Scrollmaschine

Abstract

A scroll machine (1) for carbon dioxide as a refrigerant is described. The scroll machine (1) has - a first scroll (4) with a first spiral wall (14) projecting in an axial direction (A), - a second scroll (6) with a second spiral wall (16) projecting in the axial direction (A), - a drive, - a drive shaft (7) by means of which the drive and the second scroll (6) are coupled for power transmission, and - a bearing plate (32) which is connected between the drive and the second scroll (6) and which is formed in two parts from an outer part (60) and an inner part (62) which is bordered radially on the outside at least in regions by the outer part (60), wherein the outer part (60) carries a bearing (12) for the drive shaft (7), wherein the inner part (62) is coupled to the second scroll (6) via an anti-rotation mechanism. The outer part (60) is pressed into the inner part (62) with a web (70). Furthermore, the outer part (60) is made of aluminum, and the inner part (62) is made of steel or cast iron.

Description

[0001] The invention relates to a scroll machine, in particular a scroll machine for carbon dioxide as a refrigerant, preferably a vehicle air conditioning system.

[0002] Motor vehicles are regularly equipped with air conditioning systems that use a system forming a refrigerant circuit to cool the vehicle interior. Such systems generally have a circuit containing a refrigerant. The refrigerant, for example R-744 (carbon dioxide, CO2) or R-134a (1,1,1,2-tetrafluoroethane), is heated in an evaporator and compressed by a (refrigerant) compressor. The refrigerant then releases the absorbed heat via a heat exchanger before being returned to the evaporator via a throttle.

[0003] A so-called scroll machine is often used as a refrigerant compressor to compress the refrigerant. The design and operation of such a scroll machine, used as a compressor for the refrigerant in a motor vehicle air conditioning system, is described, for example, in DE 10 2012 104 045 A1. Key components of such a scroll machine are two scroll parts (“scrolls”) that can move relative to one another. The system usually also contains oil in droplet form or as a mist, which is at least partially separated from the refrigerant (which is usually gaseous after compression) after compression. The refrigerant (possibly with residues of oil) is then introduced into the air conditioning circuit, while the separated oil can usually be fed to the moving parts within the scroll machine to lubricate them.The scroll components are typically designed as a stationary, fixed scroll (fixed scroll, displacement scroll) and a movable, orbiting scroll (counter scroll, rotor scroll). Both scrolls are fundamentally similar in design and each comprise a base plate (main body, scroll disk) and a spiral (worm-shaped) wall (spiral wall, scroll wall) extending axially from the base plate. When assembled, the spiral walls of the two scrolls are nested within each other, forming several conveying chambers between the scroll walls, which touch each other in sections.

[0004] To drive the movable scroll, an electric motor is typically provided, the motor shaft of which (A-side, i.e. output side) is coupled to the movable scroll part by means of an eccentric shaft journal (also: “shaft pin”).

[0005] An orbiting movement, here and in the following, is understood in particular to mean an eccentric, circular movement path in which the movable scroll itself does not rotate about its own axis. During operation, the two scrolls are kept as close to each other as possible axially. During each orbiting movement, essentially crescent-shaped (compression or delivery) chambers are formed between the spiral walls. As the two scrolls move toward each other (at least during a compression process), their volume migrates from the outside along the spiral walls toward the center axis of the respective scroll, thereby progressively reducing the volume (and thus compressing the medium contained within).

[0006] The orbiting movement of the movable scroll is usually achieved, among other things, by an anti-rotation mechanism, which prevents the scroll from rotating on its own. This is usually connected between the movable scroll and a stationary element of the scroll machine. The anti-rotation mechanism is often formed by a number of circular, pocket-like openings ("rings") arranged on a circular path, usually in the movable scroll, and associated pins ("pins"), usually arranged in the stationary element. The pins engage in the circular openings of the movable scroll, each forming a so-called pin-ring contact. During (compressor) operation, the pins slide along the circular opening walls, preventing self-rotation. To reduce friction and improve service life, race rings (sliding rings), for example, are inserted into the openings.Due to this design, the anti-rotation mechanism is also called a “pin-ring system”.

[0007] The motor shaft is usually mounted in a bearing plate (also called a "center plate") by means of a bearing. The pins of the anti-rotation mechanism are usually fixed (especially force-locked) in the bearing plate.

[0008] Carbon dioxide as a refrigerant requires higher pressures than chemical refrigerants (e.g., R-134a), so sufficiently high strength cannot often be achieved with aluminum as the material for the scrolls. A related problem is the connection components, which are preferably made of aluminum and therefore often exhibit different thermal expansion behavior.

[0009] The invention is based on the object of providing a particularly suitable scroll machine.

[0010] This object is achieved according to the invention by a scroll machine having the features of claim 1. Advantageous and partly inventive embodiments and developments of the invention are set out in the subclaims and the following description.

[0011] The scroll machine according to the invention is designed and intended for use with carbon dioxide as a refrigerant. Preferably, the scroll machine is designed and intended for use as a compressor for this refrigerant in a vehicle air conditioning system. For this purpose, the scroll machine has a first scroll with a first spiral wall protruding in an axial direction and a second scroll with a second spiral wall protruding in the axial direction. At least the second scroll is made of steel or cast iron. In particular, the two spiral walls interlock, so that compression or delivery chambers are formed between the contact points of the spiral walls. Furthermore, the scroll machine has a drive and a drive shaft, by means of which the drive and the second scroll are coupled for power transmission.The scroll machine also has a bearing shield that is connected between the drive and the second scroll and is made of two parts: an outer part and an inner part that is at least partially radially bordered on the outside by the outer part. The outer part carries a bearing for the drive shaft. The inner part is coupled to the second scroll via an anti-rotation mechanism. The outer part is pressed into the inner part by a web (which is in particular part of the outer part). Furthermore, the outer part is made of aluminum and the inner part is made of a material with the same or at least a comparable coefficient of thermal expansion as the steel or cast iron of the second scroll.

[0012] According to a preferred embodiment, the first scroll is also made of steel or cast iron, preferably the same steel or cast iron as the second scroll. Constructing at least the second scroll, preferably both scrolls, of steel or cast iron allows for greater strength compared to scrolls typically made of aluminum and is thus advantageous for the higher pressures when using CO2 as a refrigerant (especially compared to chemical refrigerants).

[0013] Optionally, the inner part is also made of steel or cast iron, optionally from the same steel or cast iron as the second scroll.

[0014] The invention has the advantage that the outer part of the bearing shield offers weight advantages and ease of machining due to its material, while the inner part exhibits comparable thermal expansion behavior to the second scroll, preferably to both scrolls. This prevents tension or jamming between the second scroll and the bearing shield during operation, especially at elevated temperatures, which usually occur during operation.

[0015] By “a comparable thermal expansion coefficient” is meant here and in the following in particular that the thermal expansion coefficient is within a range of up to + / - 4 × 10 -6 K -1 , preferably up to + / - 3 × 10 -6 K -1 , preferably up to + / - 2 × 10 -6 K -1 or less than the value of the thermal expansion coefficient of the steel or cast iron of the scroll(s).

[0016] For example, the value of the thermal expansion coefficient of the cast iron of the scroll(s) is approximately 10.5 × 10 -6 K -1 (+ / - 2 × 10 -6 K -1 ). The value of the steel of the scroll(s), for example, is in a range between approximately 11 and 16 × 10 -6 K -1 .

[0017] The steel used can optionally be a structural steel, a low-alloy steel, a high-alloy steel, a stainless steel (e.g., a chromium steel), a stainless steel, or the like. Preferably, a steel is used whose thermal expansion coefficient is significantly higher—that is, by at least 6 × 10 -6 K -1 - is lower than that of the aluminum of the outer part.

[0018] According to a preferred embodiment, a joining surface of the web (preferably each one in the case of several such joining surfaces) is directed radially outwards towards the inner part. Here and in the following, a joining surface is understood to mean, in particular, a surface via which a joining force is transmitted between the components to be joined. A contact force therefore acts radially inwards from the inner part onto the outer part - at least onto its web. As a result, the outer part is clamped by the inner part in a pincer-like manner. This is advantageous in that the outer part expands more than the inner part due to its larger coefficient of thermal expansion, and thus the clamping force continues to increase with increasing operating temperatures. Local operating temperatures in the area of ​​the bearing shield, particularly in a backpressure chamber formed in the bearing shield, are usually between 90 and 110 degrees Celsius for CO2 as a refrigerant.

[0019] Preferably - especially in this case - a pressure (preferably press fit or interference fit) between the web of the outer part and the inner part is set such that in an unused state (i.e. at room temperature or at least a temperature value lower than usual operating temperatures) a low contact pressure value (also: joining force value) is present. In particular, in a normal operating state and thus at a high temperature value, an increased contact pressure value is present. This in turn has the advantage that assembly of the bearing shield is simplified because at usual assembly temperatures only a comparatively low assembly force needs to be applied or at least no effort, such as heating a joining partner, is required.

[0020] According to a particularly expedient embodiment, the web is designed as an annular web, i.e., in particular, as an annular, preferably circular, and expediently also closed web. Furthermore, this annular web engages in an annular groove or bore in the inner part. The annular web enables the inner part to be centered relative to the outer part in a particularly simple manner.

[0021] For a tangential alignment of the inner part with respect to the outer part, a positive locking mechanism is preferably used. In particular, the outer part has a (preferably non-circular or asymmetrical) positioning recess (e.g., a slotted hole or similar) as a positive locking element, in which a corresponding (positive locking) element of the inner part is inserted. Conventional positioning pins are unsuitable in this case, since the different material pairings of the two bearing shield parts would cause the positioning pins to be subjected to comparatively strong tension as they heat up, which in turn can lead to damage.

[0022] Alternatively, the ring land can also be non-circular, for example, polygonal (preferably with rounded corners) or elliptical, so that the ring land allows not only centering but also alignment in the tangential direction. In this case, the ring groove is designed accordingly.

[0023] According to a practical embodiment, the inner part has a mating contact surface against which the web of the outer part (in particular with its joining surface) is pressed in the assembled state. Radially outside this mating contact surface, the inner part advantageously has a relief groove. This allows stresses caused by an increased joining or contact force—preferably in the intended operating state and thus in particular due to increased pressure compared to room temperature—to be reduced. For example, the relief groove is introduced into the inner part approximately parallel to the mating contact surface.

[0024] According to a further expedient embodiment, the outer part has an outer ring to which the web is integrally connected—in particular by means of a connecting piece also referred to as a bridge. In particular, openings or channels are incorporated between the web and the outer ring (i.e., in particular, in the bridge) through which the coolant can flow from a drive area of ​​the scroll machine into the conveying or compressor area during normal operation.

[0025] It is advisable to provide a rounded groove at the base of the web's joining surface, i.e., particularly in the area where the web's joining surface and the web itself are connected to the outer ring—i.e., particularly at the transition to the bridge. Such a groove or fillet helps reduce stress peaks at transitions.

[0026] According to a preferred embodiment, the outer ring described above forms an element of a housing of the scroll machine. The inner part is shielded from environmental influences by this outer ring. For this purpose, too, the outer part is made of aluminum, as this has a lower tendency to corrosion than cast iron (or at least low-alloy steel).

[0027] "Form fit" or a "form-locking connection" between at least two interconnected parts is understood here and below in particular to mean that the interconnected parts are held together at least in one direction by a direct interlocking of the contours of the parts themselves or by an indirect interlocking via an additional connecting part. The "blocking" of mutual movement in this direction is therefore due to the shape.

[0028] In the following, exemplary embodiments of the invention are explained in more detail with reference to a drawing. In the drawings: Fig. 1 shows a partial sectional view of a scroll machine according to the state of the art, Fig. 2 in a perspective view the scroll machine according to the invention, Fig. 3 in a perspective view a bearing plate of the scroll machine, Fig. 4 a partial sectional view of the bearing shield, Fig. 5, Fig. 6 in view according to Fig. 4 two further designs of the bearing shield.

[0029] Corresponding parts are always provided with the same reference symbols in all figures.

[0030] Based on the Fig. 1, a conventional scroll machine is described below, used as a scroll compressor 1. The scroll compressor 1 is in Fig. 1 in a schematic partial sectional view. The scroll compressor 1 has a (compressor) housing 2, as well as a first, stationary scroll (referred to as "F-Scroll 4") arranged and rigidly fastened therein and a second, movable scroll (referred to as "O-Scroll 6") also arranged in the housing 2. The O-Scroll 6 is coupled eccentrically to a drive shaft 7 by means of a shaft journal 8, which in turn is coupled to the drive shaft 7 of an electric motor (drive) (not shown) by means of a joining pin 10. The eccentric shaft journal 8 is mounted in a rolling bearing 12 held in the O-Scroll 6. During (compressor) operation of the scroll compressor 1, the O-Scroll 6 is driven in an orbiting manner due to its eccentric coupling to the drive shaft 7.

[0031] The two scrolls 4 and 6 each have a helical or spiral-shaped spiral wall (scroll spiral) 14 (F-scroll 4) or 16 (O-scroll 6). In the present embodiment, these are designed according to an Archimedean spiral. The spiral walls 14 and 16 protrude from a respective base plate 18 (F-scroll 4) or 20 (O-scroll 6). The spiral wall 14 of the F-scroll 4 forms an associated spiral flight, into which the spiral wall 16 of the O-scroll 6 engages. Between the scrolls 4 and 6, i.e. between their spiral walls 14 and 16, respectively, and the base plates 18 and 20, delivery chambers, referred to here as compression chambers 22, are formed, the volume of which changes during operation of the scroll compressor 1, specifically, is reduced during compression operation.

[0032] During operation, a gas-oil mixture is increasingly compressed by the volume change of the compression chambers 22, whereby radial, azimuthal (tangential) and axial fluid forces act on the scrolls 4 and 6. In Fig. 1, the radial forces are shown as horizontal arrows and the axial forces as vertical arrows, with the azimuthal forces acting approximately perpendicular to the plane of the drawing. The individual forces in the compression chambers 22 result in a radial force FR and an axial force FA as well as a tangential force not shown in detail. During operation, these forces also generate (torque) moments, which act in particular on the movably mounted O-scroll 6. In particular, a torque is generated that tilts the movable scroll 6, causing an axial tilting or rolling movement of the movable scroll 6. This tilting is partially prevented by supporting the base plate 20 of the O-scroll 6 on the spiral wall 14 of the F-scroll 4. However, the tangential force leads to a self-rotation of the O-scroll 6, which must be prevented.

[0033] Based on the Fig. 2 to 6, exemplary embodiments of a scroll compressor 1 according to the invention are explained in more detail below.

[0034] Fig. Figure 2 shows the scroll compressor 1 designed according to the invention, which is installed as a refrigerant compressor - here for CO2 as the refrigerant - in a refrigerant circuit (not shown in detail) of an air conditioning system of a motor vehicle. The electromotive scroll compressor 1 has an electric (electromotive) drive module 26 (or: drive area) and a compressor module 28 (compressor area) coupled to the latter. The compressor module 28 is connected to the drive module 26 via a mechanical interface 30 formed between the drive module 26 and the compressor module 28. The mechanical interface 30 serves as an output-side ("A-side") bearing plate 32 and forms an intermediate wall (see also Fig. 1). The compressor module 28 is connected (joined, screwed) to the drive module 26 by means of flange connections 36 distributed around the circumference and extending in an axial direction A of the scroll compressor 1.

[0035] A housing section of the housing 2 assigned to the drive module 26 serves as a motor housing for accommodating an electric motor (not shown in detail). The housing 2 has a refrigerant inlet or refrigerant supply 44 for connection to the refrigerant circuit and a refrigerant outlet 46. The outlet 46 is formed on the bottom of the above-described (compressor) housing 4 of the compressor module 28. When connected, the inlet 44 forms the low-pressure or suction side (suction gas side) and the outlet 46 forms the high-pressure or pump side (pump side) of the scroll compressor 1.

[0036] Between the A-side bearing plate 32 and the O-scroll 6, in the intermediate wall formed by the bearing plate 32, there is a backpressure chamber 50 (see Fig. 1). During operation, the refrigerant is introduced into the housing 2 through the inlet 44. This drive-side area of ​​the housing 2 forms the suction or low-pressure side. Within the drive-side area of ​​the housing 2, the refrigerant mixes with the oil (usually oil mist) present in the refrigerant circuit, particularly in the drive area, and is sucked through an opening (or several openings) in the bearing plate 32 to the compressor module 28. The mixture of refrigerant and oil is compressed by the compressor module 28, with the oil serving to lubricate the two scrolls 4 and 6, thus reducing friction and consequently increasing efficiency. The oil also serves as a seal to prevent uncontrolled escape of the refrigerant located between the two scrolls 4 and 6.

[0037] The compressed mixture of refrigerant and oil is fed via a central outlet 52 in the base plate 18 of the fixed F-scroll 4 into a high-pressure chamber 54 (see Fig. 1) within the housing 2. An oil separator (cyclone separator, for example) is located in the high-pressure chamber 54. Within the oil separator, the mixture of refrigerant and oil is set into a rotating motion. Due to its higher density compared to the gaseous refrigerant, the oil is directed toward the walls of the oil separator and collected in a lower region of the oil separator, while the refrigerant is discharged upwardly or laterally through the outlet 46.

[0038] Carbon dioxide (CO2) as a refrigerant generally requires higher operating pressures than chemical refrigerants (e.g., R-134a). Therefore, in the present embodiment, the two scrolls 4 and 6 are made of cast iron or steel and not aluminum. Since, as described above, the O-scroll 6 is forced into its own rotation due to the drive and the acting gas forces, the scroll compressor 1 also has an anti-rotation mechanism, which in the present embodiment is designed as a pin-ring system. For this purpose, several pins are pressed into the bearing plate 32; these pins lie in circular pockets reinforced with rings in the base plate 20 of the O-scroll 6. The pins slide along the pocket walls during operation, thus preventing rotation of the O-scroll 6.Since a displacement of the pins relative to the pockets would lead to jamming, the bearing plate 32 should have the same value of a material-specific thermal expansion coefficient as the O-Scroll 6. A design of the bearing plate 32 made of aluminum is therefore unfavorable in this case, since aluminum and cast iron or steel display significantly different thermal expansion behavior.

[0039] For this reason, the bearing shield 32 is constructed in two parts according to the invention and has an outer part 60 made of aluminum. This allows the outer part 60 to be manufactured relatively easily and used as part of the housing 2. The bearing shield 32 has an inner part 62 as a second part (see Fig. 3). This is made of the same material as Scrolls 4 and 6, i.e. cast iron or steel, or of a material that is the same or sufficiently similar (e.g., not more than 3 × 10 -6 K -1different) thermal expansion coefficients. The inner part 62 carries the pins of the anti-rotation mechanism and has six holes 64 for this purpose.

[0040] The outer part 60 has an outer ring 66 and an inner ring 68 with a web 70 (see Fig. 4). The web 70 extends approximately parallel to the axial direction A and merges into a collar 72, which serves to hold the rolling bearing 12. The outer ring 66 and the inner ring 68 are manufactured in one piece and are connected by an intermediate piece, which passes through the channels 74 described above (see Fig. 4) is interrupted, connected to each other.

[0041] The inner part 62 is connected to the outer part 60 by pressing the outer part 60 into the inner part 62. Specifically, the web 70 has an annular contact or joining surface 76 that faces radially outward relative to the axial direction A. This means that its surface normal is radially aligned. The inner part 62 has a corresponding, annularly closed mating contact surface 78 that is formed on a radially inward-facing side surface of an annular groove 79 of the inner part 62. The dimensions of the joining surface 76 and the mating contact surface 78, specifically their diameter, are dimensioned such that an interference fit (press fit) is present in the intended operating state. At room temperature, however, a joining or contact force between the outer part 60 and the inner part 62 is so low that a comparatively simple assembly is possible (in particular without the need for heating or cooling of a joining partner).Because the outer part 60 is made of aluminum and thus has a higher coefficient of thermal expansion than the inner part 62 made of cast iron or steel, and because the outer part 60 rests radially outward against the inner part 62, the joining force between the outer part 60 and the inner part 62 increases with increasing temperature. Due to the joining force between the joining surface 76 and the mating contact surface 78, the inner part 62 is centered relative to the outer part 60. For tangential alignment, a positive connection in the tangential direction between the inner part 62 and the outer part 60 is used. For this purpose, flange lugs 80 projecting radially from the inner part 62 with bores introduced therein lie in corresponding pockets 82 which are formed in the outer part 60 and form a type of elongated hole. The pockets 82 therefore represent non-circular positioning recesses. During a start-up state, i.e.As long as a usual operating temperature value (usually between 90 and 110 degrees Celsius) has not yet been reached or even negative temperatures are present, the inner part 62 is held on the outer part 60 - in particular in addition to the aforementioned tangential form fit - by means of an axial preload of the two scrolls 4 and 6 relative to one another (in particular, among other things, due to the flange connection 36).

[0042] In Fig. Figure 5 shows a further embodiment. In this case, the inner part 62 has a relief groove 84 formed radially outside the mating contact surface 78. This serves to relieve stresses that are introduced into the inner part 62, particularly at elevated operating temperatures, due to the increasing joining force.

[0043] Another example is in Fig.6. Here, the web 68 has a rounded groove 86 at a base end of the joining surface 76, i.e., at the transition to the intermediate piece between the inner part 62 and the outer part 60. This enables a reduction of stress peaks in the aforementioned transition.

[0044] In addition, depending on the design for different operating conditions, the web 70 can also be designed with different thicknesses so that its rigidity can be adapted to the expected operating conditions (temperature values, pressure values ​​and the like, as well as in particular to the dimensions (diameter) of the bearing plate 32).

[0045] The subject matter of the invention is not limited to the exemplary embodiments described above. Rather, further embodiments of the invention can be derived by those skilled in the art from the above description. In particular, the individual features of the invention and their design variants described with reference to the various exemplary embodiments can also be combined with one another in other ways. List of reference symbols 1 scroll compressor 2 housings 4 F-Scroll 6 O-Scroll 7 Drive shaft 8 shaft journals 10 joining pin 12 rolling bearings 14 Spiral wall 16 Spiral wall 18 Base plate 20 base plate 22 Compressor chamber 26 Drive module 28 Compressor module 30 Interface 32 bearing plate 36 flange connection 44 Refrigerant inlet 46 Refrigerant outlet 50 backpressure chamber 52 Outlet 54 High pressure chamber 60 outdoor part 62 Inside 64 bore 66 Outer ring 68 inner ring 70 jetty 72 collars 74 channel 76 joining surface 78 Counter contact surface 80 flange bore 82 bag 84 relief groove 86 gutter A axial direction FR radial force FA axial force QUOTES CONTAINED IN THE DESCRIPTION

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

[0000] DE 10 2012 104 045 A1

[0003]

Claims

[1] Scroll machine (1) for carbon dioxide, comprising - a first scroll (4) with a first spiral wall (14) projecting in an axial direction (A), - a second scroll (6) with a second spiral wall (16) projecting in the axial direction (A), the second scroll (6) being made of steel or cast iron, - a drive, - a drive shaft (7) by means of which the drive and the second scroll (6) are coupled for power transmission, and - a bearing plate (32) which is connected between the drive and the second scroll (6) and which is formed in two parts from an outer part (60) and an inner part (62) which is bordered radially on the outside at least in regions by the outer part (60), wherein the outer part (60) carries a bearing (12) for the drive shaft (7), wherein the inner part (62) is coupled to the second scroll (6) via an anti-rotation mechanism, wherein the outer part (60) is pressed into the inner part (62) by a web (70), and wherein the outer part (60) is made from aluminum and the inner part (62) is made from a material with the same or at least a comparable thermal expansion coefficient as the steel or cast iron of the second scroll (6). [2] Scroll machine (1) according to claim 1, wherein a joining surface (76) of the web (70) is directed radially outwards to the inner part (62). [3] Scroll machine (1) according to claim 1 or 2, wherein the web is designed as an annular web (70) and engages in an annular groove (79) or bore of the inner part (62). [4] Scroll machine (1) according to one of claims 1 to 3, wherein the inner part (62) is aligned in the outer part (60) in the tangential direction by means of a form-fitting element, in particular a positioning recess (82). [5] Scroll machine (1) according to one of claims 1 to 4, wherein the inner part (62) has a relief groove (84) radially outside a counter contact surface (76) against which the web (70) of the outer part (60) is pressed in the assembled state. [6] Scroll machine (1) according to one of claims 1 to 5, wherein the outer part (60) has an outer ring (66) to which the web (70) is integrally connected, in particular by means of a connecting piece. [7] Scroll machine (1) according to claim 6, wherein a rounded groove (86) is formed on a foot region of a joining surface (76) of the web (70), [8] Scroll machine (1) according to claim 6 or 7, wherein the outer ring (66) forms an element of a housing (2) of the scroll machine (1), wherein the inner part (62) is shielded from environmental influences by the outer ring (66). [9] Scroll machine (1) according to one of claims 1 to 8, wherein a pressure between the web (70) of the outer part (60) and the inner part (62) is set such that in an unused state a low contact pressure value is present, in particular wherein in a heated operating state an increased contact pressure value is present.

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