WO2015179353A1

WO2015179353A1 - Exhaust-gas turbocharger

Info

Publication number: WO2015179353A1
Application number: PCT/US2015/031503
Authority: WO
Inventors: Marc GUGAU; Alessio SCHERI
Original assignee: Borgwarner Inc.
Priority date: 2014-05-20
Filing date: 2015-05-19
Publication date: 2015-11-26
Also published as: JP2017516012A; CN106460520B; US20170107896A1; KR102301070B1; DE112015001237T5; KR20170007346A; DE112015001237B4; CN106460520A; US10280833B2; JP6572243B2

Abstract

The invention relates to an exhaust-gas turbocharger (1), preferably for a passenger vehicle, comprising a compressor (2) having a compressor wheel (3), a turbine (4) having a turbine wheel (5) and a turbine housing (6), a shaft (7), which connects the compressor wheel (3) to the turbine wheel (5), and a number of S 2 of channels (13, 14), which are formed in the turbine housing (6) and are intended for guiding the exhaust gas onto the turbine wheel (5), wherein an axial direction (8) is defined along the shaft (7), from the compressor (2) to the turbine (4), a radial direction (9) is defined perpendicularly to the axial direction (8), and a circumferential direction (10) is defined around the axial direction (8), counter to the direction of rotation of the turbine wheel (5), wherein each channel (13, 14) directs flow against the turbine wheel (5) over the entire width of the latter, as seen in the axial direction (8), and over a segment, as seen in relation to the circumferential direction (10), wherein the turbine wheel (5) comprises a number of Z 10 turbine blades (12), and wherein the turbine blades (12) are defined in the form of main blades (22) and intermediate blades (23), wherein the intermediate blades (23), at least at their hub-side ends (24), do not extend as far toward the turbine outlet, as seen in the axial direction (8), as the main blades (22).

Description

EXHAUST-GAS TURBOCHARGER DESCRIPTION

The present invention relates to an exhaust-gas turbocharger. It presents, in particular, a compact exhaust-gas turbocharger which is used in passenger vehicles.

In exhaust-gas turbochargers according to the prior art, exhaust gas is directed onto a turbine wheel of the exhaust-gas turbocharger via at least one volute. It is known, for pulse charging in a volute, for two channels to be separated from one another by means of a separating crosspiece. The two channels can lead to different cylinders of the associated internal combustion engine. In the case of this arrangement, the two channels are arranged one beside the other in the axial direction of the turbocharger, and therefore each individual channel does not direct flow against the entire width of the turbine wheel. The problem here is that the separating crosspiece always conceals a certain part of the turbine wheel and flow cannot be directed directly against this part of the turbine wheel. In order to ensure a certain level of stability and endurance strength, the separating crosspiece cannot be configured to be as thin as desired.

It is an object of the present invention to specify an exhaust-gas turbocharger which, along with cost-effective production and low-maintenance operation, allows pulse charging, is simultaneously compact and can be used, in particular, in passenger vehicles.

The object is achieved by the features of the independent claim. The dependent claims relate to the advantageous configuration of the invention.

The object is thus achieved by an exhaust-gas turbocharger, preferably for a passenger vehicle, comprising a compressor having a compressor wheel and a turbine having a turbine wheel. The turbine wheel is arranged in a turbine housing. The compressor wheel is connected to the turbine wheel by means of a shaft. Exhaust gas, for example from an internal combustion engine, flows against the turbine wheel. This causes the shaft, and thus also the compressor wheel, to rotate. Charge air, for example for the internal combustion engine, is compressed via the compressor wheel. At least two channels for guiding the exhaust gas onto the turbine wheel are formed in the turbine housing. The number of channels is referred to as "S". The shaft extends in an axial direction from the compressor to the turbine. This axial direction lies along the axis of the shaft and/or the axis of the turbine wheel and of the compressor wheel. A radial direction is defined perpendicularly to the axial direction. A circumferential direction is defined around the axial direction, counter to the direction of rotation of the turbine wheel. Each of the at least two channels directs flow against the turbine wheel over the entire width of the latter. The width of the turbine wheel is defined in the axial direction. Furthermore, each channel directs flow against the turbine wheel over a segment, as seen in relation to the circumferential direction. If use is made of two channels, each channel therefore directs flow against the turbine wheel over 180° and over the entire width of the turbine wheel. The invention does not provide two axially adjacent channels subdivided via a separating crosspiece. This means that the turbine wheel is not partially concealed by the separating crosspiece.

The respective channels terminate on their radial inner side with a so-called tongue. Account has to be taken of the fact that this tongue at least partially prevents optimum flow against the turbine wheel. Since the invention here provides at least two channels, which act on the turbine wheel in a state in which they are offset through 180°, there are two such tongues adversely affecting the optimum flow against the turbine wheel. This adverse effect is noticeable in particular in the case of compact exhaust-gas turbochargers and correspondingly small turbine wheels. It has been found, within the framework of the invention, that sufficiently good flow against the turbine wheel, even with the channels offset through 180°, can be achieved if there is an appropriately high number of turbine blades - at least ten blades. The number of turbine blades will be referred to hereinbelow as "Z". It is particularly preferable for at least twelve, and further preferably for at least fourteen, turbine blades to be provided.

A so-called narrowest flow-outlet cross-sectional surface area is usually defined on exhaust-gas turbochargers. This narrowest flow-outlet cross-sectional surface area is measured at the turbine outlet, on the turbine-outlet-side edges of the turbine blades. The narrowest flow-outlet cross-sectional surface area here is measured perpendicularly to the blade surfaces and is defined as the clear width of the individual surfaces between the turbine blades. The more turbine blades are arranged on the turbine wheel, the smaller is the narrowest flow-outlet cross-sectional surface area, since it is the thickness of the turbine-outlet-side edge which reduces the flow-outlet cross-sectional surface area in each case. However, a certain narrowest flow-outlet cross-sectional surface area is advantageous for the optimum operation of an exhaust- gas turbocharger. Use is therefore preferably made of main blades and intermediate blades of the turbine wheel. The intermediate blades, at least at their hub-side ends, do not extend in the axial direction as far as the main blades. This ensures that the intermediate blades do not affect the narrowest flow-outlet cross-sectional surface area. The narrowest flow-outlet cross-sectional surface area is consequently defined along the turbine-outlet-side edges of the main blades and, in addition, is adversely affected only by the thicknesses of the turbine-outlet-side edges of the main blades.

In particular, provision is made for an intermediate blade to be arranged in each case between two main blades. If the total number is at least ten turbine blades, this therefore means that use is made of five main blades and five intermediate blades. In particular, provision is made to use at least six main blades and at least six intermediate blades, particularly preferably at least seven main blades and at least seven intermediate blades.

As mentioned in the introduction, the radial inner side of each channel terminates with a so-called tongue. The end of the tongue is defined as the tip. A neck cross- sectional surface area Al of the respective channel is defined at this tip of the tongue. An imaginary straight line in the radial direction through the axis of the turbine wheel is located in the neck cross-sectional surface area Al . The abovementioned narrowest flow-outlet cross-sectional surface area at the turbine-outlet-side edges of the turbine blades is referred to as A2. Provision is preferably made for the following to be the case: A2/A1 S DO.9, preferably A2/A1 S Dl .O. This ratio of the flow-outlet cross- sectional surface area A2 to the neck cross-sectional surface area Al of the individual channels ensures optimum operation of the exhaust-gas turbocharger. In particular the narrowest flow-outlet cross-sectional surface area A2, which is relatively small for this purpose, is achieved by using the intermediate blades mentioned above. However, it is also possible, by virtue of the turbine blades being formed appropriately, to achieve the ratio without using intermediate blades.

Furthermore, provision is preferably made for a turbine-wheel inlet diameter D to be defined at the turbine wheel, as measured up to the radial ends of the turbine blades. If use is made of the main blades and of the intermediate blades, the turbine -wheel inlet diameter D is defined up to the radial ends of the main blades. It is preferably the case that S DAl/D 15 mm, preferably S DAl/D 12 mm. These variables define, in particular, that the exhaust-gas turbocharger is a small one, with a correspondingly small turbine wheel. In particular with this size of exhaust-gas turbocharger, use should be made of the arrangement according to the invention of the channels, in conjunction with the at least ten turbine blades, in order to achieve the best possible efficiency.

Furthermore, provision is preferably made for at least one tongue of one channel to be shortened. The tip of the tongue of one channel forms a geometrical reference point. Starting from this reference point, the next channel terminates at 360°/S, as measured in the circumferential direction. If use is made of two channels, therefore, the one channel terminates at 0° and the other channel terminates at 180°. Provision is preferably made for the tip of the tongue of the second channel to be shortened by an angle a in the circumferential direction. For this angle a, it is preferably the case that (360°/Z) - 5° a 5°. In particular this shortening by at least 5° reduces the risk of blade fatigue failure.

In particular the following constructions are preferably provided for the formation of the channels and volutes: according to a first variant, a dedicated volute is formed in the turbine housing for each channel. There are therefore at least two volutes, which, offset in particular through 180°, lead from the internal combustion engine to the exhaust-gas turbocharger. Each volute has a channel formed in it.

In the second variant, provision is preferably made for a volute common to the two channels to be formed in the turbine housing. This one volute contains a crosspiece which separates the two channels from one another such that the one channel is arranged radially within the other channel. The crosspiece merges, in the direction of the turbine wheel, into the tongue of the outer channel.

The exhaust-gas turbocharger is used, in particular, for internal combustion engines having an even number of cylinders. It is immaterial which channel is connected to which cylinder.

The invention will be described hereinbelow with reference to exemplary embodiments and in conjunction with the drawing, in which:

Figure 1 shows a schematically simplified view of the exhaust-gas turbocharger according to all the exemplary embodiments of the invention; Figure 2 shows a schematically simplified sectional view through the turbine of the exhaust-gas turbocharger according to a first exemplary embodiment of the invention;

Figure 3 shows the turbine wheel of the exhaust-gas turbocharger according to the first exemplary embodiment of the invention;

Figure 4 shows the turbine wheel of the exhaust-gas turbocharger according to a second exemplary embodiment of the invention;

Figure 5 shows a section through the turbine of the exhaust-gas turbocharger according to the second exemplary embodiment of the invention; and

Figure 6 shows a section through the turbine of the exhaust-gas turbocharger according to a third exemplary embodiment of the invention.

Exemplary embodiments of an exhaust-gas turbocharger 1 will be explained in detail hereinbelow. Identical, or functionally identical, components are provided with the same reference signs in all the exemplary embodiments. Figure 1 shows the general construction of the exhaust-gas turbocharger 1 for all exemplary embodiments.

According to Figure 1 , the exhaust-gas turbocharger 1 has a compressor 2 having a compressor wheel 3. Also provided is a turbine 4 having a turbine wheel 5 and a turbine housing 6. A plurality of turbine blades 12 are formed on the turbine wheel 5. A shaft 7 connects the compressor wheel 3 to the turbine wheel 5.

Two channels 13, 14 are formed in the turbine housing 6. Exhaust gas is directed onto the turbine wheel 5 via said channels 13, 14. The turbine wheel 5 is thus caused to rotate. Via the shaft 7, the compressor wheel 3 is thus also caused to rotate. Air is taken in, and compressed, via the compressor wheel 3.

The shaft 7 extends in an axial direction 8. The axial direction 8 lies along the axis 11 of the turbine wheel 5. The axial direction 8 is defined from the compressor 2 in the direction of the turbine 4. A radial direction 9 runs perpendicularly to the axial direction 8. A circumferential direction 10 is defined around the axial direction 8. The circumferential direction 10 is defined counter to the direction of rotation of the turbine wheel 5.

Figure 2 shows, in a schematically simplified illustration, a section through the turbine 4 of the exhaust-gas turbocharger 1 according to the first exemplary embodiment. It can be seen that, in the first exemplary embodiment, two volutes 15, 16 are formed in the turbine housing 6. Each volute 15, 16 contains a respective channel 13, 14.

The channels 13, 14, or the volutes 15, 16, direct flow against the turbine wheel 5 in each case over the entire width of the latter, as defined in the axial direction 8. Each channel 13, 14 directs flow against the turbine wheel 5 over a segment of 180°.

The respective radial inner side of the channels 13, 14 terminates with a tongue 17. The end of the tongue 17 is defined as the tip 18.

Ten turbine blades 12 are provided on the turbine wheel 5.

Figure 3 shows a detail of the turbine wheel 5. Each of the turbine blades 12 has a turbine-outlet-side edge 19. This turbine-outlet-side edge 19 is located approximately perpendicularly to the axis 11 and is connected to a hub 20 of the turbine wheel 5. A narrowest flow-outlet cross-sectional surface area A2 is made up of ten sub-surfaces 21. Each sub-surface 21 is measured at the respective turbine-outlet-side edge 19, in a direction perpendicular to the surface of the turbine blade 12. The sum of these, in this case, ten sub-surfaces 21 forms the narrowest flow-outlet cross-sectional surface area A2. The illustration in Figure 3 clearly shows that each turbine blade 12 used, in particular by virtue of its thickness, reduces the narrowest flow-outlet cross-sectional surface area A2.

A neck cross-sectional surface area Al of the respective channel 13, 14 is defined at the tips 18 of the tongues. The ratio A2/A1 is preferably greater than or equal to 2 D0.9, preferably 2 Dl .0.

Figure 4 shows a turbine wheel 5 according to the second exemplary embodiment. In this turbine wheel 5, the turbine blades 12 are designed in the form of main blades 22 and intermediate blades 23. An intermediate blade 23 is located in each case between two main blades 22. There are seven main blades 22 and, correspondingly, seven intermediate blades 23 provided. The critical factor in the case of the turbine wheel 5 according to Figure 4 is that the hub-side ends 24 of the intermediate blades 23 do not project as far in the axial direction 8 as the main blades 22. Consequently, the turbine-outlet- side edges 19 of the main blades 22 are decisive for the calculation of the narrowest flow-outlet cross- sectional surface area A2. The narrowest flow-outlet cross-sectional surface area A2 is not adversely affected by the design of the intermediate blades 23. This means that the preferred ratio of A2/A1 S DO.9, preferably A2/A1 S Dl .O, can be realized to good effect.

Figure 5 shows the design of the turbine housing 6 for the second exemplary embodiment. A volute 15 common to both channels 13, 14 is formed in the second exemplary embodiment. The volute 15 is subdivided into the two channels 13, 14 by means of a crosspiece 25. The crosspiece 25 is arranged such that the two channels 13, 14 are adjacent to one another in the radial direction 9. This makes it possible for each of the channels 13, 14 to act over the entire width of the turbine wheel 5. As Figure 5 shows, the crosspiece 25 merges into the tongue of the outer channel 14.

Figure 6 shows the design of the turbine housing 6 for the third exemplary embodiment. The third exemplary embodiment corresponds to the second exemplary embodiment apart from the following difference: in the third exemplary embodiment, just as in Figure 2, the tongue 17 of one channel 14 is shortened. The tip 18 of the tongue of the first channel 13 forms a geometrical reference point. Starting from this reference point, the next channel terminates at 360°/S, as measured in the circumferential direction. If use is made of two channels 13, 14, therefore, the first channel 13 terminates at 0° and the second channel 14 terminates at 180°. The tip 18 of the tongue of the second channel 14 here is shortened by an angle a in the circumferential direction. For this angle a, it is preferably the case that (360°/Z) - 5° a 5°. In particular this shortening by at least 5° reduces the risk of blade fatigue failure.

The exhaust-gas turbochargers 1 shown here are provided, in particular, for small constructions. The intention is to have, in particular, a relatively small turbine wheel 5. Figure 1 shows an inlet diameter D of the turbine wheel 5. This diameter D is preferably not more than 35 mm. The construction of the turbine wheel 5 with the main blades 22 and the intermediate blades 23 can also be used in the first exemplary embodiment. It is equally possible for a turbine wheel 5 according to Figure 3 to be used in the construction of the turbine housing 6 according to Figure 5 or Figure 6.

List of reference signs:

1 exhaust-gas turbocharger

2 compressor

3 compressor wheel

4 turbine

5 turbine wheel

6 turbine housing

7 shaft

8 axial direction

9 radial direction

10 circumferential direction

11 axis

12 turbine blades

13 first channel

14 second channel

15 first volute

16 second volute

17 tongue

18 tip of the tongue

19 turbine -outlet-side edge

20 hub

21 sub -surface

22 main blades

23 intermediate blades

24 hub-side ends

25 crosspiece

Al neck cross-sectional surface area

A2 flow-outlet cross-sectional surface area

Claims

PATENT CLAIMS

1. Exhaust-gas turbocharger (1), preferably for a passenger vehicle, comprising

a compressor (2) having a compressor wheel (3),

a turbine (4) having a turbine wheel (5) and a turbine housing (6), a shaft (7), which connects the compressor wheel (3) to the turbine wheel

(5), and

a number of S>2 of channels (13, 14), which are formed in the turbine housing (6) and are intended for guiding the exhaust gas onto the turbine wheel (5),

wherein an axial direction (8) is defined along the shaft (7), from the compressor (2) to the turbine (4), a radial direction (9) is defined perpendicularly to the axial direction (8), and a circumferential direction (10) is defined around the axial direction (8), counter to the direction of rotation of the turbine wheel (5),

wherein each channel (13, 14) directs flow against the turbine wheel (5) over the entire width of the latter, as seen in the axial direction (8), and over a segment, as seen in relation to the circumferential direction (10), wherein the turbine wheel (5) comprises a number of Z>10 turbine blades (12), and

wherein the turbine blades (12) are defined in the form of main blades (22) and intermediate blades (23), wherein the intermediate blades (23), at least at their hub-side ends (24), do not extend as far toward the turbine outlet, as seen in the axial direction (8), as the main blades (22).

2. Exhaust-gas turbocharger according to claim 1, characterized in that an intermediate blade (23) is arranged in each case between two main blades (22).

3. Exhaust-gas turbocharger according to either of the preceding claims, characterized in that a radial inner side of each channel (13, 14) terminates with a tongue (17), and a neck cross-sectional surface area Al of the respective channel is defined at a tip (18) of the tongue (17), and

in that sub-surfaces (21) are defined between turbine-outlet-side edges (19) of the turbine blades (12), in particular of the main blades (22), and these sub-surfaces together give a narrowest flow-outlet cross-sectional surface area A2,

where A2/A1 >S CD.9, preferably A2/A1≥S Dl .0.

4. Exhaust-gas turbocharger according to claim 3, characterized in that a turbine-wheel inlet diameter D is defined at the turbine wheel (5), as measured up to the radial ends of the turbine blades (12), in particular of the main blades (22), where S CA 1/D≤ 15mm, preferably S CA1/D≤12mm.

5. Exhaust-gas turbocharger according to one of the preceding claims, characterized in that

a radial inner side of each channel (13, 14) terminates with a tongue (17) and associated tip (18),

wherein the tip (18) of the tongue of one channel (13) forms a geometrical reference point and, starting from this reference point, the next channel

(14) terminates at 360°/S, as measured in the circumferential direction (10), wherein the tip (18) of the tongue of this next channel (14) is shortened by an angle Din the circumferential direction (10), and

where (360 Z)-5°≥O≥5°.

6. Exhaust-gas turbocharger according to one of the preceding claims, characterized in that a dedicated volute (15, 16) is formed in the turbine housing (6) for each channel (13, 14), wherein the volutes (15, 16) are offset through 360°/S in the circumferential direction (10).

7. Exhaust-gas turbocharger according to one of claims 1 to 5,

characterized in that at least one volute (15) is formed in the turbine housing (6), wherein, in the volute (15), two channels (13, 14) are separated by a crosspiece (25), and therefore one channel (14) is arranged radially outside the other channel (13).