DE102021133857B3 - mechanical seal arrangement - Google Patents

Abstract

The invention relates to a mechanical seal arrangement (1), comprising: a mechanical seal (2) with a rotating seal ring (3) with a first sliding surface (30) and a stationary seal ring (4) with a second sliding surface (40) which is located between the first and second sliding surface (30, 40) define a sealing gap (5), a through opening (42) which is formed on the stationary sliding ring (4) and runs from a rear side (41) of the stationary sliding ring (4) to the second sliding surface (40), a circumferentially split thrust ring unit (6) which is circumferentially split such that the thrust ring unit (6) has a first sub-ring (61) and a second sub-ring (62), the second sub-ring (62) being radially inward of the first sub-ring ( 61), a secondary sealing arrangement (7) with a first secondary seal (71) and a second secondary seal (72), the first secondary seal (71) sealing on the first sub-ring (61) and the second secondary seal (72) on the second sub-ring ( 62), a passage (8) for a barrier fluid (C) being formed between the first sub-ring (61) and the second sub-ring (62) in order to supply barrier fluid (C) to the rear side (41) of the stationary seal ring (4). , and a biasing arrangement (10) arranged to bias the first sub-ring (61) and the second sub-ring (62) in the axial direction (X-X) towards the back (41) of the stationary slide ring (4).

Description

The invention relates to a mechanical seal arrangement with a pressure ring unit divided into two sub-rings in the circumferential direction, which has improved behavior in the event of pressure surges.

Mechanical seal arrangements are known from the prior art in different configurations. In the case of gas seals, the mechanical seal arrangement seals off a gaseous product from a rotating unit, for example a shaft. In this case, pressure peaks can occur in the gaseous product, which can lead to sealing problems in the mechanical seal arrangement during operation. Such pressure peaks can be caused by speed changes in a compressor, for example, or can also have other external influences. However, particularly in the case of toxic gaseous products, it is imperative to prevent this gaseous product from escaping into the atmosphere due to failure of the mechanical seal assembly.

The US 2021/0222701 A1 describes a mechanical seal with a porous stationary slide ring. A barrier fluid is supplied to the seal, which flows from the back of the stationary slide ring through the latter into the sealing gap.

The DE 20 2007 016 407 U1 describes a mechanical seal with a flow passage in the stationary seal ring through which a barrier fluid flows into the sealing gap.

It is the object of the present invention to provide a mechanical seal arrangement which, with a simple structure and simple, cost-effective manufacturability, can absorb pressure peaks in the product to be sealed without increased leakage occurring at the mechanical seal arrangement.

This object is achieved by a mechanical seal arrangement having the features of claim 1. The dependent claims show preferred developments of the invention.

The mechanical seal arrangement according to the invention with the features of claim 1 has the advantage that pressure peaks occurring in the product to be sealed can be absorbed without increased leakage occurring at the mechanical seal arrangement. Such pressure peaks usually only last for a short time, i.e. usually less than a second, but can be absorbed by the mechanical seal arrangement according to the invention in such a way that no additional leakage occurs at the mechanical seal arrangement. According to the invention, this is achieved in that the mechanical seal arrangement has a mechanical seal with a rotating seal ring with a first sliding surface and a stationary seal ring with a second sliding surface, which defines a sealing gap between the first and second sliding surface. Furthermore, a through opening is formed in the stationary slide ring, which leads from a rear side of the stationary slide ring to the second sliding surface on the sealing gap. The mechanical seal arrangement also includes a split pressure ring unit, which is split in the circumferential direction such that the split pressure ring unit has a first sub-ring and a second sub-ring. The second sub-ring is arranged radially inside the first sub-ring. Furthermore, a secondary seal arrangement is provided which has a first and a second secondary seal, the first secondary seal sealing on the first sub-ring and the second secondary seal sealing on the second sub-ring. A passage is provided between the first and second sub-rings for a barrier fluid to be supplied to the rear of the stationary seal ring. The face seal assembly further includes a biasing assembly for biasing the first and second sub-rings axially toward the rear of the stationary face ring. Thus, the mechanical seal arrangement according to the invention has a split pressure ring unit. Pressure peaks can be absorbed by the first sub-ring, which is arranged radially outside of the second sub-ring, while the second sub-ring can continue to exert the prestressing force required for low leakage on the stationary seal ring. The first sub-ring can thus move in the axial direction independently of the second sub-ring and absorb and cushion short-term pressure peaks in the product to be sealed. The mechanical seal arrangement according to the invention nevertheless has a very simple and cost-effective design which, in particular, saves installation space.

The passage between the first and second pressure ring is a circumferential gap. This can be provided in a particularly simple and cost-effective manner by simply dividing a base ring provided as a pressure ring into two rings in the circumferential direction. The gap is formed as a wavy gap. The wave-shaped gap has the great advantage that the length of the passage is greater than in the case of an annular gap, so that a larger quantity of barrier fluid can be fed through the passage to the mechanical seal. The wavy gap preferably has rounded tips or alternatively a zigzag shape.

More preferably, the passage between the first and second sub-rings further comprises a Opening. As a result, the amount of blocking fluid supplied to the mechanical seal can be further increased in a simple manner. The opening is preferably provided exclusively in the first sub-ring or alternatively exclusively in the second sub-ring. More preferably, the opening is formed both in the first and in the second subring, for example by providing two semicircular openings in the first and second subring in the region of the gap. A plurality of openings are preferably formed along the circumference of the compression ring assembly.

More preferably, a width of the first and second sub-rings is the same in the axial direction. A height of the first and second sub-rings in the radial direction is also preferably the same.

Alternatively, a width of the first sub-ring is preferably smaller than a width of the second sub-ring. This makes it possible that due to the division of the pressure ring, the first sub-ring can slide on the second sub-ring during any axial movements that may occur. As a result, the first subring is guided on the second subring and can safely carry out the compensating movements in the axial direction. As a result, particularly safe operation can be guaranteed. The second subring thus takes over the leadership of the first subring when it moves. More preferably, a width of the first sub-ring is greater than a width of the second sub-ring.

A width of one sub-ring is particularly preferably greater than a width of the other sub-ring and is less than or equal to twice the one width of the other sub-ring. This ensures mutual adequate axial guidance of the subrings.

More preferably, in the normal operating state, the subrings are arranged in such a way that the central axes of the subrings lie one above the other.

In order to enable particularly good mobility of the first sub-ring, the first sub-ring preferably has a recess for the first secondary seal on the outer circumference. The second sub-ring preferably also has a recess for the second secondary seal on an inner circumference.

In order to enable an even distribution of the barrier fluid on the rear side of the stationary slide ring, a circumferential gap is preferably formed between the rear side of the stationary slide ring and the split pressure ring unit.

Particularly preferably, the pretensioning arrangement comprises precisely one pretensioning unit, which pretensions the first and second subrings at the same time. Alternatively, the biasing arrangement comprises two biasing units, where one of the two biasing units biases only the first sub-ring and the other of the biasing units biases only the second sub-ring.

A pretensioning unit preferably comprises a multiplicity of spring elements, in particular cylindrical springs or coil springs. The spring elements can be cylindrical or conical. If only exactly one common pretensioning unit is provided for the first and second subring, the spring elements are preferably arranged in such a way that a spring element bears against both the first and the second subring.

A spring force of all individual spring elements of the prestressing unit is preferably the same. This ensures that the split pressure ring unit is evenly preloaded.

The pressure ring unit is preferably arranged on a sleeve-shaped component in order to be able to carry out axial movements in a simple manner.

More preferably, the first and second secondary seals are designed as O-rings.

The divided pressure ring unit is preferably arranged in a sealing fluid space.

Preferably, the face seal assembly is a gas lubricated face seal assembly. The gaseous product to be sealed is, for example, natural gas. The mechanical seal arrangement according to the invention is more preferably arranged as a tandem seal, with another mechanical seal arrangement being connected in series after the mechanical seal arrangement according to the invention.

Preferred embodiments of the invention are described in detail below with reference to the accompanying drawings. Identical or functionally identical parts are each denoted by the same reference symbols.

• 1 eine schematische Schnittansicht einer Gleitringdichtungsanordnung gemäß einem ersten Beispiel,
• 2 eine Schnittansicht entlang der Linie II-II von 1,
• 3 eine schematische, vergrößerte Teilschnittansicht der Gleitringdichtungsanordnung von 1,
• 4 eine schematische Draufsicht einer geteilten Druckringeinheit der Gleitringdichtungsanordnung von 1,
• 5 eine schematische Draufsicht einer geteilten Druckringeinheit einer Gleitringdichtungsanordnung gemäß einem ersten Ausführungsbeispiel der Erfindung,
• 6 eine schematische Draufsicht einer geteilten Druckringeinheit einer Gleitringdichtungsanordnung gemäß einem zweiten Beispiel der Erfindung,
• 7 eine schematische Draufsicht einer geteilten Druckringeinheit einer Gleitringdichtungsanordnung gemäß einem zweiten Ausführungsbeispiel der Erfindung, und
• 8 eine schematische, vergrößerte Teilschnittansicht einer Gleitringdichtungsanordnung mit geteilter Druckringeinheit gemäß einem dritten Beispiel der Erfindung.

In the drawing is:

• 1 a schematic sectional view of a mechanical seal assembly according to a first example,
• 2 a sectional view along the line II-II of FIG 1 ,
• 3 a schematic, enlarged partial sectional view of the mechanical seal assembly of 1 ,
• 4 a schematic plan view of a split pressure ring unit of the mechanical seal assembly of 1 ,
• 5 a schematic plan view of a split pressure ring unit of a mechanical seal assembly according to a first embodiment of the invention,
• 6 a schematic plan view of a split pressure ring unit of a mechanical seal assembly according to a second example of the invention,
• 7 a schematic plan view of a split pressure ring unit of a mechanical seal assembly according to a second embodiment of the invention, and
• 8th a schematic, enlarged partial sectional view of a mechanical seal assembly with split pressure ring unit according to a third example of the invention.

The 1 until 4 show a mechanical seal assembly 1 according to a first example of the present invention.

The mechanical seal arrangement 1 comprises a gas-lubricated mechanical seal 2 with a rotating seal ring 3 and a stationary seal ring 4 . The rotating seal ring 3 has a first sliding surface 30 and the stationary seal ring 4 has a second sliding surface 40 . A sealing gap 5 is defined between the two sliding surfaces 30 , 40 .

How out 1 As can be seen, the stationary slide ring 4 has a through opening 42 which extends from a rear side 41 of the stationary slide ring 4 to the second sliding surface 40 .

The mechanical seal arrangement 1 seals a first area 14 in which a pressurized product to be sealed, for example natural gas, is present from a second area 15 which is, for example, an atmospheric area.

The mechanical seal arrangement 1 can be used as an individual seal or in a tandem seal, in which at least one further seal is present in series before and/or after the mechanical seal arrangement 1 .

The mechanical seal assembly 1 further includes a circumferentially split pressure ring unit 6, which in detail from the 2 , 3 and 4 is evident. The split pressure ring unit 6 comprises a first sub-ring 61 and a second sub-ring 62. As shown in FIG 3 As can be seen, the first sub-ring 61 is arranged radially outside of the second sub-ring 62 .

The split pressure ring unit 6 is prestressed in the axial direction X-X of the mechanical seal arrangement 1 by means of a prestressing arrangement 10 and thus exerts a prestressing force on the stationary slide ring 4 .

Preferably, the biasing assembly 10 comprises two biasing units having a plurality of biasing elements biasing only the first sub-ring 61 and only the second sub-ring 62 .

How out 3 can be seen further, a secondary sealing arrangement 7 is arranged between the divided pressure ring unit 6 and the stationary seal ring 4 . The secondary sealing arrangement 7 comprises a first secondary seal 71 on the first sub-ring 61 and a second secondary seal 72 on the second sub-ring 62. In this exemplary embodiment, the two secondary seals 71, 72 are designed as O-rings. The first sub-ring 71 has a first recess 61a in its radially outer area. The second sub-ring 62 has a second recess 62a in its radially inner area. The secondary seals 71, 72 are arranged in the recesses 61a, 62a.

How further from 3 As can be seen, a passage 8 is provided between the first sub-ring 61 and the second sub-ring 62 . In this example, the passage 8 is an annular gap 80 which leads continuously from a first axial side of the split sealing ring unit 6 to the other axial side.

This makes it possible for a barrier fluid, which is fed into a barrier fluid chamber 19 via a supply channel 17 , to be fed through the passage 8 in the split pressure ring unit 6 into an annular intermediate space 9 on the rear side 41 of the stationary slide ring 4 . The barrier fluid is then fed from the annular intermediate space 9 to the sealing gap 5 via the through-opening 42 . At the sealing gap 5 , the flow of barrier fluid is divided into a radially outwardly directed portion, which is supplied to the first area 14 , and a radially inwardly directed portion, which is supplied to the second area 15 . The barrier fluid flow path is in 1 indicated by the arrows C.

In this example, the prestressing arrangement 10 comprises a multiplicity of spring elements which are designed as cylindrical springs 11 . 4 shows the arrangement of the cylinder springs 11, which can each be provided as individual springs. while practicing a cylinder spring 11 only exerts a force on either the first sub-ring 61 or the second sub-ring 62 . The cylinder springs 11 are in 4 shown in dashed lines, so that the respective point of application of the cylinder spring 11 on the first sub-ring 61 and on the second sub-ring 62 can be seen.

The stationary slide ring 4 is arranged between a housing 12 and a sleeve-shaped component 18 . The split compression ring assembly 6 is also located between the housing 12 and the sleeve-like member 18 and is capable of movement in the axial direction X-X.

How further from 3 As can be seen, the first sub-ring 61 has a first height H1 and the second sub-ring 62 has a second height H2. Here, the first height H1 and the second height H2 are the same. Furthermore, the first sub-ring 61 has a first width B1 and the second sub-ring 62 has a second width B2. The first width B1 and the second width B2 are the same.

The divided pressure ring unit 6 thus comprises two separate rings which are closed in the circumferential direction and which are arranged radially one above the other and have the passage 8 between them. This configuration of the pressure ring unit 6 makes it possible that, in the event of a short-term pressure peak in the first area 14 in the product, the pressure peak, which acts on the pressure ring unit 6 via a housing gap 13 between the housing 12 and the stationary slide ring 4 (cf. 3 ), only the first sub-ring 61 is moved in the axial direction XX against the spring force of the cylinder springs 11 . The second subring 62 remains in the in den 1 and 3 shown starting position. In 3 a pressure surge 16 is indicated schematically by the arrows. The first subring 61 then moves axially in the direction of arrow A against the spring force of the cylinder springs 11.

Thus, in the event of a possible pressure surge 16, only the outer of the two sub-rings 61, 62 of the split pressure ring unit 6 is moved, and the second sub-ring 62 remains in the initial position and continues to seal the mechanical seal 2 at the sealing gap 5.

As soon as the pressure surge 16 has ended, the first subring 61 is again in the in the by the spring force of the cylinder springs 11 1 and 3 shown starting position. As a result, reliable sealing by the first secondary seal 71 on the rear side 41 and on the housing 12 and the mechanical seal 2 is again possible.

Thus, the example can absorb pressure surges in a simple and safe way by cleverly dividing the pressure ring unit 6 into two ring-shaped sub-units. In this way, it can be prevented in particular that the stationary slide ring 4 also moves away from the rotating slide ring 3 in the axial direction X-X due to the short-term pressure increase in the first area 14 and thus opens the mechanical seal 2, so that the medium from the first area 14 via the now open sealing gap 5 can flow into the second region 15. Due to the prestressing force present via the second sub-ring 62 despite the pressure surge 16 and the movement of the first sub-ring 61 in the direction of arrow A, the stationary slide ring 4 can be held in the sealing position and does not move away from the rotating slide ring 3 in the axial direction X-X, even in the case of high pressure surges. This prevents an undesirably large leakage through the sealing gap 5 in the event of pressure surges.

The compensation function of the split pressure ring unit 6 can provide a compensation function even if the pressure of the barrier fluid is too low, which can occur, for example, with fluctuations in the pressure build-up for the barrier fluid. The inner second subring 62 also remains in the in 1 and 3 shown sealing position, so that the stationary seal ring 4 is always prestressed against the rotating seal ring 3 and seals in any pressure situation and no excessive leakage through the sealing gap 5 from the first area 14 to the second area 15 occurs.

5 shows a split pressure ring unit 6 of a mechanical seal assembly according to a first embodiment of the present invention. Identical or functionally identical parts are denoted by the same reference symbols.

How out 5 As can be seen, the passage 8 in the first exemplary embodiment is designed differently from the first example. In the first exemplary embodiment, the passage 8 is provided as a wave-shaped gap 81 between the first sub-ring 61 and the second sub-ring 62 . In this way, a length of the passage 8 is lengthened in the circumferential direction, so that a larger quantity of barrier fluid can flow through the passage 8 in the direction of the stationary seal ring 4 . The wave-shaped gap 81 can be designed with rounded tips or actually taper to a point. How further from 5 As can be seen, the prestressing arrangement 10 is formed by cylinder springs 11, which prestress the first subring 61 and the second subring 62 at the same time. When a pressure surge occurs, the cylinder springs 11 are loaded on one side, with the part of the cylinder springs 11 that rests on the first sub-ring 61 being moved axially, with the other part of the cylinder springs 11 that resting on the second sub-ring 62 remaining in the starting position, see above that the cylinder spring 11 despite inclined system still spring force on the second subring 62 exercises. As a result, the tightness of the mechanical seal 2 is maintained by the prestressing of the stationary slide ring 4, which is always present. Otherwise, this exemplary embodiment corresponds to the previous example, so that reference can be made to the description given there.

6 shows a split pressure ring unit 6 of a mechanical seal assembly 1 according to a second example. Identical or functionally identical parts are denoted by the same reference symbols as in the previous exemplary embodiments.

How out 6 As can be seen, the divided pressure ring unit 6 has a passage opening 82 in the second example. The passage opening 82 is formed in the region of the passage 8 by two through-openings which are semi-circular in section, one of the semi-circular through-openings being formed on the first and second sub-rings 61, 62 in each case. By providing the passage opening 82, a fluid quantity of the barrier fluid, which is guided through the passage 8, can be increased. It should be noted that it is possible for a plurality of through openings 82 to be provided. It should also be noted that it is also possible for passage openings to be formed exclusively in one of the subrings 61, 62. Here, for example, one or more passage openings 82 can be provided only in the first subring 61 or several passage openings 82 can be provided only in the second subring 62 or individual passage openings 82 can be formed both in the first and in the second subring 61, 62.

Otherwise, this example corresponds to the previous examples, so that reference can be made to the description given there.

7 shows a split pressure ring unit 6 of a mechanical seal assembly 1 according to a second embodiment of the invention. Identical or functionally identical parts are denoted by the same reference symbols as in the previous exemplary embodiment.

How out 7 As can be seen, the second embodiment is similar to that in FIG 5 first embodiment described constructed. However, in contrast to the first exemplary embodiment, the arrangement of the cylinder springs 11 in the second exemplary embodiment is such that two cylinder springs 11 preload only the first subring 61 and two cylinder springs 11 preload only the second subring 62 . In this case, the cylinder springs 11 each prestressing a ring are arranged opposite one another on the split pressure ring unit.

The arrangement of the cylinder springs is 11 in 7 such that all four cylinder springs 11 lie on a center circle 63 which is arranged on the split pressure ring unit 6 in such a way that a distance from the center circle 63 to the outer circumference is unequal to a distance from the center circle 63 to the inner circumference. The passage 8 in the second exemplary embodiment is again designed in the form of waves, with six waves being provided in this exemplary embodiment. Otherwise, this exemplary embodiment corresponds to the previous exemplary embodiment, so that reference can be made to the description given there.

8th shows a split pressure ring unit 6 of a mechanical seal assembly 1 according to a fifth embodiment of the invention. Identical or functionally identical parts are again denoted by the same reference symbols as in the previous exemplary embodiments.

The third example essentially corresponds to the first example, in contrast to the first example, in the third example the second width B2 of the second sub-ring 62 is greater than the first width B1 of the first sub-ring 61. B2 is in a range of B1<B2≦ 2 x B1 The second width is preferably B2=1.5×B1. As a result, the second sub-ring 62 serves as a guide element for the first sub-ring 61 when the latter executes an axial compensating movement in the direction of the arrow A. In particular, tilting or tilting of the first sub-ring 61 during the compensating movement can thereby be prevented. A reset of the first subring 61 in the in 8th shown neutral starting position are made possible again safely.

It should be noted that it is also possible that, alternatively, the first width B1 is greater than the second width B2. This achieves the same effect as with the in 8th configuration shown. Otherwise, this example corresponds to the first example, so that reference can be made to the description given there.

It should be noted with regard to all the exemplary embodiments that pressure surges 16, which can occur in the medium to be sealed, can be safely cushioned by cleverly dividing the pressure ring into two separate rings, without affecting the sealing quality of the mechanical seal 2, as was previously possible in the prior art , is diminished. Due to the movement of only one ring part of the pressure ring unit, the other ring part of the pressure ring unit always remains in preloaded contact with the stationary slide ring 4, whereby the preload of the stationary slide ring 4 in the axial direction XX is maintained and, during operation, a small sealing gap 5 between the stationary slide ring 4 and rotating sliding ring 3 is maintained. As a result, leakage through the sealing gap 5 is not increased even in the event of pressure surges, so that the performance of the mechanical seal arrangement 1 is not reduced even in the event of pressure surges.

In addition to the above written description of the invention, reference is hereby explicitly made to the graphic representation of the invention in FIGS 1 until 8th referenced.

Reference List

1

mechanical seal arrangement

2

mechanical seal

3

rotating sliding ring

4

stationary slide ring

5

sealing gap

6

split compression ring unit

7

secondary sealing arrangement

8th

passage

9

annular space

10

biasing arrangement

11

Spring elements / cylinder springs

12

Housing

13

housing gap

14

first area (product)

15

second area (e.g. atmosphere)

16

pressure surge

17

Barrier fluid supply channel

18

sleeve-shaped component

19

barrier fluid space

30

first sliding surface

40

second sliding surface

41

back

42

passage opening

61

first subring

61 a

first recess

62

second subring

62a

second recess

63

center circle

71

first secondary seal

72

second secondary seal

80

annular gap

81

wavy gap

82

passage opening

A

Movement of the first subring

B1

first width of the first subring

B2

second width of the second subring

C

barrier fluid

H1

first height of the first subring

H2

second height of the second subring

X-X

axial direction

Claims (12)

Mechanical seal arrangement (1), comprising: • a mechanical seal (2) with a rotating slide ring (3) with a first sliding surface (30) and a stationary slide ring (4) with a second sliding surface (40), which between the first and second sliding surface (30, 40) has a sealing gap ( 5) define, • a through opening (42) which is formed on the stationary slide ring (4) and runs from a rear side (41) of the stationary slide ring (4) to the second sliding surface (40), • a circumferentially divided pressure ring unit (6), which is divided in the circumferential direction such that the pressure ring unit (6) has a first sub-ring (61) and a second sub-ring (62), the second sub-ring (62) being radially inward of the first sub-ring (61) is arranged, • a secondary seal arrangement (7) with a first secondary seal (71) and a second secondary seal (72), wherein the first secondary seal (71) seals the first sub-ring (61) and the second secondary seal (72) seals the second sub-ring (62), • wherein a passage (8) for a barrier fluid (C) is formed between the first sub-ring (61) and the second sub-ring (62) in order to supply barrier fluid (C) to the back (41) of the stationary slide ring (4), • wherein the passage (8) is a circumferential gap, • wherein the circumferential gap is an undulating gap (81), and • a preload assembly (10) arranged to preload the first sub-ring (61) and the second sub-ring (62) in the axial direction (X-X) towards the back (41) of the stationary slide ring (4). Mechanical seal arrangement (1) according to claim 1 , wherein the passage (8) further comprises a passage opening (82). Mechanical seal arrangement (1) according to claim 2 , wherein the passage opening (82) is formed in the region of the gap of the passage (8) or wherein the passage opening (82) only in the first th sub-ring (61) and/or is formed only in the second sub-ring (62). Mechanical seal arrangement (1) according to one of the preceding claims, wherein a width (B1, B2) and a height (H1, H2) of the first sub-ring (61) and of the second sub-ring (62) is the same. Mechanical seal arrangement according to one of Claims 1 until 3 , wherein a width (B1) of the first sub-ring (61) is different from a width (B2) of the second sub-ring (62). Mechanical seal arrangement according to claim 5 , wherein the width (B1) of the first sub-ring (61) is smaller than the width (B2) of the second sub-ring (62). Mechanical seal arrangement (1) according to one of the preceding claims, wherein an annular gap (9) is formed between the back (41) of the stationary slide ring (4) and the split pressure ring unit (6). Mechanical seal arrangement (1) according to one of the preceding claims, wherein the prestressing arrangement (10) has a prestressing unit which only the first subring (61) and/or only the second subring (62) is axially prestressed or wherein the prestressing arrangement (10) has a prestressing unit , which simultaneously preloads the first subring (61) and the second subring (62) axially. Mechanical seal arrangement (1) according to claim 8 , wherein the biasing units comprise spring elements (11). mechanical seal arrangement claim 9 , wherein a spring force of the spring elements is equal. Mechanical seal arrangement (1) according to one of the preceding claims, wherein the divided pressure ring unit (6) is arranged in a sealing fluid space (19). Mechanical seal arrangement (1) according to one of the preceding claims, which is designed as a gas-lubricated mechanical seal arrangement (1).

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