Patent Application
20100150709
The present disclosure relates to the field of exhaust turbochargers, including exhaust turbochargers for charged internal combustion engines, for example. More particularly, the present disclosure relates to a discharge region of a centrifugal compressor of such exhaust gas turbochargers, wherein the discharge region is arranged downstream of a compressor impeller and includes a vaned diffuser and an asymmetrically formed scroll casing.
In modern turbochargers, single-stage centrifugal compressors with vaned diffusers are used to increase the induction pressure of the engine. In the diffuser, the kinetic energy of the medium which is to be compressed is converted into static pressure. The compressor impellers comprise a specific number of impeller blades, and the diffusers have guide vanes with prismatic, aerodynamic profiles (i.e., wedge-shaped or airfoil-shaped). As seen in the direction of the compressor axis, the guide vanes have a determined tangential angle at the leading edge (inlet angle), a determined tangential angle at the trailing edge (exit angle), and a determined spacing in the circumferential direction between two guide vanes which are arranged adjacently to each other.
When designing compressor stages, a compromise must constantly be found between the aerodynamic performance, the mechanical load and the development of noise by the compressor. Modern compressor stages with high specific swallowing capacities have long, thin impeller blades, the natural modes of which occur at low frequencies and can easily be excited and set in oscillation. A primary source of these excitations is a pressure potential field which is created by the guide vanes of the diffuser. On account of the geometrically regularly formed compressor impeller blades and diffuser guide vanes, resonance vibrations can occur which become effective as vibrational energy increases. On account of the high speed which is required for achieving the discharge pressure, the vibrations can lead in the extreme case to mechanical damage (high-cycle fatigue—HCF) in the compressor impeller blades.
EP 1 772 596 discloses a two-stage diffuser of a centrifugal compressor, in which a diffuser vane row is arranged in front of and behind the impeller blades of the compressor which are exposed to axial throughflow. The diffuser vane rows have a different number of guide vanes each in a lower and an upper half in order to reduce the vibration influence, as a result of the uneven vane concentration, upon the impeller blades which are arranged between the diffuser vane rows. The throughflow takes place in the axial direction, wherein the flow conditions in front of and behind the represented two-stage diffuser along the circumference are symmetrical. Such symmetrical flow conditions are necessary since the axial turbine, which is to be fed a flow which is as symmetrical as possible along the circumference, is arranged downstream of the diffuser.
U.S. Pat. No. 3,873,231 discloses a liquid pump with an impeller with a multiplicity of blades and a plurality of guide vanes which are arranged in a distributed manner along the circumference. The guide vanes in this case have an uneven distribution along the circumference in order to be able to avoid constant pressure patterns in the liquid which is to be pumped.
An exemplary embodiment provides a discharge region of a centrifugal compressor, comprising: a scroll casing which is asymmetrically formed in a circumferential direction and configured to be positioned in different angular positions in the circumferential direction; a vaned diffuser configured to be positioned in different angular positions in the circumferential direction, the vaned diffuser including a plurality of guide elements configured to be arranged in a distributed manner in the circumferential direction; and means for positioning the vaned diffuser with regard to an angular position of the asymmetrically formed scroll casing. An angular spacing of two guide elements which are arranged adjacently to each other differs from an angular spacing of two other guide elements which are arranged adjacently to each other.
Additional refinements, advantages and features of the present disclosure are described in more detail below with reference to exemplary embodiments illustrated in the drawings, which illustrate exemplary embodiments of a diffuser of a centrifugal compressor, in which:
Exemplary embodiments of the present disclosure provide an improved discharge region of a centrifugal compressor in which a diffuser, in interaction with the asymmetrically formed scroll casing which is arranged downstream of the guide vanes of the diffuser, and also with the impeller blades of the centrifugal compressor impeller, causes resonance vibrations which are as low as possible.
Exemplary embodiments achieve this advantageous aspect by varying the angular spacings between two adjacently arranged guide vanes of the diffuser varying. The diffuser, which is irregularly formed as a result, is arranged in a defined angular position with regard to the scroll casing which can be positioned in different angular positions in the circumferential direction.
According to an exemplary embodiment, individual guide vane pairs can have an angular spacing which differs from the remaining guide vane pairs.
In a further exemplary embodiment, a plurality of guide vane pairs, which are arranged next to each other or distributed regularly or irregularly along the circumference, can have the same angular spacing but an angular spacing which is different from the angular spacing of the remaining guide vane pairs.
In another exemplary embodiment, a plurality of groups of guide vane pairs can have the same angular spacing. These guide vane pairs of such groups can be arranged in a manner in which they adjoin each other or in a manner in which they are distributed over the circumference.
In a further exemplary embodiment, all the guide vane pairs can have a different angular spacing.
The shape, length, inlet angle and exit angle as well as the inlet radius and exit radius of the guide vanes, with regard to the compressor axis, can be the same for all the guide vanes or can be different for some or all of the guide vanes in the axial direction as well as in the circumferential direction.
Such diffusers which are irregularly formed according to exemplary embodiments of the present disclosure can be designed in a single-stage or multistage form, wherein in the case of a plurality of stages, the diffusers are arranged one behind the other in the radial direction, that is to say concentrically with regard to the compressor axis.
According to an exemplary embodiment of the present disclosure, the diffuser has a plurality of guide vanes 21. The guide vanes 21 can have different angular spacings from each other. As used herein, the angle between the leading edges of two guide vanes 21 which are arranged adjacently to each other is referred to as the “angular spacing.” As used herein, the angle between two other corresponding points of two guide vanes 21 which are arranged adjacently to each other can optionally also be referred to as the “angular spacing,” for example when the guide vanes have differently formed inlet angles or the leading edges are located on different radii. In this case, for example, the angle between the trailing edges or the angle between the profile middle points can be referred to as the “angular spacing.”
According to an exemplary embodiment of the present disclosure, the angular spacings between guide vanes which are arranged adjacently to each other are not identical over the entire circumference. In this case, there is a plurality of possibilities of realizing diffusers with varying angular spacings between the guide vanes, as described below.
In an exemplary embodiment illustrated in
The different angular spacings αx, as can be gathered from the above table, are irregularly distributed to all the pairs of guide vanes 21 in the exemplary embodiment illustrated in
In another exemplary embodiment illustrated in
Additional embodiments are also possible in accordance with the present disclosure. For example, all the angular spacings αx can be identical except for one or a few of them. Groups of identical angular spacings αx can be formed. These pairings of guide vanes 21 with identical angular spacings αx can be arranged in a manner in which they lie adjacent to each other or are separated from each other.
In the case of diffusers with guide vanes 21 with different angular spacings αx, based on measurements, a reduction of resonance vibrations of up to 50 per cent, as compared with a regularly vaned diffuser, was proven to be achieved.
The individual guide vanes of the diffuser could optionally differ from each other in shape, length, inlet angle and exit angle, as well as inlet radius and exit radius in order to introduce additional inequalities into the diffuser. The different design in this case can be effected both in the axial direction (with regard to the compressor axis), that is to say in the direction of the blade height, as well as in the circumferential direction. In this case, all or only a few of the guide vanes 21 can be differently formed or arranged.
Such diffusers, which are irregularly formed according to exemplary embodiments of the present disclosure, can be designed in single-stage or multistage form, wherein in the case of a plurality of stages these are arranged one behind the other in the radial direction, that is to say concentrically with regard to the compressor axis.
The diffuser, which can be irregularly formed in the circumferential direction, can be positioned in a fixed angular position with regard to the scroll casing 31 which is asymmetrically formed in the circumferential direction. Moreover, the value of the different angular spacings αx and their distribution along the circumference are geared to the asymmetrically formed scroll casing 31 downstream of the guide vanes 21. For example, the angular spacings αx can increase along the circumference similar to the radius of the scroll casing 21, or a guide vane pair, which is arranged in the region of the start of the scroll tongue, can have an angular spacing αx which differs from the remaining guide vane pairs.
Since the scroll casing 31 can be positioned in different angular positions along the circumference, it is ensured with positioning means that the diffuser is located in each case in the intended angular position to the scroll casing 31. According to an exemplary embodiment, the intended angular position in this case is advantageously set so that minimum resonance vibration is created during operation. This angular position of the diffuser to the scroll casing with minimum creation of resonance vibration can be optionally calculated or experimentally determined. An example of a positioning means is indicated in
It will be appreciated by those skilled in the art that the present invention can be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The presently disclosed embodiments are therefore considered in all respects to be illustrative and not restricted. The scope of the invention is indicated by the appended claims rather than the foregoing description and all changes that come within the meaning and range and equivalence thereof are intended to be embraced therein.
| Number | Date | Country | Kind |
|---|---|---|---|
| 07112348.3 | Jul 2007 | EP | regional |
This application claims priority as a continuation application under 35 U.S.C. §120 to PCT/EP2008/058941, which was filed as an International Application on Jul. 9, 2008 designating the U.S., and which claims priority to European Application 07112348.3 filed in Europe on Jul. 12, 2007. The entire contents of these applications are hereby incorporated by reference in their entireties.
| Number | Date | Country | |
|---|---|---|---|
| Parent | PCT/EP2008/058941 | Jul 2008 | US |
| Child | 12686190 | US |
