Oil thrower for an exhaust-gas turbocharger

An oil thrower for an exhaust-gas turbocharger. The oil thrower has at least one first ring shoulder and one second ring shoulder. Formed between these two ring shoulders is an oil collection space. The lubricant is collected in this oil collection space at low rates of rotation. The oil thrower prevents the lubricant from ending up on the turbine wheel.

DETAILED DESCRIPTION OF THE DRAWINGS Depicted in FIG. 1 is a section drawing of exhaust-gas turbocharger 1 on the turbine side. The general function and the structure of an exhaust-gas turbocharger is assumed to be known. In FIG. 1, a shaft 2 is inextricably connected to turbine wheel 3 , e.g., by friction welding. A bearing 5 on a bearing housing 7 supports shaft 2 . Bearing 5 is supplied with pressurized lubricant via a lubricant port 6 . A depressurization chamber 8 is partitioned from the turbine wheel 3 by a housing cover 10 . A piston ring 12 is provided for sealing between housing cover 10 and shaft 2 . In addition, depicted in FIG. 1 between housing cover 10 and turbine wheel 3 is a jet disk 9 . Arranged between bearing housing 7 and housing cover 10 is an oil thrower 4 . Oil thrower 4 is affixed to shaft 2 so as to rotate with it, e.g., by a driving fit or a form closure. Due to the high temperatures in this area, oil thrower 4 is made out of steel. When the exhaust-gas turbocharger is standing, oil thrower 4 forms a barrier against the area of piston ring 12 . The arrangement has the following functionality at high rates of rotation: The lubricant emerging from bearing 5 is picked up by oil thrower 4 and, because of the centrifugal force, is hurled in the direction of housing cover 10 . Then the lubricant runs along housing cover 10 to a discharge groove 11 . The lubricant is collected in this discharge groove 11 and from there goes into depressurization chamber 8 . The direction of flow of the lubricant is marked in FIG. 1 using arrows. The arrangement shows the following functionality at low rates of speed &lsqb;rpm&rsqb;: The lubricant escaping from bearing 5 is radially conducted out on the outer side of oil thrower 4 . Further explanation is now given with reference to FIG. 2 , which shows the first design type of the oil thrower 4 . The lubricant arrives via a first ring shoulder 14 in an oil collection space 16 . The oil collection space 16 is formed by a first ring shoulder 14 , a second ring shoulder 15 and a part of a hub 13 of oil thrower 4 . The lubricant is picked up in this oil collection space. In this way, the lubricant is prevented from being entrained by the air because of the pressure difference between depressurization chamber 8 and turbine wheel 3 . The lubricant goes from this oil collection space 16 into depressurization chamber 8 . Depicted in FIG. 3 is a second design type of the oil thrower 4 . In this design, first ring shoulder 14 has a diameter d 1 and second ring shoulder 15 has a diameter d 2 . The diameters are configured differently. Preferably, diameter d 2 is the greater of the two. The description of FIG. 1 or FIG. 2 applies to the functionality in this case. Depicted in FIG. 4 is a third design type of oil thrower 4 . In this design, oil thrower 4 is made up of two individual disks whose hub, reference number 13 , is adjacent to a connection surface 17 . The two individual oil throwers are inextricably connected to each other on this connection surface 17 . Depicted in FIG. 5 is a fourth design type of oil thrower 4 . Depicted in this oil thrower 4 are three ring shoulders, reference numbers 14 , 15 , and 18 . Arranged between these ring shoulders are two oil collection spaces 16 . The description of FIG. 1 or FIG. 2 applies to the functionality in this case. A practically complete oil sealing between bearing housing 7 and turbine wheel 3 has been achieved through this invention. As a result, no lubricant can come from bearing housing 7 and end up on hot turbine wheel 3 and change into coke there. The formation of a coating on the turbine wheel is thus effectively prevented. As is generally known, formation of a coating on turbine wheel 3 can lead to imbalance and in the extreme case to a breakage of shaft 2 . Coking in the area of piston ring 12 can lead to jamming and thus to a partial damage to the shaft. Overall, the operational reliability of the exhaust-gas turbocharger is thus increased. The foregoing disclosure has been set forth merely to illustrate the invention and is not intended to be limiting. Since modifications of the disclosed embodiments incorporating the spirit and substance of the invention may occur to persons skilled in the art, the invention should be construed to include everything within the scope of the appended claims and equivalents thereof.