Drive unit for a grain elevator and grain elevator arrangement

Abstract

A drive unit for a grain elevator, in particular for agricultural machines, has a drive wheel operatively connected to a screw conveyor for conveying crop into the grain elevator. The drive wheel is provided with retainer means which may be engaged in a positive locking and/or friction-type connection with a continuous tension means of the grain elevator provided with one or more paddles so as to drive the continuous tension means. Several openings are provided in the drive wheel between the arms holding the retainer means in such a way that this allows or facilitates crop conveyed by the screw conveyor into the grain elevator along a direction of conveyance to flow through the drive wheel.

Claims

1. A drive unit (1) for a grain elevator (2), comprising a drive wheel (5) which is operatively connected to a screw conveyor (3) for conveying crop into the grain elevator (2), said drive wheel (5) comprising retainer means (11; 10c) which can be brought into positive locking and/or friction-type engagement with a continuous tension means (6a; 6b) of said train elevators (2) comprising several paddles (8) for driving said continuous tension means (6a; 6b), wherein in said drive wheel (5), between said arms (10) holding said retainer means (11; 10c), several openings (13) are provided so as to enable and/or facilitate crop conveyed through said screw conveyor (3) into said grain elevator (2) along a direction of conveyance (F) to flow through said drive wheel (5).

2. The drive unit (1) according to claim 1, wherein said drive wheel (5) comprises pins (11) having a rounded and/or bevelled and/or rectangular cross section as retainer means, said pins being held by the arms (10) on their perimeter, and wherein gaps (14) are provided between said pins (11), so that cams (7a) of a continuous tension means designed as a cam belt (6a) can positive lockingly engage with said gaps (14) in order to retain said cams (7a) by means of the powered drive wheel (5) to thereby drive said cam belt (6a) of said grain elevator (2), or a continuous tension means designed as a flat belt (6b) can friction-type engage with said pins (11) so as to retain said flat belt (6b) to thereby drive said flat belt (6b) of said grain elevator (2).

3. The drive unit (1) according to claim 1, wherein said arms (10) of said drive wheel (5) are provided each with a re-shaped end (10c), said re-shaped ends (10c) form said retainer means, said re-shaped ends (10c) each being disposed on the same perimeter and a gap (14) being formed between adjacent re-shaped ends (10c), so that cams (7a) of a continuous tension means designed as a cam belt (6a) can positive lockingly engage with said gaps (14) in order to retain said cams (7a) by means of the powered drive wheel (5) to thereby drive said cam belt (6a) of said grain elevator (2), or a continuous tension means designed as a flat belt (6b) can friction-type engage with said re-shaped ends (10c) so as to retain said flat belt (6b) to thereby drive said flat belt (6b) of said grain elevator (2).

4. The drive unit (1) according to claim 2, wherein said gaps (14) are connected to said openings (13) so as to prevent crop getting jammed between said continuous tension means (6a; 6b) and said drive wheel (5).

5. The drive unit (1) according to claim 1, wherein said arms (10) are designed flat whereby lateral faces (10b) of the arms (10) are aligned in parallel or angled in relation to the direction of conveyance (F) of the crop and extend starting from a hub (9) of said drive wheel (5) outwards in a radial direction and are connected, at the outer ends (10a) of which, to at least on of said retainer means (11; 10c).

6. The drive unit (1) according to claim 5, wherein said lateral faces (10b) of said arms (10) are distorted about an angle () of between 5 and 75, preferably 65, in particular, corresponding to a helical gearing (3a) of the screw-type screw conveyor (3) in relation to a longitudinal axis (A) running through said hub (9) of said drive wheel (5) so as to facilitate conveyance of the crop through said openings (13) of said drive wheel (5).

7. The drive unit (1) according to claim 5, wherein said arms (10) are additionally distorted.

8. The drive unit (1) according to claim 1, wherein said arms (10) are provided with a rounded and/or bevelled and/or rectangular cross sectional surface and extend starting from a hub (9) of said drive wheel (5) outward in a radial direction and are connected, at the outer ends (10a) of which, to at least on of said retainer means (11; 10c).

9. The drive unit (1) according to claim 1, wherein a unit comprising said arm (10) and retainer means (11; 10c) connected thereto form an L-shape or a T-shape whereby, to that end, the respective retainer means (11, 10c) protrudes on one side or both sides in an axial and/or radial direction from said arm (10).

10. The drive unit (1) according to claim 1, wherein said retainer means (11) tapers in an axial direction towards the outside.

11. The drive unit (1) according to claim 1, wherein guide ribs (15) angled and/or distorted in relation to a longitudinal axis (A) running through said hub (9) of said drive wheel (5) are arranged in the region of said openings (13) so as to facilitate conveyance of the crop through said openings (13) of said drive wheel (5).

12. The drive unit (1) according to claim 1, wherein said openings (13) make up for a share of between 30% and 85%, preferably 65%, of the surface covered by said drive wheel (5).

13. The drive unit (1) according to claim 1, wherein a hub exterior (9a) of said hub (9) of said drive wheel (5) is designed, at least in part, to be sloped in an axial direction, said hub exterior (9a), at least in part, in a first region of said hub (9) facing said screw conveyor (3), being designed as sloped axially outwards towards said screw conveyor (3) so as to prevent blocking of crop in front of said drive wheel (5).

14. The drive unit (1) according to claim 1, wherein a hub exterior (9a) of said hub (9) of said drive wheel (5) is designed, at least in part, to be sloped, said hub exterior (9a), at least in part, in a second region of said hub (9) facing away from said screw conveyor (3), being designed as sloped axially outwards away from said screw conveyor (3) so as to prevent jamming of crop in said drive wheel (5).

15. The drive unit (1) according to claim 1, wherein said drive wheel (5) further comprises at least one washer disc (12) connected at its end to said retainer means (11; 10c), said washer disc (12) protruding outwards in a radial direction beyond said retainer means (11; 10c) in such a way that a continuous tension means (6a; 6b) mounted on said drive wheel (5) is guided in an axial direction.

16. The drive unit (1) according to claim 15, wherein retainer means (11) are disposed on said washer disc (12) which are not directly held by one of said arms (10), said retainer means (11) being disposed on the same perimeter as the retainer means (11) directly held by said arms (10).

17. The drive unit (1) according to claim 1, wherein guide cams (16) protruding radially outwards are disposed on said retainer means (11; 10c), said guide cams (16) being able to engage in openings (17) on said tension means (6a; 6b) for synchronizing said drive wheel (5) and said tension means (6a; 6b).

18. The drive unit (1) according to claim 1, wherein said drive wheel (5) is mounted, resistant against rotation, on a shaft (4) of said screw conveyor (3).

19. The grain elevator arrangement (20), comprising a grain elevator (2) and the drive unit (1) according to claim 1, said drive wheel (5) of said drive unit (1) engaging with said continuous tension means (6a; 6b) of said grain elevator (2) in friction-type and/or a positive locking connection in such a way that any rotation of said screw conveyor (3) as well as said drive wheel (5) operatively connected thereto also drives said continuous tension means (6a; 6b), whereby, hereby, crop conveyed by said screw conveyor (3) into said grain elevator (2) may be conveyed by said paddles (8) on said continuous tension means (6a; 6b) through said grain elevator (2), whereby said several openings (13) enable and/or facilitate a flow of crop conveyed by said screw conveyor (3) into said grain elevator (2) through said drive wheel (5).

20. The grain elevator arrangement (20) according to claim 19, wherein said continuous tension means is designed as a cam belt (6a) provided with cams (7a) and gaps (7b) located in-between, said cams (7a) being able to engage with said gaps (14) between said retainer means (11; 10c) in a positive locking manner so as to retain said cams (7a) of said cam belt (6a) by said powered drive wheel (5) to thereby drive said cam belt (6a) of said grain elevator (2).

21. The grain elevator arrangement (20) according to claim 19, wherein said continuous tension means is designed as a flat belt (6b) being frictionally engaged with said retainer means (11; 10c) of said drive wheel (5) so as to retain said flat belt (6b) to thereby drive said flat belt (6b) of said grain elevator (2).

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0030] The Invention will be further illustrated below by means of embodiment examples. The following is shown:

[0031] FIG. 1 perspective views of a drive unit for a grain elevator;

[0032] FIG. 2 a detailed view of a drive wheel on a screw conveyor;

[0033] FIG. 3 a detailed view of the drive wheel according to FIG. 2;

[0034] FIG. 4, 5, 6a, 6b alternative embodiments of the drive wheel of the drive unit according to the invention.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS

[0035] According to FIG. 1 a drive unit 1 for a grain elevator 2 is shown, said grain elevator 2 serving to transport crop, e.g. corn or cereal grains, conveyed via a screw conveyor 3 with helical gearing 3a in the direction of a grain tank not shown here. To that end the screw conveyor 3 is rotated by a drivenot shownat a pre-determined velocity via a shaft 4 about a longitudinal axis A so that the crop is conveyed via the helically distorted gearing 3a of the screw conveyor 3 in the direction of the grain elevator 2 (direction of conveyance F). Hereby, the grain elevator 2 and the drive unit 1 together form a grain elevator arrangement 20 according to the invention.

[0036] In order for crop entering the grain elevator 2 in a lower region 2a to be held inside this and conveyed upwards in the direction of the grain tank (see arrow B), the grain elevator 2 is surrounded by a housing 2b. The housing 2b encloses the grain elevator 2 hereby comprising, in particular a discharge port 2c so that crop may be transported from the screw conveyor 3 along the direction of conveyance F into the lower region 2a. For cleaning and/or maintenance purposes the housing 2b may also be opened at the appropriate locations via a hatchnot shown here.

[0037] A drive wheel 5 is mounted on the shaft 4 of the screw conveyor 3 fixed against rotation so that any rotation of the screw conveyor 3 automatically also causes rotation of the drive wheel 5. To that end, the shaft 4 of the screw conveyor 3 protrudes into the lower region 2a of the grain elevator 2 in such a way that, according to this embodiment, a continuous cam belt 6a (continuous tension means) of the grain elevator 2 can be mounted on the drive wheel 5. The cam belt 6a comprises cams 7a at pre-determined spacings which are separated by gaps 7b and which are in positive locking engagement with the drive wheel 5 in such a way that, when the cam belt 6a is taut, any rotational movement of the powered drive wheel 5 is transmitted to the cam belt 6a. Hereby, a torque can be transmitted from the powered screw conveyor 3 via the drive wheel 5 also to the cam belt 6a so as to also drive the grain elevator 2. The cam belts 6a are usually made of networked polymer reinforced by fabric inlays.

[0038] Alternatively to the cam belt 6a a flat belt 6b, not shown for this embodiment example, can be mounted as continuous tension means on the drive wheel 5 according to FIG. 1 to operate the grain elevator 2. The transmission of the torque from the screw conveyor 3 to the flat belt 6b then happens, in particular, by means of frictional engagement between the drive wheel 5 and the flat belt 6b. An embodiment example comprising a flat belt 6b is shown in FIG. 6b, the description of which will be given below.

[0039] In order to effect conveyance of crop through the grain elevator 2 so-called paddles 8, i.e. retainer arms, are mounted on the cam belt 6a at pre-determined spacings, said paddles being designed as plates according to FIG. 1 and extend approximately perpendicularly from the cam belt 6a towards the outside. These occupy the space in the housing 2b of the grain elevator 2 at least in part in such a manner that crop coming from the screw conveyor 3 into the lower region 2a of the grain elevators 2 can be transported via the paddles 8 upwards (arrow B) in the direction of the grain tank when the cam belt 6a is driven be the drive wheel 5. The arrangement and function of the paddles 8 in the case of a continuous tension means designed as a flat belt 6b (s. FIG. 6b) is similar.

[0040] According to FIG. 2 the drive unit 1 is shown with the drive wheel 5 and the screw conveyor 3 in a detailed view. The drive wheel 5 is mounted, resistant against rotation, via its hub 9 on the shaft 4 so that the drive wheel 5 rotates together with the screw conveyor 3 about the longitudinal axis A. On its perimeter the drive wheel 5 is provided with several pins 11 as retainer means, said pins 11 are spaced apart at a distance corresponding to the partitioning of the cam belt 6a so that the pins 11 can positive lockingly engage with the gaps 7b created between the cams 7a thereby allowing slip-free driving of the cam belt 6a.

[0041] From a hub exterior 9a of the hub 9 several flat arms 10 project in a radial direction ab whereby a part of the pins 11 is affixed to outer ends 10a of the arms 10. Further, pins 11 are disposed on the same perimeter of the drive wheel 5, said pins, however, not being held in their position directly via one of the arms 10. Rather, the further pins 11 are held via two washer discs 12 disposed on the ends which are firmly attached to the pins 11 held by the arms 10 so that the further pins 11 are connected at least indirectly via the washer disc 12 also to the arms 10 and the hub 9. According to this embodiment example, merely every other pin 11 is connected directly via an arm 10 to the hub 9. However, versions are conceivable where, depending on the number of pins 11, material and load, only each third or each fourth pin 11 is connected via an arm 10 to the hub 9. Thus, the number of arms 10 may be reduced, for example, to three or merely two.

[0042] This bears the advantage that the drive wheel 5 is designed more open as a whole because larger openings 13 for conveyed crop can be created between the arms 10 (see dotted line in FIG. 2). Thus, the crop is obstructed to a lesser extend by the drive wheel 5 during a process of conveyance and is able to flow mostly unimpeded into of through respectively the grain elevator 2. Hereby, the covered surface (cross sectional surface) of the openings 13 approximately corresponds to between 40 and 85% of the total surface covered by the drive wheel 5 (cross sectional surface). This at the same time guarantees a transmission of power onto the cam belt 6a via a sufficient number of pins 11 with major loads thereby avoiding slippage of the cams 7a at high loads.

[0043] Besides positioning and holding a part of the pins 11 the washer discs 12 have the task to avoid axial slippage of the cam belt 6a on the drive wheel 5, i.e. the washer discs 12 act as lateral stop for the cam belt 6a or, respectively, as belt guide on the auf drive wheel 5.

[0044] The pins 11 of the drive wheel 5 also form a type of toothed wheel because the cams 7a of the cam belt 6a mounted on the drive wheel 5 can engage in gaps 14 between the pins 11 and the pins 11 itself can engage in the gaps 7b between the cams 7a in a positive locking manner and the cams 7a are retained by the pins 11 when the drive wheel 5 is powered. This drives the cam belt 6a or, respectively, the grain elevator 2 so as to convey crop into the grain tank. When using a flat belt 6b as continuous tension means this will be driven, in particular, by means of a friction-type connection between the pins 11 and the flat belt 6b so that hereby, too, the grain elevators 2 can be operated (compare FIG. 6b).

[0045] Using the gaps 14 between the pins 11 also helps to reduce the region or the surface respectively in which crop can get jammed between the drive wheel 5 and the Cam belt 6a. The rounded, in particular round or perhaps even oval cross sectional surface of the pins 11 supports this because the crop does not stay on the pins 11 when the drive wheel 5 rotates and, therefore, is not or only slights crushed between the cam belt 6a or, respectively, the gaps 7b and the pins 11 leading to very little crop damage The same applies when using a flat belt 6b.

[0046] In order to support the process of conveyance of crop through the openings 13 of the drive wheel 5, according to the embodiment in the FIGS. 1 through 3, lateral faces 10b of the arms 10 are angled in relation to the der longitudinal axis A or, respectively, the direction of conveyance F, for example, about an angle of between 5 and 75, preferably about 65. Hereby, the angle corresponds approximately to the angle of the helical gearing 3a of the screw-type screw conveyor 3 so that the helical gearing 3a of the screw conveyor 3with one interruptionis virtually continued in the drive wheel 5 so that the flowing properties of the crop in both elements 3, 5 are similar. In addition, a torsion may be introduced into the arms 10. Hereby, the conveyed crop, which upon entering the grain elevator 2 is essentially conveyed in a direction of conveyance F parallel to the longitudinal axis A, upon rotation of the drive wheel 5 is additionally pressed or guided out of the openings 13 towards the opposite side of the drive wheel 5, similar to a pumping action or an axially conveying impeller wheel or worm wheel, to further optimise the conveyance process.

[0047] This is further supported by the hub exterior 9a being bevelled towards both sides in such a way that crop coming from the screw conveyor 3 is not build up behind a strongly sloping step or edge in the region of the shaft 4 or the hub 9 respectively while, at the same time, crop getting jammed in the openings 13. Thus, the bevelled hub exterior 9a allows for unimpeded conveyance of crop even in and through the drive wheel 5.

[0048] Hereby, the hub exterior 9a in a first region 9b of the hub 9 next to the screw conveyor 3 is designed as sloping towards the screw conveyor 3 so as to avoid a step. This first region 9b merged in the direction away from the screw conveyor 3 into a directly adjacent second region 9c with the second region 9c rising towards the screw conveyor 3 or, respectively, sloping in die opposite direction. This avoids crop getting wedged in the openings 13.

[0049] According to a further embodiment example of the drive wheel 5, shown in FIG. 4, no washer discs 12 are present and each pin 11 is associated one arm 10 each. In this embodiment example, the drive wheel 5 is also mounted resistant to rotation on the shaft 4. Starting at the hub 9 of the drive wheel 5 for each pin 11 always one radially protruding arm 10 is provided which is connected to the pin 11 running in parallel to the longitudinal axis A as a retainer means or, respectively, merges into this so that always the arm 10 and the pin 11 each form an L-shaped unit. To that end, the arm 10 can be produced. for example as a single piece together with the pin 11 where both the arm 10 and the pin 11 exhibit a rounded, in particular round or perhaps even oval cross section so as to convey the crop with as little disturbance as possible. Here, too, a gap 14 is created between the pins 11 which is connected to the openings 13 and can positive locklingly engage with the cams 7a of the cam belt 6a. It is also possible to mount a flat belt 6b so as to use this to drive a friction-type connection.

[0050] Further, according to the embodiment example in FIG. 4, in addition to the arms 10 guide ribs 15 are provided extending starting from the hub 9 radially outwards and having the same function as the angled arms 10 in the embodiment example according to the FIGS. 1 through 3. To that end, the guide ribs 15 are angled and/or distorted and ensure that the crop coming from the screw conveyor 3 is guided or conveyed respectively in a pump-type manner through the drive wheel 5 with as little disturbance as possible. In addition to the connection to the hub 9, the guide ribs 15 are partially connected to the arms 10 and/or the pins 11 so that the stability of the drive wheel 5 is increased overall. Hereby, the shape of the guide ribs 15 may be adapted to the shape of the helical gearing 3a of the screw conveyor 3 so that the conveyance of crop in the drive wheel 5 happens in a way mostly similar to that in the screw conveyor 3 and, thus, the flow properties in both units are adapted to each other.

[0051] According to FIG. 4, the open design of the drive wheel 5 is also continued, with the washer discs 12 being omitted thereby reducing the jamming surface for the conveyed crop. According to this embodiment example, too, it is provided for the hub exterior 9a to be sloped so that the crop pass into the drive wheel 5 and through the helical guide ribs 15 unimpeded for the most part. According to this embodiment example, however, for guiding the mounted cam belt 6a a washer disc 12 may be provided in principle.

[0052] According to a further embodiment of the drive wheel 5, shown in the FIG. 5, the drive wheel 5 comprises flat arms 10 the outer ends 10b of which are always designed as re-shaped ends 10c, hereby, in accordance with this embodiment, being half open or bent in a u-shaped manner respectively. The bent ends 10c increase the contact surface of the outer ends 10b and serves as retainer means for retaining the continuous tension means 6a, 6b which can be mounted thereon in a friction-type or positive locking manner. The openings 13 according to the invention and, at the same time, also the gaps 14 are created between the arms 10 re-shaped at the ends so this also enables and/or facilitates the flow of crop conveyed by the screw conveyor 3 into the grain elevator 2 through the drive wheel 5.

[0053] Hereby, the lateral faces 10a which, according to this embodiment, are aligned in parallel to the direction of conveyance F ensure that the crop can flow through the drive wheel 5 unimpeded. In principle, the lateral faces 10a of the arms 10 in this embodiment may, at least in part, be also angled in relation to the direction of conveyance F and/or distorted, in a way similar to the embodiment example according to FIG. 3.

[0054] According to a further embodiment of the drive wheel 5, shown in FIG. 6a, it is provided for the arms 10 to have a rectangular cross section with rounded edges and for these to always merge into a pin 11 as retainer means also having a rounded cross section. The respective pin 11 protrudes away towards both sides in an axial direction from the respective arm 10 thereby and tapering slightly axially towards the outside. Thus, a unit made from the arm 10 and the pin 11 designed as a T-shape. A gap 14 is created between the pins 11 of adjacent arms 10 and the openings 13 according to the invention between adjacent arms 10. According to the variation shown in FIG. 6a, a cam belt 6b with cams 7a and in-between gaps 7b is mounted on the so designed drive wheel 5 so as to maintain positive locking and friction-type engagement between the two.

[0055] FIG. 6b shows approximately the same embodiment of the drive wheel 5 as in FIG. 6a with the difference that the drive wheel 5 receives a flat belt 6b, in particular, in friction-type engagement, i.e. the flat belt 6b is driven mainly by means of friction. To ensure driving the flat belt 6b drive cams 16, each protruding radially towards the outside, are provided on the pins 11 which cams engage in the flat belt 6b in central openings 17. The openings 17 are designed as elongated holes and serve to optimise the transmission of power from the drive wheel 5 to the flat belt 6b by preventing, by means of the drive cams, slippage of the flat belt 6b driven purely by friction under high load 16. This guarantees a synchronous run between the two. Furthermore, the drive cams 16 may be used to support guidance so that the flat belt 6b does not get displaced in an axial direction in relation to the drive wheel 5.

[0056] In principle, the guide cams 16 may be used also in the embodiments having a cam belt 6a so as to support here, too, a synchronous run as well as to enable axial guidance.

LIST OF REFERENCE NUMERALS

[0057] 1 drive unit [0058] 2 grain elevator [0059] 2a lower regions of the grain elevator 2 [0060] 2b housing [0061] 3 screw conveyor [0062] 3a helical gearing of the screw conveyor 3 [0063] 4 shaft [0064] 5 drive wheel [0065] 6a cam belt [0066] 6b flat belt [0067] 7a cams [0068] 7b gaps [0069] 8 paddle [0070] 9 hub [0071] 9a outer side of hub [0072] 9b first region of the outer side of hub 9a [0073] 9c second region of the outer side of hub 9a [0074] 10 arm [0075] 10a outer ends of the arm 10 [0076] 10b lateral face of the arm 10 [0077] 10c re-shaped ends of the arm 10 [0078] 11 pin [0079] 12 washer disc [0080] 13 passage openings [0081] 14 gap [0082] 15 guide ribs [0083] 16 drive cams [0084] 17 openings [0085] 20 grain elevator arrangement [0086] A longitudinal axis [0087] angle [0088] B direction of conveyance through grain elevator [0089] F direction of conveyance before grain elevator