Abstract
The present invention relates to a drive train assembly for driving a working unit with fluctuating power consumption from a drive source, with a unit transmission which converts a driving movement of the drive source into a working movement of the work unit and is connected by a transmission output element to the working unit and is connected by a transmission input element to the drive source, and with a flywheel accumulator for mitigating load impacts and/or power consumption fluctuations, wherein the flywheel accumulator is connected on the output side of the unit transmission to the drive train which runs from the unit transmission to the working unit.
Claims
1. A drive train assembly for driving a working unit with fluctuating power consumption from a drive source, the assembly comprising: a unit transmission configured to convert a driving movement of the drive source into a working movement of the working unit and is connected by a transmission output element to the working unit and is connected by a transmission input element to the drive source, and a flywheel accumulator for mitigating load impacts and/or power consumption fluctuations, wherein the flywheel accumulator is connected on the output side of the unit transmission to the drive train which extends from the unit transmission to the working unit.
2. The assembly of claim 1, wherein the flywheel accumulator is connected to the transmission output element and which is simultaneously connected the working unit.
3. The assembly of claim 1, wherein the transmission output element comprises a gear wheel configured to drive a crank leading to the working unit and, wherein the gear wheel is configured to engage with a connecting element for connecting the flywheel accumulator.
4. The assembly of claim 1, wherein two separate drive trains are together at the transmission output element, wherein a first drive train extends from the transmission output element through the unit transmission and via the gear stages thereof to the drive source and a second drive train extends from the transmission output element via the gear stages of the unit transmission to the flywheel accumulator.
5. The assembly of claim 4, wherein the first and second drive trains are each in face-to-face engagement with the transmission output element configured as a gear wheel and extend from the transmission output element on opposite sides.
6. The assembly of claim 5, wherein the first and second drive trains each comprise at least one or more transmission gear stages.
7. The assembly of claim 6, wherein the flywheel accumulator is connected to the transmission output element via at least one transmission gear stage so that the flywheel accumulator is configured to run at a higher speed than the transmission output element.
8. The assembly of claim 7, wherein the transmission gear stage comprises a planetary gear.
9. The assembly of claim 1, further comprising a starting aid for starting up the flywheel accumulator.
10. The assembly of claim 9, wherein the starting aid comprises a motor for supporting the starting up of the flywheel accumulator, and wherein the motor comprises a hydraulic motor or an electric motor.
11. The assembly of claim 10, further comprising an overrunning freewheel between the motor and the flywheel accumulator, wherein the overrunning freewheel is configured to permit relative rotation between the flywheel accumulator and the motor in a first direction of rotation and block a second direction of rotation, wherein the first direction is opposite to the second direction, and wherein the motor is configured to be switched off when the flywheel accumulator is rotating in the first direction.
12. The assembly to claim 1, wherein a shiftable gear comprises a shiftable planetary gear, and wherein the shifting gear is configured to act as a starting aid to support the starting of the flywheel accumulator.
13. The assembly of claim 1, wherein the unit transmission comprises a spur gear stage and an intermediate gear stage between the transmission input element and the transmission output element.
14. A working machine comprising the drive train assembly of claim 1.
15. The machine of claim 14 further comprising a working tool drivable in a reciprocating manner by a crankshaft.
16. The machine of claim 14, which is configured as an agricultural harvesting or soil tillage machine, in particular as a rectangular baler.
17. The machine of claim 14, wherein the machine is configured as an attachment device for attaching to a towing vehicle and wherein the working unit is coupleable to the drive source located on the towing vehicle via the drive train assembly.
18. The machine of claim 15, wherein the machine is configured as an attachment device for attaching to a towing vehicle and wherein the working unit is coupleable to the drive source located on the towing vehicle via the drive train assembly.
19. The machine of claim 16, wherein the machine is configured as an attachment device for attaching to a towing vehicle and wherein the working unit is coupleable to the drive source located on the towing vehicle via the drive train assembly.
Description
BRIEF DESCRIPTION OF THE DRAWINGS
[0042] The invention is explained in more detail below with reference to preferred embodiments and the corresponding drawings. The drawings show:
[0043] FIG. 1: a side view of a working machine with a drive train assembly according to an advantageous embodiment of the invention, wherein the working machine is configured as an agricultural baler, the working unit of which can be driven by the power take-off shaft of a tractor via a cardan shaft;
[0044] FIG. 2: a schematic representation of the drive train assembly of the working machine from FIG. 1, showing the unit transmission for driving the working tool of the working machine and the flywheel accumulator connected on the output side via a separate drive train, the flywheel accumulator being connected via a two-stage planetary gear;
[0045] FIG. 3: a schematic representation of the drive train of the working machine of FIG. 1 according to a further embodiment of the invention, according to which the flywheel accumulator connected on the output side of the unit transmission is connected via a single-stage planetary gear and an intermediate spur gear stage,
[0046] FIG. 4: a schematic representation of the drive train assembly of the working machine of FIG. 1 according to a further advantageous embodiment of the invention, according to which the flywheel accumulator connected on the output side of the unit transmission is connected via a planetary gear and an intermediate gear stage, an auxiliary drive for raising the flywheel accumulator being connected to the planetary gear via a spur gear stage;
[0047] FIG. 5: a side view of the unit transmission of the working machine from FIG. 1, showing the arrangement of the flywheel accumulator relative to the unit transmission;
[0048] FIG. 6: a schematic representation of the power flows during operation of the drive train assembly according to the embodiment example of FIG. 3, wherein the power flow at the highest torque peak is shown, at which a high power flow occurs from the flywheel accumulator to the transmission output wheel of the unit transmission and a low power flow occurs from the drive source into the unit transmission;
[0049] FIG. 7: a representation of the power flows in the drive train assembly according to FIG. 3 during normal operation, in which energy is supplied from the drive source to the flywheel accumulator with simultaneous output of power via the transmission output wheel to the working unit; and
[0050] FIG. 8: a representation of the power flows of the drive train assembly according to FIG. 3 during the starting process of the flywheel accumulator, in which the flywheel accumulator is started up by the start-up motor and the drive train, which leads from the unit transmission to the drive source, is also rotated without torque.
DETAILED DESCRIPTION
[0051] As shown in FIG. 1, the working machine 1 can be configured as an agricultural machine for processing harvested crops or possibly also for soil cultivation, in particular in the form of an attachment device for attachment to a tractor 2.
[0052] The working machine 1 comprises at least one working unit 3, which can be subjected to cyclically strongly fluctuating loads during operation and/or can exhibit cyclically strongly fluctuating power consumption. As shown in FIG. 1, the working machine 1 can be configured in particular as a baler, the working unit 3 of which can comprise a tamper 4 which moves into a bale forming chamber 5 or is cyclically moved back and forth therein in order to press harvested crops picked up from the ground, which have been conveyed into the bale forming chamber 5 via a suitable conveyor device, into bales.
[0053] The working unit 3 is driven by a mechanical drive train assembly 12, which can comprise a cardan shaft 11 that can be connected to the power take-off shaft of the tractor 2 in a rotary test and can be driven by the traction engine of the tractor 2, for example a diesel engine.
[0054] Said drive train assembly 12 comprises a unit transmission 6, which can be connected to the cardan shaft 11 and thus to the engine of the tractor 2 by a transmission input element 15, wherein said transmission input element 15 can be an input shaft of the unit transmission 6.
[0055] The transmission output element 14 of the unit transmission 6, which forms the output side or the output element of said unit transmission 6, can be a crankshaft 7, which drives the tamper 4 of the working unit 3 in a reciprocating manner via a connecting rod 8.
[0056] As shown in FIGS. 2 to 4, said unit transmission 6 can comprise one or more transmission gear stages between its transmission input and output elements 15, 14, which can be configured as transmission or reduction stages. In particular, the unit transmission 6 can comprise a bevel gear stage 24, which can drive the transmission output element 14, in particular said coupling shaft 7, directly or via an intermediate stage 25. The intermediate stage 25 can be a spur gear stage, for example, cf. FIGS. 2, 3 and 4.
[0057] In particular, the transmission output element 14 can have a gear wheel 26, preferably a spur gear, which can be configured in particular as a spur-toothed pinion, wherein said gear wheel 26 is seated on the crankshaft 7 and can be connected thereto in a rotationally fixed manner. Said gear wheel 26 can be driven by said intermediate stage 25 from the drive source 10, i.e. the drive train 9 connected to the power take-off shaft of the tractor 2 drives the output-side gear wheel 26 with the drive power of the tractor 2 or its power take-off shaft via the cardan shaft 11 and the unit transmission 6, which drives the crankshaft 7 in a rotary manner and thus drives the tamper 4 in a reciprocating manner.
[0058] As further shown in FIGS. 2, 3 and 4, a flywheel accumulator 13 is connected to the output side of the unit transmission 6 via a second drive train 17, wherein the second drive train 17 driving the flywheel accumulator 13 or, conversely, driven by it, can be connected in particular to the transmission output element 14 of the unit transmission 6 in the form of the gear wheel 26, so that the kinetic energy coming from the flywheel accumulator 13 can be applied directly to the crankshaft gear wheel 26 for smoothing load impacts of the tamper 4.
[0059] As shown in FIGS. 2 to 4, the second drive train 17 can be connected to the crankshaft gear wheel 26 of the unit transmission 6 via a spur gear stage 27.
[0060] The spur gears 29 and 28 of the spur gear stages 25 and 27, via which said first and second drive trains 9 and 17 are connected to the output-side crankshaft gear wheel 26, can be in engagement with said gear wheel 26 in different circumferential sections, for example arranged on opposite sides of the gear wheel 26 or also arranged in adjacent sectors of the gear wheel 26, cf. FIG. 5, wherein an overall compact configuration of the unit transmission 6 can be achieved. For example, the two said spur gears 28, 29 can both be in engagement with a lower circumferential half of the crankshaft gear wheel 26, so that the unit transmission 6 and the flywheel accumulator 13 can be arranged overall below the crankshaft 7, cf. FIG. 5, which results in an overall compact and favorable design.
[0061] The flywheel accumulator 13 can be connected to the crankshaft gear wheel 26 via one or more further gear stages, or said second drive train 17 can have one or more gear stages, in particular in order to translate the speed of the crankshaft 7 into a higher flywheel accumulator speed.
[0062] As shown in FIG. 2, the second drive train 17 can, for example, have a two-stage or even multi-stage planetary gear 18, wherein the flywheel accumulator 13 can, for example, be connected to the sun wheel 30 of the second planetary gear stage 18b.
[0063] On the input side, the planetary gear 18, for example the planet carrier 31 of the first planetary stage 18a, can be connected to said crankshaft gear wheel 26 via an intermediate stage, for example a spur gear stage 32, cf. FIG. 2.
[0064] In order to be able to start up the flywheel accumulator 13 running at high speeds during operation, even if the drive source 10 can only provide a limited starting torque, a starting aid 19 can be provided for starting up the flywheel accumulator 13, wherein said starting aid 19 can have a start-up motor 20, for example an electric motor, wherein said start-up motor 20 can, for example, be connected to the sun wheel 30 of the second gear stage or can be in mesh with it in order to be able to drive the sun wheel shaft and thus the flywheel accumulator 13.
[0065] In order to be able to switch off the start-up motor 20 during the intended operation of the drive train assembly 12, the start-up motor 20 can be connected to the flywheel accumulator 13 via an overrunning freewheel 21, which takes the flywheel accumulator 13, in particular the sun wheel 30, with it when starting up, but on the other hand allows the start-up motor 20, for example the sun wheel 30, to rotate faster than the start-up motor 20 or can also rotate when the start-up motor 20 is stationary.
[0066] In order to avoid an overload in the drive train assembly 12, for example in the area of the planetary gear 18 and/or the intermediate stage 27 or 32, in the event of a blockage of the working unit 3, for example by a stone on the tamper 4 or also a blockage of another section of the drive train assembly 12, a safety slipping clutch 33 is preferably provided, which can preferably be arranged directly on the flywheel accumulator 13 or can separate all gear stages of the second drive train 17 from the flywheel accumulator 13. Said safety slipping clutch 33 forms an emergency slipping clutch, so to speak, which does not open or uncouple the flywheel accumulator 3 in the event of the intended load fluctuations or torque surges of the working unit 3, but only when a torque surge occurs which is above or or significantly above the intended load or torque surges which occur during normal operation of the working unit 3.
[0067] As shown in FIG. 2, said safety slipping clutch 33 can be provided, for example, between the flywheel accumulator 13 and the shaft of the sun wheel 30 or can be in engagement with the flywheel accumulator 13 on the one hand and the sun wheel 30 on the other hand.
[0068] As shown in FIG. 3, the second drive train 17 can also have gear stages that are designed differently compared to FIG. 2, for example a single-stage planetary gear 18 and an additional intermediate stage between the planetary gear 18 and the connection to the crankshaft gear wheel 26, for example in the form of an additional spur gear stage 34, cf. FIG. 3.
[0069] Irrespective thereof, the start-up motor 20 can also be connected to the sun gear of the planetary gear 18 in the embodiment according to FIG. 3. Again independently of this, the flywheel accumulator 13 can also be connected to the sun gear 30 in order to rotate at its speed, wherein here again a safety slipping clutch 33 can be provided between the flywheel accumulator 13 and the gear stages of the second drive train 17, in particular between the flywheel accumulator 13 and the shaft of the sun gear 30, cf. FIG. 3.
[0070] FIG. 4 shows a further example of the second drive train 17. Here, too, the second drive train 17 comprises a single-stage planetary gear 18, similar to the embodiment according to FIG. 3, as well as an intermediate stage, in particular in the form of a spur gear stage 34, between the planetary gear 18 and the connection to the crankshaft gear wheel 26. As shown in FIG. 4, the flywheel accumulator 13 can be connected to the sun gear 30 of the planetary gear 18 and can be engaged with the shaft of the sun gear 30 via a safety slipping clutch 33.
[0071] The start-up motor 20 also provided can be connected via an intermediate gear stage 35, for example in the form of a spur gear stage, wherein an overrunning freewheel 21 can also be provided here. As shown in FIG. 4, the start-up motor 20 can be connected to the planet carrier 31 of the planetary gear 18 via said intermediate gear stage 35 in order to drive said planet carrier 31 and thus be able to start up the flywheel accumulator 13.
[0072] FIGS. 6 to 8 show the power flows occurring in various operating situations, with the hatched arrows representing the individual power flows or their branches. A thick arrow width or hatched area symbolizes a comparatively high transmitted power, while narrow arrows or narrow hatched areas symbolize relatively small power flows.
[0073] In this respect, FIG. 6 shows the power flows in the intended operation of the working unit 3 when a load impact of the tamper 4 is smoothed from the flywheel accumulator 13, i.e. a relatively high power flow is given from the flywheel accumulator 13 to the transmission output element 14, i.e. the crankshaft gear wheel 26, in order to smooth the load peak occurring at the tamper 4. As FIG. 6 further illustrates, the power flow coming from the tractor 2 via the first drive train 9 remains normal or relatively small compared to the power flow from the flywheel accumulator 13, i.e. the load peak occurring at the tamper 4 is not transferred to the first drive train 9.
[0074] As shown in FIG. 6, the power flows from the flywheel accumulator 13 and from the drive source 10 are summed up at the crankshaft gear wheel 26.
[0075] FIG. 7 also shows the power flows in the intended operation of the working unit 3, wherein an operating phase is shown in which power is only supplied from the drive source 10. The power supplied from the drive source 10 via the unit transmission 6 drives the crankshaft 7 and also drives the flywheel accumulator 13 via the second drive train 17. The power flow coming from the drive source 10 splits, so to speak, at the crankshaft gear wheel 26.
[0076] Finally, FIG. 8 shows the power flows during the starting process or starting up or running up the flywheel accumulator 13, wherein the start-up motor 20 feeds power into the planetary gear 18 and thereby runs up the flywheel accumulator 13. The first drive train 9 and thus the unit transmission 6 and the cardan shaft 11 are also dragged along load-free, so to speak, via the common crankshaft gear wheel 26. [0077] The power take-off train can [0078] allow the bevel gear set and the intermediate pinion to be smaller than before, because no more power and peak torques need to be transmitted from the flywheel; [0079] enable cost-efficient production, as the bevel gear set is a machine element in the baler gearbox that strongly influences the value and can be dimensioned smaller. [0080] The flywheel mass train can be [0081] be connected to the gearing of the crankshaft sprocket by an additional pinion [0082] the power from the flywheel train is transmitted via a second gear mesh from the crankshaft sprocket, which also receives the power from the power take-off train, wherein the crankshaft sprocket teeth can be made smaller by splitting the power; [0083] increase the flywheel mass to higher speeds by means of a transmission ratio in the flywheel mass train and thus store high kinetic energy; [0084] reduce the weight of the flywheel mass (Erot=Jo2); [0085] enable the flywheel mass and the baler to be raised via an auxiliary drive on the flywheel mass line in an advantageous manner with power sharing and bypassing the power take-off line; [0086] avoid unnecessary slippage (overrunning the freewheel) when the synchronous speed between the power take-off speed and the flywheel speed is reached, with optional monitoring of the speeds up to the synchronous point; [0087] bring the flywheel mass and the baler up to speed via a large slipping clutch on the drive; [0088] the safety slipping clutch of the flywheel mass on the high-speed shaft can be made smaller; [0089] enable power sharing via the flywheel. [0090] The intermediate wheel can [0091] provide more design space for the arrangement of the flywheel mass so that the crank arms do not collide; [0092] have a double wheel for gear ratio adjustment (see FIGS. 3, 4, 6, 7, 8) and thus tuning to optimum rotational energy without, for example, changing the flywheel mass; [0093] have a swelling tooth load due to a double wheel, thus higher torques can be transmitted in contrast to an alternating tooth load, [0094] can be arranged in the direction of travel, depending on the space available (currently transverse to the direction of travel); [0095] By using helical gears on the intermediate wheel, a flywheel axis can also be arranged perpendicularly, i.e. at right angles to the direction of travel or as required. [0096] The safety slipping clutch can [0097] be dimensioned in such a way that the moment of inertia is limited to a fixed value in the event of a blockage in the drive train or in the baler channel; [0098] advantageously be arranged in the flywheel mass line, in the immediate vicinity of the flywheel mass, e.g. on the sun wheel shaft, as this wheel carries low torques; [0099] alternatively be arranged on the web or ring gear of the planetary gear, as these have lower speeds; [0100] for other reasons, such as accessibility to the clutch or limited space, also on the intermediate gear. [0101] The auxiliary drive may have/be configured: [0102] The drive can be hydraulic or electric. [0103] The drive can be coupled to the sun gear shaft for low torques and high speeds. [0104] Alternatively, the drive can be positioned on the web or ring gear for high torques and low speeds. A connection to the intermediate gear is also possible if this is required for technical reasons, e.g. favorable space conditions or advantageous accessibility. [0105] The auxiliary drive is only used to start up the flywheel. This is equipped with an overrunning freewheel so that it can be switched off after the start-up process. [0106] Alternatively, the auxiliary drive with the pinion can also be disengaged from the meshing similar to the starter principle in a motor vehicle, so that the pinion can be disengaged from the meshing of the mating gear and does not have to run idle (torque-free). [0107] The planetary gear can be [0108] be single-stage with improved oil guidance, possibly with a shift of transmission ratios to the intermediate gear; have a short axial design; [0109] be two-stage, possibly with the use of a common ring gear; [0110] be fully integrated into the housing of the baler drive and have a very short design so that the crank arms do not collide; [0111] be partially integrated; [0112] be flanged on the outside; [0113] have an arrangement around the crankshaft wheel, in particular [0114] optimized for oil management, low splash losses [0115] designed for optimum bearing load on the crankshaft [0116] be configured for a modular system, adapted to different tractor outputs and multiple arrangements; [0117] have a multiple arrangement for engagement processes. [0118] The flywheel/flywheel housing can be [0119] external for good accessibility, [0120] encapsulated for less air turbulence, [0121] encapsulated and under negative pressure, wherein vacuum can be provided to reduce ventilation losses.
