CN111712127A

CN111712127A - Combine harvester

Info

Publication number: CN111712127A
Application number: CN201880089151.5A
Authority: CN
Inventors: Y·黑塞; B·舍纳特; M·佐伊纳; J·富尔马尼亚克; M·科赫
Original assignee: Claas Selbstfahrende Erntemaschinen GmbH
Current assignee: Claas Selbstfahrende Erntemaschinen GmbH
Priority date: 2018-04-10
Filing date: 2018-04-10
Publication date: 2020-09-25
Also published as: WO2019197019A1

Abstract

The application relates to a combine harvester (1) comprising a motor (38) having a motor output shaft (2), a countershaft (3) and a plurality of operating members, the motor output shaft (2) extending from the motor (38) toward a first side (6) of the combine harvester (1), the motor output shaft (2) and the countershaft (3) being coupled to one another by means of at least one motor belt (7) in a torque-transmitting manner. In order to provide a combine harvester by means of which the operating conditions of the operating mechanism can be changed as easily as possible, it is proposed according to the invention that a transmission device (19) is arranged on a first side (6) of the combine harvester (1), which is coupled by means of a transmission belt (20) to a secondary shaft (3) in a torque-transmitting manner, the secondary shaft (3) extending from the first side (6) of the combine harvester (1) in a direction transverse to the longitudinal axis (8) of the combine harvester (1) to a second side (9) of the combine harvester (1) opposite the first side (6), the torque provided by the secondary shaft (3) being transmittable by means of the transmission device (19) on the first side (6) of the combine harvester (1) by means of a corresponding force transmission belt to the operating mechanism of the combine harvester (1): the working mechanism (viewed in the longitudinal direction of the combine harvester (1)) is arranged spatially behind the auxiliary shaft (3), and the torque provided by the auxiliary shaft (3) can be transmitted to the working mechanism of the combine harvester (1) on the second side (9) of the combine harvester (1) by means of a corresponding force transmission belt: the working mechanism (viewed in the longitudinal direction of the combine harvester (1)) is arranged spatially in front of the secondary shaft (3).

Description

Combine harvester

Technical Field

The present application relates to a combine harvester according to the preamble of claim 1.

Background

Such a combine harvester comprises a motor, by means of which the working mechanism of the combine harvester can be driven in particular. For this purpose, the motor has a motor output shaft from which a torque provided by the motor can be transmitted indirectly or directly to the operating mechanism by means of a force transmission belt. To this end, the combine harvester comprises a countershaft (vorgelegelle) which is coupled by means of a motor belt to a motor output shaft in a torque-transmitting manner. It is known that the working mechanisms of a combine harvester are connected starting from a countershaft and in this way are each supplied with torque.

Combine harvesters of the type described at the outset are known from the prior art. For this purpose, reference is made, as an example, to german laid-open document DE 102013103450 a 1. This publication describes a drive system which, by means of a force transmission belt, enables a force transmission or a torque transmission from a motor output shaft to a corresponding operating mechanism.

In the design of a drive system for a combine harvester, it is characteristic that tests are carried out in order to be able to use the combine harvester substantially for different harvesting tasks and/or harvesting conditions. It is to be noted here that the working mechanisms of the combine harvester should be operated in different ways, in particular at different rotational speeds, depending on the crop to be harvested, in order to achieve an optimum harvesting result. It is likewise conceivable that it is advantageous or even necessary for the operating conditions of the working mechanism of the combine harvester to change on the basis of changing boundary conditions. Thus, the variability of the operating conditions of the combine harvester is of particular importance.

Accordingly, in the prior art, it is common, for example, to use so-called transmissions, by means of which the gear ratios can be set in each case. In this way, it is possible to convert the rotational speed of the drive element (which is supplied with torque to the transmission) to a further rotational speed by means of the transmission, which is transmitted from the transmission to the respective working mechanism of the combine harvester by means of the respective force transmission belt. However, it is considered disadvantageous here that the overall equipping of the respective combine harvester with a transmission represents a considerable outlay, since the transmission has a relatively complicated construction.

Disclosure of Invention

The task underlying the present application is therefore: a combine harvester is provided, by means of which changes in the operating conditions of the working mechanism can be carried out as simply as possible.

According to the invention, the underlying object is achieved by means of a combine harvester having the features of claim 1. Advantageous configurations emerge from the dependent claims 2 to 15.

According to the invention, the combine harvester has a transfer device which is arranged on a first side of the combine harvester. The "sides" of the combine harvester are separated from one another by the working mechanism, as seen in the transverse direction of the combine harvester, wherein the harvest flows from front to back through the combine harvester in a direction parallel to the longitudinal axis to some extent and is processed or treated in the process, wherein the "channels" (along which the harvest flows) are delimited laterally by means of corresponding limiting walls. These corresponding limiting walls are assigned to the sides of the combine harvester in the sense of the present application, wherein these sides are each visible in a side view of the combine harvester.

A transmission device, which can itself be formed by a so-called "drive point", is coupled in torque-transmitting manner to the (primary) secondary shaft, wherein this coupling takes place by means of a transmission belt. The latter is formed by a typical force transmission belt, for example a wedge belt.

The transfer device is used to distribute the torque provided by the layshaft to the first side of the combine. For this purpose, the transmission device interacts with at least one further force transmission belt, by means of which the torque provided by the countershaft can be transmitted to at least one operating element of the combine harvester. The transfer device is used here for feeding the following working mechanisms of the combine harvester: the working mechanism (viewed in the longitudinal direction of the combine harvester) is arranged spatially behind the secondary shaft. Advantageously, the transfer device itself is arranged spatially also behind the secondary shaft on the combine harvester. As can be seen in each case below, it is particularly conceivable to connect a plurality of operating means from the transmission device by means of corresponding force transmission belts.

The combine harvester according to the invention is furthermore characterized in that the secondary shaft extends from a first side of the combine harvester in a direction transverse to its longitudinal axis to a second side of the combine harvester opposite the first side. On the second side, the countershaft is connected in torque-transmitting fashion to at least one working mechanism of the combine harvester by means of at least one force transmission belt, wherein on the second side of the combine harvester the working mechanism coupled to the countershaft (viewed in the longitudinal direction of the combine harvester) is arranged spatially in front of the countershaft.

The combine harvester according to the invention has several advantages. In particular, it is possible for the torque provided by the motor to be distributed to both sides of the combine harvester by means of the auxiliary shaft, wherein a secondary distribution takes place to some extent on the side of the combine harvester, by means of which the working mechanisms of the combine harvester can be individually connected. In this case, for the secondary distribution and in particular for the adjustability of the transmission ratio indirectly or directly from the secondary shaft to the working mechanism of the combine harvester, it is particularly advantageous if the torque provided by the motor is distributed to both sides of the combine harvester by means of the secondary shaft. Furthermore, the drive system is equalized by means of a distribution on both sides of the combine harvester, whereby the space provided on both sides of the combine harvester can be better utilized. This involves, for example, the use of a transmission device, by means of which the transmission ratio starting from the countershaft to the respective operating means can be changed and can therefore be set to certain predefined parameters.

In an advantageous embodiment of the combine harvester according to the invention, the operating mechanism spatially upstream of the secondary shaft is formed by a threshing cylinder, wherein the secondary shaft is coupled at least indirectly by means of at least one threshing belt in a torque-transmitting manner to a threshing cylinder drive shaft of the threshing cylinder. In the sense of the present application, "indirect coupling" is understood to mean, in principle, that the respective operating means need not be connected directly to the auxiliary shaft by means of the respective force transmission belt; direct coupling is likewise conceivable. Preferably, the threshing cylinder drive shaft is equipped with two belt discs arranged coaxially. The belt pulleys differ in their diameter, wherein the diameter of the first belt pulley exceeds the diameter of the second belt pulley. By means of the belt pulley, it is possible to realize that the threshing cylinder drive shaft and thus the threshing cylinder run at different rotational speeds, while the rotational speed of the secondary shaft remains the same. It is therefore only necessary to assign a respective further belt pulley to the threshing belt starting from one of the belt pulleys. The threshing belt can thus be switched between a slow position and a fast position, wherein the threshing belt cooperates with the first belt disc when it is in its slow position and with the second belt disc when it is in its fast position. Thus, if a reduction in the rotational speed of the threshing cylinder is required, for example due to changed harvesting conditions or due to the switching of the combine harvester onto another crop, it is conceivable to change the threshing belt from its fast position to its slow position or vice versa. In this way, the rotational speed of the threshing cylinder can be varied in the simplest manner by means of mechanical switching without depending on a change in the rotational speed of the secondary shaft. In addition, the threshing belt does not need to be replaced; the length of the threshing belt is preferably kept constant.

In this embodiment, it is particularly advantageous if the combine harvester has a tensioning device which is assigned to the threshing cylinder or to the threshing cylinder drive shaft. The tensioning device can be operated in two different tensioning positions, wherein the tensioning device is adapted to tension the threshing belt in its slow position in a first tensioning position, wherein the tensioning device is adapted to tension the threshing belt in its fast position in a second tensioning position. Due to the different diameters of the two belt discs of the threshing cylinder drive shaft, the threshing belt on the second side of the combine harvester runs on a slightly changed course, so that the tensioning device, which is in direct contact with the threshing belt, in particular by means of the tensioning wheel, can follow the running change of the threshing belt. In particular, it is conceivable here for the tensioning device to be designed to be mechanically adjustable, so that the position of the tensioning wheel on the second side of the combine harvester can be spatially varied.

In an advantageous embodiment, the tensioning device has an arm which is designed to be pivotable about the bearing axis, wherein a tensioning wheel which is rotatable about a center axis of the bearing axis is arranged on the end facing away from the bearing axis. The adjustment of the position of the tensioning device can be carried out, for example, by means of a pivoting of the arm about the bearing axis. Particularly advantageous are also the following configurations: in this configuration, the tensioning wheel can first be detached from the arm of the tensioning device and can then be fitted to some extent on the opposite side of the arm. In this way, the tensioning wheel extends in a first direction starting from the side face of the arm in the first tensioning position and in an opposite direction starting from the opposite side of the arm in the second tensioning position. These two tensioning positions of the tensioning wheel can in particular correspond to the positions of the threshing belt, wherein for example the tensioning device corresponds to the threshing belt being present in its slow position, for example when the tensioning wheel is present in its first tensioning position, and conversely to the threshing belt being present in its fast position, for example when the tensioning wheel is present in its second tensioning position. As a result, the change in the transmission ratio between the secondary shaft and the threshing cylinder drive shaft can be carried out in a particularly simple manner by means of a mechanical change on the combine harvester, i.e. the displacement of the threshing belt from one pulley of the threshing cylinder drive shaft to the other pulley. No change in the length of the threshing belt or in the threshing belt as a whole is required here. The associated components are particularly simple and durable in design, so that the associated combine harvester is advantageous not only in terms of its robustness but also in terms of its relatively low production costs.

Advantageously, the combine harvester comprises at least one transmission on its second side, wherein the transmission is coupled with the countershaft in a torque-transmitting manner by means of at least one transmission belt. The transmission can in particular act as an intermediate link between the countershaft and the drive shaft of the threshing cylinder, wherein a further widening of the transmission ratio to be set between the countershaft and the drive shaft of the threshing cylinder (spraizung) is achieved by means of the transmission.

In connection with the transfer device arranged on the first side of the combine harvester, the following combine harvester is particularly advantageous: in the combine harvester, the transfer device comprises a plurality of belt discs. Advantageously, at least one of the belt pulleys is configured such that its diameter is variable. Such a change in diameter can consist, on the one hand, in a change in the diameter of the belt pulley itself, for example by putting on or taking off a cuff rim. On the other hand, it is conceivable to replace the belt pulley with a further belt pulley having a further diameter, so that a belt pulley having a further diameter now exists in the position of the original belt pulley, whereby the diameter of the belt pulley has been "changed" in the sense of the present application. In this case, the term "belt pulley" does not necessarily describe a component per se, but a functional unit on the transfer device, which is optionally formed by a different physical belt pulley.

Furthermore, the following combine harvesters are particularly advantageous: in the combine harvester, the working mechanism spatially located behind the secondary shaft is constituted by a shredder mechanism. The shredder mechanism comprises a shredder drive shaft which is coupled to a transmission by means of a shredder belt in a torque-transmitting manner. Advantageously, the chopping belt cooperates with the following belt pulley of the transfer device: the diameter of the belt pulley can be varied in the above-mentioned manner. In this way, the transmission ratio between the secondary shaft and the shredder mechanism can be changed, since the frequency of the transmission belt (that is to say the revolution of the transmission belt per time unit) changes as a result of the changing diameter of the respective belt pulley of the transmission device remaining unchanged. Here, like the above-described processing method, the change or adjustment of the rotational speed of the shredder mechanism is also effected mechanically in a particularly simple manner by merely changing the diameter of the belt pulley of the transmission. For example, it is conceivable to remove the respective belt pulley from the shaft of the transfer device and replace it with a belt pulley of another diameter.

The combine harvester according to the invention is further configured such that it comprises a tensioning device which interacts with the chopping belt, said tensioning device having two tensioning wheels which are spaced apart from one another. The tensioning device can be switched between at least two different tensioning positions, wherein the tensioning device, when present in a first tensioning position, is adapted to co-act with a chopping belt in operative connection with a belt pulley of a first diameter of the transfer device. Accordingly, the tensioning device is adapted to co-act, when present in its second tensioning position, with a chopping belt in operative connection with a belt pulley of the transfer device having a second diameter. Advantageously, the chopping belt and the tensioning device co-act such that the winding angle of the chopping belt in total around the tensioning wheel is assumed differently when the tensioning device is present in its two tensioning positions, respectively. In particular, it is conceivable for the chopping belt to be in contact with the outer lateral surfaces of the two tensioning rollers in total along a winding angle which is smaller when the chopping belt interacts with a first belt pulley of the transfer device than when the chopping belt interacts with a second belt pulley of the transfer device, which has a smaller diameter than the first belt pulley.

Similar to the above explanations in connection with threshing belts, it is noted that the chopping belt extends along a spatially varying line depending on the configuration of the belt pulley aspect of the transfer device, so that the tensioning device has to adjust its spatial position on the first side of the combine harvester in order to exert its tensioning effect independently of the line of the chopping belt. Furthermore, the tensioning device can be used in particular for receiving a length which becomes free during the switching of the shredding belt from its position into its other position, so that the shredding belt can be kept tensioned and does not have to be exchanged with a further length of shredding belt. The configuration of the tensioning device with two tensioning wheels is particularly advantageous here, since a change in the position of the tensioning device in space is particularly simple to implement.

In particular, it is conceivable for the tensioning device itself to be of oscillating design about a bearing axis parallel to the chopping drive shaft. It is to be understood here that such a bearing axis is arranged eccentrically with respect to at least one of the tensioning wheels of the tensioning device, so that during the pivoting of the tensioning device about the bearing axis, the at least one tensioning wheel is moved on a circular path about the bearing axis. The change of the position of the tensioning device can be carried out particularly simply in this way, so that the tensioning device can follow the changing course of the chopping belt particularly simply and can keep it tensioned. Preferably, the bearing axis of the tensioning device coincides with the axis of rotation of one of the tensioning wheels.

Furthermore, the following embodiments of the combine harvester according to the invention are particularly advantageous: in the above-described embodiment, the operating mechanism located spatially behind the auxiliary shaft is constituted by a shut-off mechanism. Such a working mechanism interacts, for example, with an axial cutting rotor, the longitudinal axis of which extends parallel to a vertical longitudinal plane of the combine harvester, which contains the longitudinal axis of the combine harvester. The cutting mechanism interacts with a cutting mechanism drive shaft which extends from the cutting mechanism to a first side of the combine harvester. The shut-off mechanism drive shaft is coupled to the transmission device by means of a shut-off belt in a torque-transmitting manner, so that the shut-off mechanism is also connected, at least indirectly like a possible shredder mechanism, to the secondary shaft and thus to the motor output shaft in a torque-transmitting manner. Advantageously, the shut-off mechanism drive shaft is equipped with two coaxially arranged belt discs, wherein the diameter of the first belt disc exceeds the diameter of the second belt disc. This configuration is similar to the configuration of the threshing cylinder described above, in which the cut-off belt can selectively co-act with one of the two belt discs. In this way, the cutoff belt is able to switch between a slow position and a fast position, wherein the cutoff belt engages the first belt pulley when in its slow position and engages the second belt pulley when in its fast position. In this way, the shut-off drive shaft is operated at different rotational speeds, i.e. at a fast rotational speed and a slow rotational speed, while the frequency of the transmission belt remains unchanged. The change in the rotational speed of the drive shaft of the shut-off mechanism is effected analogously to the above description particularly simply by shifting the shut-off belt from one pulley to the respective other pulley. Here, the cut-off belt itself does not have to be changed; in particular the length of the cut-off belt remains the same.

In a particularly advantageous embodiment, the shut-off mechanism drive shaft is operated even in four different transmission ratios, wherein, on the one hand, two different transmission ratios can be set by means of two belt pulleys of the shut-off mechanism drive shaft and two further transmission ratios can be achieved by means of a change in the diameter of the belt pulley of the transmission device. In this connection, reference is made to the explanations above in connection with the transfer device, which can have at least one belt pulley with a variable diameter. By means of such a configuration, the cutoff belt can be operated in four different permutations and in this way in four different transmission ratios between the frequency of the transmission belt and the frequency of the cutoff belt. These combinations are made up of different diameters of the pulley of the transmission device and the pulley of the cutting mechanism drive shaft, wherein the aforementioned combinations can be made up as follows: "major diameter-major diameter", "minor diameter-minor diameter", and "major diameter-minor diameter". This results particularly well from the examples described below.

In a particularly advantageous embodiment, the two belt discs of the shut-off mechanism drive shaft are designed in the form of a belt disc set which is connected thereto as a whole in a manner such that it can be removed from the shut-off mechanism drive shaft without damage. In this way, the belt pulley set can be removed as a whole from the shut-off mechanism drive shaft, turned over and fitted again on the shut-off mechanism drive shaft. Thereby, the order of the pulley (from the cutting mechanism) in terms of the different diameters of the pulley is changed from "large-small" to "small-large". Thus, the cut-off belt can co-act with the larger pulley when the pulley set is present in the first position and with the smaller pulley when the pulley set is present in the second position, without having to make a change in the orientation of the cut-off belt in space. By means of such a change, therefore, only the course of the cutting belt within a plane within which the cutting belt extends is changed, whereas the orientation of this plane relative to the combine harvester is maintained irrespective of whether the cutting belt is present in its slow position or its fast position.

Advantageously, the cut-off belt also interacts with a tensioning device having two tensioning rollers spaced apart from one another. The tensioning device is switchable between two different tensioning positions, wherein the tensioning positions correspond to different positions of the severed belt. Due to the different course of the cutting belts when present at different positions thereof, the winding angles at which the cutting belts are wound respectively in total around the tensioning pulley are different in the respective tensioning positions of the tensioning device. This is particularly simple to follow from the following examples. The convertibility of the tensioning device between its tensioning positions offers the following possibilities: the cutting belt is kept tensioned according to its course, ensuring a reliable transmission of torque from the transmission device to the cutting mechanism drive shaft.

Advantageously, the tensioning device is configured to be pivotable about a bearing axis parallel to the drive shaft of the severing mechanism, wherein the bearing axis preferably coincides with the axis of rotation of one of the tensioning wheels. The respective configuration has already been explained above in connection with a tensioning device which can cooperate with the chopping belt. Accordingly, advantages are obtained.

In a further preferred embodiment, the chopping belt of the chopping mechanism and the chopping belt of the chopping mechanism co-act on the transfer device with the same belt pulley having a diameter which is variable in the manner described above. In particular, it is conceivable that the aforementioned belt pulley of the transfer device has a width which corresponds at least to the sum of the widths of the chopping belt and the cutting belt, so that the chopping belt and the cutting belt can run on the belt pulley side by side to some extent. This configuration has particular advantages: the transmission ratio between the transfer device and the shredding mechanism and between the transfer device and the severing mechanism can be changed by changing the diameter of the belt pulley in a single operation. Furthermore, such synchronized changes are particularly interesting, since (typically) changes in the external environment (for example the fruit to be harvested) determine the same change in the optimal rotational speed of the severing mechanism drive shaft and the chopping drive shaft.

Drawings

The combine harvester according to the invention is explained in more detail below with reference to the embodiments shown in fig. 1 to 7. It shows that:

FIG. 1: according to the vertical longitudinal section of the combine harvester of the invention,

FIG. 2: a perspective view of the drive system on a first side of the combine harvester according to figure 1,

FIG. 3: a perspective view of the drive system on the second side of the combine harvester according to figure 1,

FIG. 4: according to the view of fig. 3, in which the threshing belt is in a changed position,

FIG. 5: a view of the drive system on a first side of the combine,

FIG. 6: according to the view of fig. 5, in which the chopping belt and the severing belt are respectively in a changed position,

FIG. 7: the view according to fig. 5, wherein the cut-off belt is in a changed position.

Detailed Description

The embodiment shown in fig. 1 to 7 comprises a combine harvester 1 according to the invention, which is equipped with a plurality of working mechanisms and a motor 38. Furthermore, the combine harvester 1 comprises in its front end an adapter 41, which here is constituted by an inclined ramp conveyor with built harvester cutter bars. In particular, the combine harvester 1 interacts with the threshing cylinder 4, the cutting mechanism 39 and the chopping mechanism 40. For driving these working mechanisms, the combine harvester 1 comprises a drive system, which is derived in particular from fig. 2 to 7.

The drive system comprises a combination of a shaft, a belt pulley and a force transmission belt, which enable the transmission of torque from the motor output shaft 2 to different operating mechanisms, so that the operating mechanisms can be driven. The motor output shaft 2 extends from the motor 38 in the direction of the first side 6 of the combine harvester 1. This is to be seen in particular from fig. 2, wherein the motor 38 itself is not shown. The motor output shaft 2 interacts with at least one belt pulley, so that it is suitable for receiving a motor belt 7, by means of which the torque provided by the motor 38 can be transmitted to the secondary shaft 3. In the embodiment shown, the latter has a plurality of belt discs, so that the secondary shaft 3 is adapted to receive the motor belt 7 and to distribute the torque provided in this way over the combine harvester 1 by means of a further force transmission belt. Furthermore, the motor belt 7 interacts with a tensioning device 42, by means of which the motor belt 7 can be kept tensioned.

The secondary shaft 3 extends transversely to the combine harvester 1 from a first side 6 to a second side 9 of the combine harvester 1, which is opposite the first side 6. The longitudinal axis of the secondary shaft 3 extends here at least substantially perpendicularly to the longitudinal axis 8 of the combine harvester 1. The following possibilities are achieved by means of the guidance of the countershaft 3 from the first side 6 to the second side 9: the drive torque of the motor 38 is distributed to the respective working mechanism on both

sides

6, 9 of the combine harvester 1. According to the invention, the countershaft 3 interacts with an operating means (viewed in the longitudinal direction of the combine harvester 1) arranged spatially behind the countershaft 3 on a first side 6 of the combine harvester 1, while the countershaft 3 interacts with an operating means spatially in front of the countershaft 3 on a second side 9. It is also possible to achieve the attachment of the attachment 41 on the second side 9 of the combine harvester 1, wherein the attachment 41 is arranged spatially on the combine harvester 1 in front of the countershaft 3.

On the second side 9 of the combine harvester 1, which is derived in particular from fig. 3 and 4, the countershaft 3 is also equipped with a belt pulley 45, which is configured here as a transmission. In this way, the effective diameter of the belt pulley 45, on which the respective force transmission belt is guided, can be changed, as a result of which the transmission ratio starting from the countershaft 3 to the respectively downstream device can be changed. In the embodiment shown, the countershaft 3 interacts with a transmission 17 on the second side 9 of the combine harvester 1 by means of a transmission belt 18. The transmission is in turn connected in torque-transmitting fashion to one of the two

belt discs

11, 12 of the threshing cylinder drive shaft 5 by means of a threshing belt 10. The threshing cylinder drive shaft 5 is assigned to the threshing cylinder 4, wherein the threshing cylinder 4 can be driven in rotation by means of the transmission of a torque to the threshing cylinder drive shaft 5. The two

belt discs

11, 12 of the threshing cylinder drive shaft 5 have different diameters. The following possibilities are thereby achieved: the transmission ratio between the transmission 17 and the threshing cylinder drive shaft 5 is changed by means of a displacement of the threshing belt 10 from one of the

belt discs

11, 12 to the respective

other belt disc

11, 12. In this regard, no change in the frequency of the transmission belt 18 is required. In this way, a particularly simple change of the operating rotational speed of the threshing cylinder 4 is achieved, for which only the threshing belt 10 has to be transferred from one of the

belt discs

11, 12 to the respective

other belt disc

11, 12.

Since the threshing belt 10 runs in space along different paths depending on the co-action with one of the

belt discs

11, 12, there is the following necessity: the tensioning device 13 co-acting with the threshing belt 10 is tracked as its position changes, so that it continues to be in tensioning engagement with the threshing belt 10. In the exemplary embodiment shown, the tensioning device 13 comprises an arm 15, which is mounted on the combine harvester 1 so as to be pivotable about a bearing axis 14. At the end facing away from the bearing axis 14, a tensioning wheel 16 is arranged on the arm 15, said tensioning wheel being rotatably mounted on the arm 15. The tensioning wheel 16 is fixed to the arm 15 on one side, so that it extends in one direction from the side of the arm 15. For the purpose of changing the tensioning position of the tensioning device 13 during a change of position of the threshing belt 10, the tensioning wheel 16 is fitted only on the opposite side of the arm 15, whereby its position in space changes in line with the lateral displacement of the line of the threshing belt 10. Furthermore, the arm 15 is swung about the bearing axis 14, whereby the tensioning device 13 overall traces the changing course of the threshing belt 10. As a result, the following possibilities are achieved in a structurally particularly simple manner by means of the combination of the tensioning device 13 and the two belt pulleys 11, 12 of the threshing cylinder drive shaft 5: the transmission ratio between the secondary shaft 3 and the threshing cylinder 4 is changed by means of a small number of manual operations. This offers the following possibilities to the user of the combine harvester 1: smoothly and with little technical expenditure, to react to changing harvesting conditions and/or to changing crops to be harvested by means of the combine harvester 1.

On the first side 6 of the combine harvester 1, the countershaft 3 is connected in a torque-transmitting manner to a transmission 19 by means of a transmission belt 20, wherein the transmission belt 20 interacts with a belt pulley 22 of the transmission 19. The transmission device 19 can also be referred to as a so-called "drive point". Starting from the transmission 19, the torque supplied is distributed in the exemplary embodiment shown to two further operating mechanisms of the combine harvester 1, namely a cutting mechanism 39 and a shredder mechanism 40. The interaction of the transfer device 19 with the severing mechanism 39 and the shredder mechanism 40 results particularly well from fig. 5 to 7.

The cutting mechanism 39 cooperates with a cutting mechanism drive shaft 25, which is driven for the operation of the cutting mechanism 39. The cutting mechanism drive shaft 25 is connected to the transmission device 19 by means of a cutting belt 24 in a torque-transmitting manner, wherein the cutting belt 24 is connected to the first belt pulley 21 on the transmission device 19. Furthermore, the cutting belt 24 interacts with a tensioning device 28, by means of which the cutting belt 24 can be kept tensioned. In a particularly advantageous manner, the shut-off mechanism drive shaft 25 is provided with two belt discs 26, 27 having mutually different diameters. The cutting belt 24 is basically adapted to selectively co-act with one of said two belt discs 26, 27, whereby the frequency of the cutting mechanism drive shaft 25 can be varied while the frequency of the transmission belt 20 and thus of the transmission device 19 remains unchanged. For this purpose, it is basically only necessary to transfer the cut-off belt 24 from one of the two belt pulleys 26, 27 onto the respective other belt pulley 26, 27. In the illustrated embodiment, the two belt discs 26, 27 of the shutoff mechanism drive shaft 25 are bundled into a belt disc pack which as a whole is configured to be removable from the shutoff mechanism drive shaft 25. In this way, a rotation of the pulley set is achieved, so that the sequence of the pulleys 26, 27 along the cutting-off mechanism drive shaft 25 is changed from the cutting-off mechanism 39.

The following possibilities are therefore achieved by means of the mentioned "turning over" of the belt pulley set: the transfer of the cutting belt 24 from one of the belt pulleys 26, 27 onto the respective other belt pulley 26, 27 is effected without changing the course of the cutting belt 24 with respect to its orientation in space relative to the vertical longitudinal plane of the combine harvester 1. In other words, although the line of severing of the belt 24 changes due to the replacement of one of the pulleys 26, 27 to the respective other pulley 26, 27, the plane in which the severing of the belt 24 lies is maintained at least substantially, preferably completely, as long as the set of pulleys is turned over. This is particularly advantageous due to the length of the cut-off belt 24, since otherwise a change in the orientation of the plane of the cut-off belt 24 would also cause a change in the position of the tensioning device 28, which cannot easily be achieved mechanically.

The tensioning device 28 can also be moved between different tensioning positions, so that it is suitable for reliably tensioning the cut-off belt 24 despite changes in its course. The tensioning device 28 has two tensioning

wheels

29, 30 which are arranged at mutually opposite ends of the arms and are connected to one another in this way. The tensioning device 28 is mounted so as to be pivotable about a bearing axis 31, the bearing axis 31 coinciding with the axis of rotation of the tensioning wheel 29. The pivoting of the tensioning device 28 about the bearing axis 31 moves the tensioning wheel 30 facing away from the bearing axis 31 along a circular path about the bearing axis 31, as a result of which a particularly simple possibility of tracking the cutting belt 24 during the changeover on the cutting-off mechanism drive shaft 25 is achieved. In order to be able to pivot the tensioning device 28 about its bearing axis 31, it interacts in the illustrated embodiment with a drive device 43, which is formed by a piston-cylinder unit. The piston cylinder unit acts with its piston on the lever arm of the tensioning device 28, so that a torque can be applied to the tensioning device 28 by means of the piston being moved in or out, by means of which the latter can be pivoted about its bearing axis 31. Furthermore, the tensioning device 28 can be fixed in its correspondingly adjusted tensioning position by means of the fixing of the drive device 43. The different tensioning positions of the tensioning device 28 can be seen particularly well in fig. 5 to 7.

In order to adjust the ratio between the frequencies of the transfer belt 20 and the cutting belt 24 to a greater extent, the diameter of the belt pulley 21 can be configured variably on the transfer device 19. In particular, the belt pulley 21 can be replaced by a further belt pulley 23, which further belt pulley 23 is then arranged on the transfer device 19 in the same position. By means of such a replacement, the diameter of the belt pulley 21 is changed in the sense of the present application in such a way that the belt pulley 21 is replaced by a belt pulley 23 of another diameter. In the shown embodiment the diameter of the belt pulley 21 is larger than the diameter of the belt pulley 23. The transmission ratio between the transfer belt 20 and the cutting belt 24 is changed by means of a change in the diameter of the pulley 21 or its replacement with another pulley of another diameter. As a result, the cutting mechanism drive shaft 25 is thus operated at a changed rotational speed with the frequency of the transmission belt 20 maintained, whereby it is possible to react to changed harvesting conditions or other situations in the manner described above.

In the exemplary embodiment shown, in general, four combinations of

belt discs

21, 23, 26, 27 are realized in the interaction of the transmission device 19 and the cutting-off mechanism drive shaft 25, with which belt discs an engagement with the cutting belt 24 can be produced. Fig. 5 to 7 show combinations of "large diameter-small diameter", "small diameter-small diameter", and "large diameter-large diameter" in this order. The tensioning device 28 can be brought into different tensioning positions depending on the different positions of the cut-off belt 24, wherein the winding angle of the two

tensioning rollers

29, 30 of the cut-off belt 24 which together wind around the tensioning device 28 changes depending on the tensioning position. In this way the following possibilities are provided: receiving the free length of the cut-off belt 24 provided depending on the position of the cut-off belt 24 and thereby keeping the cut-off belt 24 taut. In particular, the need to use different cut-off belts of different lengths is thereby eliminated.

Furthermore, proceeding from the transmission 19, the shredder mechanism 40 is indirectly connected to the countershaft 3 by means of a shredder belt 33 in a torque-transmitting manner. In the embodiment shown, the chopping belt 33 interacts with the same belt discs 21, 23 of the transfer device 19, with which the chopping belt 24 also interacts accordingly. For this purpose, the respective belt pulley 21, 23 has a width which enables it to receive the cut-off belt 24 and the chipped belt 33 side by side. The shredder mechanism 40 interacts with the shredder drive shaft 32, which interacts with the shredder belt 33 by means of a belt pulley 46 fixedly assigned thereto. In the embodiment shown, the change in the transmission ratio between the transfer belt 20 and the chopping belt 33 is effected solely by means of a change in the diameter of the pulley 21 on the transfer device 19, wherein this change can be effected in the manner described above here by means of a replacement of the pulley 21 with a pulley 23 of smaller diameter.

Similarly to the above description, the chopping belt 33 also interacts with a tensioning device 34 assigned thereto, which, like the tensioning device 28 of the chopping belt 24, has two tensioning

rollers

35, 36 spaced apart from one another. Furthermore, the tensioning device 34 is mounted so as to be pivotable about a bearing axis 37, which coincides with the axis of rotation of the tensioning wheel 35. In this way, the tracking of the tensioning device 34 in accordance with the change in the path of the chopping belt 33 in space is achieved particularly simply, wherein the pivoting of the tensioning device 34 takes place in a particularly simple manner by means of a drive 44 which is constructed and functions analogously to the drive 43 of the tensioning device 28 according to the above description.

List of reference numerals

1 combine harvester

2 Motor driven shaft

3 auxiliary shaft

4 threshing cylinder

5 threshing cylinder driving shaft

6 first side

7 motor belt

8 longitudinal axis

9 second side

10 threshing belt

11 Belt pulley

12 belt pulley

13 tensioning device

14 axis of support

15 arm

16 tensioning wheel

17 speed variator

18 speed variator belt

19 transfer device

20 transfer belt

21 belt pulley

22 belt pulley

23 Belt pulley

24 cutting belt

25 cutting mechanism driving shaft

26 Belt pulley

27 Belt pulley

28 tensioning device

29 tensioning wheel

30 tensioning wheel

31 axis of support

32 chopping drive shaft

33 chopping belt

34 tensioning device

35 tensioning wheel

36 tension wheel

37 axis of support

38 motor

39 cutting off the rotor

40 shredding mechanism

41 attachment

42 tensioning device

43 drive device

44 drive device

45 leather belt disc

46 Belt pulley

Claims

1. A combine harvester (1) comprising

A motor (38) having a motor driven shaft (2),

-a secondary shaft (3), and

-a plurality of working mechanisms,

wherein the motor output shaft (2) extends from the motor (38) in the direction of a first side (6) of the combine harvester (1),

wherein the motor output shaft (2) and the countershaft (3) are coupled to each other by means of at least one motor belt (7) in a torque-transmitting manner,

it is characterized in that the preparation method is characterized in that,

on a first side (6) of the combine harvester (1) a transmission device (19) is arranged, which is coupled with the secondary shaft (3) in a torque-transmitting manner by means of a transmission belt (20), and

the auxiliary shaft (3) extends from a first side (6) of the combine harvester (1) in a direction transverse to a longitudinal axis (8) of the combine harvester (1) to a second side (9) of the combine harvester (1) opposite to the first side (6),

wherein a torque provided by the countershaft (3) can be transmitted on the first side (6) of the combine harvester (1) by means of the transmission device (19) to the following operating means of the combine harvester (1) by means of a corresponding force transmission belt: the working mechanism is arranged spatially behind the secondary shaft (3) as seen in the longitudinal direction of the combine harvester (1), and

wherein the torque provided by the countershaft (3) can be transmitted on the second side (9) of the combine harvester (1) by means of a respective force transmission belt to the following operating mechanisms of the combine harvester (1): the working mechanism is arranged spatially in front of the secondary shaft (3) as seen in the longitudinal direction of the combine harvester (1).

2. Combine harvester (1) according to claim 1, characterized in that the operating mechanism spatially in front of the secondary shaft (3) is formed by a threshing cylinder (4), wherein the secondary shaft (3) is coupled in a torque-transmitting manner with a threshing cylinder drive shaft (5) of the threshing cylinder (4) at least indirectly by means of at least one threshing belt (10), wherein preferably the threshing cylinder drive shaft (5) is provided with two coaxially arranged belt discs (11, 12), wherein a first belt disc (11) has a diameter which exceeds a diameter of the second belt disc (12), wherein the threshing belt (10) cooperates with the first belt disc (11) when present in the slow position and with the second belt disc (12) when present in the fast position, such that the rotational speed of the threshing cylinder drive shaft (5) can be changed between a slow rotational speed and a fast rotational speed with the same frequency of the threshing belt (10).

3. Combine harvester (1) according to claim 2, characterized in that it has a tensioning device (13) which can be operated in two different tensioning positions, wherein the tensioning device (13) in its first tensioning position is adapted to tension a threshing belt (10) in its slow position of the threshing belt, wherein the tensioning device (13) in its second tensioning position is adapted to tension a threshing belt (10) in its fast position of the threshing belt.

4. A combine harvester (1) according to claim 3, characterised in that the tensioning device (13) has an arm (15) which is pivotable about a bearing axis (14), on the end of which arm facing away from the bearing axis (14) a tensioning wheel (16) is arranged which is rotatable about the centre axis of the bearing axis.

5. A combine harvester (1) according to claim 4, characterised in that the tensioning wheel (16) extends away from a first side of the arm (15) when the tensioning device (13) is present in its first tensioning position and from a second side of the arm (15) opposite the first side when the tensioning device (13) is present in its second tensioning position.

6. A combine harvester (1) according to any one of claims 1 to 5, characterised in that it has a transmission (17) which is arranged on the second side (9) of the combine harvester (1), wherein the transmission (17) is coupled with the countershaft (3) in a torque-transmitting manner by means of at least one transmission belt (18).

7. Combine harvester (1) according to any one of claims 1 to 6, characterized in that the transfer device (19) comprises a plurality of belt pulleys (21, 22), wherein preferably the diameter of at least one belt pulley (21) can be changed, in particular the belt pulley (21) can be replaced with another belt pulley (23) of a different diameter.

8. A combine harvester (1) according to any one of claims 1 to 7, the working mechanism spatially behind the secondary shaft (3) is formed by a shredder mechanism (40) comprising a shredder drive shaft (32), wherein the chopping drive shaft (32) is coupled with the transmission device (19) in a torque-transmitting manner by means of a chopping belt (33), wherein preferably the chopping drive shaft (32) is provided with two coaxially arranged belt discs, wherein the diameter of the first belt pulley exceeds the diameter of the second belt pulley, wherein the chopping belt (33) cooperates with the first belt pulley when present in the slow position and with the second belt pulley when present in the fast position, so that the rotational speed of the chopping drive shaft (32) can be changed between a slow rotational speed and a fast rotational speed with the same frequency of the chopping belt (33).

9. Combine harvester (1) according to claim 8, characterized in that it has a tensioning device (34) which interacts with the chopping belt (33) and has two mutually spaced-apart tensioning wheels (35, 36), wherein in a first tensioning position of the tensioning device the chopping belt (33) cooperates with a first belt pulley (21) of the transfer device (19), and wherein the chopping belt (33) in total winds around the tensioning wheels (35, 36) by a winding angle which differs when the tensioning device (34) is present in its first tensioning position from a winding angle which occurs when the tensioning device (34) is present in its second tensioning position in which the chopping belt (33) cooperates with a second belt pulley (23) of the transfer device (19).

10. Combine harvester (1) according to claim 9, characterized in that the tensioning device (34) is configured swingably about a bearing axis (37) parallel to the chopping drive shaft (32), wherein the bearing axis (37) preferably coincides with the axis of rotation of one of the tensioning wheels (35, 36).

11. Combine harvester (1) according to one of the claims 1 to 10, characterised in that the operating mechanism which is located spatially behind the secondary shaft (3) is formed by a cut-off mechanism (39), preferably with an axial cut-off rotor, wherein, on a first side (6) of the combine harvester (1), the transmission device (19) is coupled in a torque-transmitting manner with a cut-off mechanism drive shaft (25) of the cut-off mechanism (39) by means of a cut-off belt (24), wherein the cut-off mechanism drive shaft (25) is provided with two coaxially arranged belt discs (26, 27), wherein the diameter of the first belt disc (26) exceeds the diameter of the second belt disc (27), wherein the cut-off belt (24) cooperates with the first belt disc (26) when present in the slow position and cooperates with the second belt disc (27) when present in the fast position, so that the rotational speed of the cutting mechanism drive shaft (25) can be changed between a slow rotational speed and a fast rotational speed with the same frequency of the cutting belt (24).

12. A combine harvester (1) according to claim 11, characterised in that the two belt discs (26, 27) of the severing mechanism drive shaft (25) constitute a belt disc pack which as a whole is arranged on the severing mechanism drive shaft (25) in a reversible manner such that a belt disc (26) having selectively a larger diameter or a belt disc (27) having a smaller diameter is located on the side of the belt disc pack facing away from the severing mechanism (39).

13. A combine harvester (1) according to claim 11 or 12, characterised in that it has a tensioning device (28) which interacts with the cutter belt (24) and which has two mutually spaced-apart tensioning wheels (29, 30), wherein the tensioning device (28) can be switched between different tensioning positions, in which case the winding angles of the cutter belt (24) in total around the tensioning wheels (29, 30) respectively appear differently.

14. Combine harvester (1) according to claim 13, characterized in that the tensioning device (28) is configured to be pivotable about a bearing axis (31) parallel to the cutting-off mechanism drive shaft (25), wherein the bearing axis (31) preferably coincides with the axis of rotation of one of the tensioning wheels (29, 30).

15. A combine harvester (1) according to claims 8 and 11, characterised in that the cutting belt (24) of the cutting mechanism (39) and the chopping belt (33) of the chopping mechanism (40) co-act on the transfer device (19) with the same belt pulley (21), wherein preferably the width of the belt pulley (21) exceeds the sum of the widths of the cutting belt (24) and the chopping belt (33).