of the liquid in each oblique or _o helical sealing channel 27 or "sealing channel 35 does not occur in dynamic seals with a oblique or helical sealing channels 37 bearing stationary surface 38, during each revolution. Instead, at each helical sealing channel 37, the same peak pressure is always present during each revolution of the side walls 24 of the rotor because each helical sealing channel 37 is always at a fixed position around the circumference of the processing channel 20 penetration of the liquid in each stationary oblique or * helical sealing channel 37- differ, the maximum length of entering any given oblique or * helical sealing channel 37 will always be substantially constant as long as a constant pressure on these inclined or "helical sealing channel 37 currencies -

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- 29 -

However, as long as the penetration length of the liquid into any helical channel 37 on the stationary surface 38 does not exceed the length of any oblique or helical sealing channel 37, undesirable leakage between the surfaces will not occur.

FIG. 13 shows a further embodiment of a dynamic seal according to the invention, which is likewise formed between peripheral surfaces defining a gap 50, but which functions in the same way as that described in connection with FIGS. 12a and 12b described dynamic seal »As shown in the Fig ₀ 13, the helical sealing channels 42 are arranged in the stationary, cylindrical, inner peripheral surface 14 of the housing 12, which is coaxial with the outer peripheral surface 26 of the rotor 10 and is separated from it by the gap 50. Accordingly, the penetration of the liquid into each helical sealing channel 42 which is supported by the stationary cylindrical inner peripheral surface 14 will change "" But, as with the dynamic seal of Fig * 12; 12a and 12b, the maximum penetration length of liquid into any given helical sealing channel 42 at a location of a fixed pressure along the rotating processing passage 20 will be substantially constant as long as a constant pressure is applied at that fixed location as the permeation length of the liquid in any stationary helical sealing channel 42 does not exceed the length of the processing channel 20, there is no leakage of liquid along the dynamic seal existing between the circumferential surfaces at the gap 50.

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In the previous description of the invention, the escape of the liquid at the gap 50, which is defined by the two coaxial peripheral surfaces or "surfaces, respectively, becomes. 51 by a plurality of oblique or * helical sealing channels 271 35; 37, which are supported by one of the primary surfaces or "surfaces" or are arranged on one of these circumferential surfaces or "surfaces. Such features of the oblique or helical sealing channels 27; 35; 37, as the number, the geometry, dimensions and the angle are selected so that the length _s of penetration of the liquid in each oblique or "helical sealing channel 27; 35; 37 not the length of the oblique or _e helical sealing channel 27; 35; 37, in which the liquid penetrates _e exceeds The main function of the dynamic seals, however, is the expansion or "the size of the penetration of the liquid in the oblique or _e helical sealing channel 27 according to the present invention; 35; 37 to resist, thereby reducing the amount of the gap 50; A degree of this control can still be effected even if the length of the penetration of the loss fluid into an oblique or helical channel 27; 35; 37 the length of the penetrated oblique or helical sealing channel 27; 351 37 passes «. Under such circumstances, leakage of the liquid occurs at the gap 50; 51, the oblique or helical sealing channels 271 35; But 37 enable control of the amount of leakage and this amount may be less than the amount without the oblique or "helical sealing channels 27; 35; 37 would result ·

The Fig * 14; 14s, 15 and 15a show embodiments of the invention

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- 31 -

present invention in which an effective control of the escape of liquid to the gap 50 can be effected even if the penetration of the escaping fluid exceeds the length of the inclined or _e helical sealing channel 27 ,, The embodiment 14 and 14a shown in FIGS * includes a plurality of helical sealing channels 27 disposed on the outer peripheral flange 26 of the side walls 24. As shown, the width 1 of the outer peripheral surface 26 supporting the oblique sealing channels 27 does not extend over the entire width of the outer circumferential surface 26 and the penetration of liquid into the oblique or "helical sealing channels may exceed the length of the oblique or helical sealing channels 27. However, a penetration liquid collecting channel 57 is provided around which the oblique or helical to collect the liquid collected and retained until it can be discharged through the oblique or screw-shaped sealing channels 27 at the low pressure area of the processing passage. The channel 57 collecting the penetration liquid preferably has approximately the same depth H. FIG. A) on how the or the oblique or helical sealing channels 27 »

FIG _c 15 and 15a show a modified embodiment in Figures, the embodiment shown 14 and 14, "the width 1 of the inclined or" helical sealing channels 27 carrying outer circumferential surface 26 is again a part of the entire width of the outer peripheral surface Unlike the dynamic seal of FIG. 15 are each

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- 32 -

but a recessed portion 59, the width 1 of the inclined or "helical sealing channels carrying outer peripheral surface and the Eindringflüssigkeit collecting channel 57 along the entire width of the outer peripheral surface 26 arranged in the region of the side wall 24« The depth H of the Eindringflüssigkeit collecting channel 57 should preferably be as great as the depth H (Figure '4) of the or "the oblique or * helical sealing channels 27 _θ the depth of the recessed portion 59 may be the same as the depth H of the or the oblique or" helical sealing channels 27 "you can also differ from this depth. "The recessed part 59 can also conically taper downwards from the outer circumferential surface 26 (not shown).

The various embodiments of the dynamic seals are described in the context of multithreaded rotary processing machines having at least one dynamic seal of the invention, but preferably a plurality of dynamic seals in accordance with the present invention, for undesirable outward escape of liquid from one or more end units of the rotary processing machine Accordingly, the dynamic seals of the present invention are preferably used in multi-pass rotary bar scrubbing machines. Essentially, in multi-unit rotary processing machines, the rotor 10, which carries the processing channels 20, has cylindrical portions between the processing channels 20, which in one

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close relationship to the housing 12 of the rotor 10 stand «

In a preferred embodiment of such rotary processing machines, transfer passages between the processing channels 20 are provided with removable units controlling the flow of material to be processed held by the housing 12 of the rotary processing machine. Also, surface portions may be present which form part of the surface of the annular housing 12 The flow control of the material to be processed controlling units may also carry the Kanalendblöcke extending into the processing channels 20 of the rotor 10. In another embodiment, the top passages and the channel end blocks are circumferentially and / or axially disposed to reduce bearing stress to develop opposing radial forces in the processing channels 20. For example, the annular machining passages, the channel end blocks, and the top feed passages may be arranged to develop radial forces in at least one of the annular machining passages to oppose forces developed in at least one other annular machining pass to provide a substantially axial balance of radial forces produce,. An axial balance of the radial forces is desirable because deflection of the drive shaft 16 or rotor 10 is minimized to thereby provide closer and better control of the distances between the surfaces forming the dynamic seals of the present invention to "allow"

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- 34 -

The dynamic seals of the present invention are generally capable of providing a seal between peripheral surfaces which are separated from one another by a gap 50, 51 which extends up to about 2.5 mm. However, the dynamic seals of the present invention are particular effective when the dynamic seal forming peripheral surfaces or _c surfaces from each other through a gap 50; Are separated 51 which is about 1.2 mm or less, "Accordingly, aer degree of bending or" deflection of the drive shaft 16 or the rotor 10 a factor which considered in the selection of the particular dynamic seal of the invention for use in a rotary machine should be"

Still other advantages are achieved in that a dynamic seal is provided nested truncated conical members are provided from a stiffly resilient material between relatively rotatable coaxial peripheral surfaces at aer, said inner edge portions aer parts form a circumferential surface that nearby and is disposed in a flow resistant relationship to a coaxial peripheral surface, and wherein outer edge portions form a peripheral surface which is in close proximity and in a flow resistant relationship to the other coaxial surface of urgency, edge portions on both the inner and outer portions of the components are retained, so that a pressure against the components in each case brings the outer and inner edges into an improved sealing relationship with their "adjacent circumferential surfaces" or "presses"

FIG _e 16 and 17 show this embodiment of the dynamic seal of the present invention is _e in Figures 17 _a and shown, the truncated conical

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- 35 -

Components 44 carried by the rotor 10 are aligned such that the surfaces 43 of the truncated conical member 44 tend to bear against the processing channel 20, ie, the high pressure region. The inner edges 45 of the truncated conical members 44 are farthest from are retained against axial movement and are held in sealing relation to the rotor 10 by a shoulder 46 and a retainer 47. The retainer 47 acts on the truncated conical component 44 farthest from the processing channel 20 The outer free edges 48 of the truncated conical members 44, which are closest to the processing channel 20, form an outer peripheral surface 49, which is spaced apart to hold the truncated conical member 44 as a group is in a sealing relationship with the cylindrical inner peripheral surface 14, so that the abg estumpften conical members 44 seal the space between the outer peripheral surface 49 and the cylindrical peripheral surface 14 of the housing 12. According to the embodiment of the invention shown in FIG. 16, the outer peripheral surface 49 may have a plurality of helical sealing channels 52 to enhance the seal between the outer peripheral surface 49 and the cylindrical inner peripheral surface 14. The embodiment of the present invention shown in FIG is particularly preferred when it require deflections of the drive shaft 16 so that greater distances than 0,127 mm between the outer peripheral surface 49 and the cylindrical inner circumferential surface can be maintained 14 "Figs _e> 17 shows an alternative arrangement of the components of the dynamic seal of Fig * 16 ₀ As shown in the Figure 17 _e

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21 / ^ # 4 - 36 -

is, a plurality of helical sealing channels 53 on the cylindrical inner peripheral surface 14 is provided to form a dynamic seal between the helical sealing channels 53 supporting cylindrical inner peripheral surface 14 and the outer peripheral surface 49 »

Additional details concerning the present invention are described in connection with Figures 18 _e; 19 and 20 These figures show a calculation of the maximum length of liquid penetration into each sealing channel 27; 27a; 35; 37; 42; 52; 53 with respect to the revolutions per minute for several values of the width l _e The width 1 of the sealing channels 27; 27a; 35; 37; 42} 52; 53 bearing circumferential surface or 'surface and the number and geometry of the sealing channels 27; 27a; 35; 37; 42; 52; 53, as well as other operating conditions, are indicated in each figure. * These figures show that about ten or more sealing channels 27; 27a; 35; 37; 42; 52; 53, which have a certain geometry and have an axial length of about 12.5 mm, a flow or _e escape of fluid over the width 1 can control, especially if the pitch angle O is small, for example, below 15, is "It should It should be noted that the maximum pressure of 1000 psi is well above the normally expected pressure generated in a machining pass of a rotary processing machine. However, the maximum pressure has been selected to reduce the maximum axial penetration length of the fluid into the sealing channels of the indicated geometry or dimensions to determine extreme operating conditions «

From the above description it is apparent that the present

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- 37 -

The invention relates to a novel dynamic seal for controlling the escape of liquid between two relatively rotatable, coaxial and closely spaced circumferential surfaces. The dynamic seal of the present invention is particularly adaptable to rotary processing machines to form liquid and / or solid polymeric materials in one to process more effectively by providing a secure, low friction seal to control the inward or outward leakage of liquid with minimal loss of dynamic seal performance. Accordingly, the present invention provides a new and useful device that provides particularly desirable and unexpected improved overall function characteristics over known devices.

Claims (6)

9-fifth 80 AP F 16 0/217 244 GZ 56 617 27 & ι f & ^ 4 _ 38 claim of invention > .la.nn-inn-miiim-niftfTffwi · π m τ "ι nrm -" / ii TIIi in Ti ¹ H ¹ IIMi Rotatlonsbearbei'cungsmaschine, in particular for processing viscous plastic »or polymer materials or granular plastic« or polymer materials with a rotor having a bearing at least one processing channel circumferential surface and with a stationary housing having a complementary to the circumferential surface of the rotor peripheral surface which of the Circumferential surface of the rotor is separated by a narrow gap and is operatively connected to the processing channel to form an enclosed annular processing passage with the processing channel, wherein the stationary housing also an inlet opening for feeding the material to 'the processing passage, an outlet opening of the Inlet opening at a distance, taking into account a larger part of the circumference of the processing channel, is provided to discharge material from the processing passage, and associated with a component which in the processing channel a is ngeordnet and a surface forming the liquid material collects gathers or _e in order to inhibit this or to limit, and means for rotating the rotor is provided in a direction that leads from the inlet opening to the material limiting surface, so that the Rotor and the supplied material restricing surface of the component cooperate and a pressure along the length of the path of the processing channel is constructed in the direction of the material-restricting surface, characterized in that a dynamic seal for preventing the outflow from under 9. 5. 80 AP F 16 D / 217 244 GZ 56 617 27 Pressure material on the gap (50, 51) has a plurality of sealing channels (27, 27a, 35, 37, 42, 52, 53) on the cylindrical inner peripheral surface (14) and on the outer peripheral surface (26) are arranged so that liquid material in the sealing channels (27, 27a, 35, 37, 42, 52, 53) is penetratable, wherein the width (1) of the sealing channels (27, 27a, 35, 37, 42, 52; 53) bearing cylindrical inner peripheral surface (14) and outer circumferential surface (26), the number, aer angle and the geometry of the sealing channels (27; 27a; 35; 37; 42; 52; 53) is selected so that the outward (27; 27a; 35; 37; 42; 52; 53); directed penetration of the fluid under pressure into the gap (50 51) and in the sealing channels is directed opposite to the inward (on the liquid in the sealing channels 27; 27a; 3; 37; 42; 52; 53) force when the cylindrical inner peripheral surface (14) and the outer peripheral surface (26) relative to each other Bew In order to reduce the extent of penetration of the pressurized fluid into each of the sealing channels (27; 27a; 35; 37; 42; 52; 53) to resist. 2 'rotary processing machine according to item 1, characterized in that the part of the rotor (10) containing a liquid kiet has a zone of minimum pressure, and that a scraper (30; 31; 36) is provided which protrudes into the gap *. 3 ". Rotatxonsbearbeitungsmaschine according to item 1 or 2, characterized in that the liquid-containing part of the rotor (10) has a range of a first pressure and that a circumferentially spaced area has a greater pressure. 9 · 5 «80 AP F 16 α / 217 244 GZ 56 617 27 - 40 - 4. A rotary processing machine according to any one of items 1 to 3, characterized in that in the operation of the turning machine the amount of liquid penetration does not exceed the length of each sealing channel (27; 27a; 35; 37; 42; 52; 53),. 5 'rotation processing machine according to one of the items 1 to 4, characterized in that the sealing channels (27; 27a; 35; 37; 42; 52; 53) are arranged helically. 6e rotary processing machine according to point 5, characterized in that the pitch angle 9 of each sealing channel (27; 27a; 35; 37; 42; 52; 53) is 20 ° or less. A rotary processing machine according to item 6, characterized in that the pitch angle (Q) of each seal channel (27; 27a; 35; 37; 42; 52; 53) is 15 ° or less *. , 8th". Rotary processing machine according to one of the items 1 to 7, characterized in that the cylindrical inner peripheral surface (14) carrying the plurality of sealing channels (42; 53) is stationary ». 9 «rotation processing machine according to one of the items 1 to 7, characterized in that the outer peripheral surface (26) carrying the plurality of sealing channels (27; 27a; 52) is rotatable, '.. 10 * rotation processing machine according to one of the items 1 to 9, characterized in that the gap (50; 51) between the cylindrical inner peripheral surface (14) and oer outer peripheral surface (26) 2.5 mm or less 9. 5. 80 AP F 16 D / 217 244 GZ 56 617 27 - 41 - wearing* 11. A rotary processing machine according to item 10, characterized in that the gap (50; 51) between the cylindrical inner peripheral surface (14) and the outer peripheral surface (26) is 1.25 mm or less. 12. Rotary processing machine according to aa aer points 1. to 11, characterized in that the sealing channels (27; 27a; 35; 37; 42; 52; 53) are arranged substantially parallel to each other. A rotary processing machine according to item I _1, characterized in that the dynamic seal comprises a truncated conical component (44) of a rigidly resilient material, in that the truncated conical component (44) has a surface (43) in the vicinity of the outer free edges (48) ) disposed closest to the processing channel (20) to be displaceable by the pressure, and in that means consisting of a shoulder (46) and a holding device (47) for holding the inner edges (45) of the truncated conical member (44) is provided against a pressure displacement, so that the outer free edges (48) with the cylindrical inner peripheral surface (14) of the housing (12) form a seal, and that the sealing channels (52; 53) either in the cylindrical inner peripheral surface (14) or in the outer free edges (48) are formed « 14 «rotary processing machine according to item 1, characterized in that the outer peripheral surface (26) of the ro- 9 »5. 80 AP F 16 D / 217 244 GZ 56 617 27 - 42 and the cylindrical inner peripheral surface (14) of the housing (12) is formed by a portion of the cylindrical inner circumferential surface (14) of the housing (12). 15 * rotation processing machine according to point l _t characterized in that the rotor (10) in the region of the dynamic seal has an outer surface (32) which is annular and in the region of the outer peripheral surface (26) respectively at the end face of the rotor (10). and that said outer surface (32) faces a stationary annular member (34) having a stationary surface (33) and being fixedly secured to the stationary cylindrical inner peripheral surface (14) of the housing (12). A rotary processing machine according to any one of items 1, 14 and 15, characterized in that the dynamic seal has sealing channels (27; 27a; 35; 37; 42; 52; 53) disposed on each side of the processing channel (20) A rotary processing machine according to any one of items 1, 14, 15 and 16, characterized in that the rotor (IG) has a plurality of processing channels (20), and that each processing channel (20) has a dynamic seal associated with it on the rotor (10). an outer peripheral surface (26), an outer surface (32) or an external surface (40) and a cylindrical inner circumferential surface or a stationary surface (33, 38) located near the rotor (10) on the housing (12) * 9 * 5, 80 AP F 16 D / 217 244 GZ 56 617 27 4 4 _ 43 - 18. A rotary processing machine according to item 2 or 3, characterized in that the scraper (30; 31; 36) has a surface facing the flow, which extends over the cylindrical inner peripheral surface (14) and * the outer peripheral surface (26) and to an angle to the direction of movement of the cylindrical inner peripheral surface (14) or the outer peripheral surface (26) relative to the scraper (30; 31; 36) is inclined « 19e rotary processing machine according to one of the items 1, 14, 15 and 16, characterized in that the outlet from a processing channel (20) is connected to the inlet of a further processing channel (20) « For this .JLjäien drawings