TRANSMISSION AND AGRICULTURAL OR INDUSTRIAL VEHICLE

Description

[0001] The invention relates to a transmission according to the preamble of independent claim 1 and to an agricultural or industrial utility vehicle according to claim 10.

[0002] A variety of different transmissions are used today in agricultural or industrial commercial vehicles, preferably agricultural or industrial towing vehicles, particularly tractors or tow tractors. These transmissions enable the propulsion of the commercial vehicle to be changed continuously, even under high towing loads, for example caused by an attached implement such as a soil tillage device (e.g. plow) or the like, beyond simply changing the drive engine speed. The transmission of a commercial vehicle is generally embedded in a higher-level driveline architecture of the entire commercial vehicle. A typical driveline architecture provides for a drive motor or engine and a transmission.These can be arranged along a vehicle's longitudinal axis, i.e., a longitudinal axis of the commercial vehicle, which is an axis running in a longitudinal direction of the commercial vehicle, or along a forward direction of travel of the vehicle, in particular in a front half of the commercial vehicle. The commercial vehicle, in particular the drive engine, can comprise a crankshaft, which can be arranged in particular near or along a vehicle center plane, in particular a vertical vehicle center plane. The transmission can transmit power and / or torque from the drive engine to the ground-engaging means, for example, wheels and / or chains and / or tracks, of the commercial vehicle (drive, traction).The transmission, in particular a main transmission unit, can be arranged along the vehicle's longitudinal axis and / or along the vehicle's center plane and / or opposite the forward direction of travel behind the drive motor toward the rear end of the vehicle; in particular, the main transmission unit can be arranged directly on the drive motor. The drive element, in particular the input shaft, of the transmission, in particular of the main transmission unit, can be connected to and / or drivable by the crankshaft of the drive motor. The crankshaft axes of the crankshaft of the drive motor and the drive element of the transmission can be aligned and / or arranged coaxially with one another. Alternatively, the crankshaft axis and the drive element can be displaced parallel to one another or arranged at an angle to one another. The first output element of the transmission can be connectable or connected directly or indirectly to the ground engagement means in order to drive the ground engagement means.This allows a power and / or torque flow from the drive engine via the crankshaft and the drive element to the output element and further to a front and / or rear drive axle and thus to the ground engagement means. CN 110345210 A discloses a 16-speed automatic transmission based on a single planetary wheel type modular design.

[0003] The disadvantage here is that in these commercial vehicles with the familiar drivetrain architecture, the transmission requires too much installation space. A significant disadvantage is the large number of shafts and gear sets that conventional powershift transmissions have. This means that the transmission takes up installation space that could, for example, be used for additional components and / or a commercial vehicle cab. In addition, the known transmissions have too few gears in the working range and / or too narrow a speed range and / or too narrow a gear spread. In particular, there is a lack of a sufficient and optimal number of gear ratios in the working range of speeds in the field. The known transmissions with many shifting elements, in particular clutches and / or brakes and / or shift sleeves or synchronizers, are also technically and / or structurally complex and incur high manufacturing costs.

[0004] The present invention is therefore based on the object of proposing a transmission and a commercial vehicle by which the aforementioned problems are overcome. In particular, a transmission and a commercial vehicle are to be proposed with which the variety of transmissions in a commercial vehicle is increased and / or which are less complex technically and / or structurally and / or economically and / or the transmission has a more compact design and / or the installation space, preferably in the commercial vehicle, particularly preferably below a cab and / or between the drive motor and the rear axle module, can be better utilized and / or the performance and / or drivability of the transmission and / or commercial vehicle is improved and / or has a sufficient number of gear ratios.

[0005] This object is achieved by a transmission having the features of claim 1 and an agricultural or industrial utility vehicle having the features of claim 10. The dependent claims relate to particularly advantageous embodiments of the invention.

[0006] According to the invention, a transmission is proposed for transmitting a torque generated by a drive motor, in particular an internal combustion engine or a diesel engine, to at least one front and / or rear drive axle of an agricultural or industrial utility vehicle. The transmission comprises a drive element, in particular the input shaft, and a first output element, in particular a first output shaft, as well as a main transmission unit, an intermediate transmission, and a reversing unit.The main transmission unit has a first planetary gear set with a first sun gear, a first ring gear, a first planetary carrier, and a first planetary set, and a second planetary gear set with a second sun gear, and a third planetary gear set with a third sun gear and a third planetary set, and wherein the second and third planetary gear sets have a first common planetary set and a first common ring gear and a first common planetary carrier. The intermediate transmission has a fifth planetary gear set with a fifth sun gear, a fifth ring gear, a fifth planetary carrier, and a fifth planetary set. The reversing unit includes a fourth planetary gear set with a fourth sun gear, a fourth ring gear, a fourth planetary carrier, and a fourth planetary set.In addition, the main transmission unit comprises exactly five shifting elements, wherein the shifting elements are a first brake and a second brake and a third brake and a first clutch and a second clutch. The intermediate transmission has exactly two shifting elements. The intermediate transmission can comprise at least one or two planetary gear sets. At least two forward gears can be produced with the intermediate transmission. The reversing unit comprises exactly two shifting elements. The reversing unit is preferably designed to change a direction of rotation of the transmission, particularly preferably to change a direction of rotation of the first output element, and in particular of a second output element. Furthermore, at least one forward gear and one reverse gear can be produced with the reversing unit. The reversing unit comprises at least one planetary gear set or at least a first and second gear set, each with a loose gear and a fixed gear.At least two shifting elements of the main transmission unit and exactly one shifting element of the intermediate transmission and exactly one shifting element of the reversing unit can be actuated, preferably selectively actuated, particularly preferably lockable and releasable and / or engageable and / or switchable and / or selectively engaged in combinations of at least four, in particular exactly four or five or six, shifting elements in order to establish exactly twelve forward gears between the input element and the first output element and / or in particular the second output element. In addition, at least twelve, preferably exactly twelve, reverse gears can be established. However, only a portion of the twelve reverse gears, i.e. fewer than twelve reverse gears, can actually be used. The reversing unit is arranged downstream of the main transmission unit in the direction of power and torque flow.The drive element is connected to the first ring gear, and the drive element is releasably connectable to the first clutch with the third sun gear, and the first planet carrier is releasably connectable to the second clutch with the second sun gear.

[0007] The first common ring gear can be connected to the reversing unit or the intermediate gear, in particular permanently, preferably in a rotationally fixed and / or drivable manner. However, the main gear unit can also comprise a first intermediate element, for example, a first intermediate shaft. Specifically, the first intermediate element can be connected to the first common ring gear and the reversing unit or the intermediate gear, in particular permanently, preferably in a rotationally fixed and / or drivable manner.

[0008] Likewise, the main transmission unit can at least partially or completely comprise the input element and / or the first output element. With the main transmission unit, at least six forward gears can be produced between the input element and the first common ring gear, preferably between the input element and the first intermediate element. With the intermediate transmission, at least two forward gears can be produced. Thus, with the main transmission unit and the intermediate transmission, a total of at least twelve forward gears can be produced. With the reversing unit, one forward gear and one reverse gear can be produced. Thus, with the main transmission unit, the intermediate transmission and the reversing unit, a total of at least twelve forward gears and twelve reverse gears can be produced.

[0009] In other words, a transmission is proposed as a multi-stage transmission with a planetary design, comprising the input element, which can be connected to a drive motor, preferably drivable and / or rotationally fixed. Furthermore, the transmission can comprise at least four, in particular five or six or more, planetary gear sets, at least two rotatable shafts, the input and the first output element, and at least nine shifting elements. The shifting elements of the transmission can be designed as friction shifting elements and / or multi-disk shifting elements. Likewise, the shifting elements can be designed as positive-locking shifting elements. The shifting elements can be brakes and / or clutches.The actuation, in particular the selective actuation or engagement, of the shifting elements of the transmission in combinations of at least four shifting elements can bring about different gear ratios between the input element and the first output element and / or the second output element, so that preferably at least twelve forward gears and in particular the same number or fewer reverse gears can be produced.

[0010] The first output element can be provided to drive the rear and / or front ground engagement means of the commercial vehicle and / or can be connected to a rear axle module. This allows a force and / or torque flow to be established between the first output element and the rear and / or front drive axle, so that, for example, a force and / or torque can be transmitted to the rear and / or front drive axle of the commercial vehicle.

[0011] When the transmission is installed in the commercial vehicle, the transmission, in particular a transmission longitudinal axis, i.e., a longitudinal axis of the transmission, which is an axis running in a longitudinal direction of the transmission, can be arranged parallel or coaxially to the vehicle's longitudinal axis. The planetary gear sets can be arranged axially or along the transmission's longitudinal axis.

[0012] What is essential for the invention is that the transmission has sufficient gear ratios and / or that the construction effort and size, in particular the installation space, or the weight are advantageously optimized and that the efficiency with regard to drag and gearing losses is also improved. Advantageously, low torques are present in the shifting elements and in the planetary gear sets of the transmission, thereby advantageously reducing wear on the transmission. Likewise, the design of the transmission and / or the low torques advantageously result in a structurally simple design, in particular a compact construction, i.e. a small volume of the transmission and / or small dimensions, so that the installation space required by the transmission and the corresponding costs are reduced. In addition, low speeds are also achieved for the shafts, the shifting elements and the planetary gear sets.In addition, the transmission is designed in such a way that it can be adapted to different drivetrain architectures, both in terms of the direction of the power and / or torque flow, and spatially. The transmission can, for example, be installed in the commercial vehicle in a front-transverse design or as part of a standard drive. Due to the spatial arrangement of the planetary gear sets, the installation space, in particular the axial and radial space, of the transmission in the commercial vehicle can be advantageously minimized when the transmission is installed in the commercial vehicle. In addition, the transmission advantageously has a small or minimal number of gears and shift elements, whereby the transmission, especially when installed in the commercial vehicle, advantageously has a more compact and structurally simpler design and the construction effort is significantly reduced.The transmission advantageously results in good efficiency in the forward and / or reverse gears with regard to drag and gearing losses. Advantageously, the transmission and the commercial vehicle as a whole are therefore less complex in terms of technology, design, and cost. This also allows for additional installation space for components outside the transmission. Furthermore, the cab can be positioned lower, i.e., offset toward the footprint of the commercial vehicle, than cabs in known commercial vehicles. The inventive design of the transmission results in gear ratios suitable for commercial vehicles as well as an increased overall spread of the multi-stage transmission, thereby improving driving comfort and significantly reducing fuel consumption. This can therefore advantageously improve the performance and / or drivability and / or roadholding of the commercial vehicle.

[0013] The planetary gear sets of the main transmission unit can be arranged axially in the following order: first planetary gear set, second planetary gear set, and third planetary gear set. The first planetary gear set can be designed as a simple minus planetary gear set. As is known, a minus planetary gear set comprises a sun gear, a ring gear, and a planet carrier on which planetary gears are rotatably mounted, each of which meshes with the sun gear and ring gear. As a result, when the planet carrier is held stationary, the ring gear rotates in a direction opposite to that of the sun gear. The first planetary set can, in particular, have a set of first planet gears. The first planetary set can comprise three first planet gears. The first planetary set, i.e. the first planet gears, can be rotatably mounted on the first planet carrier. The first planetary set can mesh with the first sun gear and the first ring gear, i.e., can be in constant meshing engagement with them.The third planetary gear set can comprise a set of third planet gears, in particular three third planet gears, and / or the first common planetary gear set can comprise a set of first common planet gears, in particular three first common planet gears. The third planetary gear set, i.e. the third planet gears, and the first common planetary gear set, i.e. the first common planet gears, can be rotatably mounted on the first common planet carrier. Furthermore, the third planetary gear set can mesh with the third sun gear and the first common planet gears, i.e. in particular can be in constant meshing engagement with them. Furthermore, the first common planetary gear set can mesh with the second sun gear and the first common ring gear and the third planetary gear set, i.e. in particular can be in constant meshing engagement with them.In other words, the second and third planetary gear sets can be designed as a double planetary gear set, in particular as a Ravigneaux and / or Lepelletier planetary gear set. The double planetary gear set can comprise the second and third sun gear, the third planetary set and the first common planetary set, the first common planet carrier and the first common ring gear. The third planetary set and the first common planetary set can be rotatably mounted on the first common planet carrier. Typically, three planet gears are used for each of the planetary sets of the transmission, i.e. in particular the first and third planetary sets and / or the first common and / or a second common planetary set and / or a fourth and / or fifth. However, a different number of planet gears would also be conceivable, for example four or five or six or more planet gears each.The number of planets advantageously influences the maximum transmittable torque. Furthermore, the design exhibits all the advantages of the transmission according to the invention.

[0014] In one embodiment of the invention, the intermediate gear is arranged downstream of the main transmission unit in the direction of power and torque flow. The intermediate gear can be arranged downstream of the main transmission unit and upstream of the reversing unit in the direction of power and torque flow, or the reversing unit can be arranged downstream of the main transmission unit and upstream of the intermediate gear. The main transmission unit and / or the intermediate gear and / or the reversing unit can be arranged along the transmission longitudinal axis and / or the vehicle longitudinal axis. Likewise, the intermediate gear can also be arranged upstream of the main transmission unit. This advantageously achieves a compact axial design.

[0015] The drive element is connected or connectable to the first ring gear and / or the first clutch, preferably connected or connectable in a rotationally fixed and / or drivable manner. The transmission, in particular the main transmission unit, can comprise a first connecting element, in particular a first connecting shaft. The first connecting element can be connected or connectable to the drive element and the first ring gear and / or the first clutch, preferably connected or connectable in a rotationally fixed and / or drivable manner. The first planet carrier can be connected or connectable to the third sun gear and / or the first clutch and / or the second clutch, preferably connected or connectable in a rotationally fixed and / or drivable manner. Likewise, the transmission, in particular the main transmission unit, can comprise a second connecting element, in particular a second connecting shaft.The second connecting element can be connected or connectable to the first planetary carrier and the third sun gear and / or the first clutch and / or the second clutch, preferably connected or connectable in a rotationally fixed and / or drivable manner. Furthermore, the second sun gear can be connected or connectable to the second brake and / or the second clutch, in particular connected or connectable in a rotationally fixed and / or drivable manner. The transmission, in particular the main transmission unit, can comprise a third connecting element, in particular a third connecting shaft. The third connecting element can be connected or connectable to the second sun gear and / or the second brake and / or the second clutch, preferably connected or connectable in a rotationally fixed and / or drivable manner. Likewise, the first common planetary carrier can be connected or connectable to the third brake, in particular connected or connectable in a rotationally fixed and / or drivable manner.The transmission, in particular the main transmission unit, can comprise a fourth connecting element, in particular a fourth connecting shaft. The fourth connecting element can be connected or connectable to the third brake and / or the first common planetary carrier, preferably connected or connectable in a rotationally fixed and / or drivable manner. The first sun gear can be secured against rotation by the first brake, preferably releasably secured against rotation. The first sun gear can be coupled to a main transmission housing by the first brake and / or releasably connectable to the main transmission housing, preferably releasably secured against rotation.The drive element, and in particular the first connecting element, is detachably connectable, in particular detachably connected in a rotationally fixed and / or drivable manner, to the first planet carrier and / or the third sun gear and / or the second clutch and / or in particular the second connecting element or, via the first clutch, to the first planet carrier and / or the third sun gear and / or the second clutch and / or in particular the second connecting element. The first planet carrier can be connected to the third sun gear, in particular detachably connected in a rotationally fixed and / or drivable manner, preferably to or via the second connecting element.The first planet carrier, and in particular the second connecting element, is detachably connectable, in particular detachably and non-rotatably and / or drivably connectable, to the second or, via the second clutch, to the second sun gear and / or the second brake and / or, in particular, the third connecting element. The second clutch can therefore be designed to couple the first planet carrier, and in particular the second connecting element, to the second sun gear and / or the second brake and / or, in particular, the third connecting element. The second sun gear, and in particular the third connecting element, can be secured against rotation by the second brake, preferably releasably secured against rotation. The second sun gear can be coupled to a main transmission housing by the second brake and / or detachably connectable to the main transmission housing, preferably releasably secured against rotation.The second brake can therefore be designed to hold the second sun gear, and in particular the third connecting element, against rotation. The first common planetary carrier and / or the first common planetary set and / or the third planetary set, and in particular the fourth connecting element, can be held against rotation by the third brake, preferably releasably held against rotation. The first common planetary carrier and / or the first common planetary set and / or the third planetary set, and in particular the fourth connecting element, can be coupled to the main transmission housing by the third brake and / or releasably connectable to the main transmission housing, preferably releasably connectable against rotation. In a further embodiment, the drive element can be connected or connectable to the first planetary carrier and / or the first clutch, preferably connected or connectable in a rotationally fixed and / or drivable manner.The transmission, in particular the main transmission unit, can comprise a first connecting element, in particular a first connecting shaft. The first connecting element can be connected or connectable to the drive element and the first planet carrier and / or the first clutch, preferably connected or connectable in a rotationally fixed and / or drivable manner. The first ring gear can be connected to the third sun gear and / or the first clutch and / or the second clutch, preferably connected or connectable in a rotationally fixed and / or drivable manner. Likewise, the transmission, in particular the main transmission unit, can comprise a second connecting element, in particular a second connecting shaft. The second connecting element can be connected or connectable to the first ring gear and / or the third sun gear and / or the first clutch and / or the second clutch, preferably connected or connectable in a rotationally fixed and / or drivable manner.Furthermore, the second sun gear can be connected or connectable to the second brake and / or the second clutch, in particular connected or connectable in a rotationally fixed and / or drivable manner. The transmission, in particular the main transmission unit, can comprise a third connecting element, in particular a third connecting shaft. The third connecting element can be connected or connectable to the second brake and / or the second clutch and / or the second sun gear, preferably connected or connectable in a rotationally fixed and / or drivable manner. Likewise, the first common planetary carrier can be connected or connectable to the third brake, in particular connected or connectable in a rotationally fixed and / or drivable manner. The transmission, in particular the main transmission unit, can comprise a fourth connecting element, in particular a fourth connecting shaft.The fourth connecting element can be connected or connectable to the third brake and / or the first common planetary carrier, preferably connected or connectable in a rotationally fixed and / or drivable manner. The first sun gear can be secured against rotation by the first brake, preferably releasably secured against rotation. The first sun gear can be coupled to the main transmission housing by the first brake and / or releasably connectable to the main transmission housing, preferably releasably secured against rotation. The drive element, and in particular the first connecting element, can be releasably connectable to the first ring gear and / or the third sun gear and / or the second clutch and / or in particular the second connecting element, in particular releasably connectable to the first ring gear and / or the third sun gear and / or the second clutch and / or the second connecting element via the first clutch.The first clutch can therefore be designed to couple the drive element, and in particular the first connecting element, to the first ring gear and / or the third sun gear and / or the second clutch and / or in particular to the second connecting element. The first ring gear can be connected to the third sun gear, in particular to or via the second connecting element. The first ring gear, and in particular the second connecting element, can be releasably connected to the second or, via the second clutch, to the second sun gear and / or the second brake, and in particular to the third connecting element, in particular releasably connected in a rotationally fixed manner and / or drivably. The second clutch can therefore be designed to couple the first ring gear, and in particular the second connecting element, to the second sun gear and / or the second brake, and in particular to the third connecting element.The second sun gear, and in particular the third connecting element, can be held against rotation by the second brake, preferably releasably held against rotation. The second sun gear can be coupled to a main transmission housing by the second brake and / or releasably connectable to the main transmission housing, preferably releasably held against rotation. The second brake can therefore be designed to hold the second sun gear, and in particular the third connecting element, against rotation. The first common planetary carrier and / or the first common planetary set and / or the third planetary set, and in particular the fourth connecting element, can be held against rotation by the third brake, preferably releasably held against rotation.The first common planetary carrier and / or the first common planetary gear set and / or the third planetary gear set, and in particular the fourth connecting element, can be coupled to the main transmission housing by means of the third brake and / or can be releasably connected to the main transmission housing, preferably releasably secured against rotation. In a further embodiment, the drive element can be connected to the first sun gear, preferably connected in a rotationally fixed and / or drivable manner. The first sun gear can, for example, be designed as a fixed gear on the drive element or be connected to the drive element via a shaft or be drive-connected in a meshing manner to another fixed gear arranged on the drive element in a rotationally fixed manner. The transmission, in particular the main transmission unit, can comprise a first connecting element, in particular a first connecting shaft.The first connecting element can be connected or connectable to the drive element and / or the first clutch, preferably connected or connectable in a rotationally fixed and / or drivable manner. The first planet carrier can be connected or connectable to the third sun gear and / or the first clutch and / or the second clutch, preferably connected or connectable in a rotationally fixed and / or drivable manner. Likewise, the transmission, in particular the main transmission unit, can comprise a second connecting element, in particular a second connecting shaft. The second connecting element can be connected or connectable to the first planet carrier and / or the third sun gear and / or the first clutch and / or the second clutch, preferably connected or connectable in a rotationally fixed and / or drivable manner.Furthermore, the second sun gear can be connected or connectable to the second brake and / or the second clutch, in particular connected or connectable in a rotationally fixed and / or drivable manner. The transmission, in particular the main transmission unit, can comprise a third connecting element, in particular a third connecting shaft. The third connecting element can be connected or connectable to the second brake and / or the second clutch and / or the second sun gear, preferably connected or connectable in a rotationally fixed and / or drivable manner. Likewise, the first common planetary carrier can be connected or connectable to the third brake, in particular connected or connectable in a rotationally fixed and / or drivable manner. The transmission, in particular the main transmission unit, can comprise a fourth connecting element, in particular a fourth connecting shaft.The fourth connecting element can be connected or connectable to the third brake and / or the first common planetary carrier, preferably connected or connectable in a rotationally fixed and / or drivable manner. The first ring gear can be secured against rotation by the first brake, preferably releasably secured against rotation. The first ring gear can be coupled to the main transmission housing by the first brake and / or releasably connectable to the main transmission housing, preferably releasably secured against rotation. The drive element, and in particular the first connecting element, can be releasably connectable to the first planetary carrier and / or the third sun gear and / or the second clutch and / or in particular the second connecting element, in particular releasably connectable to the first or, via the first clutch, to the first planetary carrier and / or the third sun gear and / or the second clutch and / or in particular to the second connecting element.The first clutch can therefore be designed to couple the drive element, and in particular the first connecting element, to the first ring gear and / or the third sun gear and / or the second clutch and / or in particular the second connecting element. The first planet carrier can be connected to the third sun gear, in particular connected in a rotationally fixed and / or drivable manner, preferably to or via the second connecting element. The first planet carrier, and in particular the second connecting element, can be releasably connected to the second or, via the second clutch, to the second sun gear and / or the second brake and / or in particular the third connecting element, in particular releasably connected in a rotationally fixed and / or drivable manner.The second clutch can therefore be designed to couple the first planet carrier, in particular the second connecting element, to the second sun gear and / or the second brake and / or in particular to the third connecting element. The second sun gear, and in particular the third connecting element, can be held against rotation by the second brake, preferably releasably held against rotation. The second sun gear can be coupled to a main transmission housing by the second brake and / or releasably connected to the main transmission housing, preferably releasably held against rotation. The second brake can therefore be designed in particular to hold the second sun gear, and in particular the third connecting element, against rotation.The first common planetary carrier and / or the first common planetary gear set and / or the third planetary gear set, and in particular the fourth connecting element, can be secured against rotation by the third brake, preferably releasably secured against rotation. The first common planetary carrier and / or the first common planetary gear set and / or the third planetary gear set and / or in particular the fourth connecting element can be coupled to the main transmission housing by the third brake and / or releasably connected to the main transmission housing, preferably releasably secured against rotation. InIn a further advantageous embodiment, the drive element can be connected to the first planet carrier, preferably connected in a rotationally fixed and / or drivable manner. The transmission, in particular the main transmission unit, can comprise a first connecting element, in particular a first connecting shaft. The first connecting element can be connected to the drive element and the first planet carrier, preferably connected in a rotationally fixed and / or drivable manner. The first planet carrier can be connected or connectable to the first clutch, preferably connected or connectable in a rotationally fixed and / or drivable manner. The transmission, in particular the main transmission unit, can comprise a second connecting element, in particular a second connecting shaft. The second connecting element can be connected or connectable to the first clutch and the first planet carrier, preferably connected or connectable in a rotationally fixed and / or drivable manner.The first sun gear can be connected or connectable to the third sun gear and / or the first clutch and / or the second clutch, preferably connected or connectable in a rotationally fixed and / or drivable manner. Likewise, the transmission, in particular the main transmission unit, can comprise a third connecting element, in particular a third connecting shaft. The third connecting element can be connected or connectable to the first sun gear and / or the third sun gear and / or the first clutch and / or the second clutch, preferably connected or connectable in a rotationally fixed and / or drivable manner. Furthermore, the second sun gear can be connected or connectable to the second brake and / or the second clutch, in particular connected or connectable in a rotationally fixed and / or drivable manner. The transmission, in particular the main transmission unit, can comprise a fourth connecting element, in particular a fourth connecting shaft.The fourth connecting element can be connected or connectable to the second brake and / or the second clutch and the second sun gear, preferably connected or connectable in a rotationally fixed and / or drivable manner. Likewise, the first common planetary carrier can be connected or connectable to the third brake, in particular connected or connectable in a rotationally fixed manner. The transmission, in particular the main transmission unit, can comprise a fifth connecting element, in particular a fifth connecting shaft. The fifth connecting element can be connected or connectable to the third brake and / or the first common planetary carrier, preferably connected or connectable in a rotationally fixed and / or drivable manner. The first ring gear can be secured against rotation by the first brake, preferably releasably secured against rotation.The first ring gear can be coupled to the main transmission housing by means of the first brake and / or detachably connected to the main transmission housing, preferably detachably secured against rotation. The first planet carrier, and in particular the second connecting element, can be detachably connected to the first or, via the first clutch, to the first sun gear and / or the third sun gear and / or the second clutch and / or, in particular, the third connecting element, in particular detachably connected in a rotationally fixed and / or drivable manner. The first clutch can therefore be designed to couple the first planet carrier, and in particular the second connecting element, to the first sun gear and / or the third sun gear and / or the second clutch and / or, in particular, the third connecting element. The first sun gear can be connected to the third sun gear, in particular rotationally fixed and / or drivably connected, preferably to or via the third connecting element.The first sun gear, and in particular the third connecting element, and / or the first clutch can be releasably connected to the second or, via the second clutch, to the second sun gear and / or the second brake and / or in particular the fourth connecting element, in particular releasably connected in a rotationally fixed and / or drivable manner. The second clutch can therefore be designed to couple the first sun gear, and in particular the third connecting element, and / or the first clutch to the second sun gear and / or the second brake and / or in particular the third connecting element. The second sun gear, and in particular the fourth connecting element, can be secured against rotation by the second brake, preferably releasably secured against rotation.The second sun gear, and in particular the fourth connecting element, can be coupled to a main transmission housing with the second brake and / or releasably connected to the main transmission housing, preferably releasably secured against rotation. The second brake can thus be designed to hold the second sun gear, and in particular the fourth connecting element, against rotation. The first common planetary carrier and / or the first common planetary gear set and / or the third planetary gear set, and in particular the fifth connecting element, can be secured against rotation with the third brake, preferably releasably secured against rotation.

[0016] The first common planetary carrier and / or the first common planetary gear set and / or the third planetary gear set and / or in particular the fifth connecting element can be coupled to the main transmission housing by means of the third brake and / or can be releasably connected to the main transmission housing, preferably releasably secured against rotation.

[0017] The switching elements of the reversing unit are a third clutch and a fourth brake. The reversing unit can be arranged parallel or coaxially to the input element and / or the first output element. The fourth planetary gear set can have a set of fourth planetary gears, in particular three fourth planetary gears. The fourth planetary gears can be rotatably mounted on the fourth planet carrier. The fourth planetary gear set, in particular the set of fourth planetary gears, can mesh with the fourth sun gear and the fourth ring gear, i.e., can be in constant meshing engagement with them.The reversing unit can comprise exactly two shift elements that are actuatable, preferably selectively actuatable, particularly preferably lockable and releasable and / or engageable and / or switchable and / or selectively engageable, in order to connect the first common ring gear, and in particular the first intermediate element, with the fourth sun gear or to hold the fourth ring gear against rotation. The first common ring gear, and in particular the first intermediate element, can be connected or connectable to the fourth planet carrier and / or the third clutch, preferably connected or connectable in a rotationally fixed and / or drivable manner. The fourth sun gear can be connected or connectable to a fifth sun gear and / or the third clutch and / or a fourth clutch, preferably connected or connectable in a rotationally fixed and / or drivable manner.The transmission, in particular the reversing unit, can comprise a sixth connecting element, in particular a sixth connecting shaft. The sixth connecting element can be connected or connectable to the fourth sun gear and a fifth sun gear and / or the third clutch and / or a fourth clutch, preferably connected or connectable in a rotationally fixed and / or drivable manner. The fourth planet carrier and the first common ring gear, and in particular the first intermediate element, can be releasably connected to the third or, via the third clutch, to the fourth sun gear and / or in particular to the sixth connecting element and / or a fifth sun gear, in particular releasably connected in a rotationally fixed and / or drivable manner.The third clutch can thus be designed to couple the fourth planet carrier and the first common ring gear, and in particular the first intermediate element, to the fourth sun gear and / or in particular to the sixth connecting element and / or a fifth sun gear. The fourth ring gear can be secured against rotation by the fourth brake, preferably releasably secured against rotation. The fourth ring gear can be coupled to a housing of the reversing unit, i.e., a reversing unit housing, by the fourth brake and / or releasably connectable thereto, preferably releasably secured against rotation. The fourth brake can thus be designed to hold the fourth ring gear against rotation. Due to the combination of the main transmission unit with the reversing unit, the above-mentioned advantages according to the invention are advantageously achieved. Furthermore, due to the described planetary design, the reversing unit advantageously has a short axial length.This has a particularly advantageous overall effect on the axial length of the transmission and / or the installation space of the transmission, particularly in a state in which the transmission is installed in the commercial vehicle.

[0018] The intermediate gear can comprise exactly two shifting elements. The shifting elements of the intermediate gear are a fourth clutch and a fifth clutch. The transmission, in particular the intermediate gear, can partially or completely comprise a second intermediate element. The fifth planetary gear set can have a set of fifth planet gears, in particular three fifth planet gears. The fifth planet gears can be rotatably mounted on the fifth planet carrier. The fifth planetary gear set, in particular the set of fifth planet gears, can mesh with the fifth sun gear and the fifth ring gear, in particular be in constant meshing engagement with them. Furthermore, the intermediate gear can be arranged parallel or coaxially to the input element and / or the first output element. In particular, the intermediate gear can at least partially or completely comprise the first output element.The two shift elements of the intermediate transmission are actuatable, preferably selectively actuatable, particularly preferably lockable and releasable and / or engageable and / or switchable and / or selectively engageable, in order to connect and / or couple the fifth sun gear or the fifth planetary gear set and / or the fifth planet carrier to the second intermediate element and / or in particular to the first output element, in particular to connect them releasably, non-rotatably and / or drivably. The fifth sun gear can be connected or connectable to the fourth sun gear and / or the third clutch and / or the fourth clutch, preferably connected or connectable in a non-rotatably and / or drivably manner. The sixth connecting element can be connected or connectable to the fourth and fifth sun gears and / or the third clutch and / or the fourth clutch, preferably connected or connectable in a non-rotatably and / or drivably manner.Specifically, the reversing unit and / or the intermediate gear can comprise the sixth connecting element. The fifth sun gear and the fourth sun gear, and in particular the sixth connecting element, can be releasably connected to the fourth clutch or, via the fourth clutch, to the second intermediate element and / or the first output element, in particular releasably connected in a rotationally fixed and / or drivable manner. The fourth clutch can therefore be designed to couple the fifth sun gear and the fourth sun gear, and in particular the sixth connecting element, to the second intermediate element and / or the first output element. Furthermore, the fifth planet carrier can be connected or connectable to the fifth clutch, in particular connected or connectable in a rotationally fixed and / or drivable manner. The transmission, in particular the intermediate gear, can comprise a seventh connecting element, in particular a seventh connecting shaft.The seventh connecting element can be connected or connectable to the fifth clutch and / or the fifth planetary carrier, preferably connected or connectable in a rotationally fixed manner. The fifth planetary carrier and / or the fifth planetary set, and in particular the seventh connecting element, can be releasably connected to the fifth or, via the fifth clutch, to the first output element and / or the second intermediate element, in particular releasably connected in a rotationally fixed manner and / or drivably. The fifth clutch can therefore be designed to couple the fifth planetary carrier, and in particular the seventh connecting element, to the first output element and / or the second intermediate element. The fifth ring gear can be held against rotation. The fifth ring gear can be coupled to a housing of the intermediate transmission, i.e., an intermediate transmission housing, and / or connected thereto, preferably held against rotation.Due to the combination of the main transmission unit with the intermediate transmission, the aforementioned advantages of the invention are advantageously achieved. Furthermore, due to the described planetary design, the intermediate transmission advantageously has a short axial length. This has a particularly advantageous overall effect on the axial length of the transmission and / or the installation space of the transmission, especially when the transmission is installed in the commercial vehicle.

[0019] In an advantageous embodiment, the first output element is or can be connected to the second intermediate element in a driving manner, and in particular the first output element can be driven by the second intermediate element. Preferably, the second intermediate element and the first output element can be coupled to a gear set. For this purpose, the first output element can be driven via or with the gear set. The gear set can comprise two permanently meshing output gears, a first and a second output gear, which can be designed as fixed gears. The first output gear can be connected in a rotationally fixed manner to the second intermediate element and the second output gear can be connected in a rotationally fixed manner to the first output element. The second output element can be connected or can be connected to an output clutch, in particular releasably connected or connectable in a rotationally fixed manner and / or drivably. The output clutch can be connected in a rotationally fixed manner to a third output gear.The third output gear can permanently mesh with the second output gear. The second output element can be drivably connected or connectable to the first output element, and in particular, the second output element can be drivably connected to the first output element. This advantageously allows a modular and / or compact design of the transmission to be achieved, since the individual units of the transmission, i.e., the main transmission unit and / or the reversing unit and / or the intermediate transmission, can be interchangeable.

[0020] In an embodiment of the invention, the transmission, in particular the main transmission unit and / or the reversing unit and / or the intermediate transmission, comprises a second output element, in particular a second output shaft. The second output element can be provided for driving the front ground engagement means of the commercial vehicle and / or can be or be connected in a driveable manner to a front axle module. A force and / or torque flow can be established between the second output element and the front drive axle, so that, for example, a force and / or torque can be transmitted to the front drive axle of the commercial vehicle, and in particular, a force and / or torque flow can be established simultaneously between the first drive element and the rear drive axle.Advantageously, a force and / or torque flow, in particular a separate force and / or torque flow, can be produced from the first output element to the rear drive axle and from the second output element to the front drive axle.

[0021] In an embodiment of the invention, the transmission comprises a main transmission housing accommodating the main transmission unit and / or a reversing unit housing accommodating the reversing unit and / or an intermediate transmission housing accommodating the intermediate transmission and / or a rear axle housing accommodating a rear axle module. The transmission can therefore comprise a main transmission housing that can accommodate the main transmission unit, and / or a rear axle housing that can accommodate the rear axle module and / or a reversing unit housing that can accommodate the reversing unit, and / or an intermediate transmission housing that can accommodate the intermediate transmission. The main transmission housing can have a housing cover. The reversing unit housing can have a first cover and / or the intermediate transmission housing can have a second cover and / or the rear axle housing can have a third cover.The main transmission housing and / or the reversing unit housing and / or the intermediate transmission housing and / or the rear axle housing can advantageously have a predeterminable and / or fixed installation space, i.e., a predeterminable axial and lateral extent, regardless of the number of planetary gear sets and / or shafts. Particularly when installed in a commercial vehicle, the housings therefore always have the same installation space and / or thus a modularity in terms of installation space. The main transmission housing and / or the reversing unit housing and / or the intermediate transmission housing and / or the rear axle housing can be formed in one or more parts.A one-piece main transmission housing and / or a one-piece reversing unit housing and / or a one-piece intermediate transmission housing and / or a one-piece rear axle housing can be understood in particular to mean that the housing section surrounding the main transmission unit or the reversing unit or the intermediate transmission or the rear axle module, with the exception of the housing cover or the first or second or third cover, is made from a single piece, for example, it can be produced from a single casting. In this case, the housings can have an opening which can be closed with the housing cover or the first or second or third cover. In this case, although the main transmission housing as a whole is then formed by the housing section surrounding the main transmission unit and the housing cover, it should nevertheless be understood as a one-piece main transmission housing.The same applies to the reversing unit housing and / or the intermediate gear housing and / or the rear axle housing. The housing cover and / or the first, second and third covers can close off the respective housing to the outside, but without accommodating components of the transmission. The main gear housing and / or the reversing unit housing and / or the intermediate gear housing and / or the rear axle housing can accommodate components of the transmission. The components or parts of the main gear unit and / or the reversing unit and / or the intermediate gear and / or the rear axle module can be installed and / or maintained or repaired through an opening in the main gear housing and / or an opening in the reversing unit housing and / or an opening in the intermediate gear housing and / or an opening in the rear axle housing.As an alternative to a one-piece main transmission housing and / or reversing unit housing and / or intermediate transmission housing and / or rear axle housing, these can also be constructed in two or more parts. For example, the main transmission housing and / or the reversing unit housing and / or the intermediate transmission housing and / or the rear axle housing could be composed of two substantially equal parts. The rear axle module, in particular the rear axle housing, can preferably be arranged directly or immediately on the intermediate transmission, in particular the intermediate transmission housing. Likewise, the intermediate transmission, in particular the intermediate transmission housing, can preferably be arranged directly or immediately on the reversing unit, in particular the reversing unit housing.Furthermore, the reversing unit, in particular the reversing unit housing, can preferably be arranged directly or immediately on the main transmission unit, in particular the main transmission housing. Overall, these measures advantageously enable simple manufacture and assembly of the transmission. When the housing parts are mounted on one another, the transmission is at least largely assembled and basically ready for operation. When installed in the commercial vehicle, a coupling element or a shaft-hub connection can connect a crankshaft or a shaft of the drive motor for driving the transmission to the drive element, in particular connect them in a rotationally fixed and / or drivable manner. As a result, a torque flow can advantageously be established, in particular directly, between the drive motor and the transmission, in particular the main transmission unit and / or the reversing unit and / or the intermediate transmission.

[0022] In an embodiment of the invention, the rear axle module at least partially or entirely comprises the rear drive axle and / or a rear axle differential. The transmission can have a rear axle module. The rear axle module, in particular the rear axle differential, can comprise a rear axle pinion, for example a drive bevel gear or a bevel pinion, and a rear axle gear, for example a bevel or ring gear. The rear axle housing can accommodate the rear axle module, in particular the rear axle differential, and / or at least partially the rear drive axle. The first output element can be connected to the rear axle pinion, or the rear axle pinion and the first output element can be formed as a one-piece component. The transmission can have the front axle module. The front axle module can partially or entirely comprise the front drive axle and / or a front axle differential.The front axle module, in particular the front axle differential, can comprise a front axle pinion, for example a drive bevel gear or a bevel pinion, and a front axle gear, for example a bevel or ring gear. A front axle housing can accommodate the front axle module, in particular the front axle differential, and / or at least partially the front drive axle. The second output element can be connected to the front axle pinion, or the front axle pinion and the second output element can be formed as a single component. This advantageously enables a modular and / or compact design of the transmission.

[0023] In an advantageous development of the transmission, the transmission comprises a power take-off module. The rear axle module, in particular the rear axle housing, can be arranged between the power take-off module and the main transmission unit. The transmission can comprise a power take-off drive shaft. The power take-off module can be driven by the power take-off drive shaft. The transmission longitudinal axis can be coaxial or parallel to the power take-off drive shaft. The power take-off drive shaft can be arranged in particular in the drive element. A power take-off housing can accommodate the components of the power take-off module. The components of the power take-off module can be the power take-off drive shaft and / or the power take-off shaft stub and the power take-off gearbox. The power take-off drive shaft can be designed as a solid shaft. The drive element can be designed as a hollow shaft.The drive element can accommodate the PTO drive shaft, meaning the PTO drive shaft can be arranged in the drive element. When the transmission is installed in the commercial vehicle, the PTO drive shaft can be driven by the drive motor, in particular also coupled in such a way that the PTO drive shaft can be driven by the drive motor. The PTO module, in particular the PTO transmission, can therefore be drivingly connected to the drive motor via the PTO drive shaft through the drive element, in particular also via the rear axle module, or can be driven. This advantageously enables a direct and therefore particularly energy-efficient transmission of drive power from the drive motor to a PTO module, in particular the PTO output of the commercial vehicle.

[0024] The invention further relates to an agricultural or industrial utility vehicle, in particular a tractor or a construction machine. The agricultural or industrial utility vehicle comprises a transmission according to one of claims 1 to 9. The utility vehicle may further comprise a drive motor. The utility vehicle according to the invention has the above-described advantages of the transmission according to the invention.

[0025] In an embodiment of the invention, the transmission is arranged in the commercial vehicle such that the transmission longitudinal axis is substantially parallel or coaxial, in particular parallel or coaxial, to a vehicle longitudinal axis. The main transmission unit, and / or in particular the reversing unit and / or the intermediate transmission, can be aligned along the transmission longitudinal axis. However, the transmission can also be arranged in the commercial vehicle such that a transmission center plane is substantially parallel or congruent to the vehicle center plane, in particular that the transmission center plane is parallel or congruent to the vehicle center plane. In a commercial vehicle with a drive motor and transmission, the transmission can be used to transmit a torque generated by the drive motor to at least one front and / or rear drive axle of the commercial vehicle.The agricultural or industrial utility vehicle may comprise a cab and a chassis, wherein the cab may be arranged on, in particular on, the chassis. The axial position of the drive element of the transmission may be determined by the position of the crankshaft of the drive engine. The first output element may be longitudinally oriented and in the same vertical position as the rear drive axle, whose axis may be coaxial with the rear wheels. Likewise, the second output element may be longitudinally oriented and / or in the same vertical position as the front drive axle. The front and rear drive axles may be drivable with the first output element. However, the rear drive axle may also be drivable with the first output element and the front drive axle with the second output element.The commercial vehicle according to the invention advantageously has a significantly slimmer and / or more compact design and / or the transmission requires less installation space.

[0026] With the transmission according to the invention and the commercial vehicle according to the invention comprising the transmission, at least 12 forward gears and in particular at least 12 reverse gears can advantageously be produced and / or implemented between the input element and the first output element and / or second output element. The transmission according to the invention and / or the commercial vehicle according to the invention have at least one and / or more of the following advantages: Higher efficiency and lower power loss of the transmission. The transmission requires less packaging volume, i.e., a smaller installation space, than known comparable transmissions. More options for the transmission ratio due to the combination of multiple planetary stages. Lower noise level. Fewer clutches. Compact installation space and, in particular, a reduction in the volume of the transmission and / or the required installation space in the commercial vehicle. Coaxial arrangement of the input and first and / or second output elements. The transmission has a lower weight and lower manufacturing costs than known comparable transmissions. Higher power density and higher torque capacity. Longer service life of the transmission due to the use of planetary gear sets compared to known comparable transmissions. Low moment of inertia.

[0027] In the following, the invention as well as further advantages and advantageous developments and refinements of the invention, both in terms of apparatus and process technology, are explained in more detail using exemplary embodiments and with reference to the drawings. Components that are identical or comparable in terms of their function are identified by the same reference numerals. The schematic drawings show: In the following, the invention as well as further advantages and advantageous developments and refinements of the invention, both in terms of apparatus and process technology, are explained in more detail using exemplary embodiments and with reference to the drawings. Components that are identical or comparable in terms of their function are identified by the same reference numerals. The schematic drawings show: Fig. 1 is a schematic representation of a first embodiment of an agricultural or industrial utility vehicle according to the invention with a transmission according to the invention, and Fig. 2 is a schematic representation of a first embodiment of the transmission according to the invention, and Fig. 3 is a schematic representation of a second embodiment of the transmission according to the invention, and Fig. 4 is a schematic representation of a third embodiment of the transmission according to the invention, and Fig. 5 is a schematic representation of a fourth embodiment of the transmission according to the invention, and Fig. 6 is a schematic representation of a shift diagram of the transmission according to the invention, and Fig. 7 is a schematic representation of a second embodiment of an agricultural or industrial utility vehicle according to the invention with a transmission according to the invention.

[0028] Figure 1shows a schematic representation of a first exemplary embodiment of an agricultural or industrial utility vehicle 10 according to the invention, in particular a tractor or tow tractor, with a transmission 20 according to the invention. The utility vehicle 10 comprises a cab 12, a front drive axle 14, and a rear drive axle 16. The rear drive axle 16 can be permanently driven, and the front drive axle 14 can be engaged as needed or be permanently driven. The utility vehicle 10 further comprises a drive motor 18, which can be embodied as an internal combustion engine. The transmission 20 has a drivetrain architecture that, as described below, can be composed of various individual transmission modules.The drive train architecture described here can have, in the power and torque flow, starting from the drive motor 18, a transmission 20 according to the invention with a main transmission unit 22 and / or an intermediate transmission 150 and / or a reversing unit 120 and / or in particular a rear axle module 24 and / or a front axle module 220 and / or a power take-off module 26.

[0029] The transmission 20, in particular the main transmission unit 22, is arranged downstream of the drive motor 18 opposite the forward direction of travel 300 of the commercial vehicle and / or along a vehicle longitudinal axis 52, i.e., a longitudinal axis 52 of the commercial vehicle 10. The transmission 20, in particular the main transmission unit 22, is drive-connected to the drive motor 18 and / or can be driven by the drive motor 18. The rear axle module 24 can be arranged downstream of the transmission 20, in particular the main transmission unit 22 or the reversing unit 120 or the intermediate transmission 150. The rear axle module 24 can be drive-connected to the main transmission unit 22 or the reversing unit 120 or the intermediate transmission 150 and / or can be driven by the main transmission unit 22 or the reversing unit 120 or the intermediate transmission 150. With the shown transmission 20, a power and torque of the drive motor 18 can be transmitted with different gear stages to a first output element (see Figures 2 , reference numeral 32) and / or a second output element (see Figure 2 , reference number 190).

[0030] The first output element 32 can be drive-connected to the rear and front drive axles 14, 16. Likewise, the first output element can also be drive-connected to the rear drive axle 16, and the second output element 190 can be drive-connected to the front drive axle 14. Thus, the front and / or rear drive axles 14, 16 can be driven by the first output element 32; in particular, a force and torque can be transmitted from the first output element 32 to the front and / or rear drive axles 14, 16. However, the rear drive axle 16 can also be driven with the first output element 32 and / or the front drive axle 14 with the second output element 190, in particular a force and torque can be transmitted from the first output element 32 to the rear drive axle 16 and / or a force and torque can be transmitted from the second output element 190 to the front drive axle 14.The front and / or rear drive axles 14, 16 can convert a rotation of the first output element 32 into a rotation of one or more ground-engaging means 28 and thus into forward propulsion of the commercial vehicle. Likewise, the front drive axle 14 can also convert a rotation of the first output element 32, and the rear drive axle 16 can also convert a rotation of the second output element 190 into a rotation of one or more ground-engaging means 28 and thus into forward propulsion of the commercial vehicle. The commercial vehicle 10 can therefore be driven at different speeds depending on a gear selected in the transmission 20. Consequently, a commercial vehicle 10 equipped with the transmission 20 can be moved within different speed ranges depending on the gear selected in the transmission 20.

[0031] The towing vehicle 10 may have one or more ground engagement means 28, shown here in the form of wheels 40, 42, which engage with a ground 302 for transmitting drive forces and / or by which the towing vehicle 10 is supported on the ground. The towing vehicle 10 may also have a chassis (not shown), wherein the chassis can be supported in particular by the wheels 28 suspended from the front and rear drive axles 14, 16.

[0032] Figure 2 shows a schematic representation of a first embodiment of the transmission 20 according to the invention. Figure 2 The gearbox 20 shown essentially corresponds to the one shown in Figure 1 shown gearbox, which is why in the following only reference is made to Figure 1 details not shown. The commercial vehicle 10 can have the transmission 20, as shown in Figure 2shown, include. The transmission 20 for transmitting a torque generated by a drive motor 18 to at least one front and / or rear drive axle 14, 16 of the agricultural or industrial utility vehicle 10 comprises an input element 30 and a first output element 32 and a main transmission unit 22 and an intermediate transmission 120 and a reversing unit 150. The main transmission unit 22 has at least three planetary gear sets 70, 80, 90. The intermediate transmission (150) has at least one planetary gear set 160 and the reversing unit 120 has at least one planetary gear set. The main transmission unit 22 also comprises at least five shift elements B1, B2, B3, C1, C2 and the intermediate transmission 150 at least two shift elements C4, C5 and the reversing unit 120 at least two shift elements B4, C3.At least two shift elements B1, B2, B3, C1, C2 of the main transmission unit 22 and at least one shift element C4, C5 of the intermediate transmission 150 and at least one shift element B4, C3 of the reversing unit 120 can be actuated in combinations of at least four shift elements B1, B2, B3, B4, C1, C2, C3, C4, C5 in order to produce at least twelve forward gears between the input element 30 and the first output element 32.

[0033] The main transmission unit 22 includes first, second, and third planetary gear sets 70, 80, 90. The first planetary gear set 70 has a first sun gear 72, a first ring gear 74, a first planet carrier 76, and a first planetary gear set 78. The second planetary gear set 80 has a second sun gear 82. The third planetary gear set 90 has a third sun gear 92 and a third planetary gear set 94. Furthermore, the second and third planetary gear sets 80, 90 have a first common planetary gear set 84, a first common ring gear 86, and a first common planetary carrier 88.

[0034] The input element 30 is connected or connectable to the first ring gear 74 and / or the first clutch C1, preferably connected or connectable in a rotationally fixed and / or drivable manner. The main transmission unit 22 may comprise a first connecting element 96. The first connecting element 96 may be connected or connectable to the input element 30 and the first ring gear 74 and / or the first clutch C1, preferably connected or connectable in a rotationally fixed and / or drivable manner. The first planet carrier 76 is connected or connectable to the third sun gear 92 and / or the first clutch C1 and / or the second clutch C2, preferably connected or connectable in a rotationally fixed and / or drivable manner. The main transmission unit 22 may likewise comprise a second connecting element 98.The second connecting element 98 can be connected or connectable to the first planetary carrier 76 and the third sun gear 92 and / or the first clutch C1 and / or the second clutch C2, preferably connected or connectable in a rotationally fixed and / or drivable manner. In particular, the transmission 20, in particular the main transmission unit 22, can comprise a first intermediate element 112. The first intermediate element 112 can be connected to the first common ring gear 86, preferably connected or connectable in a rotationally fixed and / or drivable manner. Furthermore, the second sun gear 82 is connected or connectable to the second brake B2 and / or the second clutch C2, in particular connected or connectable in a rotationally fixed and / or drivable manner. The transmission 20, in particular the main transmission unit 22, can comprise a third connecting element 110, in particular a third connecting shaft.The third connecting element 110 can be connected or connectable to the second sun gear 82 and / or the second brake B2 and / or the second clutch C2, preferably connected or connectable in a rotationally fixed and / or drivable manner. Likewise, the first common planetary carrier 88 is connected or connectable to the third brake B3, in particular connected or connectable in a rotationally fixed and / or drivable manner. The transmission 20, in particular the main transmission unit 22, can comprise a fourth connecting element 114, in particular a fourth connecting shaft. The fourth connecting element 114 can be connected or connectable to the third brake B3 and / or the first common planetary carrier 88, preferably connected or connectable in a rotationally fixed and / or drivable manner. The first sun gear 72 is releasably secured against rotation by the first brake B1.The first sun gear 72 can be coupled to a main transmission housing 210 via the first brake B1 and / or releasably connected to the main transmission housing 210. The drive element 30 is connected to the first ring gear 74. The drive element 30, and in particular the first connecting element 96, can be releasably connected, in particular releasably connected in a rotationally fixed manner and / or drivably connected, to the first planet carrier 76 and / or the third sun gear 82 and / or the second clutch C2 and / or in particular the second connecting element 98, or via the first clutch C1. The first planet carrier 76, and in particular the second connecting element 98, is releasably connectable, in particular releasably non-rotatably and / or drivably connectable, to the second or via the second clutch C2 to the second sun gear 82 and / or the second brake B2 and / or in particular to the third connecting element 110.The second sun gear 82, and in particular the third connecting element 110, is releasably secured against rotation by the second brake B2. The second sun gear 82 is coupleable to the main transmission housing 210 by the second brake B2 and / or releasably connectable to the main transmission housing 210. The first common planetary carrier 88 and / or the first common planetary set 84 and / or the third planetary set 94, and in particular the fourth connecting element 114, are releasably secured against rotation by the third brake B3. The first common planetary carrier 88 and / or the first common planetary set 84 and / or the third planetary set 94, and in particular the fourth connecting element 110, can be coupled to the main transmission housing 210 by the third brake B3 and / or releasably connectable to the main transmission housing 210.As a result, an optimal compact packing density of the transmission 20, in particular of the main transmission unit 22, can advantageously be achieved, in particular also a compact spatial arrangement of the transmission 20 in the commercial vehicle in a state installed in the commercial vehicle 10.

[0035] The transmission 20 further comprises a reversing unit 120. The reversing unit 120 comprises a fourth planetary gear set 130 with a fourth sun gear 132, a fourth ring gear 134, a fourth planet carrier 136, and a fourth planetary gear set 138. The reversing unit 120 comprises two shifting elements B4, C3, which are actuatable, preferably selectively actuatable, particularly preferably lockable and releasable and / or engageable and / or switchable and / or selectively engageable, so that the first common ring gear 86, and in particular the first intermediate element 112, can be connected to the fourth sun gear 132 or the fourth ring gear 134 can be held against rotation. The shifting elements of the reversing unit 120 are a third clutch C3 and a fourth brake B4.The first common ring gear 86, and in particular the first intermediate element 112, is connected or connectable to the fourth planet carrier 136 and / or the third clutch C3, preferably connected or connectable in a rotationally fixed and / or drivable manner. The fourth sun gear 132 can be connected or connectable to a fifth sun gear 162 and / or the third clutch C3 and / or a fourth clutch C4, preferably connected or connectable in a rotationally fixed and / or drivable manner. The reversing unit 120 can comprise a sixth connecting element 142, in particular a sixth connecting shaft. The sixth connecting element 142 can be connected or connectable to the fourth sun gear 132 and a fifth sun gear 162 and / or the third clutch C3 and / or a fourth clutch C4, preferably connected or connectable in a rotationally fixed and / or drivable manner.The fourth planet carrier 136 and the first common ring gear 86, and in particular the first intermediate element 112, are releasably connectable, in particular releasably and rotationally fixedly connectable, to the fourth planet carrier or, via the third clutch C3, to the fourth sun gear 132 and / or in particular to the sixth connecting element 142. The fourth ring gear 134 is releasably secured against rotation by the fourth brake B4. The fourth ring gear 134 can be coupled to the reversing unit housing 212 by the fourth brake B4 and / or releasably connected thereto.

[0036] The transmission 20 further comprises an intermediate gear 150. The intermediate gear 150 has a fifth planetary gear set 160 with a fifth sun gear 162, a fifth ring gear 164, a fifth planetary carrier 166, and a fifth planetary gear set 168. The two shifting elements C4, C5 of the intermediate gear 150 are a fourth clutch C4 and a fifth clutch C5. The shifting elements C4, C5 of the intermediate gear 150 are actuatable, preferably selectively actuatable, particularly preferably lockable and releasable and / or engageable and / or switchable and / or selectively engageable, in order to connect the fifth sun gear 162 or the fifth planetary carrier 166 and / or the fifth planetary gear set 168 to a second intermediate element 170 and / or the first output element 32.The fifth sun gear 162 is connected or connectable to the fourth sun gear 132 and / or the third clutch C3 and / or a fourth clutch C4, preferably connected or connectable in a rotationally fixed and / or drivable manner. The sixth connecting element 142 can be connected or connectable to the fourth and fifth sun gears 132, 162 and / or the third clutch C3 and / or a fourth clutch C4, preferably connected or connectable in a rotationally fixed and / or drivable manner. In particular, the reversing unit 120 and / or the intermediate gear 150 can at least partially encompass the sixth connecting element 142. Furthermore, the fifth planet carrier 166 is connected or connectable to the fifth clutch C5, in particular connected or connectable in a rotationally fixed and / or drivable manner. The transmission 20, in particular the intermediate gear 150, can comprise a seventh connecting element 172, in particular a seventh connecting shaft.The seventh connecting element 172 can be connected or connectable to the fifth clutch C5 and / or the fifth planet carrier 166, preferably connected or connectable in a rotationally fixed and / or drivable manner. The fifth sun gear 162 and the fourth sun gear 132, and in particular the sixth connecting element 142, are releasably connectable, in particular releasably connectable in a rotationally fixed and / or drivable manner, to the fourth or, via the fourth clutch C4, to the first output element 32 and / or the second intermediate element 170. The fifth planet carrier 166, and in particular the seventh connecting element 172, is releasably connectable, in particular releasably connectable in a rotationally fixed manner, to the fifth or, via the fifth clutch C5, to the first output element 32 and / or the second intermediate element 170. The fifth ring gear 164 is held against rotation. The fifth ring gear 164 may be coupled to the intermediate gear housing 214 and / or held against rotation.The first output element 32 is connected to the second intermediate element 170 and / or can be coupled and / or driven. For this purpose, the second intermediate element 170 and the first output element 32 can be coupled to a gear set 180 and / or the first output element 32 can be driven by the second intermediate element 170. The gear set 180 comprises two permanently meshing output gears, a first and a second output gear 182, 184, which are designed as fixed gears. The first output gear 182 is connected in a rotationally fixed manner to the second intermediate element 170, and the second output gear 184 is connected in a rotationally fixed manner to the first output element 32. The second output element 190 is connected or connectable to an output clutch 194, in particular releasably connected in a rotationally fixed manner and / or drivably. The output clutch 194 is rotationally fixedly connected to a third output gear 192. The third output gear 192 permanently meshes with the second output gear 184.The output clutch 194 can be closed so that the second output element 190 can be driven with the first output element 32.

[0037] The transmission 20 can also comprise a main transmission housing 210 accommodating the main transmission unit 22 and / or a reversing unit housing 212 accommodating the reversing unit 120 and / or an intermediate transmission housing 214 accommodating the intermediate transmission 150 and / or a rear axle housing 216 accommodating a rear axle module 24. The main transmission housing 210 can at least partially or completely accommodate the input element 30 and the first, second, and third planetary gear sets 70, 80, 90. The reversing unit housing 212 can be arranged on, in particular directly on, the main transmission housing 210 and / or the intermediate transmission housing 214 can be arranged on, in particular directly on, the reversing unit housing 212. A power and / or torque flow can be established between the main transmission unit 22 via the reversing unit 120 to the intermediate transmission 150 and then to the rear axle module 24.The reversing unit 120 can therefore be arranged downstream of the main transmission unit 22 in the direction of the power and / or torque flow. Likewise, the intermediate transmission 150 can be arranged downstream of the reversing unit 120 in the direction of the power and / or torque flow. Furthermore, the rear axle module 24 can be arranged downstream of the intermediate transmission 150 in the direction of the power and / or torque flow. The main transmission housing 210 can also at least partially or completely accommodate the second output element 190. The main transmission housing 210 and / or the reversing unit housing 212 and / or the intermediate transmission housing 214 can also be designed specifically as a housing, i.e., a transmission housing, with individual sections in the transmission housing.

[0038] The rear axle module 24 may include a rear axle differential 202 and / or the rear drive axle 16. Furthermore, the rear axle module 24 may include, in particular, the rear axle differential 202, a rear axle pinion, and a rear axle gear. The rear axle differential 202 may include a rear axle pinion, for example, a drive bevel gear or a bevel pinion, as well as a rear axle gear, for example, a bevel or ring gear. In addition, the transmission 20 may include a front axle module 220 (see Figure 1) with a front axle differential (not shown) and / or the front drive axle 14. The front axle housing (not shown) can accommodate the front axle module 220, in particular the front axle differential (not shown) and / or at least partially the front drive axle 14. The front axle differential (not shown) can comprise a front axle pinion (not shown), for example a drive bevel gear or a bevel pinion, as well as a front axle gear, for example a bevel or ring gear. The second output element 190 can be connected to the front axle pinion, or the front axle pinion and the second output element 190 can be formed as a one-piece component.

[0039] The transmission 20 can also include the PTO module 26 and / or the rear axle module 24 can be arranged between the PTO module 26 and the intermediate gear 150. Furthermore, the transmission 20 can include a PTO drive shaft 230. The PTO drive shaft 230 can be connected to the drive motor 20, in particular the crankshaft, either directly or, for example, with another coupling element or a toothed or screwed connection or by means of another drive shaft (not shown). As a result, the PTO drive shaft 230 can be driven by the crankshaft, and a force and / or torque can be transmitted from the crankshaft to the PTO drive shaft 230. The PTO drive shaft 230 can be arranged partially or completely in the drive element 30.The PTO drive shaft 230 can be arranged at least partially in the main transmission unit 22, in particular the main transmission housing 210, and / or the reversing unit 120, in particular the reversing unit housing 212, and / or the intermediate transmission 150, in particular the intermediate transmission housing 214, and / or the rear axle module 24, in particular the rear axle housing 216, and / or the PTO module 26, in particular a PTO housing. Likewise, the PTO module 26 can include a PTO stub (not shown). The PTO housing can at least partially accommodate the PTO drive shaft 230 and / or at least partially the PTO stub.

[0040] Thus, at least, in particular exactly, two shift elements B1, B2, B3, C1, C2 of the main transmission unit 22 and at least, in particular exactly, one shift element C4, C5 of the intermediate transmission 150 and at least, in particular exactly, one shift element B4, C3 of the reversing unit 120 can be actuated, preferably selectively actuated, particularly preferably lockable and releasable and / or engageable and / or switchable and / or selectively engaged in combinations of at least four, in particular exactly four, shift elements in order to establish at least, in particular exactly, 12 (twelve) forward gears, and in particular at least or exactly 12 (twelve) reverse gears, between the input element 30 and the first output element 32 and / or the second output element 190. However, only a portion of the 12 (twelve) reverse gears, i.e., fewer than 12 (twelve) reverse gears, can actually be used.

[0041] Figure 3shows a schematic representation of a second embodiment of the transmission 20 according to the invention. Figure 3 Gearbox 20 essentially corresponds to the Figures 1 to 2 shown transmissions 20, so that only details and / or differences are discussed below. The commercial vehicle 10 according to Figure 1 the gearbox 20, as shown in Figure 3shown, include. The drive element 30 is connected to the first sun gear 72, preferably connected in a rotationally fixed and / or drivable manner. The first sun gear 72 can, for example, be designed as a fixed gear on the drive element 30 or be connected to the drive element 30 via a shaft. The transmission 20, in particular the main transmission unit 22, can comprise a first connecting element 396, in particular a first connecting shaft. The first connecting element 396 can be connected or connectable to the drive element 30 and / or the first clutch C1, preferably connected or connectable in a rotationally fixed and / or drivable manner. The first planet carrier 76 is connected or connectable to the third sun gear 92 and / or the first clutch C1 and / or the second clutch C2, preferably connected or connectable in a rotationally fixed and / or drivable manner.A second connecting element 398 can be connected or connectable to the first planet carrier 76 and / or the third sun gear 92 and / or the first clutch C1 and / or the second clutch C2, preferably connected or connectable in a rotationally fixed and / or drivable manner. The first ring gear 74 is held against rotation by the first brake B1, preferably releasably held against rotation. The drive element 30, and in particular the first connecting element 396, is releasably connectable to the first planet carrier 76 and / or the third sun gear 92 and / or the second clutch C2 and / or in particular to the second connecting element 398, or via the first clutch C1. The first clutch C1 can therefore be designed to couple the drive element 30, in particular the first connecting element 396, to the first planet carrier 76 and / or the third sun gear 92 and / or the second clutch C2 and / or in particular the second connecting element 398.The first planet carrier 76 is connected to the third sun gear 92, in particular to or via the second connecting element 398. The first planet carrier 76, and in particular the second connecting element 398, can be releasably connected to the second or via the second clutch C2 to the second sun gear 82 and / or the second brake B2 and / or in particular to the third connecting element 110, in particular releasably connected in a rotationally fixed manner and / or drivably.

[0042] Figure 4 shows a schematic representation of a third embodiment of the transmission 20 according to the invention. Figure 4 The gearbox 20 shown essentially corresponds to the gearboxes shown in the Figures 1 to 3 shown transmissions 20, so that only details and / or differences are discussed below. The commercial vehicle 10 according to Figure 1 the gearbox 20, as shown in Figure 4shown, include. The drive element 30 is connected or connectable to the first planet carrier 76 and / or the first clutch C1, preferably connected or connectable in a rotationally fixed and / or drivable manner. The transmission 20, in particular the main transmission unit 22, can comprise a first connecting element 496, in particular a first connecting shaft. The first connecting element 496 can be connected or connectable to the drive element 30 and the first planet carrier 76 and / or the first clutch C1, preferably connected or connectable in a rotationally fixed and / or drivable manner. The first ring gear 74 is connected or connectable to the third sun gear 92 and / or the first clutch C1 and / or the second clutch C2, preferably connected or connectable in a rotationally fixed and / or drivable manner. Likewise, the transmission 20, in particular the main transmission unit 22, can comprise a second connecting element 498, in particular a second connecting shaft.The second connecting element 498 can be connected or connectable to the first ring gear 74 and / or the third sun gear 92 and / or the first clutch C1 and / or the second clutch C2, preferably connected or connectable in a rotationally fixed and / or drivable manner. The first sun gear 72 is secured against rotation by the first brake B1, preferably releasably secured against rotation. The drive element 30, and in particular the first connecting element 496, can be releasably connected to the first ring gear 74 and / or the third sun gear 92 and / or the second clutch C2 and / or in particular the second connecting element 498, or via the first clutch C1, to the first ring gear 74 and / or the third sun gear 92 and / or the second clutch C2 and / or in particular the second connecting element 498, in particular releasably connected in a rotationally fixed and / or drivable manner. The first ring gear 74 is connected to the third sun gear 92, in particular to or via the second connecting element 498.The first ring gear 74, and in particular the second connecting element 498, can be releasably connected to the second or via the second clutch C2 to the second sun gear 82 and / or the second brake B2, in particular the third connecting element 110, in particular releasably connected in a rotationally fixed manner and / or drivably.

[0043] Figure 5 shows a schematic representation of a fourth embodiment of the transmission 20 according to the invention. Figure 5 The gearbox 20 shown essentially corresponds to the gearboxes shown in the Figures 1 to 4 shown transmissions 20, so that only details and / or differences are discussed below. The commercial vehicle 10 according to Figure 1 the gearbox 20, as shown in Figure 5shown, include. The drive element 30 is connected to the first planet carrier 76, preferably connected in a rotationally fixed and / or drivable manner. The transmission 20, in particular the main transmission unit 22, can comprise a first connecting element 596, in particular a first connecting shaft. The first connecting element 596 can be connected to the drive element 30 and the first planet carrier 76, preferably connected in a rotationally fixed and / or drivable manner. The first planet carrier 76 is connected or connectable to the first clutch C1, preferably connected or connectable in a rotationally fixed and / or drivable manner. The transmission 20, in particular the main transmission unit 22, can comprise a second connecting element 598, in particular a second connecting shaft. The second connecting element 598 can be connected or connectable to the first clutch C1 and the first planet carrier 76, preferably connected or connectable in a rotationally fixed and / or drivable manner.The first sun gear 72 is connected or connectable to the third sun gear 92 and / or the first clutch C1 and / or the second clutch C2, preferably connected or connectable in a rotationally fixed and / or drivable manner. Likewise, the transmission 20, in particular the main transmission unit 22, can comprise a third connecting element 584, in particular a third connecting shaft. The third connecting element 584 can be connected or connectable to the first sun gear 72 and / or the third sun gear 92 and / or the first clutch C1 and / or the second clutch C2, preferably connected or connectable in a rotationally fixed and / or drivable manner. Furthermore, the second sun gear 82 is connected or connectable to the second brake B2 and / or the second clutch C2, in particular connected or connectable in a rotationally fixed and / or drivable manner.Furthermore, the transmission 20, in particular the main transmission unit 22, can comprise a fourth connecting element 594, in particular a fourth connecting shaft. The fourth connecting element 594 can be connected or connectable to the second brake B2 and / or the second clutch C2 and the second sun gear 82, preferably connected or connectable in a rotationally fixed and / or drivable manner. The transmission 20, in particular the main transmission unit 22, can comprise a fifth connecting element 514, in particular a fifth connecting shaft. The fifth connecting element 514 can be connected or connectable to the third brake B3 and / or the common planetary carrier 88, preferably connected or connectable in a rotationally fixed and / or drivable manner. The first ring gear 74 is secured against rotation by the first brake B1, preferably releasably secured against rotation.The first ring gear 74 can be coupled to the main transmission housing 210 by the first brake B1 and / or releasably connected to the main transmission housing 210, preferably releasably secured against rotation. The first planetary carrier 76, and in particular the second connecting element 598, can be releasably connected, in particular rotationally fixed and / or drivably connected, to the first or, via the first clutch C1, to the first sun gear 72 and / or the third sun gear 92 and / or the second clutch C2 and / or in particular to the third connecting element 584. The first sun gear 72, and in particular the third connecting element 584, and / or the first clutch C1 can be releasably connected to the second or via the second clutch C2 to the second sun gear 72 and / or the second brake B2 and / or in particular the fourth connecting element 594, in particular releasably connected in a rotationally fixed manner and / or drivably.The second sun gear 82, and in particular the fourth connecting element 594, is secured against rotation by the second brake B2, preferably releasably secured against rotation. The second sun gear 82, and in particular the fourth connecting element 594, can be coupled to a main transmission housing 210 by the second brake B2 and / or releasably connected to the main transmission housing 210. The first common planetary carrier 88 and / or the common planetary gear set 84, and in particular the fifth connecting element 514, are secured against rotation by the third brake B3, preferably releasably secured against rotation. The common planetary carrier 88 and / or the common planetary gear set 84 and / or in particular the fifth connecting element 514 can be coupled to the main transmission housing 210 by the third brake B3 and / or releasably connected to the main transmission housing 210.

[0044] Figure 6shows a schematic representation of a shift diagram of the first, second, third and fourth embodiments. The shift diagram shows only the twelve forward gears. The twelve reverse gears result when the third clutch C3 is actuated, in particular released, and the fourth brake B4 is actuated, in particular engaged. According to the shift diagram, the first forward gear results from actuating, in particular engaging, the first brake B1 and the third brake B3 and the third clutch C3 and the fifth clutch C5. The second forward gear results from actuating, in particular engaging, the third brake B3 and the first clutch C1 and the third clutch C3 and the fifth clutch C5. Shifting from the first forward gear to the second forward gear takes place by actuating, in particular releasing, the first brake B1 and the first clutch C1 and actuating, in particular engaging it.The third forward gear is obtained by actuating, in particular engaging, the first brake B1 and the second brake B2 and the third clutch C3 and the fifth clutch C5. Shifting from the second forward gear to the third forward gear occurs by actuating, in particular releasing, the third brake B3 and the first clutch, and actuating the first and second brakes B1, B2. The fourth forward gear is obtained by actuating, in particular engaging, the second brake B2 and the first clutch C1 and the third clutch C3 and the fifth clutch C5. Shifting from the third forward gear to the fourth forward gear occurs by actuating, in particular releasing, the first brake B1 and actuating, in particular engaging, the first clutch C1. The fifth forward gear is obtained by actuating, in particular engaging, the first brake B1 and the second clutch C2 and the third clutch C3 and the fifth clutch C5.Shifting from fourth forward gear to fifth forward gear occurs by actuating, in particular releasing, the second brake B2 and the first clutch C1, and actuating, in particular engaging, the first brake B1 and second clutch C2. Sixth forward gear results from actuating, in particular engaging, the first clutch C1, the second clutch C2, the third clutch C3, and the fifth clutch C5. Shifting from fifth forward gear to sixth forward gear occurs by actuating, in particular releasing, the first brake B1, and actuating, in particular engaging, the first clutch C1. Seventh forward gear results from actuating, in particular engaging, the first brake B1, the third brake B3, the third clutch C3, and the fourth clutch C4.Shifting from sixth forward gear to seventh forward gear occurs by actuating, in particular releasing, the first, second and sixth clutches C1, C2, C6, and actuating, in particular engaging, the first and third brakes B1, B3 and the fourth clutch C4. The eighth forward gear results from actuating, in particular engaging, the third brake B3 and the first clutch C1 and the third clutch C3 and the fourth clutch C4. Shifting from seventh forward gear to eighth forward gear occurs by actuating, in particular releasing, the first brake B1 and actuating, in particular engaging, the first clutch C1. The ninth forward gear results from actuating, in particular engaging, the first brake B1 and the second brake B2 and the third clutch C3 and the fourth clutch C4.Shifting from the eighth forward gear to the ninth forward gear occurs by actuating, in particular releasing, the third brake B3 and the first clutch C1, and actuating, in particular engaging, the first and second brakes B1, B2. The tenth forward gear results from actuating, in particular engaging, the second brake B2 and the first clutch C1 and the third clutch C3 and the fourth clutch C4. Shifting from the ninth forward gear to the tenth forward gear occurs by actuating, in particular releasing, the first brake B1 and actuating, in particular engaging, the first clutch C1. The eleventh forward gear results from actuating, in particular engaging, the first brake B1 and the second clutch C2 and the third clutch C3 and the fourth clutch C4.Shifting from the tenth forward gear to the eleventh forward gear occurs by actuating, in particular releasing, the second brake B2 and the first clutch C1, and actuating, in particular engaging, the first brake B1 and second clutch C2. The twelfth forward gear results from actuating, in particular engaging, the first clutch C1 and the second clutch C2, and the third clutch C3 and the fourth clutch C4. Shifting from the eleventh forward gear to the twelfth forward gear occurs by actuating, in particular releasing, the first brake B1, and actuating, in particular engaging, the first clutch C1.

[0045] Figure 7 shows a schematic representation of a second embodiment of the commercial vehicle 10 according to the invention with a transmission 20 according to the invention. Figure 7 The commercial vehicle 10 and transmission 20 shown essentially correspond to the Figures 1 to 6shown commercial vehicles 10 and transmissions 20, so that only details and / or differences are discussed below. Figure 7 The second embodiment of the commercial vehicle shown in the Figures 2 to 5shown transmission. Counter to the forward direction of travel 300 of the commercial vehicle 10 and / or in the direction of or along the longitudinal axis 52, the components or modules of the transmission 20 and / or commercial vehicle 10 are arranged one behind the other, in particular directly one behind the other and / or adjacent to one another, as follows. First, the drive motor 18, then the transmission 20 with the main transmission unit 22 and the reversing unit 120 and the intermediate transmission 150, behind it the rear axle module 24 and behind the rear axle module 24 the PTO module 26. In particular, the transmission 20 can be arranged in the commercial vehicle 10 such that a transmission longitudinal axis 280 is substantially parallel or coaxial with the vehicle longitudinal axis 52. The power and torque flow of the commercial vehicle can be described as follows. First, a power and torque flow is generated from the drive motor 18 via the crankshaft 240 to the drive element 30.The crankshaft 240 can be connected and / or driven to the drive element 30 either directly or, for example, with a coupling element 162 or by means of a coupling shaft (not shown) or with a toothed or screwed connection. As a result, the drive element 30 can be driven by the crankshaft 240, and a force and / or torque can be transmitted from the crankshaft 240 to the drive element 30. The flow of force and torque can thus be transmitted from the drive element 30 to the main transmission unit 22, from the main transmission unit 22 via the reversing unit 120 to the intermediate transmission 150 to the output element 32, and from there to the rear axle module 26 and / or to the front axle module 220, so that a rotational movement of the rear and / or front drive axle 14, 16 and thus a movement of the ground engagement means 28, in particular a rotational movement of the rear and front wheels 40, 42, can be produced.Likewise, a force and torque flow can also be established or generated from the output element 32 to the rear axle module and / or from a further output element 190 to the front axle module 220.

[0046] The advantages listed below apply to all figures shown. Advantageously, the transmission 20 according to the invention achieves a simple structural design and / or a sufficient number of gear ratios for the transmission 20 and the commercial vehicle 10, particularly since a minimal number of gears, clutches, and brakes are required for the transmission 20. Due to the high packing density of the transmission components of the transmission 20 in the axial and lateral directions, the transmission 20 advantageously has a compact design with minimal installation space. Likewise, additional installation space is made possible for components outside the transmission 20. At the same time, an optimal number of gears can be achieved. Furthermore, the material costs for the transmission 20 can be reduced due to the optimized design.

Claims

1. Transmission for transmitting a torque generated by a drive motor (18) to at least one front and / or one rear drive axle (14, 16) of an agricultural or industrial commercial vehicle (10), wherein the transmission comprises a drive element (30) and a first output element (32) and a main transmission unit (22) and an intermediate transmission (120) and a reversing unit (150), and the main transmission unit (22) comprises a first planetary gear set (70) with a first sun gear (72), a first ring gear (74), a first planet carrier (76) and a first planetary set (78), and a second planetary gear set (80) with a second sun gear (82), and a third planetary gear set (90) with a third sun gear (92) and a third planetary set (94), wherein the intermediate transmission (150) has a fifth planetary gear set (160) with a fifth sun gear (162), a fifth ring gear (164), a fifth planet carrier (166) and a fifth planetary set (168), and the reversing unit (120) comprises a fourth planetary gear set (130) with a fourth sun gear (132), a fourth ring gear (134), a fourth planet carrier (136) and a fourth planetary set (138), and the intermediate transmission (150) comprises exactly two switching elements (C4, C5), and the reversing unit (120) comprises exactly two switching elements (B4, C3), and the reversing unit (120) is disposed in the direction of the force and torque flux downstream of the main transmission unit (22), characterized in that the second and the third planetary gear set (80, 90) have a first common planetary set (84) and a first common ring gear (86) and a first common planet carrier (88), the main transmission unit (22) comprising exactly five switching elements (B1, B2, B3, C1, C2), wherein the switching elements (B1, B2, B3, C1, C2) are a first brake (B1) and a second brake (B2) and a third brake (B3) and a first clutch (C1) and a second clutch (C2), and at least two switching elements (B1, B2, B3, C1, C2) of the main transmission unit (22) and exactly one switching element (C4, C5) of the intermediate transmission (150) and exactly one switching element (B4, C3) of the reversing unit (120) are activatable in combinations of at least four switching elements (B1, B2, B3, B4, C1, C2, C3, C4, C5) so as to establish exactly twelve forward gears between the drive element (30) and the first output element (32). and the drive element (30) is connected to the first ring gear (74), and the drive element (30) is releasably connectable to the third sun gear (92) by way of the first clutch (C1), and the first planet carrier (76) is releasably connectable to the second sun gear (82) by way of the second clutch (C2).

2. Transmission according to Claim 1, characterized in that the intermediate transmission (150) is disposed in the direction of the force and torque flux downstream of the main transmission unit (22) and upstream of the reversing unit (120), or the reversing unit (120) is disposed in the direction of the force and torque flux downstream of the main transmission unit (22) and upstream of the intermediate transmission (150).

3. Transmission according to at least one of Claims 1 to 2, characterized in that the switching elements of the reversing unit (120) are a third clutch (C3) and a fourth brake (B4).

4. Transmission according to at least one of Claims 1 to 3, characterized in that the switching elements of the intermediate transmission (150) are a fourth clutch (C4) and a fifth clutch (C5).

5. Transmission according to at least one of the preceding claims, characterized in that the first output element (32) is connected, or able to be connected, in a drivable manner to a second intermediate element (170).

6. Transmission according to at least one of the preceding claims, characterized in that the transmission (20) comprises a second output element (190).

7. Transmission according to at least one of the preceding claims, characterized in that the transmission (20) comprises a main transmission housing (210) which receives the main transmission unit (22), and / or a reversing unit housing (212) which receives the reversing unit (120), and / or an intermediate transmission housing (214) which receives the intermediate transmission (150), and / or a rear axle housing (216) which receives a rear axle module (24).

8. Transmission according to at least one of the preceding claims, characterized in that the rear axle module (24) at least partially or completely comprises a rear axle differential (170) and / or the rear drive axle (16).

9. Transmission according to at least one of the preceding claims, characterized in that the transmission (20) comprises a power take-off module (26), and / or the rear axle module (24) is disposed between the power take-off module (26) and the main transmission unit (22), and / or the transmission (20) has a power take-off drive shaft (150).

10. Agricultural or industrial commercial vehicle, in particular a tractor or hauler, comprising a transmission (20) according to one of Claims 1 to 9.

11. Agricultural or industrial commercial vehicle according to Claim 10, characterized in that the transmission (20) is disposed in the commercial vehicle (10) in such a manner that a transmission longitudinal axis (280) is substantially parallel to or congruent with a vehicle longitudinal axis (52).