WO2019197019A1 - Moissonneuse batteuse - Google Patents

Moissonneuse batteuse Download PDF

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Publication number
WO2019197019A1
WO2019197019A1 PCT/EP2018/059079 EP2018059079W WO2019197019A1 WO 2019197019 A1 WO2019197019 A1 WO 2019197019A1 EP 2018059079 W EP2018059079 W EP 2018059079W WO 2019197019 A1 WO2019197019 A1 WO 2019197019A1
Authority
WO
WIPO (PCT)
Prior art keywords
belt
combine harvester
pulley
countershaft
tensioning
Prior art date
Application number
PCT/EP2018/059079
Other languages
German (de)
English (en)
Inventor
Yannik HESSE
Benedikt Schönert
Maik Zeuner
Jan Furmaniak
Markus Koch
Original Assignee
Claas Selbstfahrende Erntemaschinen Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Claas Selbstfahrende Erntemaschinen Gmbh filed Critical Claas Selbstfahrende Erntemaschinen Gmbh
Priority to PCT/EP2018/059079 priority Critical patent/WO2019197019A1/fr
Priority to CN201880089151.5A priority patent/CN111712127A/zh
Publication of WO2019197019A1 publication Critical patent/WO2019197019A1/fr

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Classifications

    • A—HUMAN NECESSITIES
    • A01—AGRICULTURE; FORESTRY; ANIMAL HUSBANDRY; HUNTING; TRAPPING; FISHING
    • A01D—HARVESTING; MOWING
    • A01D69/00—Driving mechanisms or parts thereof for harvesters or mowers
    • A01D69/06—Gearings

Definitions

  • the present application relates to a combine harvester according to the preamble of claim 1.
  • Such a combine comprises an engine by means of which inter alia
  • the engine has an engine output shaft, from the starting by means of power belt one from the engine to
  • the combine comprises a countershaft, which is coupled by means of a motor belt in torque transmitting manner with the engine output shaft. It is known that the working organs of the combine harvester starting from the
  • Lined countershaft and are supplied in this way each with a torque.
  • a special feature in the design of a drive system for a combine harvester is that an attempt is made to use the combine harvester in principle for various crop tasks and / or harvesting conditions can. It should be noted that, depending on the crop to be harvested, the working mechanisms of the combine harvester should be operated in different ways, in particular at different rotational speeds, in order to arrive at an optimum harvest result. It is also conceivable that a change in the operation of the working elements of the combine due to changing boundary conditions seems advantageous or even necessary.
  • the present application is therefore based on the object to provide a combine, by means of which a change in the operation of work organs can be made as simple as possible.
  • the combine harvester has a transfer device which is arranged on the first side of the combine harvester.
  • the "sides" of the combine are viewed in the transverse direction of the combine separated by the working organs, the crop is effectively through the combine in a longitudinally parallel direction from front to back and thereby processed or processed, wherein a "channel” along which the crop flows, is bounded laterally by means of corresponding boundary walls.
  • These respective boundary walls are assigned to the sides of the combine harvester in the sense of the present application, wherein the sides are respectively visible in a side view of the combine harvester.
  • Counterpoint may be formed, is coupled in torque transmitting manner with a (main) countershaft, said coupling by means of a
  • Transmission belt is made.
  • the latter is formed by a typical power belt, for example by a V-belt.
  • the transfer device serves to distribute a torque provided by the countershaft on the first side of the combine harvester.
  • the transmission device cooperates with at least one further power belt, by means of which a torque provided by the countershaft can be transmitted to at least one working member of the combine harvester. This serves the
  • Transmission device to provide such working organs of the combine which - viewed in the longitudinal direction of the combine - are arranged spatially behind the countershaft.
  • the transmission device is arranged as such spatially behind the countershaft to the combine harvester.
  • a plurality of working members are connected by means of respective power belts.
  • the combine harvester according to the invention is characterized in that the countershaft, starting from the first side of the combine harvester, extends in a direction transverse to a longitudinal axis thereof to a second side of the combine harvester opposite the first side.
  • the countershaft On the second side, the countershaft is connected by means of at least one power belt with at least one working member of the combine in torque transmitting manner, wherein on the second side of the combine coupled to the countershaft work organs - viewed in the longitudinal direction of the combine - are arranged spatially in front of the countershaft.
  • the combine harvester according to the invention has many advantages.
  • Combine harvester can be connected individually. Here it is for the
  • Subdivision and in particular the adjustability of the transmission ratios of the countershaft directly or indirectly to the working organs of the combine harvester particularly advantageous that the distribution of the torque provided by the engine takes place by means of the countershaft on the two sides of the combine.
  • the drive system is equalized by distribution on the two sides of the combine harvester, whereby a respective available space on the two sides of the combine harvester is better usable. This applies, for example, the use of transmission devices by means of which gear ratios, starting from the countershaft to a respective working organ changeable and therefore adjustable to a specific specification.
  • a spatially located before the countershaft working member is formed by a threshing drum, wherein the Vorgeiegewelle at least indirectly by means of at least one
  • Dreschriemens is coupled in torque transmitting manner with a threshing drum drive shaft of the threshing drum.
  • "indirect coupling” basically means that the respective working member does not have to be connected directly to the countershaft by means of a respective power-train belt; however, direct coupling is equally conceivable.
  • the threshing drum drive shaft is equipped with two coaxially arranged pulleys. These differ in terms of their diameter, wherein a diameter of a first pulley exceeds the diameter of the second pulley. By means of the pulleys, it is possible, the threshing drum drive shaft and thus the Drum drum to operate at different speeds, while a speed of the countershaft remains identical.
  • the threshing belt can be transferred between a low position and a fast position, wherein the threshing belt in presence in its low position with the first pulley in its fast position with the second
  • Pulley is engaged. Should it therefore be necessary, for example, to reduce the speed of the threshing drum because of changing crop conditions or because of the conversion of the combine to another crop, it is conceivable to change the threshing belt from its quick position to its low position or vice versa. In this way, a variation of the rotational speed of the threshing drum is made possible by the simplest means by means of mechanical change, regardless of a change in the rotational speed of the countershaft. Furthermore, no change of the threshing belt is required; its length preferably remains unchanged.
  • Combine has a tensioning device, the threshing drum or the
  • the tensioning device in its second clamping position is suitable for tensioning the threshing belt located in its fast position. Due to the different diameters of the two pulleys of the threshing cylinder drive shaft, the threshing belt on the second side of the combine harvester runs on a slightly changed path, so that the tensioning device, which in particular is in direct contact with the threshing belt by means of a tensioning roller, can follow the change in the travel of the threshing belt. In this case, it is particularly conceivable to make the clamping device mechanically adjustable in such a way that a position of the tensioning roller on the second side of the
  • the clamping device has an arm which is designed to pivot about a bearing axis, wherein on one of the bearing axis end remote from a rotatable about its central axis tension roller is arranged.
  • An adjustment of a position of the clamping device can for example by means of a
  • Clamping device first disassembled and then back to a certain extent on one opposite side of the arm is mountable.
  • the tensioning roller in a first tensioning position, extends from a side surface of the arm in a first direction and in a second tensioning position from the opposite side of the arm in the opposite direction.
  • These two clamping positions of the tensioning roller can in particular correspond to the positions of the threshing belt, wherein, for example, the tensioning device is in its first tensioning position with the threshing belt present in its low position and vice versa when the tensioning roller is in its second tensioning position with the threshing belt present in its fast position corresponds.
  • Dreschtrommelantriebswelle in a particularly simple manner by means of a mechanical change to the combine, namely a displacement of the threshing belt from one to another pulley of the threshing drum drive shaft done.
  • a change in a length of the threshing belt or the threshing belt as a whole is not required here.
  • the associated components are designed to be particularly simple and durable, so that the associated combine harvester is advantageous both in terms of its robustness and its comparatively low production costs.
  • the combine comprises on its second side at least one variator, wherein the variator is coupled by means of at least one variator belt in torque transmitting manner with the countershaft.
  • the variator can act in particular as an intermediate member between the countershaft and the threshing drum drive shaft, wherein by means of the variator, a further spread of between the
  • Transmission device is such a combine of particular advantage, wherein the transmission device comprises a plurality of pulleys.
  • the pulleys is formed such that a diameter thereof is changeable.
  • This change in diameter may on the one hand consist in that the diameter of the pulley is changed as such, for example via the placement or removal of a curb.
  • the pulley is exchanged for another pulley, which has a different diameter, so that at the point of the original pulley now a pulley with a different diameter is present, whereby in the context of the present application, the diameter of the pulley "changed" has been.
  • the term “pulley” does not necessarily describe the component as such, but rather the functional unit on the transmission, which may optionally be formed by different bodily pulleys.
  • a spatially located behind the countershaft working member is formed by a Hburgselorgan.
  • This comprises a Hburgselantriebswelle which is coupled by means of a chopper belt in torque transmitting manner with the transmission device.
  • the chopper belt cooperates with a pulley of the transmission device whose diameter is variable in the manner described above. In this way, it is possible to change a transmission ratio between the countershaft and the Hburgselorgan, since the frequency of the chopper belt is changed due to the changed diameter of the respective pulley of the transmission device while maintaining the frequency of the transmission belt, that is circulations per transmission belt per unit time.
  • the combine harvester according to the invention further ausgestaltend this comprises a cooperating with the chopper belt tensioning device having two spaced tension rollers.
  • the tensioning device can be transferred between at least two different tensioning positions, and if present in a first tensioning position, it is suitable for cooperating with the chopping belt, which is in operative connection with a pulley of the transmission device with a first diameter.
  • the tensioning device is adapted, when in its second tensioning position, to cooperate with the chopping belt, which is in operative connection with a pulley of the transmission device with a second diameter.
  • the chopper belt and the tensioning device can be transferred between at least two different tensioning positions, and if present in a first tensioning position, it is suitable for cooperating with the chopping belt, which is in operative connection with a pulley of the transmission device with a first diameter.
  • the tensioning device is adapted, when in its second tensioning position, to cooperate with the chopping belt, which is in operative connection with
  • Chopping belt with a first pulley of the transmission device is smaller than upon interaction of the chopper belt with the second pulley of the transfer device, which has a smaller diameter than the first
  • Pulley of the transfer device along a changed path in space runs so that the tensioning device for exerting their clamping effect regardless of the path of the chopper belt in its spatial position on the first side of the
  • the tensioning device can be used, in particular, to receive a length released in the course of the transfer of the chopper belt from one of its positions to its other position, so that the
  • Chopper belt is durable and does not need to be replaced with a chopper belt of other length.
  • the design of the clamping device with two tension rollers is in this respect of particular advantage, as a change in the position of the clamping device in the room is particularly easy.
  • the clamping device is designed to be pivotable as such about a parallel to the chaff drive shaft bearing axis. It is understood that such a bearing axis is at least eccentrically arranged with respect to one of the tension rollers of the clamping device, so that in the course of pivoting the clamping device about the bearing axis at least one tensioning roller is moved on a circular path about the bearing axis.
  • the change in the position of the clamping device is particularly easy vorOSEbar in this way, so that the clamping device particularly easy to follow a changed path of the chopper belt and this can hold tension.
  • the bearing axis of the clamping device coincides with a rotational axis of one of the tension rollers.
  • such an embodiment of the combine harvester according to the invention is of particular advantage, in which a spatially located behind the countershaft working member is formed by a separating member.
  • a spatially located behind the countershaft working member is formed by a separating member.
  • Such acts for example, with an axial separation rotor whose longitudinal axis extends parallel to a vertical longitudinal plane of the combine, which includes the longitudinal axis of the combine.
  • the separating element cooperates with a Trennorganantriebswelle, starting from the
  • Separating member extends to the first side of the combine. This Trennorganantriebswelle is by means of a separation belt in torque-transmitting manner with the
  • the Trennorganantriebswelle is equipped with two coaxially arranged pulleys, wherein a diameter of the first pulley has a diameter of the second
  • Pulley exceeds. This embodiment is comparable to that of the threshing drum described above, wherein the separation belt can optionally interact with one of the two pulleys. In this way, the separation belt between a slow position and a quick position can be transferred, wherein the
  • Separating belt is engaged with the first pulley when in its low position and with the second pulley when in its quick position. In this way it is possible to operate the Trennorganantriebswelle at a constant frequency of the transmission belt at different speeds, namely at a high speed and a slow speed.
  • Trennorganantriebswelle is analogous to the above description particularly simple means of displacement of T rennjiemens from one pulley to the other
  • the separation belt as such does not have to be changed here; In particular, a length of the separation belt remains the same.
  • the Trennorganantriebswelle can be operated even with four different ratios, on the one hand two different ratios by means of the two pulleys of Trennorganantriebswelle are adjustable and two other ratios by changing the diameter of a pulley of the transmission device is possible.
  • Transfer device referenced, which may have at least one variable diameter pulley.
  • the separation belt in four different permutations and in this way to four different
  • the two pulleys of Trennorganantriebswelle are designed in the form of a pulley package, as a whole non-destructively dismountable from the Trennorganantriebswelle is connected to selbiger.
  • the separation belt in the presence of the pulley package in a first position with the larger pulley and in the presence of the
  • the separation belt also acts with a tensioning device
  • the clamping device can be transferred between different clamping positions, the clamping positions corresponding to the different positions of the separating belt. Due to the
  • the tensioning device is designed to be pivotable about a bearing axis parallel to the separating element drive shaft, wherein the bearing axis preferably coincides with an axis of rotation of one of the tensioning rollers.
  • a corresponding embodiment is already described above in connection with the clamping device, which can cooperate with a chopper belt. The advantages arise accordingly.
  • Pulley of the transmission device has a width which corresponds to at least the sum of the widths of chopping belt and separation belt, so that chopping and separation belt can run side by side on the pulley so to speak.
  • This embodiment has the particular advantage that by means of a change in the diameter of the pulley in a single operation, the transmission ratios between the transmission device and Humbleselorgan and between the transmission device and separating member are changeable. Such a concurrent change is also particularly useful, since typically a change in external circumstances, such as the fruit to be harvested, similar changes optimal rotational speeds of
  • Fig. 1 A vertical longitudinal section through an inventive
  • FIG. 2 shows a perspective view of a drive system on a first side of the combine harvester according to FIG. 1, FIG.
  • FIG. 3 shows a perspective view of the drive system on the second side of the combine harvester according to FIG. 1,
  • Fig. 4 The view according to Figure 3, wherein a threshing belt in a
  • Fig. 6 The view according to Figure 5, wherein a chopper belt and a
  • Fig. 7 The view according to Figure 5, wherein a separation belt in a
  • FIGS. 1 to 7 The exemplary embodiment illustrated in FIGS. 1 to 7 comprises a combine harvester 1 according to the invention, which is equipped with a plurality of working members and a motor 38. Further, the combine harvester 1 comprises in its front end a header 41, which is here formed by a feeder with mounted cutter bar. In particular, the combine harvester 1 cooperates with a threshing drum 4, a separating element 39 and a chopping element 40. To drive these working organs includes the Combine 1 a drive system, which results in particular with reference to Figures 2 to 7.
  • This drive system includes a combination of shafts, pulleys and power belts, which transmit torque from one
  • the engine output shaft 2 extends starting from the engine 38 in the direction of a first side 6 of the combine harvester 1. This results in particular from FIG. 2 in which the engine 38 as such is not shown.
  • Engine output shaft 2 cooperates with at least one pulley so that it is adapted to receive a motor belt 7, by means of which a torque provided by the motor 38 is transferable to a countershaft 3.
  • the latter has in the example shown a plurality of pulleys, so that the countershaft 3 is adapted to receive the motor belt 7 and the torque provided in this way by means of further power belts on the
  • the motor belt 7 further cooperates with a tensioning device 42, by means of which the motor belt 7 is maintained at tension.
  • the countershaft 3 extends transversely to the combine harvester 1 starting from the first side 6 towards a second side 9 of the combine harvester 1 which is opposite the first side 6.
  • a longitudinal axis of the countershaft 3 extends at least substantially perpendicular to a longitudinal axis 8 of the combine harvester 1.
  • the Countershaft 3 on the second side 9 of the combine harvester 1 by means of a variator belt 18 with a variator 17 together.
  • This is in turn by means of a threshing belt 10 in torque transmitting manner with one of two pulleys 11, 12 a
  • Dreschtrommelantriebswelle 5 connected.
  • This threshing drum drive shaft 5 is associated with the threshing drum 4, wherein the threshing drum 4 is rotationally drivable by means of transmission of a torque to the threshing drum drive shaft 5.
  • Pulleys 11, 12 of the threshing drum drive shaft 25 have different
  • Pulley 11, 12 to change a gear ratio between the variator 17 and the threshing drum drive shaft 5.
  • Variator belt 18 is not required for this. In this way, a particularly simple change in an operating speed of the threshing drum 4 is possible, for which only the threshing belt 10 of one of the pulleys 11, 12 to the other
  • Pulley 11, 12 must be re-clamped.
  • the tensioning device comprises
  • an arm 15 which is pivotally mounted about a bearing axis 14 on the combine 1.
  • a tensioning roller 16 is arranged on the arm 15 and is rotatably mounted on the arm 15.
  • the tension roller 16 is fixed on one side to the arm 15 so as to extend in one direction from one side of the arm 15.
  • the tension roller 16 is mounted on the opposite side of the Amrs 15, whereby their position in the room coincides with a lateral displacement of the path of the threshing belt 10 changes.
  • the arm 15 is pivoted about the bearing axis 14, whereby the
  • Clamping device 13 is tracked overall the changed path of the threshing belt 10.
  • the tensioning device 13 and the two pulleys 11, 12 of the threshing drum drive shaft 5 in a structurally particularly simple manner created the possibility to change the transmission ratio between the countershaft 3 and the threshing drum 4 by means of fewer handles.
  • Harvesting harvester 1 is to react quickly and with little technical effort.
  • Transmission device 19 is connected, wherein the Obertragungsriemen 20 cooperates with a pulley 22 of the transmission device 19.
  • Transfer device 19 can also be referred to as a so-called "transfer point". Starting from the transfer device 19, the torque provided in the example shown is distributed to two further working elements of the combine harvester 1, namely the separating element 39 and the chopper element 40. The interaction of the transfer device 19 with the separating element 39 and the chopper element 40 results particularly well with reference to FIGS. 5 to 7.
  • the separating member 39 cooperates with a Trennorganantriebswelle 25, the drive for the operation of the separating member 39 is required.
  • the Trennorganantriebswelle 25 is by means of a separation belt 24 in a torque-transmitting manner with the
  • Transfer device 19 is connected, wherein the separation belt 24 at the
  • Transmission device 19 is connected to a first pulley 21. Furthermore, the separation belt 24 cooperates with a tensioning device 28, by means of which the separation belt 24 is maintained at tension. In a particularly advantageous manner, the
  • Trennorganantriebswelle 25 equipped with two pulleys 26, 27, which have different diameter.
  • the separation belt 24 is basically suitable to selectively cooperate with one of the two pulleys 26, 27, whereby at a constant frequency of the transmission belt 20 and thus the
  • a frequency of the Trennorganantriebswelle 25 is variable. For this purpose, it is basically only necessary to reconnect the separation belt 24 from one of the two pulleys 26, 27 to the respective other pulley 26, 27.
  • the two pulleys 26, 27 of the Trennorganantriebswelle 25 are bundled into a pulley package, as a whole of the
  • Trennorganantriebswelle 25 is designed removable. In this way, it is possible to rotate the pulley package, so that - viewed from the separating member 39 - the order of the pulleys 26, 27 along the
  • the tensioning device 28 is nevertheless movable between different tensioning positions, so that it is suitable for reliably tensioning the separation belt 24 despite its changed path.
  • the tensioning device 28 has two tension rollers 29, 30, which are arranged at opposite ends of an arm and connected to each other in this way.
  • the tensioning device 28 is mounted pivotably about a bearing axis 31, the bearing axis 31 coinciding with an axis of rotation of the tensioning rollers 29.
  • the tension roller 30 facing away from the bearing axis 31 is moved along a circular path about the bearing axis 31, whereby a particularly simple way of tracking in the course of a Umspannens the separation belt 24 is provided on the Trennorganantriebswelle 25.
  • a drive means 43 which is formed by a piston-cylinder unit. This engages with its piston on a lever arm of the clamping device 28, so that by means of retraction or extension of the piston, a torque on the clamping device 28 can be exercised, by means of the latter about its bearing axis 31 is pivotable. Furthermore, the clamping device 28 can be detected by detecting the drive means 43 in their respective set clamping position. The various clamping positions of the clamping device 28 are particularly well based on the figures 5 to 7.
  • a diameter of the pulley 21 is made changeable on the transmission device 19.
  • the pulley 21 can be exchanged for another pulley 23, which is then located at the same position on the transfer device 19.
  • the diameter of the pulley 21 is changed in the sense of the present application in that it is against a pulley 23 of different diameter is changed.
  • the diameter of the pulley 21 is greater than that of the pulley 23.
  • the transmission ratio between the transmission belt 20 and the separation belt 24 is changed.
  • the isolator drive shaft 25 is operated while maintaining a frequency of the transfer belt 20 at a changed speed, thereby changing in the manner described above
  • the clamping device 28 can be brought into different clamping positions depending on the different position of the separating belt 24 , wherein an angle of wrap, by which the separating belt 24 wraps around the two tension rollers 29, 30 of the tensioning device 28, changes according to the tensioning position, thus permitting the possibility of providing a free length, depending on the position of the separation belt 24 Separate belt 24 and thereby keep the separation belt 24 to tension .In particular, this eliminates the need to use different separation belts of different lengths.
  • the chopping member 40 is also indirectly connected to the countershaft 3 in a torque transmitting manner by means of a chopper belt 33.
  • the chopping belt 33 acts in the example shown in each case with the same pulley 21, 23 of the transmission device 19 together, with the respective timing belt 24 cooperates.
  • the respective pulleys 21, 23 each have a width which enables them to receive the separation belt 24 and the chopper belt 33 next to one another.
  • the chopper 40 cooperates with a chopper drive shaft 32, which by means of a permanently assigned
  • Pulley 46 cooperates with the chopper belt 33.
  • a change in the transmission ratio between the transmission belt 20 and the chopping belt 33 is possible in the example shown only by means of a change in the diameter of the pulley 21 on the transmission device 19, this change in the manner described above here by means of a change of the pulley 21 against a pulley 23 smaller diameter can be made.
  • the chopper belt 33 also interacts with a tensioning device 34 assigned to it which is comparable to the chucking belt 34
  • Clamping device 28 of the separation belt 24 has two spaced tension rollers 35, 36 has. Furthermore, the clamping device 34 is pivotally mounted about a bearing axis 37, which coincides with a rotational axis of the tension roller 35. A tracking of the tensioning device 34 according to a change of a path of the chopper belt 33 in space is particularly easy in this way possible, wherein the pivoting of the clamping device 34 in a particularly simple manner by means of a drive device 44, which analogous to the drive means 43 of the clamping device 28 according to the above Description is designed and works.

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Abstract

La présente invention concerne une moissonneuse-batteuse (1) comprenant un moteur (38) doté d'un arbre de sortie de moteur (2), un arbre intermédiaire (3) et une pluralité d'organes de travail, l'arbre de sortie de moteur (2) s'étendant du moteur (38) dans la direction vers un premier côté (6) de la moissonneuse-batteuse (1), l'arbre de sortie de moteur (2) et l'arbre intermédiaire (3) étant couplés l'un à l'autre au moyen d'au moins une courroie de moteur (7). L'invention vise à fournir une moissonneuse-batteuse au moyen de laquelle le changement de mode de fonctionnement des organes de travail peut être effectué aussi simplement que possible. À cet effet, sur le premier côté (6) de la moissonneuse-batteuse (1), un dispositif de transfert (19) est disposé, lequel, au moyen d'une courroie de transmission (20), est couplé de manière à transmettre le couple à l'arbre intermédiaire (3) ; et l'arbre intermédiaire (3) s'étend partant du premier côté (6) de la moissonneuse-batteuse (1) dans une direction transversale à un axe longitudinal (8) de la moissonneuse-batteuse (1) à un deuxième côté (9) de la moissonneuse-batteuse (1), opposé au premier côté (6) ; au moyen du dispositif de transmission (19), un couple fourni par l'arbre intermédiaire (3) sur le premier côté (6) de la moissonneuse-batteuse (1) peut être transmis, au moyen de courroies de transmission respectives, aux organes de travail de la moissonneuse-batteuse (1), qui, vus dans la direction longitudinale de la moissonneuse-batteuse (1), sont disposés spatialement derrière l'arbre intermédiaire (3) ; et le couple fourni par l'arbre intermédiaire (3) sur le deuxième côté (9) de la moissonneuse-batteuse (1) peut être transmis au moyen de courroies de transmission respectives aux organes de travail de la moissonneuse-batteuse (1), qui, vus dans la direction longitudinale de la moissonneuse-batteuse (1), sont disposés spatialement avant l'arbre intermédiaire (3).
PCT/EP2018/059079 2018-04-10 2018-04-10 Moissonneuse batteuse WO2019197019A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/EP2018/059079 WO2019197019A1 (fr) 2018-04-10 2018-04-10 Moissonneuse batteuse
CN201880089151.5A CN111712127A (zh) 2018-04-10 2018-04-10 联合收割机

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Application Number Priority Date Filing Date Title
PCT/EP2018/059079 WO2019197019A1 (fr) 2018-04-10 2018-04-10 Moissonneuse batteuse

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WO2019197019A1 true WO2019197019A1 (fr) 2019-10-17

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GB1480566A (en) * 1974-10-11 1977-07-20 Claas Maschf Gmbh Geb Threshing drum drive for combine-harvesters
EP1044598A1 (fr) * 1999-04-16 2000-10-18 Case Harvesting Systems GmbH Entrainement pour le dispositif de battage de moissonneuses-batteuses
EP1375977A2 (fr) * 2002-06-19 2004-01-02 CNH Belgium N.V. Ensemble entraínement pour moissonneuse-batteuse
DE102013103450A1 (de) 2013-04-08 2014-10-09 Claas Selbstfahrende Erntemaschinen Gmbh Als Riementriebe ausgebildetes Antriebssystem eines selbstfahrenden Mähdreschers

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US6361435B1 (en) * 1997-08-26 2002-03-26 Yanmar Agricultural Equipment Co., Ltd. General purpose combined harvester and thresher
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