compensator spool 20 is shown in its middle actuation position in which it partially overlaps the fluid outlets a 1 a 2 leading to the hydraulic consumers v 1 and v 2 the fluid inlets e 1 and e 2 conversely are left open by the spool 20 by radial recesses 96 a permanent fluid connection is between e 1 and a 1 and between e 2 and a 2 the fluid outlets a 1 a 2 respectively are choked by the pressure compensator spool 20 depending on the position of travel of the pressure compensator spool 20 the fundamental switching possibilities for the pressure compensator 16 as shown in fig1 are achieved analogously since this pressure compensator structure is inherently known it will not be described further the embodiment shown in fig4 has been altered compared to the other embodiment shown in fig3 in that the damping orifices 92 are omitted the pressure compensator spool 20 in this embodiment in each of its positions of travel has spool ring surfaces 90 spaced apart from the pressure compensator housing 18 otherwise in terms of surface ratio the spool ring surfaces 90 opposite one another correspond to one another for the embodiments shown in fig3 and 4 for both embodiments the spool 20 is then essentially symmetrical in design in the modified embodiment shown in fig4 the fluid travels via the inlets e 1 e 2 as well as the radial recesses 96 and the respective annular gap 98 to the active spool ring surface 90 the valve block configuration according to fig5 shows that the entire valve device can be combined in one.