the view in section in fig1 shows part of a radial compressor impeller 1 which comprises a wheel disk 2 which is fastened on a shaft ( not shown ). the radial compressor impeller 1 additionally comprises a cover disk 3 spaced apart from the wheel disk 2 . blades 4 , arranged distributed around the circumference , are arranged in the space between the wheel disk 2 and the cover disk 3 . the radial compressor impeller 1 is surrounded externally by a housing 5 which is shown only partially in fig1 . when the radial compressor impeller 1 , fastened on a shaft , is set in rotation , a gas which flows in axially in the direction shown by an arrow 6 can be accelerated and hence compressed radially and circumferentially . the gas passes over the radial compressor impeller 1 and flows into a flow duct 7 formed in the housing 5 . fig2 is a view in section of the radial compressor impeller 1 in fig1 along the line ii - ii . in fig2 , only the section through the blade 4 and a part of the wheel disk 2 is shown , which is designed integrally with the blade 4 . the blade 4 has an aerodynamic profile and comprises a suction side 8 and a pressure side 9 . the blade 4 has an approximately uniform thickness over its length . it can be seen in fig2 that the blade 4 has an end portion 10 which is spaced apart inward from the radial outer end 11 of the wheel disk 2 and from the cover disk 3 arranged approximately parallel thereto . accordingly , the blade 4 has a shortened radially outer end , compared with a conventional blade . the shortened blade end , which can be produced for example by machining , in particular by boring , effects a reduction in the pressure increase of the radial compressor impeller 1 . a radial compressor impeller can thus , for example after a bench test has been performed , be modified by boring in such a way that a predetermined pressure increase is obtained . as part of the production of a new radial compressor impeller , the end portion of the blade can of course also be formed directly , as shown in fig2 , i . e . with an end portion spaced apart from the outer end of the wheel disk . on the other hand , a pre - existing radial compressor impeller can be machined as described by boring in order to shorten the blades in the impeller outlet region . fig3 and 4 show a further exemplary embodiment of a radial compressor impeller , wherein — similarly to fig2 — only a cross - section through a blade is shown , and in fig4 a detail of the view in fig3 . the blade 12 shown in fig3 corresponds in principle to the blade 4 shown in fig2 . in particular , the blade 12 has an end portion 13 which is spaced apart inward from the radial outer end of the wheel disk 2 . as can be seen best in the enlarged view in fig4 , the end portion 13 of the blade 12 has a rounded edge 14 on the suction side 8 . the rounded edge 14 and the profile of the blade 12 on the suction side 8 merge gradually into each other , and at this point the tangential condition is fulfilled , i . e . the edge 14 and the edge of the profile of the blade 12 have the same tangent at the contact point . the rounded edge 14 is a segment of a circle with a radius r which corresponds to approximately 0 . 2 times the diameter d of the wheel disk 2 . it can be seen in fig4 that approximately one third of the ( unrounded ) width of the radial outer end portion 13 of the blade 12 is designed to be approximately parallel to the outer circumference of the wheel disk 2 , and that the rounded edge 14 adjoins said third . the outer edge of the end portion 13 and the rounded edge 14 enclose an angle which is somewhat greater than 90 °. the end portion 13 having the rounded edge 14 can be formed directly during the production of the blade 12 or the wheel disk 12 formed integrally with the blades , or alternatively the end portion 13 can also be produced subsequently by shaping a conventional blade on a lathe . the production of the rounded edge 14 can thus be viewed as “ rounding off ”, i . e . the edge usually present at this point is provided with a radius . fig5 and 6 show a further exemplary embodiment of a radial compressor impeller in the region of a blade , wherein fig5 shows a similar view to that in fig2 and 3 , and fig6 shows an enlarged detail of the blade shown in fig5 . the blade 15 shown in fig5 and 6 has , in conformity with the exemplary embodiment shown in fig2 , an end portion 16 which is spaced apart from the radial outer end 11 of the wheel disk 2 . the end portion 16 of the “ shortened ” blade 15 has a rounded edge 17 on the pressure side 9 . as can best be seen in fig6 , the rounded edge 17 and the outer contour of the blade 15 on the pressure side 9 merge gradually into each other . the tangential condition is fulfilled at the contact point . it is moreover shown in fig6 that the rounded edge 17 takes the form of a segment of a circle , the radius of which corresponds to approximately 0 . 2 times the diameter d of the wheel disk 2 . in other embodiments , a different radius can be provided and this can be , for example , between 0 . 15 d and 0 . 25 d . approximately one third of the width of the radial end portion 16 of the blade 15 is designed so that it is parallel to the outer circumference of the wheel disk 2 , and the rounded edge 17 , which thus extends over approximately two thirds of the ( notional ) width , adjoins said third . a conventional radial compressor impeller can be machined by boring the radial end portion of the blades and by rounding off on the pressure side in such a way that the radial compressor impeller shown in fig5 and 6 results . on the other hand , the shape of the blade 15 shown in fig5 and 6 can be formed , during the production of a new radial compressor impeller , directly by milling or a different manufacturing method . the different methods shown in the exemplary embodiments for influencing the flow conditions cause a reduction in pressure losses and reduction or prevention of undesired mixing of fluid in the region of the sides of the impeller with fluid in the region of the impeller outlet . in this way , the efficiency of the impeller stage is increased . the measures shown in the different described exemplary embodiments can also be combined with each other . in order to obtain a radial compressor impeller with defined properties , the modifications performed in the region of the end portion of the blades can also be modified . for example , a rounded edge can be provided on both the suction side and the pressure side . additionally , the remaining length of the blades in the radial direction or the distance from the outer edge of the wheel disk can also be adapted . although the invention has been illustrated and described in detail via the preferred exemplary embodiments , the invention is not limited by the disclosed examples and other variations can be derived by a person skilled in the art without going beyond the protective scope of the invention .