DE2407925A1 - COMMERCIAL VEHICLES, IN PARTICULAR TRUCKS - Google Patents

Description

Patent attorney

Dipl.-Ing. Waiter Jackish

7 Stuttgart N, Menzetstrasse 40

Feb 20, 1974

2A07925

G. YAN DER IELY Ή. V., Weverskade 10, Maasland, Holland. "Commercial vehicle, especially tractor."

The invention "relates to a commercial vehicle, in particular a tractor with drivable wheels and connections for pulled Working tools, e.g. a plow and / or drivable working tools e.g. a harvesting machine, the drive of which has a Engine, at least one device for changing the gear ratio, in particular has a torque converter and at least one power take-off shaft for driving the work tools,

The aim of the invention is to ensure that there is always sufficient power or sufficient torque at the PTO is available, the drivable wheels output power or the torque transmitted to them should be restricted if necessary.

According to the invention, the engine has maximum power (Torque) which is greater than that which the '■ device for changing the transmission ratio transmit can, while the PTO to transmit the maximum engine

S09826 / 0247

power (torque) is suitable.

In this way there is always sufficient performance or a sufficient torque on the PTO ^.) available. The device for changing the transmission ratio can be used to move the work tools on the wheels sufficient power can be transmitted. The device for changing the transmission ratio can, however, be smaller and be designed more cheaply than if they had to be suitable for transferring the full engine power.

The invention is explained in more detail on the basis of the following figures explained. Show it:

1 shows a side view of a tractor in a position suitable for driving forward,

2 shows a side view of the tractor in a position suitable for reversing,

3 shows a side view, partially in section, of part of a housing of an injection pump and one attached to it Adjusting device,

4- a section and partially a view of an adjustable injection pump,

5 schematically shows a drive for the tractor wheels and the PTO shaft in a first embodiment, FIG. 6 a section through a regulating disk,

7 shows a section through an adjustable stop to limit the power or the torque of the motor in a first position,

8 shows a section through the adjustable stop according to FIG. 7 ija a second position,

9 schematically shows a drive for the tractor wheels and the PTO in a second embodiment,

The tractor is driven by two steerable, non-driven front wheels 1 and two non-steerable, mechanically driven Rear wheels 2 supported. The tractor is provided with a diesel engine 3, the front of which is approximately in the same vertical plane as the axes of rotation of the front wheels 1. The power of the diesel engine is about 150 hp. on On the back of the diesel engine 3 there is a clutch housing 4-, which contains the flywheel mounted on the output shaft of the engine 3

60§826 / 02A7

rad. On the rear with respect to the direction of travel A Side of the housing 4, a gear housing 5 is attached, which the Gears for driving the rear wheels 2 and the PTO shafts still to be specified. A hydraulic pump is in one housed behind the gear housing 5 arranged housing 6, together with a hydraulic motor driven by this pump and the associated hydraulic connections and controls, or regulatory bodies. The housing 6 thus contains a variable transmission ratio for the fluid Drive the rear wheels 2 and can still have a second gear with variable transmission ratio for the drive of PTO included. Behind the rear of the gear housing 6 is a gear housing 7 in which the gears for the drive of the PTO shafts 8 protruding from the rear of the tractor are mounted. One of the PTO shafts 8 can with a Standard speed of 540 revolutions per minute can be driven and another neighboring PTO shaft can be driven by this gear ratio at a higher speed, e.g. with twice the speed Speed can be driven. Behind the gearbox 7 is Finally, the housing 9 of the axle drive is attached, in which the axes of rotation of the rear wheels 2 are mounted and one in the Drive of the rear wheels 2 Hegende gear ratio and a differential gear records. Of the gear housing 5, the drive arranged under the motor 3 is at least one on the front side of the tractor arranged PTO shaft 10 guided forward.

There is a three-point lifting device on the rear of the tractor provided that consists of two lower links. 11 and an upper link 12, the length of which is adjustable. On the A two-point lifting device is attached to the front of the tractor, which comprises two lifting arms 13, which around an articulated axis are pivotable, which almost coincides with the axis of rotation of the front wheels 1 in side view.

The axes of rotation of the front wheels 1 are directly rotatable and pivotable relative to the block of the engine 3 while the rear wheels 3 are mounted directly in the axle housing 9. The housing of the diesel engine, the flywheel housing 4, as well as the Gear housing 5 »6, 7 and 9 are flanged together and

S0982S / 0247

e.g. combined by bolts to form a rigid unit, which is in essentially forms the frame of the tractor.

In relation to the direction of travel A, the tractor is provided near the rear with a driver's cab 14, the front of which is in The rear of the diesel engine compartment. In the driver's cab 14, a driver's seat 15 is provided and there are des The steering and actuation elements, such as the steering wheel, brake pedal, accelerator pedal, instruments and switch devices are also housed. The steering wheel and instruments are attached to an upright column 16, while the driver's seat 15 is on the other side Support 17 is attached. The lower sides of the column 16 and the support 17 are connected by a substantially V-shaped connecting part 18 rigidly connected to one another, in which several operating pedals are mounted. The underside of the connecting part 18 is mounted so as to be pivotable about a vertical axis 19 together with the steering wheel, the driver's seat 15, the operating pedals, etc. To the A support device, not shown, is provided for mounting the axle 19 and is arranged on the upper side of the axle drive housing 9 is. The driver's seat and the steering and actuating elements are common with respect to the tractor frame around the hinge axis 19 can be pivoted over an angle of 180 ° and can be fixed in two positions in such a way that in these positions a horizontal Connection line between the center of the driver's seat and the center of the steering wheel's axis of rotation, approximately parallel to the direction of travel A or B runs, (Fig. 1 or 2). The is in the position for driving the tractor forward (direction A) The driver's seat is located above the axle drive housing 9 and in the other position for reversing (direction of travel B, Fig. 2) the driver's seat is above the gearbox housing 6.

All movements of the steering device and the actuators are transmitted hydraulically. For this purpose they are the ' Hydraulic lines transmitting signals on the underside of the connecting part 18 are grouped around the axis 19 in such a way that that they can follow the swiveling over 180 ° by means of VerformMg.

For a better understanding of the following description, the construction known per se is based on FIGS. 3 and 4

509828/0247

-5- '2407929

to control the fuel injection system and thus the power control of the diesel engine 3 briefly discussed here.

Fig. 3 shows schematically the drive for the piston Injection pump and its regulation. The pump housing is labeled 20 ". A camshaft 21 is mounted in this housing, one of the number of pump pistons, and thus also the engine cylinder corresponding Anaahi of cam 22 has. Each of the Cam 22 is mounted via a holder 23 in a fork-like manner Sensing roller 24- scanned, due to the eccentric arrangement of the relevant cam 22 with respect to the center line the camshaft 21 of the holder 23 is movable up and down. On the top of the holder 23 is one of the cylindrical Pump piston 25 axially immovable, but around its center line rotatably arranged The piston 25 is in the axial direction guided by a piston housing 26, which with respect to the pump housing 20 is fixedly arranged (Fig. 3 and 4 ·). The cylindrical piston housing 26, the bore of which is matched to the piston 25 is, is provided on the top with two bores 27 for the supply and / or discharge of fuel. The bore of the Piston housing 26 ends freely in a boundary surface of the piston housing both on the examination and on the upper side, which runs perpendicular to the center line of the same. The lower part of the piston housing 26 is of a substantially cylindrical Control bushing 28, which is designed as a gear 29 over part of its height due to the toothing of its circumferential surface. the Wall of the control sleeve 28 is provided near the bottom with an axially extending slot 30, the lower End continues into the end face of the control sleeve 28. The slot 30 is always below the lower boundary surface of the Piston housing 26. A cam 31 is attached to the piston 25, which can be displaced in the slot 30 of the regulating sleeve 28 in the axial direction is.

The gear wheel 29, which forms the upper end of the control sleeve 28, is in engagement with the toothed path of a control rod 32. the Control rod 32 extends in the longitudinal direction perpendicular to the coinciding center lines of the piston 25, the piston housing 26 and the control sleeve 28, the toothed path of the control rod 32 is in

£ 09826/0247

Engagement with all gears 29, which are arranged side by side Piston 25 belonging to the pump. In the upper surface of the piston 25 there is an axial bore 33 which is connected to a radial bore 34- level with the lower end of bore 33 in is open connection, which opens into a slot 35, which is a recess in the cylindrical outer surface of the piston 25 is provided and runs helically over this outer surface. The recess extends in an axial view of the slitter 35, for example, over a circumferential angle of about 30 to 4-5 °. One end of the slot is thus in side view 35 higher than the other end.

If the diesel engine 3 is operating, the pistons 25 are activated by means of the cam 22 of the camshaft 21 out of phase up and down emotional. During this upward and downward movement of the piston 25, the squat 31 moves in the slot 30 of the conical bushing 28. In their lowest position, the pistons 25 are each with their upper end face below the bore 27, so that the Space above the piston, which is partially surrounded by the piston housing 26, can be filled with fuel that flows through one of the bores 27 flows in. The other bore 27 is with the fuel tank in connection. If the piston 25 moves upwards, from the moment the upper surface of the Piston 25 closes the openings 27, the fuel in the direction of the arrow G (Fig. 4-) promoted.

The injection nozzle closes on the upper side of the piston housing 26 36 (Fig. 3). The one in the space above the piston 25 The fuel pressure built up depends on the properties of the injector 36. The pressure build-up is complete when the Slot 35 communicates with the bore 27, which is connected to the fuel tank. From that moment on the fuel located above the piston 25 via the bore 33, the radial bore 34, the slot 35 and the im Piston housing 26 provided bore 27 flow back to the fuel tank. Since the slot 35 is axially helical Extends over part of the circumference of the piston 35, the depends Position of the piston 25 in which the path to the fuel tank is released via the bore 27, from the position of the piston in

509026/0247

With respect to this bore 27, the piston 25 is e.g. If the angle is rotated in the direction of the arrow D, the slot comes out during the upward and downward movement of the piston 25 35 earlier with the one connected to the fuel tank Bore 27 to overlap, as a result of which the delivery pressure is reduced at an earlier point in time than that shown in FIG Location. By rotating in or against the direction D, the amount of fuel in the corresponding cylinder of the diesel engine 3 each injected fuel controlled per work cycle will. A rotation of the piston 25 in or against the direction D takes place by longitudinal displacement of the control rod 32. Since the Tooth track of the control rod 32 with the gears 29 of all pistons of the If the injection pump is engaged, the injection quantity is controlled in the same way for all cylinders. By longitudinal displacement of the control rod 32 are the gears 29 and thus the control bushings 28 with respect to the fixedly arranged piston housing 26 twisted. Here, the slot 30 is accordingly in its Changed position, what a Yerdeehung of the piston via the cam 31 25 has the same angle result, whereby a different circumferential point of the slot 35 as the first in the new position the bore 27 communicates, and result in correspondingly changed injection quantities.

As is known, a diesel engine is generally controlled by a centrifugal governor in such a way that the Engine speed remains constant. If the load on the diesel engine increases, the speed initially decreases and it becomes the control rod 32 is adjusted by the centrifugal governor in such a way that that more fuel is injected per work cycle. This increases the torque until. the set nominal speed is reached again. Since this control always takes place at an approximately constant speed, this means an increase in the torque also a proportional increase in engine power. Furthermore, the driver can also adjust the position of the control rod 32 and thus the amount of fuel injected per work cycle that is delivered Torque, and affect engine performance. The maximum injection quantity, the maximum torque and the maximum Motor power is determined by a specified end position for the control

B09826 / 0247

rod 32 "limited, this limitation is in the form of execution according to / Fig. 3 and 4 on the right-hand side and at the right-hand end of the control rod 32. via a stop against which in this case the right end of the control rod 32 pushes. The determined thereby The extreme position of the control rod 32 corresponds to the position of the Korbens 25, in which a Γ \ rnkt near the bottom of the slot 35 Eit of the hole 27 connected to the fuel tank contacts. The one mentioned, not shown in FIGS. 3 ″ and 4 Stop next to the right end of the control rod is set and sealed in the known embodiments of diesel engines by the manufacturer.

In the embodiment shown schematically in FIG is available at the output shaft 37 <ies diesel engine 3 standing power through a gear transmission 38 on the one hand to Drive the PTO shaft 8 on a (stationary) pump 39 imd on the other hand, transmitted to a pump 40 to drive the rear wheels 2. The pump 39 intended to drive the power take-off shaft 8 is at a standstill through a high pressure line 41 and a bodice pressure line 42 with a motor 43 in connection, the output shaft mechanically directly with the PTO shaft 8 and with the eventual, by a Gear ratio is coupled to this connected auxiliary power take-offs. The unit consisting of the pump 39 and the motor 43 forms a hydrostatic torque converter, and thus a continuously variable one in its transmission ratio Fluid transmission.

The z. Bi- adjustable by means of an adjustable control mirror disc, Pump 40 for driving the rear wheels 2 is connected through a high pressure line 44 and through a low pressure line 45 a likewise adjustable motor 46, the output shaft of which is mechanically connected to the rear wheels via the rear axle drive is coupled. A signal line 47 is connected to the high pressure side of the motor 43, from the motor 43 to a control slide 48 leads. A signal line 49 is branched off from the high-pressure line 44 running between the pump 40 and the motor, which is also connected to the control slide 48. A signal line 50 also closes at the control slide 48 on whose end facing away from the control slide 48 to the housing

509826/0247

-9- 24Q7925

51 of an adjustable stop is connected. The adjustable one Stop is attached to that end face of the pump housing which corresponds to the end face, in the direction of the the control rod 32 is adjusted to increase the injection quantity.

The control slide 48 shown in Fig. 6 has a housing which has essentially two cylindrical parts 52 and 53, whose diameter can have different values. Between the two parts 52 and 53 of the housing of the slide 48 is an intermediate wall 54 arranged perpendicular to the congruent Center lines 55 of parts 52 and 53 stand. Hollow bushings 56 and 57 are rigidly attached on both sides of the partition 54, which run coaxially to the common center line 55. At the ends of the sockets 56 and 57 remote from the intermediate wall 54 are Shoulders 58 and 59 attached on both sides of the Intermediate wall 54 spring plates 6.0 and 61 are provided, which are shown in FIG Have top view ring shape, and the central openings Enclose sockets 56 and 57. Against those facing each other Inner sides of the shoulders 58 and 59 are spring + washers 62 and supported, which are formed analogously in the spring plates 60 and 61 and these are each opposite in a mirror image (Fig. 6). Between the spring plates 60 and 62 or 61 and 63 are compression springs 64 and 65 are provided. In the bores of sockets 56 and 57 » whose center lines run in alignment, a rod 66 displaceable in the axial direction is guided, one in the Intermediate wall 54 provided bore penetrated. The connection of the sockets 56 and 57 with the intermediate wall 54 and the fit of the Rod 66 in these sockets is such that there is no short circuit between housing parts 52 and 54. That in part 53 lying end of the rod 66 is fixedly attached to a piston 67 which sealingly rests against the inner surface of the part 53 and axially is movable. On the end wall 68 of the part 53 facing side of the piston 67, a guide 69 is provided which has a bore, the center line of which runs parallel to the center line 55. In the end wall 68 of the part 53 is a rod attached, whose center line runs parallel to the center line 55 of the control slide 48. The remote from the end wall 68

S09826 / 0247

The end of the rod 70 lies in a bore in the guide 69. There is a relatively large amount of play between the rod 70 and the bore of the guide 69. In place of the Guide 69 is a chamber 71 in the bottom of the bulb 67 a cylindrical bore is provided, the center line of which coincides with the center line of the bore in the guide 69. Of the The diameter of the chamber 71 is larger than that of the bore in the Guided Tour 69

The end face of the guide 69 facing the end wall 68 of the piston 67 forms a stop for a flap 72, which is in the Chamber 71 is arranged. The flap 72 is of a relatively strong compression spring 73 pressed in the direction of the stop formed by the guide 69. Furthermore, in the ground is the Chamber 71 as a connection to that between the piston 67 and the Intermediate wall 54- a hole 74- is provided. on the face of the piston 67 faces the side of the intermediate wall 54- an annular support surface 67A against which the spring plate 63 rests. In the jacket of the piston 67 is also a radial one Bore 75 is provided, which in the position shown from the space between the piston 67 and the wall 54- to the inner wall of the part 53 leads and is covered by this. In a position of the piston 67 that is closer to the intermediate wall 54, the bore opens a recess 76 in the inner wall of the part 53, which through a bore 77 communicates with a leakage line 78, which opens into the storage container.

In part 52 of the control slide 48 is between End wall 80 and the spring plate 60, a piston 79 is arranged displaceably. The end face of the partition facing the intermediate wall 54- The piston 79 has a cylindrical recess 81 lying coaxially to the center line 55. The partition wall is in operation 54 · facing end face of the piston 79 on the corresponding side of the spring plate 62. The rod 66 that is capable of after Fig. 6 protrudes beyond the shoulder 58 into the recess 81 of the piston 79 is dimensioned in its length so that at Beginning of opening of the piston side through the piston face 82 limited pressure space 85 against the signal line 50, the corresponding end of the rod 66 garada against the end wall of the Aus * ·

509826/0247

The outside surface of the piston 79 is in the outer surface of the piston an annular recess 84- is provided which is so wide that in all possible positions of the piston 79 connection to a bore 85 provided in the wall of the part 52, to which one the reservoir opening leakage line 86 is connected. In contrast to the space between the piston 67 and the partition 54 is the space between the piston 79 and the partition 54 not filled with liquid.

The signal line 50 is with the housing 51 of the adjustable Stop in connection, which in Figs. 7 and 8 in two different positions is shown. The housing 51 cLes adjustable Stop has a connector 87> that with his Flange 88 is fastened via bolts 89 to that end face of pump housing 20 in the direction towards which control rod 32 is shifted to increase the injection quantity. The connector 87 has a bore 90 into which the cylindrical end of the Control rod 32 protrudes, even if it is the smallest possible injection quantity assumes the corresponding position. From the other side, a rod 91 projects closely into the bore 90 into it, whose end 92 facing the pump housing 20 has a stop forms for the control rod 32 when the latter in the sense of a Increasing the injection quantity is shifted. In the cylindrical Ventilation holes 93 are provided on the wall of the connection piece 87, in order to move the control rod 32 and rod 91 against each other to prevent pressure build-up. At the end of the rod 91 remote from the pump housing 20 is a circular disk trained support disc 94 firmly attached, perpendicular to their A plate-shaped extension 95 on the side facing away from the rod 91 is provided, in its lying between its plate surfaces, perpendicular plane of symmetry with center lines of bore 90 and Bar 91 fall. The extension 95 has a triangular shape in the side view of FIGS. 7 and 8, the rounded vertex of the triangle facing away from the support or circular disk 94. In the in Fig. 7, the apex of the approach 95 is located on a position shown Wall of the housing 51, so that the rod 91 is its maximum Injection quantity assumes an ordered extreme position. An elongated hole 96 is located along the lower side of the triangular extension 95 in FIG. 7

509826/0247

provided, the lower end of which near the support disc 94 and the upper end of which lies obliquely above the lower end and at a greater distance from the circular disk 94. In slot 96 a hollow 97 can be moved around a piston 98 that is perpendicular to the plane of symmetry of the attachment 95 and is on the upper side attached axis is rotatable. The piston 98 is in the vertical direction of displacement guided in a cylindrical housing 99 which forms part of the stop housing 51, the center line of the housing part 99 perpendicularly intersects the center line of the bore 90 o The center line of the elongated hole 96 closes both with the center line of the bore 90 and with the center line of the cylindrical housing part 99 an angle of 4-5 °. To the housing part 99 closes at the bottom to a cylindrical space 100, of the stop housing 51 at »whose center line is the housing part 99 intersects perpendicularly and runs parallel to the center line of the bore 90. On the underside of the piston 98 is a Tension spring 101 attached, the other end of which is held on the lower end face of the stop housing 51.

In the cylindrical space 100, a piston 102 is arranged, which has a part 103 and corresponding to the diameter of the space 100 has a part 104- which is offset in diameter from the opposite. The part 104- is guided in a bore 105, the center line of which coincides with that of the space 100. On her from the pump housing 20 at the end facing away from the bore 105 is closed by an end wall 106. Between the and the facing end of the Piston part 104- a compression spring 107 is arranged. Near the end wall 106 opens into the. Bore 105 a bore 108, the

the
is connected to the signal line 50 via a branch line 109 /. In part 103 of piston 102 there is provided a bore HO which has an axial section and an adjoining radial section. In the cylindrical space 100 there is a corresponding one. A stop ring which is held in the circumferential groove and which limits the displacement path of the piston 102 in the direction of the pump housing 20 is provided. If the piston 102 is in contact with the stop ring 111 (FIG. 7), the radial section of the

509826/0247

Bore 110 with one provided in the wall of the space 100 Bore 112 connected to the reservoir via a leakage line 113 is in connection. The space receiving the circular disk 94- is vented via a bore 114A formed in its the pump housing 20 facing end wall is provided. The spaces accommodating the tension spring 101 and the compression spring 107 are also in operation Liquid filled.

The constructions of FIGS. 3 to 9 are related to their underlying functions are explained below.

In the case of a tractor according to FIGS. 1 and 2, the working tools to be driven and connected to it should be the power take-off shafts 8 and / or 10 can be driven. The drive required for this is designed in such a way that the requirement for the drive of the power take-off shaft or power take-off shafts always have a larger part of the engine power available than for the wheel drive. Of the So the tractor is primarily used to drive the work tools and only secondly to move them. With others Words, in principle, the role is used to drive the work tools The power of the tractor's diesel engine is available, while the portion of power made available as wheel drive power is intentionally limited to a certain part of the total available engine power. By the invention The design should be used when the power supplied to the drivable wheels accounts for a certain proportion of the total power seeks to exceed and thereby the power available to the PTO shafts could drop below a certain value Wheel drive power can be limited in favor of the PTO drive power, so that the PTO always has a certain share the total service is available.

For example, it can be attached to the front or rear of the tractor and driven by PTO shafts: a mower and a hay-making machine, a hay-making machine for swathing and a pick-up wagon for the crop, a beet topper and a beet harvester, a chopper and a collection truck for the chopped material. It is beneficial for those who are powered Machines that require a very good overview make them to be attached to the rear of the tractor and when attaching the

. S09826 / 0247

each other driven machine on the front of the Tractor to drive this backwards with the driver's seat rotated over 180 ° in relation to the forward drive (direction of travel B, Fig. 2). This applies, for example, when a weeding device is attached to the tractor is.

If, for example, a cultivator is attached to one side of the tractor and a rotary harrow is attached to the other, the The power required to move the cultivator must be so great that the remaining power required to drive the rotary harrow via the PTO shaft available power is too low at a certain depth setting of this harrow. In this case it should the wheel drive power can be limited (lower driving speed), that there is sufficient power available on the PTO to operate the rotary harrow.

In the following functional description, a numerical example is used, in which it is assumed that the maximum power of the diesel engine 3 on the output shaft is 150 hp and that the wheel drive power, in this case the power transmitted to the rear wheels, is limited to a maximum of 90 hp » the power developed by the diesel engine $ arises always with a certain, by eg _o a centrifugal governor set speed (eg 2000 revolutions / minute) _o the power developed at this speed can be influenced by .Ändern the injection quantity, which is also a corresponding change in torque has the consequence. The developed power is delivered to the output shaft 37 of the diesel engine 3 (see the schematic overview of FIG. 5) and via the gear ratio 38 on the one hand to the hydrostatic transmission formed by the pump 39 and motor 4-3, i.e. to the power take-off shaft (s) 8 and on the other hand to the hydrostatic transmission formed by pump 40 and motor 46 and thus to the driven wheels. The pump 39 and the motor 43 cannot be adjusted in this example, so that the power take-off shaft 8 is driven at a constant speed. The pump 39 feeds the liquid under high pressure through the line 41 to the motor 43, from where it flows back via the reveal 42 'under low pressure. Since at a constant speed of the diesel engine 3, the pump 39 with constant

509828/0247

Speed is driven, the motor 43 also rotates at a constant Speed and it is therefore the pressure of the piston of the motor 43 acting on the fluid on the power take-off shaft occurring torque is decisive. This also applies to the power that is taken from the power take-off shaft or the power take-off shafts 8 can. Since the signal line 47 to the high pressure side of the engine is connected and, as stated, the pressure prevailing there is decisive for torque and power, can be via the pressure in the signal line for torque and power at the PTO shaft (s) 8 can be inferred.

Pump 40 and motor 46 of the hydrostatic transmission located in the wheel drive are adjustable in this embodiment, and it can thus be used to control the driving speed of the tractor. The pump is e.g. Adjustment of a swash plate which controls the delivery rate of the pump. When the delivery rate of the pump 40 changes The speed of the motor 46 and thus also the drive speed of the wheels 2. However, the pump 40 is at a constant speed driven, so that the pressure in the high pressure line 44 between the pump 40 and the motor 46 is also decisive for the Torque and for the power transmitted to the rear wheels 2. The signal line 49 connected to the high pressure line 44 contains thus liquid, the pressure of which is decisive for the wheel performance. Both the fluid pressure in the line 47, which is decisive for the power take-off shaft output, and the fluid pressure in the line 49, which is decisive for the wheel power, are transferred to a control slide 48 Das in the control slide 48 arriving signal in the form of a signal in line 50 occurring fluid pressure is fed to the housing 51 of the adjustable stop, which is to be described below Way can affect the engine performance.

The starting point for the construction of the control slide 48 (Fig. 6) is (drawn on the above numerical example): If the power transmitted by the power take-off shaft (s) 8 and / or 10 to the coupled work tools is greater than the difference between the maximum power of the motor and the maximum power to be supplied to the wheel axles (i.e. greater than I50 - 90

509826/0247

= 60 HP), then the power of the diesel engine is not necessary 3 to "because in this case the transfer to the wheels Power can never be greater than 90 hp. It is Thus, the drive power for the wheels is automatically limited by the maximum power of the diesel engine 3. is the power consumed by the PTO (s) is less than the difference between the maximum power of the diesel engine and the maximum power to be transmitted to the wheels, a limitation of the power to be supplied to the wheels is necessary because without this limitation the maximum power of the motor 3 the maximum power to be supplied to the wheels (90 hp) is exceeded would make possible.

The compression spring (65) of the control slide 48 has a certain preload. This preload as well as the diameter of the piston 67 are dimensioned in such a way that when removed from the PTO shaft (s) Power (according to the numerical example) of 150 - 90 = 60 HP or more, the pressure in the signal line 47 or in the space above the piston 67, which is for the power or the torque What is decisive is a force on the piston 67 which corresponds to the preload of the compression spring 65 or is greater. the force exerted on the piston 67 will thus compress the compression spring 65, which moves in the direction of the intermediate wall 54, whereby the end of the rod 66 remote from the piston 67 rests directly against the end face of the recess 81 in the piston 79. The force exerted on the piston 67, corresponding to the selected diameter of the same, is so great that the rod 66 the Piston 79 moves in the direction of the end wall 80, namely against the oppositely directed force acting on the end face 82 of the piston 79, which is proportional to the pressure in the signal line 49 is. This pressure, which is decisive for the power transmitted to the wheels at this moment, is lower than the pressure corresponding to the pressure in the line 47, that for the relatively large filling capacity at that moment is decisive. In these circumstances, piston 79 will either stay in the position indicated in Fig. 6 or move a little to the left (Fig. 5) or down (Fig. 6), where he is the im Pressure chamber 83 from existing liquid to high pressure line 44

SÖ9826 / 0247

urges. As soon as the piston 67 moves in the direction of the intermediate wall 54 moves, the flap 72 closes under the action of Compression spring 73, since the bias of compression spring 73 is greater as the force acting on the flap as a result of the signal pressure in the line 47, since the liquid passage to the flap given as a result of the game between rod 70 and guide 69 isto If the piston 67 is under these conditions in the direction Moved on the intermediate wall 54, the bore 75 comes with the Recess 76 and thus with the bore 77 and the leakage line 78 in connection. In this way, the liquid present between the piston 67 and the intermediate wall 54 during the movement of the Piston 67 flow off in the direction of this partition. If the piston 67 moves from the position shown in the direction of End wall 68, the rod 70 pushes open the flap 72, so that Liquid can enter the space between the piston 67 and the intermediate wall 54. The hole 75 is then no longer with the annular recess 76 in connection, so that over this the liquid can no longer drain. If the power consumed by the power take-off shafts is greater than 60 hp, you are through the position of the piston 67 and the rod 66 preclude that the piston 79 moves in the direction of the intermediate wall 54, and thus the connection from the line 49, which is under high pressure, to the signal line 50 is released. The piston 79 takes under under these circumstances either the position shown in FIG. 6 or a position in which it is closer to the end wall 80.

If the power consumed by the power take-off shafts is less than 150 - 90 = 60 HP, the power from the high pressure side of the Motor 43 taken signal pressure (signal line 47), which is for the PTO torque occurring at constant speed is decisive, less than the pressure at which the pressure on piston 67 exerted force can overcome the bias of the compression spring 65, The piston 67 takes under these conditions either the position shown in Fig. 6 or a position in which he the Front wall 68 is closer “If, with the last-mentioned, relatively low power taken up by the power take-off shafts, the power required to drive the tractor wheels would increase so that it comes close to 90 hp (with a

'600026/0247

Controlled system of 85 to 90 PS is assumed), the The signal pressure corresponding to the pressure in the high pressure line 44 and also given in the line 49, that of the pump 40 Power is proportional to increase to a value at which the force exerted on the end face 82 of the piston 79 the bias the compression spring 64 overcomes. The piston 79, which presses against the spring plate 62, moves in the direction of the Partition 54. Immediately after this movement begins the end face of the recess 81 against the adjacent end of the rod 66, whereby the piston 79 takes the piston 67 with it. Here the rod 70 opens the flap 72 so that during this movement of the piston 67, liquid can flow from the line 47 into the space between the piston 67 and the partition 54,

The space between the piston 79 and the partition wall 5 ^ is liquid-free. If necessary, the wall of the part 52 can still be provided with a ventilation hole. The annular recess 84 serves to intercept any leakage fluid from the Space 83 and is connected to a storage container via the leakage line 86 tied together.

If, under the aforementioned conditions, the pressure in the signal line 49 and thus also in the pressure chamber 83 becomes so high that the piston 79 moves in the direction of the partition ^ A- , the connection from the pressure chamber 83 to the signal line 50 is released, so that the adjusting piston 98 of the stop is then also exposed to this relatively high pressure.

If the power consumed by the power take-off shafts exceeds a specified limit power, έ.Β. 60 HP according to the numerical example, so there is a displacement of the piston 79 in the direction of the opposing piston 67 prevented by the load on this, the PTO shaft power proportional pressure. Sinks on the other hand, the power consumed by the PTO shafts, to less than 60 HP, if a limit power below the maximum engine power is imminent being exceeded (in the numerical example 90 HP) through the absorbed by the tractor wheels Performance of the piston 79 as a result of the corresponding pressure in the space 83 in the direction of the opposite piston 67 shifted, whereby the corresponding to the wheel drive power

S09S26 / 0247

Pressure via the signal line 50 on the stop becomes effective.

When the wheel drive power has approached the example value of PS so far that after it is input through the piston via line 50, the space under piston 98 is also under the pressure prevailing in line 49, the piston is against the force the spring 101 shifted upwards (Fig. 8). As a result of this piston movement, the circular disk 94 is displaced in the direction of the pump housing 20 via the roller 97 guided in the obliquely running elongated hole 96. During this movement of the circular disk 94- the end face 92 of the rod 91, which forms a stop, moves in the direction of the pump housing 20, the displacement path being limited by the fact that one of the end faces of the circular disk 9 ² I- is in contact with a boundary surface of the surrounding housing which is perpendicular to the center line of the rod 91. As long as the pressure caused by the wheel drive power is maintained in the space below the piston 98, since the wheel drive power tries to exceed a value of 90 hp, the stop 92 remains in the position according to FIG. 8th.

The stop 92 serves as a stop for the control rod of the injection pump of the .Dieselmotor, and it limits its displacement in the direction corresponding to the increase in the injection quantity. The position of the stop92 is in the position in which the Wheel drive position is to be limited, so "specified that when the control rod 32 is in contact with the stop, the injected fuel amount a torque of the diesel engine 3 has the consequence that corresponds to an output of 90 hp at the set speed. If the PTO power consumed is greater than 150 - 90 = PS, the control slide 48 blocks the connection between the lines 49 and 50 and the spring 101 can push the piston into withdraw the position shown in Fig. 7, in which the rounded right end of the projection 95 the adjacent part of the housing touched. The position of the stop 92 corresponding to this position allows the control rod 32 to be displaced in FIG Direction towards a larger injection quantity and thus towards a higher performance, the illustrated position of the stop 92 of the Maximum power of the diesel engine of 150 hp according to the figures

B09826 / 0247

game corresponds. The control rod 32 is thus an adjustable one Assigned stop over which the maximum injection quantity is adjustable and of its two end positions, one of the maximum engine power of the engine and the other of the specified, corresponds to the maximum permitted wheel drive power.

During the movement of the support disc 94 in the direction of the pump housing 20 avoids an air rod in the space partially delimited by it through the ventilation bore 114A. The same purpose is used for the space between the control rod and the rod 9Ί through the bores 93 · For venting the Space above the piston 98, the support disk 94- can also have one have axial bore.

If the signal line 50 is under high signal pressure, a corresponding pressure also acts on the side of the piston 102 facing the stop 111 and via the circulation line 109 on the side of the piston 102 facing the end wall 106. Since the stop side corresponds to the diameter of the piston part 103 Piston surface is considerably larger than the opposite piston surface belonging to part 104, the result is a resulting force acting in the direction of the end wall 106. at the aforementioned high signal pressure under piston 98 is moving the piston 102 so far in the direction of the end wall 106 until it reaches a stop. In this piston position, the cylindrical locks Outer surface of the piston part 103, the bore 112, and thus the leakage line 113 shuts off, and the compression spring 107 is compressed. The said stop is through the conical Transition parts between the piston parts 103 and 104 on the one hand and between the cylindrical space 100 and the bore 105 surrounding walls soaätseite formed. However, if <üe PTO power is relatively large or if the wheel drive power does not reach the value of 90 hp, then there is reason the shut-off by the control slide 48 in the space below the piston 98 is a relatively low pressure. In this case the resulting pressure force on the piston 102 is still directed against the end wall 106, but it is so small that it is overcome by the opposing force of the compression spring 107. The piston 102 is then over the compression spring 107 in the direction of the

§09826 / 0247

Tension spring 101 is displaced until it hits the stop 111. Hun the bore 110 stands with the bore 112 and thus with the Leek line 113 in "connection, so that the liquid under the piston 98 flows back to the storage container and the spring 101 the Piston 98 can pull downwards, with the support disc 94 · "and thus the stop 92 move into the position shown in FIG. 7, which corresponds to the maximum engine power to be developed of 150 hp. If the signal pressure is present under the piston 79, the liquid can flow through the control slide 48 under the piston 98 flows, so that the stop 92 moves into the position shown in FIG. 8, and into the position that is a maximum approved wheel drive power of 90 hp.

In the position in which the bore 110 with the leakage line

113 is in connection, there is a short circuit between the line 49 and this leakage line, and thus an unwanted drainage excluded from hydraulic fluid, since the piston 79 (Fig. 6) blocks the line 50.

In a second embodiment (Fig. 9) the power of the diesel engine 3 is shown schematically via the output shaft 37 and that The illustrated gear transmission 38 is supplied to the PTO shaft (s) 8 or 8 and 10 without the interposition of a fluid transmission, so that these PTO shafts are only driven mechanically. The wheel drive power, on the other hand, is similar to that in Embodiment according to FIG. 5 »again via a pump 40 and a motor 46 comprising fluid transmission transmitted. Pump 40 and motor 46 are via a high pressure line 44 and a Low pressure line 45 connected to one another. The output shaft of the Motor 46 drives the rear wheels via the axle drive, as shown in FIG 2 on. The pump 40 has a control plate disk known per se, via which the delivery rate of the pump is set and thus the driving speed is controlled. The adjusting shaft 114 of the control plate disk, which extends out through the housing of the pump 40 is firmly connected to a lever 115, on which of the shaft

114, a rod 116 via a pivot axis 117 facing away from the end is hinged. The end of the rod 116 facing away from the pivot axis 117 is connected to a lever via a further pivot axis 118 119 connected, at its other end via a pivot axis

S09826 / 02A7

120 is connected to an actuating rod 121. The actuating rod 121 iat in the axial direction by means of a not Pedals shown can be displaced by the driver, which is attached to the connecting part 18 near the driver's seat 15. Between the swivel axes 118 and 120, a third pivot axis 122 is attached to the lever 119. A slider 123 is located on the pivot axis 122 pivotally arranged, via parallel guide surfaces on the longitudinal sides of an elongated hole provided in a guide part 125 124 is slidably applied. The guide part 125 is with the The tractor frame is firmly connected. At. the pivot axis 122 is also a rod 126 articulated, which extends through a control cylinder 127 and extends through a spring element 128 located behind it. The regulating cylinder 127 has a cylindrical outer wall 129 and two end walls 130 and 131 »in which are sealed Passage openings for the displaceable rod 126 are provided. The rod 126 is fixedly arranged in a regulating cylinder 127 Eolben 132 connected, the sealing in the cylindrical Housing is performed. The space present in the control cylinder 127 on both sides of the piston 132 has bores that are connected to both sides of the piston 132 emptying signal lines 133 and 134 in Connected. From these signal lines the line 133 is to the high pressure line 44 between the pump 40 and the hydraulic motor 46 and the line 134 connected to the low pressure line 45, via which the liquid flows back from the motor 46 to the pump 40 α

The spring element 128 has a cylindrical outer wall 135 'near both ends with inwardly projecting annular collars 136, which run parallel to a plane perpendicular to the center line of the rod 126. Both collars 136 include the passage for the rod 126 and those surrounding the rod 126 Sockets 137 »whose distance from one another corresponds approximately to the length of the cylindrical outer wall 135. Each of the sleeves 137 & at an annular The collar 138 'whose outside diameter is smaller than the inside diameter of the collar 136. On those facing each other On the sides of the collars 138, a spring plate 139 is supported, which is ring-shaped and the outer surface of the relevant Sockets 137 surrounds. The outside diameter of each spring plate 139

509826/0247

is larger than the inner diameter of the respective collar 136, so that the spring plates 139 arranged between the collars 136 use these collars as stops. Between the spring plates 139 a compression spring 140 is arranged with a preload.

In the actuating rod 121 is / is known per se impact

damper 141 in particular a hydraulic shock absorber arranged, which is designed in such a way that movements of the part of the Rod 121 are transmitted in a damped manner to the part of rod 121 which is directly coupled to pivot axis 120.

The embodiment shown in Fig. 9 operates like follows:

During operation, the diesel engine 3 delivers its' Power, the total power being determined again by the control rod 32 of the injection pump, via which the fuel injection quantity and thus the engine torque and, because of the constant speed, also the engine power can be adjusted. The one on the PTO 8 maximum power to be transmitted always corresponds to the difference between the total engine power and that consumed by the wheel drive Power. Since the gear ratio 38 is not variable is translation, the hydraulic pump 40 is always with the driven at the same speed. The one supplied by this pump 40 Power, which can be adjusted by means of the fire mirror disk fastened on the adjusting shaft 114, drives the hydraulic motor 46 with it variable drive speed due to the driving speed of the tractor is adjustable. The pressure in the high pressure line 44 or if the pressure in the low pressure line 45 is not constant, the pressure difference between the high pressure line and the spring pressure line 45, are decisive for the • The wheel drive torque supplied by the pump 40 and thus, because of the constant speed of the pump 40, for the supplied to the wheels power. The pressure in the high pressure line 44 and that in the low pressure line 45 act via the lines 133 and 134, respectively the opposite sides of the one arranged in the control cylinder / Piston 132. The bias of the compression spring 140 in the suspension element 128, that is to say that of this spring on the two spring

tsller 139 force exerted corresponds to the force exerted on the

S09826 / 02A7

Basket 132 is exerted by the pressure difference occurring in lines 44 and 45, which occurs at the specified maximum power to be transmitted from pump 40 to the wheels (in the numerical example a limit power of 90 hp). As soon as the power supplied to the wheels approaches the value of 90 HP, the rod 126 will move in the direction of arrow E as a result of the pressure difference mentioned on both sides of the piston 132, since the force exerted on the piston 132 under these conditions the preload of the compression spring 140 exceeds. If the driver does not change the position of the actuating rod 121, as a result of this movement of the rod 126, the lever 115 is pivoted in the direction F, which corresponds to an adjustment of the control mirror disk of the pump 40 in the direction of a reduction in power, so that the power supplied to the wheels decreases the pressure in the line 44, and thus also the pressure difference between the lines 44 and 45 decreases, so that finally the force exerted on the piston 132 drops to a value that is less than the pretension of the leather 140, whereby the movement of the Rod 126 in the direction E stops. If the power supplied to the wheels is less than 90 hp, the rod 126 remains in the position shown in FIG wishes to change the driving speed, the lever the Stoesdämpfer is pivoted 119 through the movement of the rod 121 about the pivot axis 122, whereby the control mirror plate of the pump 40 into the position is rotated to the desired power corresponding ^/ serves to ensure that small, undesirable. foot movements of the driver cannot be transferred to the same extent to the lever 119. The power dissipated via the PTO shaft 8 for driving tools always corresponds to the difference between the power of the diesel engine, e.g. 150 hp, and the power consumed by the wheels (in the numerical example a maximum of 90 hp ) so that when the engine is running at full power, the PTO output is at least 60 hp.

Instead of or in addition to that shown in FIGS. 5 and 9 on Rear of the tractor provided PTO shaft 8 can under the

509826/0247

Invention also at least one on the front of the tractor Ending power take-off shaft 10 may be provided, which is coupled to the power take-off shaft 8 via a gear transmission. It is also possible to be close the back of the power take-off shaft 8 and near the front of the power take-off shaft 10 via gear transmission mechanical auxiliary shafts with these To couple power take-offs, the speeds of these auxiliary shafts are in a fixed ratio with those of power take-offs 8 and 10. In a third, not shown embodiment, a known, fully mechanically acting device is used. Such a device ("load monitor") has two flanges arranged next to each other, which are attached to separate shafts, whose center lines are aligned. In the facing end faces, the plansche have grooves running in the same direction, in which Balls are guided, 'which is essentially the connection between the Establish both flanges and transfer the torque carried by the shaft assembly from one part of the shaft to the other. In the known construction, if the torque and thus the power to be transmitted is exceeded at constant speed a certain value, the balls run up against a spring tension against the edges of the grooves, whereby the flanges in be pushed apart in the axial direction, which is possible because at least one of the flanges on its shaft opposes Spring tension is arranged displaceably. The mutual spacing between the flanges is thus increased a certain, set, torque to be transmitted, and it can be used by a mechanical transmission a limit for the movement of the control rod 32 corresponding to the stop 92, similar to that in FIGS. 7 and 8 adjust. The construction of this type is well suited when a mechanical change gearbox or a hydraulic torque converter is used. The mechanical signal transmitter described in this third embodiment should then be between the Gear ratio 38 and the mechanical change gear or the hydraulic torque converter can be attached. This is also the case with a relatively low power take-off shaft output to limit the power to be transmitted to the driven wheels to the value of 90 hp mentioned in the numerical example.

£ 09826/0247

~ ²⁶ ~ 2407923

The described restriction of the Eadantriet) performance can be "remedied" in the first embodiment line 50 or both lines 48 and 49 and in the second Embodiment the lines 133 and 134 can be shut off by the driver be formed. Then full power can be fed to the wheels (e.g. for plowing), but in this case nut the torque converter for the wheels are designed so that dsss it can transmit the entire torque, while achieving the essential advantage with a limited wheel drive power becomes that the torque converter for the wheel drive power can be made considerably cheaper than known ones Smugglers.,

The invention is not limited to what is mentioned in the description and / or in the claims, but rather "also refers to the details of the figures.

-Patent claims-

509826/0247

Claims (1)

Patent attorney Dipl-mg. Wait Jackish 7 Stuttgart N, Menzelstraße 40 ρ ^ ΕΝφ ^ βρΗϋΕΟΞΕ: - 2 G, Fc b. 1Q7I 1. Commercial vehicle, especially tractor with drivable Wheels and connections for pulled tools, e.g. a plow and / or drivable tools e.g. a harvesting machine, whose drive is a motor, at least one device for changing the transmission ratio, in particular has a torque converter and at least one power take-off shaft for driving the work tools, characterized in that, that the motor (3) has a maximum output (torque), which is greater than that which the device (40, 46) can transmit for changing the transmission ratio while the PTO shaft (8, 10) to "transfer the maximum engine power (Torque) is suitable. 2. Vehicle according to claim 1, characterized in that ' the entire engine power or the entire engine torque the PTO shaft (S, 10) is to be transmitted. 3. Vehicle according to claim 1 or 2, characterized in that the power or the torque of the motor (3) is approximately the Twice that of the gear ratio change device (40, .46) corresponds to transmittable power or torque. Il ■ Vehicle according to one of the preceding claims, characterized characterized in that the device (40, 46) for changing the transmission ratio hydrodynamically or hydrostatically as Torque converter or work as a gearbox!;. ^ ——. Z-. Vehicle according to one of claims 1 to 3? characterized in that the device for changing the transmission ratio is formed by a mechanical change gear. 6. Vehicle according to one of claims 1 to 3? characterized, that the device for changing the transmission ratio is designed as a hydrostatic transmission (40, 46). 7. Vehicle according to one of the preceding claims with a motor that has an almost constant speed during operation, and with a control device for the power or torque developed at this speed, the control device has a stop which limits the maximum value of power or torque, characterized in that £ 09826/0247 ORIGINAL INSPECTED the stop (92) is adjustable. 8. Commercial vehicle in particular tractor with an engine and a control device for the power or torque developed at a certain speed, the control device has a stop which limits the maximum value of power or torque, characterized in that the stop (92) is adjustable. 9. Vehicle according to claim 7 or 8, characterized in that at least one device (48) is present through which the wheel drive power or the corresponding torque and / or the power supplied to the power take-off shaft (8, 10) or the corresponding Torque are measurable. 10. The vehicle according to claim 9 ₅ characterized in that the measured power or torque values processing means are connected to the adjustable stop (92). 11. Vehicle according to claim 10, characterized in that the devices have a control slide (4-8) in which at least one piston (67, 793 displaceable under the influence of the measured value) is provided. 12. Vehicle according to claim 11, characterized in that the control slide (4-8) has two displaceable pistons (79, 67). 13. Vehicle according to claim 11 or 12, characterized in that the piston (79, 67) can be displaced against a pretensioning force. 14-. Vehicle according to claim 13, characterized in that the pretensioning force is applied by a compression spring (64-, 65). 15. Vehicle according to one of claims 12 to 14, characterized in that that the opposite sides of the pistons (79, 67) correspond to the measured powers or torques Forces are applied. 1 ^. Vehicle according to one of Claims 9 to 15, characterized in that that the measured value (s) of the wheel power and / or the PTO shaft power is supplied in the form of fluid pressure the measured values corresponding to the wheel drive power and / or the power take-off shaft power can be recorded hydraulically and / or transferable. 509826/0247 17 · Vehicle according to one of the preceding claims, characterized characterized in that both the drivable wheels (2) and the power take-off shaft (8, 10) via a hydraulic pump (39> 40) and a hydraulic motor (43, 46) connected to this can be driven. 18. Vehicle according to claim 17 *, characterized in that the measured values of the high pressure side of the hydraulic connection (47, 49) between the pump (39, 40) and the motor (43, 46) can be removed. 19. Vehicle according to one of claims 10 to 18, characterized characterized in that the devices for processing the measured power or torque values are designed in such a way that with a power take-off shaft power or a power take-off shaft torque, which is greater than the difference between the maximum Motor power or the maximum torque of the motor and the or the via the device located in the wheel drive for changing the transmission ratio maximum transmittable power or transmittable torque of the stop (92) in a the position corresponding to the maximum engine power or the maximum torque of the engine is fixed a PTO power below the difference or power take-off shaft torque, the stop (92) is held in a position that the or the through the lying in the wheel drive Device (40, 46) for changing the transmission ratio corresponds to the maximum transferable power or transferable torque. 20. Vehicle according to one of claims 15 to 19 »thereby characterized in that the displacement of the other piston (79) can be blocked via one of the pistons (67). 21. Vehicle according to claim 20, characterized in that the second piston (79) is movable such that a Connection between the high pressure side of the hydrostatic transmission (40, 46) located in the wheel drive and the adjustable stop (92) is to be produced. 22. Vehicle according to one of claims 7 to 21, characterized in that that the adjustable stop (92) is hydraulically displaceable. 509826/0247 23. Vehicle according to one of claims 7 "to 21, characterized in that because the adjustable in.sch.lag; (92) is mechanically displaceable. 24. Vehicle according to one of claims 1 to 3, and claim 6 with a Hotor operating at almost constant speed and with a hydrostatic one in the bath drive Gear, whose pump has a device for adjusting the killer current characterized in that the setting of the device can be influenced by the size of the Hadan drive power is. 25 · Commercial vehicles, especially single-engine tractors and with a hydrostatic transmission located in the wheel drive, the pump of which is a device for adjusting the flow rate to v / e, characterized in that the setting of the device by the size of the wheel drive power can be influenced. 26. Vehicle according to claim 24 or 25, characterized in that that the power or the torque at least on the high pressure side of the hydraulic connection (44) between pump (40) and Motor (46) of the hydrostatic transmission can be detected via a measuring element (control cylinder 127). 27 »Vehicle according to claim 26, characterized in that the power or aas torque also on the low-pressure side (45) is detectable. 28. Vehicle according to claim 26 or 27, characterized in that the detected power or torque values as corresponding Pressure values are acting hydraulically on a displaceable piston (132). 29 · Vehicle according to claim 28, characterized in that the piston (132) counteracts the force of a pretensioned spring (140) is movable. 30. Vehicle according to claim 29, characterized in that the biasing force of the spring (140) of the maximum on the wheels (2) performance to be developed. 31. Vehicle according to one of claims 28 to 30, characterized in that that the displaceable piston (132) has an over- 609826/0247 Tragungsei: orrichtung with the device for adjusting the Delivery flow, the hydrostatic transmission (40, 46) is coupled. 32. Vehicle according to one of claims 28 ″ to 31 ″ thereby. characterized in that the device for adjusting the flow rate of the hydrostatic transmission regardless of the position of the displaceable piston (132) is adjustable by the driver. 33. Vehicle according to one of the claims 24 to 31 ·> thereby. characterized in that the device for adjusting the flow rate is formed by a «control plate disk. 34. Vehicle according to one of claims 1 to 6 and claim 7? characterized in that between the motor and the device for changing the transmission ratio a mechanical acting power or torque transmitting element is arranged, which is coupled to the stop (92). IT commercial vehicle, in particular single-engine tractor and a control device assigned to it, which has a stop, over the maximum value of the power or the torque is adjustable, the vehicle being provided with a device for (continuously) changing the gear ratio is, characterized in that between the motor (3) "and the Device for changing the transmission ratio (40, 46) is a mechanically acting one that transmits the power or the torque Element is arranged which is coupled to the Ansehlag (92). 36. Vehicle according to claim 3 ^ or 355, characterized in that that the element has parts that are determined when a 'is reached Shift power or a certain torque against each other. 37 · Vehicle according to claim 36, characterized in that the parts can be moved against each other against spring force. 33. Vehicle according to one of the preceding claims, characterized. characterized in that the vehicle has only one drive axle. 39. Vehicle according to one of the preceding claims, ckdureli marked that on the back of the vehicle at least 509826/0247 - 32 - a power take-off shaft (8) is provided. 40. Vehicle according to one of the preceding claims, characterized in that on the front of the vehicle
at least one power take-off shaft (10) is provided. 41. Vehicle according to one of the preceding claims, characterized in that on the rear of the vehicle a Lifting device (11, 12) is provided. 42. Vehicle according to one of the preceding claims, characterized in that one on the front of the vehicle Lifting device (I3) is provided. 4 ^. Vehicle according to one of the preceding claims, characterized characterized in that the limitation of the drivable Wheels (2) maximum transferable power can be canceled to a value below the maximum engine power. 509826/0247 Blank page