Harvester

Abstract

The harvesting tool of the harvesting device according to the invention, which rotates around a vertical axis, is driven by a drive shaft (8) connected in a rotational manner with the freewheel (10) via drive pins (16) via a gear train containing a freewheel (10). The drive pins (16) create a drive connection between the freewheel (10) and the harvesting tool in a basic direction parallel to the rotation axis of the harvesting tool in order to drive it, while when the drive shaft (8) is stationary, they perform a lifting movement together with the freewheel (10), which interrupts the drive connection between the harvesting tool and the freewheel (10). During their lifting movement, the drive pins (16) activate a brake device consisting of a brake disc (27) and counter-brake discs (28, 29), which is formed on the inner side of the gear housing, above the freewheel (10), and quickly stops the further rotating harvesting tool. à

Description

The description is 10 pages long (including 5 pages of figures) HU 221 260 B1 The invention relates to a harvesting device with a harvesting tool rotating around a vertical axis, which can be driven via a drive shaft that is rotatably connected to the freewheel via drive pins via a gear mechanism containing a freewheel. The drive pins establish a driving connection between the freewheel and the harvesting tool in a basic direction parallel to the axis of rotation of the harvesting tool in order to drive it, and when the drive shaft is stationary, they perform a lifting movement together with the freewheel, which interrupts the driving connection between the harvesting tool and the freewheel. Such harvesting devices are used for harvesting stem crops in harvesting machines, which are usually equipped with at least two such harvesting devices and can be self-propelled or tractor-mounted devices. The harvesting machine can also include a chopper for chopping whole silage crops, in particular corn. For such crops, harvesting devices combined with feed drums are usually used, which guide the crop cut by the harvesting tools to the chopper. Such a device can be found in the description HU 216 173. While the feed drums rotate at a low peripheral speed and therefore come to a short stop when the machine is switched off and the drive connection is then interrupted, the harvesting tools of the harvesting device, which are designed as circular knives or saw rotors, have a very high peripheral speed. Depending on the size of the rotor, this peripheral speed can reach, for example, 500-1500 rpm. If the drive shaft of the harvesting tool stops, for example when the tractor is released from the throttle during a blockage in the transport of the crop, the tool continues to run for a relatively long time due to the oscillating mass of the fast-moving harvesting tool, for example, for 30-50 seconds depending on its size. This can cause cuts if people come close to the harvesting tools. To avoid this, hydraulically or electrically operated braking devices for harvesting equipment or rotary harvesting machines are already known. These, such as the device described in US 5293731, require separate external power sources and electrical or hydraulic connections, which make the harvesting equipment complex and extremely sensitive to disturbances in tough agricultural harvesting work. The aim of our invention is therefore to design a harvesting device of the type described in the introduction in such a way that the harvesting tool can be braked very reliably, without the use of external drives and resources, but only mechanically. This problem is solved in principle according to the invention in that the lifting movement of the drive pins, which is performed when the drive shaft is stopped in order to break the drive connection between the freewheel and the harvesting tool, is used to activate a brake device, which is formed according to the invention on the inside of the gear housing, above the freewheel. This is done by arranging an annular pressure plate on the upper side of the drive pins, which works against the brake device on the inside of the gear housing during the lifting movement of the drive pins. The braking force exerted by the brake device on the inside of the gear housing on the drive gear of the harvesting tool or on a drive part rotating therewith and carrying a suitable brake disc can be advantageously adjusted flexibly so that different braking torques can be exerted according to the braking conditions. For this purpose, a clamping pressure can be established under spring load between two horizontal counter-brake discs on the housing side, between which the brake disc is arranged in a gap, which determines the frictional resistance of the brake disc and thus the braking effect. Instead of horizontal counter-brake discs on the housing side, between which the brake disc is arranged, a design is also possible in which the brake disc rotates in a circumferential plane with the drive gear of the harvesting tool by means of an appropriate drive device and acts against a counter-brake surface on the inner circumference of the gear housing. The braking force can also be advantageously adjusted flexibly in this case. In a further preferred embodiment of the invention, the pressure plate is connected to the brake device by vertical coupling pins arranged at a certain distance from each other in the circumferential direction, which are held in the pressure plate by a spring bias in the direction of the brake device, i.e. upwardly. To carry out the braking process, the coupling pins are engaged in longitudinal holes in the circumferential direction of the drive device holding the brake disc. For short, uniform braking, which can stop the harvesting tool released from the drive connection in about 5 seconds, and in the case of larger harvesting tools in a maximum of about 20 seconds, a locking disc is preferably arranged on the horizontal upper side of the freewheel ring disk part, which locks the freewheel drive pins at the end of their upward lifting movement when the drive shaft stops, when the drive pins take up their braking position. The gear parts, which continue to rotate with the driving gear of the harvesting tool due to its oscillating mass, thus rotate above the horizontal ring disk of the freewheel without changing their plane of rotation, and thus ensure a uniform braking effect of the co-rotating brake disk on the counterbrake device fixed to the housing. Our invention and its further features and advantages are described in more detail in connection with its exemplary embodiment with the help of our drawings, of which: Figure 1 is a top view of a harvesting machine, in which a total of eight harvesting devices equipped with a braking device according to the invention are located, the Figure 2 is a section taken along section line II-II of Figure 1, The lower part of Figure 3 is a perspective view of the overall gear of the harvesting tool, the upper part is a larger-scale perspective view of the gear parts in the gear housing, the Figure 4 is a perspective view of the freewheel with the brake system, partly shown in exploded views, HU 221 260 B1 Figure 5 is a vertical section of the arrangement according to Figure 4, in which the drive pins of the freewheel are in drive connection, the Figure 6 is a vertical section of a detail of the arrangement according to Figure 5, the Figure 7 is the arrangement according to Figure 5, but in which the freewheel drive pins are in the braking position, Figure 8 is an arrangement according to Figure 6, but with the drive pins of the freewheel in the braking position. The harvester shown in FIG. 1, which is moved forward in the direction of arrow F, is designed in the illustrated embodiment as a tractor-mounted device and includes, for example, eight M harvesters. Four of these are arranged on one side of a vertical longitudinal center plane of the machine and four on the other side of it. The M harvesters are arranged in the direction of travel indicated by arrow F only in front of the chopper H, which is indicated by its feed rollers arranged in front of it. The chopper H, together with the M harvesters, forms a unit of the harvester in the illustrated embodiment, for example a so-called corn harvester-chopper. Each M harvester comprises a rotating harvester tool. The harvester tool 1 is formed by a circular blade or a so-called saw rotor, and the harvester tool 1 is combined with a slow-moving feed drum in the illustrated embodiment. The cut crop is conveyed transversely to the chopper H by transverse transport drums 2a. Both the harvesting tool 1 and the feed drum 2 are driven by a main drive shaft 4 in a gear 3 through an angle gear 5, the bevel gear 6 at the end of which is connected to the bevel gear 7 of a vertical drive shaft 8. One main drive shaft 4 on each side of the vertical longitudinal center plane of the machine is connected to the central gear of the chopper H through the gear gear 4a, from which it receives its drive. Further details of the 3rd gear and the 3rd gear housing are in the They are shown in Figure 3. On the vertical drive shaft 8 above the bevel gear 7 of the angle gear 5 there is a small gear 9 and a freewheel 10, which are connected in a co-rotating manner with the drive shaft 8. The gear 9 is connected to the gear 11 on the shaft 12 serving as a drive shaft for the feed drum 2. The feed drum 2 is fixed at the upper end of the shaft 12. On the freewheel 10 there is a further, large-diameter gear 14, which is connected to the small-diameter gear 15 for fast driving of the harvesting tool 1. The gear 15 is on the tubular shaft 13, at the upper end of which a flange 13a serves to fix the harvesting tool 1. On the horizontal ring disk 10a of the freewheel 10, three driving pins 16 are arranged at equal angular distances from each other, which have a lower extension 16a of reduced diameter. The driving pins 16 cooperate with a locking disk 17, which is placed on the ring disk 10a. The locking disk 17 is fixed on the gear wheel 14 in such a way that it can be rotated by approximately 15°. For this purpose, a pin 17a is screwed into the gear wheel 14 from below, which extends into a longitudinal hole 17b of appropriate length, curved in the circumferential direction of the locking disk 17. The driving pins 16, in the driving connection with the freewheel 10, as can be seen in particular in Figure 5, extend with their lower extensions 16a into three curved paths 18, which are arranged in the annular disk 10a at a suitable angular distance from each other and are provided with a slope 18b on the bottom side at its deepest end point 18a. The slopes 18b pass into the surface of the annular disk 10a at their end opposite the end point 18a. The direction of rotation of the freewheel 10 when driven from the main drive shaft 4 via the angle gear 5 is shown in Figure 4 by arrow 'A'. If the drive is stopped and as a result the freewheel 10 stops, the direction of rotation of the harvesting tool 1, which continues to rotate due to its flywheel mass, is shown by arrow B. When the harvesting tool 1, together with the drive parts connected to it, continues to rotate in the direction of arrow B in the stationary position of the freewheel 10, the three driving pins or driving cams 16 run up the surface of the ring disc 10a on the slope 18b in their curved path 18, but in the meantime they are held in a locking groove 19 of the locking disc 17 on the lower side. The locking lugs 19 are arranged as through-holes on the locking disc 17, distributed at appropriate angular distances. Each locking groove 19 has a wider groove part 20 and a narrower groove part 21 connecting thereto. As shown in FIG. 5, the groove part 20 receives the driving pins 16, and the extension 16a of the driving pin 16 is pushed into the groove part 21. The extension 16a, acting together with the narrower groove part 21, locks the given driving pin 16 in its raised position, as can be seen in particular in FIG. 7. This continued rotational movement is otherwise controlled in a known manner by the contact between the vertical part of the freewheel 10 and the inner peripheral surface of the gear wheel 14 adjacent thereto, as shown in FIGS. 5-8. This is made possible by the needle roller bearing 10b shown in Fig. When the lower drive pins move from the driven position according to Figure 5 to the raised position according to Figure 7, the annular pressure plate 22 resting on the upper side of the drive pins 16 is raised, which is connected to the gear wheel 14 in a co-rotating but axially movable manner. The pressure plate 22 is provided with three coupling pins 23 arranged at equal angular distances from each other, which are permanently pressed against the pressure plate 22 by a prestressed pressure spring 24. When the drive pins 16 lift the pressure plate 22, the coupling pins 23 come into driving contact with a drive ring 25 by extending into the circumferentially arcuate elongated holes 26 machined into its lower side, on which the further rotating gear parts rest on the end side during the further rotating movement in the direction of arrow B. This operating position is primarily shown in Figures 7 and 8, where the further rotating gear wheel 14 is connected to the drive ring 25 by the coupling pins 23.In Figures 6 and 8, the coupling pins 23 are shown partially in section, so that. HU 221 260 Β1 shows the compression spring 24 placed in the inner hollow space of the coupling pin 23 and its lower side bearing on the locking disc 17. In the illustrated embodiment, the brake device comprises an annular brake disc 27 made of a suitable wear-resistant material, the inner peripheral edge of which is rigidly connected to the outer peripheral edge of the drive ring 25 by interlocking teeth. The brake device further comprises two counter-brake discs 28 and 29, between which there is a horizontal, annular gap. The counter-brake discs 28 and 29 are screwed together with the upper housing part 30 of the gear housing 3a via the spacer bushes 32 preventing distortions by means of the fixing bolts 31 so that an annular gap is formed to receive the brake disc 27. The screwing together takes place via disc springs 33 arranged around the spacer bushings 32, which allow the gap width to be flexibly adjusted in accordance with the swing mass determined by the harvesting tool 1. The narrower the annular gap formed between the counter-brake discs 28 and 29, the greater the braking effect exerted on the brake disc 27 rotating there. The brake is released automatically by lowering the pressure plate 22 when the main drive starts again, in the illustrated embodiment the tractor is again throttled. As a result, the drive shaft 8 and thus the freewheel 10 are driven in the direction of arrow 'A' via the main drive shaft 4 and the angle gear 5. As a result of the frictional engagement between the locking disc 17 and the ring disc 10a of the freewheel 10, the locking disc 17 rotates in the direction of arrow 'A'. As a result, the drive pins 16 slide back from the narrower groove part 21 of the locking lugs 19 into the wider groove part 20. Through the wider groove part 20, the driving pins 16 go down into the corresponding curved path 18, and in this, on the slope 18b, they slide down to the end point of the groove 18a, so that the harvesting tool 1 is driven again in the direction of arrow 'A' by the positive engagement of the driving pins 16 and the freewheel 10. The downward movement of the drive pins 16 and the pressure plate 22 is assisted by the return compression springs 34, which are arranged in the holes 14a of the gear wheel 14. In the illustrated embodiment, the gear wheel 14 has three holes 14a, which are at the same angular distance from each other. The upper end of the compression springs 34 rests on the annular extension of the gear wheel 14 directed towards the inside of the hole, and the lower end rests on the extension of the hole directed towards the outside of the hole corresponding to a bushing 35 inserted into the hole 14a, which thus forms an annular gap with the inner circumference of the hole 14a, which receives the return compression spring 34. The gear wheel 14 is connected to the pressure plate 22 via the bushings 35 by a screw 36 extending through the bushing 35 and screwed into the pressure plate 22. The bushings 35 are held in their bores 14a so that they can be moved axially.Opposite the holes 14a, holes 37 are machined into the locking disk 17, which holes are extended in the circumferential direction opposite the circular holes 14a at both ends in accordance with the rotational play of the locking disk 17 of approximately 15°. In the driving position of the driving pins 16, particularly as shown in FIG. 5, the lower ends of the sleeves 35 are in the holes 37 of the locking disc 17, and their upper ends are in a plane common with the upper, horizontal annular surface of the gear wheel 14. In this operating state, the pressure plate 22 is also in this plane. During the above-described lifting movement of the driving pins 16, when the pressure plate 22 is driven, the sleeves 35 compress the return pressure springs 34 and move upwards to the position shown in FIG. 7. During the downward movement of the driving pins 16, the return pressure springs 34 are relieved and return the pressure plate 22 to the position shown in FIG. 5. At the same time, the coupling pins 23 are pulled out of the elongated holes 26 of the drive ring 25. The braking system is then deactivated. The gear 3, enclosed in the gear housing 3a, is lubricated with liquid. There is a plain bearing 38 between the upper housing part 30 and the drive ring 25.

Claims

PATENT CLAIMS 1. A reaping device with a reaping tool (1) rotating around a vertical axis, which can be driven via a gear (3) containing a freewheel (10) and arranged in a gear housing (3a) by a drive shaft (8) connected in a rotational manner with the freewheel (10), by means of drive pins (16), which create a connection between the freewheel (10) and the reaping tool (1) that is perpendicular in the basic direction parallel to the axis of rotation of the reaping tool (1), and can perform a lifting movement together with the freewheel (10) when the drive shaft (8) is stationary. It is designed to interrupt the driving connection between the harvesting tool (1) and the freewheel (10), characterized in that the driving pins (16) during their lifting movement activate a braking device consisting of a brake disc (27) and counter-brake discs (28, 29), which is formed on the inner side of the gear housing (3a), above the freewheel (10).

2. Harvesting device according to claim 1, characterized in that an annular pressure plate (22) is arranged on the upper side of the drive pins (16), which, during the lifting movement of the drive pins (16), works against the braking device consisting of a brake disc (27) and counter-brake discs (28, 29) on the inner side of the gear housing (3a).

3. Harvesting device according to claim 1 or 2, characterized in that the braking device consisting of the brake disc (27) and the counter-brake discs (28, 29) is designed to be flexibly adjustable in order to generate different braking torques.

4. Harvesting device according to any one of claims 1-3, characterized in that the braking device comprises an annular horizontal brake disc (27), which is rigidly connected on its inner circumference to a drive-side drive ring (25), and which is guided with its outer circumference in an annular gap between two horizontal counter-brake discs (28, 29) on the housing side. HU 221 260 Β1 5. Harvesting device according to any one of claims 13, characterized in that the braking device consisting of the brake disc (27) and counter-brake discs (28, 29) comprises an annular brake disc curved in accordance with the inner circumference of the gear housing (3a), which can be connected to a drive member of the harvesting tool (1) and can be brought into braking engagement with the counter-brake surface on the inner circumference of the gear housing (3a).

6. Harvesting device according to any one of claims 2-5, characterized in that the pressure plate (22) is connected to the braking device consisting of the brake disc (27) and counter-brake discs (28, 29) by vertical coupling pins (23) arranged at a certain distance from each other in the circumferential direction.

7. Harvesting device according to claim 6, characterized in that the coupling pins (23) are held in the pressure plate (22) in a spring-loaded manner in the direction of the brake device consisting of a brake disc (27) and counter-brake discs (28, 29).

8. Harvesting device according to claim 7, characterized in that to perform the braking process, the coupling pins (23) can engage in the circumferential longitudinal holes (26) of the drive ring (25) holding the brake disc (27).

9. Harvesting device according to any one of claims 1-8, characterized in that a locking disc (17) is arranged on the horizontal upper side of the ring disc (10a) of the freewheel (10), which locks the drive pins (16) in their braking position at the end of their upward lifting movement.

10. Harvesting device according to claim 9, characterized in that the locking disc (17) is mounted on a drive member of the harvesting tool (1) so that it can be rotated within a limited angle.

11. Harvesting device according to any one of claims 1-10, characterized in that the braking device consisting of the brake disc (27) and counter-brake discs (28, 29) can be automatically released by lowering the pressure plate (22) when the drive of the harvesting device is reactivated.

12. Harvesting device according to claim 11, characterized in that the lowering of the pressure plate (22) and the associated downward movement of the drive pins (16) into their driving position are assisted by a spring.