CN106065878B - fluid machine - Google Patents

Abstract

Fluid machine with a stator-side housing (11) and a rotor-side impeller (12), wherein a radially outer section of the impeller (12) and an adjoining section of the housing (11) are formed an axial slot (19), the fluid machine has a stator-side first ring structure (20) and a stator-side second ring structure (21), said ring structures having faces (24, 25) facing each other, Axially extending projections (22, 23) spaced from one another in the circumferential direction are formed on the face, wherein the ring structures (20, 21) are connected to one another in at least two defined relative positions, in which In said relative position, the ring structures (20, 21) each jointly have different axial dimensions in their connected state, wherein the relative position is defined by the axial dimensions of the ring structures (20, 21) connected to each other. The axial gap between the housing (11) and the radially outer section of the impeller (12) in which the ring structures (20, 21) are connected to one another is dimensioned.

Description

fluid machine

technical field

The invention relates to a fluid machine with a stator-side housing and a rotor-side impeller.

Background technique

A turbocharger with a compressor and a turbine is known from DE 10 2009 021 968 A1. The compressor of the turbocharger disclosed there is designed as a radial compressor, to which the charge air to be compressed is supplied axially, and the compressed charge air flows away in the radial direction. The radial compressor has a stator-side housing and a rotor-side impeller, wherein the stator-side housing of the radial compressor consists of a plurality of mutually connected housing segments. The first shell section is here formed by a spiral shell section and the second shell section is formed by a so-called mounting part, wherein the spiral shell and the mounting part are connected to one another by screws at mutually adjoining flange sections. An axial gap is formed between the mounting part of the housing and the radially outer section of the impeller, which must be precisely designed with as little play as possible in order to ensure the best possible efficiency of the radial compressor. Certainly. In practice, such an axial gap is typically set on fluid machines by means of separate components. Such a separate component can be referred to as a balancing ring, which is mounted on the stator-side housing for setting the axial gap. Such gimbals must be manufactured with great precision. Only when the fluid machine is assembled can it be determined by measuring the axial play whether the balancing ring has been produced with sufficient accuracy and the axial play can be set with sufficient accuracy. If necessary, machining of the balance ring is required in order to accurately set the axial play. Overall, this increases the assembly effort for the fluid machine.

There is a need for fluid machines in which the axial gap between the housing and the radially outer section of the impeller can be set easily and reliably with little effort.

Contents of the invention

Starting from this, the object addressed by the present invention is to provide a new fluid machine.

For this purpose, the invention proposes a fluid machine with a stator-side first ring structure and a stator-side second ring structure with faces facing each other in the axial direction, circumferentially spaced from one another and axially Extended projections are formed on the surface, wherein the ring structures are in at least two relative positions defined by at least two relative positions in which the ring structures in the same connection state respectively have different dimensions in total ) are connected to each other, wherein the relative position in which the ring structures are connected to each other sets the axial gap between the shell and the radially outer section of the impeller through the axial dimension of the ring structures connected to each other size of.

The axial gap can be set precisely and simply and reliably via the stator-side ring structure. The relative position in the circumferential direction between the ring structures determines the axial dimensions of the stator-side structures composed of the stator-side ring structures, wherein the matching of the relative circumferential positions and thus the axes of the ring structures connected to each other The adaptation to the dimensions enables an exact setting of the axial play between the housing and the radially outer section of the impeller.

Preferably, the casing of the fluid machine has a plurality of connected casing sections, wherein an axial gap is formed between one of the casing sections and the radially outer section of the impeller, wherein the first ring structure is An integral part of a first shell section of a fluid machine, in particular a spiral shell section, and the second ring structure is an installation of a second shell section of a fluid machine, especially a spiral shell section, connected to the first shell section An integrated part of the software. Separate components can then be dispensed with if the ring structure is an integral component of the shell section of the fluid machine. This is particularly advantageous for simple assembly of the fluid machine and for setting an axial gap between the housing and the radially outer section of the impeller.

According to an advantageous development, the first ring structure has stepped projections spaced apart from one another in the circumferential direction on the side facing the second ring structure, wherein the second ring structure has a circumferential gap on the side facing the first ring structure. Upwardly there are stepped projections spaced apart from one another, wherein in order to reduce the axial play, the rings are arranged to reduce axial play when the projections of the first ring structure abut against the projections of the second ring structure in a defined first relative position. The structures have a ratio when, in a defined second relative position, the protrusions of the first ring structure act in the counter-protrusions formed between the protrusions of the second ring structure and the protrusions of the second ring structure act as formed in the first ring structure The larger axial dimension when in the opposite protrusion between the protrusions. According to this advantageous variant, the step-like change in the axial dimension of the stator-side structure consisting of the ring structure and thus the axial gap between the housing and the radially outer section of the impeller It is feasible to set in stages.

According to an alternative advantageous development, the first ring structure has ramp-shaped protrusions spaced apart from one another in the peripheral direction on the side facing the second ring structure, wherein the second ring structure has on the side facing the first ring structure There are ramp-shaped protrusions spaced apart from one another in the circumferential direction, wherein when the protrusions of the first ring structure abut against the protrusions of the second ring structure, a defined relative position between the ring structures can be passed steplessly The axial dimension and thus the axial play between the minimum dimension and the maximum dimension are set accurately. This variant of the invention allows a continuous stepless change of the axial dimensions of the stator-side structure composed of ring structures and thus a stepless setting of the axial play.

Preferably, the first ring structure and the second ring structure are connected to each other by bolts extending through holes in the ring structure. This is advantageous to ensure simple assembly.

Description of drawings

Preferred variants of the invention emerge from the description below. Exemplary embodiments of the invention are explained in detail with the aid of the drawings (not limited thereto). which shows:

Figure 1: Cross-section of a fluid machine configured as a radial compressor;

Figure 2: Perspective exploded view of a detail of a fluid machine according to the invention, and

FIG. 3 : Partial cross-section of the detail in FIG. 2 in a possible build-up state of the fluid machine.

Detailed ways

Here, the invention relates to fluid machines, in particular radial compressors for turbochargers. But the invention is not limited to this use case. Rather, the invention can also be used in other radial compressors and radial turbines.

FIG. 1 shows a section from a turbocharger in the region of a fluid machine configured as a radial compressor 10 . The fluid machine 10 shown in FIG. 1 in the form of a radial compressor has a stator-side housing 11 and a rotor-side impeller 12 . The stator-side housing 11 has a plurality of interconnected housing sections, ie in the exemplary embodiment shown has a spiral shell section 13 and a mounting part 14 connected to the spiral shell section 13 . The spiral shell section 13 and the mounting part 14 are connected to each other at mutually adjoining flange sections 15 , 16 , ie via a plurality of connecting screws 17 spaced apart from one another in the circumferential direction, which are preferably designed as expansion screws.

In the illustrated embodiment, in which the fluid machine is embodied as a radial compressor 10 of a turbocharger, a so-called bearing housing 18 is attached to the housing 11 of the radial compressor.

As can be seen from FIG. 1 , the axial gap 19 is formed between the housing 11 , ie, the mounting part 14 of the housing 11 , and the radially outer section of the impeller 12 . Such an axial gap 19 must be precisely set in order to ensure a high efficiency of the fluid machine, in particular the radial compressor 10 shown in FIG. 1 . Here, the invention concerns such details of a fluid machine, preferably configured as a radial compressor of a turbocharger, which enables a simple and reliable setting of such an axial gap 19 for ensuring High efficiency of fluid machines.

According to the invention, the axial gap 19 can be set easily and reliably via the stator-side ring structure. FIG. 2 thus shows a first stator-side ring structure 20 and a second stator-side ring structure 21 on which axially extending projections 22 or projections 22 or twenty three. The projections 22 , 23 are formed on the faces 24 and 25 of the ring structures 20 , 21 facing each other in the axial direction. the ring structures 20 , 21 are connected in at least two defined relative positions in the circumferential direction in which the ring structures 20 , 21 in their connected state each have different axial dimensions, Wherein, the relative position in the circumferential direction (in the circumferential direction, the ring structures 20, 21 are connected to each other) determines the axial dimension of the ring structures 20, 21 connected to each other, and the axis passing through the ring structures 20, 21 connected to each other The dimensioning defines the dimension of the axial gap 19 between the housing 11 and the radially outer section of the impeller 12 .

Preferably, one of the stator-side ring structures, for example the ring structure 21, is a component of the first housing segment, in particular of the spiral housing segment 13 in the region of its flange segment 15, while the other ring The structure, for example the ring structure 20 , is an integral component of the mounting part 14 connected to the spiral shell section 13 , ie in the region of its flange section 16 . By virtue of the defined relative position in the circumferential direction, in which the mounting part 14 is then mounted on the spiral shell 13 of the housing 11 , the axial relative position of the mounting part 14 with respect to the impeller 12 is set and thus The axial gap 19 is dimensioned.

As already implemented, in the region of the flange sections 15 , 16 the spiral housing 13 and the mounting part 14 are connected to one another via bolts 17 , wherein the bolts 17 extend through the holes 26 , 27 of the ring structures 20 , 21 .

2 and 3 show an embodiment of the invention in which the first stator-side ring structure 20 has circumferentially spaced ring structures 21 on the axial face 24 facing the stator-side second ring structure 21. The stepped protrusions 22 each have the same or stepped height in the axial direction, and in this embodiment, the stator-side second ring structure 21 is aligned with the axis of the stator-side first ring structure 20 On the facing surface 25 there are stepped projections 23 spaced apart from one another in the circumferential direction, likewise each having the same height in the axial direction or stepwise heights. When the projections 22 , 23 of the two stator-side ring structures 20 , 21 abut against each other in the first circumferential relative position, the overall structure formed by the ring structures 20 , 21 has a greater The axial dimension of , that is, when the protrusion 23 of the ring structure 21 on the stator side acts on the counter protrusion 28 configured between the protrusions 22 of the ring structure 20 on the stator side in the second circumferential relative position as shown in FIG. In this way, the protrusions 22 of the stator-side ring structure 20 engage in the counter-protrusions 29 formed between the protrusions 23 of the stator-side ring structure 21 .

In the exemplary embodiment shown in FIGS. 2 and 3 (in which case the stepped protrusions 22 of the ring structure 20 and the stepped protrusions 23 of the ring structure 21 each have the same height in the axial direction) The stator-side ring structures 20 , 21 can be connected to one another in two defined circumferential positions relative to one another, providing two different axial dimensions.

As can be seen in FIG. 2 , here, in the region of the ring structure 20 , there are twice as many holes 26 as holes 27 formed at the ring structure 21 , so that in the two possible defined ring structures In the relative position of 20 , 21 , their mechanically satisfactory connection is achieved via bolts 17 . In this case, the bore 27 is, for example, designed as a threaded bore, and the bore 26 is designed as an unthreaded bore.

In contrast to the exemplary embodiment shown in FIGS. 2 and 3 , it is possible that at least one ring structure 20 or 21 the stepped projections juxtaposed with one another in the circumferential direction are configured with more than one axially different step Height or height, so that the ring structures 20 , 21 can then be connected to each other in more than two defined positions relative to each other in the circumferential direction, providing more than two possible different axial dimensions. It is sufficient for this that, on ring structures, the projections are formed with a plurality of different axial step heights, wherein, on other ring structures, the stepped projections can all have the same height. Then the number of holes required at a ring structure with a plurality of different step heights in the axial direction corresponds to the number of holes in other ring structures multiplied by the available ring structures providing different axial dimensions The number of circumferential relative positions between. If, for example, a number N of holes is formed at the ring structure, the other ring structure must have x*N holes, where x is possible to provide different axial dimensions between the ring structures 20, 21 The number of relative positions.

A further variant of the embodiment of FIGS. 2 and 3 consists in that the first ring structure has ramp-shaped or wedge-shaped projections spaced apart from one another in the circumferential direction on the axial face facing the second ring structure, and that the second ring structure On the axial side facing the first ring structure there are likewise ramp-shaped or wedge-shaped projections spaced apart from one another in the circumferential direction. When such ramp-shaped or wedge-shaped protrusions of the first ring structure abut against ramp-shaped or wedge-shaped protrusions of the second ring structure, it is possible to pass through the defined circumferential relative contact between the ring structures. The axial dimension and thus the axial gap 19 between the housing 11 and the impeller 12 are set steplessly between a minimum dimension and a maximum dimension by position.

In this case it is then possible to provide the same number of holes on both ring structures, ie on the ring structures the threaded holes for receiving the bolts 17 spaced apart from one another in the circumferential direction and on the other ring structures are configured as elongated holes. Bore A hole that runs curved in the circumferential direction without a thread.

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 section 16 of the mount 14 . The ring structure 20 is then preferably an integral component of the flange section 15 of the spiral shell 13 . The axial position of the mounting part 14 relative to the impeller 12 can be set by twisting the mounting part 14 and thus its ring structure relative to the spiral shell 13 and thus its ring structure in the circumferential direction, so that An axial gap 19 between the shell 11 and the impeller 12 is defined. This relative position is secured by the connecting bolt 17 (the connecting bolt is used to connect the two shell sections 13, 14), wherein in one ring structure the holes are implemented without thread and in the other ring structure the described The holes are implemented as threaded holes.

If the correct relative position in the circumferential direction for the ring structures 20, 21 is used to set the axial gap 19 in the assembly of the fluid machine, then preferably at one of the ring structures, in the desired At least one of the holes, which is not required for the connection of the ring structure in the correct circumferential relative position in terms of the setting of the axial play, is closed in order to disassemble the ring structure, for example by service conditions Again it can be fitted in the correct circumferential relative position.

reference number list

10 fluid machines

11 shells

12 working wheels

13 spiral shell segments

14 mounting parts

15 Flange section

16 Flange section

17 Connecting bolts

18 Bearing housing

19 axial gap

20 ring structure

21 ring structure

22 protrusions

23 protrusions

24 sides

25 sides

26 holes

27 holes

28 reverse protrusion

29 reverse protrusion

Claims (11)

1. Fluid machine with a stator-side casing (11) and a rotor-side impeller (12), wherein between the radially outer section of the impeller (12) and the adjacent section of the casing (11) An axial gap (19) is formed between them, characterized by a stator-side first ring structure (20) and a stator-side second ring structure (21), said ring structures having faces (24, 25) facing one another, Axially extending protrusions (22, 23) spaced from one another in the circumferential direction are formed on the face, wherein the ring structures (20, 21) are connected to one another in at least two relative positions in which Among them, the ring structures (20, 21) have different axial dimensions in their connected state, wherein the relative position is set by the axial dimensions of the ring structures (20, 21) connected to each other in the shell ( 11) Dimensions of the axial gap between the radially outer section of the impeller (12), in which relative position the ring structures (20, 21) are connected to one another. 2. Fluid machine according to claim 1, characterized in that the shell (11) has a plurality of shell segments (13, 14) connected to each other, wherein one of the shell segments (14) and the impeller ( Axial gaps ( 19 ) are formed between the radially outer sections of 12 ). 3. Fluid machine according to claim 2, characterized in that one of the ring structures (20, 21) is an integral part of the first shell section, and the other of the ring structures (20, 21) is An integral part of the mount (14) associated with the second shell segment associated with the first shell segment. 4. Fluid machine according to any one of claims 1 to 3, characterized in that the first ring structure (20) and the second ring structure (21) are connected to each other by bolts (17) which extend through the ring Holes (26, 27) of structures (20, 21). 5. The fluid machine according to any one of claims 1 to 3, characterized in that the first ring structure (20) has spaced distances from one another in the circumferential direction on the face (24) facing the second ring structure (21). step-shaped protrusions (22), and the second ring structure (21) has step-shaped protrusions (23) spaced apart from each other in the circumferential direction on the surface (25) facing the first ring structure (20), wherein, When the protrusion (22) of the first ring structure (20) rests on the protrusion (23) of the second ring structure (21) in the first relative position, then the ring structure has a The protrusions (22) of the first ring structure (20) act in the opposite protrusions (29) constructed between the protrusions (23) of the second ring structure (21) and the protrusions of the second ring structure (21) ( 23) Greater axial dimension when acting in the counter-protrusions (28) configured between the protrusions (22) of the first ring structure (28). 6. The fluid machine according to claim 5, characterized in that all stepped protrusions (22) of the first ring structure (20) each have the same height in the axial direction, and likewise the second ring structure All the stepped protrusions ( 23 ) of ( 21 ) each have the same height in the axial direction, so that the ring structures ( 20 , 21 ) provide two different axial dimensions in two positions relative to each other. circumstances can be connected to each other. 7. The fluid machine according to claim 5, characterized in that the stepped projections (22, 23) of at least one ring structure (20, 21) have at least two axially different heights, so that the ring structure ( 20 , 21 ) can be connected to one another in two or more positions relative to one another, providing two or more different axial dimensions. 8. The fluid machine according to claim 5, characterized in that the number of holes (26) in the first ring structure (20) corresponds to the number of holes (27) in the second ring structure (21) multiplied by The number of relative positions between the ring structures (20, 21) for different axial dimensions. 9. Fluid machine according to any one of claims 1 to 3, characterized in that the first ring structure has ramp-shaped protrusions spaced apart from one another in the circumferential direction on the side facing the second ring structure, and the second The two-ring structure has slope-shaped protrusions spaced apart from each other in the circumferential direction on the surface facing the first ring structure, wherein when the protrusions of the first ring structure abut against the protrusions of the second ring structure, passing through the A defined relative position between the ring structures enables a stepless setting of the axial dimension and thus the axial play between the minimum dimension and the maximum dimension. 10. Fluid machine according to claim 9, characterized in that the bores of one of the ring structures are designed as threaded bores and the bores of the other ring structure are designed as curved elongated holes extending in the circumferential direction. 11. The fluid machine of claim 3, wherein said first shell section and said second shell section are helical shell sections.