• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    A conveyor rotor (30) comprises: a number of conveyor disks (44) arranged next to one another in the axial direction, around the circumference of which several prongs (45) are distributed, a rotationally drivable input shaft (64), a first shaft (64) coupled to the input shaft (64) 74), to which a first conveyor disk (44 ') is coupled, and an adjusting gear (60) which is coupled to the drive shaft (44) and a second shaft (84) and which transmits the second shaft (84) to the drive shaft (64). connects and comprises an adjusting member with which the second shaft (84) is angularly adjustable relative to the first shaft (74), a second conveyor disk (44 ") being coupled to the second shaft (84).
    公开号:BE1023765B1
    申请号:E2015/0261
    申请日:2015-11-26
    公开日:2017-07-14
    发明作者:Marco Broschart
    申请人:Deere & Company；
    IPC主号:
    专利说明:

    Promotional rotor especially for use in an agricultural
    harvester
    description
    The invention relates to a conveyor rotor, in particular for use in an agricultural harvester.
    BACKGROUND ART Conveyor rotors are used in various agricultural harvesting machines for conveying crops, for example in baling presses or loading wagons for crop conveying downstream of a pickup (cf., for example, DE 100 17 984 A1) or in combines as conveyors in a multi-drum threshing mechanism (see DE 10 2012 210 649 A1). Such conveyor rotors comprise a central shaft or drum, to which a number of conveyor discs are fixed in the axial direction, around the circumference of which a plurality of prongs are distributed. Adjacent discs are usually offset from each other in the circumferential direction, so that the tines form several helical coils around the conveyor rotor.
    task
    Since the conveyor discs are rigidly attached to the conveyor rotor in the prior art, the shape of the helical coils is fixed. However, applications are conceivable in which it may be advantageous to change this shape.
    invention
    The present invention is defined by the claims.
    A conveyor rotor comprises a number of conveyor discs arranged in the axial direction next to each other, around whose circumference a plurality of tines are distributed, a rotatably driven input shaft, a first shaft coupled to the input shaft to which a first conveyor disc is coupled, and one to the drive shaft and a second one A shaft coupled adjusting gear, which rotatably connects the second shaft to the drive shaft and includes an adjusting member with which the second shaft is angularly adjustable relative to the first shaft, wherein a second conveyor disc is coupled to the second shaft.
    In other words, the first and second shafts are driven by the input shaft, wherein the second shaft is angularly adjustable relative to the first shaft by the adjusting mechanism. In this way, it is possible, during operation and / or at a standstill by the adjusting member to adjust the adjusting mechanism such that the second shaft and with it the second conveyor disc with respect to the first shaft and the first conveyor plate angle-adjusted, i. phase-shifted. This allows the second conveyor disc of the first conveyor disc forward or lag or be the same orientation with her, so that the slope of the helix defined by the adjacent tines can be changed arbitrarily. The adjustment of the adjusting can be accomplished manually or by an automatic to adapt the conveyor rotor to its conditions of use. Thus, for example, a detected by a sensor, non-uniform lateral loading of the conveyor rotor can be compensated with Emtegut, in this case by an automatic control, the pitch of the coil is placed in the direction of the smaller load, to promote there more crop.
    In a preferred embodiment, a third conveyor disc is arranged between the first conveyor disc and the second conveyor disc, which is coupled torque-transmitting by a transmission mechanism to the first conveyor disc and second conveyor disc, which has a relatively adjusted by the adjusting relative displacement of the second conveyor disc with respect to the first conveyor plate stocky the third conveyor transmits. The helix is then formed by the three conveyor discs, of which the middle (third) conveyor disc is oriented in a central intermediate position between the first and second conveyor disc. The reduction is chosen in particular so that the third conveyor disc takes part in the rotation of the second conveyor disc in half, if a total of three conveyor discs are present. If a total of n conveyor disks are present, the conveyor disks arranged between the first and second conveyor disks are respectively rotated by 1 / (n-1) of the adjustment angle of the second conveyor disk.
    Furthermore, a further conveyor disc between the first conveyor disc and the third conveyor disc and / or between the third conveyor disc and the second conveyor disc can be arranged and coupled by the transmission mechanism with the adjacent conveyor discs, the one accomplished by the adjusting relative adjustment between two conveyor discs in half on the arranged between them, transmits further conveyor disc. In this embodiment, further (ie, fourth, fifth, sixth, seventh, etc.) conveyor discs are added between the first and third conveyor discs and third and second conveyor discs, all coupled to transfer mechanisms comprising the conveyor discs disposed between the first and second conveyor discs brings into a central intermediate position between the two conveyor discs, between which the respective conveyor disc is arranged. This gives the mentioned, formed by the tines of the conveyor discs coil.
    The transmission mechanism may include a first lever pivotally coupled to a conveyor disc at a first end, a second lever pivotally connected to another conveyor disc at a first end, and second ends of both levers coupled to each other by a connecting pin. which extends through a radially extending slot in a disposed between said conveyor discs conveyor disc.
    The adjusting mechanism may comprise a planetary gear, the ring gear is coupled to the adjusting member and the planet carrier is drivingly connected to the input shaft and the sun gear with the second shaft.
    The adjusting gear can also comprise a planetary gear, the ring gear is fixed to the housing and the planet carrier is drivingly connected to the input shaft and the sun gear to the first shaft.
    The conveyor rotor may be used in any harvester for crop conveying, e.g. in a combine harvester or baler or a loader wagon.
    Ausführunasbeispiel
    In the drawings, an embodiment of the invention described in more detail below is shown, wherein the reference numerals must not be used to a restrictive interpretation of the claims. It shows:
    1 is a schematic side view of a combine harvester with a multi-drum thresher,
    2 is a perspective view of the conveyor rotor of the multi-drum thresher,
    3 is a plan view of the conveyor rotor,
    4 is an exploded view of three conveyor discs of the conveyor rotor,
    5 is a side plan view of the conveyor discs of Figure 4,
    6 is a schematic diagram of the variable transmission of the conveyor rotor,
    Fig. 7 is a perspective view of the conveyor rotor in one in a first
    Endstellstell Asked adjusting, in which the tines form a helix with a relatively large pitch,
    Fig. 8 is a perspective view of the conveyor rotor in one in a second
    Endstellstell Asked adjusting, in which the tines form a helix with a relatively large pitch, but in opposite direction to Figure 7,
    9 is a perspective view of the conveyor rotor in one in a
    Intermediate position between the positions of Figure 8 and Figure 10 Asked adjusting, and
    Fig. 10 is a perspective view of the conveyor rotor in a set in a neutral center position adjustment, in which the tines are oriented in parallel.
    1 shows a self-propelled combine harvester 10 with a frame 12 which is supported by driven front wheels 14 and steerable rear wheels 16 on the ground and is moved away from them. The wheels 14 are rotated by means not shown driving means to drive the combine 10 e.g. to move over a field to be abandoned. In the following, directional details, such as from the rear and the rear, relate to the direction of travel V of the combine harvester 10 in harvesting operation. The combine harvester 10 shown is an application example of the conveying rotor 30 according to the invention, which could also be used on other types of harvesting machines, in particular as a loading rotor in a baling press or a loading wagon.
    At the front end portion of the combine harvester 10, a crop gathering device 18 is detachably connected in the form of a cutter to harvest harvested crops in the form of crops or other threshable culottes from the field and feed them up and down by a feeder 20 to a multi-drum threshing unit. which - arranged one behind the other in the direction of travel V - comprises a threshing drum 22, a stripping drum 24, a conveyor rotor 30 operating with superficial action, a separating drum 28 and a discharge conveyor 26. Downstream of the discharge conveyor 26 is a straw shaker 32. The threshing drum 22 is surrounded by a concave 34 in its lower and rear regions. Above the conveyor rotor 30 is a fixed cover and below the Abscheidetrommel 28 a separating basket 36 with adjustable finger elements. Below the unterzuschächtig conveying discharge conveyor 30, a separation grate 38 is arranged. A scraper 35 is on the discharge side below the conveyor rotor 30 upstream of the inlet region of the separation drum 28. The separating basket 36 is equipped in its central region with conventional squeegee blades 37 and in its inlet and outlet areas with finger rake 39.
    The conveying rotor 30 is shown in FIG. 2 in a perspective view. It comprises a number (in the illustrated embodiment 20) conveyor discs 44, which are arranged on a first, central, rotatably driven shaft 74 and held by circular cylindrical, attached to one side of the conveyor discs 44 spacers 54 spaced from each other. The conveyor discs 66 each comprise five tines 45 distributed about their circumference, although more or fewer tines 45 could be used. The prongs 45 are approximately triangular with radially outer ends and circumferentially symmetrical about a radial centerline. The tines 45 of adjacent conveyor discs 44 (in the position shown in Figures 2 and 3 of Verstellgetriebes 60, which is variable according to Figures 7 to 10) are arranged angularly offset relative to each other, so that the outer ends of the tines 45 of the conveyor rotor 30 respectively one of a total of five imaginary spirals lie.
    The drive of the conveyor rotor 30 takes place via a belt pulley 61, which is connected directly to an input shaft 64, which in turn is connected to the first shaft 74 so as to transmit torque (see FIG. The leftmost in Figures 2, 3 and 7 to 10 shown conveyor disc 44 'is on the left in the mentioned figures drawn, spaced from the pulley 61 and one of these adjacent adjusting 60 end 40 of the first shaft 74 and one with the End 40 connected end plate 42 coupled directly to the first shaft 74. The remaining conveyor discs 44 are freely rotatably mounted relative to the first shaft 74 in the circumferential direction on the first shaft 74. The rightmost drawn conveyor disc 44 "is driven by a second, designed as a hollow shaft shaft 84 from the adjusting 60 ago, within which the first shaft 74 extends. The drive of the conveyor discs 44 and their coupling with each other will be explained below with reference to Figures 4 to 6.
    The first shaft 74 is rotatably mounted on the frame 12 at the first end 40. Between the conveyor discs 44 and the adjusting 60 an intermediate wall (not shown) is arranged so that only the conveyor discs 44 come into contact with the crop flow in the combine 10. Also on the intermediate wall and / or in the adjusting gear 60, a bearing of the first shaft 74 may be mounted.
    Each three adjacent conveyor discs 44 are coupled together in the manner shown in Figures 4 and 5. The conveyor discs 44 each include a central, axial opening 56 through which the first shaft 74 extends and against which the conveyor discs 44 (with the exception of the first conveyor disc 44 ') are freely rotatable. The spacer ring 54 is attached to one side of the conveyor pulley 44. The conveyor discs 44 also include two spaced apart from the axis of rotation, axial bores 52 and aligned with the bores 52, radially extending slots. A first lever 46 is rotatably connected with its first, inner end to the bore 52 of the leftmost in Figure 4 marked conveyor disc 44 about the longitudinal axis of the bore 52, to which serves a pin. A second lever 46 is rotatably connected with its first, inner end to the bore 52 of the right in Fig. 4 drawn conveyor disc 44 about the longitudinal axis of the bore 52, to which serves a further pin. A third pin 48 extends through the slot 50 of the center conveyor disc 44 and is coupled to the second, outer ends of both levers 46, at least one of which is rotatably mounted relative to the third pin 48. The transmission mechanism shown in Figure 4 with the levers 46, the pins, the slot 50 and the holes 52 has the effect that a relative rotation of an outer conveyor disc 44 relative to the other, outer conveyor disc 44 in a relative rotation of the middle, arranged therebetween conveyor disc 44th is implemented, which corresponds to exactly half of the mentioned relative rotation. During this rotation, the third pin 48 moves along the slot 50.
    Each three immediately adjacent conveyor discs 44 of the conveyor rotor 30 are coupled in the manner shown in Figures 4 and 5, so that all conveyor discs 44 of the conveyor rotor 30 are coupled to each other by one of these transmission mechanisms. If the second conveyor disc 44 "of Figures 2 and 3 is thus rotated by an angle α relative to the first conveyor disc 44 'and n (in the illustrated embodiment, n = 20) conveyor discs 44 are disposed therebetween, the individual conveyor discs rotate 44 (with Except the fixed, first conveyor disc 44 ') relative to the respective adjacent conveyor disc 44 by an angle of a / (n-1). In this way it is achieved that by turning the second shaft 84 and the second conveyor disc 44 "relative to the first shaft 74, the helix formed by the tips of the tines 45 is adjustable in the manner shown in Figures 7 to 10. However, the first shaft 74 and the second shaft 84 are driven in operation at the same speeds. A relative rotation of the second shaft 84 relative to the first shaft 74 takes place only when the adjusting 60 by means of an adjusting lever 58, which can be operated manually or by an actuator and from the cab of the combine 10 by the operator or by means of an automatic remote control , is adjusted. This adjustment causes an angular displacement (phase shift) of the second shaft 84 relative to the first shaft 74.
    FIG. 6 shows the structure of the variable-speed transmission 60 in detail. It includes a housing 62 having a central, axial opening through which the input shaft 64 extends. At the opening, the input shaft 64 may be rotatably supported relative to the housing 62. The housing 62 is rigidly connected to the frame 12. Within the housing 62, a first planetary gear with a sun gear 72 is arranged, which is rigidly coupled to the first shaft 74. A sun gear 72 meshing with the planetary gears 70 retaining planet carrier 66 also carries planet wheels 80 of a second planetary gear and is connected to the input shaft 64. The ring gear 68 of the first planetary gear is rigidly mounted on the housing. The sun gear 82 of the second planetary gear meshes with the Planetenrädem 80 and is directly and rotatably coupled to the second shaft 84. The ring gear 76 of the second planetary gear is rotatably supported in the housing 62 and coupled to a worm wheel 78 which extends in the circumferential direction of the ring gear 76. Serving as adjusting worm wheel 78 can be rotated either by a Verstellaktor not shown about its longitudinal axis, or the ring gear 76 is connected directly or via a translation mechanism with the then serving as adjusting lever 58, the worm wheel 78 would be omitted. It would also be conceivable to drivingly connect the adjusting lever 58 to the worm wheel 78 so that a pivoting movement of the adjusting lever 58 about the central axis of the first shaft 74 would result in rotation of the worm wheel 78 about its axis, which in turn would turn the ring gear 76 about the first shaft 74 turns.
    In any case, can be accomplished by adjusting the adjusting the above-described angular displacement of the second shaft 84 relative to the first shaft 74, wherein the rotational movement of the input shaft 64 via the planet 66, the planetary gears 70 and the sun gear 72 to the first shaft 74 and - if necessary with the accomplished angle adjustment - is transmitted via the planetary gears 80 and the sun gear 82 to the second shaft 84.
    It should also be noted that further refinements of the teaching according to the invention are conceivable. Thus, the second shaft 84 could not drive the outermost (in Figure 2 right) arranged conveyor disc 44 ", but a central conveyor disc 44 of the conveyor rotor 30. The outermost conveyor disc 44" would then by a third time (not shown) and a third planetary gear of the variable speed drive (not shown), which corresponds to the second planetary gear of the variable speed drive 60. Thus, the left half of the conveyor rotor 30 could form an adjustable helix of the tines 45 with a first pitch (and pitch direction) and the right half of the feeder rotor 30 a helix having a second pitch (and pitch direction) which is independently adjustable therefrom.
    权利要求:
    Claims (7)
    [1]
    claims
    A conveyor rotor (30) comprising: a plurality of axially adjacent conveyor discs (44) about the periphery of which a plurality of prongs (45) are distributed, a rotatably driven input shaft (64), a first coupled to the input shaft (64) A shaft (74) to which a first conveyor disc (44 ') is coupled, and a variable speed gear (60) coupled to the input shaft (64) and a second shaft (84) for rotationally transmitting the second shaft (84) to the input shaft (84). 64) and comprises an adjusting member, with which the second shaft (84) is angularly adjustable relative to the first shaft (74), wherein a second conveyor disc (44 ") is coupled to the second shaft (84).
    [2]
    2. conveyor rotor (30) according to claim 1, wherein between the first conveyor disc (44 ') and the second conveyor disc (44 ") a third conveyor disc (44) is arranged, the torque transmitting by a transmission mechanism with the first conveyor disc (44') and second conveyor disc (44 ") is coupled, which transmits a by the adjusting gear (60) accomplished relative adjustment of the second conveyor disc (44") relative to the first conveyor disc (44 ') stocky on the third conveyor disc (44).
    [3]
    3. conveyor rotor (30) according to claim 2, wherein a further conveyor disc (44) between the first conveyor disc (44 ') and the third conveyor disc (44) and / or between the third conveyor disc (44) and the second conveyor disc (44 "). arranged and coupled by the transmission mechanism with the adjacent conveyor discs (44), which transmits a by the adjusting gear (60) accomplished relative adjustment between two conveyor discs (44) in half on the interposed, further conveyor disc (44).
    [4]
    4. conveyor rotor (30) according to claim 2 or 3, wherein the transmission mechanism comprises a first lever (46) pivotally connected at a first end to a conveyor disc (44), a second lever (46) having a first end pivotally coupled to another conveyor disc (44) and the second ends of both levers (46) are coupled together by a pin (48) extending through a radially extending slot (50) in a conveyor disc disposed between said conveyor discs (44) (44) extends.
    [5]
    5. conveyor rotor (30) according to any one of the preceding claims, wherein the adjusting mechanism (60) comprises a planetary gear whose ring gear (76) is coupled to the adjusting member and the planet carrier (66) with the input shaft (64) and the sun gear (82) is drive connected to the second shaft (84).
    [6]
    6. conveying rotor (30) according to any one of the preceding claims, wherein the adjusting gear (60) comprises a planetary gear, the ring gear (68) is fixed to the housing and the planet carrier (66) with the Eingangswelie (64) and the sun gear (72) with the first Shaft (74) is drivingly connected.
    [7]
    7. An agricultural harvesting machine, for example, combine harvester (10), with a conveying rotor (30) according to any one of the preceding claims.
    类似技术:
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    DE102007015101C5|2016-03-03|Gutaufnehmer with a dependent on the direction of rotation position of the tine carrier
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    DE102012210649B4|2018-01-11|Tangential threshing unit with a conveyor drum and a threshing or separating drum
    EP1495664A1|2005-01-12|Machine for mowing stalk crops
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    DE3211177A1|1982-10-28|LOOSE AND DISTRIBUTION DEVICE ON STRAW TUBE
    DE102015205086B3|2016-08-25|Gear assembly for driving a lower cutting disc and coaxially arranged above conveyor discs mowing and intake device of a machine for mowing stalk-like crop
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    同族专利:
    公开号 | 公开日
    DE102014226267B4|2022-03-03|
    DE102014226267A1|2016-07-07|
    BE1023765A1|2017-07-14|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE19806630A1|1998-02-18|1999-08-26|Claas Selbstfahr Erntemasch|Bale press for agricultural stalk material|
    DE102004061678A1|2004-12-22|2006-07-13|Welger Maschinenfabrik Gmbh|Feed and cutter rotor for round and square balers and front loaders has tines mounted along shaft, radial positions of tines being altered using adjusting system|
    DE102012210649A1|2012-06-22|2013-12-24|Deere & Company|Tangential threshing unit with a conveyor drum and a threshing or separating drum|
    DE10017984B4|2000-04-11|2009-06-04|Maschinenfabrik Kemper Gmbh & Co. Kg|feed rotor|
    US6886312B1|2003-11-07|2005-05-03|Miller-St. Nazianz, Inc.|Compacting rotor for bagging machines|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE102014226267.4|2014-12-17|
    DE102014226267.4A|DE102014226267B4|2014-12-17|2014-12-17|Conveyor rotor for an agricultural harvesting machine|
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