DE4020161A1 - Multiple shaft gearbox with input shaft driven oil pump - has suction pipe with filter fitted lower end in sump and upper end with constantly filled intermediate reservoir at pump level - Google Patents

Abstract

The multiple-shaft gearbox (1) has a pump (18), in the upper region of the gearbox, connected directly to the drive shaft (8). The pump provides lubrication for the gears (19-28) and pressure for disc clutch operation. A lower end of a pump suction pipe (16) is fitted with a filter (36) and submerged in an oil reservoir (31). The upper end feeds an intermediate oil reservoir (18a) located at pump level and on the output side (14) of the gearbox. The intermediate oil reservoir does not empty when the pump is not operating. ADVANTAGE - Dry running of the pump is avoided.

Description

The invention relates to a multi-shaft transmission according to Preamble of claim 1, which starts from the DE-A-25 29 248, in which a self-contained Gear system with several parallel to each other and partially superimposed shafts or axes various actuatable via hydraulic fluid Multi-plate clutches, gears, bearings and rotary unions is shown. In it the supply is one too Leading clutch actuating cylinders, bearings and gears and pressure oil system equipped with control valves With the help of a motor driven directly Pressure pump provided.

The pressure pump is located directly on the Drive shaft, at the end of a connector for engine-dependent power take-off is provided. So that's one independent of all switching states of the transmission Function of the pressure pump and one power take-off ensured. To replace the pump rotor had to however, the drive shaft will be removed, and at Use cases with rough alternating operation in different directions and frequent starts and Stops as well as in the cold and changing equipment requirements with regard to power take-offs, it was disadvantageous that the arrangement located relatively high above the oil reservoir the pump and narrow suction cross sections a quick and reliable oil production difficult and none on the suction side Fine filtration appropriate to the working gaps of the pump was possible. Both pump and valve damage from Dirt parts and idling of the pump during breaks in operation The risk of dry start damage was therefore frequent. In addition  the familiar design pointed out some more service aggravating arrangements and other variable applications hindering design features.

The object of the invention is based on this seen to create a multi-shaft gearbox that the avoids the disadvantages indicated above and is suitable highly stressed and intermittently operable switching and reversing gear with couplings that can be actuated by pressure medium Functional and compact brakes in one common assembly and maintenance friendly and versatile use case customizable housing to bring a pressure pump even after Breaks an oil pressure system immediately enables to make ready for operation.

Another object of the invention is to provide an arrangement do not find the inspection and maintenance of the pump Require removal of the drive shaft and by Connecting parts for power take-offs are hampered and still Extensions or re-dimensioning with others Power take-offs without influencing the drive shaft or of the clutches are possible.

The solution comes with the distinctive features of Claim 1 achieved in particular in that the Multi-shaft gearbox approximately at the center of the pump arranged intermediate container is provided, which in a somewhat lower pump suction nozzle opens, the Suction line for a submerged in the collection container Main filter begins.

With this suction line principle, one can be tight Working column instructed pressure pump for the actuation of Pressure cylinders on multi-plate clutches are reliable and  be operated with low wear so that even after Breaks of operation neither threaten dry running nor valve- and control effort is required. Thereby from the pressure lines only have very short wall or cover areas claimed, which easily with sufficient Cross-section and pressure-resistant are executable, while the Pressure connections to the lubrication points and actuators via high-strength and easily sealable hoses, Slewing rings and shaft bores are made. The longer one The suction line of the pump is usually warm permanent gear wall so amply dimensioned and nonetheless embedded in a space-saving manner, that after a one-off Initial commissioning no longer causes suction problems. This succeeds by flooding the pump and allows towards a valve control for the intermediate container dispense. The submerged arrangement has a favorable effect of a large filter constantly kept below the oil level on the suction side of the pump. This makes it possible to ensure particularly fine filtration and the pump train safely as a high pressure pump and also on the pressure side correspondingly sensitive high pressure Control valves and actuators for small To use actuating cylinders. The pump can easily accessible near the housing cover and easy to maintain.

Control valves can be located in an upper housing cover be provided so that only short pressure lines up to an overflow valve in a common Multiple valve plate are required. Of this Overflow valve and any other outflow spouts of the valve plates can leadless drains into the Gearbox housing or the existing ones Lubrication points take place from where the draining oil is free in the sump of the gearbox, which acts as a sump serves, can expire.  

According to the invention, the pump remains despite its arrangement in the upper part of the housing thanks to the oil accumulation effect of the Intermediate container in their supply line at any time without any Control valve ready to start and absorbent from the Large fine filter located on the housing base. As a result of that this is not on the pressure side and also not in a narrow Line section must be installed, but in large Lower part of the gearbox practically all-round, well-tempered Offers oil access, its pressure drops are also at Fine filtration is not impermissibly large and can also be Dirt residues in the oil pump, valves and actuating cylinders Protect damage effectively.

Further advantageous embodiments are the Subclaims 2 to 8 specified.

When designing the intermediate container as with its apex up to about the center of the pump and after there falling cable bend within the output-side housing wall, which both from Oil reservoir and the pump are always open is held in the simplest and most valveless way broad intake cross section achieved and without any Control effort for the pump constantly immediately suckable oil volume ready.

The fact that the axial bores in the shafts both main courses in ring channels of the respective Coupling hubs with connections to the pressure cylinders of the Receiving actuators, side outlets are also permitted Lubrication points, for example, in the bearings or above Manufacture gears easily.

If the pump is a gear or Rotary lobe pump is used in conjunction with a bearing jointly removable structural unit within the  Housing wall on the end protruding from the bearing driving shaft is attached, the pump is for Maintenance and inspection easily accessible even when the gear cover and those on it Control valves cannot be dismantled.

If the couplings are mounted on short hollow shafts, the core waves passing through the housing wall enclose, so the short hollow shafts can be velvet Couplings after pulling out the core shafts through the Housing walls easily removed or removed through the housing cover install. Axially split are preferred Tapered bearings mounted in the housing walls.

The integration of a valve plate in the Housing cover results in an assembly and maintenance-friendly housing design and valve arrangement. Depending on the size of the gear cover, there is even space for additional gear outlets on not from the Valve plate occupied area.

Due to the sandwich structure of the multiple valve plate is this as a connecting flange in the housing walls integrated connecting lines and control valves can be used particularly advantageously, the Valve drain connection from the valve plate in the direction the inside of the gearbox or to the lubrication points there, such as bearings or gears.

By designing the main filter in the form of a closable pipe with walls on the outlet side Filter material and an inflow end face in which a Replacement of the filter basket that closes automatically Blocking plate is provided, it is possible to close the filter clean without draining more oil from the gearbox than the filter housing.  

A particularly advantageous gear design and Housing arrangement is achieved when the housing cover and Multiple valve plate together have a narrower area than cover the housing plan and only with one of the Seal the longitudinal edges of the upper part of the housing approximately flush and in the place of another flush longitudinal edge an inclined surface is cast on, the other if necessary Can receive mounting openings, in which decentralized, from the power take-offs on the input shaft of the gearbox can be retrofitted without extending the gearbox.

The invention is not based on this Characteristic combinations of the claims limited. For the Specialists arise more sensible Possible combinations of claims and individual Claim characteristics from the task.

The invention is based on several schematic Drawings explained in more detail below:

Fig. 1 shows a schematic section of an overall view of a multi-shaft transmission according to the invention.

Fig. 2 shows a side view of this with the flanges of the pump and bearings and an arrangement of the pressure hoses between the multiple valve plate and the rotary unions in the flanges. You can also see the optional inclined surface for the possible attachment of additional power take-offs over a longitudinal edge of the housing.

Fig. 3 shows a cross section through a cover designed as a bearing plate for a decentralized power take-off of an inclined surface over a longitudinal edge of the transmission housing.

Fig. 4 shows a partial cross section through the upper housing part with input shaft input, pump mounting option and the sandwich-shaped multiple valve plate.

Fig. 5 shows an outside plan view of the upper housing part.

Fig. 6 shows a partial longitudinal section through the transmission middle section with two main shift shafts and their couplings including the shaft bores with the rotary unions.

FIGS. 7 and 8 show longitudinal sections through the gear base with output gear, the output shaft and abgetauchtem in the accumulator tank main filter.

In Fig. 1, the gear housing 1 shown as an example has a total of three shafts 5 , 6 , 7 equipped with double clutches 2 , 3 , 4 and a simple clutchless drive shaft 8 or its hollow shaft 8 A, an intermediate shaft 9 and an output shaft 10 . With the exception of the intermediate shaft 9 , which is not rotatably attached to the drive-side housing end wall 13 , all shafts 5 , 6 , 7 and 8 each have at least one bearing 12 in one of the end walls 13 , 14 of the gear housing 1 or in the side covers 46 or 46 A, which are provided on the gear housing 1 ..

The opening covered by the upper housing cover 15 is sufficient to be able to use it for the assembly or disassembly of the double clutches 2 , 3 , 4 on the hollow shafts or inner disk carriers carrying them. The actual shafts 5 , 6 , 7 etc. are then installed and removed through the normal-sized side openings on the bearings 12 .

The hollow shaft 8 A is carried by the drive shaft 8 via a torsional vibration damper or a converter clutch 11 , which are driven by the motor, not shown.

The drive shaft 8, which is introduced through the upper side housing cover 46 A with a coaxial hollow shaft 8 A, is guided in the drive-side housing wall 13 and at its opposite end in the output-side housing wall 14 , each with a bearing 12 and provided with a pump 18 driven by the drive shaft 8 . The on which the drive shaft 8 enclosing the hollow shaft 8. A fitting fixed gear 19 is in direct engagement with a respective one inner disk carrier of the associated dual clutch 2, 3 entraining idler gear 20, 21 on the plane parallel to the drive shaft 8 shafts 5 and 6. FIG. The idler gear 21 is in turn engaged with a small reversing gear 22 on the intermediate shaft 9 , which in turn drives a small idler gear 23 with an attached inner disk carrier of the double clutch 4 on the shaft 7 . The outer disk carriers of the double clutches 2 , 3 and 4 also have external toothings on their circumference, which mesh directly with one another at the same time. Further inner disk carriers are located on the side of the double clutches 5 , 6 , 7 facing away from the drive. Of that one of the double clutch 2 is connected to an idler gear 24 on the shaft 5 , which is in engagement with a large idler gear 25 also connected to the corresponding inner disk carriers on the shaft 6 , which is directly upstream of a smaller idler gear 26 on the pump side, which also has a a larger idler gear 27 that engages the inner disk carrier meshes on the shaft 7 , from which a somewhat smaller fixed gear 28 is driven on the output shaft 10 . The latter can optionally be provided on one or both end faces 13 , 14 outside of its bearings 12 with output connections 29 , 30 . The fixed gear 28 on the output shaft 10 plunges approximately one third of its diameter into an oil reservoir 31 , which is located in the bottom of the transmission housing 1 . A main filter 32 with a horizontal axis is immersed in this oil reservoir 31 , in which the oil drawn to the pump 18 via the oil channel 17 can flow horizontally through an end opening 34 which can be shut off with a valve cone 33 or a closure plate 39 . On the valve plug 33 opposite end side of the main filter 32 of the valve plug 33 is provided via a rod 37 with an applied under spring pressure against the end opening of the main filter 32 closure disc 35 which thereby a said housing holds 32 A of the main filter 32 inside lining filter basket 36th The closure disk 35 holds an axially penetrating rod 37 with the valve cone 33 . It is on the drive side with a flange cover 38 which permits removal of the closure disk 35 together with the filter housing 36 , the valve cone 33 and the closure plate 39 lying in front of the inlet opening 34 . The oil reservoir 31, which surrounds the filter housing 32 A, thereby flowing via a supply channel 34 A back running oil from the overlying gear 1 is no longer, as long as the valve 33 and the plate holding closed 39, the filter housing 36th A relatively quick and efficient oil filter cleaning is thus possible without having to open the transmission 1 in the area of the clutches 2 , 3 , 4 .

Above the top of the filter housing 32 , the oil channel 16 to the pump begins in a horizontal partition 40 , which is let into the side gear housing wall and is designed with a large flow cross-section. The filter 32 is guided past the fixed wheel 28 in the region of the lowest oil level, and the horizontal separating floor 40 located above it causes an inflow to the filter 32 only at the deepest point of the oil supply 31 .

The oil channel 16 is led up to the area of the pump 18 and there up to approximately in the middle of its axis and forms with its connecting bend in the pump 18 one of these intermediate containers 18 A directly upstream with an outlet opening directly into the pump 18 .

The pump 18 feeds into a further oil channel 17 , which is embedded in the wall of the transmission housing 1 and opens into a multiple valve plate 41 on the upper housing cover 15 . From this multiple valve plate 41 , overflow empties can be blown down directly onto gear wheels and shaft bearings. The control pressure lines 43 from there to the not shown in detail the hydraulic operations of the twin clutches 2, 3, 4 are provided from the multi-valve plate 41 in to the outer wall of the transmission housing 1 installed Hochdruckschlauch- or pipes 43 and open at the pump side of the wall of the housing 1 emerging ends of the shafts 5 , 6 , 7 in rotary unions to axially parallel oil channels arranged within the shafts 5 , 6 , 7 , from which radial inlets to the clutch pistons and lubrication openings are provided at bearing points and gear wheels.

In FIG. 2, the view of the output-side housing end face 14 is shown. At the bottom of the gear housing 1 , the main filter 32 is indicated at the edge of the housing 1 , which is held by a partition 40 outside the flow influences of the fixed wheel 28, which is immersed in the oil reservoir 31 but is not visible here. Above the housing 32 A of the main filter 32 , a wide suction channel 16 to the pump 18 starts in the wall of the housing 1 . For a possible cleaning facilities etc. is provided in the example, this oil passage easy to make 16 A in the end wall 14 with a separate flange 16 B inspectable. Shortly before entering the housing of the pump 18 , the oil channel 16 has a bend which extends up to approximately the axis of the pump 18 and is then inclined to the pump 18 , so that a small intermediate container 18 A is formed directly in front of the pump 18 and when the drive shaft 8 is at a standstill the pump 18 cannot run backwards to the filter 32 . Thus, without the need for complicated control valves and controls, there is no danger of a dry start. Above the intermediate container 18 A, the pressure channel 17, which is also let into the wall here, leaves the pump 18 and opens after a short distance from below into a multiple valve plate 41 that is flanged to the housing cover 15 in a sandwich-like manner. The pressure control lines lead from the housing cover 15 by means of pressure hoses or pipes 43 to the rotary unions 44 at the ends of the shafts 5 , 6 , 7 which are occupied by the double clutches 2 , 3 , 4 and protrude from the pump 1 . These shafts 5 , 6 , 7 are arranged here in an isosceles triangle slightly obliquely below the drive shaft 8 with the pump 18 , the shaft 5 taking the top and the shaft 7 the bottom place. The intermediate gear 9 is arranged here in a housing bulge near the shafts 5 and 6 . Exactly vertically below the drive shaft 8 , the output shaft 10 is provided, which laterally pierces a large lower side cover 46 for the oil reservoir 31 , where it also has its bearings 12 . One upper side edge of the housing is chamfered in the example so that, if necessary, a flange closure 47 can be provided there for one or more power take-offs 48 that can be attached laterally to the drive shaft 8 . For this purpose, only the wall material needs to be worked away accordingly or left out during casting.

In Fig. 3, an example for such built-in Gehäuseschrägung the power take-off 48 is shown in cross section. In it, the drive shaft 8 entering through the housing end face 13 carries a fixed gear 49 on the output side of the fixed gear 19 , which drives an idler gear 50 which is guided with a bearing 52 on a plug-in axle 51 inserted in parallel into an edge of the flange cover 15 . The molded-Zusatzflanschdeckel 15 A for the auxiliary drive 48 is an auxiliary housing 53 directly formed, in which a both sides out with passing shaft flanges 57 PTO shaft 54 rotates at a Nebenabtriebsfestrad 55 on the PTO bearing 56th Pumps 58 can be connected to the shaft 54 , for example. To supply oil to the power take-off bearings 52 and 56 , a special power take-off oil channel 59 cast into the wall is branched off from the pressure channel 17 in the area of the end wall 13 and continues into the radial bores under the double clutches 2 , 3 , 4 or bearing points 12 etc. with radial bores flows. the channel 59 is closed on the housing side by a bearing housing 19 B inserted into the additional flange cover 15 A, which has an opening (not shown) for the passage of the gear wheel 19 .

In FIG. 4, an example of the configuration of the multiple valve plate 41 is shown, the 15 shared here the housing cover as part of a so-called sandwich construction. For this purpose the housing cover 15, the various control channels are provided to the A 41 is guided in the flange screwed multiple valve plate 41 adjacent magnet slide valves 41 B to control the twin clutches 2, 3, 4 in the top. The oil supply to the valves 41 B takes place via a transverse channel 41 C or via pressure channels 17 in the end walls 13 , 14 and in the housing cover 15 from the pump 18 . Overpressure relaxation can, for. B. take place in the interior of the transmission housing 1 outlet openings 41 D and contribute to the further lubrication of the gears and bearings. This design allows the valve assembly separate from the gearbox assembly and easy accessibility from above, so that gearboxes of this type can be put together closely with other units. In the same FIG. 4, the incorporation of the bearing, the drive shaft 8 shown 12 for the fixed gear 19 and with a eingeflanschten in the housing end face 13 of its own bearing housing 19 B and the pump 18 in the face 14. The bearing housing 19 A is part of the upper side cover 46 A. The pump 18 can be provided with an outwardly open shaft extension 18 B for the attachment of a further power take-off. The various oil channels 17 , 41 A, 41 C etc. can be easily inspected and cleaned if necessary thanks to the cleaning spigot not shown and thanks to the sandwich construction.

In Fig. 5, the housing cover 15 with the multiple valve plate 41 is shown in plan view. The connections for the high-pressure hoses 43 go down from the pump-side end face 14 to the rotary unions 44 . To the left of the multiple valve plate 41 are the solenoid coils 41 E for driving the invisible integrated valve slide. The possibility of completely removing only a few connections from the entire housing cover 15 after the solution has been made easier to inspect by barely hindered access to the double clutches 2 , 3 , 4 and the further built-in parts in the transmission housing 1 . The double clutches 2 , 3 , 4 and associated gear wheels 19 . . . 28 can be removed from the housing 1 upwards because they are mounted on core shafts, which can be pulled out on a housing side 13 by rotary unions 44 designed as shaft flanges with relatively small diameters, so that the hollow shafts carrying the couplings 2 , 3 , 4 are radial get free.

This can be seen in more detail from FIG. 6, in which the arrangement and configuration of the double clutches 3 and 4 on the shafts 6 and 7 is shown in cross section as a constructively illustrated section of FIG. 1. On the shafts 6 and 7 are here twin clutches 3 and 4 with their associated gears 21, 23 and 25, 26, delayed 27 so that the shafts 6 and 7 also easily switched from the drive-side end face 13 forth at an installation or are easy to pull out during disassembly. For this purpose, the openings in the walls do not also have to have the diameter of the double clutches 2 , 3 , 4 . The double clutches 3 , 4 etc. have axially between their two disk packs 62 one radial web 60 , which is rotationally fixed on the respective shaft 6 , 7 and on the circumference, and one external toothing 64 which meshes with the associated radial web 60 . In the end faces of the radial webs 60 , annular pistons 61 are guided which, when pressure is supplied via the oil channels 45 in the shafts 3 , 4 , etc., compress the respective disk set 62 against the restoring force of springs 63 surrounding them. The outer plates rotate with the radial web 60 , the inner plates rotate with a respectively assigned gear 21 , 23 or 25 , 27 and are held in the open position by the springs 63 surrounding them in a depressurized state. The arrangement for coupling 2 is practically the same as for couplings 3 and 4 . In the shafts 3 , 4 , etc., radial bores leading to the channels 45 are provided in the radial webs 60 in order to open there in front of the annular piston 61 . Further radial bores, but of smaller diameter, are guided in the shafts 3 , 4 , etc. to the various bearings 12 , etc. as lubrication channels.

From FIGS. 7 and 8 it can be seen the configuration of the oil supply chamber 31 with the bearings 12 of the output shaft 10 and the main filter 32 and to the lower part of the suction channel 16 in the pump-side end wall 14. The output shaft 10 ends outside the end walls 13 , 14 and the cover 46 with the output connections 29 and 30, respectively, and is driven by its fixed gear 28 , which is arranged just inside the end wall 13 on the output side above a partition 40 which horizontally above the housing 1 of the main filter 32 divided. The return oil originating from the couplings and bearings runs down through an area in the image behind the filter 32 or the partition 40 arranged above it, from where it flows via an inlet channel 34 A installed in the pump cover 46 on the pump side in front of the front inlet opening 34 of Main filter 32 flows. The cylindrical main filter 32 is sealed on the end face opposite the inlet 34 by a tight sealing disk 35 which is fastened on a rod 37 which penetrates the filter basket 36 axially. This is mounted on an externally removable, drive-side cleaning flange cover 38 in the gearbox housing wall and ends with its free end outside the filter basket 36 in front of its opposite end face, which has the inlet opening 34 with a valve cone 33 covering its cross section. A spreading spring 38 A between the flange cover 38 and the closure disk 35 presses the closure disk 35 and the filter basket 36 against the edge of an opening in the vertical intermediate wall 40 A through the inlet opening 34 of the filter basket 36 with the valve cone 33 lying on the inlet side when the cleaning flange cover 38 is closed protrudes. Said opening 40 A and the valve cone 33 in turn are now in turn sealed by an axially movable closure plate 39 , which bears tightly against the latter and is biased by a further spring 39 A and is guided in the side cover 46 A as soon as the flange cover 38 is removed and the filter basket 36 is expanded because the central stop of the closure plate 39 is replaced with the rear of the valve cone 33 by a stop of its outer sealing edge against the vertical partition 40 A around the inlet 34 of the filter basket 36 . So that any further oil flow to the filter 36 is blocked until it is brought back into its operating position by means of the flange cover 38 and the rod 37 and in turn is sealed again. The cleaned oil flows out of the filter basket 36 along the entire filter circumference in the direction of a gap surrounding it and in the direction of the suction opening 16 A into the suction channel 16 to the pump 18 .

Reference numerals

1 gearbox
2 double clutch on 5
3 double clutch on 6
4 double clutch on 7
5 shaft with 2
6 shaft with 3
7 shaft with 4
8 drive shaft
8 A hollow shaft by 8
9 intermediate shaft of 3 and 4
10 output shaft
11 -
12 bearings of 2, 3, 4 8 A.
13 Front face of the drive
14 Housing end face on the pump side
15 housing cover
15 A edge of 15
16 oil channel in 14 to 18
16 A inlet channel
16 B flange cover
17 oil channel in 14 of 18
18 pressure oil pump
18 A intermediate container
18 B shaft extension from 18
19 fixed gear on 8 to 20/21
19 A -
19 B bearing housing for 12/19
20 idler gear on 5 drive side
21 idler gear on 6 drive side
22 reverse gear on 9
23 idler gear on 7 drive side
24 idler gear on 5 pump side
25 idler gear on 6 pump side
26 idler gear on 6 pump side of 25
27 idler gear on 7 pump side
28 fixed gear on 10 drive side
29 output connection of 10 on the drive side
30 output connection of 10 on the pump side
31 Oil storage room
32 main filter
32 A filter housing
33 valve cone
34 front inlet and inlet opening of 32
34 A inlet channel to 32
35 lock washer from 32
36 filter basket
37 valve rod
38 flange cover
38 A spreading spring between 38 and 35
39 closing plate for 31
39 A spreading spring between 39 and 46 A.
40 partition in 1 , above 31
40 A vertical partition in 31
41 Multiple valve plate
41 A control channels in 15
41 B valves
41 C cross channel under 41
41 D outlet opening
41 E electromagnetic coils
42 -
43 High pressure hose or pipeline
44 rotating union for 2, 3, 4
45 oil channels in the waves
46 side covers from 31
46 A side cover from 13
47 flange lock
48 power take-off from 8
49 fixed gear for 48 on 8
50 idler gear
51 thru axle
52 bearings for 50
53 Additional housing
54 PTO shaft
55 PTO fixed gear
56 power take-off bearings
57 connection flanges
58 pumps on 48
59 PTO oil duct
60 radial web of 2, 3, 4
61 ring pistons in 60
62 plate packs
63 springs
64 external teeth of 60
65 -

Claims (9)

1. Multi-shaft gear

• - With a pressure pump ( 18 ) permanently driven directly by a drive shaft ( 8 ) arranged in the upper area for the pressure medium actuation of multi-plate clutches ( 2 , 3 , 4 ) and the lubrication and cooling of gears ( 20 ... 28 ) and bearings ( 12 ) Etc.,
• a suction line ( 16 ) from an oil reservoir ( 31 ) and pressure distribution channels ( 17 , 43 , 44 ) and control valves ( 41 ) are provided,

characterized,

• - That at the upper end of the suction line ( 16 ) in the output-side housing wall ( 14 ) an oil intermediate tank ( 18 A) is provided in the level area of the pressure pump ( 18 ), the emptying of which is prevented during breaks and
• - That at the lower end of the suction line ( 16 ) in the oil reservoir ( 31 ) immersed filter basket ( 36 ) is provided.

2. Transmission according to claim 1, characterized in

• - That the intermediate container ( 18 A) with its apex up to about the center of the axis of the pump ( 18 ) and falling there to a line bend within the output-side housing wall ( 14 ),
• - Which is kept open both from the oil reservoir ( 31 ) and the pump ( 18 ).

3. A transmission according to claim 1, characterized in that the pump ( 18 ) has a gear or rotary piston rotor plugged onto the end of the drive shaft ( 8 ) projecting from its bearing ( 12 ) and a jointly preassembled structural unit with the bearing ( 12 ), the pump rotor being removable in the axial direction from the shaft end without dismantling the bearing ( 12 ), to which a further shaft ( 18 A) can be connected for additional power take-offs. 4. Transmission according to claim 1, characterized in

• - That the control valve (s) ( 41 B) on the pressure side of the pump ( 18 ) are installed in an upper housing cover ( 15 ) at least partially covering multiple valve plate ( 41 ),
• - And that lead from the multiple valve plate ( 41 ) outside the pump-side housing wall ( 14 ) to shaft bores ( 45 ) and associated rotary connections ( 44 ) pressure hoses ( 43 ) or pipes.

5. Transmission according to claim 1, characterized in that the couplings ( 2 , 3 , 4 ) equipped shafts ( 5 , 6 , 7 ) are designed as core shafts in hollow shafts or inner disk carriers and without the latter outwards from the housing of the transmission ( 1 ) and can also be pulled out horizontally from hollow shafts or disk packs ( 62 ), the hollow shafts or disk packs ( 62 ) being short enough to be inserted vertically into the gearbox housing ( 1 ) through an upper housing cover combined with the multiple valve plate ( 41 ) ( 15 ) together with completely assembled couplings ( 2 , 3 , 4 ) or remove from them as long as the core shafts are not installed. 6. Transmission according to claim 1, characterized in

• - That the multiple valve plate ( 41 ) as a cover flange ( 15 ) of the in the housing walls ( 13 , 14 ) integrated connecting lines ( 16 , 17 ) and the control valves ( 41 B) is sandwiched with at least one cover plate, an intermediate plate and a bottom,
• - In which plates control channels ( 41 A) and recesses with control edges etc. are directly molded,
• - Control the pressures of the immediately adjacent pressure hoses ( 43 ) or oil channels ( 45 ) or in the interior of the gearbox on lubrication points ( 12 ) via the movable valve body.

7. Transmission according to claim 1, characterized in that the immersed in the oil reservoir ( 31 ) main filter ( 32 ) is designed in the form of an inlet and outlet side detachably closed tube with a filter basket ( 36 ) resting against its inlet side, in which both inlet opening (34 a) and a filter basket (36) enclosing the filter housing (32 a) with a closable in a removal of the filter basket (36), valve cone (33) and a this automatically nachrutschenden closure plate (39) on the inlet side lockable. 8. Transmission according to claim 1, characterized in

• - That the housing cover ( 15 ) and multiple valve plate ( 41 ) together cover a narrower area than the housing plan, the housing cover ( 15 ) only being approximately flush with one of the longitudinal edges of the housing upper part and
• - That an inclined surface is provided on the other longitudinal edge, which can be provided with mounting openings and an additional cover flange ( 15 A) for decentralized power take-offs ( 45 ) from the drive shaft ( 8 ).