CA1090567A - Drilling machine for blast furnace tapholes - Google Patents
Drilling machine for blast furnace tapholesInfo
- Publication number
- CA1090567A CA1090567A CA272,134A CA272134A CA1090567A CA 1090567 A CA1090567 A CA 1090567A CA 272134 A CA272134 A CA 272134A CA 1090567 A CA1090567 A CA 1090567A
- Authority
- CA
- Canada
- Prior art keywords
- drilling machine
- tool holder
- bar
- support arm
- taphole
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Classifications
-
- C—CHEMISTRY; METALLURGY
- C21—METALLURGY OF IRON
- C21B—MANUFACTURE OF IRON OR STEEL
- C21B7/00—Blast furnaces
- C21B7/12—Opening or sealing the tap holes
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Manufacturing & Machinery (AREA)
- Materials Engineering (AREA)
- Metallurgy (AREA)
- Organic Chemistry (AREA)
- Earth Drilling (AREA)
- Blast Furnaces (AREA)
- Furnace Charging Or Discharging (AREA)
Abstract
Abstract of the Disclosure The invention provides a machine for drilling tap holes for shaft furnaces, particularly of blast furnaces, wherein the machine can be moved to the working position and withdrawn therefrom in one single movement, in contrast to the two independent movements of prior art mechanisms. The apparatus therefore requires only a single driving mechanism, instead of two independent driving mechanisms. The apparatus consists of an inclined support column on which a bar carrying a drilling mechanism is mounted by means of a radial arm extend-ing from the support column. The support column is inclined at an angle to the vertical in dependence upon the space available around the furnace for movement of the radial arm and bar from a working position to a retracted position and vice versa. The bar is mounted on the arm for rotation in the vertical plane to vary the angle of inclination of the tap hole. The hydraulic driving device for moving the machine between its two positions comprises means for limiting the amplitude to which it can be extended, and for insuring that the extreme extended position which is thereby selected corresponds to the operating position of the tool holder bar in order to avoid inaccuracies in drilling. Means for maintaining the pressure of the hydraulic fluid during the operation of the drilling machine may consist of rigid jointed piping, or alternatively a flexible conduit which is mounted on a wind-up reel.
Description
~gori~i7 The present invention relates to a machine for drilling tapholes of shaft furnaces, particularly of blast furnaces.
It is known that present progress in the design of blast furnaces provides for increasingly large units and for the adoption of increasingly high pressures in the furnace throat.
One ~f the consequences of this tendency is the use of increa-singly hard materials for sealing tapholes, while production requirements and the increasing length of these tapholes require high speed drilling means. It is therefore advisable to have robust and simple drilling machines available which will enable high stresses to be applied and transmitted, particularly the pressures required for the drilling tools.
The increase in the number of tapholes and other items of equipment required for the satisfactory operation and maintenance of blast furnaces, such as the working platforms, reduces the space available around the furnace, and this has to be taken into account when designing the machine, in order to avold movements necessitating a great deal of free space.
The problems facing the designers of these machines are rendered still more complicated by the limitations of a purely geometrical nature, particularly the necessity of enabling the drilling tool or tools to be withdrawn without having to touch the tap spout.
In the known drilling machines in general use the operation of positioning the bar on whichthe drilling tool slides usually involves the displacement of the said bar in an approximately horizontal plane, until it is above the tap spout, followed by a vertical displacement, e.g. by a pivoting movement, in order to lower the bar into the operating position, in which it is then locked mechanically. The withdrawal of the bar to an inoperative position obviously entails the same . . , . ~
1090~ j~7 movements in the reverse order. These compound movements are required by reason of the fact that the nose of the bar bearing the drilling tool must necessarily be lowered fairly down into the tap spout and that impact against the edges of the latter must be avoided at all costs, both when the drilling tool is being positioned for operation and when it is being withdrawn.
The mechanisms for the displacement of the bar, which are already complicated in themselves, to enable these movements to be effected, are rendered still more so by the auxiliary mechanisms for the stepless adjustment of the angle of appli-cation of the bar and also for the selection of its horizontal and vertical positions. All these regulating and displacement mechanisms are generally provided at the sacrifice of the rigidity of the machine as a whole, a drawback incompatible with present-day needs.
Furthermore, the means for displacing the bar and also those for actuating the working tool generally consist of hydraulic or pneumatic motors, for which purpose a set of flexible tubes is provided in order to convey the driving fluid between the various moving elements and components. These flexible tubes, generally made of rubber, not only prove cumbersome and inconvenient but are also a constant potential source of accidents, as they are suspended above the tap spout during operation and thus occupy a position subject to a very high temperature.
An object of the present invention is to provide a machine for the drilling of tapholes which will enable the aforementioned drawbacks to be considerably reduced, or elimi-nated, and in particular, to provide a drilling machine which can accurately be moved into the working position by simple movements and which can thus be constructed on simple lines 1090S~7 and with the required degree of rigidity and without excessive height and which will enable the withdrawal position for the drilling tool bar and also the traject of the movement by which it is conveyed into the said position to be selected as desired and in accordance with the space available around the furnace.
In accordance with the present invention there is provided for use with a shaft furnace having a taphole and a molten metal flow channel in register with said taphole, a taphole drilling machine comprising a support column, a support arm rotatably mounted on said column for movement about an axis inclined to the vertical, a tool holder connected to said arm for movement therewith and operable to support a tool for boring said taphole, drive means operable upon said support arm to effect rotation of said support arm about said axis between a retracted position and a working position in which said tool holder is in register with said taphole, stop means associated with said drive means to prevent movement of said support arm beyond said working position and adjustment means to adjust said stop means relative to said support arm and thereby vary said working position relative to said taphole, said drive means including a fluid operated motor and control means to maintain pressurised fluid in said motor to oppose movement of said arm during drilling of said taphole.
In accordance with a first embodiment of the invention the stem consists of one single supporting arm with which the tool holder bar forms a predetermined angle. There is no hinged connection between the stem and the tool holder but a rigid and adjustable connection enabling a more stable construction.
In one advantageous embodiment of the invention the 10905-;7 hydraulic or pneumatic fluid serving to actuate the working tool is conveyed through a rigid system of piping consisting of a number of branches pivotable in relation to one another in one plane by means of articulated joints interconnecting the adjacent ends of two adjacent branches.
~ 3A -109~S~.7 According to a further embodiment, the hydraulic or pneumatic fluid is conveyed via flexible conduits which are wound on and unwound from a reel.
Further advantages and characteristics will emerge more clearly from the detailed description given hereunder of certain possible embodiments, without any limitative effect and by reference to the drawings, in which :
Figure 1 is a schematic vertical section through part of a blast furnace, comprising a taphole and a tap spout and a machine serving to drill the taphole.
Figure 2 is a similar view to that provided by Figure 1, with a different angle of inclination for the support column about which the tool holder bar pivots.
Figures 3 - 5 show lateral views of the drilling machine, with different angles of inclination for the support column.
Figures 6 - 8 provide schematic diagrams of a first version of the invention, with facilities for adjusting the height at which the tool holder bar is affixed in relation to the stem.
Figure 9 is a schematic diagram showing different positions, in the vertical direction, for the drilling tool, corresponding to the positions shown in Figures 6 - 8 for the bar.
Figure 10 shows a second embodiment, serving to adjust the height at which the bar is fixed in relation to the stem.
Figure 11 is a schematic diagram of a third embodiment, serving to change the height at which the bar is fixed in relation to the stem.
Figure 12 shows the drilling tool at various angles of inclination in relation to the wall of the furnace.
~' ` 10905~7 Figures 13 - 15 are schematic diagrams of a first embodiment enabling the angle of inclination of the drilling tool to be adjusted in accordance with Figure 12.
Figures 16 - 19 are schematic diagrams of a second embodiment enabling the angle of inclination of the drilling tool to be adjusted in accordance with Figure 12.
Figures 20 and 21 are schematic diagrams of the longi-tudinal sections through two embodiments of the hydraulic jack for swinging the drilling machine.
Figures 22 - 25 are longitudinal sections through different embodiments of the hydraulic jack with a moving cylinder and a fixed piston.
Figure 26 shows a first embodiment of the piping system through which hydraulic or pneumatic fluid is fed to the drilling machine.
Figure 27 is a section across one of the articulated joints used for the pipes shown in Figure 26.
Figures 28 - 30 are cross sections through the feed pipes.
Figures 31 - 33 show winding reels for the flexible feed conduits for the hydraulic or pneumatic fluid, for different positions of the operating tool ïn relation to the tool holder bar.
Figure 34 shows a rotary passage for the feed of the hydraulic or pneumatic fluid through the hub of the reel.
Figure 35 is a vertical section through the support column about which the stem pivots.
In the following description any element occurring in different diagrams retains the same reference number throughout the description.
10905~7 .
The reference number 1 ( see Figures 1 and 2 ) indicates the outer wal] of a blast furnace, the refractory lining of the la~ter being marked 3. It will be noted that, in accordance with the presenttendency, the lining is made thicker in the vicinity of the taphole, which is marked 5. This taphole 5 terminates above the tap spout 7, defined by lateral walls 9.
The taphole drilling machine essentially consists of a bar 11 on wnich is slidably mounted a drill 13 connected to a drilling tool or bit 15. The bar itself is integral with a stem 17 ( see Figures ~ - 5 ) borne by a support column 19 serving as a pivot for the said stem. A driving ~echanism is provided which is not shown in Figures 1 - 5 and which serves to swing the stem 17 and the bar 11, either in a horizontal or in an inclined plane, from a retracted position to an operative position and vice versa.
~ The support column 19 iB advantageously secured in a concrete base 21 and, according to one of the essential characteristics of the present invention, is inclined in relation to the vertical, in the direction of the blast furnace, as shown by the angles ~ and ~ in Figures 1 and 2. This incli-nation of the column 19 makes it possible, in particular, to move the bar 11 in an inclined plane, which means that as and when the bar is withdrawn from the working position it i~
raised, whereas when being moved into the working position it is simultaneously caused to descend in the direction of the tap spout 7, until the bit 15 i~ aligned with the taphole 5 which it is desired to drill.
The bar 11 may be moved to the working position and withdrawn therefrom in one single movement, whereas in the systems existing hitherto the bar is first of all displaced in an approximately horizontal ,~; .
109(~5~7 pl~ne until it is above the tap spout, after which it is lowered in the direction of the latter by an auxiliary vertical movement, involving two independent displacement mechanisms.
The fact is that the auxiliary vertical movement, whether during the positioning of the bar for operation or during its withdrawal, is necessary owing to the fact that the pose of the said bar 11 and the drill bit 15 are situated between the walls 9 of the tap spout 7, which precludes a horizontal pivoting movement of the bar 11 if the.bar or the bit is to be prevented from knocking against the walls 9 of the channel 7.
The embximent discloseqenables this risk to be avoided, even though the bar only performs one movement, one single driving mechanism thus proving sufficient.
As may be seen, the drilling machine disclosed may be constructed to a very moderate height and as the bar ll is lowered as it approaches the taphole, the working platform 23 which is indispensable in present-day blast furnaces to enable automatic lift trucks to circulate.does not have to be interrupted on a level with the tap spouts,/an impprtant factor.~
The angle of inclination of the bar 11 in relation to the horizontal determines the angle of inclination of the tap-hole 5. In Figure 1 the angle of inclination of the supportcolumn 19 in relation to the vertical is equal to that of the bar 11 in relation to the horizontal, so that the said bar will always remain in the same plane, as shown by the arrow A, throughout its pivoting movement about the support column 19.
In the version shown in Figure 2, on the other hand, the angle~
differs from the angle of inclination of the bar 11 and of the taphole 5 in relation to the horizontal, so that while the bar ' . .,, _ ,.
is being pivoted in order to move it into the operative or inoperative position it is displaced parallel to itself, as shown by the arrows C and D.
Figures 3 - 5 are schematic diagrams of ~ree different embodiments, viewed in the direction of the tap spout 7, the positions shown in full lines being the operative positions of the stem 17 and of the bar 11, while those shown in broken lines are the retracted positions, which may be offset, by 120 or 180, for example, in relation to the working positions.
The support column 19~ in Figure 4 is likewise inclined in the direction of the furnace but iS also inclined in the direction of the tap spout. The angle between the stem 17 and the support column 19' is thus different from 90, and the bar 11, in the retracted position, will be higher up than in Figure 3. ~ -The user of a drilling machine can choose between the versions shown in Figure~
3 - 5 in the light of the space available around the furnace and particularly in the place swept by the stem 17 and the bar 11. Thus, it will be possible to select the height of the-retracted position of the drilling machine 90 as to insure an easy access to the drilling tool for its replacement from the working platform 23 or from the ground without the need of a lifting table. Needless to say, different geometrical configu-
It is known that present progress in the design of blast furnaces provides for increasingly large units and for the adoption of increasingly high pressures in the furnace throat.
One ~f the consequences of this tendency is the use of increa-singly hard materials for sealing tapholes, while production requirements and the increasing length of these tapholes require high speed drilling means. It is therefore advisable to have robust and simple drilling machines available which will enable high stresses to be applied and transmitted, particularly the pressures required for the drilling tools.
The increase in the number of tapholes and other items of equipment required for the satisfactory operation and maintenance of blast furnaces, such as the working platforms, reduces the space available around the furnace, and this has to be taken into account when designing the machine, in order to avold movements necessitating a great deal of free space.
The problems facing the designers of these machines are rendered still more complicated by the limitations of a purely geometrical nature, particularly the necessity of enabling the drilling tool or tools to be withdrawn without having to touch the tap spout.
In the known drilling machines in general use the operation of positioning the bar on whichthe drilling tool slides usually involves the displacement of the said bar in an approximately horizontal plane, until it is above the tap spout, followed by a vertical displacement, e.g. by a pivoting movement, in order to lower the bar into the operating position, in which it is then locked mechanically. The withdrawal of the bar to an inoperative position obviously entails the same . . , . ~
1090~ j~7 movements in the reverse order. These compound movements are required by reason of the fact that the nose of the bar bearing the drilling tool must necessarily be lowered fairly down into the tap spout and that impact against the edges of the latter must be avoided at all costs, both when the drilling tool is being positioned for operation and when it is being withdrawn.
The mechanisms for the displacement of the bar, which are already complicated in themselves, to enable these movements to be effected, are rendered still more so by the auxiliary mechanisms for the stepless adjustment of the angle of appli-cation of the bar and also for the selection of its horizontal and vertical positions. All these regulating and displacement mechanisms are generally provided at the sacrifice of the rigidity of the machine as a whole, a drawback incompatible with present-day needs.
Furthermore, the means for displacing the bar and also those for actuating the working tool generally consist of hydraulic or pneumatic motors, for which purpose a set of flexible tubes is provided in order to convey the driving fluid between the various moving elements and components. These flexible tubes, generally made of rubber, not only prove cumbersome and inconvenient but are also a constant potential source of accidents, as they are suspended above the tap spout during operation and thus occupy a position subject to a very high temperature.
An object of the present invention is to provide a machine for the drilling of tapholes which will enable the aforementioned drawbacks to be considerably reduced, or elimi-nated, and in particular, to provide a drilling machine which can accurately be moved into the working position by simple movements and which can thus be constructed on simple lines 1090S~7 and with the required degree of rigidity and without excessive height and which will enable the withdrawal position for the drilling tool bar and also the traject of the movement by which it is conveyed into the said position to be selected as desired and in accordance with the space available around the furnace.
In accordance with the present invention there is provided for use with a shaft furnace having a taphole and a molten metal flow channel in register with said taphole, a taphole drilling machine comprising a support column, a support arm rotatably mounted on said column for movement about an axis inclined to the vertical, a tool holder connected to said arm for movement therewith and operable to support a tool for boring said taphole, drive means operable upon said support arm to effect rotation of said support arm about said axis between a retracted position and a working position in which said tool holder is in register with said taphole, stop means associated with said drive means to prevent movement of said support arm beyond said working position and adjustment means to adjust said stop means relative to said support arm and thereby vary said working position relative to said taphole, said drive means including a fluid operated motor and control means to maintain pressurised fluid in said motor to oppose movement of said arm during drilling of said taphole.
In accordance with a first embodiment of the invention the stem consists of one single supporting arm with which the tool holder bar forms a predetermined angle. There is no hinged connection between the stem and the tool holder but a rigid and adjustable connection enabling a more stable construction.
In one advantageous embodiment of the invention the 10905-;7 hydraulic or pneumatic fluid serving to actuate the working tool is conveyed through a rigid system of piping consisting of a number of branches pivotable in relation to one another in one plane by means of articulated joints interconnecting the adjacent ends of two adjacent branches.
~ 3A -109~S~.7 According to a further embodiment, the hydraulic or pneumatic fluid is conveyed via flexible conduits which are wound on and unwound from a reel.
Further advantages and characteristics will emerge more clearly from the detailed description given hereunder of certain possible embodiments, without any limitative effect and by reference to the drawings, in which :
Figure 1 is a schematic vertical section through part of a blast furnace, comprising a taphole and a tap spout and a machine serving to drill the taphole.
Figure 2 is a similar view to that provided by Figure 1, with a different angle of inclination for the support column about which the tool holder bar pivots.
Figures 3 - 5 show lateral views of the drilling machine, with different angles of inclination for the support column.
Figures 6 - 8 provide schematic diagrams of a first version of the invention, with facilities for adjusting the height at which the tool holder bar is affixed in relation to the stem.
Figure 9 is a schematic diagram showing different positions, in the vertical direction, for the drilling tool, corresponding to the positions shown in Figures 6 - 8 for the bar.
Figure 10 shows a second embodiment, serving to adjust the height at which the bar is fixed in relation to the stem.
Figure 11 is a schematic diagram of a third embodiment, serving to change the height at which the bar is fixed in relation to the stem.
Figure 12 shows the drilling tool at various angles of inclination in relation to the wall of the furnace.
~' ` 10905~7 Figures 13 - 15 are schematic diagrams of a first embodiment enabling the angle of inclination of the drilling tool to be adjusted in accordance with Figure 12.
Figures 16 - 19 are schematic diagrams of a second embodiment enabling the angle of inclination of the drilling tool to be adjusted in accordance with Figure 12.
Figures 20 and 21 are schematic diagrams of the longi-tudinal sections through two embodiments of the hydraulic jack for swinging the drilling machine.
Figures 22 - 25 are longitudinal sections through different embodiments of the hydraulic jack with a moving cylinder and a fixed piston.
Figure 26 shows a first embodiment of the piping system through which hydraulic or pneumatic fluid is fed to the drilling machine.
Figure 27 is a section across one of the articulated joints used for the pipes shown in Figure 26.
Figures 28 - 30 are cross sections through the feed pipes.
Figures 31 - 33 show winding reels for the flexible feed conduits for the hydraulic or pneumatic fluid, for different positions of the operating tool ïn relation to the tool holder bar.
Figure 34 shows a rotary passage for the feed of the hydraulic or pneumatic fluid through the hub of the reel.
Figure 35 is a vertical section through the support column about which the stem pivots.
In the following description any element occurring in different diagrams retains the same reference number throughout the description.
10905~7 .
The reference number 1 ( see Figures 1 and 2 ) indicates the outer wal] of a blast furnace, the refractory lining of the la~ter being marked 3. It will be noted that, in accordance with the presenttendency, the lining is made thicker in the vicinity of the taphole, which is marked 5. This taphole 5 terminates above the tap spout 7, defined by lateral walls 9.
The taphole drilling machine essentially consists of a bar 11 on wnich is slidably mounted a drill 13 connected to a drilling tool or bit 15. The bar itself is integral with a stem 17 ( see Figures ~ - 5 ) borne by a support column 19 serving as a pivot for the said stem. A driving ~echanism is provided which is not shown in Figures 1 - 5 and which serves to swing the stem 17 and the bar 11, either in a horizontal or in an inclined plane, from a retracted position to an operative position and vice versa.
~ The support column 19 iB advantageously secured in a concrete base 21 and, according to one of the essential characteristics of the present invention, is inclined in relation to the vertical, in the direction of the blast furnace, as shown by the angles ~ and ~ in Figures 1 and 2. This incli-nation of the column 19 makes it possible, in particular, to move the bar 11 in an inclined plane, which means that as and when the bar is withdrawn from the working position it i~
raised, whereas when being moved into the working position it is simultaneously caused to descend in the direction of the tap spout 7, until the bit 15 i~ aligned with the taphole 5 which it is desired to drill.
The bar 11 may be moved to the working position and withdrawn therefrom in one single movement, whereas in the systems existing hitherto the bar is first of all displaced in an approximately horizontal ,~; .
109(~5~7 pl~ne until it is above the tap spout, after which it is lowered in the direction of the latter by an auxiliary vertical movement, involving two independent displacement mechanisms.
The fact is that the auxiliary vertical movement, whether during the positioning of the bar for operation or during its withdrawal, is necessary owing to the fact that the pose of the said bar 11 and the drill bit 15 are situated between the walls 9 of the tap spout 7, which precludes a horizontal pivoting movement of the bar 11 if the.bar or the bit is to be prevented from knocking against the walls 9 of the channel 7.
The embximent discloseqenables this risk to be avoided, even though the bar only performs one movement, one single driving mechanism thus proving sufficient.
As may be seen, the drilling machine disclosed may be constructed to a very moderate height and as the bar ll is lowered as it approaches the taphole, the working platform 23 which is indispensable in present-day blast furnaces to enable automatic lift trucks to circulate.does not have to be interrupted on a level with the tap spouts,/an impprtant factor.~
The angle of inclination of the bar 11 in relation to the horizontal determines the angle of inclination of the tap-hole 5. In Figure 1 the angle of inclination of the supportcolumn 19 in relation to the vertical is equal to that of the bar 11 in relation to the horizontal, so that the said bar will always remain in the same plane, as shown by the arrow A, throughout its pivoting movement about the support column 19.
In the version shown in Figure 2, on the other hand, the angle~
differs from the angle of inclination of the bar 11 and of the taphole 5 in relation to the horizontal, so that while the bar ' . .,, _ ,.
is being pivoted in order to move it into the operative or inoperative position it is displaced parallel to itself, as shown by the arrows C and D.
Figures 3 - 5 are schematic diagrams of ~ree different embodiments, viewed in the direction of the tap spout 7, the positions shown in full lines being the operative positions of the stem 17 and of the bar 11, while those shown in broken lines are the retracted positions, which may be offset, by 120 or 180, for example, in relation to the working positions.
The support column 19~ in Figure 4 is likewise inclined in the direction of the furnace but iS also inclined in the direction of the tap spout. The angle between the stem 17 and the support column 19' is thus different from 90, and the bar 11, in the retracted position, will be higher up than in Figure 3. ~ -The user of a drilling machine can choose between the versions shown in Figure~
3 - 5 in the light of the space available around the furnace and particularly in the place swept by the stem 17 and the bar 11. Thus, it will be possible to select the height of the-retracted position of the drilling machine 90 as to insure an easy access to the drilling tool for its replacement from the working platform 23 or from the ground without the need of a lifting table. Needless to say, different geometrical configu-
2~ rations from those shown in Figures 3 - 5 could be adopted~
accor~ing to need.
Figures 6 - 8 illustrate three different positions of the bar 11 in relation to the stem 17. Although the bar 11 is constantly integral with the stem 17 in a drilling machine , a means is nevertheless _~_ .
~09OS67 -provided for changing the height of the bar 11, i.e. that of the tQphole 5. According to Figures 6 - 8, the bar 11 is screwed or bolted to the end of the stem 17, and the system is so designed that the position in which it is so affixed can be raised or lowered, e.g. by unscrewing the bar and then screwing it on again. The positions of the bar 11 in Figures 6, 7 and ~ correspond to the vertical positions VI, VII and VIII of the bit 1~ in Figure 9, respectively.
, The applicants have found that it is very rarely necessary to change the drilling height, w.llcn permits a rigid or semi-rigid connection between the stem 17 and the bar 11 rather than for a hinged interconnection with numerous possibilities of adjustment which would inevitably detract from the rigidity of the machine.
Figure 10 illustrates a different version of the system for changing the height of the bar 11. In Figure 10 one or more intermediate pieces 25 are provided, to be screwed or bolted on between the bar 11 and the stem 17 and forming part of this latter. These intermediate-piec-es~ form a certain angle with the stem 17, and the bar 11 can be raised or lowered by unscrewing this piece 25 and turning it round or by substituting a different intermediate piece with a different angle of incli-nation in respect of the stem 17. It should be noted that the embodimen,t shown in Figure 10 can be easily combined with that shown in Figures 6 - 8.
While the embodimentsshown in Figures 6 - 8 and 10 comprise rigid connections between the bar 11 and the stem 17, the version shown in Figure 11 comprises a semi-rigid connec-tion between the bar 11 and the stem 17. This connection _q_ - lU905~7 consists essentially of a pair of plates 27 and 29, each articulated by its ends to the stem 17 and to a flange 31 of the bar 11, in such a way as to form articulations of the parallelogram type, as shown in Figure 11. To ensure the rigidity of this connection a traverse 33 is provided which is connected to diagonally opposite points of the parallelogram and of which the length determines the height of the bar.
For the purpose of adjusting the height of the said bar 11, a means is provided for varying the length of the traverse, such as an adjusting thread 35, which enables the height of the bar 11 to be steplessly regulated.
Figures 12 - 19 relate to the angular adjustment of the bar in a vertical plane. This adjustment enables the bar 11 to be rotated in a vertical plane in order to vary the angle f inclination of the taphole, and Figures 13 - 15 show a first embodiment for this adjust-ment, shown schematically in Figure 12. As a result of consi-derations analogous to those relating to the adjustment of the bar 11 and the bit 15 in the vertical direction,-the anglè
adjusting means illustrated in Figures 13 - 19 are rigid in the present invention, as changes in the angle of inclination of the taphole are very rarely necessary, and a robust construction supporting the vibration stress is now of far greater value than one enabling easy stepless adjustment to be effected, these latter only being possible at the sacrifice of rigidity.
The bar is suspended from a bracket 37 integral with a ho~low sleeve 39 having a cheek 43. The sleeve 39 is borne by an intermediate piece 45 having a cheek 47 designed to interact with the cheek 43 of the sleeve 39. The intermediate piece is integral with a flange 41 of the stem 17. The stem 17 1o90S67 and the bar 11 are rendered integral with each other by the aid of the cheeks 43 and 47 and by means of a securing collar 51.
When this collar 51 is released, the bar 11 is enabled to pivot in a vertical plane about the longitudinal axis of the sleeve 39 and of the piece 45. A ring 49, made of a material with a high frictional coefficient, such as that known by the commercial name of " Ferodo ",increases the friction between the two cheeks 43 and 47, thus enabling the parts in question to be connected still more firmly together. The inner groove of the collar 51 having a trapezoidal cross section designed to interact with the inclined external surfaces of the cheeks 43 and 47, the tightening of the collar 51 generates a considerable axial compressive stress on the cheeks, thus providing a securing system which is no longer releasable, particularly since a friction ring 49 can also be inserted.
In order to prevent the bar 11 from tilting under the effect of its own weight during the release of the collar 51 and in order to facilitate the angular adjustment of the bar 11 an adjustable connection is provided between the bracket 37 and the stem 17, e.g. in the form of a threaded rod 53, linked at one end to the inside of the bracket 37 and secured at the other end in the boring of a traverse 55 connected to the stem 17. The bar 11 can thus be pivoted by causing the rod 53 to perform a sliding movement ( controlled, for example, by adjusting nuts on both sides of the traverse ) through the traverse 55, or by other means known per se.
In ~igure 16 the end of a stem 17 is illustrated, a cheek 56 being integral therewith. A second cheek 58, associated with a tool holder bar not shown in the drawing, either rigidly or via an adjustable securing system such as shown in Figure 19, interacts with the cheek 56 and with the tool holder bar.
~090S67 The cheek 58 comprises an axial bore by means of which it is caused to engage a central axial extension 60 of the cheek 56.
The end of this axial extension 60 is provided with a screw threading designed to receive a securing nut 62.
The opposite adjacent surfaces of the cheeks 56 and 58 are provided with rims, 64 and 66 respectively, of radial corrugations. The corrugations of these two rims 64 and 66 are of complementary shape so as to engage each other, as shown in the enlarged view provided by Figure 18. The radial corru-gati~ons can be provided by milling or dying.
~igure 17 is a schematic diagram of a front view of one of the rims of corrugations, e.g. the rim 64, certain corrugations having been shown schematically thereon. It will be obvious that these corrugations extend around the entire circumference of the cheek. The number of corrugations is left to the choice of the designer and may be 90, for example, in which case each of them corresponds to an angle of 4.
To alter the angle of inclination of the tool holder bar, all that is required is to release the securing nut 62 and tilt the bar by rotating the cheek 58 in relation to the cheek 56. A rotation of one notch in the cheek 58 in relation to the cheek 56 will correspond, in the case of the afore-mentioned number of corrugations, to a change of 4 in the angle of inclination of the bar.
The fineness of adjustment rendered possible by the securing system shown in ~igure 16 thus depends on the number of corrugations in the two cheeks 64 and 66.
In ~igure l9 " a " indicates the angular-pitches by which the angular inclination of a tool holder bar ll can be adjusted about the axis 0, which is the longitudinal axis of the stem not shown in this diagram. The version shown in this ~.vso567 ~igure 19 also provides a means of steplessly adjusting the angle of inclination of the bar 11 about a second axis 0' which is different from the axis 0. This axis 0~ is formed by the centre of articulation of one of the two fastenings between the bar 11 and one end of an arm 68 integral with the cheek 58. The opposite end of this arm 68 comprises a traverse 70 capable of sliding on a screw-threaded rod 72 articulated to the bar 11. The sliding movement of the rod 72 in the traverse 70 and thus the pivoting movement of the bar 11 about the axis 0' can be adjusted and controlled by means known per se, such as regulating nuts which are not shown and which are screwed onto both sides of the traverse 70.
In contradistinction to the angular adjustment rendered possible by the securing system shown in Figure 16, the adjustment provided by the assembly consisting of the traverse 70 and the rod 72 is continuous. The reference letters b provide a schematic illustration of the pivoting movement of the bar 11 about the axis 0' by the sliding movement of the rod 72 in the traverse 70.
The assembly shown in Figure 19 could be replaced by a similar assembly serving to obtain an angular adjustment about the axis 0 or about the axis of the other fastening.
The stem 17 may consist of a single arm or a double arm forming with the bar 11 a parallelogram-type linkage becoming deformed during the swinging movement of the stem 17.
The stem 17 is rotated about the longitudinal axis of the support column by a hydraulic jack. The mounting of this hydraulic jack may be similar to the mounting disclosed in the British patent specification N 1367332, i.e. the piston rod of the hydraulic jack acts directly on the stem in a 120 type machine, whereas in a 180 type machine the hydraulic jack 10905{;7 is reversed and its displaceable cylinder acts on the stem via an intermediate hinged stirrup.
The drilling machines covered by the prior art generally comprise a locking mechanism serving to secure the bar in the working position. The mechanisms may consist either of hooks by which the bar is hooked onto the wall of the furnace or limit stops for blocking the driving device of the bar, e.g. for blocking the stem, in a certain position.
In the preferred embodLment !no mechanical locking in the operating positio ~ so that the drilling machine in question is simplified still further.
In order to i~mmobilize the bar 11 in a certain position during the drilling of the taphole, the preferred embodiment provides for the displacement~~of the piston of the hydraulic jack actuating the stem as far as a certain predetermined position, e.g. the end of its travel, and for the maintenance of the pressure of the hydraulic fluid in this position. The movements a~d lengths of the different elements must naturally be coordinated in such a way that the position selected, e.g.
the end of travel of the hydraulic piston, corresponds to the operating position of the supportlng armli .and of the bar 11. In order to compensate any assembly inaccuracies and enable the drilled hole to be displaced laterally the present invention includes means for adjusting the working position.
~igures.20 and 21 show two embodiments for a retracted position at 120, in which the hydraulic jack 67 i8 actuated as far as the end of travel of the piston 105. In each case means have been provided for adjusting the length of the piston rod 59 in order to ensure that the position of the end of travel of the piston 105 corresponds to the working position of the bar 11 and the stem 17, not shown in these diagrams. In the .
lO~lOS~i7 embodiments of Figures 20 and 21 the piston rod 59 acts on a pin 77 held between two lug9 of the stem. In the case of \
Figure 20 the adjusting means consist of a simple screw-threaded tension coupling 108, while in the case of Figure 21 1~0 there is a set of interposed segments~of which the number canbe increased or reduced in order to obtain the desired length for the piston rod ~9 The hydraulic jack is mounted on a pivot 71 in order to accomodate the changes of orientation involved by the swinging movement of the stem.
In the embodiment illustrated in Figures 20 and 21 the jack 67 is in each case actuated as far as the end of travel of the piston 105, and the pressure of the hydraulic fluid i8 maintained during the drilling in the working position, QO that no mechanical device is required for locking the bar 11 or the supporting arm 59 in the operative position.
Figures 22 to 25 are schematic diagrams of longitudinal sections through different constructional embodiments of a hydraulic jack ~1 for the rotation of the supporting arm in a 1~0 type machine. In contradistinction to the con~truc-tional version shown in Figures 20 and 21, it is the cylinder 107 which is displaced in relation to the piQton 109 and to the rod 83 and which, ~ia a journal 93 and an intermediate stirrup, not shown, causes the stem to pivot. The rod 83 is mounted on a pivot 87 corresponding to pivot 71 of Figures 20 and 21. ~ue to the mobility of the cylinder 107 the hydraulic fluid is conveyed through a central bore 111 of the rod 83 into the interior of the jacket 81, in order to move the cylinder as far as the position of operatlon shown in Figure 22.
To cause the bar and the stem to return to the position of rest, fluid is injected through an annular passage 113 surroun-ding the bore 111, through which the return fluid is expelled from the cylinder 107.
~
1090~7 As in the case of Figure~ 20 and 21, the pressure is maintained in fluid in the operating position and thus al~o provides for mean~ for limiting and adjusting the travel of the cylinder 107 in such a way as to determine its end of travel so that the latter will correspond to the operating position. In the case of a reversed jack such as shown in Figures 22 to 25, however, it is more difficult to vary the length of the rod 83, since the feed is effected through the said rod, and recourse to other means becomes preferable.
In the embodiment shown in Figures 22 and 23, the jack is actuated as far as the end of travel of the cylinder 107, i.e. until the movement when the latter can no longer be dis-placed in relation to the piston 109, as shown in Figures 22 and 23. In order to ensure that this end of travel will correspond to the operating position of the bar, the connection between the movable cylinder 107 and the journal 93 i8 ad justable .
In the embodiment shown in Figure 22 the cylihder 107 comprises an external threading onto which are ~crewed two regulating nuts 104 and 106, the journal 93 being secured between these two nuts. The longitudinal position of the journal 93 in relation to the cylinder 107 can thu~ be alt~red simply by moving the two nuts 104 and 106.
In the em~bodiment shown in Figure 23 the cylinder 107 comprises a flange 115 made integral with the journal 93 by means of regulating rod~ 117, 117', which enable the journal 93 to be moved closer to or farther away from the flange 115.
It is thus by these regulating rod 117, 117', that the journal i8 diBplaCed.
In the embodiment shown in Figures 24 and 25 the travel of the cylinder 107 i~ delimited not by displacing the cylinder . , , ' ~ .
109~5ti7 to the maximum, as in the case of Figure 23, but by providing external stops for the purpose.
Rods 119 and 119' pass through the journal 93. These rods are integral with the pivot 87, and the journal 93 slides on the rods 119 and 119' during the operation of the hydraulic jack. Figures 24 and 25 illustrate the two extrem~
positions of the cylinder 107, that shown in Figure 24, in which it is moved completely out of the way, being produced when the journal 93 encounters the adjusting nuts 121, 121'.
The position of these adjusting nuts 121 and 121' thus deter-mines the end of travel of the cylinder 107 and thus the working position of the stem and of the bar.
It should be noted that the values 120 and 180 mentioned farther back for the retracted position of the machine are not limitative and that intermediate or even higher or lower values could be adopted, according to requirements and possibilities.
The longer the stem 17 and the bar 11, the more essential is the presence of the adjusting means according to Figures 20 to 25. The fact i8 that a slight displacement of the piston or the cylinder may cause a comparatively great dis-placement of the bar and the drilling tool so that the constructional and assembly inaccuracies have to be compensated ~ by these adjusting means before the operation of the machine.
?5 It is to be noted that the hydraulical locking of the drilling machine in the operating position affords a better damping of the vibrations as compared to the known mechanical - locking means.
Figure 26 shows the bar 11 with the drill 13 shown in full lines to the rear of the bar 11 and in broken lines in the . ` 1~J9~S~;7 forward position. The means for actuating the drilling machine 13 and displacing it on the bar are well known per se and do not form part of the present invention. On the other hand, the latter provides novel means for feeding hydraulic or pneumatic fluid to the drilling machine.
This feed is effected via a rigid piping system 125 having articulated joints 127 to folIow the movement of the drilling machine. A number of pipes, according to the requirements of the drill 13, can be caused to pass through this system of piping 125. In accordance with the sectional diagrams provided by Figure 28~, the piping 125 comprises an outer pipe 129 and two small juxtaposed inner pipes 133 and 133, enabling three different fluids to circulate in the piping 1~5 without being mixed together.
In Figure 29 the piping consists of three concentric pipes 135, 137 and 139, again enabling three different currents to circula,te. The piping 125, shown in ~ection in ~igure 30, only compri~es two pipes 141 and 143, 90 that in thi~ case only two different current~ can circulate.
Figure 27 shows a version of a system of joints 127 enabling the different branches of the piping system 125 to pivot in relation to one another. The joint system 127 is designed for a double pipe system such a~ shown in Figure 28 but could easily be adapted to ~ystems with three or four or more pipes.
The articulated system 127 consists essentially of a hollow external cylinder 145 in which an inner cylinder 147 is hermetically accomodated, and these two cylinders can under-go angular displacement~ in relation to each other. Each of ~, .
the two cylinders 145 and 147 i8 integral with one of the~\
\ ' . ~ ~
1~ 9 ~ ~ 7 branches 149 and 151 of the piping system. The inner cylinder comprises internal passages 153 and 155 each of which leads at one end into one of the pipes contained in the branch 151 with which the inner cylinder i8 integral and at the other end 5 into one of the angular grooves 157 and 159 provided on the periphery of the said cylinder 147. The external cylinder 145 is provided, in its lateral wall, with radial passages 161 and 163. Each of these passages communicate~ at one end with one of the pipes contained in the branch 149 with which the outer cylinder is integral and at the other with one of the angular grooves 157 and 159. The-peripheral grooves 157 and 159 thus provide communication between the passages 153 and 155 of the inner cylinder 147 and the corresponding passages 161 and 163 of the external cylinder 145 and thus between the pipes of the branch 151 and the çorresponding pipes of the branch 149, even in the course of a pivoting movemént between the two cylinders 145 and 147.
To enable the system of articulation 127 and the system~
of piping 125 to be dismantled, the internal cylinder 147 is subdivided diametrically, the two parte being secured to each other by an axial screw 165.
In order to avoid leakages between the two cylinders 145 and 147 or the intermixture of fluid between the groove~
157 and 159, annular jointB 167 are provided around the internal cylinder.
Thanks to the rigid piping, provided with joints enabling it to perform pivoting and bending movements in one plane and giving pa3~ages to a number of different currents of hydraulic and/or pneumatic fluid 30 ~ ~a simple and effective solu ~O~ heed problem caused by the entanglement of a large number of flexible tubes suspended around known types of drilling machines, as one \
0~
.
single piping system Ruffices to give passage to all the required currents of fluid.
~ This advantage is the more important as most of modern drilling machines necessitate several distinct pneumatic fluid lines. The drill, which, in fact, is a percussion drill is in certain types of machines equipped with means enabling the percussion mechanism to be actuated in both directions in order to facilitate the removal of the drilling tool from the taphole. In this type of machine an additional feed line is required for actuating the percussion mechanism in the direction of removal. Furthermore, if the percussion mechanism is sepa-rated from the drill mechanism a further pneumatic feed line is required. Besides the above possib~ities certain machines are equipped with a blower in order to remove the cuttings from the taphole during the drilling operation.
The articulated rigid piping can be mounted in two different ways, according to the space available. The method shown by 125 in Figure 26, in continuous and broken double lines, corresponds to a first arrangement, while the method shown by 125', in continuous and broken single lines, corres-ponds to a second arrangement for the piping.
Figure~ 31 to 35 show a second embodiment for feeding the pneumatic fluid to the drill 13.
Figure 31 shows a bar 11 bearing a drill 13, to actuate a drill bit 15, the machine being shown in full lines to the rear of the bar 11 and in broken lines when in the advanced position. ;the supply of hydraulic or pneumatic fluid to the drill 13 is effected via flexible conduit 236 which is unwound from a reel 240 as and when the drill 13 is fed forward. The reel 240 is mounted at ~._ l~ it;7 the rear end of the bar 11 and is subjected to the action of a spring which is not shown and which tends to cause the reel 240, in the example illustrated, to rotate anti-clockwise, in order to wind up the conduit 236 when the drill 13 is returning to the retractedposition shown in full lines.
A feed conduit 242 for hydraulic or pneumatic fluid communicates via the hub of -the reel 240 with the flexible conduit 236.
Instead of providing a spring to actuate the reel it is also possible to couple this latter to the traversing mechanism of the drill 13 in such a way that the reel is automatically rotated synchronously with the traversing movement of the drill 13.
Figure 33 shows a similar construction to that illus-trated in Figure 31 but with the drill 13 ' mounted above the bar 11. The reel 240~ is mounted, similarly to the reel 240, on the bar 11, but undergoes the action of a spring or of a traversing mechanism not shown in the drawing, in such a way as to cause it to rotate, in the example shown in Figure 33, in a clockwise direction, in order to wind up the conduit 236.
In Figure 32 the drill 13 ' is mounted in a similar manner to that shown in Figure 33. In the version illustrated in Figure 32 a reel 244 is provided, mounted on a suitable support 246 above the bar 11, the hydraulic or pneumatic fluid likewise being fed, via a feed conduit, through the hub of the reel 244.
Figures 31 - 33 show that the arrangement can be adapted to local circumstances and to the space available for a suitable assembly. ~he great advantage offered by the system in which conduits are wound onto a reel is the fact that the latter are always in place when the drill occupies its retracted position and are thus not inconveniently suspended below the ~ jt;7 bar 11 and possibly above the tap spout.
If two or more separate conduits for hydraulic or pneumatic fluid are required, it will then be possible to provide two reels for winding up each of the conduits and/or for winding up the two conduits side by side on the same reel.
Figure 34 which is a section along the line A-A of Figure 31, illustrates this last possibility. Two parallel conduits 242 and 242' for the feed of the fluid lead via the fixed shaft 250 of the hub 25~ of the reel ?40 into peripheral grooves 252 and 252' of the said hub 251. These peripheral grooves 252 and 252' communicate direct, via radial conduits 254 and 254', with the conduits 236 and 236' respectively.
The feed conduits 242 and 242' are thus constantly in communi-cation with the conduits 236 and 236', even in the event of the rotation of the hub 25~ in relation to the shaft 250.
A set of joints 256 isolates the peripheral grooves 252 and 252' both from the outside and from each .
It i8 obvious that in the case of one single flexible conduit per reel the system of supplying the fluid by rotary passage in the hub of the reel is analogous to the embodiment shown in Figure 34. If necessary, moreover, more than two conduits could be provided, by means of assemblies based on the same principles as those shown in the diagrams.
Instead of providi~g two parallel conduits 242 and 242' it will be possible to provide multiple conduits such as described with reference to Figures 28 - 30.
~igure 35 shows how pneumatic or hydraulic fluids are fed through the support column 19 ~he support column comprises a fixed internal cylinder 173 and an external cylinder 171 capable of pivoting ,~, ' lV90~7 about the internal cylinder, the external cylinder being integral with the stem 17.
the feed of the pneumatic or hydraulic fluid required for the operation of the drilling machine is effected through the internal cylinder 173 of the column. Three pipes 175, 177 and 179 have been shown by way of an example, although a still greater number of pipes could be installed if desired. Each of the pipes 175, 177 and 179 comprises a fixed lower section 175 ~ 177 ~
and 179' respectively and a movable upper section 175", 177"
and 179" respectively, the connection between the upper and lower sections being provided by swivels 185, 187 and 189 respectively. These swivels, wh1le ensuring hermeticity between the adjacent ends of the upper sections 175", 177" and 179"
and lower sections 175 ', 177 ' and 179 ', enable the upper sections to rotate in relation to the lower sections when the said upper sections follow the pivoting movement of the stem 17 about the fixed cylinder 173. These swivels 185, 187 and 189, needless to say, must be positioned on the rotation axis of the cylinder 171. This system of feeding and distri-buting the fluids via the interior of the support column form~ a valuable contribution to the reduction in the total height of the drilling machine, since the pneumatic fluid in existing systems was supplied and distributed above the support column, involving an unnecessary increase in the over-all height of the apparatus.
It should also be noted that the pipes 175, 177 and 179 may be of the single or multiple type, e.g. concentric, as shown in Figure 29, according to requirements.
~- .
accor~ing to need.
Figures 6 - 8 illustrate three different positions of the bar 11 in relation to the stem 17. Although the bar 11 is constantly integral with the stem 17 in a drilling machine , a means is nevertheless _~_ .
~09OS67 -provided for changing the height of the bar 11, i.e. that of the tQphole 5. According to Figures 6 - 8, the bar 11 is screwed or bolted to the end of the stem 17, and the system is so designed that the position in which it is so affixed can be raised or lowered, e.g. by unscrewing the bar and then screwing it on again. The positions of the bar 11 in Figures 6, 7 and ~ correspond to the vertical positions VI, VII and VIII of the bit 1~ in Figure 9, respectively.
, The applicants have found that it is very rarely necessary to change the drilling height, w.llcn permits a rigid or semi-rigid connection between the stem 17 and the bar 11 rather than for a hinged interconnection with numerous possibilities of adjustment which would inevitably detract from the rigidity of the machine.
Figure 10 illustrates a different version of the system for changing the height of the bar 11. In Figure 10 one or more intermediate pieces 25 are provided, to be screwed or bolted on between the bar 11 and the stem 17 and forming part of this latter. These intermediate-piec-es~ form a certain angle with the stem 17, and the bar 11 can be raised or lowered by unscrewing this piece 25 and turning it round or by substituting a different intermediate piece with a different angle of incli-nation in respect of the stem 17. It should be noted that the embodimen,t shown in Figure 10 can be easily combined with that shown in Figures 6 - 8.
While the embodimentsshown in Figures 6 - 8 and 10 comprise rigid connections between the bar 11 and the stem 17, the version shown in Figure 11 comprises a semi-rigid connec-tion between the bar 11 and the stem 17. This connection _q_ - lU905~7 consists essentially of a pair of plates 27 and 29, each articulated by its ends to the stem 17 and to a flange 31 of the bar 11, in such a way as to form articulations of the parallelogram type, as shown in Figure 11. To ensure the rigidity of this connection a traverse 33 is provided which is connected to diagonally opposite points of the parallelogram and of which the length determines the height of the bar.
For the purpose of adjusting the height of the said bar 11, a means is provided for varying the length of the traverse, such as an adjusting thread 35, which enables the height of the bar 11 to be steplessly regulated.
Figures 12 - 19 relate to the angular adjustment of the bar in a vertical plane. This adjustment enables the bar 11 to be rotated in a vertical plane in order to vary the angle f inclination of the taphole, and Figures 13 - 15 show a first embodiment for this adjust-ment, shown schematically in Figure 12. As a result of consi-derations analogous to those relating to the adjustment of the bar 11 and the bit 15 in the vertical direction,-the anglè
adjusting means illustrated in Figures 13 - 19 are rigid in the present invention, as changes in the angle of inclination of the taphole are very rarely necessary, and a robust construction supporting the vibration stress is now of far greater value than one enabling easy stepless adjustment to be effected, these latter only being possible at the sacrifice of rigidity.
The bar is suspended from a bracket 37 integral with a ho~low sleeve 39 having a cheek 43. The sleeve 39 is borne by an intermediate piece 45 having a cheek 47 designed to interact with the cheek 43 of the sleeve 39. The intermediate piece is integral with a flange 41 of the stem 17. The stem 17 1o90S67 and the bar 11 are rendered integral with each other by the aid of the cheeks 43 and 47 and by means of a securing collar 51.
When this collar 51 is released, the bar 11 is enabled to pivot in a vertical plane about the longitudinal axis of the sleeve 39 and of the piece 45. A ring 49, made of a material with a high frictional coefficient, such as that known by the commercial name of " Ferodo ",increases the friction between the two cheeks 43 and 47, thus enabling the parts in question to be connected still more firmly together. The inner groove of the collar 51 having a trapezoidal cross section designed to interact with the inclined external surfaces of the cheeks 43 and 47, the tightening of the collar 51 generates a considerable axial compressive stress on the cheeks, thus providing a securing system which is no longer releasable, particularly since a friction ring 49 can also be inserted.
In order to prevent the bar 11 from tilting under the effect of its own weight during the release of the collar 51 and in order to facilitate the angular adjustment of the bar 11 an adjustable connection is provided between the bracket 37 and the stem 17, e.g. in the form of a threaded rod 53, linked at one end to the inside of the bracket 37 and secured at the other end in the boring of a traverse 55 connected to the stem 17. The bar 11 can thus be pivoted by causing the rod 53 to perform a sliding movement ( controlled, for example, by adjusting nuts on both sides of the traverse ) through the traverse 55, or by other means known per se.
In ~igure 16 the end of a stem 17 is illustrated, a cheek 56 being integral therewith. A second cheek 58, associated with a tool holder bar not shown in the drawing, either rigidly or via an adjustable securing system such as shown in Figure 19, interacts with the cheek 56 and with the tool holder bar.
~090S67 The cheek 58 comprises an axial bore by means of which it is caused to engage a central axial extension 60 of the cheek 56.
The end of this axial extension 60 is provided with a screw threading designed to receive a securing nut 62.
The opposite adjacent surfaces of the cheeks 56 and 58 are provided with rims, 64 and 66 respectively, of radial corrugations. The corrugations of these two rims 64 and 66 are of complementary shape so as to engage each other, as shown in the enlarged view provided by Figure 18. The radial corru-gati~ons can be provided by milling or dying.
~igure 17 is a schematic diagram of a front view of one of the rims of corrugations, e.g. the rim 64, certain corrugations having been shown schematically thereon. It will be obvious that these corrugations extend around the entire circumference of the cheek. The number of corrugations is left to the choice of the designer and may be 90, for example, in which case each of them corresponds to an angle of 4.
To alter the angle of inclination of the tool holder bar, all that is required is to release the securing nut 62 and tilt the bar by rotating the cheek 58 in relation to the cheek 56. A rotation of one notch in the cheek 58 in relation to the cheek 56 will correspond, in the case of the afore-mentioned number of corrugations, to a change of 4 in the angle of inclination of the bar.
The fineness of adjustment rendered possible by the securing system shown in ~igure 16 thus depends on the number of corrugations in the two cheeks 64 and 66.
In ~igure l9 " a " indicates the angular-pitches by which the angular inclination of a tool holder bar ll can be adjusted about the axis 0, which is the longitudinal axis of the stem not shown in this diagram. The version shown in this ~.vso567 ~igure 19 also provides a means of steplessly adjusting the angle of inclination of the bar 11 about a second axis 0' which is different from the axis 0. This axis 0~ is formed by the centre of articulation of one of the two fastenings between the bar 11 and one end of an arm 68 integral with the cheek 58. The opposite end of this arm 68 comprises a traverse 70 capable of sliding on a screw-threaded rod 72 articulated to the bar 11. The sliding movement of the rod 72 in the traverse 70 and thus the pivoting movement of the bar 11 about the axis 0' can be adjusted and controlled by means known per se, such as regulating nuts which are not shown and which are screwed onto both sides of the traverse 70.
In contradistinction to the angular adjustment rendered possible by the securing system shown in Figure 16, the adjustment provided by the assembly consisting of the traverse 70 and the rod 72 is continuous. The reference letters b provide a schematic illustration of the pivoting movement of the bar 11 about the axis 0' by the sliding movement of the rod 72 in the traverse 70.
The assembly shown in Figure 19 could be replaced by a similar assembly serving to obtain an angular adjustment about the axis 0 or about the axis of the other fastening.
The stem 17 may consist of a single arm or a double arm forming with the bar 11 a parallelogram-type linkage becoming deformed during the swinging movement of the stem 17.
The stem 17 is rotated about the longitudinal axis of the support column by a hydraulic jack. The mounting of this hydraulic jack may be similar to the mounting disclosed in the British patent specification N 1367332, i.e. the piston rod of the hydraulic jack acts directly on the stem in a 120 type machine, whereas in a 180 type machine the hydraulic jack 10905{;7 is reversed and its displaceable cylinder acts on the stem via an intermediate hinged stirrup.
The drilling machines covered by the prior art generally comprise a locking mechanism serving to secure the bar in the working position. The mechanisms may consist either of hooks by which the bar is hooked onto the wall of the furnace or limit stops for blocking the driving device of the bar, e.g. for blocking the stem, in a certain position.
In the preferred embodLment !no mechanical locking in the operating positio ~ so that the drilling machine in question is simplified still further.
In order to i~mmobilize the bar 11 in a certain position during the drilling of the taphole, the preferred embodiment provides for the displacement~~of the piston of the hydraulic jack actuating the stem as far as a certain predetermined position, e.g. the end of its travel, and for the maintenance of the pressure of the hydraulic fluid in this position. The movements a~d lengths of the different elements must naturally be coordinated in such a way that the position selected, e.g.
the end of travel of the hydraulic piston, corresponds to the operating position of the supportlng armli .and of the bar 11. In order to compensate any assembly inaccuracies and enable the drilled hole to be displaced laterally the present invention includes means for adjusting the working position.
~igures.20 and 21 show two embodiments for a retracted position at 120, in which the hydraulic jack 67 i8 actuated as far as the end of travel of the piston 105. In each case means have been provided for adjusting the length of the piston rod 59 in order to ensure that the position of the end of travel of the piston 105 corresponds to the working position of the bar 11 and the stem 17, not shown in these diagrams. In the .
lO~lOS~i7 embodiments of Figures 20 and 21 the piston rod 59 acts on a pin 77 held between two lug9 of the stem. In the case of \
Figure 20 the adjusting means consist of a simple screw-threaded tension coupling 108, while in the case of Figure 21 1~0 there is a set of interposed segments~of which the number canbe increased or reduced in order to obtain the desired length for the piston rod ~9 The hydraulic jack is mounted on a pivot 71 in order to accomodate the changes of orientation involved by the swinging movement of the stem.
In the embodiment illustrated in Figures 20 and 21 the jack 67 is in each case actuated as far as the end of travel of the piston 105, and the pressure of the hydraulic fluid i8 maintained during the drilling in the working position, QO that no mechanical device is required for locking the bar 11 or the supporting arm 59 in the operative position.
Figures 22 to 25 are schematic diagrams of longitudinal sections through different constructional embodiments of a hydraulic jack ~1 for the rotation of the supporting arm in a 1~0 type machine. In contradistinction to the con~truc-tional version shown in Figures 20 and 21, it is the cylinder 107 which is displaced in relation to the piQton 109 and to the rod 83 and which, ~ia a journal 93 and an intermediate stirrup, not shown, causes the stem to pivot. The rod 83 is mounted on a pivot 87 corresponding to pivot 71 of Figures 20 and 21. ~ue to the mobility of the cylinder 107 the hydraulic fluid is conveyed through a central bore 111 of the rod 83 into the interior of the jacket 81, in order to move the cylinder as far as the position of operatlon shown in Figure 22.
To cause the bar and the stem to return to the position of rest, fluid is injected through an annular passage 113 surroun-ding the bore 111, through which the return fluid is expelled from the cylinder 107.
~
1090~7 As in the case of Figure~ 20 and 21, the pressure is maintained in fluid in the operating position and thus al~o provides for mean~ for limiting and adjusting the travel of the cylinder 107 in such a way as to determine its end of travel so that the latter will correspond to the operating position. In the case of a reversed jack such as shown in Figures 22 to 25, however, it is more difficult to vary the length of the rod 83, since the feed is effected through the said rod, and recourse to other means becomes preferable.
In the embodiment shown in Figures 22 and 23, the jack is actuated as far as the end of travel of the cylinder 107, i.e. until the movement when the latter can no longer be dis-placed in relation to the piston 109, as shown in Figures 22 and 23. In order to ensure that this end of travel will correspond to the operating position of the bar, the connection between the movable cylinder 107 and the journal 93 i8 ad justable .
In the embodiment shown in Figure 22 the cylihder 107 comprises an external threading onto which are ~crewed two regulating nuts 104 and 106, the journal 93 being secured between these two nuts. The longitudinal position of the journal 93 in relation to the cylinder 107 can thu~ be alt~red simply by moving the two nuts 104 and 106.
In the em~bodiment shown in Figure 23 the cylinder 107 comprises a flange 115 made integral with the journal 93 by means of regulating rod~ 117, 117', which enable the journal 93 to be moved closer to or farther away from the flange 115.
It is thus by these regulating rod 117, 117', that the journal i8 diBplaCed.
In the embodiment shown in Figures 24 and 25 the travel of the cylinder 107 i~ delimited not by displacing the cylinder . , , ' ~ .
109~5ti7 to the maximum, as in the case of Figure 23, but by providing external stops for the purpose.
Rods 119 and 119' pass through the journal 93. These rods are integral with the pivot 87, and the journal 93 slides on the rods 119 and 119' during the operation of the hydraulic jack. Figures 24 and 25 illustrate the two extrem~
positions of the cylinder 107, that shown in Figure 24, in which it is moved completely out of the way, being produced when the journal 93 encounters the adjusting nuts 121, 121'.
The position of these adjusting nuts 121 and 121' thus deter-mines the end of travel of the cylinder 107 and thus the working position of the stem and of the bar.
It should be noted that the values 120 and 180 mentioned farther back for the retracted position of the machine are not limitative and that intermediate or even higher or lower values could be adopted, according to requirements and possibilities.
The longer the stem 17 and the bar 11, the more essential is the presence of the adjusting means according to Figures 20 to 25. The fact i8 that a slight displacement of the piston or the cylinder may cause a comparatively great dis-placement of the bar and the drilling tool so that the constructional and assembly inaccuracies have to be compensated ~ by these adjusting means before the operation of the machine.
?5 It is to be noted that the hydraulical locking of the drilling machine in the operating position affords a better damping of the vibrations as compared to the known mechanical - locking means.
Figure 26 shows the bar 11 with the drill 13 shown in full lines to the rear of the bar 11 and in broken lines in the . ` 1~J9~S~;7 forward position. The means for actuating the drilling machine 13 and displacing it on the bar are well known per se and do not form part of the present invention. On the other hand, the latter provides novel means for feeding hydraulic or pneumatic fluid to the drilling machine.
This feed is effected via a rigid piping system 125 having articulated joints 127 to folIow the movement of the drilling machine. A number of pipes, according to the requirements of the drill 13, can be caused to pass through this system of piping 125. In accordance with the sectional diagrams provided by Figure 28~, the piping 125 comprises an outer pipe 129 and two small juxtaposed inner pipes 133 and 133, enabling three different fluids to circulate in the piping 1~5 without being mixed together.
In Figure 29 the piping consists of three concentric pipes 135, 137 and 139, again enabling three different currents to circula,te. The piping 125, shown in ~ection in ~igure 30, only compri~es two pipes 141 and 143, 90 that in thi~ case only two different current~ can circulate.
Figure 27 shows a version of a system of joints 127 enabling the different branches of the piping system 125 to pivot in relation to one another. The joint system 127 is designed for a double pipe system such a~ shown in Figure 28 but could easily be adapted to ~ystems with three or four or more pipes.
The articulated system 127 consists essentially of a hollow external cylinder 145 in which an inner cylinder 147 is hermetically accomodated, and these two cylinders can under-go angular displacement~ in relation to each other. Each of ~, .
the two cylinders 145 and 147 i8 integral with one of the~\
\ ' . ~ ~
1~ 9 ~ ~ 7 branches 149 and 151 of the piping system. The inner cylinder comprises internal passages 153 and 155 each of which leads at one end into one of the pipes contained in the branch 151 with which the inner cylinder i8 integral and at the other end 5 into one of the angular grooves 157 and 159 provided on the periphery of the said cylinder 147. The external cylinder 145 is provided, in its lateral wall, with radial passages 161 and 163. Each of these passages communicate~ at one end with one of the pipes contained in the branch 149 with which the outer cylinder is integral and at the other with one of the angular grooves 157 and 159. The-peripheral grooves 157 and 159 thus provide communication between the passages 153 and 155 of the inner cylinder 147 and the corresponding passages 161 and 163 of the external cylinder 145 and thus between the pipes of the branch 151 and the çorresponding pipes of the branch 149, even in the course of a pivoting movemént between the two cylinders 145 and 147.
To enable the system of articulation 127 and the system~
of piping 125 to be dismantled, the internal cylinder 147 is subdivided diametrically, the two parte being secured to each other by an axial screw 165.
In order to avoid leakages between the two cylinders 145 and 147 or the intermixture of fluid between the groove~
157 and 159, annular jointB 167 are provided around the internal cylinder.
Thanks to the rigid piping, provided with joints enabling it to perform pivoting and bending movements in one plane and giving pa3~ages to a number of different currents of hydraulic and/or pneumatic fluid 30 ~ ~a simple and effective solu ~O~ heed problem caused by the entanglement of a large number of flexible tubes suspended around known types of drilling machines, as one \
0~
.
single piping system Ruffices to give passage to all the required currents of fluid.
~ This advantage is the more important as most of modern drilling machines necessitate several distinct pneumatic fluid lines. The drill, which, in fact, is a percussion drill is in certain types of machines equipped with means enabling the percussion mechanism to be actuated in both directions in order to facilitate the removal of the drilling tool from the taphole. In this type of machine an additional feed line is required for actuating the percussion mechanism in the direction of removal. Furthermore, if the percussion mechanism is sepa-rated from the drill mechanism a further pneumatic feed line is required. Besides the above possib~ities certain machines are equipped with a blower in order to remove the cuttings from the taphole during the drilling operation.
The articulated rigid piping can be mounted in two different ways, according to the space available. The method shown by 125 in Figure 26, in continuous and broken double lines, corresponds to a first arrangement, while the method shown by 125', in continuous and broken single lines, corres-ponds to a second arrangement for the piping.
Figure~ 31 to 35 show a second embodiment for feeding the pneumatic fluid to the drill 13.
Figure 31 shows a bar 11 bearing a drill 13, to actuate a drill bit 15, the machine being shown in full lines to the rear of the bar 11 and in broken lines when in the advanced position. ;the supply of hydraulic or pneumatic fluid to the drill 13 is effected via flexible conduit 236 which is unwound from a reel 240 as and when the drill 13 is fed forward. The reel 240 is mounted at ~._ l~ it;7 the rear end of the bar 11 and is subjected to the action of a spring which is not shown and which tends to cause the reel 240, in the example illustrated, to rotate anti-clockwise, in order to wind up the conduit 236 when the drill 13 is returning to the retractedposition shown in full lines.
A feed conduit 242 for hydraulic or pneumatic fluid communicates via the hub of -the reel 240 with the flexible conduit 236.
Instead of providing a spring to actuate the reel it is also possible to couple this latter to the traversing mechanism of the drill 13 in such a way that the reel is automatically rotated synchronously with the traversing movement of the drill 13.
Figure 33 shows a similar construction to that illus-trated in Figure 31 but with the drill 13 ' mounted above the bar 11. The reel 240~ is mounted, similarly to the reel 240, on the bar 11, but undergoes the action of a spring or of a traversing mechanism not shown in the drawing, in such a way as to cause it to rotate, in the example shown in Figure 33, in a clockwise direction, in order to wind up the conduit 236.
In Figure 32 the drill 13 ' is mounted in a similar manner to that shown in Figure 33. In the version illustrated in Figure 32 a reel 244 is provided, mounted on a suitable support 246 above the bar 11, the hydraulic or pneumatic fluid likewise being fed, via a feed conduit, through the hub of the reel 244.
Figures 31 - 33 show that the arrangement can be adapted to local circumstances and to the space available for a suitable assembly. ~he great advantage offered by the system in which conduits are wound onto a reel is the fact that the latter are always in place when the drill occupies its retracted position and are thus not inconveniently suspended below the ~ jt;7 bar 11 and possibly above the tap spout.
If two or more separate conduits for hydraulic or pneumatic fluid are required, it will then be possible to provide two reels for winding up each of the conduits and/or for winding up the two conduits side by side on the same reel.
Figure 34 which is a section along the line A-A of Figure 31, illustrates this last possibility. Two parallel conduits 242 and 242' for the feed of the fluid lead via the fixed shaft 250 of the hub 25~ of the reel ?40 into peripheral grooves 252 and 252' of the said hub 251. These peripheral grooves 252 and 252' communicate direct, via radial conduits 254 and 254', with the conduits 236 and 236' respectively.
The feed conduits 242 and 242' are thus constantly in communi-cation with the conduits 236 and 236', even in the event of the rotation of the hub 25~ in relation to the shaft 250.
A set of joints 256 isolates the peripheral grooves 252 and 252' both from the outside and from each .
It i8 obvious that in the case of one single flexible conduit per reel the system of supplying the fluid by rotary passage in the hub of the reel is analogous to the embodiment shown in Figure 34. If necessary, moreover, more than two conduits could be provided, by means of assemblies based on the same principles as those shown in the diagrams.
Instead of providi~g two parallel conduits 242 and 242' it will be possible to provide multiple conduits such as described with reference to Figures 28 - 30.
~igure 35 shows how pneumatic or hydraulic fluids are fed through the support column 19 ~he support column comprises a fixed internal cylinder 173 and an external cylinder 171 capable of pivoting ,~, ' lV90~7 about the internal cylinder, the external cylinder being integral with the stem 17.
the feed of the pneumatic or hydraulic fluid required for the operation of the drilling machine is effected through the internal cylinder 173 of the column. Three pipes 175, 177 and 179 have been shown by way of an example, although a still greater number of pipes could be installed if desired. Each of the pipes 175, 177 and 179 comprises a fixed lower section 175 ~ 177 ~
and 179' respectively and a movable upper section 175", 177"
and 179" respectively, the connection between the upper and lower sections being provided by swivels 185, 187 and 189 respectively. These swivels, wh1le ensuring hermeticity between the adjacent ends of the upper sections 175", 177" and 179"
and lower sections 175 ', 177 ' and 179 ', enable the upper sections to rotate in relation to the lower sections when the said upper sections follow the pivoting movement of the stem 17 about the fixed cylinder 173. These swivels 185, 187 and 189, needless to say, must be positioned on the rotation axis of the cylinder 171. This system of feeding and distri-buting the fluids via the interior of the support column form~ a valuable contribution to the reduction in the total height of the drilling machine, since the pneumatic fluid in existing systems was supplied and distributed above the support column, involving an unnecessary increase in the over-all height of the apparatus.
It should also be noted that the pipes 175, 177 and 179 may be of the single or multiple type, e.g. concentric, as shown in Figure 29, according to requirements.
~- .
Claims (25)
1. For use with a shaft furnace having a taphole and a molten metal flow channel in register with said taphole, a taphole drilling machine comprising a support column, a support arm rotatably mounted on said column for movement about an axis inclined to the vertical, a tool holder connected to said arm for movement therewith and operable to support a tool for boring said taphole, drive means operable upon said support arm to effect rotation of said support arm about said axis between a retracted position and a working position in which said tool holder is in register with said taphole, stop means associated with said drive means to prevent movement of said support arm beyond said working position and adjustment means to adjust said stop means relative to said support arm and thereby vary said working position relative to said taphole, said drive means including a fluid operated motor and control means to maintain pressurised fluid in said motor to oppose movement of said arm during drilling of said taphole.
2. A drilling machine as claimed in claim 1, wherein said axis is inclined toward said furnace.
3. A drilling machine as claimed in claim 2, wherein said axis is inclined to a vertical plane passing through said taphole.
4. A drilling machine as claimed in claim 1, wherein said tool holder is affixed to said support arm in a rigid manner.
5. A drilling machine as claimed in claim 4, wherein the connection between the tool holder and the support arm is adjust-able to vary the height of said tool holder relative to said taphole in said working position.
6. A drilling machine as claimed in claim 4, comprising at least one removable intermediate piece, for mounting between said support arm and said tool holder, each of said pieces forming a different angle with the longitudinal axis of the support arm when the pieces are mounted.
7. A drilling machine as claimed in any one of claims 1 to 3, wherein said tool holder is affixed to said support arm by an adjustable joint, said joint including two parallel links each of which is pivoted at one end to said support arm and at another end to a plate integral with said tool holder and an adjustable rod extending diagonally from said one end of one of said links to said other end of said other of said links.
8. A drilling machine as claimed in claim 1, further com-prising means enabling the angle of inclination of the tool holder in relation to the horizontal to be adjusted.
9. A drilling machine as claimed in claim 8, wherein said means consist of a pair of cheeks of complementary shapes, one of which is integral with said tool holder and the other of which is integral with the support arm and a collar firmly interconnecting said cheeks.
10. A drilling machine as claimed in claim 9, further comprising means for preventing the accidental pivoting movement of the tool holder and of its cheek when said collar is released.
11. A drilling machine as claimed in any one of claims 9 or 10, including a ring made of a material with a high co-efficient of friction, interposed between said cheeks of complementary shapes.
12. A drilling machine as claimed in claim 8, wherein said means consist of cheeks of complementary shapes, associated with said support arm and with said tool holder respectively and wherein the adjacent surfaces of each of said cheeks include a rim of radial corrugations extending in an axial direction, a securing means being provided for maintaining the engagement between said rims of radial corrugations.
13. A drilling machine as claimed in claim 12 wherein said cheek associated with said support arm is integral with the latter and comprises an axial screw-threaded extension passing through an axial bore of the cheek associated with said tool holder and accommodating a securing nut outside said cheek of said tool holder.
14. A drilling machine as claimed in claim 12 wherein the connection between the support arm and the cheek associated with it is provided by means of two fastenings, one of which constitutes an articulation point of the support arm in relation to its cheek and the other of which is adjustable.
15. A drilling machine as claimed in claim 14, wherein said other fastening is provided by a screw threaded rod flexibly connected to said tool holder and threadingly received in a guide pivotally connected to the cheek.
16. A drilling machine as claimed in claim 1 wherein said fluid motor means includes a piston reciprocally mounted within a cylinder and said stop means includes abutting walls of said piston and cylinder, said adjustment means being operable to adjust the length of said piston rod.
17. A drilling machine as claimed in claim 1 wherein said fluid motor means includes a piston reciprocally mounted within a cylinder and said stop means includes abutting walls of said piston and cylinder, said adjustment means being operable to vary the position of said cylinder relative to said support arm.
18. A drilling machine as claimed in claim 1 wherein said fluid motor includes a cylinder and a piston reciprocally mounted in said cylinder, said stop means including a flange integral with said cylinder and a tie rod mounted for movement with said piston, said adjustment means including a nut threaded on said tie rod and movable to vary said working position.
19. A drilling machine as claimed in claim 1 wherein said fluid motor means is fed via a rigid system of piping consisting of a number of branches capable of pivoting in a plane in relation to one another as a result of articulated joints interconnecting the adjacent ends of two adjacent branches.
20. A drilling machine as claimed in claim 19 wherein the system of piping comprises an outer pipe and one or more inner pipes, to enable more than one flow of different fluids to be conveyed.
21. A drilling machine as claimed in claim 1 wherein said fluid motor means is fed through flexible conduits which are unwound from a reel supported by said tool holder during advance of a tool supported on said tool holder, and which are then wound onto the said reel during the return movement of the operating tool, the feed of fluid into these conduits being effected via rotatory passages in the hub of the reel.
22. A drilling machine as claimed in claim 21, comprising several flexible conduits to feed the hydraulic or pneumatic fluid to the operating tool, these conduits being wound side by side onto the same reel.
23. A drilling machine as claimed in claim 22, wherein the feed of the fluid into the rotatory passage of the hub of the reel is effected via separate conduits.
24. A drilling machine as claimed in claim 23, wherein the feed of fluid into the rotatory passages of the hub of the reel is effected via multiple conduits positioned one inside the other or others.
25. A drilling machine as claimed in any one of claims 19 or 20 wherein the support column is hollow and contains swivels positioned axially and ensuring hermeticity and also rotatability between upper sections and lower sections of the piping serving to feed hydraulic or pneumatic fluid through the support column.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| LU74398A LU74398A1 (en) | 1976-02-20 | 1976-02-20 | |
| LU74,398 | 1976-02-20 | ||
| LU76348A LU76348A1 (en) | 1976-12-08 | 1976-12-08 | |
| LU76,348 | 1976-12-08 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1090567A true CA1090567A (en) | 1980-12-02 |
Family
ID=26640193
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA272,134A Expired CA1090567A (en) | 1976-02-20 | 1977-02-18 | Drilling machine for blast furnace tapholes |
Country Status (11)
| Country | Link |
|---|---|
| JP (1) | JPS52105503A (en) |
| AU (1) | AU510166B2 (en) |
| BR (1) | BR7701109A (en) |
| CA (1) | CA1090567A (en) |
| CS (1) | CS208195B2 (en) |
| DE (1) | DE2704891A1 (en) |
| ES (1) | ES456007A1 (en) |
| FR (1) | FR2341651A1 (en) |
| GB (1) | GB1525088A (en) |
| IT (1) | IT1078078B (en) |
| PL (1) | PL107929B1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| LU78209A1 (en) * | 1977-09-30 | 1978-01-23 | ||
| LU78756A1 (en) * | 1977-12-22 | 1978-04-17 | ||
| LU79749A1 (en) * | 1978-06-01 | 1978-11-28 | Wurth Paul Sa | MECHANISM FOR GUIDING AND POSITIONING THE WORKING TOOL OF A DRILLING MACHINE OR CLOSING THE CASTING HOLE OF A TANK OVEN |
| LU82942A1 (en) * | 1980-11-17 | 1982-06-30 | Wurth Anciens Ets Paul | SYSTEM OF MODULAR ELEMENTS FOR PROVIDING PIVOTING CONNECTIONS ARTICULATED ARM CONSISTING OF SUCH ELEMENTS AND APPLICATION TO A TAPER DRILLER OF A TANK OVEN |
| JPH04371508A (en) * | 1991-06-17 | 1992-12-24 | Nippon Steel Corp | Hole opening machine for iron tapping hole |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE437206C (en) * | 1926-05-05 | 1926-11-16 | Ag Deutsche Maschf | Device for parting blast furnaces |
| DE1231272B (en) * | 1959-04-21 | 1966-12-29 | Dango & Dienenthal Kommanditge | Method and device for opening the tap hole of shaft ovens, in particular blast furnaces, by drilling |
| FR1308811A (en) * | 1961-10-28 | 1962-11-09 | Westinghouse Air Brake Co | Blast furnace installation and casting method |
| DE1243219B (en) * | 1964-08-17 | 1967-06-29 | Dango & Dienenthal K G | Tap hole drilling machine |
| FR1587346A (en) * | 1968-02-15 | 1970-03-20 | ||
| GB1301236A (en) * | 1970-07-18 | 1972-12-29 | ||
| LU69766A1 (en) * | 1974-04-02 | 1976-03-17 |
-
1977
- 1977-02-05 DE DE19772704891 patent/DE2704891A1/en active Pending
- 1977-02-10 GB GB559777A patent/GB1525088A/en not_active Expired
- 1977-02-17 CS CS104877A patent/CS208195B2/en unknown
- 1977-02-17 ES ES456007A patent/ES456007A1/en not_active Expired
- 1977-02-18 FR FR7704743A patent/FR2341651A1/en active Granted
- 1977-02-18 IT IT2046177A patent/IT1078078B/en active
- 1977-02-18 JP JP1769577A patent/JPS52105503A/en active Pending
- 1977-02-18 BR BR7701109A patent/BR7701109A/en unknown
- 1977-02-18 AU AU22462/77A patent/AU510166B2/en not_active Expired
- 1977-02-18 CA CA272,134A patent/CA1090567A/en not_active Expired
- 1977-02-19 PL PL19612577A patent/PL107929B1/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| CS208195B2 (en) | 1981-08-31 |
| FR2341651A1 (en) | 1977-09-16 |
| GB1525088A (en) | 1978-09-20 |
| JPS52105503A (en) | 1977-09-05 |
| IT1078078B (en) | 1985-05-08 |
| AU510166B2 (en) | 1980-06-12 |
| ES456007A1 (en) | 1978-02-01 |
| DE2704891A1 (en) | 1977-08-25 |
| FR2341651B1 (en) | 1980-07-11 |
| AU2246277A (en) | 1978-08-24 |
| BR7701109A (en) | 1977-12-13 |
| PL107929B1 (en) | 1980-03-31 |
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Legal Events
| Date | Code | Title | Description |
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| MKEX | Expiry |