CN112867883A

CN112867883A - Slip ring seal

Info

Publication number: CN112867883A
Application number: CN201980069111.9A
Authority: CN
Inventors: M·舍贝施; P·范多布策温斯基; W·文德尔
Original assignee: Kako Co ltd
Current assignee: Kako Co ltd; Kaco GmbH and Co KG
Priority date: 2018-12-20
Filing date: 2019-12-19
Publication date: 2021-05-28
Also published as: DE102018010082A1; WO2020126071A1

Abstract

The invention relates to a sliding ring seal comprising a mating ring (6) and a sliding ring (17) which, under the force of a bellows structure (27), rests with a sealing surface (23) against a mating sealing surface (16) of the mating ring (6). The slip ring (17) and the mating ring (6) are enclosed by a housing (1) which at least together with the slip ring (17) defines an annular space (31) and which is connected to the slip ring (17) via a bellows structure (27). The leather chamber structure (27) is provided with a leather chamber area (33), the leather chamber area is connected to the connecting area (32), and the leather chamber structure (27) is fixed on the shell (1) through the connecting area. The annular space (31) between the housing (1) and the slip ring (17) is radially inwardly delimited by the bellows structure (27). The skin cavity region (33) is located at least substantially outside the annular region (31).

Description

Slip ring seal

Technical Field

The present invention relates to a slide ring seal according to the preamble of claim 1.

Background

Such a slip ring seal is known, for example, from EP 2607757B 1. The slip ring generates an axial force by using the compression spring under the action of the force of the compression spring, and the slip ring and the matching ring are attached to each other by using the axial force. The elastomer element, which is a bellows structure, assumes a secondary sealing function. Since two separate components are provided for the spring and sealing functions, the manufacturing costs are correspondingly increased.

For this reason, sliding ring seals are also known (DE 102004035658 a1), in which the spring elements simultaneously fulfill a secondary sealing function.

In the use of a sliding ring seal, axial movements are usually produced which must be absorbed by the sliding ring seal without affecting the sealing function. The shaft to be sealed moves axially during operation. Furthermore, axial movement of the shaft can cause wear of components or, for example, thermal expansion of the shaft. The slip ring seal performs this movement with the shaft.

This can lead to a change in the contact pressure between the slip ring and the counter ring in such an axial movement, in particular when the axial movement is large. The spring force acting on the mating ring varies relatively strongly over the axial movement path.

Disclosure of Invention

The object of the invention is to configure a sliding ring seal of the type mentioned in such a way that it can follow large axial movements without affecting its sealing capacity.

This object is achieved according to the invention by the features of the generic type with the characterizing portion of claim 1.

In the sliding ring seal according to the invention, the bellows region is located at least substantially outside an annular space which is arranged between the housing and the sliding ring and which is defined radially inwards by the bellows structure. Therefore, under the condition of the same installation state, the movement range of the leather cavity structure is enlarged. This is achieved in particular by the position of the bellows region, so that the bellows structure can have a comparatively flat force-displacement curve, as a result of which an axial displacement of movement can be achieved with only a small change in the spring force. Thus, even when the axial movement displacement is large, the pressing force between the slip ring and the mating ring does not change greatly.

An advantageous development is achieved if, viewed in an axial section, the central axis of the bellows region forms an angle of 0 ° to 90 ° with the central axis of the housing part to which the bellows structure is connected via the connection region. If the angle is, for example, 0 deg., the bellows region is located directly adjacent to the annular space. If the angle between the two central axes is large, the bellows region extends somewhat largely outwards, so that the range of motion of the bellows structure becomes correspondingly larger.

In a preferred embodiment, the skin space region extends from the connection region to the outside from the housing. The connecting section for connecting the bellows region to the slip ring has a correspondingly large length, which advantageously contributes to a flat force-displacement curve of the bellows structure.

The housing part to which the bellows region is connected is advantageously an annular flange which is arranged at an axial end of the housing and extends radially inward. This radial flange defines a through hole for the machine part to be sealed. A connection portion of the bellows structure also extends through the through hole, the connection portion connecting the bellows region with the slip ring.

The force-displacement curve of the bellows structure can be influenced in an advantageous manner if the cross-sectional thickness of the bellows region increases in the direction of the connecting region.

In a particularly advantageous embodiment, the outer contour and the inner contour of the thickened part of the skin space are each described by a closed curve, as seen in an axial sectional view. Here the two curves have different midpoints. It can be determined for the two closed curves and their positions relative to each other how the thickened part of the cavity area can be designed in order to obtain an optimally flat force-displacement curve.

It is also conceivable to use any other suitable contour with which the inner contour and the outer contour of the thickened portion can be approximately described in the tangential direction. Examples of such further profiles may be elliptical, involute, spiral, rectangular and similar profiles. These further profiles have a midpoint or center of gravity, respectively.

The closed curves are advantageously circular, the positions of which relative to each other can be described in a simple manner.

The offset of the midpoint of the two curves may be set in the x-direction and/or the y-direction. The x-y coordinate system relates to an axial cross-sectional view of the slip ring seal. Depending on the inner and outer contours of the thickened region, the approximate curve may have a corresponding deviation in the x and/or y direction.

The offset coefficient of the two curves in the x direction is advantageously 0.1. ltoreq. x2/x 1. ltoreq.10, preferably 0.3. ltoreq. x2/x 1. ltoreq.1, where x1, x2 are the spacings between the curves in the x direction.

The shift coefficient of the middle point of the two curves along the y direction is 0.1 ≦ y2/y1 ≦ 10, preferably 0.3 ≦ y2/y1 ≦ 1, wherein y1 and y2 are the spacing between the curves along the y direction.

In an advantageous embodiment, the slide ring of the slide ring seal is connected to the rotating machine part by at least one elastic retaining element. The elastic holder makes it possible for the mating ring to also perform an axial movement relative to the machine part. The elastic holder ensures that the slide ring and the counter ring are always securely pressed against one another.

A simple design is obtained if the elastic holder is fastened to a holder that is fixed to the rotating machine part. The elastic holder can be very easily fixed to this machine part-side holder.

The slide ring seal is advantageously a gas-lubricated slide ring seal.

The subject matter of the invention is not only derived from the subject matter of the individual claims, but also from all the information and features disclosed in the figures and the description. As long as these information and features are new with respect to the prior art, alone or in combination with one another, even if these information and features are not the subject of the claims, they are claimed as important matters of the present invention.

Further features of the invention emerge from the further claims, the description and the drawings.

Drawings

The invention will be described in detail hereinafter with reference to a few embodiments shown in the drawings. Wherein:

fig. 1 shows half of a slide ring seal according to the invention in an axial sectional view;

fig. 2 to 6 each show an embodiment of the slide ring seal according to the invention in the representation according to fig. 1.

Detailed Description

The sliding ring seal according to fig. 1 has a housing 1 with which the sliding ring seal is fixed in an installation space of an installation (not shown). The housing 1 is made of a correspondingly hard material, such as metal or hard plastic. The shape of the housing 1 is designed according to the shape of the installation space. In the exemplary embodiment shown, the housing 1 has a cylindrical housing part 2 and a cylindrical housing part 3. The housing part 2 has a larger inner and outer diameter than the housing part 3. The housing part 3 has a radially inwardly directed flange 4 at the free end. The housing part 2 has a bevel 5 at the free end, which is oriented obliquely radially inward and has a smaller wall thickness than the housing part 2.

The

housing parts

2, 3, the flange 4 and the bevel 5 are advantageously designed in one piece.

The housing 1 encloses, at a radial distance, a mating ring 6, which is connected in a rotationally fixed manner to a machine part 7 to be sealed, preferably a shaft. A cylindrical fastening section 8 of a holder 9 is mounted in a rotationally fixed manner on the machine part 7. The fastening section merges into a radially outwardly extending annular collar 10, the outer edge 11 of which is surrounded by a retaining sealing ring 12. The retaining sealing ring has a substantially U-shaped cross section and surrounds the annular flange 10 on both sides and on its end side over a part of its radial width. The retaining sealing ring 12 is made of an elastomer material and serves as a static sealing element.

The mating ring 6 is fixed, for example glued, in a suitable manner to said retaining seal ring 12 in the region of its radially outer edge. The connection between the retaining sealing ring 12 and the mating ring 6 is media-tight, so that the medium to be sealed on the medium side 13 cannot enter radially inward between the retaining sealing ring 12 and the mating ring 6.

In order to securely connect the mating ring 6 to the retaining ring 12, the radial section 14 of the retaining ring 12, which bears against the side of the annular flange 10 facing the mating ring 6, is wider than the opposite section 15 of the retaining ring 12.

The mating ring 6 has a rectangular cross section and encloses a cylindrical fixing section 8 of a holder 9. The counter ring 6 is connected in a rotationally fixed manner to the machine part 7 via a holder 9.

The mating ring 6 is in surface contact with the sliding ring 17 at the end side 16 facing away from the retaining ring 12. As with the mating ring 6, the slide ring also has a rectangular cross section and surrounds the fastening section 8 of the holder 9 at a radial distance.

The mating ring 6 and the slip ring 17 advantageously have the same radial width, so that the outer and inner

circumferential surfaces

18, 19; 20. 21 are respectively located on the same cylindrical surface. The mating ring 6 and the slip ring 17 may be made of any suitable material.

The mating ring 6 is provided with an annular recess 33 along its end face 16 in the radially inner region, said recess opening out to the radially inner circumferential surface 19 of the mating ring 6. The mating ring 6 therefore rests on the respective radial end face 23 of the slide ring 17 only on a part of its end face 16. The radial width of the recess 22 is determined according to the application of the slide ring seal. In the embodiment shown, the radial width of the recess 22 is for example less than half the radial width of the mating ring 6. The slide ring seal can also be designed without the recess 22.

The outer circumferential surface 24 of the retaining sealing ring 12 is also advantageously located on the same cylindrical surface as the outer

circumferential surfaces

18, 20 of the mating ring 6 and the sliding ring 27.

The outer diameters of the retaining sealing ring 12, the mating ring 6 and the sliding ring 17 are smaller than the inner diameter of the housing part 3.

The slip ring 17 is substantially radially enclosed by the housing part 3. The radial sealing gap formed by the end faces 16, 23 of the mating ring 6 and the slide ring 17 is located, for example, approximately at the level of the transition 25 between the two

housing parts

2 and 3. The mating ring 6 is substantially enclosed by the housing part 2. The retaining ring 12 is also surrounded by the housing part 2 and is spaced apart from the end face 26 of the bevel 5. The retaining sealing ring 12, the mating ring 6 and the slip ring 17 are thereby arranged in a protected manner inside the housing 1.

The slide ring 17 is held by a bellows structure 27, which is advantageously formed in one piece and is fastened to the annular flange 4 of the housing 1. The bellows structure 27 is made of an elastomer material and serves both as a sealing element and as a spring element with which the slide ring 17 is pressed axially against the mating ring 6. The bellows structure 17 may also be made of a polymer material.

The bellows structure 27 surrounds the free edge of the annular flange 4 of the housing 1 and is fixedly connected to the annular flange in a suitable manner, for example by gluing or vulcanization.

The bellows structure 27 has an annular fastening portion 28, the end face 29 of which is fastened with a surface-to-surface fit to the radial end face 30 of the slip ring 17 facing away from the mating ring 6 and is connected to the bellows region 33 by a connecting section 46. The skin cavity region is curved in an axial sectional view. The connecting portion 46 is of substantially cylindrical design and surrounds the machine part 7 at a distance. Proceeding from the fastening portion 28, the connecting section 46 extends approximately to the height of the flange 4 and then merges into the leather chamber region 33. The bellows region is thus located in an area outside the annular space 31 in the housing 1 and also outside the housing 1. As shown in fig. 1, the bellows region 33 is located on the side of the annular flange 4 facing away from the slide ring 17, as viewed in an axial sectional view.

The fastening part 28 is fastened in the region of the end side 30 of the slip ring 17 in the radially inner direction. Furthermore, the mating ring 6 is connected to the retaining ring 12 or to the section 14 thereof in a region radially outside the mating ring 6.

An annular space 31 is formed between the slip ring 17 and the housing 1 or the housing part 3 thereof and is closed radially inwards by the bellows structure 27. The stationary part 28 of the bellows structure 27 is connected to the slide ring 17 in such a way that the medium from the annular space 31 cannot pass radially inwards through the region between the stationary part 28 and the slide ring 17.

The mechanical component 7, preferably a shaft, is moved in the axial direction during operation or as a result of wear of components or also as a result of thermal expansion of the machine components. The mating ring 6 and the slip ring 17 perform said movement together with the machine part 7. This entails that the end side 23 of the slip ring 17 has to follow this movement. The bellows structure 27 allows the movement to be achieved. Here, however, the bellows structure can also be designed such that the contact pressure between the mating ring 6 and the slide ring 17 does not vary greatly. In other words, the spring force of the bellows structure 27 changes only slightly. Even when the axial movement is of a large extent, the pressing force with which the slide ring 17 bears against the counter ring 6 therefore fluctuates only slightly.

The connection region 32 of the bellows structure 27 on the annular flange 4 of the housing 1 is located partly in a region outside the annular space 31. The bellows region 33 adjoining the connecting region 32 extends obliquely outward from the connecting region 32, so that the bellows region 33 is located outside the housing 1. In this way, the range of motion of the bellows structure 27 can be increased in the same installation situation. Viewed in an axial section according to fig. 1, the portion of the bellows region 33 adjoining the connection region 32 is at an angle α to a radial plane 34 of the annular flange 4 of the housing 1. The axial section shown by reference in fig. 1 shows the longitudinal axis 35 of the skin space 33, which is at the angle α to the radial plane 34.

The angle α is in the range of 0 ° to 90 °. If the angle α is 0 °, the bellows region 33 extends radially inward from the connecting region 32. If the angle alpha has a value greater than 0 deg., the bellows region 33 extends outwardly as shown in fig. 1, whereby this region is not located within the housing 1 or the annular space 31.

The cross-sectional thickness of the skin space region 33 is advantageously reduced from the connecting region 32.

In a particularly advantageous embodiment of the bellows structure 27, the cross-sectional thickenings of the bellows region 33 in the direction of the connecting region 32 are defined in the form of two circular contours and their position relative to one another, to which reference is made in each case to the axial sectional view shown in fig. 1.

Circle a tangentially approximates the inner contour of the leather chamber region 33, while circle B tangentially approximates the outer contour of the leather chamber region 33. The two circles A, B are not concentric with each other, since the cortical space 33 gradually thickens in a direction towards the connecting region 32. This concentricity condition occurs only when the cross-sectional thickness 36 of the bellows region 33 is constant.

The midpoint of circle B is offset in the y-direction with respect to the midpoint of the smaller circle a. Additionally, the midpoint of the larger circle B is also offset in the x-direction with respect to the midpoint of the smaller circle a.

The shift of the midpoint may be described by a shift coefficient in the x-direction and a shift coefficient in the y-direction. Depending on the design of the skin space 33, it can be offset only in the x-direction, only in the y-direction or also in both directions.

The offset coefficient vx in the x direction can be between 0.1. ltoreq. x2/x 1. ltoreq.10, advantageously between 0.3. ltoreq. x2/x 1. ltoreq.1. The coefficient of offset vy in the y-direction may be between 0.1. ltoreq. y2/y 1. ltoreq.10, advantageously between 0.3. ltoreq. y2/y 1. ltoreq.1.

These variables x1, x2, y1, y2 are shown in the figure. These quantities describe the deviation of the two circles A, B from each other in the x-direction and the y-direction.

The described design of the bellows 27 allows the sliding ring seal to follow even large axial movements, without the pressure of the bellows 27 acting to press the sliding ring 17 against the mating ring 6 fluctuating significantly. The contact pressure is minimized by the design of the bellows 27, so that the sealing conditions in the sealing

gaps

16, 23 between the mating ring 6 and the slide ring 17 remain almost unchanged, independently of the axial movement of the two sealing rings or machine parts 7.

Since the bellows region 33 is arranged in a region outside the annular space 31, the range of motion of the bellows structure 27 is increased in the same installation state. Furthermore, a flat force-displacement curve of the bellows structure 27 is achieved thereby. As a result, the spring force changes only slightly in the axial path. This cross-sectional thickening of the skin space region 33 in the direction of the connecting region 32 has a positive influence on the force-displacement curve. In particular, stresses in the component can be reduced when deformation occurs.

The thickened design of the skin space 33 can also be described, depending on the specific design, by any different contour, with which the inner and outer contours of the skin space 33 can be approximated tangentially to the full thickness. As such, the thickening may be described by a rectangle, an ellipse, an involute, a spiral, and the like. The thickened region for the skin cavity region 33 is different from the contour shape of a circular contour, the offset or thickening being similarly defined relative to the midpoint or center of gravity of the respective contour.

In the same manner, the following exemplary embodiment according to fig. 2 to 4 has the described thickening of the skin space region 33 in the direction of the connecting region 32. For this purpose, the contour of the thickening is not described in detail below. Only different designs of the slide ring seal are described here.

In the slide ring seal according to fig. 2, the width of the annular flange 10 of the holder 9 is smaller than in the previous embodiment. The holder 9 is fitted with the cylindrical fastening section 8 in a rotationally fixed manner on the machine part 7, which is preferably a shaft.

Instead of a retaining sealing ring, a conical retaining piece 37 is provided in this embodiment. The holder surrounds the annular flange 10 on the outer edge with a connecting region 38.

This holding element 37 is fixedly connected to the mating ring 6 by means of a further connecting region 39. The connecting region 39 is a ring coaxial to the sealing axis, which bears with its end face 40 against the radial end face 41 of the mating ring 6.

The connecting region 39 is advantageously constructed identically to the annular fastening portion 28 of the bellows structure 27. In the end faces 29, 40 of the fastening part 28 and of the connecting region 39, there are provided shaped

structures

42, 43 in the form of recesses in which an adhesive is provided, by means of which the bellows structure 27 or the holding element 37 is connected to the sliding ring 17 and to the mating ring 6. The bellows structure 27 and the holder 7 may also be vulcanized on the slip ring 17 and the mating ring 6.

The connection region 39 is arranged such that its radially outer edge 44 lies on the same cylindrical surface as the

circumferential surfaces

18 and 20 of the mating ring 6 and the slip ring 17.

The diameter of the tapered region 45 increases from the connection region 38 of the holding element 37 towards the connection region 39. The conical region 45 is elastically deformable, so that during a possible axial movement of the mating ring 6 and the slip ring 17, the conical region is correspondingly elastically deformed.

As in the previous embodiment, the connection region 39 is located on the radially outer edge of the mating ring 6 and the fastening portion 28 is located on the radially inner edge region of the slip ring 17.

The embodiment according to fig. 3 differs from the embodiment according to fig. 2 in that the retaining section 28 has no shaping on its end side 29 and the cross section of the skin space region 33 does not increase toward the connecting region 32, as in the embodiments according to fig. 1 and 2. The holding part 28 is in surface contact with an end side 29 on an end side 30 of the slip ring 17.

The slip ring seal according to fig. 4 differs from the slip ring seal according to fig. 1 in that no shaping structures are provided on the end side 29 of the holding section 28 of the bellows structure 27. The holding part 28 thereby engages over the end face 30 of the slide ring 17. Here too, the cross section of the skin cavity region 33 does not increase towards the connecting region 32.

The slide ring seal according to fig. 5 has a housing 1 with

housing parts

2 and 3 which are offset from one another in the radial direction. The outer side of the housing part 3 is covered by a coating 47 which extends up to the transition to the housing part 2. The outer side of the coating 47 is advantageously provided with a profiling 48, which is advantageously designed as a wave in a radial sectional view.

The coating 47 on the housing part 3 has such a thickness that it projects radially outward from the housing part 2. If the housing 1 is pressed into the installation space of the corresponding device, the coating 48 is elastically deformed and forms a static sealing fit. The coating 47 is made of a corresponding, sealing, elastically deformable material, for example rubber.

The coating 47 also covers the annular collar 4 at least partially on the outer side of the radial annular collar facing away from the slip ring 17. The coating 47 is advantageously formed integrally with the bellows structure 27, which can be formed according to the embodiments according to fig. 1 to 4 and 6.

The coating 47 can cover the two

housing parts

2, 3 on the outside. In this case, it is not necessarily necessary for the housing 1 to have

housing parts

2, 3 which are offset from one another in the radial direction.

The slide ring 17 is pressed axially against the mating ring 6 in the manner described by means of the bellows structure 27. According to the embodiment according to fig. 2 and 3, the engagement ring is connected via a holder 37 to a holder 9 which is non-rotatably engaged on the machine part. In contrast to the embodiment according to fig. 2 and 3, the fixing section 8 of the holder 9 is stepped radially inwards. The fastening portion 8 rests with its free end region 8a on the machine part 7. This portion 8a merges into a portion 8b which surrounds the machine part 7 at a distance from it and merges into a radially outwardly directed annular collar 10. As in the embodiment according to fig. 2 and 3, the holding part 9 is advantageously of one-piece design and made of a metallic material, but can also be made of a correspondingly hard plastic and the like.

The annular space between the portion 8b and the machine part 7 is filled with the material of the connecting region 38 of the holder 37. A static sealing region is thus also formed in this region between the holder 9 and the machine part 7.

The annular flange 10 of the holder 9 projects axially beyond the free end of the housing 1. However, according to the embodiment according to fig. 2 and 3, the annular collar 10 can also be axially set back relative to the free end of the housing 1 or can be arranged at the same height as the free end.

The coupling of the mating ring 6 and the slip ring 17 on the holder 37 and on the bellows structure 27 can be arranged in the same way as in the embodiment according to fig. 2.

As shown in fig. 5, the mating ring 6 is not provided with the recess 22. Thereby, the mating ring 6 and the slip ring 17 abut against each other over the entire radial width of their

end sides

16, 23. The mating ring 6 and the slide ring 17 surround the fastening section 8 of the holder 9 at a small distance as in the previous exemplary embodiment. In contrast to the previous exemplary embodiment, the housing 1 encloses the mating ring 6 and the slip ring 17 at a significantly greater distance.

The slide ring seal can advantageously be configured as a gas-lubricated slide ring seal.

In the exemplary embodiment shown, the bellows structure 27 is fastened to the radial flange 4 of the housing 1. In these embodiments of the housing part 3, however, the bellows structure 27 can also be fastened to the inner and/or outer wall of the housing 1. The bellows structure 27 can also be designed in these cases such that the bellows region 33 is located axially outside the housing 1 or the annular space 31. Fig. 6 shows an exemplary embodiment of this type.

The housing 1 has two

housing parts

2, 3 which have different diameters. Unlike the previous embodiments, the housing part 3 does not have a radially inwardly directed annular flange. The bellows structure 27 surrounds the end of the housing part 3 facing away from the housing part 2 with a connecting region 32.

For the rest of the cases, this embodiment is configured identically to the exemplary embodiment according to fig. 1.

In this embodiment, it is also possible to dispense with the annular collar 4.

Claims

1. A sliding ring seal having a mating ring (6) and a sliding ring (17) which, under the force of a bellows structure (27), rests with a sealing surface (23) on a mating sealing surface (16) of the mating ring (6), the sliding ring seal further has a housing (1) which surrounds a sliding ring (17) and a mating ring (6) and which defines at least with the sliding ring (17) an annular space (31), and the slip ring (17) is connected with the housing via a bellows structure (27), the leather cavity structure is provided with a leather cavity area (33) which is connected on a connecting area, the leather cavity structure (27) is fixed on the shell (1) by utilizing the connecting area, characterized in that the bellows structure (27) radially inwardly defines the annular space (31) between the housing (1) and the slip ring (17), and the cortical region (33) is located at least substantially outside the annular region (31).

2. Slip ring seal according to claim 1, characterized in that the centre axis (35) of the bellows region (33) has an angle (a) of 0 ° to 90 ° with the centre axis (34) of the housing part (4) as seen in an axial sectional view.

3. Slip ring seal according to claim 1 or 2, characterized in that the bellows region (33) extends from the connection region (32) outwards from the housing (1).

4. Slide ring seal according to any one of claims 1 to 3, characterized in that the housing part (4) is a radial flange which is provided on one axial end of the housing (1) and extends radially inwards.

5. Slip ring seal according to any one of claims 1 to 4, characterized in that the cross-sectional thickness (36) of the bellows region (33) increases in the direction of the connection region (32).

6. Slip ring seal according to one of claims 1 to 5, characterized in that the outer and inner contour of the thickened part of the skin space (33), viewed in axial section, can each be described by a closed curve (A, B) having different center points.

7. Slip ring seal according to any of claims 1 to 6, characterized in that the offset of the midpoint of the two curves (A, B) is provided in the x-direction and/or the y-direction.

8. Slip ring seal according to any of claims 1 to 7, characterized in that the offset coefficient (vx) in the x-direction is 0.1 ≦ x2/x1 ≦ 10, preferably 0.3 ≦ x2/x1 ≦ 1, wherein x1, x2 are the spacing between the curves (A, B) in the x-direction.

9. Slip ring seal according to any of claims 1 to 8, characterized in that the offset coefficient (vy) in the y-direction is 0.1 ≦ y2/y1 ≦ 10, preferably 0.3 ≦ y2/y1 ≦ 1, wherein y1, y2 are the spacing between the curves (A, B) in the y-direction.

10. Slide ring seal according to one of claims 1 to 9, characterized in that the mating ring (6) is connected to the rotating machine part (7) by means of at least one flexurally elastic holder (37).

11. Slide ring seal according to one of claims 1 to 10, characterized in that the flexurally elastic holder (37) is fixed to a holder (9) which is fixed to the rotating machine part (7).

12. Slip ring seal according to any of claims 1-11, characterized in that the slip ring seal is a gas lubricated slip ring seal.