GB2095964A

GB2095964A - Combine harvester

Info

Publication number: GB2095964A
Application number: GB8209460A
Authority: GB
Original assignee: VEB Kombinat Fortschritt Landmaschinen Neustadt (Bestand)
Current assignee: VEB Kombinat Fortschritt Landmaschinen Neustadt (Bestand)
Priority date: 1981-04-02
Filing date: 1982-03-31
Publication date: 1982-10-13
Also published as: BE892746A; DD158460A3; BG42686A1; FR2502892A1; CS239338B1; DE3211177A1; PL235793A1; HU186920B; SU1227130A1

Abstract

A combine harvester comprises a loosening and distributing device arranged transversely to the conveying direction of harvest stock above a straw shaker and comprising a plurality of tine rakes (8), which rotate about a horizontal axis and are arranged on crossbeams (7) continuous over the entire width. The tine rakes (8) are arranged one beside the other on the crossbeams (7), are each mounted to be pivotable above a respective bolt (9) perpendicularly to the plane of the respective crossbeam (7), and are together steplessly settable parallelly to each other. <IMAGE>

Description

SPECIFICATION Combine harvester The present invention relates to a combine harvester and has particular reference to a straw loosening and distributing device, on straw shakers of a combine harvester, the device being arranged transversely to the conveying direction of the harvester stock above the straw shaker and comprising tine rakes.

Devices for the loosening and distributing of the harvest stock above such straw shakers are already known in different constructions and arrangements.

Thus, for example, in DE-OS 21 03 981 there is disclosed a receiving drum which is arranged in the space above the straw shaker, receives the straw, conveys it over the drum and thereafter delivers it back to the straw shaker or to a further receiving drum. As a result, the path which the straw to be shaken out traverses on the shaker is increased by the length of the circumference of the receiving drnm However, as the layer of the straw is moved additionaliy only in vertical direction upwardly and downwardly and is loosened, and no transverse conveying and distribution takes place, the device is only of limited effectiveness.

in ad described in DE-OS 20 01 386 for distributing and loosening of stockfrom the threshing device by distributor tines rotating on a drive shaft transversely to the conveying direction, these tines are arranged on swash plates which are mounted to be freely rotatable on swash hubs connected to the drive shaft to be secure against rotation and are drivable at different speeds relative to the drive shaft. In this manner, the harvest stock is more intensively acted on by to and fro lateral movements of the distributor members, since the movements of the distributor members take place more frequently per unit time by comparison with their rotary motion.

Moreover, a distributor device is disclosed in DE-AS 19 04 406, in which adjustable distributor tines are drivably arranged around an axle or shaft extending transversely to the conveying direction of the straw shaker. The distributor tines are arranged at least partially in a drum rotatably mounted in the shaker housing and adjustable through an eccentric drive transversely to the conveying direction of the stock by an axle provided in the drum. As a result, the distributor tines can transport the harvest stock in the conveying direction and in that case effect a distribution and loosening of the same.However, the two last mentioned loosening devices have the disadvantage of a small slope capability during operation of the combine harvester on a contour line, since although they enable movement of the stock to and fro transversely to the conveying direction, they do not provide uniform stock distribution over the width of the straw shaker in sloping positions.

There is accordingly a need in such combine harvesterto intensify the residual grain separation of the straw shakers and to improve the slope capability,for example through a more advantageous construction of the loosening and distributing devices as well as their possibilities of adjustment.

According to the present invention, there is provided a combine harvester comprising shaking means for shaking harvest stock conveyed in a given direction over the shaking means and at least one stock loosening and distributing device arranged above the shaking means to extend transversely to the conveying direction and to be rotatable about a substantially horizontal axis, the or each device comprising a plurality of support members each extending over substantially the entire width of the shaking means and a respective plurality of mutually parallel rake elements arranged one adjacent the other along each support member, each rake element being so mounted to the respective support member for pivotal movement about an axis perpen dicularto a reference plane of the support member that the settings of the rake elements of each plurality relative to the respective support member are simultaneously and steplessly variable while maintaining the parallel relationship of the rake elements.

In a preferred embodiment, cross beams are arranged continuously over the entire width of the loosening and distributing device rotating above straw shakers, and mounted on the cross beams are several tine rakes which are arranged one beside the other, are each mounted to be pivotable about a respective bolt perpendicularlytothe plane of the associated cross beam, and are together steplessly settable parallellyto each other.

The angular setting of the cross beams relative to the conveying plane of the straw shakers may be varied through, for example, a double crank gear or a cam gear. The pivotal position of the tins rakes is preferably settable through axially movable adjusting shafts accessible from the outside of a housing of the shakers. For preference, associated with each tine rake is a connecting strap, which is fastened on an associated adjusting shaft and which has a recess in which is guided a pin arranged eccentrically on the pivot bolt of the rake. The bearing of the adjusting shafts may at the same time form the pivot point for the cross beam. Expediently, arranged on the ends of the adjusting shafts are runners which stand in running contact with thrust washers secure against rotation and movable in axial direction.The thrust washers are preferably connected with pipe sections which stand in contact through a trapezium toothing with counterpieces secured against axial displacement, the counterpieces being arranged to be rotatable by means of levers relative to the pipe sections secured against rotation.

In the above-mentioned preferred embodiment, the tine rakes can be pivoted parallelly one to the other steplessly in both pivoting directions up to an angle of, for example, about 45" relative to a centre position in which they are disposed in a line perpendicular to the conveying direction. In cooperation with the respectively opposite cross beam, six combinations, which may enable universal use of the device, result from the possible basic settings of the tine rakes. The first setting variant is the centre position of all tine rakes. This position has a loosening effect extending in the direction of the stream of the stock and enhances transport of the stock. The second and third combinations result from the centre position of the tine rakes of one cross beam, whilst the oppositely disposed tine rakes are pivoted in a desired direction.This setting has a loosening and at the same time one-sided transverse conveying effect. The fourth combination consists of the opposite pivotation of the tine rakes on the oppositely disposed cross beams so that loosening of the stock is enhanced by the transversely oscillating movement of the stock. The fifth and sixth combinations relate to symmetrical setting of the oppositely disposed rakes into the respectively desired direction, whereby a loosening and transverse conveying effect on the stock takes place analogously to the second and third combinations, for which twice the transverse conveying performance compared with these settings is achieved.

An embodiment of the present invention will now be more particularly described by way of example with reference to the accompanying drawings, in which: Figure l is a schematic longitudinal sectional view of part of a combine harvester according to the said embodiment, showing the arrangement of loosening and distributing device above straw shakers; Figure 2 is a front elevation, to an enlarged scale, of one of the loosening and distributing devices; Figure 3 is a cross-section along the section line in Figure 2; Figure 4 is a view of the lower side of the loosening and distributing device, showing a mechanism for adjustment of tine rakes of the device; and Figure 5 is a schematic diagram of an alternative control system for adjusting the setting of cross beams of the device.

Referring now to the drawings, there is shown part of a combine harvester in which two rotatable loosening and distributing devices 4 and 5 are arranged at side walls 6 of a shaker housing 3 transversely to the conveying direction of harvest stock between straw shakers 1 and the upper wall 2 of a shaker housing 3. Several tine rakes 8 are mounted one beside the other on each of two cross beams 7 pivotable in circumferential direction on the circumference of the loosening and distributing devices 4 and 5. The rakes 8 are rotatably mounted on each cross beam 7 each by means of a bolt 9, which is guided in a pipe section 10. The entraining connection is effected by a fit pin 11. A washer 12 of plastics material is provided between each rake 8 and the cross beam 7 to reduce friction. For the same purpose, the pipe section 10 is surrounded by a plastics material sleeve.

The required setting of the rake 8, each consisting of four individual tines 13, relative to the conveying plane of the straw shaker 1 takes place by means of a four-bar linkage designed as a double crank. One side wall 14 of the loosening and distributing device 4 or 5 and one control rod 16 mounted on an eccentric member 15 form the two cranks so that the cross beam 7 as coupling member between the two side walls 14 assumes the appropriate angular position of the rakes. The setting of the engagement and exit angle of the rakes 8 is provided by rotation of the eccentric member 15, rigidly connected with a stationary axle 17, about the centre point of the axle.

Another possible construction for the control of the setting of the cross beams 7, by means of a cam gear, is illustrated in Figure 5. In this case, a wheel 18 scans the external outline of a cam 19 and thereby sets the length of a telescopic rod 20, which in its turn controls the setting angle. Constant contact between the wheel 18 and cam 19 is maintained by a tension spring 21. Since the cam 19 is, similarly to the eccentric member 15, firmly connected to the axle 17, influencing of the control can take place in like manner from outside during the rotary motion of the devices 4 and 5.

The setting of the respectively required pivotal position of the rakes 8 on the cross beams 7 take splace through the displacement of adjusting shafts 22 in axial direction. For this purpose, associated with each rake is a connecting strap 23, which is fastened on the respective adjusting shaft 22 by means of a securing washer 24. A pin 26 fastened eccentrically to the bolt 9 of each rake is guided within a recess 25, in the form of an elongate hole, in an associated strap 23. The longitudinal movement of each adjusting shaft 22 is converted by these pins 26 into pivotal movement of the relevant rakes 8. The selected setting of the tine rakes 8 is secured under loading in co-operation with the adjusting force of the adjusting shaft 22 by a compression spring 27 arranged at the end of the adjusting shaft 22.The compression spring 27 bears on the one hand against a metal abutment plate 28 connected with the crossbeam 7 and is on the other hand biased by means of a washer 29 and a key 30. The bearing of the adjusting shaft 22, consisting of a bearing tube 31 with plastics material sleeve 32, in the cross beam 7 and the side wall 15 at the same time forms a pivot point for the cross beam 7. The axial displacement of the adjusting shaft 22 is effected by thrust washers 33 and 34, which are connected to axially movable pipe sections 35 and 36. The contact between the adjusting shafts 22 and the thrust washers 33 and 34 is produced by runners 38 mounted on the shaft ends 37. The axial movement of the thrust washers 33 and 34 takes place through a trapezium toothing through the rotation of counterpieces 39 and 40, secured against axial displacement, relative to the pipe sections 35 and 36. The adjusting movement is initiated through levers 41, which are operated directly by hand or through Bowden cables or linkages from the harvester cab in accordance with requirements.

The axial locating of each loosening and distributing device 4 and 5 takes place through bearing blocks 42 at both sides, in which the separate axles 17 and 43 are firmly clamped. The drive of each device takes place through a V-belt pulley 44. Ball bearings for the bearing of the device on the axles 17 and 43 are arranged within a sleeve 45. Since two, mutually separate axles 17 and 43 are provided, the required strength is achieved through two U-shaped profiles 46 detachably connected with the two side walls 14. Under special harvest conditions it is also possible to screw metal plates to the individual rakes 18 so that closed buckets are formed. Moreover, adjustable metal baffle plates 47 and 48, which are arranged downstream of the devices 4 and 5, can be fastened to the wall 2.

Claims

1. A combine harvester comprising shaking means for shaking harvest stock conveyed in a given direction over the shaking means and at least one stock loosening and distributing device arranged above the shaking means to extend transversely to the conveying direction and to be rotatable about a substantially horizontal axis, the or each device comprising a plurality of support members each extending over substantially the entire width of the shaking means and a respective plurality of mutually parallel rake elements arranged one adjacent the other along each support member, each rake element being so mounted to the respective support member for pivotal movement about an axis perpen dicularto a reference plane of the support member that the settings of the rake elements of each plurality relative to the respective support member are simultaneousiy and steplessly variable while maintaining the parallel relationship of the rake elements.

2. A harvester as claimed in claim 1, wherein each of the support members of the or each device is angularly displaceable to vary the angular setting of the respective reference plane with respect to a conveying plane of the shaking means.

3. A harvester as claimed in claim 2, wherein the support members are angularly displaceable by one of cam means and crank gear means.

4. A harvester as claimed in any one of the preceding claims, comprising axially movable adjusting shafts operable externally of housing means of the shaking means to effect said pivotal movement of the rake elements.

5. A harvester as claimed in claim 4, wherein the rake elements are connected to the shafts each by means of a pin which is connected to the rake element eccentrically of the pivot axis thereof and is slidably engaged in a recess of a cam member connected to an associated one of the shafts.

6. A harvester as claimed in either claim 4 or claim 5 when appended to either claim 2 or claim 3, wherein each of the shafts is mounted in respective bearing means defining an axis for angular displacement of an associated one of the support members.

7. A harvester as claimed in any one of claims 4 to 6, wherein each of the adjusting shafts for the rake elements of the or each device is provided at one end thereof with engaging means bearing against a respective thrust element which is secure against rotation and which is axially displaceable to effect axial movement of the associated adjusting shaft.

8. A harvester as claimed in claim 7, wherein each of the thrust elements comprises a cam surface engaging a cam surface of a respective displacing member, which is secure against axial movement and which is rotatable relative to the associated thrust element to so relatively displace the cam surfaces as to cause the thrust element to be axially displaced.

9. A harvester as claimed in claim 7, wherein the cam surfaces are provided by a trapezium-shaped toothing.

10. A harvester as claimed in either claim 8 or claim 9, wherein each of the displacing members is provided with lever means to enable rotation thereof.

11. A combine harvester substantially as hereinbefore described with reference to Figures 1 to 4 of the accompanying drawings.

12. A harvester as claimed in claim 11 and modified substantially as herein before described with reference to Figure 5 of the accompanying drawings.