the harvesting attachment 10 described above with reference to fig1 is illustrated in greater detail in fig2 . the harvesting attachment 10 comprises a corn picker that is arranged on the feeder house of a combine 22 . the central section 12 and the side sections 14 and 16 , respectively , comprise four and two known gathering and picking devices with gathering elements that rotate about the horizontal axis and draw plants into a picking gap during operation of the combine . the crop ( ears of corn ) from the plants is fed to the combine 22 . in order to reduce the width of the harvesting attachment 10 when driving on public roads the attachment can be folded as illustrated in fig2 b . two hydraulic cylinders 24 that extend transverse to the driving direction of the combine 22 are coupled to the upper side of the frame of the central section 12 for pivoting the side sections 14 and 16 about pivot shafts 18 that are rigidly attached to the central section and extend in the driving direction . the piston rods of the hydraulic cylinders 24 are connected to the upper sides of frames of the side sections 14 and 16 by means of mounting supports 26 . when acted upon by the hydraulic cylinders 24 , the mounting supports 26 convert the linear movements of the hydraulic cylinders 24 into pivoting movements , so that the side sections 14 and 16 are pivoted upward and inward about the pivot shafts 18 , which is shown in fig2 b . in the operating position ( fig2 a ), the side sections 14 and 16 are aligned parallel to the central section 12 and , for example , are rigidly connected to it due to gravitational force and / or appropriate action of the hydraulic cylinder 24 and / or latching elements . the hydraulic cylinders 24 consist of double - action cylinders , since lifting forces need to be generated at the beginning of each pivoting movement ( from the operating position into the transport position and vice versa ). as mentioned above , pivoting forces that vary over time need to be generated when the side sections 14 and 16 of the harvesting attachment 10 are pivoted . in fig3 these pivoting forces are illustrated in the form of the line 20 that represents the progression of forces as a function of the travel of a hydraulic cylinder 24 causing the pivoting movement . when one of the side sections 14 or 16 is raised from the operating position ( fig1 a , a in fig3 ), the piston rod chamber 28 ( see fig4 ) of the hydraulic cylinder 24 is pressurized . a relatively high force needs to be generated initially which subsequently decreases again after a maximum is reached , with said force being reduced to zero in the equilibrium position shown in fig1 b ( b in fig3 ), and subsequently assumes negative values . shortly before the transport position ( fig1 c , c in fig3 ) is reached , the force , which is no longer compressive but rather tensile because the respective side section 14 or 16 is pulled downward by gravity , reaches another maximum and then slightly decreases again . the piston chambers 30 of the hydraulic cylinders 24 are pressurized analogously when the side sections 14 and 16 are moved from the transport position into the operating position . increasing forces initially need to be generated , which soon decrease and are transformed from compressive forces into tensile forces after the elements have passed the equilibrium position shown in fig1 b . the line 20 corresponds to the forces to be generated by conventional adjusting drives . in conventional harvesting attachments , the two force maxima determine the dimensions and the operating speed of the hydraulic cylinders 24 . according to the invention , springs 34 and 36 are arranged within the housing 32 of the hydraulic cylinders 24 in order to allow the utilization of smaller hydraulic cylinders 24 . a first coil spring 34 is arranged between the end of the housing 32 of the hydraulic cylinder 24 on the piston rod side and the piston 38 , and a second coil spring 36 is arranged between the piston 38 and the bottom 40 of the housing 32 of the hydraulic cylinder 24 . the springs 34 and 36 exert forces upon the piston 38 which tend to move the piston into its central position , which approximately corresponds to the equilibrium or intermediate position of the side sections 14 and 16 shown in fig1 b . the forces exerted upon the piston 38 by the springs 34 and 36 are illustrated in the form of the line 40 in fig3 . the line 42 characterizes the resultant force profile . the springs 34 and 36 lower the forces to be generated by the piston 38 significantly in comparison with instances in which no springs 34 and 36 are provided . this means that the hydraulic cylinders 24 can have smaller dimensions and that faster pivoting speeds can be achieved . [ 0025 ] fig3 and 4 show that , when the piston 38 is in the position a which corresponds to the position shown in fig1 a , the spring 34 biases the piston 38 in the direction of the position b that corresponds to the position shown in fig1 b . in this situation , the spring 36 remains ineffective . analogously , the spring 36 prestresses the piston 38 in the direction of the position b if it is in the position c . in this case , the spring 34 remains ineffective . this means that the forces to be generated by the piston 38 are significantly reduced . the dimensions of the springs 34 and 36 may also be chosen such that they exert forces upon the piston 38 in the equilibrium position . however , in this case these forces balance one another . one advantage of this can be seen in the fact that a steeper force increase can be attained . it should also be noted that the total forces initially appearing in the operating position and the transport position which are directed oppositely to the further force progression can be counteracted by choosing the dimensions of the springs 34 and 36 differently and / or by pressurizing upon the hydraulic cylinders 24 . the springs 34 and 36 could also be arranged outside the housing 32 of the hydraulic cylinders 24 . it would also be conceivable to utilize only a single spring that can be compressed and extended , and the idle position of which at least approximately coincides with the equilibrium position ( fig1 b ). having described the illustrated embodiment , it will become apparent that various modifications can be made without departing from the scope of the invention as defined in the accompanying claims .
an adjusting device for a movable element of a harvesting attachment is provided with an adjusting drive for moving the movable element between a first operating position and a second transport position in which it is raised relative to the first operating position . a spring biases the movable element in the direction of the second transport position .