DE19953380A1 - Self-propelled mower unit - Google Patents

Abstract

Self-propelled mowing unit, consisting of a carrier vehicle (1) with a front mower (2) and side mowers (3, 3 ') articulated on both sides of the carrier vehicle (1) for mowing agricultural crops with or without conditioner (11), the side mowers (3 , 3 ') between the front (7) and rear wheels (8) laterally projecting on a boom arm (4, 4') are arranged and guided, and the boom arms (4, 4 ') each for vertically movable suspension of the side mowers (3, 3 ') on the support bars (22, 22') of the chassis (9) of the carrier vehicle (1) so as to be pivotable about an axis of a hinge joint connection (25, 25 ') oriented approximately in the travel and working direction (F) of the carrier vehicle (1) and each mowing unit (10, 10 ') of the side mowers (3, 3') is connected in an articulated manner to the outer end of the boom arm (4, 4 '), and each side mower (3, 3') each with its boom arms (4 , 4 ') by means of a piston-cylinder arrangement the chassis (9) of the carrier vehicle (1) is articulated and connected to it from an approximately horizontal working position to an almost vertical transport position, each side mower (3, 3 ') having a first actuator as a pressure medium cylinder (35, 35') Swiveling a mowing unit (10, 10 ') about the pivot axis (27, 27') for transferring the side mower (3, 3 ') from its working to its transport position and vice versa, and wherein each side mower (3, 3') has one ...

Description

The invention relates to the articulation of side mowers Carrier vehicle as a self-propelled mower unit according to the generic term of Claim 1, wherein the mower units preferably as a rotary mower are trained which for mowing straw, in particular Green fodder is suitable for agricultural purposes.

Such linkages are particularly of a variety of mowers Executions known.

For example, in EP 0 808 556 A1 the suspension and Drive arrangement for one or both sides of a carrier vehicle attached mower units shown, which a front mower and two arranged laterally between the axles of the carrier vehicle Has side mowers. Each of the two side mowers is one aligned approximately in the direction of travel and work of the carrier vehicle Axis pivotally arranged on a cantilever arm. On the outside Ends of the cantilever arms is a hinge arrangement on which the Working units are articulated as mowing units. The linkage of the Mowing units take place approximately in the center of gravity which is transverse to the driving and Working direction extending mower unit. The drive train for the drive the cutting tools is part of the articulated connection, the Drive train for example as a V-belt drive in connection with  Transmission elements such as shafts with universal joints and Bevel gear can be formed.

The object of this invention is to provide a self-propelled mower unit Carrier vehicle, front mower and articulated on both sides of the carrier vehicle To create side mowers, the steering characteristics in the operating state of mowing can be improved.

This task is solved with the characteristics of the characteristic part of the Claim 1. The further embodiment of the invention is the following Description, the drawings and claims 2 to 20 can be found.  

Reference list

1

Carrier vehicle

2nd

Front mower

3rd

,

3rd

'Side mower

4th

,

4th

'' Boom arm

5

Front axle

6

Rear axle

7

Front wheel

8th

Rear wheel

9

chassis

10th

,

10th

',

10th

'' Mowing unit

11

,

11

',

11

'' Conditioner

12th

,

12th

'Main beam

13

,

13

'' Jockey wheel carrier

14

Swivel bearing

15

,

15

'Jockey wheel

16

Vertical axis

17th

,

17th

,

17th

'' Jack bracket

18th

Spring element

19th

,

19th

',

19th

'' Lift cylinder

20th

Handlebar coupling

21

,

21

Coupling link

22

,

22

'Tragholm

23

Front three-point hydraulic

24th

Lifting cylinder

25th

,

25th

'' Hinge joint

26

,

26

'' Hinge joint

27

,

27

'' Swivel axis

28

,

28

'' Swivel axis

29

V-belt pulley

30th

Transfer case

31

PTO shaft

32

PTO shaft

33

Transfer case

34

,

34

'PTO shaft

35

,

35

'' Pressure cylinder

36

,

36

'' Pressure cylinder

37

,

37

'Hinge point

38

,

38

'Hinge point

39

,

39

'Hinge point

40

,

40

'Hinge point

41

Main middle level

42

Riot level

43

horizontal

44

,

44

',

44

'' Valves

45

,

45

'' Directional valves

46

,

46

'' Directional valves

47

Directional control valve

48

Row flange plate

49

Control pump

50

,

50

'' Pressure sensor

51

,

51

'' Pressure sensor

52

,

52

'Displacement transducer

53

,

53

'Displacement transducer

54

,

54

'' Servo directional valve

55

,

55

'' Servo pressure valve

56

,

56

'' Supporting structure
a switch position
b Switch position
x ₁

Lever arm
x ₂

Lever arm
F direction of travel
F ₂₈

, F _'28

Weight
-F ₂₈

, -F _'28

Ground support
F ₃₉

, F _'39

Cylinder support force
F ₄₀

, F _'40

Weight
M engine
P pump line
T tank line
α angle of inclination
β angle of inclination
γ angle of inclination

It shows:

Fig. Mowing unit 1 in a side view in the direction of travel (F)

Fig. 2 Self-propelled mower unit in side view in the direction of travel (F) with mower units lifted off the ground

Fig. 3 mowing unit with a carrier vehicle (1) in a simplified illustration in a view (X) from the top of the work plane directed according to Fig. 1

Fig. 4 view (Y) of FIG. 1 in a simplified, enlarged view

Fig. 5 articulation of the pressure medium cylinders ( 35 , 36 ) according to FIG. 4 in an enlarged view

FIG. 5a Simplified representation of the forces on the example of the cantilever arm (4)

Fig. 5b simplified graphic representation of the forces on the example of the cantilever arm (4 ')

Fig. 6 view (V11) of FIG. 5

Fig. 7 View (Z) of FIG. 5

Fig. 8 mowing unit according to the invention in a representation analogous to FIG. 3

Fig. 9 showing a mowing unit according to the invention similar to FIG. 4

FIG. 10 One possible working position of the mowing unit analogous to FIG. 9

FIG. 11 view (Y) shown in Figure 1 but in a simplified enlarged illustration.

Fig. 12 embodiment of a hydraulic circuit of the pressure medium cylinder, without position control

Fig. 13 embodiment of a hydraulic circuit of the pressure medium cylinder, with position control

Fig. 1 shows a mowing unit according to the invention in a side view in the direction of travel (F), the wheels of which are supported on a flat contact plane ( 42 ). The mower unit shown consists of a carrier vehicle ( 1 ) with a front mower ( 2 ) coupled to the front three-point hydraulic system ( 23 ) and two on both sides of the carrier vehicle ( 1 ) between the front wheels ( 7 ) and the rear wheels ( 8 ) of the carrier vehicle ( 1 ) arranged side mowers ( 3 , 3 ').

The mowing units ( 10 , 10 ', 10 ''), those of the side mowers ( 3 , 3 ') and that of the front mower ( 2 ), are shown in simplified form as rotary mowers with rotating mowing tools with integrated conditioners ( 11 , 11 ', 11 '' ). The mower units ( 10 , 10 ', 10 '') are drivable and operatively connected to the carrier vehicle ( 1 ) by means of a link coupling ( 20 ).

The side mowers ( 3 , 3 ') additionally have a support wheel ( 15 , 15 ') which is pivotally mounted at the end of a support wheel carrier ( 13 , 13 ') in a pivot bearing ( 14 ) around the vertical axis ( 16 ), as a freely running support wheel ( 15 , 15 ') is formed. The support wheel carrier ( 13 , 13 ') is connected to a main carrier ( 12 , 12 ') which is articulated laterally on the carrier vehicle ( 1 ).

The link coupling ( 20 ) consists of articulated coupling links ( 21 , 21 '), which on the one hand on the mowing units ( 10 , 10 ', 10 '') and on the other hand on a boom, designed as a jack bracket ( 17 , 17 ', 17 '' ), are coupled. Due to the type of articulation, the coupling links ( 21 , 21 ') are mainly exposed to tensile forces during mowing, whereby the mowing units ( 10 , 10 ', 10 '') are subjected to towing behavior when the carrier vehicle ( 1 ) travels in the direction of travel (F) .

The jack bracket ( 17 '') of the front mower ( 2 ) or the jack bracket ( 17 , 17 ') of the side mowers ( 3 , 3 ') are part of the main beam ( 12 , 12 ') and thus part of the supporting structure ( 56 , 56 ' ) in total, on which the mowing units ( 10 , 10 ', 10 '') can be moved vertically and, due to the link coupling ( 20 ), can also be pivoted about a roll axis transversely to the direction of travel (F), whereby both forms of movement can overlap. Furthermore, due to the formation of the position of the coupling points of the coupling links ( 21 , 21 '), the handlebar coupling ( 20 ') allows the mowing units ( 10 , 10 ', 10 ') to pass over an obstacle on the ground, such as a ground elevation that the mowing units ( 10 , 10 ', 10 '') can move back and away from the direction of travel (F) in addition to and relative to the carrier vehicle ( 1 ) at the same time as the height-adjustable change of position, which reduces the momentary force amplitudes of the towing force of a mower.

The front mower ( 2 ) can be lifted into its final transport position with the lifting cylinder ( 24 ).

In addition, the mowing units ( 10 , 10 ', 10 '') can be lifted from the ground during the mowing process with the lifting cylinders ( 19 , 19 ', 19 ''), for example, to be able to drive over already mowed green forage without the mowing tools getting stuck Ground.

The articulated points on each side of each coupling member ( 21 , 21 ') are expediently designed as ball-and-socket eyes. The position of the front connection points of the coupling links ( 21 , 21 ') in the direction of travel (F) as part of a jib bracket ( 17 , 17 ', 17 '') is determined so that the mowing units ( 10 , 10 ', 10 '') during the sliding of a floor lift or floor depression is largely independent of the current orientation of the jack bracket ( 17 , 17 ', 17 '').

This type of design of the handlebar coupling ( 20 ) enables the mowing units ( 10 , 10 ', 10 ''), independently of one another, within the restrictions of their freedom of movement to have a translatory upward or downward movement, a momentary translational leading or trailing movement relative to the driving movement and these Perform translational movements overlaying current rotary movements of all three degrees of freedom.

Parallel to the handlebar coupling ( 20 ), the mowing units ( 10 , 10 ', 10 '') are operatively connected by means of prestressed spring elements ( 18 ) to their associated trestle booms ( 17 , 17 ', 17 '') in such a way that a part of the weight of a Mowing unit ( 10 , 10 ', 10 '') is carried by the respective jack stand boom ( 17 , 17 ', 17 '') during mowing.

The remaining part of the weight of the mowing units ( 10 , 10 ', 10 '') is supported during the mowing operation by the contact surfaces of the mowing units ( 10 , 10 ', 10 '') on the ground, so that these supporting forces are the reaction forces of the remaining part which represents weight.

The vertical component of the spring forces as the sum vector of the spring elements ( 18 ), which represents the relief component for reducing the ground support forces of the mowing units ( 10 , 10 ', 10 ''), must also be supported as a reaction force against the ground.

The coupling between the front mower ( 2 ) and carrier vehicle ( 1 ) is designed so that the vertical component of the spring forces, to relieve the ground support force of the mowing unit ( 10 ''), is supported on the front wheels ( 7 ) of the carrier vehicle ( 1 ).

The coupling between the side mowers ( 3 , 3 ') and the carrier vehicle ( 1 ) is designed so that the vertical component of the spring forces to relieve the ground support force of the mowing unit ( 10 , 10 ') partly on the front wheels ( 7 ), partly on the Rear wheels ( 7 ) of the carrier vehicle ( 1 ), and partly on the support wheels ( 15 , 15 ') of the side mowers ( 3 , 3 ') is supported.

The amounts of the remaining ground support forces for supporting the mowing units ( 10 , 10 ', 10 '') with respect to the ground can be divided by the adjustability of the spring preload forces.

Part of the link coupling ( 20 ) are also the actuators which can be pressurized, for example designed as hydraulically actuated lifting cylinders ( 19 ). In the working position shown, the lifting cylinders ( 19 ) are in the floating position, so that they do not hinder the ground adaptation of the mowing unit ( 10 , 10 ').

Fig. 2 shows a self-propelled mowing unit according to the invention in a side view in the direction of travel (F) with the mower units ( 10 , 10 ', 10 '') lifted off the ground. The mowing units ( 10 , 10 ', 10 '') can be transferred from the mowing position to a raised position and vice versa with the lifting cylinders ( 19 , 19 ') pressurized with pressure medium. In the raised position, the mowing units ( 10 , 10 ') can be held in the raised position, for example by pilot operated, non-return valves.

Fig. 3 shows a self-propelled mower unit according to the invention with a carrier vehicle ( 1 ) in a simplified representation in a view (X) from above towards the working level according to Fig. 1. Both side mowers ( 3 , 3 ') are symmetrical to the plane perpendicular to the road arranged in the direction of travel (F) main central plane ( 41 ). The mowers, the front mower ( 2 ) and the side mowers ( 3 , 3 ') are driven by a combustion engine, not shown, for better clarity of illustration, which has the torque required to drive the mower units ( 10 , 10 ', 10 '' ) for example via a transmission drive to the V-belt pulley ( 29 ) into a transfer case ( 30 ), for example designed as a bevel gear. There are two output shafts on the transfer case ( 30 ). These are coupled to the cardan shafts ( 31 , 32 ). The PTO shaft ( 31 ) represents the continuation of the drive train for driving the mower unit ( 10 '') of the front mower ( 2 ), and the PTO shaft ( 32 ) represents the continuation of the drive train for driving the mower units ( 10 , 10 ') of the side mowers ( 3 , 3 '). The transfer case ( 33 ), for example designed as a bevel gear, branches the drive train for driving the mowing units ( 10 , 10 ') in such a way that from the transfer case ( 33 ) two output shafts with the articulated shafts ( 34 , 34 '), the cardan shaft ( 34 ) representing the drive train for the mowing unit ( 3 ) and the cardan shaft ( 34 ') representing the drive train for the mowing unit ( 3 ').

Both the front mower ( 2 ) and the side mowers ( 3 , 3 ') are articulated on the chassis ( 9 ) of the carrier vehicle ( 1 ).

The carrier vehicle ( 1 ) can, as shown, be equipped with a front three-point hydraulic system to which the front mower ( 2 ) is coupled.

Both side mowers ( 3 , 3 ') are each by means of a boom arm ( 4 , 4 ') through a hinge joint connection ( 25 , 25 ') with a hinge axis predominantly parallel to the direction of travel as a pivot axis ( 27 , 27 ') for the boom arm ( 4 , 4 '), articulated to the chassis ( 9 ) of the carrier vehicle ( 1 ). The boom arms ( 4 , 4 ') represent the link between the support frame ( 9 ) of the carrier vehicle ( 1 ) and the main carrier ( 12 , 12 ') of the side mowers ( 3 , 3 ').

This connection is made by the outrigger arms ( 4 , 4 ') facing outwards, also by means of a hinge joint connection ( 26 , 26 ') with a hinge axis predominantly parallel to the direction of travel as a pivot axis ( 28 , 28 ') for folding up the respective side mower ( 3 , 3 ') in its respective transport position, are connected to the main carrier ( 12 , 12 ').

FIG. 4 shows the view (Y) according to FIG. 1 in a simplified but enlarged illustration. Two side mowers ( 3 , 3 ') are each assigned two actuators acted upon by pressure medium, designed as pressure medium cylinders ( 35 , 36 ) or ( 35 ', 36 '). The pressure medium cylinders ( 35 , 36 ) are functionally assigned to the side mower ( 3 ) and the pressure medium cylinders ( 35 ', 36 ') are functionally assigned to the side mower ( 3 ').

Due to the spatially restricted accommodation options within the installation space of the carrier vehicle, the functionally interacting pressure medium cylinders ( 35 , 36 ) are assigned to a first vertical plane and the functionally interacting pressure medium cylinders ( 35 ', 36 ') are assigned to a second vertical plane, with the two vertical planes being approximately spaced apart from one another run.

For the sake of clarity, the graphic representation of the pressure medium cylinders ( 35 ', 36 ') has been omitted in FIG. 4, since the pressure medium cylinders ( 35 ', 36 ') are largely covered by the pressure medium cylinders ( 35 , 36 ) shown in this representation.

On the cylinder side, the pressure medium cylinders ( 35 , 35 ') are supported in the articulation points ( 37 , 37 ') and the pressure medium cylinders ( 36 , 36 ') in the articulation points ( 39 , 39 ') on the chassis ( 9 ) of the carrier vehicle ( 1 ) .

On the piston rod side, the pressure medium cylinders ( 35 , 35 ') in the articulation points ( 38 , 38 ') on the main supports ( 12 , 12 ') of the side mowers ( 3 , 3 ') and the pressure medium cylinders ( 36 , 36 ') in the articulation points ( 40 , 40 ') on the cantilever arms ( 4 , 4 ').

FIG. 5 shows the articulation of the pressure medium cylinders ( 35 , 36 ) according to FIG. 4 in an enlarged representation. The main supports ( 12 , 12 ') of the supporting structure ( 55 , 55 ') of the mowing units ( 10 , 10 ') are supported in the hinge joints ( 26 , 26 ') with respect to the chassis ( 9 ). Accordingly, the weight forces are supported in the joints with the swivel axes ( 28 , 28 '), which thereby simultaneously exert a torque about the swivel axis ( 27 , 27 ') on the extension arms ( 4 , 4 ').

Fig. 5a shows a simplified graphical representation of the reaction forces (F _28, F _28, F _40, F _39), caused by the weight force (F ₂₈₎ on the example of the cantilever arm (4). The illustration of the bearing forces in the hinge joint connection ( 25 ) has been omitted for reasons of clarity. The cantilever arm ( 4 ), rotatably mounted about the pivot axis ( 27 ) in the hinge joint connection ( 26 ), has the lever arm (x ₁ ) with respect to the weight (F ₂₈ ) around the pivot axis ( 27 ) and the supporting force of the piston rod of the pressure medium cylinder ( 36 ) at the pivot point ( 40 ) the lever arm (y ₁ ).

If the cantilever arm ( 4 ) is at rest, the pressure medium cylinder ( 36 , 36 ') must apply corresponding counterforce (F ₄₀ , F ₃₉ ) at the articulation points ( 39 , 40 ), where (F ₃₉ ) the reaction force of (F ₄₀ ). These counterforces represent the cylinder support forces (F ₄₀ , F ₃₉ ) and these generate a hydrostatic pressure in the pressure medium cylinders ( 36 , 36 ') which must be applied by the hydraulic system, ie it must be supported.

Fig. 5b shows analogously to Fig. 5a shows the situation in consequence of the weight force (F _'28) the reaction forces (F' _28, -F _'28, M' _40, M _'39) on the arm (4'). The illustration of the bearing forces in the hinge joint connection ( 25 ') has been omitted for reasons of clarity.

FIG. 6 shows the view (W) according to FIG. 5. It shows the pressure medium cylinders ( 35 , 35 ') arranged approximately parallel to one another.

FIG. 7 shows the view (Z) according to FIG. 5. It shows the pressure medium cylinders ( 36 , 36 ') arranged approximately parallel to one another.

FIG. 8 shows a self-propelled mowing unit according to the invention in the representation analogous to FIG. 3, the position of the pressure medium cylinders ( 35 , 35 ') being additionally shown in this figure.

Fig. 9 shows the representation of a self-propelled mowing unit according to the invention analogous to Fig. 4 in a non-flat terrain in the working position. The alignment of carrier vehicle ( 1 ) and side mowers ( 3 , 3 ') shown is adapted to the ground horizon of the site. As a result, the carrier vehicle ( 1 ) has an inclination angle (α) with respect to the horizontal ( 43 ), the side mower ( 3 ) has an inclination angle (β), and the side mower ( 3 ') has an inclination angle (β').

In the event that the mower combination is used on very uneven terrain or, for example, for mowing embankments, it may be advantageous for the mower unit to have an adjustment and control device which determines the position of the pivot axes ( 28 , 28 ') the side mowers ( 3 , 3 ') and thus can change the distance to the ground and regulate if necessary.

In particular, this can improve the independence of the momentary rolling and / or pitching movements of the carrier vehicle ( 1 ) along its travel path. As a result, the mobility of the mowing units ( 10 , 10 ') can also be improved in uneven terrain, which can reduce the force peaks of the towing forces of the mowing units ( 10 , 10 ').

The pressure medium cylinders ( 36 , 36 ') can be used as an adjusting and regulating device according to the invention, in that these pressure medium cylinders are equipped, for example on the piston bottom and piston rod side, with pressure sensors which sense the respective hydraulic pressures and feed these values as digitized input signals to a microprocessor. Furthermore, the respective positions of the piston rod of the hydraulic cylinders ( 36 , 36 ') can be detected by sensors as displacement transducers, the values thus recorded being able to be fed to a microprocessor as digitized input signals. With the aid of these input signals, the microprocessor can generate output signals in the sense of a control circuit, which in turn can act on the respective position of the piston rods of the hydraulic cylinders ( 36 , 36 '), as a result of which the respective extension arms ( 4 , 4 ') about their respective pivot axes ( 27 , 27 ') can be rotated, which can be used to change the distance of the pivot axes ( 28 , 28 ') from the ground.

Fig. 10 shows analogous to Fig. 9 that the handlebar coupling ( 20 ) between the cutting unit ( 10 ) and the main carrier ( 12 ), the cutting unit ( 10 ) can perform a rotational movement relative to the main carrier ( 12 ). Since the mowing unit ( 10 ) is located in front of the support wheel ( 15 ), the mowing unit ( 10 ) can experience an additional angle of inclination (γ) due to the upstream changes in the soil horizon, for example through elevations or depressions.

FIG. 11 shows the view (Y) according to FIG. 1 in a simplified but enlarged illustration with the side mower ( 3 ) folded up on one side in the transport position.

Fig. 12 shows an embodiment of a hydraulic circuit of a self-propelled mower unit according to the invention. This figure shows a simplified hydraulic plan for controlling all hydraulic functions of the mowing unit, but without a control unit.

This exemplary embodiment shows electrically operated directional valves ( 44 , 44 '; 45 , 45 '; 46 , 46 '; 47 ) for actuating the lifting cylinders ( 19 , 19 ', 19 ''; 24 ) and the other actuators as pressure medium cylinders ( 35 , 35 '; 36 , 36 ').

All directional valves ( 44 , 44 '; 45 , 45 '; 46 , 46 '; 47 ) for controlling the hydraulic functions are arranged on a row flange plate ( 48 ) which is connected to the pump line (P) and the tank line (T). The hydrostatic pressure is generated by a control pump ( 49 ) which is driven by the motor (M) of the carrier vehicle ( 1 ).

The electrically operated directional valves ( 44 , 44 '; 45 , 45 ; 46 , 46 '; 47 ) have a central position as the blocking position, as well as two further switching positions (a and b). The valves are controlled, for example, with a control panel in the driver's cabin.

In the working position, the support bars ( 12 , 12 ') of the side mowers ( 3 , 3 ') are aligned approximately horizontally. The pressure medium cylinders ( 36 , 36 ') are clamped hydraulically, ie the directional control valves ( 45 , 45 ') for actuating them are switched to the blocking position.

The pressure medium cylinders ( 35 , 35 ') are controlled by the directional control valves ( 46 , 46 '). In the mowing mode, the valves ( 46 , 46 ') are switched to the floating position, ie in the control position (a).

The lifting cylinders ( 19 , 19 ', 19 ''; 24 ) are controlled by the valves ( 44 , 44 ', 44 ''). The lifting cylinders ( 19 , 19 ', 19 ''; 24 ) are in the mowing mode in the floating position, ie they are switched in position (a). With the lifting cylinders ( 19 , 19 ', 19 ''; 24 ), the mowers can be controlled individually or in groups by switching the directional control valves ( 44 , 44 ', 44 ''), with the mower units ( 10 , 10 ', 10 '') are lifted off the floor. in the middle position of the valves ( 44 , 44 ', 44 '') as the blocking position, the mowing units ( 10 , 10 ', 10 '') are held in their raised position.

With the lifting cylinders ( 24 ), the front mower ( 2 ) is raised by actuating the directional control valve ( 47 ) in the switching position (b). In the middle position as the blocking position of the valve ( 47 ), the front mower ( 2 ) is held in the transport position. In switch position (a) the front mower ( 2 ) can be lowered relative to the ground.

The pressure medium cylinders ( 35 , 35 ') for lifting the mowing units ( 10 , 10 ') are controlled by the directional control valves ( 46 , 46 '). In the mowing mode, the valves ( 46 , 46 ') are switched to the floating position in switch position (a).

The pressure medium cylinders ( 36 , 36 ') are controlled by the valves ( 45 , 45 '). In the mowing mode, the piston rods of both pressure medium cylinders ( 45 , 45 ') are hydraulically clamped, ie the directional control valves ( 45 , 45 ') are in the middle position as the blocking position.

To lower the side mowers ( 3 , 3 ') from the transport position into the working position, the directional valves ( 45 , 46 ; 45 ', 46 ') can be controlled together in groups.

To lift the side mowers ( 3 , 3 ') with the mowing units ( 10 , 10 ') from the mowing mode to the transport position, the directional control valves ( 45 , 45 ') are switched to the switching position (a) and at the same time the valves ( 46 , 46 ') switched to switch position (b).

To lower the side mowers ( 3 , 3 ') from the transport position to the mowing mode, the directional control valves ( 45 , 45 ') are switched to switch position (a) and the directional control valves ( 46 , 46 ') are also switched to switch position (a).

Fig. 13 shows a further embodiment of a hydraulic circuit of a self-propelled mower unit according to the invention. This figure shows a simplified hydraulic plan for controlling all hydraulic functions of the mower unit with control unit for position control of the boom arms ( 4 , 4 '). The control structure corresponds in principle to the description in FIG. 12.

The pressure medium cylinders ( 36 , 36 ') stand with the pressure sensors ( 50 , 51 ); ( 50 ', 51 ') for recording their current hydrostatic pressure in connection. The piston rods of the pressure medium cylinders ( 35 , 35 '); ( 36 , 36 ') stand with the incremental displacement transducers ( 52 , 52 '); ( 53 , 53 ') for sensory detection of their position in relation to their cylinder in connection. The output signals of the pressure sensors ( 50 , 51 ); ( 50 ', 51 ') and the displacement sensor ( 52 , 52 ', 53 , 53 ') are available to a microprocessor (not shown) as input signals in the control sense of the feedback. The hydrostatic pressure on the piston crown side of the pressure medium cylinders ( 36 , 36 ') represents the controlled variables, which controlled variables can in turn represent a function of the position of the piston rods.

The directional control valves ( 45 , 45 ') according to FIG. 12 are replaced by the electrically operated microprocessor-controlled servo directional control valves ( 54 , 54 '), each with a servo pressure valve ( 55 , 55 ').

The servo directional valves ( 54 , 54 ') with their servo pressure valves ( 55 , 55 ') including the pressure medium cylinders ( 36 , 36 ') act as actuators to create a microprocessor-controlled control system to support a dynamically controlled adaptation of the mowing units ( 10 , 10 ' ) to the floor relief.

In the mowing mode, the pressure sensors ( 50 , 51 ) record the hydrostatic pressures on the piston rod and piston crown sides, from which the differential pressure of the two pressure chambers can be determined. The displacement sensors ( 53 , 53 ') determine the current position of the piston rods of the pressure medium cylinders ( 36 , 36 ') and the displacement sensors ( 52 , 52 ') determine the current position of the piston rods of the pressure medium cylinders ( 35 , 35 '). These values are available to the microprocessor as input signals, so that the microprocessor knows the overall instantaneous state of the mowing units ( 10 , 10 ') as regards their alignment with the carrier vehicle. The input signals of the pressure sensors ( 50 , 51 ) provide information about the current force relationships in the articulation points ( 40 , 40 ') or in the swivel axes ( 28 , 28 '), which means that the vertical load in the hinge joint connections ( 26 , 26 ') can be closed. By actuating the servo pressure valves ( 55 , 55 ') in connection with the servo directional valves ( 54 , 54 '), the momentary equilibrium state of the cantilever arms ( 4 , 4 ') about the respective swivel axes ( 27 , 27 ') can be restored become.

This type of articulation of the mowing units ( 10 , 10 ') in connection with the arms ( 4 , 4 ') and their support by the pressure medium cylinders ( 36 , 36 ') relative to the carrier vehicle ( 1 ) in connection with the handlebar coupling ( 20 ) and the support wheel ( 15 , 15 ') of the mowing units ( 10 , 10 '), the ground support forces of the mowing units ( 10 , 10 ') can be minimized and sensitively adjusted and adapted to the given conditions of use.

As a result, the mowing units ( 10 , 10 ') have a good dynamic behavior with regard to the adaptation to the ground horizon during mowing operation, which likewise minimizes the towing forces, in particular those of the side mowers ( 3 , 3 ').

The transfer of part of the weight forces of the mowing units ( 10 , 10 ', 10 '') to support wheels ( 15 , 15 ') increases the overall stiffness with regard to the tracking behavior of the carrier vehicle ( 1 ), which has a particularly favorable effect on the steering behavior on slopes.

In particularly uneven terrain, this type of articulation of side mowers to a carrier vehicle can be further supported by a position control of the main girders ( 12 , 12 ') of the supporting structure ( 56 , 56 ') of the side mowers ( 3 , 3 '), whereby the undesirable yaw moments, which attack the carrier vehicle ( 1 ) are minimized. This improves in particular the stiffness of the carrier vehicle ( 1 ) in terms of its lane behavior and thus overall the steering properties and operational safety.

Claims (23)

1. Self-propelled mower unit consisting of a carrier vehicle ( 1 ) with a front mower ( 2 ) and on both sides of the carrier vehicle ( 1 ) articulated side mowers ( 3 , 3 '), for mowing agricultural straw with or without conditioner ( 11 ), the side mowers ( 3 , 3 ') between the front ( 7 ) and rear wheels ( 8 ) laterally projecting on a boom arm ( 4 , 4 ') are arranged and guided, and the boom arms ( 4 , 4 ') each for the vertically movable suspension of the side mowers ( 3 , 3 ') on the support bars ( 22 , 22 ') of the chassis ( 9 ) of the carrier vehicle ( 1 ) about an axis of a hinge joint connection ( 25 , 25 ') oriented approximately in the travel and working direction (F) of the carrier vehicle ( 1 ). are pivotally mounted, and each mowing unit ( 10 , 10 ') of the side mowers ( 3 , 3 ') is pivotally connected to the outer end of the boom arm ( 4 , 4 '), and each side mower ( 3 , 3 ') each with its boom arm en ( 4 , 4 ') articulated by means of a piston-cylinder arrangement on the chassis ( 9 ) of the carrier vehicle ( 1 ) and thus connected to it from an approximately horizontal working position to an almost vertical transport position, characterized in that

• a) each side mower ( 3 , 3 ') a first actuator as a pressure medium cylinder ( 35 , 35 ') for pivoting a mowing unit ( 10 , 10 ') about the pivot axis ( 27 , 27 ') for transferring the side mower ( 3 , 3 ') from its working to its transport position and vice versa,
• b) each side mower ( 3 , 3 ') has a second actuator as Druckmittelzylin ( 36 , 36 ') for bridging the hinge joint connection ( 25 , 25 ') in such a way that the pivoting movement of the boom arms ( 4 , 4 ') about the pivot axis ( 27 , 27 ') can either be released or prevented,
• c) each side mower ( 3 , 3 ') has a support wheel ( 15 ) at the outer end of its longitudinal extension.

2. Self-propelled mower unit according to claim 1, characterized in that each side mower ( 3 , 3 ') comprises a boom ( 4 , 4 ') and a support structure ( 56 , 56 ') for articulated coupling of a mower unit ( 10 , 10 '), the boom ( 4 , 4 ') and support structure ( 56 , 56 ') are connected to each other by means of a hinge joint connection ( 26 , 26 '), and the support structure ( 56 , 56 ') on the outside with respect to the main median plane ( 41 ) is a support wheel ( 15 , 15 '). 3. Self-propelled mower unit according to claim 1 and 2, characterized in that the articulation of a support wheel ( 15 , 15 ') to the supporting structure ( 56 , 56 ') is designed as a pivot bearing ( 14 ) with a predominantly vertically oriented vertical axis ( 16 ) . 4. Self-propelled mower unit according to claim 1 and 2, characterized in that the articulated coupling of a mowing unit ( 10 , 10 ') to the support structure ( 56 , 56 ') consists of a link coupling ( 20 ), the coupling members ( 21 , 21 ' ) are articulated in their coupling points on the one hand to the supporting structure ( 56 , 56 ') and on the other hand to the mowing unit ( 10 , 10 '). 5. Self-propelled mower unit according to claim 1 and 4, characterized in that the coupling points of the coupling members ( 21 , 21 ') are designed as ball joint connections. 6. Self-propelled mower unit according to claim 1 and 4, characterized in that the coupling points between the supporting structure ( 56 , 56 ') and the coupling members ( 21 , 21 ') in the working position mowing operation based on the direction of travel (F) before the coupling points between the supporting structure ( 56 , 56 ') and the mowing unit ( 10 , 10 ') are arranged. 7. Self-propelled mower unit according to claim 1 and 4, characterized in that the coupling points between the supporting structure ( 56 , 56 ') and the coupling members ( 21 , 21 ') in the working position mowing operation based on the contact plane ( 42 ) above the coupling points between the supporting structure ( 56 , 56 ') and the mowing unit ( 10 , 10 ') are arranged. 8. Self-propelled mower unit according to claim 1 and 2 in conjunction with one or more of claims 3 to 7, characterized in that the coupling members ( 21 , 21 ') are bridged by means of prestressed spring elements ( 18 ), whereby part of the weight of the mowing unit ( 10 , 10 ') is supported on the one hand on the support wheel ( 15 , 15 ') and on the other hand on the extension arm ( 4 , 4 '). 9. Self-propelled mower unit according to claim 1 and 2 in connection with one or more of claims 2 to 8, characterized in that the coupling members ( 21 , 21 ') are bridged by means of pressurizable lifting cylinders ( 19 , 19 '), whereby the mower units ( 10 , 10 ') can be lifted from their working position from the ground, locked in a raised position and vice versa can be lowered from the raised position to the mowing operation working position. 10. Self-propelled mower unit according to claim 1, characterized in that the hinge joint connections ( 25 , 25 ') and ( 26 , 26 ') with their pivot axes ( 27 , 27 ') and ( 28 , 28 ') and the articulation points ( 38 , 38 ') and ( 40 , 40 ') are aligned with each other so that the pressure medium cylinders ( 35 , 36 ; 35 ', 36 ') predominantly in their longitudinal extension both in the working and in the transport position of the side mowers ( 3 , 3 ') are aligned horizontally with respect to the contact plane ( 42 ). 11. Self-propelled mower unit according to claim 1 and 10, characterized in that the hinge joint connections ( 25 , 25 ') and ( 26 , 26 ') with their pivot axis ( 27 , 27 ') and ( 28 , 28 '), the articulation points ( 38 , 38 ') and ( 40 , 40 ') are aligned with each other in such a way that the pressure medium cylinders ( 35 , 36 ); ( 35 ', 36 ') are aligned approximately parallel to each other both in the working and in the transport position. 12. Self-propelled mower unit according to claim 1, characterized in that the pressure medium cylinders ( 36 , 36 ') are arranged below the connecting line between the pivot axes ( 27 , 27 ') and the contact plane ( 42 ). 13. Self-propelled mower unit according to claim 1, characterized in that the pressure medium cylinders ( 35 , 35 ') above the connecting line between the pivot axes ( 27 , 27 ') and the contact plane ( 42 ) are arranged. 14. Self-propelled mower unit according to claim 1, characterized in that the articulation points ( 40 , 40 ') and the articulation points of the hinge joint connections ( 25 , 26 ); ( 25 ', 26 ') of a boom ( 4 , 4 ') have a fixed positional relationship to one another. 15. Self-propelled mower unit according to claim 1, characterized in that the distance between the pivot axis ( 27 ) and pivot point ( 40 ) or between pivot axis ( 27 ') and pivot point ( 40 ') is smaller than the distance between pivot axis ( 27 , 28 ) or ( 27 ', 28 '). 16. Self-propelled mower unit according to claim 1, characterized in that the support force (F ₄₀₎ or (F _'40) on the piston crown side clamped oil column of the pressure medium cylinder (36, 36') is supported. 17. Self-propelled mower unit according to claim 1 and 16, characterized net that the maximum hydrostatic pressure on the piston crown side clamped oil column is limited by a pressure relief valve. 18. Self-propelled mower unit according to claim 1 and 16, characterized net that the hydrostatic pressure of the piston bottom clamped Oil column is controlled controllably. 19. Self-propelled mower unit according to claim 1 and 16, characterized net that the hydrostatic pressure of the piston bottom clamped Oil column controllable is regulated in the sense of a controlled system. 20. Self-propelled mower unit according to claim 1 and 16, characterized net that the hydrostatic pressure of the piston bottom clamped Oil column controllable in the sense of a microprocessor controlled system is regulated. 21. Self-propelled mower unit according to claim 1, characterized in that the drive train for driving the mowing units ( 10 , 10 ', 10 '') a first transfer case ( 30 ) in the front region of the carrier vehicle ( 1 ) and a second transfer case ( 33 ) in middle area of the carrier vehicle ( 1 ) comprises such that the first transfer case ( 30 ) is the input gear for introducing the drive torque of all mowing units ( 10 , 10 ', 10 ''), and this transfer case ( 30 ) contains two output shafts, one Output shaft for driving the cutting unit ( 10 '') of the front mower ( 2 ) and, on the other hand, an output shaft for driving the second transfer case ( 33 ) for driving the mowing units ( 10 , 10 ') of the side mowers ( 3 , 3 '). 22. Self-propelled mower unit according to claim 1, characterized in that the transfer case ( 30 ) is arranged within the area between the front mower ( 1 ) and the front axle ( 5 ) of the carrier vehicle ( 1 ). 23. Self-propelled mower unit according to claim 1, characterized in that the transfer case ( 33 ) is arranged in relation to the direction of travel (F) between the front axle ( 5 ) and the rear axle ( 6 ) of the carrier vehicle ( 1 ).