CH711012B1 - Flow machine. - Google Patents

Abstract

Turbomachine, comprising a stator-side housing and a rotor-side impeller, wherein between a radially outer portion of the impeller and an adjacent portion of the housing, an axial gap is formed, with a first stator-side ring structure (20) and a second stator-side ring structure (21) facing each other Surfaces (24, 25) on which circumferentially spaced, axially extending projections (22, 23) are formed, the ring structures (20, 21) in one of at least two defined relative positions in which the ring structures (20 , 21) in an interconnected state thereof have respective different axial dimensions, are interconnected, wherein the relative position in which the ring structures (20, 21) are interconnected via the axial dimension of the interconnected ring structures (20, 21) one Dimension of the axial gap between the housing and the radially outer portion of the impeller (12).

Description

CH 711 012 B1

Description: The invention relates to a turbomachine according to the preamble of claim 1.

[0002] DE 10 2009 021 968 A1 discloses a turbocharger with a compressor and a turbine. The compressor of the turbocharger disclosed there is designed as a radial compressor, to which charge air to be compressed is fed in the axial direction, and from which compressed charge air flows out in the radial direction. The radial compressor has a stator-side housing and a rotor-side impeller, the stator-side housing of the radial compressor being composed of a plurality of housing sections connected to one another. A first housing section is formed by a spiral housing section and a second housing section by a so-called insert, the spiral housing and the insert being connected to one another by screws on adjoining flange sections. An axial gap is formed between the insert of the housing and a radially outer section of the impeller, which must be set exactly with as little play as possible to ensure the best possible efficiency of the radial compressor. In practice, such an axial gap on a turbomachine is typically set using a separate component. Such a separate component can be a compensating ring which is mounted on the stator-side housing to adjust the axial gap. Such a compensation ring must be manufactured very precisely. Only when the turbomachine is installed can you determine by measuring the axial gap whether the compensating ring was manufactured with sufficient accuracy and whether the axial gap could be set with sufficient accuracy. Mechanical processing of the compensating ring may be necessary in order to set the axial gap exactly. This increases the overall assembly effort for a turbomachine.

There is a need for a turbomachine in which the axial gap between the housing and a radially outer section of an impeller can be adjusted easily and reliably with less effort.

Proceeding from this, the present invention has for its object to provide a novel flow machine.

This object is achieved by a turbomachine according to claim 1. The turbomachine according to the invention has a first stator-side ring structure and a second stator-side ring structure with surfaces facing each other in the axial direction, on which projections are formed which are spaced apart in the circumferential direction and extend in the axial direction, the ring structures in one of at least two defined relative positions, in which the ring structures in a connected state of the same each have different axial dimensions, are connected to one another, the relative position in which the ring structures are connected to one another via the axial dimension of the connected ring structures a dimension of the axial gap between the housing and the radially outer portion of the impeller established.

[0006] The axial gap can be set precisely and simply and reliably via the stator-side ring structures. The relative position between the ring structures in the circumferential direction determines the axial dimension of the stator-side structure composed of the stator-side ring structures, whereby by adjusting the circumferential relative position and accordingly by adjusting the axial dimension of the interconnected ring structures, the axial gap between the housing and the radially outer section of the Impeller can be adjusted exactly.

Preferably, the housing of the turbomachine has a plurality of interconnected housing sections, the axial gap being formed between one of the housing sections and the radially outer section of the impeller, the first ring structure being an integral part of a first housing section of the turbomachine, in particular a spiral housing section, and the second Ring structure is an integral part of a second housing section of the turbomachine connected to the first housing section, in particular of an insert piece connected to the spiral housing section. If the ring structures are an integral part of housing sections of the turbomachine, a separate component can be dispensed with. This is particularly advantageous for simple assembly of the turbomachine and for adjusting the axial gap between the housing and the radially outer section of the impeller.

According to an advantageous development, the first ring structure on a surface facing the second ring structure has circumferentially spaced step-like projections, wherein the second ring structure has a step-like projection on the surface facing the first ring structure in the circumferential direction, then when in In a first defined relative position, the projections of the first ring structure lie against the projections of the second ring structure, they have a larger axial dimension to reduce the axial gap than if, in a second defined relative position, the projections of the first ring structure in recesses formed between the projections of the second ring structure and the projections of the second ring structure engage in recesses formed between the projections of the first ring structure. According to this advantageous development, a step-like change in the axial dimension of the stator-side structure assembled from the ring structures and thus a step-by-step adjustment of the axial gap between the housing and the radially outer section of the impeller is possible.

According to an alternative advantageous development, the first ring structure on a surface facing the second ring structure has circumferentially spaced ramp-like projections, the second ring structure on a surface facing the first ring structure spaced apart in the circumferential direction ram

CH 711 012 B1 has pen-like projections, wherein when the projections of the first ring structure abut the projections of the second ring structure, the axial dimension and thus the axial gap between a minimum dimension and a maximum dimension can be infinitely adjusted via a defined relative position between them. This development of the invention allows a continuous, stepless change in the axial dimension of the stator-side structure composed of the ring structures and thus a stepless adjustment of the axial gap.

[0010] The first ring structure and the second ring structure are preferably connected to one another by screws which extend through bores in the ring structures. This is advantageous to ensure easy installation.

Preferred further developments of the invention result from the dependent claims 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 shows a cross section through a turbomachine designed as a radial compressor;

2: an exploded perspective view of a detail of a turbomachine according to the invention; and

Fig. 3: a partial cross section through the detail of Fig. 2 in a possible assembled state of the same.

The present invention relates to a turbomachine, in particular a radial compressor for a turbocharger. However, the invention is not limited to this application. Rather, the invention can also be used in other radial compressors and in radial turbines.

1 shows a partial cross section from a turbocharger in the region of a turbomachine designed as a radial compressor 10. The turbomachine 10 shown in FIG. 1, designed as a radial compressor, has a stator-side housing 11 and a rotor-side impeller 12. The stator-side housing 11 has a plurality of housing sections connected to one another, namely in the exemplary embodiment shown via a spiral housing section 13 and one connected to the spiral housing section 13 Insert 14. The volute casing section 13 and the insert 14 are connected to one another at adjacent flange sections 15, 16, namely via a plurality of circumferentially spaced connecting screws 17, which are preferably designed as expansion screws.

In the embodiment shown, in which the turbomachine is designed as a radial compressor 10 of a turbocharger, a so-called bearing housing 18 connects to the housing 11 of the radial compressor.

As can be seen in Fig. 1, an axial gap 19 is formed between the housing 11, namely the insert 14 of the housing 11, and a radially outer portion of the impeller 12. This axial gap 19 must be set exactly in order to ensure a high efficiency of the turbomachine, in particular of the radial compressor 10 shown in FIG. 1. The present invention relates to such details of a turbomachine, which is preferably designed as a radial compressor of a turbocharger, which enable simple and reliable adjustment of this axial gap 19 to ensure high efficiency of the turbomachine.

According to the invention, the axial gap 19 can be set simply and reliably via stator-side ring structures. 2 shows a first stator-side ring structure 20 and a second stator-side ring structure 21, on each of which projections 22 and 23 are formed which are spaced apart in the circumferential direction and extend in the axial direction. These projections 22, 23 are formed on surfaces 24 and 25 of the ring structures 20, 21 facing one another in the axial direction. The ring structures 20, 21 are connected in one of at least two defined relative positions in the circumferential direction, in which the ring structures 20, 21 each have different axial dimensions in a connected state thereof, the relative positions in the circumferential direction in which the ring structures 20, 21 are connected to one another are connected, the axial dimension of the interconnected ring structures 20, 21 is determined and the dimension of the axial gap 19 between the housing 11 and the radially outer section of the impeller 12 is set via this axial dimension of the interconnected ring structures 20, 21.

Preferably, one of the stator-side ring structures, for example the ring structure 21, is part of a first housing section, in particular part of the spiral housing section 13 in the region of the flange section 15 thereof, whereas the other ring structure, for example the ring structure 20, is an integral part of the one with the spiral housing section 13 connected insert 14, namely in the region of the flange section 16 of the same. The defined relative position in the circumferential direction, in which the insert 14 is then installed on the spiral housing 13 of the housing 11, sets the axial relative position of the insert 14 relative to the impeller 12 and thus the dimension of the axial gap 19.

As already stated, the spiral housing 13 and the insert 14 are connected to one another by screws 17 in the region of the flange sections 15, 16, these screws 17 extending through bores 26, 27 of the ring structures 20, 21.

CH 711 012 B1 [0019] FIGS. 2 and 3 show an embodiment of the invention, in which the first stator-side ring structure 20 on the axial surface 24 facing the second stator-side ring structure 21, step-like projections 22 spaced apart in the circumferential direction, each having identical heights or step heights in the axial direction, and in which the second stator-side ring structure 21 on the axial surface 25 facing the first stator-side ring structure 20 has step-like projections 23 spaced apart from one another in the circumferential direction, likewise with identical heights or step heights in the axial direction. If, in a first circumferential relative position, the projections 22, 23 of the two stator-side ring structures 20, 21 abut one another, the assembly of the ring structures 20, 21 has a larger axial dimension than if, as shown in FIG. 3, in a second circumferential relative position, the projections 23 of the stator-side ring structure 21 engage in recesses 28 formed between the projections 22 of the stator-side ring structure 20 and thus the projections 22 of the stator-side ring structure 20 in recesses 29 formed between the projections 23 of the stator-side ring structure 21.

In the embodiment shown in Fig. 2 and 3, in which the step-like projections 22 of the ring structure 20 and the step-like projections 23 of the ring structure 21 each have identical heights in the axial direction, the stator-side ring structures 20, 21 in two defined relative positions in Circumferential direction can be connected to each other with the provision of two different axial dimensions.

As can be seen in FIG. 2, twice as many holes 26 are present in the area of the ring structure 20 as holes 27 are formed on the ring structure 21, so that the mechanical ones in the two possible defined relative positions of the ring structures 20, 21 To meet requirements meeting the same via the screws 17. The bores 27 are e.g. designed as threaded bores and the bores 26 as unthreaded bores.

In contrast to the embodiment shown in FIGS. 2 and 3, it is possible that step-like projections with more than one step height or height different in the axial direction are formed on at least one ring structure 20 or 21 in the circumferential direction, so that then the ring structures 20, 21 can be connected to one another in more than two defined relative positions in the circumferential direction with the provision of more than two possible different axial dimensions. For this purpose, it is sufficient if the projections with the several different step heights are formed in the axial direction on one ring structure, wherein the step-like projections on the other ring structure can all have identical heights. The number of holes that is then required on the ring structure with the several different step heights in the axial direction corresponds to the number of holes in the other ring structure multiplied by the number of possible circumferential relative positions between the ring structures that provide different axial dimensions. If, for example, a number N holes are formed on a ring structure, then the other ring structure must have an x * N holes, where x is the number of possible relative positions between the ring structures 20, 21 that provide different axial dimensions.

A further modification of the embodiment of FIGS. 2 and 3 is that the first ring structure on an axial surface facing the second ring structure is spaced apart in the circumferential direction, ramp-like or wedge-like projections and the second ring structure on an axial surface facing the first ring structure in Has circumferentially spaced, also ramp-like or wedge-like projections. If such ramp-like or wedge-like projections of the first ring structure abut the ramp-like or wedge-like projections of the second ring structure, the axial dimension and thus the axial gap 19 between the housing 11 and the impeller 12 can be steplessly between one over a defined circumferential relative position between them Minimum dimension and a maximum dimension can be set.

In this case, it would then be possible to provide an identical number of bores on both ring structures, namely on one ring structure the circumferentially spaced threaded holes for receiving the screws 17 and on the other ring structure designed as elongated holes, unthreaded bores in The circumferential direction is curved.

In the preferred embodiment of the radial compressor 10 shown in Fig. 1, the ring structure 21 is preferably an integral part of the flange portion 16 of the insert 14. The ring structure 20 is then preferably an integral part of the flange portion 15 of the volute 13. By turning the insert 14 and thus the ring structure of the same relative to the spiral housing 13 and thus the ring structure thereof in the circumferential direction, the axial position of the insert 14 can be adjusted relative to the impeller 12, as a result of which the axial gap 19 between the housing 11 and the impeller 12 can be adjusted. This relative position is secured by the connecting screws 17 which serve to connect the two housing sections 13, 14, the bores in one ring structure being unthreaded and in the other ring structure the bores being designed as threaded bores.

If the correct relative position in the circumferential direction for the ring structures 20, 21 for setting the axial gap 19 is found during assembly of the turbomachine, then at least one of the bores, which is used for connecting the ring structures in the desired setting, is preferably on one of the ring structures of the axial gap correct circumferential relative position is not required, closed in order for example disassembly of the ring structures caused by a service case to be able to reassemble them in the correct circumferential relative position.

CH 711 012 B1

Reference symbol list [0027]

flow machine

casing

Wheel

Volute section

insert

flange

flange

connecting screw

bearing housing

axial gap

ring structure

ring structure

head Start

head Start

area

area

drilling

drilling

Claims (8)

29 return claims 1. Turbomachine, with a stator-side housing (11) and a rotor-side impeller (12), an axial gap (19) being formed between a radially outer portion of the impeller (12) and an adjacent portion of the housing (11), characterized by a first stator-side ring structure (20) and a second stator-side ring structure (21), which have mutually facing surfaces (24, 25), on which circumferentially spaced, axially extending projections (22, 23) are formed, the ring structures ( 20, 21) are connected to one another in one of at least two defined relative positions in which the ring structures (20, 21) each have different axial dimensions when in a connected state thereof, the relative position in which the ring structures (20, 21) are interconnected, one dimension via the axial dimension of the interconnected ring structures (20, 21) of the axial gap between the housing (11) and the radially outer portion of the impeller (12). 2. Turbomachine according to claim 1, characterized in that the housing (11) has a plurality of interconnected housing sections (13, 14), the axial gap (19) between one of the housing sections (14) and the radially outer section of the impeller (12) is trained. 3. Turbomachine according to claim 2, characterized in that one of the ring structures (20, 21) is an integral part of a first housing section, in particular a spiral housing section (13), and the other of the ring structures (21, 20) is an integral part of a connection to the first housing section second housing section, in particular an insert (14) connected to the spiral housing section (13). 4. Turbomachine according to one of claims 1 to 3, characterized in that the first ring structure (20) and the second ring structure (21) by screws (17) through bores (26, 27) of the ring structures (20, 21) extend, are interconnected. CH 711 012 B1 5. Turbomachine according to one of claims 1 to 4, characterized in that the first ring structure (20) on a surface facing the second ring structure (21) (24) has circumferentially spaced step-like projections (22), and that the second ring structure (21) on a surface (25) facing the first ring structure (20) has circumferentially spaced step-like projections (23), when, in a first relative position, the projections (22) of the first ring structure (20) on the projections ( 23) of the second ring structure (21), they have a larger axial dimension than when, in a second relative position, the projections (22) of the first ring structure (20) into recesses formed between the projections (23) of the second ring structure (21) (29) and the projections (23) of the second ring structure (21) in recess formed between the projections (22) of the first ring structure (28) intervene (28). 6. Turbomachine according to claim 5, characterized in that all step-like projections (22) of the first ring structure (20) each have identical heights in the axial direction, and that all step-like projections (23) of the second ring structure (21) each have identical heights in the axial direction have so that the ring structures (20, 21) can be connected to one another in two defined positions relative to one another while providing two different axial dimensions. 7. Turbomachine according to claim 5, characterized in that the step-like projections (22, 23) of at least one ring structure (20, 21) have at least two different heights in the axial direction, so that the ring structures (20, 21) in more than two defined relative positions to one another can be connected to one another while providing more than two different axial dimensions. 8. Turbomachine according to one of claims 5 to 7, characterized in that the number of bores (26) of the first ring structure (20) multiplies the number of bores (27) of the second ring structure (21) by the number of the different axial dimensions providing relative positions between the ring structures (20, 21).