FLANGE CONNECTION AND TURBOCHARGER HEREBY

Description

[0001] The invention relates to a flange connection with a profile clamp according to the preamble of claim 1 and to a turbocharger with such a flange connection according to claim 10.

[0002] A profile clamp can be used, for example, to create a fluid-tight connection between two pipe ends or two housings equipped with radially outward-facing flanges. For this purpose, the flanges are positioned relative to each other, and the profile clamp is placed onto the flanges using a tensionable, split profile band. The flanges are fixed relative to each other by tightening the profile clamp, which exerts axial and radial holding forces on the flanges. The profile band of the profile clamp typically has a U-shaped or V-shaped cross-section, which is brought into surface contact with the flanges. An example of a profile clamp of this type is shown in DE 10 2009 039 862 A1.

[0003] A disadvantage of such a clamp is that components with flanges to be joined are subjected to torsional forces in various technical applications. These forces are not sufficiently counteracted by the axial and radial clamping forces of the profile clamp. For example, such torsional forces exist in the connection between a turbine housing and a compressor housing of a turbocharger. This can lead to twisting of the connected components relative to each other. In turbochargers, high clamping forces are used by the profile clamp to generate enough friction to counteract the relative twisting. However, these necessary high clamping forces can diminish over time due to creep, expansion, temperature fluctuations, loosening of fasteners, and similar factors.

[0004] Profile clamps with inwardly projecting spring elements are known from EP 1 600 680 A1 and WO 2020 / 037029 A1. When the profile clamp is mounted on a joint between two flanges, the spring elements rest on the circumference of both flanges and hold them in a coaxial position relative to each other when the profile clamp is tightened.

[0005] DE 10 2019 112 884 B3 discloses a profile clamp with an additional element having a lug that projects from the clamp circumference towards the clamp center. When the profile clamp is mounted on a connection of two flanges, the lug engages in a recess in one of the two flanges and forms an anti-rotation device for that flange.

[0006] US Patent 9,212,769 B2 describes a profile clamp with a clamp band that has a gap between two clamping heads of the clamp band. This gap is closed by a separate bridge element such that the clamp band extends 360 degrees around a flange connection. A connection is formed between the clamp band and the bridge element, which has two lugs on the clamp band that engage in two recesses in the bridge element.

[0007] US 2018 / 0223692 A1 specifies a flange connection in which a profile clamp with a locking feature engages in two recesses of two opposing flanges to form an anti-rotation device between the flanges. The profile clamp has a clamp band with two clamping heads. This band has fixed V-shaped segments on its inner side in which the opposing flanges rest. The locking feature is fixed to one of these V-shaped segments.

[0008] The object of the invention is to develop technical solutions that counteract torsional forces between two component flanges connected by means of a profile clamp in a more effective, reliable and permanent manner. Furthermore, the technical solutions should be feasible in the smallest possible installation space and cost-effective.

[0009] The main features of the invention are specified in the characterizing part of claim 1 and in claim 10. Embodiments are the subject of claims 2 to 9 and the description.

[0010] The invention relates to a flange connection with a first and a second component flange arranged opposite each other in a longitudinal direction, wherein a profile clamp clamps the two component flanges together. The profile clamp has a profile band extending circumferentially around a clamp center and has two clamping heads connected to each other via a clamping element. A circumferentially extending profile groove is formed on the inner side of the profile band, which has a profile band base that is arranged at least partially between groove flanks. It is provided that this profile clamp has a locking feature on the inner side of the profile band that projects from the profile band base towards the clamp center.

[0011] The first and second component flanges each have a recess, with the locking feature projecting into both recesses and thereby forming an anti-rotation device between the first and second component flanges.

[0012] A particularly cost-effective design is achieved by integrating the locking feature as a single unit with the profile strip, especially through forming. This reduces the number of components and assembly steps required during manufacturing. Furthermore, the groove flanks are interrupted in the area of ​​a bridge section of the profile strip base, and the locking feature projects from the profile strip base towards the clamp center in this bridge section. This makes the locking feature easy to locate and align during installation.

[0013] Such a bridge section facilitates the opening of the profile clamp during assembly. It then preferably acts as a rigid hinge. The profile strip is preferably designed as a single piece, including the two clamping heads. However, the bridge section can also form a connection between two sections of the profile strip. Thus, it is possible for a bridge element rigidly connected to the two sections to form a rigid hinge, or for a movable connection to be formed between the two sections.

[0014] The locking feature thus creates a form-fit anti-rotation device for the profile clamp relative to the first and second component flanges, and consequently also between the first and second component flanges. This anti-rotation device remains permanently intact, even if the clamping force of the profile clamp decreases over time due to creep, stretching, temperature fluctuations, loosening of fasteners, and the like. This solution can be used in principle for all applications where a profile band is intended to connect two component flanges between which higher requirements for slip torque resistance are necessary.

[0015] When connecting two component flanges, this profile clamp ensures that the profile groove can continue to apply axial clamping forces to the component flanges and secures them against lateral displacement. The locking feature also provides additional anti-rotation protection for the profile clamp relative to and between the first and second component flanges. This anti-rotation protection remains permanently effective, even if the clamping force of the profile clamp decreases over time due to creep, expansion, temperature fluctuations, loosening of fasteners, and similar factors.

[0016] This profile clamp can have a V-shaped or U-shaped cross-section in its profile groove. This design is geometrically simple to manufacture and suitable for clamping the two flanges against each other with axial force in the longitudinal direction.

[0017] Optionally, the profile strip can have a V-shaped or U-shaped cross-section. This is particularly easy to manufacture. Furthermore, the profile strip can be made of metal. Production is especially cost-effective when the profile strip is manufactured by forming a metal sheet.

[0018] According to one variant of the profile clamp, the locking feature includes a first locking pin that projects from the base of the profile band towards the center of the clamp. Such a locking pin is inexpensive and usually sufficient to create a sufficiently stable anti-rotation device. In most applications, the torsional forces are not expected to be high enough to cause the locking pin to shear off.

[0019] In a particular embodiment, the locking feature has a second locking pin that projects into the profile groove, or projects from the profile band sole towards the clamp center, or projects into the profile groove and from the profile band sole towards the clamp center, wherein the second locking pin is arranged circumferentially offset to the first locking pin and / or in a longitudinal direction of the profile clamp transverse to the circumferential direction.

[0020] An offset in the circumferential direction is suitable for increasing the torsional forces that the locking feature can withstand. This can be achieved by simply doubling the forces it can withstand. Alternatively, the locking pins can be designed to absorb forces in one of the two circumferential directions. In this case, the first and second locking pins can be oriented in opposite directions so that equal torsional forces can be absorbed in both circumferential directions.

[0021] Optionally, the first and / or second locking pin is provided for from the group bolt, pin, peg, tooth, prong, mandrel and cam.

[0022] According to a more detailed embodiment, the recesses of the first and second component flanges are arranged opposite each other and together form a locking recess which forms a radially outwardly pointing insertion opening, wherein the locking feature projects into the locking recess and thereby forms an anti-rotation device by extending into the recesses of the first and second component flanges.

[0023] This allows for a simple orientation of the first and second component flanges before the profile clamp is mounted, by positioning the two recesses relative to each other. Furthermore, a simple locking mechanism provides direct anti-rotation protection between the first and second component flanges.

[0024] The component flanges should each have an inclined clamping flank that corresponds in particular to the cross-sectional shape of the profile groove and is in contact with the groove flanks for clamping.

[0025] Optionally, the recesses are designed to be so deep that the recess bases pointing towards the center of the clamp and the locking feature are spaced apart from each other. This allows the profile clamp to be tightened without colliding with the recess bases.

[0026] In a particular embodiment, the recesses are designed to be so wide that the longitudinally oriented recess walls and the locking feature are spaced apart from each other. This prevents the locking feature from colliding with the component flanges in the longitudinal direction and ensures uniform longitudinal tension around the circumference of the component flanges.

[0027] It is also possible to design the locking feature such that it has play in the recesses in the circumferential direction. This play facilitates assembly. Furthermore, minimal twisting within the circumference of the play rarely causes problems in most applications.

[0028] Furthermore, the invention relates to a turbocharger with a flange connection as specified above and below, wherein the first component flange and the second component flange are each formed on a component from the group consisting of a turbine housing, an optional intermediate housing and a receiver housing, wherein a drive shaft extends from the turbine housing through the flange connection into the receiver housing, wherein the drive shaft is driven by a turbine wheel in the turbine housing, and wherein the drive shaft drives a receiver in the receiver housing.

[0029] Especially with turbochargers like these, the simple anti-rotation device with the profile clamp proves particularly advantageous. It can be designed to save space and weight, and the extremely hot components of the turbocharger are prevented from shifting due to relative rotation within the engine compartment. This protects the entire turbocharger periphery, including its inlet and outlet pipes as well as electrical connections. The anti-rotation device is also unaffected by thermal stresses.

[0030] The optional intermediate housing can, in particular, accommodate a bearing with or without a seal for the drive shaft. Alternatively, a bearing with or without a seal for the drive shaft can also be located in the turbine housing or the receiver housing.

[0031] Optionally, the turbocharger may be provided with two flange connections as specified above and below, wherein the first component flange and the second component flange of the first of the two flange connections are formed on a turbine housing and an intermediate housing, and wherein the first component flange and the second component flange of the second of the two flange connections are formed on the intermediate housing and a receiver housing, wherein a drive shaft extends from the turbine housing through the intermediate housing and the two flange connections into the receiver housing, wherein the drive shaft is driven by a turbine wheel in the turbine housing, and wherein the drive shaft drives a receiver in the receiver housing.

[0032] In both single-flange and dual-flange configurations, a seal should be provided between the turbine wheel and the consumer, either in the turbine housing and / or the consumer housing. This seal preferably includes a shaft passage for the drive shaft. Furthermore, the turbine housing preferably has an exhaust gas inlet and an exhaust gas outlet.

[0033] Optionally, the receiver housing can have an air intake and a compressed air outlet, with the receiver being a compressor wheel. This allows compressed combustion air to be supplied.

[0034] Alternatively or additionally, the customer can be a gearbox, especially to form a turbo-compound engine.

[0035] Alternatively or additionally, the consumer can be an electric generator.

[0036] Hybrid forms of these different customers are also conceivable.

[0037] Further features, details and advantages of the invention will become apparent from the wording of the claims and from the following description of exemplary embodiments with reference to the drawings. The drawings show: Fig. 1 shows a cross-section through a flange connection with a profile clamp; Fig. 2 shows a perspective view of the profile clamp. Fig. 1 Fig. 3 a perspective view of a profile clamp not included in the scope of the claims; Fig. 4 a perspective cross-section through a flange connection with a profile clamp not included in the scope of the claims; Fig. 5 a section of a receiver housing with a second component flange; Fig. 6 a section of a cross-section through a receiver housing and a turbine housing arranged adjacent to each other with a first and second component flange; and Fig. 7 a semi-transparent representation of a turbocharger.

[0038] Fig. 1shows a cross-section through a flange connection 50 with a profile clamp 1. This profile clamp is in Fig. 2 Presented in a perspective view. Therefore, identical reference numbers refer to the same features and are described together.

[0039] The profile clamp 1 essentially consists of a profile band 2 that extends in a circumferential direction U around a clamp center Z and has two clamping heads 3, 4. The two clamping heads 3, 4 are connected to each other via a clamping element 5, namely a screw with nut.

[0040] A circumferential groove 10 is formed on an inner surface I of the profile strip 2. The profile groove 10 has a profile strip base 11, which is arranged section by section between groove flanks 12, 13. This gives the profile groove 10 a V-shaped cross-section, which, with a greater width and rounder shape, can also be considered U-shaped. The profile strip 2 is produced by forming a metal plate, and the profile strip 2 itself also has a V-shaped or U-shaped cross-section.

[0041] In the area of ​​a bridge section 14 of the profile strip base 11, the groove flanks 12, 13 are interrupted. The bridge section 14 lies in the circumferential direction U opposite the tension heads 3, 4 and forms a flexible solid hinge.

[0042] The profile clamp 1 has a locking feature 20 on the inside I of the profile band 2 in the area of ​​bridge section 14, extending from the profile band base 11 towards the clamp center Z. The locking feature 20 is a first locking pin 21 that projects from the profile band base 11 towards the clamp center Z. This locking pin 21 is formed as a tooth or prong in one piece by forming it with the profile band 2.

[0043] As can now be seen from the flange connection 50 of the Fig. 1 As can be seen, the locking feature 20, namely the locking pin 21, engages in a recess 53. Therefore, the structure of the component flanges 51, 52 will first be described in more detail using the Fig. 5 and 6 described.

[0044] According to Fig. 6A first and a second component flange 51, 52 are arranged opposite each other in a longitudinal direction L. The component flanges 51, 52 each have an inclined clamping flank which corresponds in particular to the cross-sectional shape of the profile groove 10 and is in contact with the groove flanks 12, 13 for clamping.

[0045] The first and second component flanges 51, 52 each have a recess 53, 54, whereby the recess 54 of the second component flange 52 is also visible in perspective view from Fig. 6 The recesses 53, 54 of the first and second component flanges 51, 52 are arranged opposite each other in the longitudinal direction L and together form a securing recess 55 with a radially outwardly pointing insertion opening 56.

[0046] Into this safety recess 55 after Fig. 6 Security feature 20 now applies according to Fig. 1The profile clamp 1 forms an anti-rotation device between the first and second component flanges 51, 52 by extending into the recesses 53, 54 of the first and second component flanges 51, 52. The profile clamp 1 also clamps the two component flanges 51, 52 together. This clamping occurs primarily in the longitudinal direction L. Transversely to the longitudinal direction L, the component flanges 51, 52 are fixed in position by the fact that component 72 with the second component flange 52 fits into component 71 with the first component flange 52.

[0047] The recesses 53, 54, and thus also the locking recess 55, are designed to be so deep that the recess bases 57, 58 of the recesses 53, 54, pointing towards the clamp center Z, and the locking feature 20 are still slightly spaced apart from each other even after tensioning. The recesses 53, 54 should also be designed to be so wide that the recess walls 59, 60 of the recesses 53, 54, pointing in the longitudinal direction L, and the locking feature 20 are still spaced apart from each other even after tensioning. The locking feature 20 can be seen to have some play in the circumferential direction U within the recesses 53, 54.

[0048] Fig. 3 shows a perspective view of a profile clamp 1, which differs from the design of the safety feature 20. Fig. 1 and 2This differs and therefore does not fall within the scope of protection of the claims. Instead of a safety feature 20 in the area of ​​the bridge section 14, the profile clamp 1 demonstrates Fig. 3 a safety feature 20 on the inside I of the profile strip 2, which projects into the profile groove 10 and in particular from the profile strip base 11 between the groove flanks 12, 13.

[0049] Also the profile clamp 1 after Fig. 4The locking feature 20 differs and is not within the scope of the claims. Here, the locking feature 20 comprises a first and a second locking pin 21, 22, which are arranged at approximately 1 o'clock and 11 o'clock relative to the bridge section 14, and which each project into the profile groove 10 and from the profile band base 11 towards the clamp center Z. Thus, the first and second locking pins 21, 22 are offset from each other in the circumferential direction U. To form the anti-rotation device, the second locking pin 22 also corresponds to a locking recess 61, which is formed by two longitudinally adjacent recesses L in each of the component flanges 51, 52.

[0050] In the case of component 71 with the first component flange 51 of the Fig. 6 This is a section of a turbine housing 71. The component 72 with the second component flange 52 is a section of a customer housing 72.

[0051] Turbine housing 71 and receiver housing 72 can be combined to form a turbocharger 70 according to Fig. 7 belonging to the turbine housing 71 and the receiver housing 72, which are connected to each other by one of the flange connections 50 described above. In the semi-transparent representation of the turbocharger 70 according to Fig. 7It can be seen that a drive shaft 73 extends from the turbine housing 71 through the flange connection 50 into the receiver housing 72. The drive shaft 73 is driven by a turbine wheel 74 in the turbine housing 71. In the receiver housing 72, the drive shaft 73 drives a receiver 75, namely a compressor wheel. A seal is formed between the turbine wheel 74 and the receiver 75 in the turbine housing 71 and / or in the receiver housing 72, so that a compressor chamber in the receiver housing 72 and a drive chamber in the turbine housing are separated from each other. An exhaust gas inlet 76 opens into the drive chamber of the turbine housing 71, and an exhaust gas outlet 77 opens out. On the other side, an air supply connection 78 opens into the compressor chamber of the receiver housing 72, and a compressed air outlet 79 opens out of the compressor chamber.

[0052] The invention is not limited to one of the embodiments described above, but can be modified in a variety of ways. In particular, the number and shape of the locking features and recesses in the component flanges can be adapted by a person skilled in the art to the objectives of the specific technical application. Reference symbol list

[0053] 1 Profile clamp 57 recessed sole 2 Profile band 58 recessed sole 3 chuck 59 recess wall 4 chuck 60 recess wall 5 Clamping element 61 Safety recess 10 Profile groove 70 turbocharger 11 Profiled sole 71 Turbine housing 12 groove flank 72 Customer housing 13 groove flank 73 drive axle 14 bridge section 74 75 Turbine wheel customer 20 Security feature 76 Exhaust gas inlet 21 first safety pin 77 exhaust outlet 22 second safety pin 78 79 Air supply connection, compressed air outlet 50 flange connection 51 first component flange I inside 52 second component flange L Longitudinal direction 53 recess U Circumferential direction 54 recess Z Bell Center 55 Safety recess 56 insertion opening

Claims

1. Flange connection (50) comprising a first and a second component flange (51, 52) which are arranged opposite one another in a longitudinal direction (L), wherein a profile clamp (1) clamps the two component flanges (51, 52) together, wherein the profile clamp (1) comprises a profile strip (2) which extends in a circumferential direction (U) about a clamp centre (Z) and has two clamping heads (3, 4) which are connected to one another via a clamping element (5), wherein a profile groove (10) running in the circumferential direction (U) is formed on an inside (I) of the profile strip (2) and has a profile strip base (11) arranged at least in portions between groove flanks (12, 13), and wherein the profile clamp (1) has a securing feature (20) on the inside (I) of the profile strip (2), which protrudes from the profile strip base (11) in the direction of the clamp centre (7), wherein the first and second component flanges (51, 52) each have a cutout (53, 54), wherein the securing feature (20) protrudes into the two cutouts (53, 54) and thereby prevents twisting between the first and the second component flanges (51, 52), and wherein the securing feature (20) is formed integrally with the profile strip (2), characterized in that the groove flanks (12, 13) are interrupted in the region of a bridging portion (14) of the profile strip base (11), and the securing feature (20) protrudes from the profile strip base (11) in the direction of the clamp centre (Z) in the region of the bridging portion (14).

2. Flange connection (1) according to Claim 1, characterized in that the securing feature (20) has a first securing pin (21) which protrudes from the profile strip base (11) in the direction of the clamp centre (Z).

3. Flange connection (50) according to Claim 2, characterized in that the securing feature (20) has a second securing pin (22) which protrudes into the profile groove (10) and / or from the profile strip base (11) in the direction of the clamp centre (Z), wherein the second securing pin (22) a) is offset to the first securing pin (21) in the circumferential direction (U), and / or b) is offset to the first securing pin (21) in a longitudinal direction (L) of the profile clamp (1) running transversely to the circumferential direction (U).

4. Flange connection (50) according to one of Claims 2 or 3, characterized in that the first and / or second securing pin (21, 22) are from the group bolts, pins, pegs, teeth, tines, mandrels and cams.

5. Flange connection (50) according to any one of the preceding claims, characterized in that the profile strip (2) is formed integrally inclusive of the two clamping heads (3, 4).

6. Flange connection (50) according to any one of the preceding claims, characterized in that the cutouts (53, 54) of the first and second component flanges (51, 52) are arranged opposite one another and together form a securing recess (55) forming an insertion opening (56) facing radially outwards, wherein the securing feature (20) protrudes into the securing recess (55) and prevents twisting in that it extends into the cutouts (53, 54) of the first and second component flanges (51, 52).

7. Flange connection (50) according to any one of the preceding claims, characterized in that the cutouts (53, 54) are made sufficiently deep that cutout bases (57, 58) of the cutouts (53, 54) facing towards the clamp centre (Z) and the securing feature (20) are arranged spaced apart from one another.

8. Flange connection (50) according to any one of the preceding claims, characterized in that the cutouts (53, 54) are designed sufficiently wide that cutout walls (59, 60) of the cutouts (53, 54) facing in the longitudinal direction (L) and the securing feature (20) are arranged spaced apart from one another.

9. Flange connection (50) according to any one of the preceding claims, characterized in that the securing feature (20) has a play in the cutouts (53, 54) in the circumferential direction (U).

10. Turbocharger (70) with a flange connection (50) according to any one of the preceding Claims 1 to 9, wherein the first component flange (51) and the second component flange (52) are each formed on a component of the group turbine casing (71), optional intermediate casing and consumer casing (72), wherein a drive shaft (73) extends from the turbine casing (71) through the flange connection (50) into the consumer casing (72), wherein the drive shaft (73) is driven by a turbine wheel (74) in the turbine casing (71), and wherein the drive shaft (73) drives a consumer (75) in the consumer casing (72).