Mounting portion for an exhaust gas turbocharger, and exhaust gas turbocharger

Abstract

A bearing section for an exhaust turbocharger comprises a receiving opening for receiving a shaft of a rotor assembly of the exhaust turbocharger. The bearing section is designed for positioning bearing elements for supporting the shaft. A lubricant circuit is designed for supplying lubricant to the bearing elements. Lubricant channels are formed in the bearing section. In order to reduce a component temperature of the bearing section, a cooling jacket is provided, through which coolant can flow. The cooling jacket comprises a coolant channel, an inlet channel and an outlet channel. The inlet channel issues at a first opening point into the coolant channel and the outlet channel is connected at a second opening point to the coolant channel in such a way that a flow can pass therethrough. A rib is provided in the coolant channel.

Claims

1. A bearing section for an exhaust turbocharger, comprising a receiving opening (4) for receiving a shaft of a rotor assembly of the exhaust turbocharger (2), wherein the bearing section (1) is configured for positioning bearing elements for supporting the shaft, wherein a lubricant circuit is configured for supplying lubricant to the bearing elements, wherein lubricant channels are formed in the bearing section (1), wherein, in order to reduce a component temperature of the bearing section (1), a cooling jacket (9) is provided, through which a coolant can flow, wherein the cooling jacket (9) formed in the bearing section (1) comprises a circular coolant channel (10) formed in the bearing section (1), an inlet channel (11) for the coolant; which is connected in the bearing section (1) to the cooling jacket (9), and an outlet channel (12) for the coolant which is connected in the bearing section (1) to the cooling jacket (9), wherein the inlet channel (11) is connected to the coolant channel (10) at a first opening point (17), which is formed in the bearing section (1), and wherein the outlet channel (12) is connected to the coolant channel (10) at a second opening point (18), which is formed in the bearing section (1), and wherein a first rib (15) is provided in the coolant channel (10) opposite the first opening point (17) to divide the coolant entering through the inlet channel (11) into a first part flowing through a first side of the coolant channel and a second part flowing through a second side of the circular coolant channel, and wherein a second rib (16) is arranged opposite the second opening point (17) at which the first part of the coolant and the second part of the coolant are combined to exit the coolant channel (10) through the outlet channel (12).

2. The bearing section as claimed in claim 1, wherein the rib (15; 16) has a curved rib surface (19).

3. The bearing section as claimed in claim 1, wherein the rib (15; 16) has a trapezoidal cross-section.

4. The bearing section as claimed in claim 1, wherein the rib (15; 16) has a rib wall (20), and wherein a transition (24) is formed between the rib wall (20) and a coolant channel bottom (21), said transition being curved.

5. The bearing section as claimed in claim 1, wherein the opening point (17; 18) has a curved circumferential edge (23).

6. The bearing section as claimed in claim 1, wherein the cooling jacket (9) is produced with the aid of a dead mold.

7. An Exhaust turbocharger comprising a bearing section for receiving a rotor assembly of the exhaust turbocharger, wherein the bearing section is configured as claimed in claim 1.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 shows a longitudinal sectional view of a bearing section and an exhaust gas conducting section of an exhaust turbocharger.

(2) FIG. 2 shows a perspective sectional view of the bearing section.

(3) FIG. 3 shows a perspective sectional view of a detail of the bearing section in the region of a cooling water inlet.

(4) FIG. 4 shows a perspective sectional view of a detail of the bearing section in the region of a rib on the cooling water inlet.

(5) FIG. 5 shows a perspective sectional view of a detail of the bearing section in the region of a rib on a cooling water outlet.

(6) FIG. 6 shows a perspective view of a core of a water jacket of the bearing section.

DETAILED DESCRIPTION

(7) A bearing section 1—designed as shown in FIG. 1—of an exhaust turbocharger 2 comprises a receiving opening 4, which extends along a longitudinal axis 3, for receiving a shaft, not illustrated in greater detail, of a rotor assembly, not illustrated in greater detail. The receiving opening is also designed to receive bearing elements, not illustrated in greater detail, supporting the shaft. The bearing elements are lubricated with the aid of a lubricant which flows through the bearing section and which can flow into the bearing section 1 and out of the bearing section 1 via a lubricant circuit 13.

(8) The bearing section 1 is arranged adjoining an exhaust gas conducting section 5 of the exhaust turbocharger 2. The exhaust gas conducting section 5 is designed to receive a turbine wheel, not illustrated in greater detail, of the rotor assembly in a wheel chamber 6. The wheel chamber is formed downstream of a spiral channel 7 of the exhaust gas conducting section 5, wherein the spiral channel 7 is configured such that a flow can pass therethrough with the wheel chamber 6. Formed upstream of the spiral channel is an inflow channel, not illustrated in greater detail, of the exhaust gas conducting section 5 which is provided for the entry of a fluid into the exhaust gas conducting section 5, in general exhaust gas of an internal combustion engine, not illustrated in greater detail. Arranged downstream of the wheel chamber 6 is an outlet channel 8 which is connected to the wheel chamber 6 such that a flow can pass therethrough.

(9) The exhaust gas conducting section 5 is connected to an internal combustion engine, not illustrated in greater detail, so that the exhaust gas of the internal combustion engine can enter into the spiral channel 7 via the inlet channel in order to act upon the turbine wheel. During operation of the internal combustion engine, the component temperature of the exhaust gas conducting section increases by reason of the exhaust gas flowing therethrough. During operation of the internal combustion engine, the bearing section 1 likewise has an increased component temperature because it is formed adjoining the exhaust gas conducting section 5 and therefore is acted upon indirectly by the hot exhaust gas mass flow.

(10) The bearing section 1 is cooled by a cooling jacket 9 which is designed such that it at least partially encompasses the receiving opening 4. The cooling jacket 9 is positioned for cooling in particular the bearing, in particular a radial bearing in the form of a slide bearing, located in proximity to the exhaust gas conducting section 5.

(11) The cooling jacket 9 comprises not only a fully formed, i.e. in other words a circular, coolant channel 10 but also an inlet channel 11 and an outlet channel 12, wherein both channels 11, 12 are connected to the coolant channel 10 such that a flow can pass therethrough. The inlet channel 11 is provided for introducing the coolant into the coolant channel 10. The outlet channel 12 serves to discharge the coolant which, after being heated, can be supplied to a cooling circuit, in which it is then cooled to its cooling temperature as it enters via the inlet channel 11.

(12) In order to fasten attachment elements, not illustrated in greater detail, for entry of the coolant into the inlet channel 11 or for exit of the coolant via the outlet channel 12, the bearing section 1 has in each case a fastening element 14 in the form of a bore.

(13) FIG. 2 illustrates the bearing section 1 in a perspective sectional view in a cross-section, wherein it is illustrated in the viewing direction of the exhaust gas conducting section 5. The coolant channel 10 has a first rib 15 and a second rib 16 which are arranged opposite one another. The ribs 15, 16 are arranged at an opening point of the inlet channel 11 and the outlet channel 12 respectively. In other words, this means that between the inlet channel 11 and the coolant channel 10 a first opening point 17 is formed, opposite which downstream the first rib 15 is arranged, and between the outlet channel 12 and the coolant channel 10 a second opening point 18 is formed, opposite which upstream the second rib 16 is arranged.

(14) Each rib 15, 16 is curved in a flow-optimized manner, wherein a rib surface 19 opposite the opening points 17, 18 is curved as is a transition 24 between rib walls 20 and a coolant channel bottom 21. Furthermore, each rib 15, 16 has a trapezoidal cross-section 25.

(15) FIG. 3 illustrates a perspective sectional view of a detail of the bearing section 1 in the region of the coolant inlet, wherein the inlet channel 11 is illustrated in section. It is particularly apparent from FIG. 3 that the first rib 15 is arranged opposite the first opening point 17 which connects the inlet channel 11 to the coolant channel 10 such that a flow can pass therethrough.

(16) FIGS. 4 and 5 illustrate exemplary flow threads of the coolant in the region of the first rib 15 and the second rib 16 respectively. Starting from the inlet channel 11, the coolant is guided onto a wall 26 of the coolant channel 10, wherein it is divided into two parts with the aid of the first rib 15. This promotes a continuous inflow of coolant into the coolant channel 10 without the creation of any turbulence. Likewise, the coolant can be diverted out of the coolant channel 10 in an improved manner with the aid of the second rib 16.

(17) The coolant 9 is produced in the form of a so-called dead mold, i.e. in other words with a core 22 which can be used only once because it is destroyed after cooling of the bearing section 1. FIG. 6 illustrates the core 22 for the cooling jacket 9, wherein the ribs 15, 16 are shown in the form of indentations. The core 22 is formed as a negative of the cooling jacket 9. For improved inflow and outflow of the coolant into and out of the coolant channel 10, the opening points 17, 18 are also provided in a flow-optimized manner with rounded circumferential edges 23 to ensure that no sharp edges which can be edges which break up a flow are formed.

(18) The coolant channel 10 is to be designed so as to be adapted to the requirements of cooling the bearing section 1, wherein the position, height and radii of the ribs 15, 16 are to be configured in an optimized manner in terms of flow technology.