EP0308597B1 - Rotary sliding gate for a metallugical vessel just as rotor and or stator for such a rotary gate - Google Patents

Abstract

The invention relates to a rotary sliding gate for tapping liquid molten metal out of a metallurgical vessel, with a rotationally symmetrical rotor which serves as gate element, is, for example, refractory, is arranged in a manner which allows rotation about an axis of rotation in a stator (6), for example a refractory stator, having an outflow channel, and has at least one flow channel which can be opened by rotating the rotor relative to the stator to connect the inlet opening of the outflow channel of the stator to the outlet opening of the outflow channel of the stator and can be closed again by interrupting this connection. To improve and increase the possible functions of such a rotary sliding gate, the stator has an aperture with a circular-cylindrical inner surface which serves as a sealing seat, into which the rotor is fitted in sealing fashion with a circular-cylindrical circumferential surface and within which the rotor can be both rotated and axially displaced. In the inner surface of the aperture there is at least one inlet opening and/or at least one outlet opening of a flow channel. <IMAGE>

Description

The invention relates to a rotary slide closure for tapping liquid molten metal from a metallurgical vessel with a rotationally symmetrical, serving as a closure body refractory rotor, which is arranged rotatably about an axis of rotation in a stator having an outflow channel and at least one while rotating the rotor relative to the stator Connection of the inlet opening of the outflow channel of the stator with the outlet opening of the outflow channel of the stator with the outlet opening of the outflow channel of the stator to be opened and to be closed again by interrupting this connection.

A pure twist lock is known, for example, from DE-PS 33 06 670. In this case, a tubular plug is provided as the rotor, which has a radial connection opening in a conical extension. The conical shoulder is fitted in a correspondingly conical blind hole of a fitting fixedly arranged in the vessel lining with a removal opening. To achieve the required tightness, a high surface pressure between the conical approach of the rotary plug and the exclusively conical sealing seat of the fitting is required, which must be applied by an axial spring pressure. Opening and closing is done by turning the plug in relation to the fitting.

Proceeding from this, it is an object of the present invention to provide a rotary closure of the type mentioned at the outset with a more reliable and versatile function without the sealing surfaces sliding on one another being braced against one another by means of pressure elements for the functionality and the required tightness.

This object is essentially achieved in that the stator has a recess with a circular cylindrical inner surface serving as a sealing seat, into which the rotor is fitted with a circular cylindrical outer surface and within which the rotor is both rotatable and axially displaceable.

Here are either at least the inlet opening of the outflow channel of the stator in the circular cylindrical inner surface of its recess and the inlet opening of the throughflow channel of the rotor in its circular cylindrical lateral surface or at least the outlet opening of the outflow channel of the stator in the circular cylindrical inner surface of its recess and the outlet opening of the throughflow channel of the rotor in the circular cylindrical surface. No contact pressure is required for the required tightness of the screw cap. In addition, the twist lock can be opened and closed both by rotating the rotor relative to the stator and by axially displacing the rotor in the stator. For example, the pouring jet can be throttled by rotating the rotor relative to the stator and completely opening and closing the rotary slide closure by axially displacing the rotor relative to the stator. This has the advantage that in the two functions different closing surface areas of the rotor in the vicinity of the flow channel are acted upon by the outer surface, whereby the service life of the rotor as a control and closing element is considerably increased compared to the known solution.

In the simplest case, at least the inlet or the outlet openings of the stator and rotor are arranged in the circular cylindrical inner surface of the stator or the circular cylindrical outer surface of the rotor.

To achieve the advantageous object, both the inlet opening of the outflow channel of the stator in the circular cylindrical inner surface of the recess and the inlet opening of the flow channel of the rotor in the circular cylindrical outer surface of the rotor, as well as the outlet opening of the flow channel of the rotor in the circular cylindrical outer surface of the rotor and the outlet opening of the outflow channel of the stator lie in the circular cylindrical inner surface of the recess.

In particular, if an at least partially horizontal tapping is to be achieved, the inlet opening of the outflow channel of the stator and the inlet opening of the throughflow channel of the rotor preferably lie in an end face of the stator or of the rotor that is substantially perpendicular to the axis of rotation or the outlet opening of the outflow channel of the stator and the outlet opening of the flow channel of the rotor each in an end face of the stator or of the rotor which is substantially perpendicular to the axis of rotation of the rotor.

An inlet-side and outlet-side closing and opening of the flow channel of the rotor is achieved when the outflow channel of the stator and the flow channel of the rotor as a whole run essentially perpendicular to the axis of rotation. In this case, the rotor and stator are very simple shaped bodies.

If both the outflow duct of the stator and the throughflow duct of the rotor run parallel to the axis of rotation of the rotor over a substantial part of their length, the stator and rotor are in any case in this part of their length essentially tubular with a relatively thin wall thickness, which is at the beginning of the casting process Relatively quick heating of the rotary slide closure to the desired operating temperature guaranteed.

In this case, preferably both the outflow channel of the stator and the flow channel of the rotor - viewed in the flow direction - initially run essentially in the direction of the axis of rotation of the rotor and then essentially perpendicular to the axis of rotation, or vice versa.

The risk of the rotary slide closure freezing is then substantially reduced if the stator and rotor — with the vessel filled — are arranged wholly or at least partially in the molten metal.

However, it is also possible to arrange the stator and rotor on the outside of the vessel wall.

It has proven to be particularly advantageous if the stator and rotor lie at least partially within the vessel wall and, in yet another embodiment of the inventive concept, the stator forms part or all of the refractory vessel bottom lining and / or the vessel wall lining. This saves a part of the vessel wall lining and the twist lock is housed in a thermally favorable position to save space.

If the stator is arranged in the transition area between the vessel bottom lining and the vessel wall lining, the rotary lock for actuating the rotor is easily accessible even in this case, in which the stator and rotor are arranged in the direct area of action of the metal melt present in the vessel.

The rotor can be driven through the vessel wall and the vessel wall lining.

If the axis of rotation of the rotor is vertical, for example, it can preferably be driven from below through the bottom of the vessel and the bottom of the vessel or from above through the molten metal.

It is also particularly advantageous if the rotor can be actuated by two different drives for rotation and axial displacement. If, for example, the pouring jet is to be controlled by rotation, this requires a relatively precise actuation, which, however, does not need to take place particularly quickly. On the other hand, a relatively rapid movement is required for opening and closing the rotary slide closure by axially displacing the rotor in the recess of the stator, which movement can be limited by stops in the open and closed positions.

In the rotary slide closure according to the invention, it is also possible for the stator or the rotor or a part or an extension thereof to be designed as a pour protection tube.

In order to ensure that the forces for rotating and / or axially displacing the rotor in the stator recess, also taking into account any different thermal expansion coefficients of the rotor and stator, it is advantageous to use a fireproof sliding sleeve to guide the stator or rotor Equip rotor or stator. This causes the rotor to float in the stator.

With regard to the choice of materials, the invention proposes that the thermal expansion coefficient of the rotor and ggs. whose sliding sleeve is equal to or less than the thermal expansion coefficient of the stator and, if necessary, its sliding sleeve. This can jam the rotor relative to the Stator can be reliably avoided during casting under operating temperatures.

The stator and rotor can preferably consist of materials of different hardness, in particular ceramic materials.

The rotor and / or stator and / or their sliding sleeve preferably consist of oxide ceramic.

In order to improve the sliding ability of the rotor relative to the stator, the refractory material of the rotor and / or of the stator and / or of the sliding sleeve contains carbon, graphite or the like, at least in the surface areas facing one another.

In particular, the invention also provides that the refractory material of the rotor and / or the stator and / or the sliding sleeve contains ceramic fibers or ceramic fibers and fibers made of carbon or graphite.

The invention further relates to a rotor and a stator, in particular for a twist lock of the type according to the invention.

The rotor is characterized in that it has a circular cylindrical outer surface which corresponds to a circular cylindrical inner surface serving as a seat of a recess in a refractory stator and in which at least one inlet opening and / or at least one outlet opening of a flow channel lie / lie.

On the other hand, the stator according to the invention is characterized in that it has a recess with a circular cylindrical inner surface serving as a seat, which has a circular cylindrical Corresponds to the lateral surface of a refractory rotor and in which at least one inlet opening and / or at least one outlet opening of an outlet channel lie / lies.

In a particularly simple embodiment, the inlet opening or outlet opening of the flow channel of the rotor lie in the circular-cylindrical outer surface, but one or the other opening can also lie in an end surface which is essentially perpendicular to the axis of rotation.

Correspondingly, the inlet opening and outlet opening of the outflow channel of the stator preferably lie in the circular cylindrical inner surface of the recess, while the two openings can optionally also lie in an end surface which is substantially perpendicular to the longitudinal axis of the recess.

The simplest design of the rotor or stator is obtained when the flow channel is essentially perpendicular to the axis of rotation of the rotor or the outflow channel is essentially perpendicular to the longitudinal axis of the recess in the stator.

If the spatial conditions require it, it can also be provided that the flow channel of the rotor - viewed in the flow direction - initially runs essentially in the direction of the axis of rotation and then essentially perpendicular to the axis of rotation or vice versa, while correspondingly the flow channel of the stator - in the direction of flow first seen essentially in the direction of the longitudinal axis of the recess and then essentially perpendicular to the longitudinal axis or vice versa, the axis of rotation of the rotor coinciding with the longitudinal axis of the stator.

The stator can be designed so that part or an extension of it serves as a pouring protection tube.

The rotor or stator are preferably made of oxide ceramic.

The stator or rotor can also have a plurality of inlet or outlet openings in order to increase the service life of these parts. If the openings are of different sizes, e.g. an opening with a large cross-section can be opened by pouring, e.g. to fill a tundish quickly, while in the casting operation the regulation of the casting speed by turning and / or moving openings with a smaller cross-section can be carried out relatively precisely.

Other goals, characteristics. Advantages and possible uses of the present invention result from the following description of exemplary embodiments with reference to the drawing. All of the described and / or illustrated features, alone or in any meaningful combination, form the subject matter of the present invention, regardless of how they are summarized in the claims or their relationship.

1 to 8 each schematically illustrate in vertical section a metallurgical vessel with a rotary slide closure of the invention having various designs, the rotary axis of the rotor running horizontally according to FIGS. 1 to 3 and vertically according to FIGS. 4 to 8. 1 and 3, the rotary closure is on the outside of the vessel wall, the liquid metal melt being fed to the rotary slide closure via an inlet stone in the vessel bottom lining, during the execution 2, the twist lock is integrated in the vessel wall lining and is arranged in the transition area from the vessel bottom to the vessel wall. In the embodiment according to FIGS. 4 to 8, the rotary slide closure also takes up part of the vessel wall lining, but it stands vertically in the central region of the vessel bottom.

The rotary slide closure 1 for tapping liquid melt from a metallurgical vessel 2 has a rotationally symmetrical, refractory rotor 3 serving as a closure body. The rotor 3 is rotatable about a horizontal axis of rotation A in this case in a stator 5 having a recess 4. The rotor 3 has at least one flow channel 8 to be opened with rotation D of the rotor 3 relative to the stator 5 by connecting the inlet opening 6 of the outlet channel 4 of the stator 5 to the outlet opening 7 of the outlet channel 4 of the stator 5 and to be closed again by interrupting this connection . The stator 5 has a recess 9 with a circular cylindrical inner surface 10 serving as a seat, into which the rotor 4 with its circular cylindrical outer surface 11 is fitted in a sealing manner. The rotor 3 is both rotatable and axially displaceable within the recess 9. The inlet opening 6 of the outflow channel 4 of the stator 5 lies in the circular cylindrical inner surface 10 of the recess 9 and the inlet opening 12 of the throughflow channel 8 of the stator 3 in the circular cylindrical outer surface 11 of the rotor 3. Furthermore, the outlet opening 13 of the throughflow channel 8 of the rotor 3 lies in the Circular cylindrical outer surface 11 of the rotor 3 and the outlet opening 7 of the outflow channel 4 of the stator 5 in the circular cylindrical inner surface 10 of the recess 9. The stator 5 and rotor 3 are arranged overall on the outside of the vessel wall, namely on the vessel bottom 18. An inlet stone 20, which in the vessel bottom lining 14th is arranged, has a conical flow opening 21, which opens into the inlet opening 6 of the outflow channel 4 of the stator 5. Both the outflow channel 4 of the stator 5 and the flow channel 8 of the rotor 3 run essentially perpendicularly to the axis of rotation A, that is to say vertically in this case. As indicated by double arrows, the rotor can not only be subjected to a rotation D about the axis of rotation A, but also an axial longitudinal displacement V. For this purpose, two different drives can be used, for example by controlling the pouring jet by rotating the rotor 3 and by axially displacing it Opening and closing the twist lock 1 is accomplished. In this embodiment, the rotor 3 is guided in the recess 9 of the stator 5 by means of a refractory sliding sleeve 17.

In the embodiment of FIG. 2, in which the stator 5 and the rotor 3 are partially arranged in the interior of the vessel intended for the molten metal and partially inside the vessel wall, the stator 5 and the rotor 3 at least partially form part of the refractory vessel bottom lining 14 and the vessel wall lining 15. The inlet opening 6 of the outflow channel 4 of the stator 5 and the inlet opening 12 of the throughflow channel 8 of the rotor 3 each lie in an end face of the stator 5 or of the rotor 3 which is essentially perpendicular to the axis of rotation A, so that the metal melt initially in the substantially horizontally to the axis of rotation A and then vertically, perpendicular to the axis of rotation A out of the interior of the vessel. The rotor 3 can be driven from the side through the vessel wall 19 and the vessel wall lining 15. The stator 5 has an extension which is designed as an immersion nozzle with a nozzle tube 16.

3 is similar to the one according to FIG. 1 on the outside of the vessel bottom 18. In contrast to the embodiment according to FIG. 1, however, the outflow channel 4 of the stator 5 and the flow channel 8 of the rotor 3 initially run essentially vertically, vertically to the axis of rotation A and then essentially horizontally, parallel to the axis of rotation A. In this way, the pouring jet is first led vertically and then horizontally out of the interior of the vessel. The rotor 3 is preferably actuated at the end opposite the outlet opening 13 of the flow channel 8. Just as in the embodiment according to FIG. 2, rotor 3 and stator 5 are thus fitted into one another with tubular sections over at least part of their length. The outlet opening 7 of the outlet channel 4 of the stator 5 and the outlet opening 13 of the outlet channel 8 of the rotor 3 each lie in an end face of the stator 5 and the rotor 3 that is substantially perpendicular to the axis of rotation A of the rotor 3.

In the exemplary embodiment according to FIG. 4, the axis of rotation A of the rotor 3 is vertical, that is to say perpendicular to the bottom of the vessel 18. The rotor 3 is both rotated and axially displaced with respect to the vertically standing sleeve-shaped stator 5 by means of a fireproof-coated actuating rod 22. Stator 5 and rotor 3 are also partially in the interior of the vessel, which is taken up by the molten metal, and partially form part of the vessel bottom lining 14. Both the outflow channel 4 of the stator 5 and the flow channel 8 of the rotor 3 initially run horizontally and then vertically , because the inlet opening 6 of the outflow channel 4 in the circular cylindrical inner surface 10 of the recess 9, the inlet opening 12 of the throughflow channel 8 in the circular cylindrical outer surface 11 of the rotor 3, the outlet opening 13 of the throughflow channel 8 in the downwardly facing end face of the rotor 3 and the Outlet opening 7 of the outflow channel 4 lie in the downward-facing end face of the stator 5.

2, the inlet opening 6 of the outflow channel 4 of the stator 5 lies somewhat above the inner surface of the vessel bottom lining 14, so that undesired residues of slag are retained in the interior of the vessel.

5 differs from that shown in FIG. 4 essentially in that the rotor 3, like the stator 5, is designed as a continuous tube and is actuated from above the bath level. The tubular end of the tubular stator 5 is incorporated into the vessel bottom lining 14.

In the exemplary embodiment according to FIG. 6, the stator 5 is a tube which is closed at the top and which is received with its lower end in the vessel bottom lining 14. The rotor 3 protrudes downward through the vessel bottom lining 14 and the vessel bottom 18 in the form of a pour protection tube 16 and can be actuated from below. Rotor 3 and stator 5 each have two diametrically opposite inlet openings 6 and 12. Guide strips 23 made of slidable material can be accommodated between rotor 3 and stator 5. To reduce the frictional resistance between the rotor 3 and the stator 5, the inner cross section of the stator 5 in the lower region is slightly larger than the outer cross section of the rotor 3 in this region, so that the rotor 3 is guided in the stator 5 only over the upper part of its length.

7 is similar to that of FIG. 6. However, in addition to two diametrically opposed small inlet openings 6, the stator has another inlet opening 6 'of larger cross section lying further down, which can be opened completely if the rotor 3 is pulled down far enough.

It is similar in the embodiment of Fig. 8, in which the larger inlet opening 6 'of the stator 5 can be completely released if the rotor 3 is pulled far enough upwards.

Reference symbol list:

1

Rotary slide lock

2nd

vessel

3rd

rotor

4th

Outflow channel of the stator

5

stator

6, 6 ′

Inlet opening of the outflow channel

7

Outlet opening of the outflow channel

8th

Flow channel of the rotor

9

Recess

10th

Inner surface of the stator

11

Lateral surface of the rotor

12

Inlet opening of the flow channel

13

Outlet opening of the flow channel

14

Vessel bottom lining

15

Vascular wall lining

16

Pour protection tube

17th

Sliding sleeve

18th

Vessel bottom

19th

Vessel wall

20th

Inlet stone

21

Flow opening

22

Actuating rods

23

Guide rails

A

Axis of rotation

D

rotation

V

shift

Claims (36)

1. Rotary sliding gate valve for tapping liquid metal melt from a metallurgical vessel (2) with a rotationally symmetrical e.g. refractory rotor (3) which serves as a valve body and which is arranged to be rotatable about a rotary axis (A) in an e.g. refractory stator (5) having an outlet passage (4) and has at least one flow passage (8) which may be opened by rotation (D) of the rotor (3) with respect to the stator (5) to connect the inlet opening (6) of the outlet passage (4) of the stator (5) with the outlet opening (7) of the outlet passage (4) of the stator (5) and which may be closed again by interrupting this connection, characterised in that the stator (5) has a recess (9) with a circular cylindrical inner surface (10) serving as a sealing seat in which the rotor (4) with a circular cylindrical outer surface (11) is sealingly fitted and within which the rotor is not only rotatable but also axially slidable.
2. Rotary sliding gate valve as claimed in Claim 1, characterised in that at least the inlet or the outlet openings (6, 12; 7, 13) of the stator (5) and rotor (3) are disposed in the circular cylindrical inner surface (10) of the stator (5) or the circular cylindrical outer surface (11) of the rotor (3), respectively.
3. Rotary sliding gate valve as claimed in one of Claims 1 or 2, characterised in that not only is the inlet opening (6) of the outlet passage (4) in the stator (5) in the circular cylindrical inner surface (10) of the recess (9) and the inlet opening (12) of the flow passage (8) in the rotor (3) in the circular cylindrical outer surface (11) of the rotor (3) but also the outlet opening (13) of the flow passage (8) in the rotor (3) is in the circular cylindrical outer surface (11) of the rotor (3) and the outlet opening (7) of the outlet passage (4) in the stator (5) is in the circular cylindrical inner surface (10) of the recess (9) (Fig. 1).
4. Rotary sliding gate valve as claimed in one of Claims 1 or 2, characterised in that the inlet opening (6) of the outlet passage (4) in the stator (5) and the inlet opening (12) of the flow passage (8) in the rotor (3) are in a respective end surface of the stator (5) and of the rotor (3) extending perpendicular to the rotary axis (A) (Fig. 2).
5. Rotary sliding gate valve as claimed in one of Claims 1 or 2, characterised in that the inlet opening (7) of the outlet passage (4) in the stator (5) and the outlet opening (13) of the flow passage (8) in the rotor (3) are in a respective end surface of the stator (5) and the rotor (3) extending perpendicular to the rotary axis (A) of the rotor (3) (Figs. 3 to 8).
6. Rotary sliding gate valve as claimed in one of Claims 1 to 5, characterised in that not only the outlet passage (4) in the stator (5) but also the flow passage (8) in the rotor (3) extend overall substantially perpendicular to the rotary axis (A) (Fig. 1).
7. Rotary sliding gate valve as claimed in one of Claims 1 to 6, characterised in that not only the outlet passage (4) in the stator (5) but also the flow passage (8) in the rotor (3) extend parallel to the rotary axis (A) of the rotor (3) over a substantial proportion of their length (Figs. 2 to 4 to 8).
8. Rotary sliding gate valve as claimed in one of Claims 1 to 7, characterised in that not only the outlet passage (6) in the stator (5) but also the flow passage (8) in the rotor (3) extend initially substantially in the direction of the rotary axis (A) of the rotor (3) and then substantially perpendicular to the rotary axis (A) or vice versa - seen in the flow direction (Figs. 2 to 8).
9. Rotary sliding gate valve as claimed in Claim 1 to 8, characterised in that the stator (5) and rotor (3) are arranged wholly or at least partially in the metal melt when the vessel (2) is full (Figs. 2 and 4 to 8).
10. Rotary sliding gate valve as claimed in Claim 1 to 8, characterised in that the stator (5) and rotor (3) are arranged externally on the vessel wall (18, 19) (Figs. 1 and 3).
11. Rotary sliding gate valve as claimed in one of Claims 1 to 9, characterised in that the stator (5) and rotor (3) are arranged at least partially within the vessel wall (18, 19) (Figs. 2 and 4 to 8).
12. Rotary sliding gate valve as claimed in Claim 11, characterised in that the stator (5) and the rotor (3) constitute in whole or in part a component of the refractory vessel floor lining (14) and/or of the vessel wall lining (15) (Figs. 2 and 4 to 8).
13. Rotary sliding gate valve as claimed in Claim 12, characterised in that the stator (5) is arranged in the transition region between the vessel floor lining (14) and vessel wall lining (15) (Fig. 2).
14. Rotary sliding gate valve as claimed in one of Claims 1 to 13, characterised in that the rotor (3) may be driven through the vessel wall (19) and the vessel wall lining (15) (Fig. 2).
15. Rotary sliding gate valve as claimed in one of Claims 1 to 13, characterised in that the rotor (3) may be driven from below through the vessel floor (18) and the vessel floor lining (14) or from above, optionally through the metal melt (Figs. 4 to 8).
16. Rotary sliding gate valve as claimed in one of Claims 1 to 15, characterised in that the rotor (3) is actuable by two different drives for rotation and axial sliding.
17. Rotary sliding gate valve as claimed in one of Claims 1 to 16, characterised in that the stator (5) or the rotor (3) or a part or an extension of the same is constructed as a pouring protection tube (16) (Figs. 2, 6 and 7).
18. Stator or rotor for a rotary sliding gate valve as claimed in one of Claims 1 to 17, characterised by a refractory sliding sleeve (17) for guiding of the rotor (3) or in the stator (5).
19. Stator or rotor for a rotary sliding gate valve (1) as claimed in one of Claims 1 to 17 or as claimed in Claim 18, characterised in that the coefficient of thermal expansion of the rotor (3) and optionally its sliding sleeve (17) is the same as or smaller than the coefficient of thermal expansion of the stator (5) and optionally its sliding sleeve (17).
20. Stator or rotor for a rotary sliding gate valve (1) as claimed in one of Claims 1 to 17 or as claimed in Claim 18 or 19, characterised in that the stator (5) and rotor (3) comprise particularly ceramic materials of differing hardness.
21. Stator or rotor for a rotary sliding gate valve (1) as claimed in one of Claims 1 to 17 or as claimed in one of Claims 18 to 20, characterised in that the stator (5) and/or rotor (3) and/or their sliding sleeve (17) comprise oxide ceramic material.
22. Stator or rotor for a rotary sliding gate valve (1) as claimed in one of Claims 1 to 17 or as claimed in one of Claims 18 to 21, characterised in that the refractory material of the rotor (3) and/or of the stator (5) and/or of the sliding sleeve (17) contains carbon, graphite or the like permanent lubricant, at least in the surface regions directed towards one another.
23. Stator or rotor for a rotary sliding gate valve (1) as claimed in one of Claims 1 to 17 or as claimed in one of Claims 18 to 22, characterised in that the refractory material of the rotor (3) and/or of the stator (5) and/or of the sliding sleeve (17) contain ceramic fibres or ceramic fibres and fibres of carbon or graphite.
24. Rotor for a rotary sliding gate valve (1) as claimed in one of Claims 1 to 17 or as claimed in one of Claims 18 to 23, characterised in that it has a circular cylindrical outer surface (11) which corresponds to a circular cylindrical inner surface (10), which serves as a seat, of a recess (9) in the stator (5) and in which at least one inlet opening (12) and/or at least one outlet opening (13) of a flow passage (8) is/are situated.
25. Stator for a rotary sliding gate valve (1) as claimed in one of Claims 1 to 17 or as claimed in one of Claims 18 to 23, characterised in that it has a recess (9) with a circular cylindrical inner surface (10) which serves as a seat and which corresponds to a circular cylindrical outer surface (11) of a refractory rotor (3) and in which at least one inlet opening (6) and/or at least one outlet opening (7) of an outlet passage (4) is/are situated.
26. Rotor as claimed in Claim 24, characterised in that the inlet opening (12) and outlet opening (13) of the flow passage (8) are situated in the circular cylindrical outer surface (11).
27. Rotor as claimed in Claim 24, characterised in that the inlet opening (12) or the outlet opening (13) of the flow passage (8) is situated in an end surface extending substantially perpendicular to the rotary axis (A).
28. Stator as claimed in Claim 25, characterised in that the inlet opening (6) and outlet opening (7) of the outlet passage (4) are situated in the circular cylindrical inner surface (10) of the recess (9).
29. Stator as claimed in Claim 25, characterised in that the inlet opening (6) or the outlet opening (7) of the outlet passage (4) is situated in an end surface extending substantially perpendicular to the longitudinal axis of the recess (9).
30. Rotor as claimed in one of Claims 24, 26 or 27, characterised in that the flow passage (8) extends substantially perpendicular to the rotary axis (A).
31. Stator as claimed in one of Claims 25, 28 or 29, characterised in that the outlet passage (4) extends substantially perpendicular to the longitudinal axis of the recess (9).
32. Rotor as claimed in one of Claims 24, 26 or 27, characterised in that the flow passage (8) extends initially substantially in the direction of the rotary axis (A) and then substantially perpendicular to the rotary axis or vice versa - seen in the flow direction.
33. Stator as claimed in one of Claims 25, 28 or 29, characterised in that the outlet passage (4) extends initially substantially in the direction of the longitudinal axis of the recess (9) and then substantially perpendicular to the longitudinal axis or vice versa - seen in the flow direction.
34. Stator or rotor for a rotary sliding gate valve as claimed in one of Claims 1 to 17 or as claimed in one of Claims 18 to 33, characterised in that a portion or an extension of it is constructed as a pouring protection tube (16).
35. Stator or rotor for a rotary sliding gate valve (1) as claimed in one of Claims 1 to 17 or as claimed in one of Claims 18 to 34, characterised in that the stator (5) and/or rotor (3) has a plurality of inlet or outlet openings (6, 6', 12; 7, 13) (Figs. 6 to 8).
36. Stator or rotor as claimed in Claim 35, characterised in that the plurality of inlet openings (6, 6', 12) or plurality of outlet openings (7, 13) have cross-sections whose sizes differ from one another.

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