DE102019101868A1 - turbocharger - Google Patents

Abstract

Turbocharger, with a turbine (2) for expanding a first medium, the turbine (2) having a turbine housing and a turbine rotor (5), with a compressor for compressing a second medium using in the turbine (2) when the energy obtained from the first medium, the compressor having a compressor housing and a compressor rotor coupled to the turbine rotor (5) via a shaft (8), with a bearing housing (9) arranged between the turbine housing and the compressor housing and in which the shaft (8) a bearing (18) facing the turbine (2) is mounted, with an end plate (22) which is located on a side of a bearing ring or a bearing bush (19) of the bearing (18) facing the turbine (2) facing the turbine (2) ) to the bearing ring or the bearing bush (19). A swirling space (24) open in the direction of the bearing ring or the bearing bush (19) is located in the end disk (22) on an axial surface (23) facing the bearing ring or the bearing bush (19) of the bearing (18) facing the turbine (2). brings in, the oil, which emerges from a lubrication gap (20) of the bearing (18), collects and drains.

Description

The invention relates to a turbocharger.

The basic structure of a turbocharger is known to those skilled in the art. A turbocharger has a turbine in which a first medium is expanded. Furthermore, a turbocharger has a compressor in which a second medium is compressed, using the energy obtained in the turbine when the first medium is expanded. The turbine of the turbocharger has a turbine housing and a turbine rotor. The turbocharger's compressor has a compressor housing and a compressor rotor. A bearing housing is positioned between the turbine housing of the turbine and the compressor housing of the compressor, the bearing housing being connected on the one hand to the turbine housing and on the other hand to the compressor housing. A shaft is mounted in the bearing housing, via which the turbine rotor is coupled to the compressor rotor.

From the DE 10 2010 038 527 A1 a turbocharger with a compressor, a turbine and a bearing housing is known. A shaft, via which the turbine rotor is coupled to the compressor rotor, is mounted in the bearing housing, specifically via a plurality of slide bearings. A slide bearing, which serves to support the shaft in the bearing housing, faces the turbine. Another slide bearing, which serves to support the shaft in the bearing housing, faces the compressor. At the bearing facing the turbine, there is an end plate, which, when the plain bearing has a floating bearing ring or a floating bearing bush, limits the axial displacement of the bearing ring or the bearing bush in the direction of the turbine, and which if the Bearing bush or the bearing ring is fixed, serves to hold the bearing bush or the bearing ring.

An essential requirement with regard to the operational safety of a turbocharger is the oil-tightness of the bearing of the shaft, in particular towards the turbine wheel of the turbine. Especially on the hot turbine side there is a risk that oil escaping from the bearing housing can ignite. For this reason, shaft seals for bearing the shaft in the bearing housing are essential components for the operational safety of turbochargers.

There is therefore a need for a turbocharger in which an oil-tightness can be provided safely and reliably for mounting the shaft in the bearing housing, in particular adjacent to the turbine, using simple means. Proceeding from this, the object of the present invention is to create a new type of turbocharger.

This object is achieved by a turbocharger according to claim 1. According to the invention, a swirling space which is open in the direction of the bearing ring or the bearing bush is introduced into the end plate on an axial surface facing the bearing ring or the bearing bush of the turbine-facing bearing and collects and drains off the oil which escapes from a lubricating gap in the bearing. In the sense of the invention, it is proposed that the end plate, which adjoins the bearing ring or the bearing bush of the bearing of the shaft facing the turbine adjacent to the turbine, has a swirling space which is open in the direction of the bearing ring or the bearing bush. Oil that escapes from the lubrication gap of the bearing can enter the swirling space that is open in the direction of the bearing ring or the bearing bush, where it can be collected and calmed down. The swirl chamber drains collected and calmed oil, in the direction of an oil drain in the area of the bearing housing. This can ensure oil tightness for the bearing of the shaft in the bearing housing, in particular adjacent to the turbine. The operational safety of the turbocharger can thus be increased with simple means.

According to a further development of the invention, the swirling space of the cover disk, which is open in the direction of the bearing ring or the bearing bush, is delimited on one side facing away from the bearing ring or the bearing bush by a closed axial wall and on a radially outer side by a closed radial wall. The swirling space of the cover plate, which is open in the direction of the bearing ring or the bearing bush, is delimited on one side on a radially inner side facing the shaft by a web which, starting from the axial wall, defines the open swirling space on the side facing away from the bearing ring or the bearing bush is limited, extends in the axial direction to the axial surface facing the bearing ring or the bearing bush and ends at a distance from this axial surface. Such a contouring of the swirling space of the cover plate, which is open in the direction of the bearing ring or the bearing bush, is particularly preferred in order to reliably catch and calm oil escaping from the lubricating gap of the bearing.

The open swirling space is preferably contoured in such a way that an extension of a chamfer of the bearing ring or the bearing bush facing the swirling space intersects the closed axial wall. These details also serve to safely catch and soothe the oil that escapes from the lubrication gap of the bearing.

The web, which delimits the swirling space radially on the inside, defines a sealing gap to the shaft, the axial length of which is preferably between the 0.1 times and 0.7 times the axial thickness of the cover plate and / or its radial width is preferably between 2 times and 20 times the radial bearing clearance between the bearing ring or the bearing bush and the shaft. These details of the cover plate, namely the web that delimits the swirling space radially on the inside, are advantageous in order to reliably collect the oil that leaves the lubrication gap.

• 1 einen Querschnitt durch einen Turbolader,
• 2 ein Detail eines erfindungsgemäßen Turboladers,
• 3 ein Detail der 2, und
• 4 ein weiteres Detail eines erfindungsgemäßen Turboladers.

Preferred developments of the invention result from the subclaims and the following description. Exemplary embodiments of the invention are explained in more detail with reference to the drawing, without being restricted to this. It shows:

• 1 a cross section through a turbocharger,
• 2nd a detail of a turbocharger according to the invention,
• 3rd a detail of the 2nd , and
• 4th another detail of a turbocharger according to the invention.

1 shows the basic structure of a turbocharger 1 . A turbocharger 1 has a turbine 2nd to relax a first medium, in particular to relax exhaust gas from an internal combustion engine. It also has a turbocharger 1 via a compressor 3rd for compressing a second medium, in particular charge air, using in the turbine 2nd energy gained during the relaxation of the first medium.

The turbine 2nd has a turbine housing 4th and a turbine rotor 5 . The compressor 3rd has a compressor housing 6 and a compressor rotor 7 . The compressor rotor 7 is with the turbine rotor 5 over a wave 8th coupled in a bearing housing 9 is stored, the bearing housing 9 between the turbine housing 4th and the compressor housing 5 positioned and both with the turbine housing 4th and the compressor housing 5 connected is.

The turbine housing 4th the turbine 2nd includes an inflow housing 11 and an outflow housing 12th . About the inflow housing 11 can do that in the area of the turbine 2nd first medium to relax the turbine rotor 5 are fed. Via the outlet housing 12th flows in the area of the turbine rotor 5 relaxed first medium from the turbine 2nd path.

The turbine housing 4th includes in addition to the inflow housing 11 and the outflow housing 12th an insert 13 , the insert 13 especially in the area of the inflow housing 11 runs, namely adjacent to the turbine rotor 5 radially outside adjacent to blades 14 of the turbine rotor 5 .

The turbine housing 4th also includes a nozzle ring 15 . The nozzle ring 15 is also referred to as a turbine nozzle.

Furthermore shows 1 in the connection area of the inflow housing 11 and bearing housing 9 a sealing cover 16 . The sealing cover 16 is also known as a bearing housing cover or heat shield.

The inflow housing 11 the turbine 2nd is with the bearing housing 9 via a fastening device 17th connected, which is preferably designed as a claw. In this connection area between the bearing housing 9 and inflow housing 11 the turbine becomes a radially outer portion of the sealing cover 15 clamped. The nozzle ring is preferably also clamped with a section in this connection area.

As already stated, the turbine rotor 5 and the compressor rotor 7 over the wave 8th coupled that in the bearing housing 9 is stored. To support the shaft 8th in the bearing housing 9 serve bearings, namely one of the turbine 2nd facing bearing and one to the compressor 3rd bearing facing the shaft 8th to be stored along their axial extent via these bearings in at least two axial positions. 2nd shows a section of a turbocharger in the area of a bearing 18th which the bearing of the shaft 8th in the bearing housing 9 on one of the turbine 2nd or the turbine wheel 5 the turbine 2nd facing side of the shaft 8th or the bearing housing 9 serves.

In this the turbine or the turbine wheel 5 facing camp 18th is a radial slide bearing, which has a bearing ring or a bearing bush 19th includes. Between the bearing ring or the bearing bush 19th and the wave 8th is a lubrication gap 20 trained of a hole 21 in the bearing housing 9 can be supplied with oil.

To the bearing ring or the bearing bush 19th of the camp 18th closes on the of the turbine 2nd or the turbine wheel 5 facing side a lens 22 on. Then when the bearing ring 19th or the bearing bush of the bearing 18th in the bearing housing 9 is taken up floating, limits the lens 22 the axial mobility of the bearing ring or the bearing bush 19th . In the case of a fixed bearing ring or bush 19th holds the lens 22 the bearing ring or the bearing bush 19th fixed in the axial direction.

From the lubrication gap 20 between the bearing ring 19th or the bearing bush and the shaft 8th oil can escape during operation, even in Direction to the turbine wheel 5 . To the oil tightness for the bearing of the shaft 8th in the bearing housing 9 especially adjacent to the turbine 2nd To ensure is according to the invention in the lens 22 , which is made in one piece or in one piece, on one of the bearing ring or the bearing bush 19th facing axial surface 23 one towards the bearing ring or the bearing bush 19th open swirl space 24th educated. In this swirl room 24th can oil coming from the lubrication gap 20 in the area of the swirl room 24th facing bevel 25th of the bearing ring or the bearing bush 19th emerges, caught and in the swirl room 24th be reassured.

The swirl room 24th rotates in the circumferential direction and has an oil drain opening at a circumferential position 26 on which then in the swirl room 24th trapped and calmed oil towards an oil drain of the bearing housing 9 can be derived. This oil drain opening 26 has an opening angle β in the circumferential direction between 5 ° and 90 °.

As already stated, the swirling space is 24th towards the bearing ring 1 or the bearing bush 19th of the camp 18th open. This in the direction of the bearing ring or the bearing bush 19th open swirl space 24th is on one of the bearing ring or the bearing bush 19th opposite side through a closed axial wall 27 and radially outside through a closed radial wall 28 limited. Starting from the axial wall 27 that the swirl space 24th on the of the bearing ring or the bearing bush 19th of the camp 18th facing away from the side, extends in the direction of the bearing ring or the bearing bush 19th a footbridge 29 which is the swirl space 24th radially inward adjacent to the shaft 8th limited in sections and which at a distance in front of the bearing ring or the bearing bush 19th facing axial surface 23 the lens 22 ends. The jetty 29 therefore has an axial length that is less than the axial thickness or width of the lens 22 .

The jetty 29 which is a sealing gap 30th to the wave 8th defined, has an axial length that is between 0.1 times and 0.7 times the axial thickness or axial width of the lens 22 is.

The radial width of the sealing gap 30th between the jetty 29 the lens 22 and the wave 8th is between 2 times and 20 times the radial bearing clearance between the bearing ring 19th of the camp 18th and the wave 8th . To get that out of the lubrication gap 20 of the camp 18th escaping oil in the area of the swirling space 24th that towards the bearing ring or the bearing bush 19th is openly designed to optimally collect, is the swirling space 24th in particular contoured such that an extension of that chamfer 25th of the bearing ring or the bearing bush 19th going towards the swirl space 24th diverges, the closed axial wall 27 that cuts the swirl space 24th on the of the bearing ring or the bearing bush 19th facing away from the side.

In 3rd is this extension of the chamfer 25th shown in dashed lines. The extension of the chamfer 25th cuts the closed axial wall 27 especially in the transition area to the closed radial wall 28 which the swirl space 24th limited radially outside.

The invention therefore proposes that in the end cover 22 that is between the turbine wheel 5 and the camp 18th which is the shaft 8th on the of the turbine 2nd facing side in the bearing housing 9 bearings, one in the direction of the bearing ring or the bearing bush 19th of the camp 18th open swirl space 24th is introduced. Oil coming out of the lubrication gap 20 between the bearing ring or the bearing bush 19th of the camp 18th and the wave 8th emerges, reaches the area of the swirling space 24th , is caught there and calmed down and over the circumferential swirling space 24th towards the oil drain opening 26 the lens 22 guided. In this way, the oil collected can be discharged in a defined manner.

The swirl room 24th is radially inside through the web 29 limited, radially outside by the radial wall 28 and on that of the bearing ring or the bearing bush 19th opposite side through the axial wall 27 . An extension of the chamfer preferably cuts 25th of the bearing ring or the bearing bush 19th this axial wall 27 . Adjacent to the bearing ring or the bearing bush 19th is the swirl space 24th open.

In the area of the bearing that the shaft 8th at the the compressor 3rd supports facing side, a cover plate, as described above, can also be arranged.

Reference list

1

turbocharger

2nd

turbine

3rd

compressor

4th

Turbine casing

5

Turbine rotor

6

Compressor housing

7

Compressor rotor

8th

wave

9

Bearing housing

10th

silencer

11

Inflow housing

12th

Outlet housing

13

Insert

14

Blade

15

Nozzle ring

16

Sealing cover

17th

Fastening device

18th

camp

19th

Bearing ring / bearing bush

20

Lubrication gap

21

drilling

22

Cover lens

23

Axial surface

24th

Swirling space

25th

chamfer

26

Oil drain opening

27

Axial wall

28

Radial wall

29

web

30th

Radial gap

QUOTES INCLUDE IN THE DESCRIPTION

This list of documents listed by the applicant has been generated automatically and is only included for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Patent literature cited

• DE 102010038527 A1 [0003]

Claims (10)

Turbocharger (1), with a turbine (2) for expanding a first medium, the turbine (2) having a turbine housing (4) and a turbine rotor (5), with a compressor (3) for compressing a second medium using Energy obtained in the turbine (2) when the first medium relaxes, the compressor (3) having a compressor housing (6) and a compressor rotor (7) coupled to the turbine rotor (5) via a shaft (8), with one between the Turbine housing (4) and the compressor housing (6) arranged bearing housing (9), in which the shaft (8) is mounted via a bearing (18) facing the turbine (2), with an end plate (22) which is located on one of the Turbine (2) facing side of a bearing ring or a bearing bush (19) of the bearing (18) facing the turbine (2) connects to the bearing ring or the bearing bush (19), characterized in that in the end plate (22) on one of the bearing ring or the bearing bush (19) of the A turbulence chamber (24), which is open towards the bearing ring or the bearing bush (19), is introduced into the bearing (18) facing the turbine (2), the oil, which emerges from a lubrication gap (20) of the bearing (18) , catches and derives. Turbocharger after Claim 1 , characterized in that the end plate (22) is integrally formed. Turbocharger after Claim 1 or 2nd , characterized in that the swirling space (24) rotates in the circumferential direction and has an oil drain opening (26) at a circumferential position. Turbocharger after Claim 3 , characterized in that the oil drain opening (26) has an opening angle in the circumferential direction between 5 ° and 90 °. Turbocharger according to one of the Claims 1 to 4th , characterized in that the swirling space (24) of the cover plate (22), which is open in the direction of the bearing ring or the bearing bush (19), on a side facing away from the bearing ring or the bearing bush (19) through a closed axial wall (27) and on a radial one outer side is limited by a closed radial wall (28). Turbocharger after Claim 5 , characterized in that the open swirling space (24) is contoured such that an extension of a chamfer (25) of the bearing ring or the bearing bush (19) facing the swirling space (24) intersects the closed axial wall (27). Turbocharger after Claim 6 , characterized in that the extension of the chamfer (25) of the bearing ring (19) or the bearing bush (19) facing the swirling space (24) intersects the closed axial wall (27) in the transition region to the closed radial wall (28). Turbocharger according to one of the Claims 1 to 7 , characterized in that the swirling space (24) of the cover disk (22) which is open in the direction of the bearing ring or the bearing bush (19) is delimited by a web (29) on a radially inner side facing the shaft (8). Turbocharger after Claim 8 , characterized in that the web (29), starting from the axial wall (27) which delimits the open swirling space (27) on the side facing away from the bearing ring or the bearing bush (19), towards the bearing ring or the bearing bush (19) facing axial surface (23) extends and ends at a distance in front of this axial surface (23). Turbocharger after Claim 8 or 9 , characterized in that the web (29) defines a sealing gap (30) to the shaft (8), the axial length of which is between 0.1 times and 0.7 times the axial thickness of the cover plate (22) and / or whose radial width is between 2 times and 20 times the radial bearing clearance between the bearing ring (19) or the bearing bush and the shaft (8).

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