DD152891A5 - Disconnecting and / or threshing device, in particular for threshing machines - Google Patents

Abstract

The invention relates to a separating and / or threshing device, in particular for threshing machines, which is preferably used in self-propelled combine harvesters. The aim of the invention is to reduce the technical-oeconomic production costs, to increase the quality and to allow better adaptation to different operating conditions. The task is to enable predictable and at the same time controllable forced feeding of the goods in the direction of the outlet and to achieve a much better treatment of the goods. As a solution, it is proposed that the drive for the good engagement parts and their connection to the frame are designed such that during the intervention all the good engagement parts promote the goods in the direction of the outlet. As a result, the material in a substantially spiralfoermigen way, ie circumferentially and axially in the housing vorschaubar and controllable moves. The separator consists, inter alia, of a housing surrounding a rotor, the task of which is differentiated according to its function.

Description

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Separating and / or threshing device, in particular for threshing machines

Field of application of the invention

The invention relates to a separating and / or threshing device, in particular for threshing machines, the. is preferably used in self-propelled combine harvesters.

Characteristic of the known technical solutions

Separating and / or threshing devices are already known. In DB-AS 2 540 147 such a device is described, which is provided with an at least partially through holes for the G _u t having to be machined housing and arranged in the housing rotor with a frame. The material to be processed is conveyed between the rotor and the housing in its longitudinal direction to an outlet, and the rotor has connected to its frame drivable Guteingriffsteile circulating in an orbit with respect to the axis of the housing and connected to the frame in such a way in that a relative movement arises between the frame and the elements of good contact. This separator is to replace conventional straw walkers in combine harvesters. , ,

In detail here is located in the housing straw and grain mixture moves over the good engagement parts,. so that the grain can be separated from the straw. The

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Movement is a rotating one with a superimposed back and forth motion. The straw is thus moved back and forth in the detection area by the good engagement parts with respect to the longitudinal axis of the housing, wherein the conveyor rails on the housing are likely to serve to promote the trohort to a discharge-side end. % e but an axial positive promotion can take place, this document is not apparent.

The Hachteil this solution consists in the fact that a controlled movement of the ^above utes is not guaranteed, "

Object of the invention

The aim of the invention is to reduce the technical-economic Hersteilungsauf v / and to increase the quality of the goods and to allow better adaptation to different operating conditions.

Explanation of the reading of the invention

The object of the invention is a separating and / or threshing device, in particular for threshing machines with an at least partially through-holes for the material to be machined .housing and a rotor arranged in the housing with a frame, wherein the material to be processed between the rotor and the housing in its longitudinal direction sü an outlet, is promoted and

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the rotor having its frame connected drivable Goodingriff steep parts, which rotate in an orbit with respect to the axis of the housing and are connected to the frame such that between the frame and good engagement parts a relative movement is created to create a predictable and simultaneously controllable forced delivery allows the good in the direction of the outlet and with a much better treatment can be achieved.

According to the invention the object is achieved in that the drive for the good engagement parts and their connection to the frame are designed such that promote during the engagement all the good engagement parts of the good in the direction of the outlet. In this way, a positive good movement is created by the good engagement parts, through which the good in a substantially spiral ^rf eg, so circumferentially and axially in the housing predictively and can be controlled! is, without the conveyor bars would be required and without a reciprocating movement of the goods would take place.

So that the good does not wrap, is. the separating and / or threshing device provided with a region in which the good engagement parts engage deeper in the ^G ut, and thus also with an area in which the good engagement parts in the good less deeply or not at all intervene.

According to the invention, it is now proposed for the area with deeper engaging in the good ^ uteingriffsteilen that this is rotatable in the housing.

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Because the housing γ formed as a result of receiving the rotor suitably substantially round / ird, it has a center axis, and the arrangement of the rotatable range for the intended in the G _u t deeper engaging Guteingriffsteile according to the invention at least a part of the axis de, s the good engagement parts receiving frame to be rotatable about the axis of the housing.

The frame is provided with a crankshaft.

The drive for the crankshaft and / or the drive for the good engagement parts is changeable.

In certain types of use, it may also be appropriate that the crank does not rotate constantly, wes'half proposed for a separating device in which the good engagement parts are mounted on a crank on a crank, that the crank rotatable about its axis and in different positions is detectable. On the other hand, it is also possible according to the invention to rotate the crank or the crankshaft in its rotated position again about the axis and determine.

Advantageously, the good engagement parts can be articulated on the rotor such that they are freely pivotable in a region which is limited by its essentially radial position and an inclined position in the conveying direction. Thus, it is possible that in the radial position, a promotion in the axial direction, wherein in

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the inclined position the goods easily to the Goodingriffsteilerivigbe glide. With such arranged good engagement parts can be 'connected' in a separator with a swash plate drive and a rotating drum device of the swash plate drive with the good engagement parts receiving drum device. In this way, the good engagement parts then move back and forth in the longitudinal direction of the housing, wherein they additionally granted a circulation movement. This achieves a very good treatment. This is further improved if two counter-rotating over the swash plate drive reciprocating drum devices are provided.

The drum devices can of course be non-solid, which is why each has the good engagement parts receiving circularly arranged longitudinal struts, wherein the longitudinal struts of both drum devices are arranged coaxially. ? ..

In order that the drum devices can be easily guided, both are longitudinally displaceable, but non-rotatable, on a drivable shaft of quadrilateral section. The drum devices themselves are concentric with the housing.

On the other hand, the GoodingriffsteiIe be connected to circumferentially driven Längsstangengest., The longitudinal rods are mounted in driven pulleys, which are inclined to the axis of the housing, so that the good Steing always remain in the same direction. to

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With good guidance, the discs are mounted on a revolving drum having slanted slots for the passage of the engaging parts. The discs themselves are arranged concentrically in the housing. By virtue of the fact that the drive for the disks and the drum can be varied independently of one another, a multiplicity of operating conditions can be set.

The number of operating conditions is still increased when the frame is surrounded by a rotary drum device arranged eccentrically to it. This can be provided with functional strips which extend longitudinally on it, so that owing to the eccentric arrangement, the area in which the engaging parts do not engage in the material is reprocessed.

At the apiel

The invention will be explained in more detail below on several embodiments v / ground. In the accompanying drawing show:

Fig. 1 a schematically illustrated combine harvester in side view with a longitudinally arranged rotating irenneinrichtung;

Fig. 2 is a similar representation as in -'ig. T, however, with a conventional threshing device and two juxtaposed longitudinally extending rotary separators;

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Pig · 3 make a cut along the line 3.- 3 in Pig. 2;

Pig, 4 one of the separators after Pig. 3 in section;

Pig. 5 is a section along the line 5 - 5 in Pig. 4;

Pig. 6 is a representation similar to that in Pig. 4,

however, the axis of the rotor is detectable; ·

Pig. 7 the rotation axis of a pinger star after Pig. 6; Pig. 8 a section along the line 8 - 8 in Pig. 6;

Pig. 9 is a representation similar to that in Pig. 8, but with the rotor twisted;

Pig. Fig. 10 is a schematic sectional view of the separator to show the relationship between the rotor and the straw mat in the housing of the separator;

Pig. 11

up to 18 different rotor axes and the axial movements that can be achieved with them;

Pig. 19. , ,

and 20 schematic representations of the versions of the Pig. 4 and 5, wherein the crankshaft is shown in Fig., Which are 90 ° apart;

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Pig. 21 is a schematic representation similar to that in the Pig. 19 and 20 to represent the axial movement can;

Fig. 22 is a view similar to that in Fig. 4, but wherein the rotor is provided with axially reciprocating rods on which the. , are hinged uteingriffsteile;

Pig. 23 a section along the line 23 - 23 in Pig. 22;

Pig. 24 a schernatic representation for the execution according to Pig. 22, to represent their axial movement can;

Pig. 25 is a schematic representation of the execution of Pig. 24, showing how engage in the Guteingriffsteile ^ü ut and exit again;

Pig. 26 is a similar representation as in Pig. 4, but showing another embodiment;

27 is a ^s chnitt along the line 27-27 in FIG. 26.;

Fig. 28 is an approximately 'similar representation wie.in Fig. 5 for a v / eitere embodiment with a concentrically arranged Tromnielvorrichtung.

The separating device according to the invention is preferably used in a combine of conventional design, as shown in FIG. 1 and described for example in US Pat. No. 4,173,943.

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Such combines have a main frame 10 with front wheels 12 and rear wheels 14, and a driver's cab. He receives his drive from a motor 16 which is connected via a gear with the drive wheels - in the present imsführungsbeispiel with the front wheels 12 - connected. By means of a harvesting device 20 provided on the front side, the crop is picked up by the field when the combine harvester is in use and further conveyed into a separating device 22, which consists of a single rotor in the direction of travel.

The. Separator consists inter alia of a housing 24 surrounding a rotor 26, the task of which is differentiated depending on its function. In the present case, it has a front inlet 28, a threshing 30 and a separator 32. The product discharged from the harvester 20 into the inlet is then conveyed backwards through the threshing and separating part of the separator, the rotor 26 cooperating with the housing 24 to move the crop in a substantially spiral path in a relatively thin mat to promote backwards. The mat is located on the inside of the housing 24. At least part of this housing 24 is provided with through-holes, so that the separated grain from the straw and other small particles can pass outwardly through these holes, where they are collected by a granule 34. From here, the grain is conveyed to a conventional cleaning part 36 * The clean grain in turn passes into a grain tank 38 where it remains until it is discharged through an E _n tleerschnecke 40 :. The remaining part of the material, mainly straw, is returned to

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be promoted to an outlet 42 and stored there on the floor via a racket shaft 44.

A separating device according to the invention can also be advantageously used in a self-propelled combine harvester according to FIGS. 2 and 3, which follows the combine harvester. 1 differs essentially in that two juxtaposed separators 50 are provided in Axialbauweise that take over the threshed property of a transverse threshing unit, which consists in the embodiment of a threshing cylinder 52 and a concave 54. A guide roller 56 supports the delivery of the threshed goods in a front inlet 58 of the separators 50, which in turn deliver the good through an -A- outlet 60 «

In the following, the invention will be described with reference mainly to a rotor or an intermediate part, a rotor cooperating with a substantially conventional separating housing, with no particular reference to the inlet or outlet of the separating device or the other aggregates of the separating device, such as For example, in the Pig. 1 to 3 is taken. In the following description, therefore, the inlets and outlets for the separating housing are described only schematically and also shown in the drawing only, with particular structural details or preferred USführungsformen for the inlet and outlet was not discussed. High is intended to limit the separator to a particular form of mobile harvester or the like

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pointed out that the rotors are nach.der invention particularly advantageous for the inclusion of Good at an inlet end and Wqiterfordern designed. More particularly, there is a trouble-free positive and effective action at the inlet and the outlet when crop conditioning elements or good-grip parts with substantially radially extending tines are used , as addressed in the following embodiments.

The J ¹ Ig. Figures 4 and 5 show an embodiment according to the invention with rotors eccentric to the rotor housing and lying in planes which may be inclined to the axis of the housing. A substantially cylindrically shaped housing 100 has a 'G _e housing wall 102 having an upper housing portion 104 without openings and eirm lower housing part with openings, such as a grating 106. Me inner surface of the housing part 104 and the inner edges of ^G itter Stang-en 108 are arranged substantially concentrically with each other and are referred to below as the inner surface 110 of the housing.

For a better understanding, it should be noted that in the following description it has been assumed that the separating device according to FIGS. 4 and 5 is installed in a combine harvester, as described in Pig. 2, so that its axis runs essentially horizontally and in the longitudinal axis of the vehicle. The ends of the housing are closed by front and rear transverse walls 112 and 114, which together with corresponding interruptions in the

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Transverse wall 102, the ^E inlet 11β and the outlet 118 form. A rotor 120 extends within the housing with its longitudinal axis parallel to the housing axis, and more particularly comprises a shaft assembly in the form of a frame 122 which receives a number of relatively closely spaced tine wheel assemblies 124 surrounded by a cage 126 .

This cage 126 may be considered as a cylinder skeleton having four circumferentially spaced apart coaxial transverse walls 128 serving as a support for four equidistant axially extending struts 130, the latter being equipped with outwardly angled splashes 132 of FIG each of which receives a wear band 134 which counteracts wear and preferably consists of compliant material. The end surfaces 136 of each wear band 134 form a longitudinal groove 138 which extends over the entire length of the cage.

The front end of the cage 126 is mounted concentrically in the housing on a stub shaft 140, which is fixedly connected to the transverse wall 128 and extends into a bearing 142 which is provided in the transverse wall 112 of the housing. The rearmost transverse wall 128 is provided with a fixed, rearwardly extending bearing sleeve 144 which has a keyway 146 in the region of its free end and is received by a cam follower 148 so that the rearward end of the cage 126 is also concentric is angeorndet in the housing 100. Each of the central transverse walls 128 is provided with a bearing 150 which

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Also koa2: ial are arranged in the cage.

The frame 122 of the rotor is supported in the cage 126 by a plurality of short coaxial bearings, including a forward bearing 152 and two central bearings 154. All can freely circulate in the bearings I50 in the corresponding transverse walls 128. A relatively long-trained end bearing 156 with a keyway 158 is provided near the rear end, extends through the bearing sleeve 144 and is mounted in this via roller bearings I60.

The frame 122 or its axis is provided with three offsets, which, as indicated in Fig. 4, are diametrically opposed and formed of three shaft parts I62, ^ ine additional cranking is by a forwardly extending stub shaft portion I64 at the front End of the separator provided. Each offset is considered to be the major axis of the rotor which is parallel to, but offset from, the housing axis. The shaft parts 1o2; 164 are fixed to the bearing 152; 154 and the end bearing 156 via cranks 166 connected. Each shaft part receives a plurality of equally spaced inclined plates I68, while a single swash plate is provided on the stub shaft I64. The axes of these inclined disks 168 are inclined, all in an identical angle to the axis of the shaft parts with which they are firmly connected, so that the axes of the inclined disks 168 are the axes of the shaft parts 162; I64 cut. As in S ¹ Ig. 4, the axes are all

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Slant discs with respect to the V / ellenteile on which they are arranged, inclined in the same seal arranged inclined Thus, the planes of the slices are parallel to each other. , , _; ,

On each inclined disk 168 is mounted in the drawing of the • simplest case not shown rolling bearings ever a .Zinkenradanordnung freely rotatably, the main plane of each Zinkenradanordnung perpendicular to the axis of the slant 168 slices. In detail, each tine wheel assembly 124 is comprised of a hub 170 having a radially extending concentric paddle 172 (see FIG. 5) on which are mounted, via respective fasteners, a set of four double prongs 176, each having two substantially radially extending prongs or has good engagement elements 178. The tips 180 of these tines form the main points of engagement of the tine wheel assemblies, and extend through the longitudinal grooves 138 in the cage 126. As best seen in Pig. 5 ago, so the Porm of each double tine 176 is selected such that adjacent tines 168 diverge slightly in each longitudinal groove 138, so that there is a so-called fork effect.

In the case of this exemplary embodiment-the same applies, however, to embodiments to be described below-the tine wheel arrangements are of relatively narrow design in terms of their transverse section. Their gutingriffst rush are shaped so that the Gutmatte 3- ^m engagement area is not compressed if possible, "

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Conventional drive means, only in Pig. 4 are schematically illustrated with the cage 126 and with the frame 122 via the keyways 146; 158, so that both, when circulating, can independently circulate in desired rates of rehabilitation and direction. For this serve drives 182; 184 and controllers 186; 188. The drives may be, for example, conventional variable diameter wedge pulleys or hydrostatic actuators having their own power source or connected to the combine, the control units of the operator enabling the relative speeds to be adjusted according to the harvesting conditions Also, reversible directions of rotation can be used to solve any clogging binds as a drive means conventional chain, drive or a gear drive use, so it is only necessary to change the speeds that sprockets or gears are replaced accordingly.

6, 7, 8 and 9 show two further embodiments of the eccentrically arranged rotor with inclined tines, as in the '' ig. 4 and 5 is described. As best of the half-schematic side view from Pig. 6, these embodiments are formed similarly to the above-described embodiment. Identical or more or less similar parts are marked with a mark, the last two digits of which are those of the embodiment of the Pig. 4 and 5 correspond. Unnecessary repetitions of the description will be omitted. The fixed housing 200 is arranged with a substantially cylindrical

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Casing shell 202 with an inner flange 210 and an outlet 218 provided. A rotor 222, whose axis is parallel to the axis of the housing 200, is equipped with a shaft assembly or frame 222, a tine wheel assembly 224, and a cage 226. The cage 226 is disposed concentrically with the housing shell 202 and has longitudinal grooves 238, to allow the tines 27.8 of Zinkenanorndung can pass through the cage 224 _e "ine bearing sleeve 244 is in a calender Schlager 248 arranged at the rear end of the housing. The Cage 226 is driven by a drive 282, which in turn engages the bearing sleeve 244.

The rearward end bearing 256 of the frame 222 is rotatably disposed via rolling bearings 160 and concentrically in the bearing sleeve 244. The shaft portion 262 is connected to the end bearing 256 via a crank 266. The tine wheel assemblies 224 are rotatably provided on swash plates 268, which in turn are fixedly connected to the shaft member 262 and a plurality of. are provided in a substantially radially extending and spaced-apart tines or good engagement parts 278 whose outer tips 280 lie in a plane which is perpendicular to the axis of the swash plates, they are rotatable on these swash plates on hubs 270 and tine bearing 271.

The main difference between the embodiment of FIGS. 4 and 5 and that according to the ⁱⁿ ig. '6 and 9 is that the latter is not provided with a positive drive for the frame 222. During the mission here the shaft portions 262 remain with - ehäuseachse ° ezug the ^G or

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However, the embodiments according to the Pig. 6 and 9 devices with which the position of the longitudinal axis of the shaft assembly can be adjusted, this is done by a rotation of the shaft parts 262, so that the ratio of the axes of the inclined plates 268 can be changed to the common plane of each crankshaft section, d , h, the plane in which the axis from a given shaft part 262 and the bearings for the * ellen arrangement such. B. the repository 256, lie. Preferably, in this embodiment, the frame 222 or its axis has a single section, i. h, all parts of the parts 262 are arranged coaxially with one another.

One embodiment of the invention will be described below, in which the actuator 300 is disposed on the rear transverse wall 214 of the housing 200. Specifically, an actuator housing 302 is connected to the rear transverse wall 214 and provided with a rear surface 304 which is substantially parallel but extends at a distance from the transverse wall 214. The end bearing 256 extends through a hub 306 fixedly connected to the back surface 304. Concentric with the housing 306, as indicated in FIGS. 8 and 9, 304% locking points 308 are arranged on a circular arc in the rear side. In the lower half of the back side 304 is also concentric with the hub 306 on a Halbkras von.180 ° a ^S tellschlitz incorporated 310th

The end bearing 256 is modified and formed with a through hole 312 and at its rear walls

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a planch 314, which is in the area of the rear side of the rear side 304 and extends over the adjusting slot, a sump pump / bimimg 315 or other means may, as in * 'ig. 6, secure the rotational position of the flange 314 with respect to the back surface 304. The crank 266 is provided with a bore 318 coaxial with the shaft portion 262.

A 3-fceuerwelle 320 extends through the through hole 312 and is provided with a pin bore 322 at its rear ends and with a spur gear. 324 firmly seated on her front -% de. The attachment of the shaft member 262 to the crank 266 has been modified to allow rotation of the shaft member 262 relative to the crank. This includes .a spur gear 326 which meshes with the spur gear 324 and which is journaled in the bore 318 via a pin 328.

The determination of the rotational position of the shaft part 262 is achieved via an adjusting device 330. This v / eist a ^s tellhebel332 which is connected to the control shaft 320 via a pin 334 and which can be locked in the desired position, characterized in that a grid engages 336 in one of the Binraststellen 308 in the back 304% ne movement the ^ le lever 332 on a quarter circle arc, as indicated in Figure 8, transmits through the spur gears 324; 326 a mirror image rotation on the shaft portion 262, whereby the position of the Zinkenradanordnungen from its in Pig. 6 position shown in the Pig. 7 changed position shown.

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In order to be able to adjust the rotational position of the shaft part 262 now, only the chute 314 needs to be loosened and adjusted to a desired position in the region of the adjusting slot 310. The adjustment of the frame 222 from the lowest position to another position is shown in FIGS. 8 and 9.

Further exemplary embodiments of the invention will be referred to in the following paragraphs, but first of all, reference will be made to some general principles of the method of operation for the exemplary embodiments according to the Pig. 4 to 9 with reference to the ig. 10 to 12 received.

First, some constructive elements and assumptions concerning the operation of the present invention are schematically shown. 10 is shown. In a substantially cylindrical housing 400 with a grid 406, a rotor member 424 is rotatably mounted about a center or bearing 462 · which is offset from the center A of the housing. The rotor element 424 is preferably provided with a plurality of spaced-apart prongs 478, and devices are provided.

in order to be able to rotate the rotor element, with the radially outermost tips 480 of the prongs 478 describing a circular path B in the housing 400. In the tangent point C, this is actually the point at which a minimum distance between the G _u teingriffsteilen 478 and the housing there is the '400, this way is B substantially tangential to the housing. '.

If the ^above ut from which the grains to be separated has been entered into the case, then it is from the Ziiienrad-

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arrangement detects 224 and reaches a steady state in which the crop mat D is continuously distributed around the ^ ehäuseinnenfläche having the same ^u volume setting on and is moved circumferentially there by engagement of the tines 478 '. At the same time remains the Uutmatte with the inner surface of the housing jacket infolge'der Centrifugal force in contact.

Furthermore, it is assumed that the circular arc B, which is described by Zinkenradanordnungen 224, has a certain diameter with a Gutmattenstärke, then results from the direct contact of the prongs 478 with the Gutmatte D an engagement region Ξ on a circular portion having an engagement phase E1 in that the tines penetrate the good mat essentially radially (see arrow P) and preferably do not compress them, and an exit phase E2 in which the tines 478 retract substantially radially out of the feed mat as indicated by the arrow C. ,

In a particular embodiment, the tine wheel assembly 424 may be supported on a support member 4o2 disposed in the housing but spaced apart from the housing center A by the crank 466. Again, devices are provided through which the various rotational positions of the shaft portion 462 can be determined with respect to the crank.

In. In other embodiments, the crank 466 may be formed such that it is detectable with respect to the housing center A in different positions, whereby a setting range for the division of the shaft 462 of the rotor element 424 is achieved.

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On the other hand, it is also possible that the crank rotates around the center A of the housing so that there, s rotor_, element 424 (and the engagement region E and the tangent point C) rotates in the housing 400,

Designs "are possible in which the. The above-described variations (rotatable detection of the shaft part, rotatable and lockable crank and positively driven crank) in various combinations with the basic body of the housing, the eccentric rotor element and the drive means for the rotor element combined v / earth.

In the foregoing description, the elements of the mechanism have been described only with reference to a plane which is perpendicular to the axis of the housing, with reference only to the orbital movement of the mat D due to the action of the tines. Referring now to Figs. 11-18, axial travel will be discussed.

11, there is schematically illustrated a special embodiment of a separating device according to the invention, in which the center of the rotor element or the "hurry 462" is located directly under the center of the housing A. For a better understanding, the tine wheel arrangement 424 will be referred to below as one thin annular disk J viewed (as · is shown in Fig. 10, the flat plane perpendicular to Gehtluseachse), which is rotatable about a slant part 468, the AEIE center of the shaft portion 462 intersects such ^s cheibe arranged around the shaft part 462 as indicated in Fig. 10,

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If, however, the disc is reciprocatable about a vertical diameter H passing through the axes A of the housing 400 and the tangent point C, as shown in Figs. 11, 11 and 12, the disc would only move circumferentially is given, then the engagement region "Θ also has an axial dimension corresponding to the sector I (if the direction of rotation corresponds to that indicated.) The tine wheel assemblies 424 then have the possibility of axial movement of the material mat ·, which movement is proportional to that Sector I is.

In Figs. 13 and 14, the same conditions are reproduced as in Fig. 11, except that the curve 466 has been rotated 90 degrees to a new detected position. The bottom of the engagement area E then has a new location, but the ITetto engagement area remains the same as indicated by the projection of the engagement area E on the horizontal plane in sector I. '

In the pig. 15 and 16, the conditions are the same as in 3? Ig. 11 except that the shaft portion 462, now in its lowest position, has been rotated 90 ° so that the skew portions 468 of the tine wheel assemblies 424 are assumed to be opposite the shaft portion 462; and thus the plane of rotation of the tine wheel assemblies 424 (disc J) a new position with respect to the housing, as described in Pig. In the engagement phase E1 of the engagement region E, a net engagement effect of the tine wheel assemblies on the good mat, which is proportional to the sector K1, will occur while in the exit phase

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same but opposite effect, and zv / ar the sector K2, occurs whose Uetto effect is zero. Pigs 17 and 18 show the result which is reached when the condition of i'ig. 13 and 14 was modified so that the shaft portion 462 was rotated by 180 °. This results in a reversal of the axial index direction,

In the. 19 and 20, further details are given for the above embodiments. S _{0 they} show fixed bearings 46O and 46I for supporting a rotor in a housing 400. Here, the rotor is provided with a frame 422 which supports the rotor elements 424 (only one of which is shown in the drawing for the sake of simplicity) , which are rotated via a rotor element 426 in rotation.

The frame 422 is provided with an outer portion 462, to which in turn a slant portion 468 is incorporated, which forms an angle M with respect to the axis of the shaft portion 462. Detachable couplings 425 allow the rotatable plunger position between the Veltell part 462 and the cranks 466. It should be noted that in the embodiments according to the Pig. 19 and 20, the axes of rotation of the inclined parts of the rotor elements 424 lie in a plane which is perpendicular to the plane of the frame 422 (or the cranks 466), this condition applies to the maximum possible axial index effect at a given inclination angle M.

The circulating drive or the control of the rotor 420 by the rotor rotating parts 426 'via drive means

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482 and a controller 486. The drive or rotation control of the rotational position of the shaft assembly 422 is performed by a drive means 484 and a controller 488, as shown schematically in Figs. 19 and 20. Illustrate the foregoing, such as a variable net axial Index effect of a Zinkenradanordnung is derived or can be controlled by it over a member that has an inclined axis of rotation is eccentrically disposed in a housing ^f ^ race. Due to the eccentricity, the tines of the tine wheel arrangement of the rotor element eccentrically process a gut mat in the housing with an aggregate effect sufficient to move the feed mat in the circumferential direction at a speed substantially against the gutter surface Housing by the centrifugal force pushes ·

Understanding the axial movement of the mechanism just described, which is described in the Pig. 19 and 20, can also be found in Pig. 21 are derived, assuming that the rotor elements do not rotate, d. H. are stationary and controlled by the rotor 426.

Assuming that the frame 422 orbits, the rotor 424 tends to rotate due to friction on the skew 468. This movement is prevented by the system on the rotor 426 rotation. But now, if the orbital motion of the frame 422 stops, then rotates the shaft portion 4β2, which receives the V / ellenanordnung to the housing axis A. Thus arises between dam

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Rotor member 424 and the shaft member 462 a relative movement and der'der inclined axis of the inclined part 468 of the rotor elements a reciprocating motion with respect to the rotor 426 and the housing 400 ·

The basic points in a rotation cycle of the shaft part 462 are in igig. 21 is indicated by the letters N, 0, P and Q, while the corresponding points of the corresponding geometrical locations of the tips 480 of the prongs 478 of the rotor element 424 are designated by the letters R, S, T and U,

In the ingress area with the good mat D, the axial component of the movement of the tips 480 of the good engagement parts 478 always has the same direction as indicated by the vector V. Fig. 21 shows that with the mechanism described above, which allows the periodic engagement in the Gutmatte, an effect is achieved over which the part of the detected Gutmatte is always moved in the same direction. This is true even if the prongs do not fully pull out of the gutmatte during a work cycle. It follows that the axial indexing action of the prongs or their tips 480 is maintained even when both the frame 422 and the rotor 426 rotates rotation, as long as there is a relative rotation in the corresponding direction of rotation between the two. Of course, in such a combined rotation, the travel of the tine tips 480, when engaged in the gut mat D as indicated between the engagement points W and X, will be substantially helical with respect to the housing, with axial and circumferential movement.

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the Gutmatte be combined. It is a characteristic feature of such embodiments (such as, for example, in the frame 122 of FIG. 4) that during the revolution of the rotor, the engagement region is constantly in motion and revolves around the inner wall of the housing so that it depends on the distances st the Guteingriff hasten the entire inner casing is covered. the quality of separation is increased when the balance between the centrifugal force and the force of gravity for engaging area and areas in which there is no Guteingriff varied. minimum speeds are required, the ^G utmatte on the inside of Housing and at the same time to move axially, but in this case the circumferential direction of the frame is of secondary importance _β

FIGS. 22 and 23 show another embodiment of the invention wherein the periodic engagement of the prongs in the mat on the inside of the separator housing is derived from a hinged (jute engaging member disposed on a concentric reciprocating member. about which the orbital and axial movement of the material mat is accomplished, which was not the case with the embodiments discussed above, because there the movements with the periodic detection and release were done solely by the eccentric arrangement in that a certain eccentricity could also be allowed and that such an eccentricity is actually recommended in some embodiments In this embodiment, a coaxial threshing and separating part is provided concentrically in a housing 500 with a cylinder jacket which has a

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upper closed housing shell 502 and lower gratings 504; Having 506 for the threshing and separating part. In this case, the grating 5O4for the threshing member is provided with raised worm strips 508 on its inner surface. The ends of the housing 500 are through transverse walls 510; 512 and the housing shell has an inlet 514 and an outlet 516.

The rotor is designed such that it each has a coaxial threshing 520 and a separating part 522, which - if necessary - can be driven at different speeds. Better performance is achieved when a higher speed is used for the threshing part and a lower one for the separating part. The threshing member 520 is keyed on a rotor shaft 524 which is coaxial with the housing shell 502 and the grate 504. It is disposed in the transverse wall 510 via a bearing 526. The exit end of the rotor shaft 524 extends from the separator 522 and decreases at its end there is a pulley 528 through which the drive can pass into the threshing member 520. The wiper strips 508 cooperate with the threshing member 520 to move the cut mat on the discharge side so that it can be grasped by the separating member 522.

Two coaxially arranged, oppositely displaceable tines, drum 530; 532, the tine elements or good engagement parts of the separating part 522 receive. A S _c hiefscheibenanordnung 534 causes the reciprocation of the zinc drums dieihren driven by a hollow shaft drive 536 obtained which also the bearing surface for the zinc drums

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The slanted disk arrangement 534 and the hollow shaft drive 536 are both mounted concentrically on the rotor shaft 524 like a sleeve. A rotor bearing 538 serves to support the output-side element of the rotor 518 and the rotor shaft 524. It is arranged in the transverse wall 512. The hollow shaft drive 536 in the region of the separating part consists of a square shaft 540, which extends substantially over the length of the separating part and is connected to a drive sprocket 542 via a sleeve 544, which is guided by the output side transverse wall 512. The hollow shaft drive 536 is arranged concentrically rotatably on the rotor shaft 524 and stored there via three rolling bearings 546.

To the inclined disk assembly 534 includes a sleeve 51-8, which also extends through the output side transverse wall 512 and is supported there via the rotor bearing. The sleeve 548 receives at its inner end a swash plate 550 and at its outer end a drive in the form of a sprocket 552 on. Two rolling bearings 554 allow concentric rotation of the slanted disk assembly 534 about the hollow shaft drive 536. The output side swash plate assembly 556, shown only in Fig. 22, is disposed parallel to the swash plate 550 and is free to rotate on the swash plate 550 via the corresponding force bearing bearings 553. It accommodates two diametrically arranged drive cables 560, which extend radially and are each provided with a ball head 562.

The two, each having five rods having zinc drums 530; 532 consist of two axial distances from each other

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and only one set of five identical rods 5 ^ 6 and differ only in their axial position, therefore, it is only necessary to describe a single Zinkentrornmel 530.

Each drum device 564 is arranged for reciprocation on the square shaft 540 of the hollow shaft drive 536 and consists essentially of a substantially circular drum 568 with a Kingflansch 570 and a pair of rollers 574, which are mounted in corresponding recessed diametrical openings 572 and the V run-shaped grooves on the opposite edges of the square shaft and so allow the reciprocating motion of the rod drum device 564 on the drum 540, but do not circulate around this - the five identical rods 566 of the tine grains 530 are by suitable means, such as shown rivets 576, connected to the annular flanges 570 of the two drum devices 564, have circumferentially same distance and are parallel to the housing axis and of course arranged around this axis.

Each ^ö tange 566 takes several axial distance zueinander'aufweisende double tines or Guteingriffsteile 578 in having in cross-section U-shaped brackets 580 via pins 582, which itenwä by their opposing radially extending S _e extend "hands 584th Each double finger .can be made of a single piece of round iron, so that adjacent tines 586 are formed from a hinge part 588 for receiving the pin 582 and a foot piece 59O ^- .

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handle parts are arranged in the holders 580, they can freely pivot about their pins 582. They are designed so that the pivotal movement toward the discharge end is stopped by a foot 590 which rests on the bottom 592 of the support when the tines 586 extend substantially radially, stops 594 are disposed inside on the side walls 584 that they limit the folding back of the tines 586 in the inclined position 593, as in Pig. 22 is shown. Each tine drum 530; 532 is provided with a reciprocating drive connection 596. They take over pans 59, the ball head 562 of the drive parts 5o0 of the oblique disc assembly 534 on. How best of the pig. 22 and 23, the two zinc tromrnelri are 530; 532 substantially axially equally expansive, with the balanced counter-rotating reciprocation and the liming, the in. 23, as well as a suitable axial spacing of the drum devices 564 allows them to not collide with each other as they reciprocate. Other suitable separators using the motor principle may comprise, for example, parallel juxtaposed devices, each having a single reciprocating motor portion, but for balance, the reciprocating motion is in opposition. The rash-like effect of the zinc drums 530; 532 is apparent from the drawings and the foregoing description. The use and operation of a SchiefSschibenanordnung to reshape a rotary motion in a linear reciprocating motion, are known, for example, from the application in hydraulic pumps or Mähmesserant rub,. However, a remark to the Cha _ra kteristika of A guide _us urig embodiment according to the ^ ig hereinafter. 22 and 23 with reference to Fig. 24

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and 25 made. In the hinged embodiment of Figs. 22 and 23, the third disc assembly 534 and the tine drones 530; 533 about a common axis, with a relative rotation between the two elements giving rise to a reciprocating motion, * on such cycle is shown in ⁱⁱ 'ig..24, v / o the essential features of the device are schematically indicated. A slanted disk arrangement 534 ^f is arranged coaxially in a housing jacket 502 and is provided with a slanted disk arrangement 556 ^f . see, with the tines 586 'are connected. These are freely pivotally connected to the slanted disk assembly 556 ', however, stops are provided to limit the pivotal range of the prongs from a substantially radially outwardly extending position to a second one in which they extend outwardly but inclined in " extend ichtung of utflusses. This device is driven such that when the hinge parts are 588 'is driven in the circumferential direction in the housing casing 502', is carried out of the crop flow through the housing over the prongs 586 ^f, the tines in the dip periodically and good evenly into a mat as a result of centrifugal force against the inside of the housing jacket ^{and n} ^ ^e ß ^ · ^ ^e axial component of each hingedly suspended tine 586 * can be examined, wherein the rotational movement wird.während neglected relative rotation of the swash plate assembly 534 ^f -. 'ies is schematic in Pig. 24, in each case for a movement g in the conveying direction and for the return path of the opposite tine in the direction h. ,

When moving in the conveying direction between a and b, the tine is fully erect against its stop and has

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its maximum engagement in the center D (upper part of Fig. 24) · However, at point c (inversion of the seal), the tine is slightly inclined in the conveying direction due to the combination of the decreasing acceleration, the reversal of the linear movement , the persistence of the good mat D and the tines themselves. In the return movement, in the lower part of the ^. 24 is indicated, in the direction h, the movement reversal point 'durun c' is indicated, wherein the tines occupy the same, teil'geneigte position. In an intermediate position at the return (d to e) the tines will be fully collapsed and abut against their stops, in a position resulting from the combination of tine retention force and axial movement between the tines and the crop mat D, when the tines pull out of the Gutmatte. At point f, where the return is reversed again, the deceleration and inertia will help the tines to rise again to a more radial position to engage the gut mat D, after which they will later enter an intermediate area a in the Conveying movement in a completely radial position.

Pig. 25 gives essentially the same analysis of the tine movement as Pig. 24 again with the exception that here in a side view, the pinger in position a to f (f) dar-. When the tines circulate in the housing, of course, the hinge parts 588 'move concentrically around the housing axis. Each actual revolution of the tines is associated with a relative rotation of the inclined disk arrangement 534 ', so that a complete rotation of the tines results in a reciprocating movement of the tines.

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advantage. Pig. 25 shows the periodic engagement of the tines in a good mat D. In the conditions assumed here, a maximum aperture between a and b and absolutely no engagement between d and e, wherein between b and d and e and a the engagement reduced or is enlarged. During the engagement period or in an arc, the tines promote a part of the crop mat both circumferentially and axially, so that a '^ express the ^G describes utes a spiral ^ EC with respect to the housing casing 502nd The aggregate effect of the entire tines in the device after the - ⁰ Ig. 22 and 23 causes the entire Gutmatte is supported by the housing in a spiral path.

In a ~ _rr Vo jL _C ntung according to Pig. 22 and 23, the reciprocation should be greater than the axial displacement of the tips of the tines with respect to their hinge. Of course, the net axial indexing effect will depend on a variety of variables, such as operating speed and matting. The power can be selectively influenced by changing the balance of the tines. S _0, for example, the casting 590 may be provided with a counterweight, whereby the steady-state effect is increased, which in turn results in that the G pivot back _u teingriffsteile 578 in their radial position.

When running after the pig. 26 and 27, the spiral movement of the material mat with fingers which intervene periodically in the product is achieved by a mechanism provided in the inside of a raceway housing and

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is very similar to a conventional swath having parallel bars. As in the. 26 and 27, the device comprises a housing 600 with a housing jacket 602, into which the threshed material passes from an article via an inlet 604 and out of which it is discharged via a water outlet 6o6. The ends of the housing are by transverse walls 608; 610 closed. The rotor 612 has a substantially cylindrical drum 614 with a plurality of helical slots 616 and is supported in the transverse walls 608; -610 by bearings 618; 620, wherein the output side bearing is formed in the shape of a neck 622 that extends through the transverse wall 610. The parallel bar device 624 has discs 626; 628, which are held obliquely by a bearing 630 at the input side end and a - output shaft 632 of a gear housing 634. An input shaft 636 is coaxial with the sleeve 622 and extends through it. Four parallel-spaced longitudinal bars 638 are between the discs 626; Each longitudinal rod 638 are mounted 628 is provided with a plurality of Eingriffsei _em ducks in ^ orm of mutually parallel Guteingriffsteilen 64o, which are arranged so that, arranged 628, v / obei their connection points circumferentially uniformly distributed in the appropriate "eheiben 626th When the parallel bar device 624 is driven in the direction of rotation, each tine moves on an inclined circular arc, the arrangement being such that they assume a constant orientation with respect to the drum 614 and move in their associated slots 616 during one part of the revolution and moving from the drum 614 into a cavity 642 between the drum and

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the housing 600 extend. At its maximum extent and maximum engagement with the Girtmatte 644, each Guteingriffsteil 640 extends radially with respect to the drum 614. The latter and the parallel rod device 624 are driven by conventional, not shown in the drawing drives, such as a variable in its effective diameter V-belt drive or a hydrostatic drive to be connected to the sleeve 622 and the input shaft 636. By varying the relative speeds and directions of rotation, the speed and angle of the tines 640 with respect to the housing can be controlled and the direction and throughput of the feed mat in the separator housing can be controlled. In this embodiment, each tine is connected to the rotor assembly so that a part moves in a circular path concentric with the housing but oblique to the axis of the housing, while another part of the J is oriented in a certain direction with respect to the rotor frame as the rotor rotates so that engagement in the feed mat in the region between the rotor and the housing is radial at least during a portion of engagement of the prongs with the mat.

The execution after ^i? ig. FIG. 28 uses components similar to those of the embodiment of FIGS. 4 and 5, but here the rotor is provided with a drum device which is eccentric to the housing and performs additional functions (such as threshing or separating), however Zinkenradtrommel concentrically arranged to the housing .ist. ^ Ig. 28 shows in semi-

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matic cross-section of a separating device comprising a housing 700 with a lower grid 702 and a rotor 704 which extends into the housing, parallel to. Housing axis extends and has a drum cage 706, which rotates about an axis which is disposed below the housing 700, circumferentially spaced-apart - ¹ × ¹ sktionsleisten 708 take axially extending Dreschleisten 710 and sockets 712 on. Both strips are shown in the preferred embodiment, but can also be formed in one piece.

Several tine assemblies _714} which are arranged concentrically, but mounted in parallel inclined planes are provided on a shaft 716 and Guteingriffsteile 718 which extend through slots 720 in the drum cage 706, IJE a drive via conventional means is a rotation of the drum cage 706 have a Rotation of the tine assembly 714 thereby cause the tines 718 abut against the strips 708. The tines 718 move with a constant radial clearance with respect to the housing 700, but the eccentricity of the drum cage 7O6 forms an operating zone 722 (for threshing or separating) in the region of the main part of the grid 702 where the tangs 710 or the separator bars 712 are close to the grid. Here they reach the best efficiency when they engage in the Gutmatte, the tines then act as a result of the eccentricity that they are fed into the drum.

The material that is grabbed by the tines and moved in the upper part of the separator is recovered by the tines

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stripped when they are withdrawn into the drum in the lower part of the separating housing. Of course, the angle of inclination of the tine assemblies 714 may be selected to achieve a desired amount of axial movement of the suture mat (in the area where the tines have their maximum engagement with the utrean) by virtue of the plane of the teeth zinc star rt in a manner ^a and is inclined to that in Pig. 7 or 12 corresponds. Of course, the execution of Pig. 28 used in conjunction with 'features of the other embodiments, such as. B. the adjusting devices to Pig. β to control the pitch plane of the tine stars, which in turn affects throughput, or the location of the drive axle to optimize threshing or separation.

Claims (21)

Separating and / or threshing device, in particular for threshing machines, having an at least partially through-holes for the housing to be processed good and having a housing arranged in the housing with a frame, wherein the machined G _u t between the rotor and the housing in its longitudinal direction is conveyed to an outlet and the rotor has connected to its frame drivable good engagement parts which rotate in an orbit with respect to the axis of the housing and are connected to the ^K ahiaen such that there is a relative movement between the frame and good engagement parts, characterized in that by the connection of the drives (182; 282; 482) for the good engagement parts (178; 278; 478; 578; 640; 718) with the frame (122; 222; 422) during the singing engagement all the good engagement parts move the goods in the direction of promote the outlet (118; 218; 516). 2.! Separating and / or threshing device according to item 1, characterized .dadurch in that the area which is in the G _u t. is provided with deeper, intervening engaging parts. Housing is rotatable. The separating and / or threshing device according to item 1 or 2, characterized in that at least one of the axes of the frame (122; 222; 422) receiving the good engagement parts (178: 278; 478; 578; 640; 718) the axis of the housing (100; 200; 400; 500) is rotatable. 4 -β- 10 * 12.1980   '. - A 01 D / 222 57 716/23 4 · separating and / or threshing device according to point 3, * denotes in that the frame (122, 222, 422) is provided with a crankshaft (162, 262) 5. separating and / or threshing device according to one or more of the preceding points, characterized in that the drive for the crankshaft (162; 262) and / or the drive for the Öuteingriffsteile (178; 278; 478; 578; 64Ο; 718 ) is changeable. 6. separating and / or threshing device according to one or more of the preceding points, wherein the good engagement parts are mounted on a crank on a crank, characterized in that the crank is rotatable and lockable about its axis ^A. 7. separating and / or threshing device according to one or more of the preceding points, characterized in that the crank or the crankshaft (162; 262) is detectable in its rotated about the axis of the housing position. 8. separating and / or threshing device according to one or more of the preceding points, characterized characterized in that the G _include teingriffsteile (578) on the rotor (518) is hinged, and are free to pivot in a region which is bounded by its substantially radial RECOVERY * H and an inclined position in i'örderrichtung. -i- · 10.12.1980 • A 01 D / 222, 57 716/23 9. separating and / or threshing device according to one or more of the preceding points, characterized in that the swash plate drive (556) with the good engagement parts (678) receiving drum device (564) is connected. - $ - "10.12.1980 , A 01 D / 222 57 716/23 10 »separating and / or threshing device according to item 9, characterized in that zv / ei in opposite directions over the ^ primescheibenantrieb (556) back and herbev / egenbare drum devices (564) are provided. - \ -. 12/10/1980 A 01 D / 222 •. · 57 716/23 invention claim Separating and / or threshing device according to the items 10 and 10, characterized in that each drum device (564) has the longitudinally engaging webs (566) receiving the good engagement parts (578), the longitudinal struts of both drum devices being arranged coaxially. 12. separating and / or threshing device according to one or more of the preceding points, characterized in that the drum devices (564) on a drivable ^; ^ (540) are longitudinally displaceable, but not arranged rotatable. Separating and / or threshing device according to one or more of the preceding points, characterized in that the drum devices (564) are arranged concentrically to the housing (500). 4 ^fc * "-4- · 10,12.1980 ' _v ' A 01 D / 222 484 ', 57 716/23 14 · separating and / or. Threshing device according to one or more of the preceding points, characterized in that the good engagement parts (640) are fixedly connected to revolvingly driven longitudinal bars (638). Separating and / or threshing device according to item 14, characterized in that the longitudinal rods (638) are mounted in driven discs (626; 628) which are inclined relative to the axis of the housing. 16. Separating and / or threshing device according to item 15, characterized in that the discs (626; 628) are mounted on a revolving drum (614) which. Slanted slots (616) for the passage of Gutein-.griffsteile (640). , Separating and / or threshing device according to item 15, characterized in that the discs (626; 628) are arranged concentrically in the housing (600). 18. separating and / or threshing device according to the points 14 and 16, characterized in that the drive for the discs (626; 628) and the drum (614) are independently variable. 19. separating and / or threshing device according to one or more of the preceding points, characterized in that the frame is surrounded by an eccentrically arranged troirring device (7O6). 22 2 41 20, separating and / or threshing device according to one or more of the preceding points, characterized in that the drum device is provided with ^ unktionsleisten,. , 21 ,. Separating and / or threshing device according to item 20, characterized in that the friction bars are arranged in the longitudinal direction on the front axle in the direction of travel ο HtefziLdO-JSetten drawings