PTO gearbox and agricultural vehicle

Description

[0001] The invention relates to a power take-off transmission according to the preamble of independent claim 1 and to an agricultural utility vehicle according to the preamble of independent claim 14.

[0002] Power output shafts, also called output shafts, and especially power take-off shafts, are typically located at the front and / or rear of agricultural vehicles. These shafts supply power to implements or machinery attached to the vehicle and used in fieldwork. These implements or machinery may require different drive torques and speeds. Therefore, power take-off gearboxes are known that provide different speeds. These gearboxes can also allow switching between operating modes of the power take-off shaft when the vehicle is unloaded.

[0003] With a view to the various agricultural implements, the rated speeds of PTO shafts are now standardized. Nominal speeds of 540 revolutions per minute, 750 revolutions per minute, 1000 revolutions per minute and 1400 revolutions per minute have become established (standard gear ratio). These nominal speeds, also known as gear steps or gear ratios, are present on the output shaft or PTO shaft in the range of the rated engine speed (maximum power). At lower engine speeds, the rated speeds of the output shaft or PTO are therefore not reached. The rated speed of the output shaft or PTO is therefore referred to as the gear step or gear ratio. For example, if the speed on the drive shaft side is 2300 rpm (rated engine speed), a gear ratio of 540 means that the speed on the output shaft or PTO is 540 rpm.A gear ratio of 1000 indicates a rotational speed of 1000 rpm. For agricultural implements with low power consumption, operating the output shaft or PTO at the engine's rated speed is not necessary. For this purpose, PTO gearboxes with so-called economy gear ratios have become established in recent years. With economy gear ratios 540E and 1000E, for example, rated speeds of 540 and 1000 rpm, respectively, are already available at a reduced engine speed, usually near the engine's maximum torque, at approximately 1400 to 1600 rpm. This makes it possible to operate implements with low power consumption in a fuel-efficient manner. This allows for savings in fuel consumption and drive energy. German patents DE 10 2011 084 623 A1 and DE 10 2016 220 130 A1 disclose PTO gearboxes with load-free PTO engagement.The disadvantage here is that known PTO transmissions have an overly complex design, for example, they comprise too many gears and shifting elements and / or require too much installation space. EP 3 715 668 A1 discloses a power transmission transmission in which each clutch is arranged on a countershaft.

[0004] The present invention is based on the object of proposing a power take-off transmission and a commercial vehicle that overcome the aforementioned problems. In particular, a power take-off transmission and a commercial vehicle are to be proposed that are structurally less complex and / or that have a more compact design.

[0005] This object is achieved by a power take-off transmission having the features of claim 1 and an agricultural utility vehicle having the features of claim 14. The dependent claims relate to particularly advantageous embodiments of the invention.

[0006] According to the invention, a power take-off (PTO) transmission for an agricultural vehicle is proposed. The PTO transmission comprises an input shaft, an output shaft, a first and a second intermediate shaft, and a first gear stage. The gear stage is arranged, and in particular designed, such that the input shaft has a first fixed gear, the first intermediate shaft has a second fixed gear, and the second intermediate shaft has a third fixed gear, wherein only the first fixed gear meshes with the second fixed gear and the first fixed gear meshes with the third fixed gear. Thus, only the first and second fixed gears and the first and third fixed gears mesh with each other. The input shaft is designed as a hollow shaft, and the output shaft is arranged at least partially within the input shaft.

[0007] Specifically, the second fixed gear and the third fixed gear can be identical. This allows the distance between the output shaft and the first intermediate shaft, as well as the distance between the output shaft and the second intermediate shaft, to be identical, particularly in magnitude. A fixed gear can be a gear that is rotationally fixed on the shaft associated with it. A loose gear, on the other hand, can be a gear that is rotatably mounted on the shaft associated with it. The switching elements of the present invention make it possible to connect the gears to a shaft in a rotationally fixed manner or to operate them in freewheel mode. Thus, the loose and / or fixed gears can be switched using a switching element.Due to the switchable nature of the gears, i.e., the loose and / or fixed gears, of the present invention, a customized switching strategy can be implemented, whereby the switchable gears can optionally have a freewheel or be connected to the respective associated shaft or to another shaft. In the neutral position, the gears can, for example, run freely and transmit no power. Furthermore, a connection can be established between the shafts by means of the switchable gears.

[0008] The input and output shafts are arranged coaxially. Alternatively, the input and / or output shafts and / or the first and / or second intermediate shafts can be arranged parallel to each other. Furthermore, the output shaft can be arranged offset from the first and second intermediate shafts.

[0009] Furthermore, the switching elements, in particular a first switching element and / or a second switching element and / or a third switching element, can have a neutral position. Likewise, the first switching element and / or the second switching element and / or the third switching element can be configured to be switchable under load or under no load. A switching element can be designed in a known form as a jaw coupling or as an actuating device, in particular sliding sleeves, and synchronizer rings comprising switching packages or synchronizers. The switching elements can be actuated or switched mechanically via corresponding levers or by means of an actuator (hydraulic, pneumatic, or electromechanical). Actuation can be manual or automatic.In any case, a switching element can be a coupling element arranged in a rotationally fixed manner and axially displaceable on the shaft associated with the switching element. This coupling element allows the loose and / or fixed gears to be connected to the shaft associated with the switching element in a rotationally fixed manner for engaging a transmission. The axial displacement of the coupling elements can be effected via the actuating element. For this purpose, the power take-off (PTO) transmission can include corresponding actuating elements, or, in particular, each switching element can include an actuating element. The switching assemblies or synchronizers can comprise actuating devices or sliding sleeves that are axially displaceable on the associated shaft but rotationally fixed to the shaft, and synchronizer rings arranged axially adjacent to it, i.e., to the right and / or left of the actuating device or sliding sleeve. The actuating device or sliding sleeve, or the actuating element, can be manually or power-assisted to actuate the switching elements.For this purpose, the PTO transmission can, for example, comprise an actuator, in particular a piston-cylinder arrangement, so that the actuating device or actuating element can be actuated with auxiliary power. The actuator, in particular the piston-cylinder arrangements, can be operated by a hydraulic or pneumatic pressure medium. The PTO transmission can have a first gear ratio and / or a second gear ratio and / or a third gear ratio and / or a fourth gear ratio. The following applies to the gear ratio: first gear ratio < second gear ratio < third gear ratio < fourth gear ratio.

[0010] A key aspect of the invention is that the power take-off (PTO) gearbox provides multiple gears or transmission stages, in particular four transmission stages, which enable different speeds and / or different power outputs for the PTO during operation. Advantageously, a compact and structurally simple PTO gearbox is provided. Furthermore, the PTO gearbox makes it possible to operate the engine economically while simultaneously driving the agricultural implement at the rotational speed for which it is designed.

[0011] In an embodiment of the invention, the power take-off (PTO) transmission, in particular the output shaft, comprises a first switching element. The first fixed gear, and / or in particular the input shaft, can be connected and / or coupled to the output shaft by means of or via the first switching element, preferably in a rotationally fixed manner, and more preferably in a releasable rotationally fixed manner. The first switching element can be associated with the output shaft. In other words, the PTO transmission, in particular the output shaft, can have the first switching element for the rotationally fixed connection of the first fixed gear and / or the input shaft to the output shaft. Furthermore, the first gear stage can be switched by means of the first switching element. Thus, by actuating the first switching element, the first fixed gear and / or the input shaft can be rotationally fixed to the output shaft.The first switching element can be actuated such that it is movable, particularly axially in a first direction along the output shaft, into a first position, especially in the direction of the first fixed gear and / or the input shaft. The first fixed gear and / or the input shaft are thus connected to the output shaft via the first switching element. Therefore, torque and speed can be transmitted from the input shaft to the output shaft when the first fixed gear and / or the input shaft has a rotationally fixed connection to the output shaft via the first switching element, i.e., when the first switching element is actuated. The first switching element can thus be used to switch a power path that leads directly from the input shaft to the output shaft.When the first fixed gear and / or the input shaft is connected to the output shaft, i.e., the first switching element is actuated, a fourth gear stage with a PTO speed of 1000 revolutions per minute can be achieved with this first switching element during economical engine operation. Economical engine operation can be understood as engine operation at a reduced engine speed, where the drive motor can operate under partial or full load, i.e., rated speed. The fourth gear stage is assigned the gear ratio 1000E.

[0012] In an embodiment of the invention, the power take-off transmission, in particular the first intermediate shaft, has a second shifting element. With the second shifting element or by means of the second shifting element, the first intermediate shaft can be connected and / or coupled to the output shaft, preferably connected and / or coupled in a rotationally fixed manner, particularly preferably releasably connected and / or coupled in a rotationally fixed manner. The second shifting element can be assigned to the first intermediate shaft. In other words, the power take-off transmission, in particular the first intermediate shaft, can have the second shifting element for the rotationally fixed connection of an idler gear to the first intermediate shaft. One or two power paths can be switched using the second shifting element. One power path can correspond to a second gear ratio and leads in particular from the input shaft to the first intermediate shaft and then to the output shaft.When the second shifting element is actuated, in particular when it is in a first position, the second shifting element can be used to establish the second gear ratio with a PTO speed of 540 revolutions per minute during economical engine operation. The second shifting element is assigned gear ratio 540E. Another power path can correspond to a third gear ratio, which in particular also leads from the input shaft to the first intermediate shaft and from there to the output shaft. When the second shifting element is actuated, in particular when it is in a second position, the third gear ratio with a PTO speed of 1000 revolutions per minute at the rated speed of the drive engine can be achieved with the second shifting element. The third gear ratio is assigned gear ratio 1000.Advantageously, this allows multiple gear ratios, particularly three gear ratios, to be implemented with a simple PTO design. Furthermore, the PTO's installation space can be minimized.

[0013] In an embodiment of the invention, the power take-off transmission, in particular the second intermediate shaft, has a third shifting element. With the third shifting element or by means of the third shifting element, the second intermediate shaft can be connected and / or coupled to the output shaft, preferably connected and / or coupled in a rotationally fixed manner, particularly preferably releasably connected and / or coupled in a rotationally fixed manner. The third shifting element can be assigned to the second intermediate shaft. In other words, the power take-off transmission, in particular the second intermediate shaft, can have the third shifting element for the rotationally fixed connection of an idler gear to the second intermediate shaft. A further power path can be shifted with the third shifting element. The power path can correspond to a first gear ratio and leads in particular from the input shaft to the second intermediate shaft and then to the output shaft.When the third switching element is actuated, specifically when it is in its first position, the first gear ratio can be achieved with a PTO speed of 540 revolutions per minute at the rated speed of the drive motor. The 540 gear ratio is assigned to the first gear ratio. Advantageously, this allows for the implementation of multiple gear ratios, particularly a total of four gear ratios, with a structurally simple PTO gearbox design. Furthermore, this minimizes the installation space required for the PTO gearbox.

[0014] In an embodiment of the invention, the power take-off (PTO) gearbox comprises a first gear pair with two gears. The first gear pair can be coupled to the first intermediate shaft or output shaft. The first gear pair is arranged, and / or, in particular, designed such that the first intermediate shaft and the output shaft each have one gear. The gears of the first gear pair are in mesh, in particular between the output shaft and the first intermediate shaft; preferably, the gears of the first gear pair mesh permanently with each other. The first gear pair can comprise a first loose gear on the first intermediate shaft, in particular a first loose gear rotatably mounted on the first intermediate shaft and couplingable to the first intermediate shaft, and a fourth fixed gear on the output shaft, in particular a fourth fixed gear arranged non-rotatably on the output shaft.The first intermediate shaft can be connected to the output shaft via the second switching element, preferably via the first gear pair, and more preferably via the first loose gear and the fourth fixed gear. The first gear pair, particularly the first loose gear on the first intermediate shaft, can be switched by the second switching element. The first loose gear can be connected and / or coupled to the second intermediate shaft or to the first intermediate shaft via the second switching element, preferably in a rotationally fixed manner, and more preferably in a releasable rotationally fixed manner. In other words, the power take-off gearbox, particularly the first intermediate shaft, can have the second switching element for a rotationally fixed connection of the first loose gear to the output shaft. By actuating the second switching element, the first loose gear can thus be rotationally fixed to the output shaft.The second switching element can be actuated such that it is movable, particularly axially in a first direction along the first intermediate shaft, into a first position. The first loose gear is thus provided on the first intermediate shaft and is connected to the first intermediate shaft via the second switching element. This allows torque and rotational speed to be transmitted from the input shaft via the first fixed gear to the second fixed gear to the first intermediate shaft and then via the first loose gear to the fourth fixed gear to the output shaft, particularly if the first loose gear has a rotationally fixed connection to the first intermediate shaft via the second switching element, preferably when the second switching element is actuated, and most preferably when it is in a first position.Thus, especially when the first loose gear is connected to the first intermediate shaft, i.e., when the second switching element is actuated, the second transmission stage can be produced with the second switching element.

[0015] In an embodiment of the invention, the first gear pair comprises a fourth fixed gear on the first intermediate shaft, in particular a fourth fixed gear arranged on the first intermediate shaft in a rotationally fixed manner, and a first loose gear on the output shaft, in particular a first loose gear rotatably mounted on the output shaft and coupleable to the output shaft. The first intermediate shaft can be connected to the first shifting element or through the first shifting element, preferably via the first gear pair, particularly preferably via the first loose gear and the fourth fixed gear. The first gear pair, in particular the first loose gear on the output shaft, can be switchable with the first shifting element. The first loose gear on the output shaft can be connectable and / or coupled to the first or through the first shifting element, preferably connectable and / or coupled in a rotationally fixed manner, particularly preferably releasably connectable and / or coupled to the output shaft.In other words, the power take-off (PTO) gearbox, particularly the output shaft, can include a first switching element for the rotationally fixed connection of the first loose gear or the first fixed gear and / or the input shaft to the output shaft. By actuating the first switching element, the first loose gear can be rotationally fixed to the output shaft. For this purpose, the first switching element can be actuated in such a way that it is movable into a second position, particularly axially in a second direction opposite to the first along the output shaft. The first loose gear is thus located on the output shaft and is connected to the output shaft via the first switching element.This allows torque and speed to be transmitted from the input shaft via the first fixed gear to the second fixed gear to the first intermediate shaft, and from the first intermediate shaft via the fourth fixed gear and the first loose gear to the output shaft, particularly when the first loose gear has a rotationally fixed connection to the output shaft via the first switching element, preferably when the first switching element is actuated, and especially preferably in the second position. Thus, particularly when the first loose gear is connected to the output shaft, i.e., when the first switching element is actuated, the third gear ratio can be achieved with the first switching element, with a PTO speed of 1000 revolutions per minute at the rated speed of the drive motor.

[0016] As an advantageous measure, the power take-off transmission comprises a second gear stage which is arranged and in particular designed such that the output shaft has a fifth fixed gear and the first intermediate shaft has a second idler gear and the second intermediate shaft has a third idler gear, wherein only the fifth fixed gear engages with the second idler gear and the fifth fixed gear engages with the third idler gear, preferably permanently meshing with one another. The second gear stage can be shifted as follows. The first intermediate shaft can be connected to the output shaft with the second shifting element or through the second shifting element, preferably via the first gear stage, particularly preferably via the second idler gear and the fifth fixed gear. The second gear stage, in particular the second idler gear on the first intermediate shaft, can be shifted with the second shifting element.The second idler gear can be connected and / or coupled to the second intermediate shaft or, via the second shifting element, to the first intermediate shaft, preferably connected and / or coupled in a rotationally fixed manner, particularly preferably releasably connected and / or coupled in a rotationally fixed manner. In other words, the power take-off transmission, in particular the first intermediate shaft, can have the second shifting element for the rotationally fixed connection of the second idler gear to the first intermediate shaft. By actuating the second shifting element, the second idler gear can therefore be connected in a rotationally fixed manner to the first intermediate shaft. For this purpose, the second shifting element can be actuated such that it can be moved into a first position, in particular axially in a first direction along the first intermediate shaft.Similarly or additionally, the second switching element can be actuated such that it is movable into a second position, particularly axially in a second direction opposite to the first along the first intermediate shaft. The second loose gear is thus provided on the first intermediate shaft and is connected to the first intermediate shaft via the second switching element. A torque and a speed can be transmitted from the input shaft via the first fixed gear to the second fixed gear to the first intermediate shaft and then via the second loose gear to the fifth fixed gear to the output shaft, particularly if the second loose gear has a rotationally fixed connection to the first intermediate shaft via the second switching element, preferably when the second switching element is actuated, and most preferably when it is in a first position.Thus, particularly when the second loose gear is connected to the first intermediate shaft, i.e., when the second switching element is actuated, the second transmission stage can be produced using the second switching element. Likewise or additionally, torque and speed can be transmitted from the input shaft via the first fixed gear to the second fixed gear to the first intermediate shaft and then via the second loose gear to the fifth fixed gear to the output shaft, particularly when the second loose gear has a rotationally fixed connection to the first intermediate shaft via the second switching element, preferably when the second switching element is actuated, and especially preferably when it is in a second position. Thus, particularly when the second loose gear is connected to the first intermediate shaft, i.e., when the second switching element is actuated, the third transmission stage can be produced using the second switching element.The second intermediate shaft can be connected to the output shaft by the third shifting element or by the third shifting element, preferably via the second gear stage, particularly preferably via the third idler gear and the fifth fixed gear. The second gear stage, in particular the third idler gear on the second intermediate shaft, can be shifted by the third shifting element. The third idler gear can be connected and / or coupled to the third or, via the third shifting element, to the second intermediate shaft, preferably connected and / or coupled in a rotationally fixed manner, particularly preferably releasably connected and / or coupled in a rotationally fixed manner. In other words, the power take-off transmission, in particular the second intermediate shaft, can have the third shifting element for the rotationally fixed connection of the third idler gear to the second intermediate shaft. By actuating the third shifting element, the third idler gear can therefore be rotationally fixedly connected to the second intermediate shaft.For this purpose, the third shifting element can be actuated such that it can be moved into a first position, in particular axially in a first direction along the second intermediate shaft. The third idler gear is therefore provided on the second intermediate shaft and is connected to the second intermediate shaft via the third shifting element. As a result, a torque and a rotational speed can be transmitted from the input shaft via the first fixed gear to the third fixed gear to the second intermediate shaft and then via the third idler gear to the fifth fixed gear to the output shaft, in particular when the third idler gear has a rotationally fixed connection to the second intermediate shaft via the third shifting element, i.e. preferably when the third shifting element is actuated, i.e. particularly preferably when it is in a first position.Thus, especially when the third loose gear is connected to the second intermediate shaft, i.e., when the third switching element is actuated, the first transmission stage can be produced with the third switching element.

[0017] In an embodiment of the invention, the power take-off (PTO) gearbox comprises a second gear pair with two gears. The second gear pair can be coupled to the first intermediate shaft or output shaft. The second gear pair is arranged, and / or, in particular, designed such that the first intermediate shaft and the output shaft each have one gear. The gears of the second gear pair are in mesh, in particular between the output shaft and the first intermediate shaft; preferably, the gears of the second gear pair mesh permanently with each other. The second gear pair can comprise a second loose gear on the first intermediate shaft, in particular a second loose gear rotatably mounted on the first intermediate shaft and coupling to the first intermediate shaft, and a fifth fixed gear on the output shaft, in particular a fifth fixed gear arranged non-rotatably on the output shaft.The first intermediate shaft can be connected to the output shaft via the second switching element, preferably via the second gear pair, and particularly preferably via the second loose gear and the fifth fixed gear. The second gear stage, especially the second loose gear on the first intermediate shaft, can be switched by the second switching element. The second loose gear can be connected and / or coupled to the second intermediate shaft, or via the second switching element to the first intermediate shaft, preferably in a rotationally fixed manner, and particularly preferably in a releasable rotationally fixed manner. In other words, the power take-off gearbox, especially the first intermediate shaft, can have the second switching element for a rotationally fixed connection of the second loose gear to the first intermediate shaft. By actuating the second switching element, the second loose gear can thus be rotationally fixed to the first intermediate shaft.The second switching element can be actuated such that it is movable, in particular axially in a first direction along the first intermediate shaft, into a first position. Likewise or additionally, the second switching element can be actuated such that it is movable, in particular axially in a second direction opposite to the first along the first intermediate shaft, into a second position. The second loose gear can therefore be provided on the first intermediate shaft and connected to it via the second switching element.This allows torque and speed to be transmitted from the input shaft via the first fixed gear to the second fixed gear to the first intermediate shaft, and then via the second loose gear to the fifth fixed gear and finally to the output shaft, particularly if the second loose gear has a rotationally fixed connection to the first intermediate shaft via the second switching element, preferably when the second switching element is actuated, i.e., particularly preferably in a second position. Thus, especially when the second loose gear is connected to the first intermediate shaft, i.e., when the second switching element is actuated, the third transmission stage can be achieved using the second switching element.

[0018] In an embodiment of the invention, the power take-off transmission comprises a third gear pair with two gears. The third gear pair can be coupled to the second intermediate shaft or output shaft. The third gear pair is arranged and / or in particular designed such that the second intermediate shaft and the output shaft each have a gear. The gears of the third gear pair are in engagement, in particular between the output shaft and the second intermediate shaft; preferably, the gears of the third gear pair permanently mesh with one another. The third gear pair can comprise a third idler gear on the second intermediate shaft, in particular a third idler gear rotatably mounted on the second intermediate shaft and coupleable to the second intermediate shaft, and a sixth fixed gear on the output shaft, in particular a sixth fixed gear arranged on the output shaft in a rotationally fixed manner.The second intermediate shaft can be connected to the output shaft by the third shifting element or by the third shifting element, preferably via the third gear pair, particularly preferably via the third idler gear and the sixth fixed gear. The third gear pair, in particular the third idler gear on the second intermediate shaft, can be shifted by the third shifting element. The third idler gear can be connected and / or coupled to the third or, via the third shifting element, to the second intermediate shaft, preferably connected and / or coupled in a rotationally fixed manner, particularly preferably releasably connected and / or coupled in a rotationally fixed manner. In other words, the power take-off transmission, in particular the second intermediate shaft, can have the third shifting element for the rotationally fixed connection of the third idler gear to the second intermediate shaft. By actuating the third shifting element, the third idler gear can therefore be rotationally fixedly connected to the second intermediate shaft.For this purpose, the third shifting element can be actuated such that it can be moved into a first position, in particular axially in a first direction along the second intermediate shaft. The third idler gear can therefore be provided on the second intermediate shaft and connected to the second intermediate shaft via the third shifting element. As a result, a torque and a rotational speed can be transmitted from the input shaft via the first fixed gear to the third fixed gear to the second intermediate shaft and then via the third idler gear to the sixth fixed gear to the output shaft, in particular when the third idler gear has a rotationally fixed connection to the second intermediate shaft via the third shifting element, i.e. preferably when the third shifting element is actuated, i.e. particularly preferably when it is in a first position.Thus, in particular when the third idler gear is connected to the first intermediate shaft, i.e. the third shifting element is actuated, the first gear ratio can be produced with the third shifting element.

[0019] The invention further relates to an agricultural utility vehicle, in particular a tractor or tow tractor. The agricultural utility vehicle comprises a power take-off (PTO) transmission, in particular a PTO transmission according to one of claims 1 to 13. The utility vehicle can further comprise a drive motor, for example an internal combustion engine or an electric motor. The agricultural utility vehicle, in particular the drive motor, can comprise an output shaft. A drive shaft of the PTO transmission can be the output shaft of the drive motor. Likewise, the PTO transmission, in particular the drive shaft, can be coupled to the output shaft. The output shaft can be coupled to a transmission of the utility vehicle. In particular, the utility vehicle or the PTO transmission can comprise a clutch. An input side of the clutch can be connected to the output shaft, and an output side of the clutch can be connected to a second drive wheel.The second drive gear can be designed as a fixed gear and be non-rotatably connected to the output side of the clutch. Furthermore, a first drive gear, which can also be designed as a fixed gear, can be arranged on the input shaft and, in particular, be non-rotatably connected to the input shaft. The clutch and the first and second drive gears can be designed as part of the power take-off (PTO) gearbox. Alternatively, only the first drive gear can be designed as part of the PTO gearbox, while the clutch and the second drive gear can be designed as part of the vehicle.

[0020] The power take-off (PTO) gearbox is designed to transmit torque and rotational speed generated by a drive motor to a work implement or unit. The commercial vehicle according to the invention exhibits the advantages of the gearbox described above.

[0021] With the PTO transmission according to the invention and the commercial vehicle according to the invention, which includes the PTO transmission, the following advantages can be achieved in addition to the advantages mentioned above. The PTO transmission advantageously achieves good efficiency with regard to drag and gearing losses. Therefore, the PTO transmission and the commercial vehicle as a whole are technically and structurally less complex and economically less expensive. Likewise, additional installation space is made possible for components outside the PTO transmission. Furthermore, the performance of the commercial vehicle can be advantageously improved and / or fuel consumption reduced.

[0022] The invention, as well as further advantages and advantageous developments and embodiments of the invention, both in terms of apparatus and process engineering, are explained in more detail below with reference to exemplary embodiments and the drawings. Components that are functionally identical or comparable are marked with the same reference numerals. The schematic drawings show: Fig. 1 is a schematic representation of a first embodiment of an agricultural vehicle according to the invention with a power take-off (PTO) transmission according to the invention, and Fig. 2 is a schematic representation of a first embodiment of the PTO transmission according to the invention, and Fig. 3 is a schematic representation of a second embodiment of the PTO transmission according to the invention, and Fig. 4 is a schematic representation of a third embodiment of the PTO transmission according to the invention.

[0023] Figure 1 Figure 1 shows a schematic representation of a first embodiment of an agricultural vehicle 10 according to the invention, in particular a tractor. The agricultural vehicle 10 can be equipped with the power take-off (PTO) transmission according to the invention (see Figure 1). Figures 2 to 4, reference numeral 20) to enable the supply of drive power to aggregates or work machines via the output shaft or PTO. On such a commercial vehicle, the output shaft or PTO is usually provided at the front and / or rear of the vehicle. For this purpose, the PTO gearbox is necessary, which supplies the output shaft or PTO with drive power and enables the control of the output shaft or PTO. The agricultural commercial vehicle can further comprise a drive motor. In this case, a drive shaft of the PTO gearbox can be an output shaft of the drive motor. Likewise, the drive shaft or a drive wheel can also be connected and / or coupled to the output shaft.

[0024] Figure 2 Figure 1 shows a schematic representation of a first embodiment of the power take-off (PTO) gearbox 20 according to the invention. The in Figure 2The power take-off gearbox 20 shown essentially corresponds to the one in Figure 1 the aforementioned power take-off gearbox, which is why only references to it will be made below. Figure 1 Details not shown will be discussed. The commercial vehicle 10 can use the power take-off gearbox 20, as shown in Figure 2 depicted, include.

[0025] The power take-off transmission 20 comprises an input shaft 30, an output shaft 32, a first intermediate shaft 34, a second intermediate shaft 36, and a first gear stage. The first gear stage 40 is arranged such that the input shaft 30 has a first fixed gear 42, the first intermediate shaft 34 has a second fixed gear 44, and the second intermediate shaft 36 has a third fixed gear 46. Only the first fixed gear 42 is in engagement with the second fixed gear 44, and the first fixed gear 44 is in engagement with the third fixed gear 46, i.e., in particular, they are permanently meshed.

[0026] The power take-off gearbox 20, in particular the output shaft 32, has a first switching element 50. The first fixed gear 42 and / or the input shaft 30 can be connected and / or coupled to the output shaft 32 by means of or via the first switching element 50, preferably in a rotationally fixed manner, and particularly preferably in a releasable rotationally fixed manner. By actuating the first switching element 50, the first fixed gear 42 and / or the input shaft 30 can thus be connected to the output shaft 32 in a rotationally fixed manner. For this purpose, the first switching element 50 can be actuated such that it is movable, in particular axially in a first direction along the output shaft 32, to a first position 52.Thus, a torque and a rotational speed can be transmitted from the input shaft 30 to the output shaft 32, in particular when the first fixed gear 42 and / or the input shaft 30 has a rotationally fixed connection with the output shaft 32 via the first shifting element 50, i.e. the first shifting element 50 is actuated. The power take-off transmission 20 further comprises a first gear pair 60 with two gears. The first gear pair 60 is arranged such that the first intermediate shaft 34 and the output shaft 32 each have a gear and the gears of the first gear pair 60 are in engagement, in particular permanently meshing with one another, in particular between the output shaft 32 and the first intermediate shaft 34. The gears of the first gear pair 60 are a fourth fixed gear 62 and a first idler gear 64. The first intermediate shaft 34 has the fourth fixed gear 62 and the output shaft 32 has the first idler gear 64.The first intermediate shaft 34 can be connected to the output shaft 32 via the first switching element 50, preferably via the first gear pair 60, and particularly preferably via the first loose gear 64 and the fourth fixed gear 62. Furthermore, the first gear pair 60, especially the first loose gear 64, can be switched by the first switching element 50. The first loose gear 64 can be connected and / or coupled to the output shaft 32 via the first switching element 50, preferably in a rotationally fixed manner, and particularly preferably in a releasable rotationally fixed manner. Thus, by actuating the first switching element 50, the first loose gear 64 can be connected to the output shaft 32 in a rotationally fixed manner. For this purpose, the first switching element 50 can be actuated in such a way that it can be moved, in particular axially in a second direction opposite to the first direction along the output shaft 32, into a second position 54.As a result, a torque and a rotational speed can be transmitted from the first intermediate shaft 34 via the fourth fixed gear 62 and the first idler gear 64 to the output shaft 32, in particular when the first idler gear 64 has a rotationally fixed connection to the output shaft 32 via the first switching element 50, i.e. the first switching element 50 is actuated.

[0027] The power take-off transmission 20 further comprises a second gear stage 70. The second gear stage 70 is arranged such that the output shaft 32 has a fifth fixed gear 72, the first intermediate shaft 34 has a second idler gear 74, and the second intermediate shaft 36 has a third idler gear 76, with only the fifth fixed gear 72 meshing with the second idler gear 74 and the fifth fixed gear 72 meshing with the third idler gear 76. The power take-off transmission 20, in particular the first intermediate shaft 34, has a second shifting element 80. The first intermediate shaft 34 is connectable to the second gear stage 70, particularly preferably via the second idler gear 74 and the fifth fixed gear 76, with the output shaft 32. Furthermore, the second switching element 80 can be used to switch the second gear stage 70, in particular the second loose gear 74.The second loose gear 74 can be connected and / or coupled to the second intermediate shaft 34, or via the second switching element 80 to the first intermediate shaft 34, preferably in a rotationally fixed manner, and particularly preferably in a releasable rotationally fixed manner. By actuating the second switching element 80, the second loose gear 74 can thus be connected to the first intermediate shaft 34 in a rotationally fixed manner. For this purpose, the second switching element 80 can be actuated such that it is movable, in particular axially in a first direction along the first intermediate shaft 34, to a first position 82. The second loose gear 74 is therefore provided on the first intermediate shaft 34 and is connected to the first intermediate shaft 34 via the second switching element 80.As a result, a torque and a rotational speed can be transmitted from the first intermediate shaft 34 via the second idler gear 74 and the fifth fixed gear 72 to the output shaft 32, in particular when the second idler gear 74 has a rotationally fixed connection with the first intermediate shaft 34 via the second switching element 80, i.e. the second switching element 80 is actuated.

[0028] The power take-off transmission 20, in particular the second intermediate shaft 36, has a third shifting element 90. The second intermediate shaft 36 is connectable to the output shaft 32 by the third shifting element 90, preferably via the second gear stage 70, particularly preferably via the third idler gear 76 and the fifth fixed gear 72. Furthermore, the second gear stage 70, in particular the third idler gear 76, can be shifted by the third shifting element 90. The third idler gear 76 is connectable and / or coupled to the third or via the third shifting element 90, the second intermediate shaft 36, preferably connectable and / or coupled in a rotationally fixed manner, particularly preferably releasably connectable and / or coupled in a rotationally fixed manner. In other words, the power take-off gearbox 20, in particular the second intermediate shaft 36, can have the third switching element 90 for the rotationally fixed connection of the third loose gear 76 with the second intermediate shaft 36.By actuating the third shifting element 90, the third idler gear 76 can be connected in a rotationally fixed manner to the second intermediate shaft 36. For this purpose, the third shifting element 90 can be actuated such that it can be moved into a first position 92, in particular axially in a first direction along the second intermediate shaft 36. The third idler gear 76 is therefore provided on the second intermediate shaft 36 and is connected to the second intermediate shaft 36 via the third shifting element 90. As a result, a torque and a rotational speed can be transmitted from the second intermediate shaft 36 via the third idler gear 76 and the fifth fixed gear 72 to the output shaft 32, in particular when the third idler gear 76 has a rotationally fixed connection to the second intermediate shaft 36 via the third shifting element 90, i.e. when the third shifting element 90 is actuated.

[0029] Specifically, as in Figure 2As shown, the agricultural vehicle 10 or the power take-off (PTO) gearbox 20 comprises a clutch 100. An input side of the clutch 100 can be connected to an output shaft 102 of the drive motor, and an output side of the clutch 100 can be connected to a second drive wheel 106 designed as a fixed gear. Furthermore, a first drive wheel 104, also designed as a fixed gear, can be arranged on the input shaft 30. The first drive wheel 104 is designed as part of the PTO gearbox 20, and the clutch 100 and the second drive wheel 106 are designed as part of the agricultural vehicle 10.

[0030] The power take-off (PTO) gearbox 20 has four stages, meaning it has four transmission stages. The four transmission stages for the first embodiment are described below. The first transmission stage can be engaged by actuating or engaging the third switching element 90. This connects the third loose gear 76 to the second intermediate shaft 36 in a rotationally fixed manner. The third switching element 90 can be actuated such that it moves into a first position 92 and connects the third loose gear 76 to the second intermediate shaft 36 in a rotationally fixed manner. This allows torque and speed to be transmitted from the input shaft 30 via the first fixed gear 42 to the third fixed gear 46 onto the second intermediate shaft 36, and further via the third loose gear 76 to the fifth fixed gear 72 onto the output shaft 32. The first transmission stage corresponds to transmission stage 540.The first gear stage therefore delivers a speed of 540 revolutions per minute at the rated speed of the drive motor. The second gear stage can be engaged by actuating or engaging the second switching element 80. This connects the second loose gear 74 to the first intermediate shaft 34 in a rotationally fixed manner. The second switching element 80 can be actuated such that it moves into a first position 82 and connects the second loose gear 74 to the first intermediate shaft 34 in a rotationally fixed manner. This allows torque and speed to be transmitted from the input shaft 30 via the first fixed gear 42 to the second fixed gear 44 onto the first intermediate shaft 34, and further via the second loose gear 74 to the fifth fixed gear 72 onto the output shaft 32. The second gear stage is assigned gear stage 540E.The second gear stage therefore delivers a speed of 540 revolutions per minute during economical engine operation. The third gear stage can be engaged by actuating or engaging the first switching element 50. This connects the first loose gear 64 to the output shaft 32 in a rotationally fixed manner. The first switching element 50 can be actuated in such a way that it moves into a second position 54, thus connecting the first loose gear 64 to the output shaft 32 in a rotationally fixed manner. This allows torque and speed to be transmitted from the input shaft 30 via the first fixed gear 42 to the second fixed gear 44, then to the first intermediate shaft 34, and further via the fourth fixed gear 62 to the first loose gear 64, and finally to the output shaft 32. The third gear stage corresponds to gear stage 1000.The third gear ratio therefore delivers a speed of 1000 revolutions per minute at the rated speed of the drive motor. The fourth gear ratio can be established or realized by actuating or engaging the first shifting element 50. This connects the first fixed gear 42 and / or the input shaft 30 in a rotationally fixed manner to the output shaft 32. The first shifting element 50 can be actuated such that the first shifting element 50 is moved to a first position 52 and the first fixed gear and / or the input shaft 30 can be connected in a rotationally fixed manner to the output shaft 32. This allows torque and speed to be transmitted from the input shaft 30 to the output shaft 32 via the first fixed gear 42. The fourth gear ratio is assigned the gear ratio 1000E. The fourth gear ratio therefore delivers a speed of 1000 revolutions per minute during economical engine operation.

[0031] Figure 3Figure 1 shows a schematic representation of a second embodiment of the power take-off (PTO) gearbox 20 according to the invention. The [unclear text] Figure 3 The power take-off gearbox 20 shown essentially corresponds to the one described in the Figures 1 to 2 The power take-off gearboxes 20 shown are shown, so only details and / or differences will be discussed below. The commercial vehicle 10 according to Figure 1 the PTO gearbox 20, as shown in Figure 3The first gear pair 60, as shown, comprises a first loose gear 64 on the first intermediate shaft 34 and a fourth fixed gear 62 on the output shaft 32. Thus, the first intermediate shaft 34 has the first loose gear 64, and the output shaft 32 has the fourth fixed gear 62. The first intermediate shaft 34 can be connected to the output shaft 32 via the second switching element 80, preferably via the first gear pair 60, and particularly preferably via the first loose gear 64 and the fourth fixed gear 62. Specifically, the first gear pair 60, and in particular the first loose gear 64, can be switched using the second switching element 80. The first loose gear 64 can be connected and / or coupled to the second or, via the second switching element 80, to the first intermediate shaft 34, particularly preferably detachably connected and / or coupled in a rotationally fixed manner.In other words, the power take-off gearbox 20, in particular the first intermediate shaft 34, can have the second switching element 80 for the rotationally fixed connection of the first loose gear 64 to the first intermediate shaft 34. By actuating the second switching element 80, the first loose gear 64 can thus be rotationally fixed to the first intermediate shaft 34. For this purpose, the second switching element 80 can be actuated such that it is movable, in particular axially in a first direction along the first intermediate shaft 34, to a first position 82. This allows torque and speed to be transmitted from the first intermediate shaft 34 via the first loose gear 64 and the fourth fixed gear 62 to the output shaft 32, in particular when the first loose gear 64 has a rotationally fixed connection to the first intermediate shaft 34 via the second switching element 80, i.e., when the second switching element 80 is actuated.

[0032] The power take-off transmission 20 of the second exemplary embodiment further comprises the second gear stage 70. The second gear stage 70, in particular the second idler gear 74, can also be shifted using the second shifting element 80. The second idler gear 74 can be connected and / or coupled to the second intermediate shaft 34 or, via the second shifting element 80, to the first intermediate shaft 34, preferably connected and / or coupled in a rotationally fixed manner, particularly preferably releasably connected and / or coupled in a rotationally fixed manner. In other words, the power take-off transmission 20, in particular the first intermediate shaft 34, can have the second shifting element 80 for the rotationally fixed connection of the second idler gear 74 to the first intermediate shaft 34. By actuating the second shifting element 80, the second idler gear 74 can therefore be rotationally fixedly connected to the first intermediate shaft 34.The second switching element 80 can be actuated such that it is movable, in particular axially in a second direction opposite to the first direction, along the first intermediate shaft 34, into a second position 84. The second loose gear 74 is thus provided on the first intermediate shaft 34 and is connected to the first intermediate shaft 34 via the second switching element 80. This allows torque and rotational speed to be transmitted from the first intermediate shaft 34 to the output shaft 32 via the second loose gear 74 and the fifth fixed gear 72, particularly when the second loose gear 74 has a rotationally fixed connection to the first intermediate shaft 34 via the second switching element 80, i.e., when the second switching element 80 is actuated.

[0033] The four transmission stages of the second embodiment are as follows. The first transmission stage can be established or realized by actuating or engaging the third switching element 90. This connects the third loose gear 76 to the second intermediate shaft 36 in a rotationally fixed manner. The third switching element 90 can be actuated such that it moves into a first position 92 and connects the third loose gear 76 to the second intermediate shaft 36 in a rotationally fixed manner. This allows torque and speed to be transmitted from the input shaft 30 via the first fixed gear 42 to the third fixed gear 46 on the second intermediate shaft 36, and further via the third loose gear 76 to the fifth fixed gear 72 on the output shaft 32. The first transmission stage corresponds to transmission stage 540. Consequently, the first transmission stage provides a speed of 540 revolutions per minute at the rated speed of the drive motor.

[0034] The second transmission stage can be established or realized by actuating or engaging the second switching element 80. This connects the first loose gear 64 to the first intermediate shaft 34 in a rotationally fixed manner. The second switching element 80 can then be actuated such that it moves into a first position 82, thus connecting the first loose gear 64 to the first intermediate shaft 34 in a rotationally fixed manner. This allows torque and speed to be transmitted from the input shaft 30 via the first fixed gear 42 to the second fixed gear 44, then to the first intermediate shaft 34, and further via the first loose gear 64 to the fourth fixed gear 62, and finally to the output shaft 32. The second transmission stage is assigned the transmission stage 540E. Consequently, the second transmission stage provides a speed of 540 revolutions per minute during economical motor operation.

[0035] The third transmission stage can be established or realized by actuating or engaging the second switching element 80. This connects the second loose gear 74 to the first intermediate shaft 34 in a rotationally fixed manner. The second switching element 80 can be actuated such that it moves into the second position 84, thus connecting the second loose gear 74 to the first intermediate shaft 34 in a rotationally fixed manner. This allows torque and speed to be transmitted from the input shaft 30 via the first fixed gear 42 to the second fixed gear 44, then to the first intermediate shaft 34, and further via the second loose gear 74 to the fifth fixed gear 72, and finally to the output shaft 32. The third transmission stage corresponds to transmission stage 1000. Consequently, at the rated speed of the drive motor, the third transmission stage delivers a speed of 1000 revolutions per minute.

[0036] The fourth gear ratio can be established or realized by actuating or engaging the first shifting element 50. This connects the first fixed gear 42 and / or the input shaft 30 in a rotationally fixed manner to the output shaft 32. The first shifting element 50 can be actuated such that the first shifting element 50 is moved to a first position 52 and the first fixed gear 42 and / or the input shaft 30 can be connected in a rotationally fixed manner to the output shaft 32. This allows torque and rotational speed to be transmitted from the input shaft 30 to the output shaft 32 via the first fixed gear 42. The fourth gear ratio is assigned the gear ratio 1000E. The fourth gear ratio therefore delivers a speed of 1000 revolutions per minute during economical engine operation.

[0037] Figure 4 Figure 1 shows a schematic representation of a third embodiment of the power take-off (PTO) gearbox 20 according to the invention. The figure shown in Figure 20 is a schematic representation of a third embodiment of the PTO gearbox 20. Figure 4The power take-off gearbox 20 shown essentially corresponds to the one described in the Figures 1 to 3 The power take-off gearboxes 20 shown are shown, so only details and / or differences will be discussed below. The commercial vehicle 10 according to Figure 1 the PTO gearbox 20, as shown in Figure 4 The power take-off shaft transmission 20 of the third embodiment comprises the first gear pair 60 according to Figure 3 , wherein the first loose gear 64 can be connected to the first intermediate shaft 34 in a rotationally fixed manner by actuating the second switching element 80. For this purpose, the second switching element 80 can be actuated such that it is movable, in particular axially in a first direction along the first intermediate shaft 34, into the first position 82.

[0038] The power take-off transmission 20 further comprises a second gear pair 110 with two gears. The second gear pair 110 is arranged such that the first intermediate shaft 34 and the output shaft 32 each have a gear, and the gears of the second gear pair 110 are in mesh, in particular between the output shaft 32 and the first intermediate shaft 34. The gears of the second gear pair 110 are a second idler gear 114 on the first intermediate shaft 34 and a fifth fixed gear 112 on the output shaft 32. The first intermediate shaft 34 is connectable to the second shift element 80, preferably via the second gear pair 110, particularly preferably via the second idler gear 114 and the fifth fixed gear 112, with the output shaft 32. In particular, the second gear pair 110, in particular the second idler gear 114, can be shifted with the second shifting element 80.The second idler gear 114 can be connected and / or coupled to the second or, via the second shifting element 80, to the first intermediate shaft 34, particularly preferably releasably connected and / or coupled in a rotationally fixed manner. In other words, the power take-off transmission 20, in particular the first intermediate shaft 34, can have the second shifting element 80 for the rotationally fixed connection of the second idler gear 114 to the first intermediate shaft 34. By actuating the second shifting element 80, the second idler gear 114 can therefore be rotationally fixedly connected to the first intermediate shaft 34. For this purpose, the second shifting element 80 can be actuated such that it can be moved into a second position 84, in particular axially in a second direction opposite to the first direction along the first intermediate shaft 34. The second idler gear 114 is therefore provided on the first intermediate shaft 34 and is connected to the first intermediate shaft 34 via the second shifting element 80.As a result, a torque and a rotational speed can be transmitted from the first intermediate shaft 34 via the second idler gear 114 and the fifth fixed gear 112 to the output shaft 32, in particular when the second idler gear 114 has a rotationally fixed connection with the first intermediate shaft 34 via the second switching element 80, i.e. the second switching element 80 is actuated.

[0039] The power take-off transmission 20 further comprises a third gear pair 120 with two gears. The third gear pair 120 is arranged such that the second intermediate shaft 36 and the output shaft 32 each have a gear, and the gears of the third gear pair 120 are in mesh, in particular between the output shaft 32 and the second intermediate shaft 36. The gears of the third gear pair 120 are a third idler gear 124 on the second intermediate shaft 36 and a sixth fixed gear 122 on the output shaft 32. The power take-off transmission, in particular the second intermediate shaft 36, has the third shifting element 90. The second intermediate shaft 36 is connectable to the third gear pair 120 or through the third shifting element 90, preferably via the third gear pair 120, particularly preferably via the third idler gear 124 and the sixth fixed gear 122.Furthermore, the third gear pair 120, in particular the third idler gear 124, can be shifted with the third shifting element 90. The third idler gear 124 can be connected and / or coupled to the third gear or, via the third shifting element 90, to the second intermediate shaft 36, preferably connected and / or coupled in a rotationally fixed manner, particularly preferably releasably connected and / or coupled in a rotationally fixed manner. In other words, the power take-off transmission 20, in particular the second intermediate shaft 36, can have the third shifting element 90 for the rotationally fixed connection of the third idler gear 124 to the second intermediate shaft 36. By actuating the third shifting element 90, the third idler gear 124 can thus be rotationally fixedly connected to the second intermediate shaft 36. For this purpose, the third switching element 90 can be actuated in such a way that it can be moved, in particular axially in a first direction along the second intermediate shaft 36, into a first position 92.As a result, a torque and a rotational speed can be transmitted from the second intermediate shaft 36 via the third idler gear 124 and the sixth fixed gear 122 to the output shaft 32, in particular when the third idler gear 124 has a rotationally fixed connection with the second intermediate shaft 36 via the third switching element 90, i.e. the third switching element 90 is actuated.

[0040] The four gear ratios of the third exemplary embodiment are as follows. The first gear ratio can be established or realized by actuating or engaging the third shift element 90. This causes the third idler gear 124 to be connected in a rotationally fixed manner to the second intermediate shaft 36. This allows torque and rotational speed to be transmitted from the input shaft 30 via the first fixed gear 42 to the third fixed gear 46 on the second intermediate shaft 36 and further via the third idler gear 124 to the sixth fixed gear 122 on the output shaft 32. The first gear ratio is assigned gear ratio 540. The first gear ratio therefore delivers a speed of 540 revolutions per minute at the rated speed of the drive motor.

[0041] The second transmission stage can be established or realized by actuating or engaging the second switching element 80. This connects the first loose gear 64 to the first intermediate shaft 34 in a rotationally fixed manner. The second switching element 80 can then be actuated such that it moves into the first position 82, thus connecting the first loose gear 64 to the first intermediate shaft 34 in a rotationally fixed manner. This allows torque and speed to be transmitted from the input shaft 30 via the first fixed gear 42 to the second fixed gear 44, then to the first intermediate shaft 34, and further via the first loose gear 64 to the fourth fixed gear 62, and finally to the output shaft 32. The second transmission stage is assigned the transmission stage 540E. Consequently, the second transmission stage provides a speed of 540 revolutions per minute during economical motor operation.

[0042] The third gear ratio can be established or realized by actuating or engaging the second shifting element 80. This causes the second idler gear 114 to be connected in a rotationally fixed manner to the first intermediate shaft 34. The second shifting element 80 can be actuated such that the second shifting element 80 is moved into the second position 84 and the second idler gear 114 can be connected in a rotationally fixed manner to the first intermediate shaft 34. This allows torque and rotational speed to be transmitted from the input shaft 30 via the first fixed gear 42 to the second fixed gear 44 on the first intermediate shaft 34 and further via the second idler gear 114 to the fifth fixed gear 112 on the output shaft 32. The third gear ratio is assigned a gear ratio of 1000. The third gear ratio therefore delivers a speed of 1000 revolutions per minute at the rated speed of the drive motor.

[0043] The fourth gear ratio can be established or realized by actuating or engaging the first shifting element 50. This connects the first fixed gear 42 and / or the input shaft 30 in a rotationally fixed manner to the output shaft 32. The first shifting element 50 can be actuated such that the first shifting element 50 is moved to a first position 52 and the first fixed gear 42 and / or the input shaft 30 can be connected in a rotationally fixed manner to the output shaft 32. This allows torque and rotational speed to be transmitted from the input shaft 30 to the output shaft 32 via the first fixed gear 42. The fourth gear ratio is assigned the gear ratio 1000E. The fourth gear ratio therefore delivers a speed of 1000 revolutions per minute during economical engine operation.

[0044] The advantages mentioned above and those mentioned below apply to all figures shown. The power take-off (PTO) gearbox 20 according to the invention offers the advantage of a simple design for both the PTO gearbox 20 and the commercial vehicle 10, as well as a compact design requiring minimal installation space. Furthermore, the optimized design allows for a reduction in material costs for the gearbox 20.

Claims

1. PTO shaft transmission for an agricultural utility vehicle (10), comprising: an input shaft (30), an output shaft (32), a first intermediate shaft (34), a second intermediate shaft (36), a first gearwheel stage (40), which is arranged in such a way that the input shaft (30) has a first fixed gear (42) and the first intermediate shaft (34) has a second fixed gear (44) and the second intermediate shaft (36) has a third fixed gear (46), wherein only the first fixed gear (42) is in engagement with the second fixed gear (44) and the first fixed gear (42) is in engagement with the third fixed gear (46), characterized in that the input shaft (30) is designed as a hollow shaft, and the output shaft (32) is at least partially arranged in the input shaft (30).

2. PTO shaft transmission according to Claim 1, characterized in that the PTO shaft transmission (20) has a first shifting element (50), and the first fixed gear (42) is connectable by the first shifting element (50) to the output shaft (32).

3. PTO shaft transmission according to Claim 1 or 2, characterized in that the PTO shaft transmission (20) has a second shifting element (80), and the first intermediate shaft (34) is connectable by the second shifting element (80) to the output shaft (32).

4. PTO shaft transmission according to at least one of the preceding claims, characterized in that the PTO shaft transmission (20) has a third shifting element (90), and the second intermediate shaft (36) is connectable by the third shifting element (90) to the output shaft (32).

5. PTO shaft transmission according to at least one of the preceding claims, characterized in that the PTO shaft transmission comprises a first gearwheel pair (60) with two gearwheels, and / or the first gearwheel pair (60) is arranged in such a way that the first intermediate shaft (34) and the output shaft (32) each have a gearwheel and the gearwheels of the first gearwheel pair (60) are in engagement.

6. PTO shaft transmission according to Claim 5, characterized in that the first gearwheel pair (60) comprises a first idler gear (64) on the first intermediate shaft (34) and a fourth fixed gear (62) on the output shaft (32).

7. PTO shaft transmission according to Claim 5, characterized in that the first gearwheel pair (60) comprises a fourth fixed gear (62) on the first intermediate shaft (34) and a first idler gear (64) on the output shaft (32).

8. PTO shaft transmission according to Claim 7, characterized in that the output shaft (32) is connectable by the first shifting element (50) to the first intermediate shaft (34).

9. PTO shaft transmission according to at least one of the preceding claims, characterized in that the PTO shaft transmission comprises a second gearwheel stage (70), which is arranged in such a way that the output shaft (32) has a fifth fixed gear (72) and the first intermediate shaft (34) has a second idler gear (74) and the second intermediate shaft (36) has a third idler gear (76), wherein only the fifth fixed gear (72) is in engagement with the second idler gear (74) and the fifth fixed gear (72) is in engagement with the third idler gear (76).

10. PTO shaft transmission according to at least one of Claims 1 to 6, characterized in that the PTO shaft transmission (20) comprises a second gearwheel pair (110) with two gearwheels and / or the second gearwheel pair (110) is arranged in such a way that the first intermediate shaft (34) and the output shaft (32) each have a gearwheel and the gearwheels of the second gearwheel pair (110) are in engagement.

11. PTO shaft transmission according to Claim 10, characterized in that the second gearwheel pair (110) comprises a second idler gear (114) on the first intermediate shaft (34) and a fifth fixed gear (112) on the output shaft (32).

12. PTO shaft transmission according to at least one of Claims 10 to 11, characterized in that the PTO shaft transmission (20) comprises a third gearwheel pair (120) with two gearwheels and / or the third gearwheel pair (120) is arranged in such a way that the second intermediate shaft (36) and the output shaft (32) each have one gearwheel and the gearwheels of the third gearwheel pair (120) are in engagement.

13. PTO shaft transmission according to Claim 12, characterized in that the third gearwheel pair (120) comprises a third idler gear (124) on the second intermediate shaft (36) and a sixth fixed gear (122) on the output shaft (32).

14. Agricultural utility vehicle, comprising a PTO shaft transmission according to one of Claims 1 to 13.

15. Agricultural utility vehicle according to Claim 14, characterized in that the agricultural utility vehicle comprises a drive motor, wherein a drive shaft of the PTO shaft transmission is a driven shaft of the drive motor or is coupled to said driven shaft.