GRAIN ARRANGEMENT FOR AN AGRICULTURAL WORK MACHINE

Description

[0001] The present invention relates to a transmission arrangement for an agricultural work machine, in particular a tractor, combine harvester or forage harvester, according to claim 1. Furthermore, the present invention relates to the use of such a transmission arrangement as a pump distribution gearbox according to claim 11.

[0002] Agricultural machines, such as tractors or self-propelled harvesters, for example, combine harvesters or forage harvesters, are well known in the art. These typically have multiple working elements and / or attachments for performing or supporting agricultural work. Several of the working elements and / or attachments are hydraulically actuated or operated. Hydraulically actuated working elements can be, for example, the steering system of the agricultural machine or a lifting device such as a rear power lift for an attachment. The hydraulically actuated consumers are supplied with the necessary hydraulic energy via at least one, usually one each, fluid pump, each of which is driven by a power take-off. A power take-off is part of a drive train of the machine, which is branched off from a main transmission or represents an independent drive.Agricultural machines usually have a number of power take-offs in order to be able to supply the hydraulically operated working elements with sufficient hydraulic pressure.

[0003] The fluid pumps required for this are typically driven jointly via a gear assembly such as a pump distribution gearbox as a power splitter. The gear assembly comprises meshing gears as transmission elements, which are connected, for example, to a drive shaft and / or to an output shaft each as a power take-off. The gear assembly is lubricated by a fluid such as oil that circulates within the gear assembly. The gears are at least partially immersed in oil, which creates splashing losses and heats up the oil and thus the gear assembly.To avoid excessive churning losses, it is known, for example, from DE 103 59 109 A1, to provide a separating agent between adjacent transmission sections in a transmission arrangement, with which the two transmission sections can be separated from each other, thereby retaining lubricant in the transmission section that is not currently operating or is operating at a lower speed. The disadvantage of this is that fluctuating churning losses continue to occur within a transmission section, particularly with a fluctuating oil level, and thus undesirable heating occurs, which can lead to the permissible temperature limits of the transmission elements being exceeded, for example, when higher performance requirements are met.

[0004] DE 11 2013 007 520 T5 describes a transmission arrangement according to the preamble of claim 1.

[0005] The invention is therefore based on the object of providing a transmission arrangement for an agricultural working machine which enables reliable, efficient operation of the transmission arrangement.

[0006] The object is achieved according to the invention by the characterizing features of claim 1. Advantageous embodiments of the invention are specified in the subclaims.

[0007] According to the invention, a gear arrangement for an agricultural work machine, in particular a tractor, combine harvester, or forage harvester, is provided with a drive gear and at least one first output gear, each of which is rotatably mounted about a rotational axis and designed for rotationally fixed connection to a drive shaft or output shaft as a power take-off of the agricultural work machine. The gear arrangement has an intermediate gear meshing with the drive gear and the at least one output gear. The gear arrangement has a gear housing, the gears being arranged in an interior space formed by the gear housing. The interior space has an internal structure for enlarging the surface area of ​​the gear housing and improving heat dissipation from the gear housing, and is at least partially filled with a fluid during operation.The gear arrangement is characterized in that the gear housing has a recess on the inside at the bottom, i.e. below, the intermediate gear, which is separated from the interior at least in a lower region of the interior by a separating means, whereby a bottom-side fluid reservoir is formed at least below the intermediate gear, wherein the separating means of the bottom-side fluid reservoir has a fluid-permeable opening through which the fluid reaches the lower region of the interior during operation, wherein the tip circle of the intermediate gear is arranged lower on the bottom than the tip circles of the other gears, such that the intermediate gear is immersed in the fluid in the lower region of the interior during operation.

[0008] The interior of the transmission housing has only one section in which the gears are arranged. On the inside, the transmission housing has the internal structure and at least one recess, which is at least partially covered by the, in particular precisely, one separating means to form a fluid reservoir. The recess can be formed by the internal structure of the transmission housing. A separating means arranged on the recess, in particular on the inside of a side assigned to a gear, forms a fluid reservoir together with the recess. Fluid that is not directly used as a lubricant for the transmission arrangement can be accommodated in the fluid reservoir.By arranging the fluid reservoir laterally, adjacent to a gearwheel and, for example, with a separating agent arranged essentially perpendicular to the gearwheel's axis of rotation, one or more gearwheels can be shielded and / or encapsulated against an undesirably high fluid level, thereby reducing churning losses and heating. The lateral arrangement of at least one fluid reservoir is particularly advantageous in inclined positions, as this can prevent fluid from accumulating at the outputs and / or fluid pumps, which could lead to undesirable fluid loss. In addition, one or more fluid reservoirs have the advantage that, in the event of fluctuating oil levels, in particular an increase in the oil level, a stable and essentially constant fluid supply within the gear arrangement can be ensured, which can also enable a stable temperature balance.The internal structure and the design of one or more fluid reservoirs also increase the area of ​​the gear assembly usable for cooling the fluid, thus improving the cooling of the fluid and the gear assembly. This enables reliable and efficient lubrication of the gear assembly, especially in inclined positions.

[0009] Due to the arrangement of the intermediate gear, the fluid collects below the intermediate gear when the gear arrangement is normally aligned or flows there under the influence of gravity, so that during operation at least the intermediate gear is immersed in the fluid in a lower area and distributes the fluid through its rotation in the interior of the gear housing for lubrication and / or cooling of the other gears.

[0010] The recess located at the bottom of the intermediate gear can, for example, be completely sealed by a separating means formed integrally with the gear housing. A fluid-permeable opening in the form of a bore can be formed in the separating means in a lower region adjacent to the intermediate gear, whereby any fluid escaping through the opening toward the intermediate gear can be directly captured by the latter. The intermediate gear, for example, can be used to lubricate the gear assembly. The fluid reservoir below the intermediate gear can create a calm area for the fluid, into which contaminants can settle.

[0011] In a preferred embodiment of the invention, the gear arrangement has a second output gear, wherein the drive gear serves to drive the first output gear and the second output gear, which is rotatably mounted in the gear housing about a rotational axis, wherein the first output gear is in meshing engagement with the second output gear in addition to the intermediate gear, whereby a rotational movement of the first output gear is also transmitted to the second output gear.

[0012] In a further preferred embodiment of the invention, the separating means is in the form of a sheet metal and / or is formed integrally with the gear housing. The separating means in the form of a sheet metal can be made of metal and / or plastic. A separating means in the form of a sheet metal can be detachably arranged on the gear housing to at least partially cover a recess. A separating means made of sheet metal offers the advantage that it can be adapted cost-effectively and using simple means to the spatial conditions of the gear arrangement. For example, the separating means for a lateral recess can be designed in the form of a circular segment, which can be arranged on a correspondingly shaped recess that can be formed laterally to a gear wheel around the axis of rotation of the gear wheel.A release agent formed integrally with the gearbox housing can be manufactured together with the gearbox, for example, in the case of a gearbox made of a cast alloy. This has the advantage that the release agent can be manufactured together with the gearbox housing without any assembly.

[0013] In a preferred embodiment of the invention, the gear housing has at least one lateral fluid reservoir arranged laterally next to a gear, wherein the bottom-side fluid reservoir is connected to the fluid reservoir in a fluid-permeable manner. Fluid reservoirs arranged laterally of gears are arranged at least partially above the bottom-side fluid reservoir, so that the fluid flows in the direction of the bottom-side fluid reservoir. The laterally arranged fluid reservoirs can only have this connection to the bottom-side fluid reservoir as a fluid outlet. This has the effect that at least a portion of the fluid from the interior can be fed to the gear, in particular the intermediate gear, via a defined path via the bottom-side fluid reservoir and its gear-side opening for redistribution in the interior. This has the advantage of reliable fluid distribution in the interior, particularly in inclined positions.

[0014] In a preferred embodiment of the invention, a clearance with a height is formed between the intermediate gear and the separating means of the bottom-side fluid reservoir, wherein the separating means of the bottom-side fluid reservoir at least partially follows the circumference of the intermediate gear with a constant height, whereby the clearance is designed as a clearance with an at least partially constant cross-section. The clearance is the distance between a tip circle of the intermediate gear and a bottom of the transmission housing, which is arranged radially adjacent to the intermediate gear. As a result, the bottom follows the contour of the intermediate gear at least along part of its circumference, whereby the conveyance of the fluid by the rotating intermediate gear can be improved. In addition, the clearance can be relatively narrow, whereby, for example, the clearance can be less than or equal to the tooth width of the intermediate gear.

[0015] In a further advantageous embodiment of the invention, the internal structure is annular at least in the region of the axis of rotation of a gear, and the annular structure, in particular on an upper side, has at least one fluid-permeable opening for supplying fluid to the axis of rotation. The internal structure of the gear housing can be rib-shaped and / or annular. An annular internal structure can be formed around an axis of rotation and configured as a bearing seat for receiving a bearing of a gear. Fluid can be guided from the interior to a gear, in particular on the inside of the gear to a shaft, through the fluid-permeable opening on the upper side of the annular internal structure or the bearing seat.

[0016] It is further advantageous that the internal structure, particularly in the region above the at least one fluid-permeable opening in the annular structure, is funnel-shaped. The fluid-permeable opening is formed in the annular internal structure or the bearing seat. The funnel-shaped internal structure can be formed by ribs, which can increase the amount of fluid that can be supplied to the opening. This has the advantage of improved lubrication of the gear and the shaft connected to it in a rotationally fixed manner, for example, the output shaft.

[0017] In a further advantageous embodiment of the invention, the internal structure has at least one guide element which essentially guides a fluid away from an inner side of the gear housing. The guide element can be detachably connected to the inside of the gear housing and can be made, for example, from a metal and / or a plastic. A one-piece design of the guide element with the gear housing is also conceivable. The guide element is essentially an arc-shaped U-profile and guides fluid away from the inside of the gear housing and, for example, towards and into a rotational axis of a gear, so that the fluid can be used to lubricate the gear or a shaft connected to it in a rotationally fixed manner, and thus the outputs.

[0018] In a preferred embodiment of the invention, at least one gear has an annular cap on its inside to retain the fluid. The cap is formed on the inside of the gear, around its axis of rotation. On the gearbox side, the cap forms a circumferential edge directed radially inward towards the axis of rotation. The edge of the cap can retain at least a portion of the fluid, which is guided into the gear in particular by means of the guide element, in the gear to ensure minimum lubrication. A guide element can extend over the cap and in particular the edge of the cap into the interior of the gear to ensure reliable guidance of the fluid into the gear.

[0019] Furthermore, the invention relates to an agricultural working machine, in particular a tractor or a self-propelled harvesting machine, with at least one gear arrangement as described and designed above.

[0020] Furthermore, the invention relates to the use of the gear assembly described and configured above as a pump transfer case. The transfer case can be configured such that it can drive at least two auxiliary drives, such as fluid pumps, simultaneously, with one drive being provided via the drive shaft.

[0021] The invention is explained in more detail below with reference to the attached drawings

[0022] They show: Fig. 1 shows a transmission arrangement for an agricultural working machine according to the invention in a perspective view with an opened transmission housing; Fig. 2 shows a detailed sectional view of the transmission arrangement from Fig. 1 along the line AA; Fig. 3 a detailed perspective view of a fluid reservoir arranged below a gear; Fig. 4 a sectional view (BB) of the fluid reservoir from Fig. 3; Fig. 5 a detailed perspective view of the internal structure of the gear housing with a guide element; and Fig. 6 a sectional view of the gear arrangement from Fig. 5 along line CC.

[0023] In Figure 1a gear arrangement 10 for an agricultural work machine such as a tractor or a self-propelled harvester is shown. The structure of a tractor or a self-propelled harvester will not be discussed in detail, as this is considered to be known to those skilled in the art. The gear arrangement 10 has a gear housing 12 in which a drive gear 14 is arranged, which is mounted so as to be rotatable about an axis of rotation 24 and which can be driven via a drive shaft 22, for example by a drive train (not shown) with a drive motor. The drive gear 14 serves to drive a first output gear 16 and a second output gear 18, which are also mounted so as to be rotatable about axes of rotation 24 in the gear housing 12.The output gears 16, 18 can each be connected to an output shaft (not shown), whereby auxiliary drives can be provided for driving, for example, hydraulic fluid pumps, via which hydraulically actuated working units of the agricultural working machine can be driven.

[0024] The first and second output gears 16, 18 are driven by an intermediate gear 20. The intermediate gear 20 meshes with the corresponding teeth 26 of the drive gear 14 via radially outwardly arranged teeth 26. In the illustrated embodiment, the intermediate gear 20 also meshes with the first output gear 16, so that a rotational movement of the drive gear 14 is transmitted via the intermediate gear 20 to the first output gear 16. In addition to the intermediate gear 20, the first output gear 16 also meshes with the second output gear 18, whereby a rotational movement of the first output gear 16 is also transmitted to the second output gear 18. The second output gear 18 is thus driven by the drive gear 14 via the intermediate gear 20 and the first output gear 16.The gears 14, 16, 18, 20, which have different diameters, are arranged essentially in a horizontal row adjacent to one another in the housing and, in particular, in one plane. For lubrication and cooling of the gear assembly 10, a fluid 46 is arranged within the interior space 30 formed by the gear housing 12. This fluid is distributed within the interior space by the rotation of the gears 14, 16, 18, 20. Excessive immersion of the gears 14, 16, 18, 20 can lead to increased splashing losses and undesirable heating of the gear assembly.

[0025] In the gear assembly 10 according to the invention, the fluid is distributed within the interior 30 of the gear assembly 10 via the intermediate gear 20, which is arranged lower than the drive gear 14 and the driven gears 16, 18. The tip circle of the intermediate gear 20 is arranged lower on the bottom side than the tip circles of the other gears 14, 16, 18, so that the fluid 46 is distributed within the interior 30, the so-called lubrication, essentially via the intermediate gear 20. The fluid 46 distributed within the interior 30 can be at least partially returned to the bottom side via the inner surfaces of the gear housing 12. An internal structure 28 formed on the inside of the gear housing 12 can enlarge its surface area and improve heat dissipation.To accommodate the particularly recirculated fluid 46, the gear housing 12 has a recess 38 on the bottom side, which is separated from the interior 30 at least in a lower region 32 by a separating means 34, thereby forming a bottom-side fluid reservoir 39. The bottom-side fluid reservoir 39 is arranged substantially below the intermediate gear 20.

[0026] A small lower clearance with a height h is formed between the intermediate gear 20 and the separating means 34 of the bottom-side fluid reservoir 39, whereby the conveying and distribution of the fluid 46 in the interior can be improved. The height h of the clearance is essentially less than or equal to the tooth width b of the intermediate gear 20. The lower region 32 is designed such that the separating means 34 of the bottom-side fluid reservoir 39 at least partially follows the circumference of the intermediate gear 20 with a constant distance and / or height h, whereby a clearance with an at least partially constant cross-section is formed, whereby the conveying of the fluid can be improved.

[0027] A fluid 46 located in the bottom-side fluid reservoir 39 can flow through an opening 36 in the separating means 34 of the bottom-side fluid reservoir 39 in the direction of the intermediate gear 20 into the lower region 32, for example, to be distributed from there back into the interior 30 of the gear housing 12. The bottom-side fluid reservoir 39 offers the advantage that the fluid located there can be calmed, allowing foreign matter and contaminants to settle there and not be distributed back into the interior 30. Furthermore, the bottom-side fluid reservoir 39 can increase the amount of fluid available in the gear assembly 10 without causing an increase in the temperature of the gear assembly, for example due to splashing losses. This has the advantage that the service life of the fluid, for example oil, can be increased and the necessary maintenance intervals can be extended.

[0028] In Figure 21 shows a sectional view of the gear housing 12 along section line AA. The section runs through the intermediate gear 20, which is rotatable about the rotational axis 24 and is supported relative to the gear housing 12 by means of bearings 44. The bottom fluid reservoir 39 is formed on the bottom side, i.e., below the intermediate gear 20. This fluid reservoir is separated from the intermediate gear 20 by the separating means 34, wherein fluid 46 can escape via the opening 36 into a lower region 32 of the interior. The separating means 34 of the bottom fluid reservoir 39 can be detachably arranged on the gear housing 12 or formed integrally therewith. The separating means 34, in particular of the bottom fluid reservoir 39, can be formed in one or more parts and can be made, for example, from a metal and / or a plastic.

[0029] In the lower region 32, recesses 38 are arranged on both sides of the intermediate gear 20. These recesses are covered by separating means 34 in the form of metal sheets relative to the intermediate gear 20, thereby forming lateral fluid reservoirs 40. The sheet-metal separating means 34 and / or the lateral recesses 38 are semicircular or arcuate in shape. The lateral recesses 38 and / or lateral fluid reservoirs 40 can be formed around the rotational axis 24 of the intermediate gear 20 and can accommodate fluid 46, which flows back toward the floor via the inner surfaces of the interior space 30.

[0030] The lateral fluid reservoirs 40 can initially absorb backflowing fluid 46 and keep it away from the intermediate gear 20 in the lower region 32, thereby preventing excessive immersion of the intermediate gear 20 in the fluid and reducing splashing losses. Furthermore, the arcuate and / or semicircular design of the lateral recesses 38 and / or separating means 34 and / or lateral fluid reservoirs 40 allows fluid to be reliably retained even when the transmission housing 12 is at an angle. Furthermore, the lateral separating means 34 offer the advantage that, in an inclined position, no fluid, or oil, can accumulate at the output gears 16, 18 and, for example, the hydraulic fluid pumps connected thereto. Fluid loss due to so-called suction pumps can thus be avoided.

[0031] The fluid which is propelled through the housing by the gears 14, 16, 18, 20 during operation can flow down the inner walls of the gear housing 12 and collect behind the separating means 34 in the lateral fluid reservoirs 40. The bottom-side fluid reservoir 39 can be connected in a fluid-permeable manner, in particular on the inlet side, to at least one of the lateral fluid reservoirs 40 in order to convey the collected fluid from the lateral fluid reservoirs 40 into the bottom-side fluid reservoir 39. From the bottom-side fluid reservoir 39 ( Figure 3) the fluid can pass through the at least one opening 36 into the lower region 32 to the intermediate gear 20, from where it can be distributed again into the interior space 30. By connecting at least one lateral fluid reservoir 40 and the bottom-side fluid reservoir 39, as well as supplying the fluid into the interior space 30 from the bottom, the influence of fluctuations in the fluid level on the gear arrangement 10 can be reduced. The influence of the fluid fill level on churning losses and on an increase in temperature can thereby be reduced. The bottom-side fluid reservoir 40 has a sufficiently large volume so that fluid flowing back thereto can be calmed before escaping through the opening 36, whereby impurities in the fluid can settle and do not re-enter the fluid circuit in the interior space 30 of the gear arrangement 10.In the gear housing 12, a drain opening 48 is arranged on an underside of the bottom-side fluid reservoir 40, which is releasably closed by a drain screw 50 in order to be able to drain the fluid and / or deposited contaminants from the gear housing 12.

[0032] In Figure 4a sectional view of the gear housing 12 along the section line BB is shown. The section shown runs through the lateral fluid reservoirs 39 arranged on both sides of the intermediate gear 20 and the bottom fluid reservoir 39 arranged below them. The fill level of the fluid 46 in the lateral fluid reservoirs 40, which can, for example, flow back into the lateral fluid reservoirs 40 via the inner walls after distribution in the interior 30, is higher than on the underside of the intermediate gear 20 in the lower region 32, whereby churning losses can be reduced. The fluid 46 passes through fluid-permeable connections (not shown) into the bottom fluid reservoir 39, from where it can flow through the opening 36 (not shown) into the lower region 32 on the intermediate gear 32, from where it can flow through the opening 36 (not shown) into the lower region 32 on the intermediate gear 32, from where it is distributed by the intermediate gear 20 in the gear housing 12.The transmission housing 12 has a housing cover 42 detachably secured by fastening means 52. The housing cover 42 has an internal structure 28 and recesses 38 on the inside, which partially form lateral fluid reservoirs 40 and the bottom-side fluid reservoir 39. The separating means 34 of the bottom-side fluid reservoir 39 is at least partially formed in the housing cover 42.

[0033] In Figure 5the area of ​​the transmission housing 12 in which the second output gear (not shown) is arranged is shown. The internal structure 28 of the transmission housing 12 is designed both in the form of ribs 56 and in the form of an annular bearing seat 54. The bearing seat 54 serves to accommodate the bearings (not shown) of the second output gear (not shown). The ribs 56, in particular above the bearing seat 54, and / or a lateral fluid reservoir (not shown), are arranged in a funnel shape and open into an opening 36. The opening 36 is arranged on top of the bearing seat 54 and allows a fluid, which has been directed there from the inner wall via the funnel-shaped ribs 56, to flow into the bearing seat 54.

[0034] The output gears 16, 18, in particular the one in Figure 6The second output gear 18, shown along section line CC, has a cavity arranged concentrically around the axis of rotation 24, through which the fluid can be guided, for example via appropriately designed output shafts (not shown), to lubricate the auxiliary output. The fluid is guided into the output gear 16, 18 by a guide element 58 arranged on the inside of the transmission housing 12, within the bearing seat 54. The guide element 58 is connected at one end, in particular detachably, to the transmission housing 12 and has at the other end a profile angled from the inside of the transmission housing 12 for guiding the fluid.

[0035] From the inner wall of the gear housing 12, the fluid can pass through an opening (not shown) directly through the internal structure 28 or the bearing ring 54 to the guide element 58. Via a groove-shaped opening 36 arranged externally on the upper side of the bearing seat 54, the fluid can pass from the inner wall of the gear housing 12 to the gear 16, 18 and from there, for example, flow through the bearing 44 to the guide element 58. The fluid is then at least partially guided from within the bearing seat 54 via the guide element 58 into the output gear 16, 18.

[0036] To ensure that the fluid remains within the output gear 16, 18, the latter has a circumferential cap 60 on the edge of the cavity on the guide element side, which protrudes radially inward like a collar and retains the fluid in the output gear 16, 18. The second output gear 18 is rotatably mounted in the transmission housing 12 via bearings 44 supported in the bearing seats 54. A bearing seat 54 is formed in the housing cover 42. On the housing cover side, no guide element is arranged on the output gears 16, 18, since the output shafts (not shown) protrude through the transmission housing 12 and the housing cover 42. List of reference symbols

[0037] 10Gearbox assembly 12Gearbox housing 14Drive gear 16First driven gear 18Second driven gear 20Idler gear 22Drive shaft 24Rotation axis 26Teeth 28Internal structure 30Interior 32Lower area 34Separator 36Opening 38Recess 39Bottom fluid reservoir 40Side fluid reservoir 42Housing cover 44Bearing 46Fluid 48Drain opening 50Drain plug 52Fastener 54Bearing seat 56Rib 58Baffle 60Cap bTooth width hHeight

Claims

1. A gear assembly (10) for an agricultural working machine, in particular a tractor, combine harvester or forage harvester, with a driving toothed wheel (14) and at least one first driven toothed wheel (16), which are respectively rotatably mounted about an axis of rotation (24) and are configured for connection, in a manner which is fixed against rotation, to a drive shaft (22) or driven shaft as a power take-off for the agricultural working machine, wherein the gear assembly (10) has an intermediate toothed wheel (20) which is in meshing engagement with the driving toothed wheel (14) and the at least one driven toothed wheel (16), wherein the gear assembly (10) has a gear housing (12), wherein the toothed wheels (14, 16, 20) are disposed in an interior space (30) formed by the gear housing (12) which has an interior structure (28) in the interior for increasing the surface area of the gear housing (12) and for improving the dissipation of heat from the gear housing (12) and which is at least partially filled with a fluid (46) during operation, characterized in that the interior of the gear housing (12) has a recess (38) on the bottom, i.e. underneath the intermediate toothed wheel (20), which is separated from the interior space (30) by a separating means (34) in at least a lower region (32) of the interior space (30), whereupon a bottom fluid reservoir (39) is formed at least underneath the intermediate toothed wheel (20), wherein the separating means (34) of the bottom fluid reservoir (39) has a fluid-permeable opening (36) via which, during operation, the fluid (46) gains access to the lower region (32) of the interior space (30), wherein the disposition of the bottom of the tip circle of the intermediate toothed wheel (20) is deeper than the tip circles of the other toothed wheels (14, 16) such that in operation, the intermediate toothed wheel (20) dips into the fluid (46) in the lower region (32) of the interior space (30).

2. The gear assembly (10) according to claim 1, characterized in that the gear assembly (10) has a second driven toothed wheel (18), wherein the driving toothed wheel (14) serves to drive the first driven toothed wheel (16) and the second driven toothed wheel (18) which is rotatably mounted in the gear housing (12) for rotation about an axis of rotation (24), wherein in addition to the toothed wheel (20), the first driven toothed wheel (16) is also in meshing engagement with the second driven toothed wheel (18), whereupon a rotational movement of the first driven toothed wheel (16) is also transmitted to the second driven toothed wheel (18).

3. The gear assembly (10) according to claim 1 or claim 2, characterized in that the separating means (34) is in the form of a sheet of metal and / or is formed in one piece with the gear housing (12).

4. The gear assembly (10) according to one of the preceding claims, characterized in that the interior of the gear housing (12) has at least one lateral fluid reservoir (40) disposed laterally next to a toothed wheel (14, 16, 18, 20), wherein the bottom fluid reservoir (39) is connected to the fluid reservoir (40) in a fluid-permeable manner.

5. The gear assembly (10) according to one of the preceding claims, characterized in that a clearance with a height (h) is formed between the intermediate toothed wheel (20) and the separating means (34) of the bottom fluid reservoir (39), wherein the separating means (34) of the bottom fluid reservoir (39) follows at least part of the circumference of the intermediate toothed wheel (20) at a constant height (h), whereupon the clearance is configured as a clearance with a cross section which is constant at least in parts.

6. The gear assembly (10) according to one of the preceding claims, characterized in that the interior structure (28) is annular in configuration at least in the region of the axis of rotation (24) of a toothed wheel (14, 16, 18, 20), and the annular structure (54), in particular at an upper side, has at least one fluid-permeable opening (36) for the supply of fluid to the axis of rotation (24).

7. The gear assembly (10) according to claim 6, characterized in that the interior structure (28) is configured in the shape of a funnel, in particular in the region above the at least one fluid-permeable opening (36) of the annular structure (54).

8. The gear assembly (10) according to one of the preceding claims, characterized in that the interior structure (28) has at least one guide element (58) which substantially guides the fluid away from an interior of the gear housing (12).

9. The gear assembly (10) according to one of the preceding claims, characterized in that the interior of the at least one toothed wheel (14, 16, 18, 20) has an annular cap (60) for holding back the fluid (46).

10. An agricultural working machine with at least one gear assembly (10) according to one of the preceding claims.

11. Use of a gear assembly (10) according to one of claims 1 to 9 as a pump transfer gear.