Scroll machine

Abstract

The invention relates to a scroll machine. A scroll machine includes: a first scroll having a first spiral wall protruding in an axial direction; a second scroll member having a second spiral wall protruding in the axial direction; a driving device; a drive shaft, by means of which the drive device and the second scroll member are coupled in force transmission; and a bearing end cover which is connected between the driving device and the second scroll part and is composed of an outer part and an inner part which is surrounded by the outer part at least partially on the radial outer side, the outer part carries a bearing for the driving shaft, and the inner part is coupled with the second scroll part through an anti-rotation mechanism. The outer part is pressed into the inner part by means of a web. Further, the outer portion is made of aluminum and the inner portion is made of steel or cast iron.

Description

Technical Field

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

[0002] Motor vehicles are often equipped with air conditioning systems that use a system that forms a refrigerant circuit to condition the vehicle interior. Such systems typically have a circuit in which a refrigerant is conducted. The refrigerant, such as R-744 (carbon dioxide, CO2) or R-134a (1,1,1,2-tetrafluoroethane), is heated in an evaporator and compressed using a (refrigerant) compressor or extruder. The refrigerant then dissipates the absorbed heat via a heat exchanger before being redirected to the evaporator via a throttle element.

[0003] So-called scroll machines are commonly used as refrigerant compressors to compress the refrigerant. For example, DE 10 2012 104 045 A1 describes the structure and working method of such a scroll machine used as a compressor for refrigerants in motor vehicle air conditioning systems. The main components of such a scroll machine are two scroll parts ("scrolls") that can move relative to each other. In most cases, there is also oil in the form of droplets or as a mist in the system, which, after compression, is at least partially separated from the refrigerant (which is usually gaseous after compression). The refrigerant (possibly with residual oil) is then introduced into the air conditioning circuit, and the separated oil can usually be guided past the movable parts within the scroll machine to lubricate them. The scroll parts are generally implemented as a stationary, fixed scroll (fixed scroll, displacement scroll) and a movable, orbiting scroll (matching scroll, rotor scroll). The two scroll elements are essentially similar in design and each have a base plate (basic body, scroll disk) and a spiral (helical) wall (spiral wall, scroll wall) extending axially from the base plate. In the assembled state, the spiral walls of the two scroll elements are interlaced and nested, forming a plurality of transport chambers between the partially touching spiral walls.

[0004] To drive the movable scroll element, an electric motor is typically provided, the motor shaft of which (on the A side, ie the output side) is coupled to the movable scroll part in terms of drive technology by means of an eccentric journal (also called a “shaft pin”).

[0005] Here and hereinafter, an orbiting movement is understood to mean, in particular, an eccentric, circular movement path, in which the movable scroll element itself does not rotate about its own axis. The two scroll elements are arranged at the smallest possible axial distance from one another during operation, wherein, during each orbiting movement, essentially crescent-shaped (compression or transport) chambers are formed between the spiral walls. During the movement of the two scroll elements relative to one another (at least during the compression process), the volume of these chambers moves from the outside along the spiral walls in the direction of the central axis of the respective scroll element, gradually decreasing there (and thus compressing the medium guided therein).

[0006] Here, the orbital movement of the movable scroll is usually caused in particular by means of an anti-rotation mechanism, which prevents the scroll from rotating on its own. The anti-rotation mechanism is mostly connected between the movable scroll of the scroll machine and an element fixed in relative position. Usually, the anti-rotation mechanism is formed by a certain number of circular pocket-shaped openings ("rings") arranged on a circular trajectory in the movable scroll and associated bolts ("pins") arranged in the elements fixed in relative position. These bolts are embedded in the circular openings of the movable scroll and form so-called pin-ring contacts respectively. During (compression) operation, the bolts slide on the circular opening wall, thereby preventing self-rotation. In order to reduce friction and improve service life, a seat ring (sliding ring) is placed in the opening, for example. Based on this design, the anti-rotation mechanism is also called a "pin-ring system".

[0007] The motor shaft is usually supported by means of a bearing in an end shield (also called a “center plate”). The pin of the anti-rotation lock is usually fixed in the end shield (especially in a non-positive manner).

[0008] Compared to chemical refrigerants such as R-134a, carbon dioxide as a refrigerant requires a higher pressure, so using aluminum as the material for the scroll element generally does not achieve a sufficiently high strength. A related problem is the coupling components, which are preferably made of aluminum and therefore generally have a different thermal expansion behavior. Summary of the Invention

[0009] The object of the present invention is to provide 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 listed in the dependent claims and the following description.

[0011] The scroll machine according to the present invention is designed and configured for use with carbon dioxide as a refrigerant. Preferably, the scroll machine is designed and configured for use in a compressor for this refrigerant in a vehicle air conditioning system. To this end, the scroll machine comprises a first scroll member and a second scroll member, the first scroll member having a first spiral wall protruding in the axial direction, and the second scroll member having a second spiral wall protruding in the axial direction. At least the second scroll member is made of steel or cast iron. In particular, the two spiral walls interlock, thereby forming a compression chamber or a transport chamber between the points at which the spiral walls touch each other. The scroll machine also comprises a drive device and a drive shaft, by means of which the drive device and the second scroll member are coupled in terms of power transmission technology. The scroll machine also comprises a bearing end cap, which is connected between the drive device and the second scroll member and is composed of two parts, consisting of an outer part and an inner part that is at least partially radially surrounded on the outside by the outer part. The outer part supports the bearing for the drive shaft. The inner part is coupled to the second scroll member via an anti-rotation mechanism. The outer part is pressed into the inner part by a tab (part of the outer part in particular). In addition, the outer part is made of aluminum, while the inner part is made of a material having the same or at least similar thermal expansion coefficient as the steel or cast iron of the second scroll.

[0012] According to a preferred embodiment, the first scroll also consists of steel or cast iron, preferably the same steel or cast iron as the second scroll. An embodiment in which at least the second scroll, preferably both scrolls, are made of steel or cast iron allows for greater strength than scrolls typically made of aluminum and is therefore advantageous for higher pressures when CO2 is used as the refrigerant (in particular compared to chemical refrigerants).

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

[0014] The invention has the advantage that the outer part of the end cap can achieve weight advantages due to the material and simple machinability, while the inner part has a thermal expansion behavior similar to that of the second scroll element, preferably both scroll elements. This prevents jamming or blocking between the second scroll element and the end cap during continuous operation, in particular at the elevated temperatures that often occur during continuous operation.

[0015] Here and hereinafter, a “similar coefficient of thermal expansion” is understood to mean in particular a coefficient of thermal expansion which lies at most + / - 4 × 10 -6 K -1 , preferably up to + / - 3 × 10 -6 K -1 , preferably at most + / - 2 × 10 -6 K -1or smaller.

[0016] For example, the coefficient of thermal expansion of cast iron of one or more scroll members may be approximately 10.5 × 10 -6 K -1 (+ / -2 ×10 -6 K -1 For example, the value of the steel of one or more scroll members is approximately 11×10 -6 K -1 to 16 × 10 -6 K -1 within the range between.

[0017] As steel, structural steel, low alloy steel, high alloy steel, stainless steel (eg chrome steel), high-grade steel etc. can be used optionally. The thermal expansion coefficient of the steel used is preferably significantly smaller (ie at least 6×10 -6 K -1 ).

[0018] According to a preferred embodiment, the joining surface of the web (preferably each joining surface if there are multiple such joining surfaces) points radially outward relative to the inner part. Here and hereinafter, a joining surface is understood to be, in particular, a surface via which the joining force is transmitted between the components to be joined. Consequently, the contact force acts radially inward from the inner part onto the outer part, at least onto the web of the outer part. This clamps the outer part against the inner part in a clamp-like manner. This is advantageous because the outer part expands more than the inner part due to its greater coefficient of thermal expansion, and thus the clamping force continues to increase with increasing operating temperature values. For carbon dioxide as a refrigerant, the local operating temperature values in the area of the bearing end cap, in particular in the back pressure chamber formed in the bearing end cap, are mostly between 90 and 110 degrees Celsius.

[0019] Preferably, in this case in particular, the pressing force (preferably a press fit or interference fit) between the tabs of the outer part and the inner part is adjusted so that in the unused state (i.e., at room temperature or at least at temperatures reduced compared to typical operating temperatures), low pressing force values (also referred to as "joining force values") are present. In particular, in the intended operating state, and therefore at high temperatures, increased pressing force values are present. This in turn has the advantage of simplifying the installation of the end cap, since, at typical assembly temperatures, only relatively low assembly forces need to be applied, or at least no expenditure, such as heating of the mating parts, is required.

[0020] According to a particularly advantageous embodiment, the tab is designed as an annular tab, i.e., in particular as an annular, preferably circular, and preferably also closed tab. Furthermore, the annular tab engages in an annular groove or bore in the inner part. The annular tab can thereby achieve, in a particularly simple manner, centering of the inner part relative to the outer part.

[0021] To align the inner part tangentially with respect to the outer part, a form-fitting mechanism is preferably used. In particular, the outer part has a (preferably non-circular or asymmetrical) locking recess (e.g., an elongated hole or the like) as a form-fitting element, into which a corresponding (form-fitting) element of the inner part is inserted. Conventional locating bolts are disadvantageous in the present case because, due to the different material combinations of the two end shield parts, the locating bolts become relatively tightly clamped during gradual heating, which can in turn lead to damage.

[0022] Alternatively, the annular web can also be non-circular, for example polygonal (preferably with rounded corners) or elliptical, so that the annular web can not only be centered but also oriented in the tangential direction. In this case, the annular groove is correspondingly configured.

[0023] According to a preferred embodiment, the inner part has a mating contact surface against which the tabs of the outer part (particularly with their contact surfaces) are pressed in the assembled state. The inner part advantageously has a load-reducing groove radially outside of this mating contact surface. This allows for the reduction of stresses caused by, preferably in the intended operating state, and therefore in particular by increased joining or pressing forces compared to room temperature. For example, the load-reducing groove can be introduced into the inner part approximately parallel to the mating contact surface.

[0024] According to another advantageous embodiment, the outer part comprises an outer ring, to which webs are integrally connected (in particular by means of connecting pieces, also referred to as bridges). In particular, recesses or channels are introduced between the webs and the outer ring (i.e., in particular in the bridges), through which coolant can flow from the drive region into the delivery region or compression region of the scroll machine during proper operation.

[0025] Expediently, a rounded groove is formed in the heel area of the connecting surface of the web, i.e., in particular in the connecting surface of the web and in the area where the web itself is connected to the outer ring, i.e., in particular at the transition to the bridge. Such a groove, or also rounding, supports the reduction of stress peaks at the transition.

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

[0027] A "positive fit" or a "positive connection" between at least two parts connected to one another is understood here and hereinafter to mean that the connected parts are held together at least in one direction by direct interlocking engagement of the contours of the parts themselves or by indirect interlocking engagement via additional connecting elements. The "prevention" of mutual movement in this direction is therefore due to the shape. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] An embodiment of the present invention is described in detail below with reference to the accompanying drawings, in which:

[0029] Figure 1 A scroll machine according to the prior art is shown in partial cross-section,

[0030] Figure 2 A scroll machine according to the invention is shown in a perspective view,

[0031] Figure 3 The bearing cover of a scroll machine is shown in perspective.

[0032] Figure 4 shows a partial cross-sectional view of the bearing end cover,

[0033] Figure 5 、 Figure 6 Based on Figure 4 The figures show two further embodiments of the end caps.

[0034] In all the figures, parts that correspond to one another are always provided with the same reference numerals. DETAILED DESCRIPTION

[0035] With the help of Figure 1 , a conventional scroll machine used as a scroll compressor 1 is described below. The scroll compressor 1 is Figure 1The scroll compressor 1 is shown in a schematic partial cross-section. The scroll compressor 1 has a (compressor) housing 2 and a first, stationary scroll member (referred to as "F scroll member 4") arranged in the housing and rigidly fastened, and a second, movable scroll member (referred to as "O scroll member 6") also arranged in the housing 2. The O scroll member 6 is eccentrically coupled to the drive shaft 7 by means of a journal 8 (which in turn is coupled to the drive shaft 7 of an electric motor (drive device) not shown) by means of a coupling bolt 10. The eccentric journal 8 is supported in a rolling bearing 12 retained in the O scroll member 6. During the (compression) operation of the scroll compressor 1, the O scroll member 6 is driven in an orbital manner due to its eccentric coupling to the drive shaft 7.

[0036] The two scroll members 4 and 6 each have a spiral or helical spiral wall (scroll spiral portion) 14 (F scroll member 4) or 16 (O scroll member 6). In the present embodiment, these scroll members are constructed according to Archimedean spirals. The spiral walls 14 and 16 extend vertically from their respective base plates 18 (F scroll member 4) or 20 (O scroll member 6). The spiral wall 14 of the F scroll member 4 forms the associated spiral path, in which the spiral wall 16 of the O scroll member 6 is embedded. Between the scroll members 4 and 6, this means that a transport chamber (here referred to as a compression chamber 22) is formed between their spiral walls 14 or 16 and the base plates 18 and 20, the volume of which changes during the operation of the scroll compressor 1, specifically shrinks during compression operation.

[0037] During operation, the oil-air mixture is squeezed incrementally by the volume change of the compression chamber 22, whereby radial, azimuthal (tangential) and axial fluid forces act on the scroll members 4 and 6. Figure 1 In the figure, radial forces are shown as horizontal arrows and axial forces as vertical arrows, wherein the azimuthal forces act approximately perpendicularly to the plane of the drawing. The various forces in the compression chamber 22 generate radial forces FR and axial forces FA as well as tangential forces that are not shown in detail. Through these forces, (rotational) moments are also generated during operation, which act in particular on the movably supported O scroll 6. Here, in particular, a rotational moment is generated that causes the movable scroll 6 to flip, thereby causing the movable scroll 6 to flip axially or roll. This flipping is partially prevented by the support of the base plate 20 of the O scroll 6 on the spiral wall 14 of the F scroll 4. However, the tangential force causes the self-rotation of the O scroll 6, which should be prohibited.

[0038] The following text uses Figures 2 to 6 An embodiment of the scroll compressor 1 according to the present invention will be explained in detail.

[0039] Here, Figure 2The scroll compressor 1 designed according to the invention is shown and is installed as a refrigerant compressor (here for CO2 as refrigerant) in a refrigerant circuit (not shown in detail) of an air conditioning system of a motor vehicle. The electric motor-type scroll compressor 1 has an electric (electric motor-type) drive module 26 (or: drive area) and a compression module 28 (compression area) coupled to the drive module. The compression module 28 is connected to the drive module 26 for drive technology via a mechanical interface 30 formed between the drive module 26 and the compression module 28. The mechanical interface 30 serves as a bearing shield 32 on the output side ("A side") and forms an intermediate wall (see also Figure 1 The compression module 28 is connected (joined, screwed) to the drive module 26 by means of flange connections 36 distributed on the circumference and extending in the axial direction A of the scroll compressor 1 .

[0040] The housing portion of housing 2 associated with drive module 26 serves as a motor housing for accommodating an electric motor (not shown in detail). Housing 2 has a refrigerant inlet or refrigerant input 44 for connection to the refrigerant circuit and a refrigerant outlet 46. Outlet 46 is formed at the bottom of the aforementioned (compressor) housing 4 of compression module 28. In the connected state, inlet 44 forms the low-pressure side or suction side (intake side) of scroll compressor 1, while outlet 46 forms the high-pressure side or pump side (discharge side).

[0041] Between the A-side bearing cover 32 and the O scroll 6, there is a counter-pressure chamber (back pressure chamber) 50 (see Figure 1 During operation, refrigerant is introduced into the housing 2 via the inlet 44. This drive-side region of the housing 2 forms the suction side, or low-pressure side. Within the drive-side region of the housing 2, the refrigerant mixes with the oil (mostly oil mist) present in the refrigerant circuit, particularly in the region of the drive, and is drawn through an opening (or openings) in the bearing end cap 32 to the compression module 28. The refrigerant and oil mixture is compressed by means of the compression module 28, with the oil being used to lubricate the two scrolls 4 and 6, thereby reducing friction and thus increasing efficiency. The oil also serves as a seal to prevent uncontrolled escape of the refrigerant between the two scrolls 4 and 6.

[0042] The compressed mixture of refrigerant and oil is directed via a central outlet 52 in the base plate 18 of the stationary F scroll 4 to a high-pressure chamber 54 inside the housing 2 (see FIG. Figure 1). An oil separator (cyclone separator), for example, is located in the high-pressure chamber 54. Inside the oil separator, a mixture of refrigerant and oil undergoes a swirling motion, wherein the oil, due to its higher density compared to the gaseous refrigerant, is directed to the walls of the oil separator and accumulates in the lower region of the oil separator, while the refrigerant is directed upward or laterally through the outlet 46.

[0043] Compared to chemical refrigerants such as R-134a, carbon dioxide (CO2) as a refrigerant generally requires higher operating pressures. Therefore, in this embodiment, both scrolls 4 and 6 are constructed from cast iron or steel rather than aluminum. Because, as described above, self-rotation occurs due to the drive and gas forces acting on scroll O 6, scroll compressor 1 also includes an anti-rotation mechanism, which in this embodiment is constructed as a pin-and-ring system. To this end, multiple pins are pressed into bearing cap 32 and inserted into circular pockets reinforced with rings in base plate 20 of scroll O 6. During operation, the pins slide on the pocket walls, preventing scroll O 6 from rotating. Because movement of the pins relative to the pocket could lead to seizure, bearing cap 32 should have the same material-specific coefficient of thermal expansion as scroll O 6. Therefore, in the present case, an embodiment in which bearing cap 32 is constructed from aluminum is unfavorable because aluminum and cast iron or steel exhibit significantly different thermal expansion behaviors.

[0044] For this reason, according to the invention, the end shield 32 is constructed in two parts and has an outer part 60 made of aluminum. As a result, the outer part 60 can be produced relatively simply and used as part of the housing 2. The end shield 32 has an inner part 62 as a second part (see Figure 3 The inner portion is made of the same material as the scroll members 4 and 6, i.e. cast iron or steel, or of a material having the same or sufficiently similar properties (e.g. with a difference of not more than 3 × 10 -6 K -1 The inner part 62 carries the pins of the anti-rotation mechanism and has six boreholes 64 for this purpose.

[0045] The outer portion 60 has an outer ring 66 and an inner ring 68 as well as a web 70 (see Figure 4 ). The web 70 extends approximately parallel to the axial direction A and transitions into a ring 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 to each other via an intermediate piece, which is connected via the above-mentioned channel 74 (see Figure 4 ) interrupt.

[0046] The inner part 62 is connected to the outer part 60 by being pressed into the inner part 62. Specifically, the tab 70 has a circular contact or engagement surface 76 that points radially outward relative to the axial direction A. In other words, the surface normal of the engagement surface is oriented radially. The inner part 62 has a corresponding, closed, annular mating contact surface 78, which is formed on the radially inward-facing side of the annular groove 79 of the inner part 62. The dimensions of the engagement surface 76 and the mating contact surface 78 (specifically, their diameters) are dimensioned so that an interference fit (press fit) exists under the specified operating conditions. In contrast, at room temperature, the engagement or contact forces between the outer part 60 and the inner part 62 are very low, enabling relatively simple assembly (particularly when heating or cooling the mating parts is not required). Because outer part 60 is made of aluminum and therefore has a higher coefficient of thermal expansion than inner part 62, which is made of cast iron or steel, and because outer part 60 rests radially outward against inner part 62, the joining force between outer part 60 and inner part 62 increases as temperature rises. The joining force between joining surface 76 and mating contact surface 78 centers inner part 62 relative to outer part 60. For tangential alignment, a positive fit is used between inner part 62 and outer part 60 in the tangential direction. To this end, a flange lug 80, which projects radially from inner part 62 and has a borehole formed therein, is inserted into a corresponding recess 82 formed in outer part 60 and forming a kind of elongated hole. Recess 82 is therefore a non-circular positioning recess. During the startup state, i.e. as long as the usual operating temperature values (which are mostly between 90 and 110 degrees Celsius) have not yet been reached or even negative temperatures are present, the inner part 62 is retained on the outer part 60 (in particular in addition to the prestressed tangential form lock) also via the axial prestressing of the two scroll elements 4 and 6 with respect to each other (in particular mainly due to the flange connection 36).

[0047] Figure 5 . In this case, the inner part 62 has a load-reducing groove 84, which is formed radially outside the mating contact surface 78. The load-reducing groove serves to relieve stresses introduced into the inner part 62 due to increased joining forces, particularly at elevated operating temperatures.

[0048] Figure 6 A further embodiment is shown in . Here, the tab 68 has a rounded groove 86 at the heel end of the joint surface 76, ie at the transition to the middle block between the inner part 62 and the outer part 60. This groove makes it possible to reduce stress peaks in the aforementioned transition.

[0049] Furthermore, depending on the design for different operating states, webs 70 can also be designed with different thicknesses so that their stiffness can be adapted to the expected operating conditions (temperature values, pressure values, etc., and in particular the size (diameter) of end shield 32 ).

[0050] The subject matter of the present invention is not limited to the above-described embodiments. On the contrary, those skilled in the art can deduce other embodiments of the present invention from the above description. In particular, the individual features of the present invention described with reference to the different embodiments and their design variations can also be combined with each other in other ways.

[0051] Reference Signs List

[0052] 1 scroll compressor

[0053] 2 shell

[0054] 4F scroll parts

[0055] 6O scroll parts

[0056] 7 drive shaft

[0057] 8 journals

[0058] 10 joint bolts

[0059] 12 rolling bearings

[0060] 14 Spiral Wall

[0061] 16 spiral wall

[0062] 18 substrates

[0063] 20 substrates

[0064] 22 compression chamber

[0065] 26 driver modules

[0066] 28 compression modules

[0067] 30 interfaces

[0068] 32 bearing end cover

[0069] 36 flange connection

[0070] 44 Refrigerant input part

[0071] 46 Refrigerant outlet

[0072] 50 back pressure chamber

[0073] Exit 52

[0074] 54 High-pressure chamber

[0075] 60 external part

[0076] 62 internal division

[0077] 64 drilling

[0078] 66 outer ring

[0079] 68 inner circle

[0080] 70 splices

[0081] 72 rings

[0082] 74 channels

[0083] 76 joint surface

[0084] 78 mating contact surface

[0085] 80 flange lugs

[0086] 82 recess

[0087] 84 load reduction tank

[0088] 86 groove

[0089] A axial direction

[0090] FR radial force

[0091] FA axial force

Claims

1. A scroll machine (1) for carbon dioxide, comprising: - a first scroll member (4) having a first spiral wall (14) protruding in the axial direction (A), - a second scroll member (6) having a second spiral wall (16) protruding in the axial direction (A), wherein The second scroll member (6) is made of steel or cast iron, - drive unit, - a drive shaft (7), by means of which the drive device and the second scroll element (6) are coupled in terms of force transmission, and - a bearing end cap (32) which is connected between the drive device and the second scroll element (6) and is composed of two parts, consisting of an outer part (60) and an inner part (62) which is at least partially surrounded radially on the outside by the outer part (60), wherein the outer part (60) carries a bearing (12) for the drive shaft (7), and wherein the inner part (62) is coupled to the second scroll element (6) via an anti-rotation mechanism, The outer part (60) is pressed into the inner part (62) by means of webs (70), and the outer part (60) is made of aluminum, while the inner part (62) is made of a material having the same or at least similar coefficient of thermal expansion as the steel or cast iron of the second scroll element (6).

2. The scroll machine (1) according to claim 1, in, The contact surface (76) of the web (70) points radially outward relative to the inner part (62).

3. The scroll machine (1) according to claim 1 or 2, in, The web is designed as an annular web (70) and engages in an annular groove (79) or a bore in the inner part (62).

4. A scroll machine (1) according to any one of claims 1 to 3, in, The inner part (62) is oriented in the outer part (60) in a tangential direction by means of form-fitting elements, in particular locking recesses (82).

5. A scroll machine (1) according to any one of claims 1 to 4, in, The inner part (62) has a load-reducing groove (84) radially outside of a mating contact surface (76) against which the web (70) of the outer part (60) is pressed in the assembled state.

6. A scroll machine (1) according to any one of claims 1 to 5, in, The outer part (60) has an outer ring (66) which is connected to the web (70) in one piece, in particular by means of a connecting block.

7. The scroll machine (1) according to claim 6, in, A rounded groove (86) is formed in the heel region of the joining surface (76) of the web (70).

8. A scroll machine (1) according to claim 6 or 7, in, The outer ring (66) forms an element of the housing (2) of the scroll machine (1), wherein the inner part (62) is shielded from environmental influences by the outer ring (66).

9. A scroll machine (1) according to any one of claims 1 to 8, in, The pressing force between the webs (70) of the outer part (60) and the inner part (62) is adjusted such that in the unused state lower pressing force values are present, wherein in particular increased pressing force values are present in the heated operating state.

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