Tunnelling machine

Abstract

The invention relates to a tunnelling machine in which a sealing assembly (212) is provided which has a first internal chamber (369) and a second internal chamber (372) to which lubricants can be applied via a fluid-supply assembly. A pressure in the first internal chamber (369) can be adjusted by the fluid-supply assembly such that the pressure is between a pressure in a head chamber (306), which is at the front in the advancing direction of the first internal chamber (369), and a pressure in the second internal chamber (372), which is behind the first internal chamber (369) in the advancing direction. As a result, and also for environmental-protection reasons, loss-free lubrication is advantageously achieved, and mixing of the lubricant present in the first internal chamber (369) with components of other substance families present in the head chamber (306) is prevented.

Description

[0001] Tunnel boring machine

[0002] The invention relates to a tunnel boring machine having the features of the preamble of claim 1.

[0003] Such a tunnel boring machine is known from DE 20 2020 104 813 U1. This previously known tunnel boring machine has a drive shaft which is designed to rotate a cutting wheel. Furthermore, a sealing arrangement is provided which is designed to seal an annular gap formed around the drive shaft between stationary components and rotating components. The sealing arrangement has a number of sealing rings and chambering rings arranged between the sealing rings. Furthermore, a fluid supply arrangement designed to supply lubricants and a number of receiving chambers formed between adjacent sealing rings are provided, which comprise a first internal chamber located at the front in an advance direction and a second internal chamber located at the rear of the first internal chamber in an advance direction, which can be pressurized with lubricants.

[0004] From EP 3 854 990 A1 a cascade-like sealing arrangement similar to that in the aforementioned DE 20 2020 104 813 U1 is known, in which an increase in pressure in the interior is provided compared to a support pressure.

[0005] From CN 107 401 678 A, a cascade-type sealing arrangement for a tunnel boring machine is also known, similar to that in the aforementioned DE 20 2020 104 813 Ul, which is intended for high support pressures and in which a pressure equalization chamber is provided.

[0006] From DE 10 2009 014 214 A1 a sealing device for a rotary feedthrough for sealing a vacuum against atmospheric pressure is known, which has an intermediate chamber with an intermediate vacuum.

[0007] The invention is based on the object of specifying a tunnel boring machine of the type mentioned at the outset, which is characterized by a resource-saving sealing arrangement with relatively low wear and which, in addition, for reasons of environmental protection, leaves the conditioning of media in the direction of advance in the area in front of the sealing arrangement essentially unaffected during normal operation.

[0008] This object is achieved according to the invention in a tunnel boring machine of the type mentioned at the outset with the characterizing features of claim 1.

[0009] Because in a tunnel boring machine according to the invention there is an intermediate pressure in the area of ​​the first inner chamber, which lies between the pressure of the area in front of the first inner chamber in the direction of advance and the pressure in the second inner chamber, lubricant present in the first inner chamber remains in the first inner chamber essentially without loss, so that in normal operation a largely resource- and environmentally friendly lubrication results and an escape of lubricant from the first inner chamber into the area in the direction of advance, which is usually conditioned with additives of a different material class in order to improve environmental protection, is avoided.

[0010] Further useful embodiments are the subject of the dependent claims.

[0011] Further expedient embodiments and advantages of the invention will become apparent from the following description of an embodiment of the invention with reference to the figures of the drawing.

[0012] It shows :

[0013] Fig. 1 shows a perspective view of an embodiment of a tunnel boring machine according to the invention in the front area on the mining side, with a view of a cutting wheel,

[0014] Fig. 2 in a perspective view corresponding to Fig. 1 the embodiment of the tunnel boring machine with removed cutting wheel and view of a rotary drive arrangement of the tunnel boring machine, which is sealed by an exemplary sealing arrangement, which has a radially outside arranged first sealing area and a radially inside arranged second sealing area, Fig. 3 in a sectional view a

[0015] Embodiment of the first sealing area of ​​the sealing arrangement according to Fig. 2 for the rotary drive arrangement,

[0016] Fig. 4 shows a sectioned end view of the sealing areas of the sealing arrangement according to Fig. 2,

[0017] Fig. 5 shows a perspective view of a partial section of a chamber ring of the sealing arrangement according to Fig. 3,

[0018] Fig. 6 in a perspective, enlarged section of a chambering ring on both sides of a groove boundary compared to the illustration in Fig. 5,

[0019] Fig. 7 shows a sectional view of an embodiment of the second sealing region of the sealing arrangement according to Fig. 2,

[0020] Fig. 8 shows a schematic hydraulic circuit diagram of an embodiment of a fluid supply arrangement,

[0021] Fig. 9 shows a schematic view of an exemplary sealing arrangement with an exemplary first pressure curve,

[0022] Fig. 10 shows a schematic view of the exemplary sealing arrangement according to Fig. 9 with an exemplary second pressure curve and Fig. 11 shows a schematic view of the exemplary sealing arrangement according to Fig. 9 with an exemplary third pressure curve.

[0023] Fig. 1 shows a perspective view of an embodiment of a tunnel boring machine designed to drive a tunnel in the region of a boring head 103. The boring head 103 is designed with a shield casing 106 closed in the circumferential direction and with a cutting wheel 109 which, in a direction of advance, closes off the shield casing 106 at the end to form a working face with an excavation area 112 and, in the illustration according to Fig. 1, faces the viewer. The cutting wheel 109 is equipped in a conventional manner with a number of excavation tools (not explained in detail) and is rotatable.

[0024] Fig. 2 shows, in a perspective view corresponding to the view in Fig. 1, the tunneling head 103 with a view of a baffle 203 located to the rear of the cutting wheel 109 (not shown in Fig. 2) in the direction of advance. From Fig. 2 it can be seen that the baffle 203 has a ring-segment-like basic shape with a radially inner breakthrough area in which a drive shaft 206 designed as a hollow shaft is arranged. During operation of the tunnel boring machine, the drive shaft 206 is in rotationally fixed engagement with the cutting wheel 109 (not shown in Fig. 2) and with a rotary drive arrangement 209 arranged to the rear of the baffle 203 in the direction of advance, which is designed to drive the cutting wheel 109 to rotate in expediently two directions of rotation.

[0025] To seal the drive shaft 206 in the passage area through the baffle 203, the exemplary embodiment explained has a sealing arrangement 212 which has a first sealing area 215 arranged radially on the outside and a second sealing area 218 arranged radially on the inside.

[0026] Fig. 3 shows a sectional view in a sectional plane extending in the axial direction of the first sealing region 215 of the sealing arrangement 212 according to Fig. 2.

[0027] The sealing arrangement 212 has in the first sealing region 215 a head seal 303 which is arranged at the front in the direction of advance and delimits a head chamber 306 which is expediently designed in a labyrinthine manner and extends in the direction of the cutting wheel 109 and thus into the mining region 112. The head chamber 306 is delimited radially on the inside by a sealing support ring 309 and on the front side by a closing ring 312. The head seal 303, in turn, is arranged between the sealing support ring 309 and a cover ring 315. The head chamber 306 is fluid-mechanically connected to a feed line 321 of a feed line arrangement 324 via end sections 318 formed in the closing ring 312 and in the cover ring 315. A conditioning agent can be fed in via the supply line 321 opening into the head chamber 306 and is designed to condition the area in the direction of advance in front of the sealing arrangement 212.The head gasket 303 is held on the front side in the direction of advance by a fixing section 327 of the end ring 312.

[0028] On the rear side of the head gasket 303 in the direction of advance, a first chambering ring 330 is arranged, which is arranged as a stationary component between the seal support ring 309 and a seal carrier 336 arranged in the radial direction on the outside of the seal support ring 309, forming an annular gap 333.

[0029] On the rear side of the first chambering ring 330 in the direction of advance, a first internal seal 339 is arranged, which is held by the first chambering ring 330 on its front side in the direction of advance and by a second chambering ring 342 on its rear side in the direction of advance. The second chambering ring 342 is also located between the seal support ring 309 and the seal carrier 336.

[0030] On the side of the second chambering ring 342 which is located at the rear in the direction of advance, a second internal seal 345 is positioned, next to which a third chambering ring 348 is arranged on its side which is located at the rear in the direction of advance.

[0031] Finally, in the embodiment shown in Fig. 3, on the side located to the rear of the third chambering ring 348 in the direction of advance, a closing seal 351 is arranged, which is held in the direction of advance at the rear by a fixing section 354 lying against the seal carrier 336. As can be seen from the illustration according to Fig. 3, the head seal 303, the internal seals 339, 345 and the closing seal 351 are each formed with a block-like base body 357, which is positioned radially on the outside, and with a sealing lip 360, which is pivotally attached to the respective base body 357 via a joint section with a relatively low material thickness and rests on the seal support ring 309 with a certain preload.The sealing lips 360 of the head gasket 303 and the internal seals 339, 345 are aligned such that they point in the direction of the end ring 312, while the sealing lip 360 of the end seal 351 is aligned away from the end ring 312 and towards the fixing section 354.

[0032] Furthermore, it can be seen from the illustration in Fig. 3 that the chamber rings 330, 342, 348 are each formed with a radially outer annular groove 363, which is open in the direction of the seal carrier 336 and opens into the end sections 318 of supply lines 321 of the supply line arrangement 324 for the required supply of lubricants or compressed air. In turn, passage recesses 366, distributed in the circumferential direction, open into the annular grooves 363 and create a fluid connection between the annular grooves 363 and the annular gap 333.

[0033] Thus, a first internal chamber 369 is formed as receiving chambers between the head seal 303 and the first internal seal 339, and a second internal chamber 372 is formed between the first internal seal 339 and the second internal seal 345, while a closing chamber 375 is formed as a further receiving chamber between the second internal seal 345 and the closing seal 351.

[0034] During mining operation, a pressure prevails in the head chamber 306, which is connected to the mining area 112, which is at least slightly higher than the support pressure prevailing in the mining area 112, wherein the support pressure in a pressure-supported mining operation corresponds to a multiple of the atmospheric pressure.

[0035] The area located on the side of the end seal 351 opposite the end chamber 375 is, in normal operation, delimited by a roller bearing 378, and is connected on its rear side in the direction of advance to a pressure prevailing in a gear housing, for example atmospheric pressure, via a connecting line 381, which extends in sections between the seal support ring 309 and the roller bearing 378.

[0036] Furthermore, it can be seen from the illustration in Fig. 3 that a flange ring 384 is arranged radially inside the sealing support ring 309, which is connected in a rotationally fixed manner to the drive shaft 206 (not shown in Fig. 3). A labyrinth plate 387 is detachably attached to the end ring 312 by a screw connection on its front side in the direction of advance.

[0037] In the first sealing area 215, the

[0038] Seal support ring 309, an inner ring of the roller bearing 378 and the flange ring 384 are running components, while the head seal 303, the end ring 312, the cover ring 315, the first chambering ring 330, the seal carrier 336, the first internal seal 339, the second chambering ring 342, the second internal seal 345, the third chambering ring 348, the end seal 351, an outer ring of the roller bearing 378 and the labyrinth plate 387 are stationary components.

[0039] It is understood that in modifications of the embodiment explained above, particularly in the case of propulsion with very high support pressures, at least one further internal chamber is present in addition to the two aforementioned internal chambers 368, 372 in order to achieve a pressure reduction in at least three or more internal chambers, including the provision of redundancy.

[0040] Fig. 4 shows a sectional view in the area of ​​the first internal chamber 369, a section of the sealing arrangement 212 in the first sealing region 215. From the illustration according to Fig. 4, it can be seen that the passage recesses 366 are arranged at a regular distance over the circumference of the first chambering ring 330. In the apex region shown in Fig. 4, which is located at the top with respect to gravity, a zenith groove limiter 403 is arranged at its zenith and an edge groove limiter 406 is arranged on either side of the zenith groove limiter 403, which limit the annular groove 363 in the circumferential direction as a flow brake and expediently also seal it off from the seal carrier 336 to a certain extent.This ensures that in both directions of rotation of the cutting wheel 109, lubricant entering via the end sections 318 of the supply lines 321 is held in the apex region and passes essentially completely through the passage recesses 366 to produce reliable lubrication in the apex region.

[0041] The areas around the second chambering ring 342, not visible in Fig. 4, and around the third chambering ring 348, also not visible in Fig. 4, are constructed accordingly.

[0042] Fig. 5 shows, in a sectional perspective view, the structure of the first chambering ring 330, the second chambering ring 342 and the third chambering ring 348 being constructed correspondingly. From the illustration in Fig. 5, it can be seen that a number of passage recesses 366 are formed between the zenith groove boundary 403 and each edge groove boundary 406. On the side of each edge groove boundary 406 facing away from the zenith groove boundary 403, further passage recesses 366 are formed in the first chambering ring 330 in order to ensure a supply of lubricants even outside the zenith region shown in Fig. 5.

[0043] Fig. 6 shows, in a perspective view corresponding to Fig. 5, an enlarged view of the area around a groove boundary acting as a flow brake, for example the zenith groove boundary 403. The illustration according to Fig. 6 shows that the zenith groove boundary 403, like the corresponding edge groove boundaries 406, is formed by a sliding block 603 which crosses the annular groove 363 and terminates radially on the outside with the annular groove 363, which is detachably and firmly connected to the first chambering ring 330 by a sliding block fastening screw 606.

[0044] In a modification not shown, the zenith groove limitation 403 and the edge groove limitations 406 are formed by cross pieces formed integrally with the respective chambering ring 330, 342, 348.

[0045] Fig. 7 shows a sectional view corresponding to the illustration in Fig. 3 of the sealing arrangement 212 in the second sealing region 218. From the illustration in Fig. 7 it can be seen that the essential components of the sealing arrangement 212 in the second sealing region 218 are constructed in a manner corresponding to the first sealing region 215 explained above, wherein, to avoid repetition in the two sealing regions 215, 218, functionally corresponding components are provided with the same reference numerals and, to avoid repetition, some of them are not explained in detail again below.A difference between the chambering rings 330, 342, 348 installed in the first sealing area 215 and the chambering rings 330, 342, 348 installed in the second sealing area 218 is generally that the chambering rings 330, 342, 348 installed in the second sealing area 218 are free of passage recesses 366 and are therefore solid and uninterrupted in the circumferential direction in the central area.

[0046] Furthermore, in the second sealing region 218, the sealing support ring 309 is designed as a stationary component, while the flange ring 384 is a rotating component. The supply of lubricants for the internal chambers 369, 372 takes place via end sections 318 of supply lines 321 of the supply line arrangement 324, which are formed in the sealing support ring 309 and which also extend, for example, through a gear housing 703 arranged radially on the inside of the sealing support ring 309. Separators 706 are arranged as flow brakes in the region of the end sections 318 of the supply lines 321. This ensures a reliable supply of lubricants in the apex region of the second sealing region 218.

[0047] In the second sealing area 218 s , the head seal 303 , the end ring 312 , the first chambering ring 330 , the first internal seal 339 , the second chambering ring 342 , the second internal seal 345 , the third chambering ring 348 , the end seal 351 , an inner ring of the roller bearing 378 and the flange ring 384 are moving components, while the seal support ring 309 , an outer ring of the roller bearing 378 and the gear housing 703 are stationary components.

[0048] Fig. 8 shows a schematic circuit diagram of an embodiment of a fluid supply arrangement 803 which is set up in particular to feed lubricant or compressed air into the first internal chambers 369 and into the second internal chambers 372, as explained in more detail below, the following explanations relating by way of example to the conditions in one of the sealing areas 215, 218, which behave identically in both sealing areas 215, 218. The fluid supply arrangement 803 has a first level compensation container 806 which is connected via a fluid inlet line 809 to the zenith area of ​​the first internal chamber 369 and via a fluid outlet line 812 on the sump side to the first internal chamber 369. The fill level of the first level compensation container 806 is expediently indicated by two sensors shown in Fig.8 is equipped with fill level sensors (not shown for clarity), which are designed to issue a warning signal when a maximum fill level is exceeded or a minimum fill level is undershot in the first level compensation tank 806. Furthermore, the fluid supply arrangement 803 has a circulation pump 815, which is connected via a closed circulation line 818 on the inlet side to the sump region of the first internal chamber 369 and on the outlet side to the zenith region of the first internal chamber 369.The circulation pump 815 cooperating with the first internal chamber 369 is designed to circulate lubricant fed into the first internal chamber 369 in order to ensure, particularly in the case of large diameters, reliable lubrication in the zenith region independent of the respective pressure conditions in the internal chambers 369, 372 and in the closing chamber 375 both in the first sealing region 215 and in the second sealing region 218.

[0049] Furthermore, the fluid supply arrangement 803 is equipped with a compressed air reservoir 821, which is designed to maintain a predetermined pressure and which is connected to the first level compensation tank 806 via a pneumatic throttle 824.1 and a switchable seat valve 827.1. Thus, when the seat valve 827.1 connected to it is in the open position, the first level compensation tank 806 can be pressurized with pressure originating from the first compressed air reservoir 821, namely a pressure higher than atmospheric pressure, so that the first internal chamber 369 can be selectively pressurized with lubricant or with compressed air via the fluid inlet line 809.

[0050] Furthermore, a vacuum line 830 is connected to the first level compensation tank 806 via a further throttle 824.2 and a further switchable seat valve 827.2, which is connected to the inlet side of a vacuum pump 833 of the fluid supply arrangement 803. The vacuum pump 833 is, as explained in more detail below, configured to pressurize the first internal chamber 369 with a predetermined pressure lower than atmospheric pressure when the seat valve 827.2 arranged in the vacuum line 830 is in the open position and when the seat valve 827.1 arranged between the first compressed air reservoir 821 and the first level compensation tank 806 is in the closed position.

[0051] Furthermore, it can be seen from the illustration according to Fig. 8 that the first level compensation tank 806 is connected to a pressure measuring unit 842 via a pressure measuring line 836 with an intermediate ball valve 839. The pressure measuring unit 842, which can be connected to the first level compensation tank 806, is designed to measure the pressure prevailing in the first level compensation tank 806 as needed.

[0052] The fluid supply arrangement 803 further comprises a second level compensation tank 845, which is connected to the zenith region of the second internal chamber 372 via a fluid inlet line 809 and to the sump side of the second internal chamber 372 via a fluid outlet line 812. The fill level of the second level compensation tank 845 is expediently equipped with two fill level sensors (not shown in Fig. 8 for clarity), which are configured to emit a warning signal when a maximum fill level is exceeded or a minimum fill level is undershot in the second level compensation tank 845. Furthermore, the fluid supply arrangement 803 has a circulation pump 815 which is connected via a closed circulation line 818 on the inlet side to the sump region of the second inner chamber 372 and on the outlet side to the zenith region of the second inner chamber 372.The circulation pump 815 cooperating with the second inner chamber 372 is designed to circulate lubricant fed into the second inner chamber 372 in order to ensure reliable lubrication in the zenith area, particularly in the case of large diameters.

[0053] The compressed air reservoir 821 of the fluid supply arrangement 803 is connected to the second level compensation tank 845 via a pneumatic throttle 824.1 and a switchable seat valve 827.1. Thus, when the seat valve 827.1 connected to it is in the open position, the second level compensation tank 845 can be pressurized with pressure originating from the compressed air reservoir 821, namely a pressure higher than atmospheric pressure, so that the second internal chamber 372 can be selectively pressurized with lubricant or with compressed air via the fluid inlet line 809.

[0054] Furthermore, the vacuum line 830, which is connected to the inlet side of the vacuum pump 833, is connected to the second level compensation tank 845 via a further throttle 824.2 and a further switchable seat valve 827.2. The vacuum pump 833 is, as explained in more detail below, configured to apply a predetermined negative pressure to the second internal chamber 372 relative to atmospheric pressure when the switchable seat valve 827.2 arranged in the vacuum line 830 is in the open position and when the seat valve 827.1 arranged between the compressed air reservoir 821 and the second level compensation tank 845 is in the closed position.

[0055] Furthermore, it can be seen from the illustration in Fig. 8 that the second level compensation tank 845 is connected to a pressure measuring unit 842 via a pressure measuring line 836 with an interposed ball valve 839. The pressure measuring unit 842, which can be connected to the second level compensation tank 845, is configured to measure the pressure prevailing in the second level compensation tank 845 as needed. In addition to the arrangement in connection with the first internal chamber 369 and the first level compensation tank 806, a ventilation part 848 is connected to the second level compensation tank 845 with the interposition of a pneumatic throttle 824.3 and a switchable seat valve 827.3, with which the second level compensation tank 845 when the seat valve 827.3 arranged downstream of the ventilation part 848 is in the open position and when the seat valve 827 arranged downstream of the compressed air reservoir 821 is in the closed position.1 and when the seat valve 827.2 downstream of the vacuum pump 833 is in the closed position, it can be pressurized with atmospheric pressure.

[0056] The fluid supply arrangement 803 further comprises a fluid buffer tank 851, which is connected to the zenith region of the closure chamber 375 via a fluid inlet line 809 and to the sump side of the closure chamber 375 via a fluid outlet line 812. The fluid buffer tank 851 is configured to supply air to the closure chamber 375, but also lubricant if necessary, particularly for lubricating the closure seal 357.

[0057] The compressed air reservoir 821 of the fluid supply arrangement 803 is connected to the fluid buffer tank 851 via a pneumatic throttle 824.1 and a switchable seat valve 827.1. Thus, when the seat valve 827.1 connected to it is in the open position, the fluid buffer tank 851 can be pressurized with pressure originating from the compressed air reservoir 821, namely a pressure higher than atmospheric pressure.

[0058] Furthermore, the vacuum line 830, which is connected to the inlet side of the vacuum pump 833, is connected to the fluid buffer tank 851 via a further throttle 824.2 and a further switchable seat valve 827.2. The vacuum pump 833 is, as explained in more detail below, configured to pressurize the fluid buffer tank 851 with a predetermined pressure that is lower than atmospheric pressure when the seat valve 827.2 arranged in the vacuum line 830 is in the open position and when the seat valve 827.1 arranged between the compressed air reservoir 821 and the fluid buffer tank 851 is in the closed position.

[0059] Furthermore, it can be seen from the illustration in Fig. 8 that the fluid buffer tank 851 is connected to a pressure measuring unit 842 via a pressure measuring line 836 with an interposed ball valve 839. The pressure measuring unit 842, which can be connected to the fluid buffer tank 851, is configured to measure the pressure prevailing in the fluid buffer tank 851 as needed.

[0060] A ventilation part 848 is connected to the fluid buffer tank 851 with the interposition of a pneumatic throttle 824.3 and a switchable seat valve 827.3, with which the fluid buffer tank 851 can be pressurized with atmospheric pressure when the seat valve 827.3 arranged downstream of the ventilation part 848 is in the open position and when the seat valve 827.1 arranged downstream of the compressed air reservoir 821 is in the closed position and when the seat valve 827.2 arranged downstream of the vacuum pump 833 is in the closed position.

[0061] From the illustration according to Fig. 8 it can further be seen that the closing chamber 375 is equipped in the sump area with a liquid outlet 854 which is designed to discharge liquid into a collecting container 857 when it accumulates in the closing chamber 375.

[0062] Furthermore, the fluid supply arrangement 803 is equipped with a vacuum storage tank 860, which is connected to the vacuum line 830 to compensate for pressure fluctuations. The vacuum storage tank 860 is also connected to a pressure measuring unit 842 via a pressure measuring line 836 with an interposed ball valve 839 in order to determine the average pressure in the vacuum line 830.

[0063] In addition, it is expedient that the fluid supply arrangement 803 is equipped with various monitoring sensors, not shown in Fig. 8 for reasons of clarity, for measuring in particular temperatures, water contents, volume flows and / or dirt contents, which are also advantageously designed to detect or predict fault conditions and to emit warning signals when limit values ​​are exceeded or undershot.

[0064] Furthermore, it is understood that in one embodiment the circulation pumps 815 and the vacuum pump 833 form a structural unit for a space-saving design.

[0065] The fluid supply arrangement 803 is further equipped with a central control and regulation module 863 which, as shown by arrows with two arrowheads each, is designed to receive the signals from the components explained above, such as in particular the throttles 824.1, 824.2, 824.3, seat valves 827.1, 827.2, 827.3 and pressure measuring unit 842, or to control them, as explained in more detail below.

[0066] If a support pressure is present at the working face 112 or, for example, if a reference pressure p_ref prevails in the head chamber 306 that is greater than a limit pressure p_limit, then the fluid supply arrangement 803 is operated in an overpressure mode. A predetermined target pressure is stored in the control and regulation module 863 for the first internal chamber 369, the second internal chamber 372, the closing chamber 375, and the connecting line 381 connected to the gear chamber. This target pressure depends, for example, on the atmospheric pressure as the reference pressure p_ref. Typically, the values ​​for the target pressures are available in a table as a function of the reference pressure p_ref.Furthermore, the reference pressure p_ref is greater than the pressure in the first internal chamber 369, the pressure in the first internal chamber 369 is greater than the pressure in the second internal chamber 372, the pressure in the second internal chamber 372 is greater than the pressure in the closing chamber 375, and the pressure in the closing chamber 375 is less than or equal to the pressure in the connecting line 381. If necessary, the pressure in the gear chamber is higher than the pressure in the closing chamber 375 so that the sealing lip 360 of the closing seal 357 located between the gear chamber and the closing chamber 375 is pressed to support the sealing effect.

[0067] If the pressure in the first internal chamber 369, in the second internal chamber 372 or in the closing chamber 375 falls below a target pressure or if the target pressure in the first internal chamber 369, in the second internal chamber 372 or in the closing chamber 375 has not yet been reached, the relevant seat valve 827.1 downstream of the compressed air reservoir 821 is opened. As a result, compressed air flows into the first internal chamber 369, into the second internal chamber 372 or into the closing chamber 375 until the required pressure in the first internal chamber 369, in the second internal chamber 372 or in the closing chamber 375 is reached or reached again. The seat valve 827.2, which is connected in parallel and downstream of the vacuum pump 833, is closed.

[0068] When the target pressure is reached, the relevant seat valve 827.1 upstream of the compressed air reservoir 821 is closed and the pressure is maintained.

[0069] If the pressure in the first internal chamber 369 rises above the target pressure, for example because the reference pressure p_ref falls, the seat valve 827.2 located between the first internal chamber 369 and the vacuum pump 833 is opened, and the vacuum pump 833 sucks air out of the first internal chamber 369 via the throttle 824.2 upstream of the vacuum pump 833 until the target pressure is reached again in the first internal chamber 369.

[0070] The parallel seat valve 827.1 connected to the compressed air reservoir 821 is closed.

[0071] If the pressure in the second internal chamber 372 rises above the target pressure, for example because the reference pressure p_ref and / or the pressure in the first internal chamber 369 falls, either the seat valve 827.2 located between the second internal chamber 372 and the vacuum pump 833 is opened, whereby the vacuum pump 833 sucks air out of the second internal chamber 372 via the throttle 824.2 upstream of the vacuum pump 833 until the target pressure in the second internal chamber 372 is reached again, or the seat valve 827.3 upstream of the ventilation part 848 is opened and the pressure in the second internal chamber 372 is released if the target pressure in the second internal chamber 372 is atmospheric pressure. The seat valve 827.1 located between the compressed air reservoir 821 and the second internal chamber 372 is closed in both cases.

[0072] If the pressure in the closing chamber 375 rises above the target pressure, for example because the reference pressure p_ref and / or the pressure in the second internal chamber 372 falls, the seat valve 827.2 located between the closing chamber 375 and the vacuum pump 833 is opened, and the vacuum pump 833 sucks air out of the closing chamber 375 via the throttle 824.2 downstream of this seat valve 827.2 until the target pressure in the closing chamber 375 is reached again. The seat valve 827.3 upstream of the venting part 848 is closed in this case. In another procedure, the seat valve 827.3 upstream of the venting part 848 is opened, and the pressure in the closing chamber 375 is released when the target pressure in the closing chamber 375 is atmospheric pressure.

[0073] The corresponding seat valve 827.1 upstream of the compressed air reservoir 821 is closed in both of the above-mentioned procedures.

[0074] The second internal chamber 872 and / or the closing chamber 375 are permanently maintained at atmospheric pressure via the ventilation part 848, without the need for any control. For this purpose, the seat valves 827.1 upstream of the compressed air reservoir 821 and the seat valves 827.2 upstream of the vacuum pump 833 are closed, and the seat valves 827.3 upstream of the respective ventilation part 848 are opened.

[0075] Preferably, if the reference pressure p_ref is greater than the limit pressure p_limit, the pressure in the closing chamber 375 is less than or equal to atmospheric pressure. The atmospheric pressure can be adjusted via the respective venting part 848.

[0076] To reduce the pressure, the seat valves 827.1 upstream of the compressed air reservoir 821 and the seat valves 827.3 upstream of the ventilation parts 848 are closed, while the seat valves 827.2 upstream of the vacuum pump 833 are opened until the predetermined negative pressure is set as the target pressure. Subsequently, the pressure is controlled by opening and closing the seat valves 827.2 upstream of the vacuum pump 833 to maintain or restore the negative pressure. To increase the pressure, the relevant seat valves 827.1 upstream of the compressed air reservoir 821 are briefly opened. The seat valves 827.3 upstream of the ventilation parts 848 are closed.

[0077] In another procedure, the overpressure in the first internal chamber 369, in the second internal chamber 372 and in the closing chamber 375 is regulated in that the seat valves 827.2 downstream of the compressed air reservoir 821 and / or in the second internal chamber 372 or in the closing chamber 375 the seat valves 827.3 upstream of the ventilation parts 848 are always open, but the volume flow in the throttles 824.2, 824.3 respectively assigned to the seat valves 827.2, 827.3 is smaller than the volume flow through the throttles 824.1 arranged between the compressed air reservoir 821 and the respectively downstream seat valves 827.1. The seat valves 827.2 upstream of the vacuum pump 833 and the seat valves 827.3 upstream of the ventilation components 848 are only closed when no compressed air supply is possible. The throttles 824.2, 824.1, and 824.3 can be controlled for this purpose.

[0078] In yet another approach, the overpressure in the first internal chamber 369, in the second internal chamber 372, and in the closing chamber 375 is regulated by closing the seat valves 827.1, 827.2, 827.3, individually or in combination, as needed, only with a predetermined time delay relative to the other seat valves 827.1, 827.2, 827.3. This occurs when the volume flow through the throttles 824.2 upstream of the vacuum pump 833 or through the throttles 824.3 upstream of the ventilation parts 848 is smaller than the volume flow through the throttles 824.1 upstream of the compressed air reservoir 821.

[0079] If a support pressure is present at the working face 112 or, for example, if a reference pressure p_ref prevails in the head chamber 306 that is lower than a limit pressure p_limit, then the fluid supply arrangement 803 is operated in a vacuum mode. For this purpose, a predetermined target pressure is stored in the control and regulation module 863 for the first internal chamber 369, for the second internal chamber 372, for the closing chamber 375, and for the gear chamber, which, for example, depends on the atmospheric pressure as the reference pressure p_ref. The values ​​for the target pressures are stored in a table as a function of the reference pressure p_ref.

[0080] Also in the negative pressure mode, the reference pressure p_ref is greater than the pressure in the first internal chamber 369, the pressure in the first internal chamber 369 is greater than the pressure in the second internal chamber 372 and the pressure in the second internal chamber 372 is greater than the pressure in the closing chamber 375.

[0081] To improve the sealing effect, a vacuum is applied in the first internal chamber 369, the second internal chamber 372, and the closing chamber 375. To adjust the vacuum in the first internal chamber 369, the second internal chamber 372, and the closing chamber 375, the seat valve 827.2, which is located upstream of the vacuum pump 833 and connected to the first internal chamber 369, the second internal chamber 372, and the closing chamber 375, respectively, is opened, and air is sucked out accordingly by the vacuum pump 833 until the respective target pressure is reached as a vacuum. The seat valves located upstream of the compressed air reservoir 821

[0082] 827.1 and the seat valves 827.3 upstream of the ventilation parts 848 are closed.

[0083] When the respective target pressure is reached, the respective seat valve 827.2 upstream of the vacuum pump 833 is closed, and the pressure is maintained in the first internal chamber 369, in the second internal chamber or in the closing chamber 375.

[0084] If the pressure in the first internal chamber 369, the second internal chamber 372, or the closing chamber 375 rises above the target pressure, the corresponding seat valve 827.2 upstream of the vacuum pump 833 is opened, and the vacuum pump 833 draws air through the corresponding throttle 824.2 until the target pressure is reached again. The respective seat valve 827.1 upstream of the compressed air reservoir 821 and the respective seat valve 827.3 upstream of the ventilation part 848 are closed.

[0085] Once the target pressure is reached again, the respective seat valve upstream of the vacuum pump 833

[0086] 827.2 is closed, and the pressure is maintained in the first internal chamber 369, in the second internal chamber 372, or in the closing chamber 375. If the pressure in the first internal chamber 369, in the second internal chamber 372, or in the closing chamber 375 now falls below the target pressure, the respective seat valve 827.1 upstream of the compressed air reservoir 821 is opened, and compressed air flows into the first internal chamber 369, into the second internal chamber 372, or into the closing chamber 375, until the target pressure in the first internal chamber 369, in the second internal chamber 372, or in the closing chamber 375 is reached again. The respective seat valve 827.2 upstream of the vacuum pump 833 and the respective seat valve 827.3 upstream of the ventilation part 848 are closed.

[0087] Once the target pressure is reached, the respective seat valve 827.1 upstream of the compressed air reservoir 821 is closed, and the pressure in the first internal chamber 369, in the second internal chamber 372 or in the closing chamber 375 is maintained.

[0088] If provided in vacuum mode, the second internal chamber 372 and / or the closing chamber 375 are permanently maintained at atmospheric pressure via the respective ventilation part 848, without the need for regulation. For this purpose, the respective seat valves 827.1 upstream of the compressed air reservoir 821 and the seat valves 827.2 upstream of the vacuum pump 833 are closed, and the seat valve 827.3 upstream of the respective ventilation part 848 is opened. The pressure in the gear chamber is higher than the pressure in the closing chamber 875, if necessary, so that the sealing lip 860 of the closing seal 357 is pressed between the gear chamber and the closing chamber 375 to support the sealing effect.

[0089] In a different procedure in the negative pressure mode, the negative pressure in the first internal chamber 369, in the second internal chamber 372 and in the closing chamber 375 is regulated by the respective seat valves 827.1 upstream of the compressed air reservoir 821 and / or in the second internal chamber 372 or in the closing chamber 375 the respective seat valves 827.3 upstream of the ventilation parts 848 being always open, the respective volume flow in the throttles upstream of the compressed air reservoir 821

[0090] 824.1 or in the throttles 824.3 upstream of the ventilation parts 848, however, is smaller than the respective volume flow through the throttles 824.2 upstream of the vacuum pump 833. The seat valves upstream of the compressed air reservoir 821

[0091] 827.1 and the throttles 827.3 upstream of the ventilation components 848 are only closed when air extraction is not possible. Throttles 824.1, 824.2, and 824.3 are designed for this purpose.

[0092] In yet another procedure in the vacuum mode, the vacuum in the first internal chamber 369, in the second internal chamber 372, and in the closing chamber 375 is regulated by the seat valves 827.1, 827.2, 827.3 being closed individually or in combination only after a predetermined time delay relative to the other seat valves 827.1, 827.2, 827.3. This occurs when the volume flow in the respective throttles 824.1 upstream of the compressed air reservoir 821 or in the respective throttles 824.3 upstream of the ventilation parts 848 is smaller than the volume flow through the respective throttles 824.2 upstream of the vacuum pump 833.

[0093] In yet another procedure in the vacuum mode, the setting of the vacuum in the first internal chamber 369, in the second internal chamber 372 and in the closing chamber 375 is carried out via a control of the vacuum pump 833. For this purpose, the corresponding seat valve 827.2 upstream of the vacuum pump 833 is opened until the target pressure is set, while the respective seat valves 827.1 upstream of the compressed air reservoir 821 and the respective seat valves 827.3 upstream of the ventilation parts 848 are closed. If the pressure in the first internal chamber 369, in the second internal chamber 372 or in the closing chamber 375 increases, the respective seat valve 827.2 upstream of the vacuum pump 833 is opened, and the vacuum pump 833 sucks air until the desired pressure is reached in the first internal chamber 369, in the second internal chamber 372 or in the closing chamber 375.

[0094] Fig. 9 to Fig. 11 show schematic representations of essential components of the sealing arrangement 212 in the first sealing region 215, which have already been explained in detail above, as well as diagrams illustrating the qualitative pressure conditions prevailing in various mining environments. These pressure conditions can be selectively and predeterminably adjusted depending on the respective mining conditions through the interaction explained above, particularly in connection with Fig. 8.

[0095] Fig. 9 shows, in a schematic representation, essential components of the sealing arrangement 212 in the first sealing region 215, as well as a diagram with qualitatively prevailing pressure ratios during a propulsion carried out with pressure support at a relatively high support pressure, wherein in the diagram a distance x from an arbitrary zero point lying in the direction of propulsion on the front side of the head seal 303 is plotted on the abscissa 903 and a pressure p in arbitrary units based on a reference pressure p_ref, for example the atmospheric pressure, on the side lying in the direction of propulsion on the rear side of the end seal 351 is plotted on an ordinate 906. From the representation according to Fig.9 shows that, compared to the pressure prevailing in the head chamber 306, which may also be relatively high, there is a reduced pressure in the first internal chamber 369 due to the considerable reduction already caused by the head gasket 303, which pressure, in the embodiment shown in Fig. 9, has already been reduced in the second internal chamber 372 to the reference pressure p_ref, which also prevails in the connecting line 381. Due to the equally intimate orientation of the head gasket 303 and the internal seals 339, 345, a loss-free feeding of lubricants into the internal chambers 369, 372 is thus created.

[0096] In preferred embodiments, the lubricant fed into the first internal chamber 369 is a fluid grease or an oil, while the lubricant fed into the second internal chamber 372 is a fluid grease or an oil. Fluid grease is understood above to mean a medium that has a consistency according to a corresponding consistency index of the NLGI classes of 000, 00, 0, or 1 according to DIN 51818 with a flowing, weakly flowing, semi-fluid, or very soft flow behavior.

[0097] Furthermore, it can be seen from the illustration according to Fig. 9 in conjunction with the explanations of Fig. 8 that the second internal chamber 372 can also serve as a further pressure reduction stage in addition to the first internal chamber 369 or as a replacement pressure reduction stage in the event of a failure of the sealing effect of the first internal chamber 369.

[0098] Deviating from the pressure ratios shown in Fig. 9, the pressure ratios explained below can also be set in combination with one another, depending on the respective propulsion conditions.

[0099] In a first variation, the pressure in the second internal chamber 372 is lower than the reference pressure p_ref .

[0100] In a second variation, the pressure in the closing chamber 375 is lower than the reference pressure p_ref .

[0101] In a third modification, the pressure in the connecting line 381 is higher than the reference pressure p_ref . Fig. 10 shows a representation corresponding to Fig. 9, wherein in Fig. 10 the pressure conditions are qualitatively shown in the diagram during propulsion without support pressure. From the representation according to Fig. 10, it can be seen that the pressures in the internal chambers 369, 372 up to the closing chamber 375 gradually fall below the reference pressure p_ref by connecting the vacuum line 830 in accordance with the explanations for Fig. 8, whereby here too the closing function of the head seal 303, the internal seals 339, 345 and the closing seal 351 is ensured by their respective orientation.

[0102] Deviating from the pressure conditions shown in Fig. 10, in a modification the pressure in the connecting line 381 is higher than the reference pressure p_ref.

[0103] Fig. 11 shows a representation corresponding to Fig. 9, wherein in Fig. 11 the pressure conditions are qualitatively shown with a relatively low support pressure for pressure-supported propulsion. The representation according to Fig. 11 shows that the pressures in the inner chambers 369, 372 up to the end chamber 375 fall gradually below the reference pressure p_ref by connecting the vacuum line 830 as explained in Fig. 8, starting from a pressure in the head chamber 306 which is higher than the reference pressure p_ref, the pressure in the connecting line 381 is again set higher than the reference pressure p_ref and the closing function of the head seal 303, the inner seals 339, 345 and the end seal 351 is also ensured by their respective orientation.

[0104] Deviating from the pressure conditions shown in Fig. 11, in a modification the pressure in the connecting line 381 corresponds to the reference pressure p_ref.

[0105] The pressure cascades explained with reference to Fig. 9 to Fig. 11 with a gradual return of the support pressure prevailing in the head chamber 306 to the inner chambers 369, 372, free from intermediate pressure increases, ensure reliable lubrication even in the event of leaks.

[0106] The invention is therefore based on a respectively predetermined interaction of absolute pressure values, which, due to a preferred choice of low-viscosity lubricants such as fluid grease or oil, and thus in contrast to the commonly used high-viscosity lubricants such as lubricating grease, can be measured relatively easily and with sufficient accuracy as explained above, and pressure differences which are set up in such a way that, on the one hand, in contrast to a loss lubrication which discharges lubricating grease, a largely loss-free lubrication and, on the other hand, a relatively low load on the sealing arrangement 212, and in particular on the sealing lips 360, is created.

Claims

CLAIMS 1. Tunnel boring machine with a drive shaft (206) which is designed to rotate a cutting wheel (109), with a sealing arrangement (212) which is designed to seal an annular gap (333) formed around the drive shaft (206) between stationary components (309, 336) and rotating components (309, 384), wherein the sealing arrangement (212) has a number of sealing rings (303, 339, 345, 351) and chambering rings (330, 342, 348) arranged between the sealing rings (303, 339, 345, 351), with a fluid supply arrangement (803) which is designed to supply lubricants to the sealing arrangement (212), and with a number of sealing rings (303, 339, 345, 351) formed receiving chambers, which comprise a first inner chamber (369) located at the front in a propulsion direction and a second inner chamber (372) located at the rear of the first inner chamber (369) in a propulsion direction,which can be supplied with lubricants, characterized in that the fluid supply arrangement (803) is designed to adjust the pressure in the first inner chamber (369) such that the pressure in the first inner chamber (369) is lower than the pressure in a sealing ring which is arranged in the direction of advance in front of the first inner chamber (369) sealing against a mining area (112), (303) and higher than the pressure prevailing in the second inner chamber (372).

2. Tunnel boring machine according to claim 1, characterized in that the fluid supply arrangement (803) is designed to adjust the pressure in the second internal chamber (372) such that this pressure lies between the pressure in the first internal chamber (369) and the pressure in a closing chamber (375) located to the rear of the second internal chamber (372) in the direction of advance.

3. Tunnel boring machine according to claim 1 or claim 2, characterized in that the first internal chamber (369) can be subjected to an overpressure or a negative pressure compared to the atmospheric pressure.

4. Tunnel boring machine according to claim 3, characterized in that the second internal chamber (372) can be selectively pressurized with atmospheric pressure or with an overpressure compared to atmospheric pressure or with a negative pressure compared to atmospheric pressure.

5. Tunnel boring machine according to claim 3 or claim 4, characterized in that for applying a vacuum, a vacuum line (830) and a vacuum pump (833) are provided, which are in fluid communication with the respective internal chamber (369, 372).

6. Tunnel boring machine according to one of the claims 3 to 5, characterized in that a compressed air reservoir (821) is provided for applying an overpressure, which is in fluid communication with the respective internal chamber (369, 372).

7. Tunnel boring machine according to one of the claims 4 to 6, characterized in that a ventilation part (848) is provided for applying atmospheric pressure, which is in fluid communication with the second internal chamber (372).

8. Tunnel boring machine according to one of claims 1 to 7, characterized in that a closing chamber (375) is provided which is arranged to the rear of the last internal chamber (372) in the direction of advance and which can be pressurized optionally with atmospheric pressure or with an overpressure compared to atmospheric pressure or with a negative pressure compared to atmospheric pressure.

9. Tunnel boring machine according to claim 8, characterized in that for applying a vacuum, a vacuum line (830) and a vacuum pump (833) are provided, which are in fluid communication with the closure chamber (375).

10. Tunnel boring machine according to claim 8 or claim 9, characterized in that for applying an overpressure a compressed air reservoir (821) is provided, which is connected to the closing chamber (375) is in fluid communication.

11. Tunnel boring machine according to one of claims 8 to 10, characterized in that a ventilation part (848) is provided for applying atmospheric pressure, which is in fluid communication with the closure chamber (375).

12. Tunnel boring machine according to one of claims 8 to 11, characterized in that a connecting line (381) is provided which is arranged in the direction of advance to the rear of the closure chamber (375) and can be pressurized optionally with atmospheric pressure or with an overpressure compared to the atmospheric pressure.

13. Tunnel boring machine according to one of claims 1 to 12, characterized in that the fluid supply arrangement (803) is designed to deliver a fluid grease or oil as a lubricant into the first internal chamber (369) and a fluid grease or oil into the second internal chamber (372).

14. Tunnel boring machine according to one of claims 1 to 13, characterized in that the fluid supply arrangement (803) is designed to convey a fluid grease or oil as a lubricant into the closing chamber (375).

15. Tunnel boring machine according to one of claims 1 to 14, characterized in that Chambering rings (330, 342) arranged in the inner chambers (369, 372) are formed with an annular groove (363) and with passage recesses (366) located in the apex region with respect to gravity.

16. Tunnel boring machine according to claim 15, characterized in that flow brakes (403, 406; 706) are arranged on both sides of an apex region of internal chambers (369, 372).

17. Tunnel boring machine according to one of claims 1 to 16, characterized in that the drive shaft (206) is designed as a hollow shaft and that the sealing arrangement (212) has a first sealing region (215) arranged radially on the outside and a second sealing region (218) arranged radially on the inside.

18. Method for driving a tunnel comprising the steps - Providing a tunnel boring machine according to one of claims 1 to 17 and - Adjusting the pressure in the first internal chamber (369) such that the pressure in the first internal chamber (369) is lower than the pressure in a sealing ring (303) sealing the first internal chamber (369) against a mining area (112) in the direction of advance and higher than the pressure prevailing in the second internal chamber (372).

19. Method according to claim 18, comprising the step - Adjusting the pressure in the second internal chamber (372) such that the pressure in the second internal chamber (372) is different from a reference pressure (p_ref).

20. Method according to claim 19, comprising the step - Setting the reference pressure (p_ref) such that the reference pressure (p_ref) is different from an atmospheric pressure.

21. Method according to claim 18 to 20, insofar as a tunnel boring machine according to claim 8 to 12 or according to claim 14 is provided, comprising the step - Adjusting the pressure in the closing chamber (375) such that the pressure in the closing chamber (375) is lower than the pressure in the second inner chamber (372).

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