radial compressor

Abstract

Radial compressor (100), comprising a blower housing (10), an impeller (40) rotatably arranged about an axis in the blower housing (10) and a bursting element (50), wherein the blower housing (10) comprises an inlet channel (20) and a spiral section (30), characterized in that the bursting body (50) is arranged radially outside the inflow channel (20), wherein the bursting body (50) is radially outside the inlet channel (20) in a first area (51) and is radially spaced from the inlet channel (20) in a second area (52), so that a radial deformation gap (60) is formed in the second area (52).

Description

[0001] The invention relates to a radial compressor according to the preamble of claim 1.

[0002] Radial compressors are known in the art. A radial compressor has an impeller that rotates about an axis of rotation and a blower housing that surrounds the impeller. Rapid rotation of the impeller draws in a gas axially and accelerates it radially outwards. Typically, high volume flows can be conveyed and delivered at the outlet of the radial compressor at an overpressure. Radial compressors are used, for example, in exhaust gas turbochargers for internal combustion engines or in industrial ventilation and cooling systems. Their use in pneumatic conveying applications is also known.

[0003] Due to the thermal and mechanical stresses that occur during the operation of a radial compressor, damage to the compressor can occur in rare cases, such as the impeller detaching from the axis of rotation or being damaged in other ways, particularly by bursting. Fragments of the burst impeller, due to their high kinetic energy, can often penetrate the blower housing and cause damage to objects or serious injuries to people.

[0004] To prevent damage or injury in the vicinity of the radial compressor, a rupture hood is often installed around the outside of the blower housing. Alternatively or additionally, a rupture ring is sometimes provided inside the blower housing. Both the rupture ring and the rupture hood serve to contain ruptured impeller fragments and debris within the rupture ring or hood. For this purpose, the rupture ring and hood are typically made of mechanically strong and tough materials, such as steel.

[0005] In this context, for example, a compressor housing made of light metal, ferritic materials, or plastic is known from DE 27 06 110 A1. At least part of the wall of the compressor housing is provided with a cast-in or slip-on reinforcement. The reinforcement can be designed as a perforated steel strip, mesh, spiral winding, or screw winding.

[0006] German patent DE 10 2014 012 123 A1 discloses a compressor for compressing charge air for an exhaust gas turbocharger. The compressor comprises a multi-part compressor housing joined by a screw connection and a compressor rotor positioned within the compressor housing and coupled to the turbine rotor. Housing components of the multi-part compressor housing are clamped against each other using C-shaped clamps. The clamps are easy to manufacture and provide effective burst protection, allowing existing exhaust gas turbochargers to be easily retrofitted.

[0007] From EP 0 834 646 A1, a burst protection device for radial turbines of turbochargers is known. According to EP 0 834 646 A1, a first burst protection device is arranged radially between a gas inlet housing and a gas outlet housing, but excluding the guide vane channel. A second burst protection device is arranged on the gas inlet housing.

[0008] US patent 2012 / 0039703 A1 discloses a fragment containment arrangement for a turbine, comprising a plurality of bands arranged around a turbine cover to prevent debris from being released outside the bands in the event of turbine damage. The bands are wound spirally around the outer circumference of the cover and exhibit comparatively higher toughness than the cover, particularly at high temperatures.

[0009] DE 10 2020 213 708 A1 describes a turbine arrangement for an exhaust gas turbocharger. The turbine arrangement comprises a turbine housing which circumferentially surrounds a turbine wheel, wherein the turbine housing has an insert recess open on the downstream side in which a burst ring is arranged, which extends circumferentially around the turbine wheel and axially at least to a center of gravity of the turbine wheel.

[0010] However, the known burst protection devices are disadvantageous in that they require a comparatively high amount of material and are therefore correspondingly heavy and expensive.

[0011] It is an object of the present invention to propose an improved radial compressor.

[0012] This problem is solved according to the invention by the radial compressor according to claim 1. Advantageous embodiments and further developments of the invention are described in the dependent claims.

[0013] The invention relates to a radial compressor comprising a blower housing, an impeller rotatably arranged in the blower housing about an axis, and a bursting element, wherein the blower housing comprises an inlet channel and a spiral section.

[0014] The invention proposes a radial compressor which, in addition to a blower housing, also includes an impeller arranged within the blower housing. The impeller is rotatably mounted about an axis within the blower housing in order to convey a gas, in particular air, by means of turbine blades arranged on the impeller. For example, the impeller can be driven by an electric motor or a turbine.

[0015] The blower housing is preferably formed in one piece, particularly as a sand-cast component made of a light metal alloy, but comprises two functionally separate elements. A first of these elements is the inlet channel, which is essentially tubular or hollow cylindrical and is designed to allow a gas, particularly air, to flow into the blower housing towards the impeller.

[0016] A second of these elements is the spiral section, which is arranged radially outside the impeller and provides the air or gas accelerated by the impeller for further use via an outlet opening.

[0017] Furthermore, the radial compressor also includes a rupture element. The rupture element is designed to prevent debris and fragments from escaping the blower housing in the event of an impeller rupture, particularly if fragments or splinters are ejected from the impeller. The rupture element thus performs a crucial safety function, as the high rotational speed of the impeller means that any fragments or splinters detached from it can possess very high kinetic energy. This means that the ejected fragments and splinters are capable of causing significant damage to objects and serious injuries to people in their vicinity.

[0018] The presence of the bursting element also makes it advantageous to design the blower housing to be comparatively thin and lightweight, since the blower housing itself does not need to be designed to prevent fragments and debris breaking off from the impeller from exiting the blower housing in the event of a burst. This function is instead performed by the bursting element.

[0019] This allows the manufacturing costs of the radial compressor to be kept low and enables comparatively easy handling of the radial compressor during assembly or in case of service.

[0020] The bursting body is preferably formed in one piece.

[0021] According to the invention, it is now provided that the bursting body is arranged radially outside the inlet channel, wherein the bursting body is radially adjacent to the inlet channel in a first area and is radially spaced from the inlet channel in a second area, so that a radial deformation gap is formed in the second area.

[0022] By arranging the bursting element radially outside the inlet channel, preferably exclusively radially outside the inlet channel and not radially outside the spiral section, the bursting element can also be designed to be comparatively compact and lightweight. This further contributes to low manufacturing costs and a low overall weight of the radial compressor according to the invention.

[0023] The invention takes advantage of the fact that fragments and debris detaching from the impeller in the spiral section generally do not possess sufficient kinetic energy to penetrate the housing radially outwards. As is known, the spiral section is significantly larger and more extensive radially and contains considerably more material surrounding the impeller than the inlet channel. Therefore, the arrangement of a bursting element in the spiral section is advantageously unnecessary.

[0024] In contrast, there is significantly less material radially outside the impeller in the area of ​​the inlet duct. This makes it much easier for fragments and debris breaking off from the impeller to penetrate the blower housing in the inlet duct area and cause damage or injury to objects and people in the vicinity of the radial compressor.

[0025] According to the invention, by arranging the bursting body radially outside the inlet channel, the escape of splinters and debris from the impeller from the blower housing can now also be reliably prevented here.

[0026] By placing the bursting body radially outside the inlet channel in a first area, a connection between the bursting body and the outer wall of the inlet channel can also be advantageously established.

[0027] In a second area of ​​the bursting element, however, the bursting element does not rest against the inlet channel. Specifically, the outer contour of the inlet channel tapers to follow the contour of the impeller. The bursting element, however, advantageously does not follow this taper, so that a radial deformation gap is formed between the outer contour of the inlet channel and the bursting element.

[0028] The advantage of the deformation gap is that it allows the blower housing to deform radially outwards in the area of ​​the inlet channel before the blower housing is forced against the bursting body in this area, thus preventing further deformation of the inlet channel by the bursting body.

[0029] This deformation movement of the blower housing allows for the additional absorption of kinetic energy from a splinter or fragment that has detached from the impeller and its conversion into deformation energy at the inlet duct. Thus, the splinter or fragment already possesses reduced energy upon reaching the rupture body. This, in turn, makes it possible to design the rupture body for comparatively lower kinetic energies of the splinters and fragments, allowing the rupture body to be made even lighter and thinner.

[0030] Advantageously, the second section of the bursting element is arranged axially at the same position on the blower housing as the impeller. The first section of the bursting element, however—that is, the section that does not form a deformation gap with the blower housing—advantageously has an axial offset from the impeller. Since fragments and debris breaking off from the impeller are typically ejected radially without any axial motion, the first section of the bursting element generally does not need to retain any impeller fragments or debris. Rather, its primary function is to secure the bursting element to the inlet duct.

[0031] According to a preferred embodiment of the invention, it is provided that a material of the bursting body has a higher material toughness and / or material strength than a material of the impeller and / or than a material of the blower housing.

[0032] Material strength is the ability of a material to withstand external mechanical stresses such as tension, compression, or bending without failing, i.e., without permanently deforming or breaking. Material strength is generally an important material property and is also defined as the maximum stress a material can withstand before it yields.

[0033] Material toughness, on the other hand, is a material's ability to absorb energy and deform plastically without breaking, making it a measure of its resistance to fracture or crack propagation. Unlike brittle materials, which can absorb little energy, tough materials, such as many metals, can absorb significant amounts of energy and thus withstand mechanical stresses more effectively.

[0034] By using a rupture body with a higher material toughness or strength than the impeller material, it is ensured that the fragments and debris detached from the impeller are highly unlikely to penetrate the rupture body. Instead, the high energy of the rupture causes the impeller fragments and debris to deform upon impact with the rupture body and potentially break further.

[0035] Furthermore, by ensuring that the bursting body also has a higher material toughness or higher material strength than the material of the blower housing, it can also be prevented that fragments of the blower housing, which are knocked out of the blower housing by splinters or debris from the impeller, can penetrate the bursting body.

[0036] According to a particularly preferred embodiment of the invention, the material of the bursting body is steel and / or a wrought alloy.

[0037] Steels typically exhibit comparatively high material strength and toughness compared to other metals. Therefore, steel is particularly well-suited as a material for manufacturing the bursting body.

[0038] The steel may also be a steel alloy.

[0039] A wrought alloy is a material specifically designed to be shaped by forming processes such as forging, rolling, bending, or extrusion, rather than being cast. Unlike cast alloys, which are intended for casting, wrought alloys are shaped through mechanical processing and are therefore suitable for applications requiring high strength and precision.

[0040] Wrought alloys of this type typically exhibit increased material strength and toughness compared to other materials, such as cast alloys.

[0041] According to a further particularly preferred embodiment of the invention, the material of the impeller is a wrought light metal alloy and the material of the blower housing is a sand-cast light metal alloy.

[0042] For example, the light metal wrought alloy and the light metal sand casting alloy can be different aluminum or magnesium alloys.

[0043] Lightweight metal alloys generally have a low weight, allowing the radial compressor to be designed to be relatively lightweight overall. This simplifies assembly and repairs during servicing.

[0044] Furthermore, the blower housing in particular can be manufactured relatively cost-effectively, with high precision and in large quantities using the sand casting process.

[0045] Alternatively, it is also possible, preferably, to manufacture the blower housing or impeller using a die-casting process, in particular from a light metal die-casting alloy.

[0046] According to a further particularly preferred embodiment of the invention, it is provided that the material of the impeller and the material of the blower housing have an identical or similar thermal expansion.

[0047] This ensures that, on the one hand, a temperature change and the resulting thermal expansion of the impeller and the blower housing will not cause the impeller to strike the blower housing, and on the other hand, that the gap between the blower housing and the impeller will not become undesirably large. The former would damage or destroy the radial compressor, and the latter would at least reduce the efficiency of the radial compressor.

[0048] However, by ensuring that the material of the impeller and the material of the blower housing have an identical or at least similar coefficient of thermal expansion, it can be guaranteed that the contour gap remains essentially at the desired size during temperature changes.

[0049] According to a further preferred embodiment of the invention, the bursting body is provided to have a cylindrical shape.

[0050] Due to its cylindrical shape, the bursting element can be positioned radially on the outside of the typically also essentially cylindrical inlet channel. This allows the bursting element to be mounted relatively easily on the blower housing.

[0051] Furthermore, the cylindrical shape of the bursting body ensures a comparatively simple and cost-effective manufacturing process.

[0052] According to a further preferred embodiment of the invention, the bursting body is attached to the inlet channel in the first area.

[0053] Since the bursting element does not form a deformation gap with the blower housing in its first section, it lies flat against the inlet channel of the blower housing in this area. Therefore, the first section of the bursting element is well suited for establishing a mechanically robust connection to the blower housing.

[0054] According to a particularly preferred embodiment of the invention, it is provided that the bursting body is detachably fastened in the first area by means of a screw connection.

[0055] Screw connections allow for the simple creation of a robust connection. Furthermore, since screw connections are detachable, the bursting element can be removed from the blower housing for maintenance or servicing.

[0056] Screws are also relatively inexpensive and widely available in different sizes and thicknesses.

[0057] Furthermore, the arrangement of the bursting element by means of a screw connection also makes it possible, in principle, to retrofit a bursting element to radial compressors that have already been delivered and put into operation.

[0058] According to an alternative particularly preferred embodiment of the invention, it is provided that the bursting body is permanently attached in the first area by means of a shrink connection.

[0059] A shrink connection has the advantage that it guarantees a secure fit of the bursting body to the inlet channel without the need for any additional aids or fasteners.

[0060] Because the bursting element is permanently attached to the blower housing, it is impossible to accidentally forget to reattach it after maintenance or repair work. This prevents damage and accidents that could otherwise occur if the bursting element is not reattached.

[0061] According to a further preferred embodiment of the invention, the bursting body has a collar-shaped third area with which the bursting body rests axially against the spiral section.

[0062] This also prevents fragments and debris that break off from the impeller from leaving the blower housing. The safety of the radial compressor in the event of a burst is thus further increased.

[0063] According to a particularly preferred embodiment of the invention, it is provided that the bursting body is attached to the spiral section in the third area.

[0064] This further improves the strength of the connection between the bursting element and the blower housing. In particular, this also prevents splinters or debris that break off from the impeller and penetrate the blower housing from deforming or bending the bursting element to such an extent that they subsequently emerge axially from the bursting element and enter the environment.

[0065] Because the bursting element is connected to the blower housing in the first and third areas, it is virtually impossible for splinters or debris detached from the impeller to bend the bursting element away from the blower housing in the first or third area.

[0066] Since the second area is located midway between the first and third areas, the second area can only be bent away from the inlet channel as far as the first and third areas, which are anchored to the blower housing, mechanically allow due to deformations.

[0067] According to a further particularly preferred embodiment of the invention, it is provided that the bursting body is detachably fastened in the third area by means of a screw connection.

[0068] As previously described, screw connections allow for the simple creation of a reliable and robust connection. The fact that screw connections can be loosened allows the bursting element to be detached from the blower housing for maintenance or servicing.

[0069] The connection of the bursting body to the blower housing at two points, namely in the first and third area, offers the further advantage that even a complete tearing off of the inlet channel from the spiral section can be prevented, since in this case the inlet channel is held on the spiral section by the bursting body.

[0070] If, for example, relatively large and wedge-shaped fragments of the impeller or impeller hub break off, they can, in principle, separate the inlet channel axially from the spiral section by tearing it open all the way around. However, the bursting element, which connects the inlet channel and the spiral section, prevents the inlet channel from being thrown away from the blower housing uncontrollably and endangering people and objects.

[0071] According to a further preferred embodiment of the invention, the bursting body comprises at least two connectable body segments.

[0072] The at least two connectable body segments can, for example, each be designed as a half-cylinder.

[0073] Advantageously, the at least two connectable body segments can also have connecting surfaces or other overlapping areas in order to be able to connect the body segments to each other, for example by means of screw connections.

[0074] This offers the advantage that the bursting element does not have to be pushed axially across the entire inlet channel, but can be mounted directly at its location on the inlet channel.

[0075] This also allows, for example, the arrangement of the bursting body on an inlet channel that has radial projections which would otherwise prevent the bursting body from being pushed onto the inlet channel.

[0076] Furthermore, this design of the bursting body also facilitates the easy retrofitting of already delivered and commissioned radial compressors with the bursting body.

[0077] According to a further preferred embodiment of the invention, the inlet channel is formed in two parts, consisting of a rear inlet section integrally connected with the spiral section and a front inlet section connected with the rear inlet section, wherein a radial outer circumference of the rear inlet section is less than or equal to a radial inner circumference of the bursting body and wherein a radial outer circumference of the front inlet section is larger than the radial inner circumference of the bursting body.

[0078] In this case, the inlet duct, and therefore the blower housing, is made of two parts. The rear inlet section is permanently connected to the spiral section of the blower housing and is formed as a single piece with it.

[0079] The front inlet section, however, is an independent component that must be connected to the rear inlet section during assembly of the radial compressor. Since the rupture element rests radially against the rear inlet section, its inner diameter corresponds to the outer diameter of the rear inlet section.

[0080] The two-part design of the inlet channel makes it possible to first slide the bursting body axially onto the rear inlet section before the front inlet section is positioned on the rear inlet section and connected to it.

[0081] This makes it possible for the front inlet section to have a larger outer diameter than the rear inlet section and than the inner diameter of the bursting body, without preventing the bursting body from being mounted on the inlet channel.

[0082] According to a further preferred embodiment of the invention, the bursting element is cast into the blower housing.

[0083] This represents an alternative embodiment of the arrangement of the rupture element on or in the blower housing. Since the rupture element is cast into the blower housing in this case—that is, it is already positioned within the blower housing during the casting process—the rupture element is permanently connected to the blower housing. Otherwise, the advantages already mentioned apply.

[0084] The invention is explained below by way of example with reference to embodiments shown in the figures.

[0085] They show: Fig. 1. An exemplary and schematic representation of a possible embodiment of a radial compressor according to the invention in a perspective view. Fig. 2. Exemplary and schematic representation of the radial compressor of the Fig. 1 in a sectional view, Fig. 3. An exemplary and schematic embodiment of a bursting body for a radial compressor according to the invention.

[0086] Identical objects, functional units, and comparable components are designated across all figures using the same reference symbols. These objects, functional units, and comparable components are identical in their technical characteristics unless explicitly or implicitly stated otherwise in the description.

[0087] Fig. Figure 1 shows, by way of example and schematically, a possible embodiment of a radial compressor 100 according to the invention in a perspective view.

[0088] The radial compressor 100 of Fig. 1 comprises a blower housing 10, which includes an inlet channel 20 and a spiral section 30. Furthermore, the radial compressor 100 comprises an impeller 40 rotatably arranged about an axis within the blower housing 10, as shown in the view of the Fig. However, only a portion of it can be seen.

[0089] When the impeller 40 rotates, air is drawn into the blower housing 10 through an inlet opening 21 of the inlet channel 20. The drawn-in air is radially compressed by the impeller 40 and forced into the spiral section 30, where it is made available for further use via the outlet opening 31 at a low overpressure of, for example, 1.5 bar.

[0090] Finally, the radial compressor comprises 100 of the Fig. 1 also a bursting body 50. As can be seen, the bursting body 50 is arranged radially outside the inlet channel 20.

[0091] The bursting body 50 comprises a first area 51, a second area 52 and a third area 53.

[0092] The first section 51 and the second section 52 are cylindrical in shape. The third section 53, however, connects to the second section 52 in a collar-like manner and rests against the spiral section 30 of the blower housing 10.

[0093] The first area 51 of the bursting body 50 is located axially in front of the second area 52 and in the area of ​​screws 54, by means of which the first area 51 of the bursting body 50 is detachably connected to the inlet channel 20.

[0094] The second area 52 of the bursting body 50 separates the first area 51 of the bursting body 50 axially from the third area 53 of the bursting body 50.

[0095] The third area 53 also has screws 54 by means of which the bursting body 50 in the third area 53 is detachably connected to the spiral section 30 of the blower housing 10.

[0096] According to the exemplary embodiment of the Fig. 1 The inlet channel 20 is designed in two parts. It comprises a rear inlet section 23, which is integrally connected to the spiral section 30, and a front inlet section 22, which is connected to the rear inlet section 22, for example, by joining. The bursting element 50 is located exclusively in the area of ​​the rear inlet section 23.

[0097] The inner diameter of the bursting body 50 corresponds to the outer diameter of the rear inlet section 23. However, the front inlet section 22 has a larger radial outer circumference than the rear inlet section 23 and thus a larger radial outer circumference than the inner circumference of the bursting body 50.

[0098] During the assembly of the exemplary radial compressor 100 of the Fig. Therefore, the bursting element 50 must first be positioned and mounted on the rear inlet section 23 before the front inlet section 22 is joined to the rear inlet section 23. Otherwise, it would no longer be possible to position the bursting element 50, which is formed as a single piece, on the inlet channel 20.

[0099] For example, the blower housing 10, i.e., the inlet channel 20 and the spiral section 30, is made of a light metal sand-casting alloy, namely an aluminum sand-casting alloy. The impeller 40 is made of a light metal wrought alloy, namely an aluminum wrought alloy. Since both the blower housing 10 and the impeller 40 are thus essentially made of aluminum, it is ensured that the impeller 40 and the blower housing 10 exhibit identical thermal expansion in response to temperature changes.

[0100] The bursting body 50, for example, is made of a forged steel alloy. This steel alloy has a significantly higher material strength and toughness than the aluminum alloys from which the blower housing 10 and the impeller 40 are made.

[0101] In the event of a bursting of the impeller 40, whereby splinters and debris are uncontrollably detached from the impeller 40 and ejected radially, it is not possible to reliably guarantee, due to the high kinetic energy of these splinters and debris and the comparatively low material strength and toughness of the blower housing 10, that the splinters and debris remain within the inlet channel 20 and that no objects outside the blower housing 10 are damaged and, in particular, no persons are injured.

[0102] The bursting body 50 can only ensure that the fragments and debris of the impeller 40 are safely contained within the inlet channel 20.

[0103] Since the invention recognizes that the fragments and debris detached from the impeller 40 generally do not possess sufficient kinetic energy to penetrate the significantly larger and more robust spiral section 30 of the blower housing 10, the bursting element 50 is arranged exclusively in the area of ​​the inlet channel 20. This allows for savings in material, weight, and manufacturing costs.

[0104] Thus, the safety of the radial compressor 100 according to the invention can be significantly increased in operation with a comparatively small and lightweight bursting body 50.

[0105] Fig. Figure 2 shows, by way of example and schematically, the radial compressor 100 of the Fig. 1 in a sectional view.

[0106] It can be seen in Fig. 2, in particular, that the bursting body 50 rests radially on the outside of the inlet channel 20 in a first region 51. In the first region 51, the bursting body 50 is detachably connected to the inlet channel 20 via the screw connections already described. Likewise, in the third region 53, the bursting body 50 is detachably connected to the spiral section 30 via the screw connections already described.

[0107] In the second region 52 of the bursting body 50, however, the bursting body 50 does not rest against the inlet channel 20, but is radially spaced from it. This creates a radial deformation gap 60 between the bursting body 50 and the inlet channel 20 in the second region 52.

[0108] The deformation gap 60 allows the blower housing 10 to deform radially outwards in the area of ​​the inlet channel 20, thus enabling greater energy absorption than would occur through a simple rupture of the inlet channel 20 wall. This further slows down any fragments and debris that have detached from the impeller 40 and prevents them from exiting the blower housing 10. This additional energy absorption through the deformation gap 60, in turn, allows the rupture body 50 to be made comparatively lighter and thinner. Thus, material, weight, and manufacturing costs can be saved without reducing the operational reliability of the radial compressor 100 according to the invention.

[0109] This can also be clearly seen in Fig. 2 also the two-part inlet channel 20 with the front inlet section 22 and the rear inlet section 23.

[0110] The front inlet section 22 and the rear inlet section 23 overlap axially and radially in sections. For example, the front inlet section 22 is permanently attached to the rear inlet section 23 by means of a joining process.

[0111] Fig. Figure 3 shows, by way of example and schematically, a possible embodiment of a bursting body 50 for a radial compressor 100 according to the invention.

[0112] As can be seen, the bursting body 50 is formed in one piece. It comprises a first region 51 and a second region 52, which merge into one another and have a cylindrical shape.

[0113] Furthermore, the bursting body 50 also includes a third section 53, which connects to the second section 52 like a collar and extends radially outwards. The first section 51 and the third section 53 each have openings 55 through which screws 54 can be inserted to form screw connections with corresponding threaded openings on the blower housing 10.

[0114] For example, the bursting body 50 is made of a steel alloy and is manufactured by forging. Reference symbol list 100 radial compressors 10 blower housings 20 Inlet channel 21 Entrance 22 front inlet section 23 rear inlet section 30 spiral section 31 Outlet opening 40 wheel 50 burst bodies 51 first area of ​​the bursting body 52 second area of ​​the bursting body 53 third area of ​​the bursting body 54 screw 55 Opening 60 Deformation gap QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] DE 27 06 110 A1

[0005] DE 10 2014 012 123 A1

[0006] EP 0 834 646 A1

[0007] US 2012 / 0039703 A1

[0008] DE 10 2020 213 708 A1

[0009]

Claims

[1] Radial compressor (100), comprising a blower housing (10), an impeller (40) rotatably arranged about an axis in the blower housing (10) and a bursting element (50), wherein the blower housing (10) comprises an inlet channel (20) and a spiral section (30), characterized by , that the bursting body (50) is arranged radially outside the inlet channel (20), wherein the bursting body (50) is radially outside the inlet channel (20) in a first area (51) and is radially spaced from the inlet channel (20) in a second area (52), so that a radial deformation gap (60) is formed in the second area (52). [2] Radial compressor (100) according to claim 1, characterized by , that a material of the bursting body (50) has a higher material toughness and / or material strength than a material of the impeller (40) and / or than a material of the blower housing (10). [3] Radial compressor (100) according to claim 2, characterized by , that the material of the bursting body (50) is a steel and / or a wrought alloy. [4] Radial compressor (100) according to at least one of claims 2 and 3, characterized by , that the material of the impeller (40) is a wrought light metal alloy and the material of the blower housing is a sand-cast light metal alloy. [5] Radial compressor (100) according to at least one of claims 2 to 4, characterized by , that the material of the impeller (40) and the material of the blower housing (10) have identical or similar thermal expansion. [6] Radial compressor (100) according to at least one of claims 1 to 5, characterized by , that the bursting body (50) has a cylindrical shape. [7] Radial compressor (100) according to at least one of claims 1 to 6, characterized by , that the bursting body (50) is attached to the inlet channel (20) in the first area (51). [8] Radial compressor (100) according to claim 7, characterized by , that the bursting body (50) is detachably fastened in the first area (51) by means of a screw connection (54). [9] Radial compressor (100) according to claim 7, characterized by , that the bursting body (50) is permanently attached in the first area (51) by means of a shrink connection. [10] Radial compressor (100) according to at least one of claims 1 to 9, characterized by , that the bursting body (50) has a collar-shaped third area (53) with which the bursting body (50) axially abuts the spiral section (30). [11] Radial compressor (100) according to claim 10, characterized by , that the bursting body (50) is attached to the spiral section (30) in the third area (53). [12] Radial compressor (100) according to claim 11, characterized by , that the bursting body (50) is detachably fastened in the third area (53) by means of a screw connection. [13] Radial compressor (100) according to at least one of claims 1 to 12, characterized by , that the bursting body (50) comprises at least two connectable body segments. [14] Radial compressor (100) according to at least one of claims 1 to 13, characterized by , that the inlet channel is formed in two parts, consisting of a rear inlet section (23) integrally connected with the spiral section (30) and a front inlet section (22) connected with the rear inlet section (23), wherein a radial outer circumference of the rear inlet section (23) is less than or equal to a radial inner circumference of the bursting body (50) and wherein a radial outer circumference of the front inlet section (22) is larger than the radial inner circumference of the bursting body (50). [15] Radial compressor (100) according to at least one of claims 1 to 6, characterized by , that the bursting body (50) is cast into the blower housing (10).

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