EP0028593B1 - Device to preclude physical contact between the cutter boom and the gathering arm of a cutting machine - Google Patents

Device to preclude physical contact between the cutter boom and the gathering arm of a cutting machine Download PDF

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Publication number
EP0028593B1
EP0028593B1 EP80890126A EP80890126A EP0028593B1 EP 0028593 B1 EP0028593 B1 EP 0028593B1 EP 80890126 A EP80890126 A EP 80890126A EP 80890126 A EP80890126 A EP 80890126A EP 0028593 B1 EP0028593 B1 EP 0028593B1
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EP
European Patent Office
Prior art keywords
piston
cutting
loading ramp
boom
hydraulic
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Expired
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EP80890126A
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German (de)
French (fr)
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EP0028593A1 (en
Inventor
Erich Dröscher
Hans Peter Pfundner
Herwig Wrulich
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Voestalpine AG
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Voestalpine AG
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Publication of EP0028593A1 publication Critical patent/EP0028593A1/en
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    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21C—MINING OR QUARRYING
    • E21C35/00—Details of, or accessories for, machines for slitting or completely freeing the mineral from the seam, not provided for in groups E21C25/00 - E21C33/00, E21C37/00 or E21C39/00
    • E21C35/20—General features of equipment for removal of chippings, e.g. for loading on conveyor
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21C—MINING OR QUARRYING
    • E21C27/00—Machines which completely free the mineral from the seam
    • E21C27/20—Mineral freed by means not involving slitting
    • E21C27/24—Mineral freed by means not involving slitting by milling means acting on the full working face, i.e. the rotary axis of the tool carrier being substantially parallel to the working face
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21C—MINING OR QUARRYING
    • E21C35/00—Details of, or accessories for, machines for slitting or completely freeing the mineral from the seam, not provided for in groups E21C25/00 - E21C33/00, E21C37/00 or E21C39/00
    • E21C35/04—Safety devices

Definitions

  • the invention relates to a device for preventing a collision between a part of the cutting arm and a part of the loading ramp in a cutting machine with a at least one cutting head-supporting cutting arm pivotable about at least one horizontal axis and a lifting and lowering loading ramp arranged below the cutting arm.
  • the cutting arm is usually pivoted on all sides and the loading ramp is usually pivoted on the frame of the cutting machine about a horizontal axis. If the cutting arm is pivoted downwards and / or the loading ramp is raised, there is a risk of a collision between the cutting arm and the loading ramp.
  • the loading ramp usually has movable loading arms which continuously push the cut material on the loading ramp upwards to a conveying device.
  • the invention has for its object to provide a device by means of which collisions between the cutter arm and loading ramp are avoided without the loading area of the loading ramp being impaired and which in a simple manner and with the avoidance of stops on the cutter arm and on the loading ramp to the given conditions can be customized.
  • the invention consists essentially in the fact that for the cutting arm there is provided a transmitter device registering the position thereof relative to the cutting machine and for the loading ramp a transmitter device registering the position thereof relative to the cutting machine and that the two transmitter devices are connected to a common receiver device, which in Depending on a combination of the signals of the two transmitter devices, a control element which interrupts the downward movement of the cutting arm and the upward movement of the loading ramp controls.
  • the device according to the invention responds to a dangerous approach of the cutting arm to the loading ramp, regardless of whether this approach by lowering the Low-cutting or by lifting the loading ramp or by both movements.
  • the transmitter devices are formed by hydraulic cylinder-piston units, one part of which is connected to part of the cutting machine and the other part of which engages the loading ramp or the cutting arm, at least in the lower region of the pivoting thereof, the working spaces of the two cylinder-piston units, which become smaller during the downward movement of the cutting arm or the upward movement of the loading ramp, are connected to the working space of a hydraulic cylinder-piston unit forming the receiver device, with the piston of which the control element for the lower part Refraction of the movements of the cutter arm and loading ramp is connected.
  • the receiver device becomes dependent on the sum of the mutually directed movements of the cutting arm and loading ramp controlled, and this sum of the movements directed towards each other is decisive for the respective collision position. It is only necessary that the quantity of hydraulic medium pressed into this common working space corresponds to the path of the corresponding part, cutting arm and loading ramp. With the same kinematics of the points of attack of the two cylinder-piston units, the piston cross sections can be the same. However, the piston cross section and the articulation kinematics can also be different when registering the movements of the cutting arm and the loading ramp. It is only relevant that the quantities of the hydraulic medium pressed into the working space of the piston of the receiver device during the movement of these two parts are proportional to the movement.
  • the working spaces of the hydraulic cylinder-piston units and of the cylinder-piston unit forming the receiver device are filled with an empirically determined amount of a hydraulic medium, in particular grease.
  • a hydraulic medium in particular grease.
  • the use of grease as a hydraulic medium has the advantage of simplifying the seals.
  • the extent of the amount of hydraulic medium filled can be set empirically in a simple manner in such a way that the cutting arm and loading ramp are brought into a position just before the collision and then the relevant working spaces are filled with the hydraulic medium.
  • the swiveling mechanism of the cutting arm can be increased. This increase can be up to 800 mm or more. Due to the extent of the filling, this increase can be taken into account in a simple manner, so that the setting of the device preventing the collision is extremely simple when the swivel mechanism is increased.
  • the arrangement is preferably such that the transmitter device or the cylinder-piston unit assigned to the cutting arm is attached on the one hand to a part of the cutting machine and on the other hand only engages non-positively with a part of the cutting arm by a stop, the stop only taking effect.
  • the cutter arm is in the lower half of the vertical swivel range.
  • the cutting arm makes a relatively large pivoting movement in the vertical direction and only in the lower part of this pivoting area is there a risk of a collision.
  • the loading ramp on the other hand, carries out a relatively small swiveling movement in the vertical direction and there is a risk of collision in all swiveling positions of the loading ramp.
  • the pivoting path controlled by the encoder device can be kept approximately the same as the pivoting path of the loading ramp, so that these pivoting paths can be easily summed up.
  • the switching element is preferably formed by a piston slide with control recesses which simultaneously connect the hydraulic lines which cause the lowering of the cutting arm and the lifting of the loading ramp to a return line.
  • the piston slide is expediently connected to the hydraulic piston of the receiver device coaxially or consists of one piece with it.
  • Fig. 1 shows a cutting machine.
  • Fig. 2 shows the arrangement of the hydraulic cylinder-piston units forming the transmitter devices and the piston forming the receiver device.
  • Fig. 3 shows the hydraulic piston forming the receiver device with the control slide.
  • the cutting arm 1 is articulated on the cutting machine 3 so that it can be raised and lowered about the horizontal axis 2.
  • the loading ramp 4 '5 pivotably articulated about a horizontal axis at the cutting machine.
  • the cutter arm is pivoted about the axis 2 by means of a cylinder-piston unit 6, which is articulated at 7 on the cutter arm 1. Furthermore, the cutting arm 1 can be pivoted laterally about a vertical axis 8.
  • An encoder device 11 formed by a hydraulic cylinder-piston unit is assigned to the cutting arm, and an encoder device 12 formed by a hydraulic cylinder-piston unit is assigned to the loading ramp. These transmitter devices are shown on a larger scale in FIG. 2.
  • the transmitter device 11 consists of a cylinder-piston unit, the cylinder of which is designated by '1'3 and the piston of which is designated by 14.
  • the cylinder 13 is fixed to a part connected to the cutting machine, as indicated by 15.
  • the cutting arm 1 has a stop 1 ' 6, on which the piston rod 17 of the piston 14 engages.
  • the piston 14 is pressed in the direction of the stop 16 by a spring 18.
  • the path of the piston 14 is limited so that the piston rod 17 only in the bottom Ren part of the vertical swivel stroke of the cutting arm reaches the stop 16.
  • the hydraulic cylinder 9, which is articulated at 10 on the loading ramp 4, is fixed on the cutting machine.
  • the cylinder 19 of the cylinder-piston unit forming the transmitter device 12 is fixed on the cylinder 9 and thus also on the cutting machine itself.
  • the piston rod 20 of the cylinder-piston unit 12 is firmly connected to the eye 21 of the piston rod 22 of the cylinder of the cylinder-piston unit 9 acting on the loading ramp by means of a part 23 welded to this eye 21. No spring loading is therefore required here.
  • the piston chamber 24 of the cylinder-piston unit 11 shrinks and presses hydraulic medium, for example grease, via a line 25, '26 into the working chamber 27 of a cylinder-piston unit 28 which forms the receiver device
  • hydraulic medium for example grease
  • the working space 29 of the piston 21 of the cylinder-piston unit 12 is reduced, which represents the transmitter device assigned to the loading ramp.
  • the hydraulic medium is also pressed via the line 30, 26 into the working space 27 of the cylinder-piston unit forming the receiver device.
  • Hydraulic medium is thus pressed into the working space 27 when the cutter arm 1 is lowered and the loading ramp 4 is raised, and the piston 31 of the cylinder-piston unit 28 forming the receiver device is pressed to the right by the sum of the volumes of these displaced hydraulic media.
  • the movement of the piston 31 to the right is thus shifted to the right both as a function of the lowering movement of the cutting arm and as a function of the upward movement of the loading ramp and when the sum of the volumes of these media displaced from the cylinder-piston units 11 and 12 reached a dimension at which the cutting arm and loading ramp approach each other to a dangerous extent, the piston 31 interrupts the downward movement of the cutting arm and the upward movement of the loading ramp.
  • the relevant arrangement is shown in Fig. 3.
  • the piston 31 is pressed to the left by a spring 32.
  • the line 26 opens into the working space 27 of this piston via a connection 33.
  • a control slide 34 is connected to the piston 31 and is displaceable in a slide mirror 35.
  • the control opening 36 is connected to the hydraulic line which causes the cutting arm 1 to be lowered.
  • the control opening 37 is connected to the hydraulic line which causes the loading ramp 4 to be raised.
  • the control opening 38 is connected to a return.
  • the control slide 34 has control grooves 39 and 40, which are connected via radial bores 41 and 42 to a central bore 43 of the control slide 34.
  • control recesses 39, 40 open the control recesses 36 and 37, these control recesses pass through the control grooves 39, 40, the bores 41 and 42 and the central bore 43 in connection with the control recess 38.
  • Hydraulic lines causing the loading ramp are connected to the return flow via the control recess 38 and the lowering movement of the cutting arm and at the same time also the lifting movement of the loading ramp is interrupted, so that a collision is avoided.

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  • Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Geology (AREA)
  • Manipulator (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Component Parts Of Construction Machinery (AREA)
  • Earth Drilling (AREA)
  • Excavating Of Shafts Or Tunnels (AREA)

Description

Die Erfindung bezieht sich auf eine Einrichtung zur Verhinderung einer Kollision zwischen einem Teil des Schrämarmes und einem Teil der Laderampe bei einer Schrämmaschine mit einem wenigstens einen Schrämkopf tragenden um zumindest eine horizontale Achse schwenkbaren Schrämarm und einer unterhalb des Schrämarmes angeordneten heb- und senkbaren Laderampe. Bei solchen Schrämmaschinen ist üblicherweise der Schrämarm allseitig schwenkbar gelagert und die Laderampe ist üblicherweise am Rahmen der Schrämmaschine um eine horizontale Achse schwenkbar angelenkt. Wenn nun der Schrämarm abwärts verschwenkt wird und/oder die Laderampe angehoben wird, so besteht die Gefahr einer Kollision zwischen Schrämarm und Laderampe. Üblicherweise weist die Laderampe bewegliche Ladearme auf, welche kontinuierlich das geschrämte Material auf der Laderampe aufwärts zu einer Fördereinrichtung schieben. Wenn der Schrämarm mit diesen Ladearmen kollidiert, so ist die Gefahr einer Beschädigung besonders gross. Um eine solche Kollision des Schrämarmes mit empfindlichen Teilen, beispielsweise mit den beweglichen Ladearmen zu vermeiden, ist es bekannt (vgl. DE-A-2 639 582), an Schrämarm und Laderampe Anschläge vorzusehen, deren Höhe so bemessen ist, dass eine Berührung zwischen Schrämarm und Ladearmen in allen Schwenkstellungen vermieden ist. Hiebei müssen diese Anschläge die volle Kraft des Verschwenkmechanismus aufnehmen und um dies zu vermeiden, wurde auch bereits vorgeschlagen (vgl. DE-A-2 719 595), einen der Anschläge beweglich auszubilden und durch diesen beweglichen Anschlag ein Steuerventil zu betätigen, welches die hydraulische Leitung, welche beim Abwärtsschwenken des Schrämarmes unter Druck gesetzt wird und die hydraulische Leitung, welche beim Hochschwenken der Laderampe unter Druck gesetzt wird, mit einem Rückfluss verbindet, so dass die Schwenkbewegung von Schrämarm und Laderampe gestoppt wird. In allen Fällen aber sind Anschläge auf der Fläche der Laderampe erforderlich und diese Anschläge müssen so breit bemessen sein, dass sie bei allen Seitenschwenkstellungen des Schrämarmes zur Wirkung gelangen. Diese Anschläge bilden daher Hindernisse auf der Oberfläche der Laderampe, mit welchen wieder das geförderte Material kollidieren kann. Wenn durch diese Anschläge grössere Teile des geförderten Materials auf der Laderampe zurückgehalten werden, so besteht wieder die Gefahr, dass solche Gesteinsstücke mit den Anschlägen des Schrämarmes in Berührung gelangen und damit der Antrieb von Schrämarm und Laderampe in einer ungewünschten Stellung bereits ausgeschaltet wird. Es gibt auch die Möglichkeit, das Schwenkwerk des Schrämarmes zu erhöhen und den Schrämarm zu verlängern, um grössere Flächen schrämen zu können. In diesem Fall bieten sich bereits grosse Schwierigkeiten, Kollisionen durch auf der Laderampe und am Schrämarm angeordnete Anschläge zu verhindern. Es müssten dann die Anschläge ausgetauscht werden, was einen erheblichen Arbeitsaufwand erfordert, und diese Anschläge müssen übermässig hoch bemessen werden, wodurch wieder Störungen entstehen.The invention relates to a device for preventing a collision between a part of the cutting arm and a part of the loading ramp in a cutting machine with a at least one cutting head-supporting cutting arm pivotable about at least one horizontal axis and a lifting and lowering loading ramp arranged below the cutting arm. In such cutting machines, the cutting arm is usually pivoted on all sides and the loading ramp is usually pivoted on the frame of the cutting machine about a horizontal axis. If the cutting arm is pivoted downwards and / or the loading ramp is raised, there is a risk of a collision between the cutting arm and the loading ramp. The loading ramp usually has movable loading arms which continuously push the cut material on the loading ramp upwards to a conveying device. If the cutter arm collides with these loading arms, the risk of damage is particularly great. In order to avoid such a collision of the cutter arm with sensitive parts, for example with the movable loading arms, it is known (cf. DE-A-2 639 582) to provide stops on the cutter arm and loading ramp, the height of which is dimensioned such that a contact between Cutting arm and loading arms in all swivel positions is avoided. Hiebei these stops must absorb the full force of the pivoting mechanism and in order to avoid this, it has already been proposed (cf. DE-A-2 719 595) to design one of the stops to be movable and to actuate a control valve by this movable stop, which controls the hydraulic Pipe which is pressurized when swiveling the cutter arm down and connects the hydraulic line which is pressurized when swiveling the loading ramp up with a return flow, so that the swiveling movement of the cutter arm and loading ramp is stopped. In all cases, however, stops on the surface of the loading ramp are required and these stops must be dimensioned so wide that they come into effect in all side pivot positions of the cutting arm. These stops therefore form obstacles on the surface of the loading ramp, with which the conveyed material can collide again. If larger parts of the conveyed material are held back on the loading ramp by these stops, there is again the risk that such rock pieces come into contact with the stops of the cutting arm and thus the drive of the cutting arm and loading ramp is already switched off in an undesired position. There is also the possibility of increasing the swiveling mechanism of the cutting arm and lengthening the cutting arm in order to be able to cut larger areas. In this case, there are already great difficulties in preventing collisions due to stops arranged on the loading ramp and on the cutting arm. The stops would then have to be replaced, which requires a considerable amount of work, and these stops have to be dimensioned excessively high, as a result of which faults occur again.

Die Erfindung stellt sich zur Aufgabe, eine Einrichtung zu schaffen, durch welche Kollisionen zwischen Schrämarm und Laderampe vermieden werden, ohne dass die Ladefläche der Laderampe beeinträchtigt wird und welche in einfacher Weise und unter Vermeidung von Anschlägen am Schrämarm und an der Laderampe an die gegebenen Verhältnisse angepasst werden können. Die Erfindung besteht hiebei im wesentlichen darin, dass für den Schrämarm eine die Position desselben relativ zur Schrämmaschine registrierende Gebereinrichtung und für die Laderampe eine die Position derselben relativ zur Schrämmaschine registrierende Gebereinrichtung vorgesehen ist und dass die beiden Gebereinrichtungen mit einer gemeinsamen Empfängereinrichtung verbunden sind, welche in Abhängigkeit von einer Kombination der Signale der beiden Gebereinrichtungen ein die Abwärtsbewegung des Schrämarmes und die Aufwärtsbewegung der Laderampe unterbrechendes Steuerorgan steuert. Auf diese Weise werden Anschläge am Schrämarm und mit diesem zusammenwirkende Anschläge auf der Laderampe vermieden, so dass die Fläche der Laderampe nicht beeinträchtigt wird. Dadurch, dass die beiden Gebereinrichtungen mit einer gemeinsamen Empfängereinrichtung verbunden sind und in dieser Empfängereinrichtung die Signale der Anzeigen der beiden Gebereinrichtungen kombiniert werden, spricht die erfindungsgemässe Einrichtung bei einer gefährlichen Annäherung des Schrämarmes an die Laderampe an, unabhängig davon, ob diese Annäherung durch Absenken des Schrämarmes oder durch Anheben der Laderampe bzw. durch beide Bewegungen bewirkt wird.The invention has for its object to provide a device by means of which collisions between the cutter arm and loading ramp are avoided without the loading area of the loading ramp being impaired and which in a simple manner and with the avoidance of stops on the cutter arm and on the loading ramp to the given conditions can be customized. The invention consists essentially in the fact that for the cutting arm there is provided a transmitter device registering the position thereof relative to the cutting machine and for the loading ramp a transmitter device registering the position thereof relative to the cutting machine and that the two transmitter devices are connected to a common receiver device, which in Depending on a combination of the signals of the two transmitter devices, a control element which interrupts the downward movement of the cutting arm and the upward movement of the loading ramp controls. In this way, stops on the cutting arm and stops cooperating with it on the loading ramp are avoided, so that the area of the loading ramp is not impaired. Due to the fact that the two transmitter devices are connected to a common receiver device and the signals of the displays of the two transmitter devices are combined in this receiver device, the device according to the invention responds to a dangerous approach of the cutting arm to the loading ramp, regardless of whether this approach by lowering the Low-cutting or by lifting the loading ramp or by both movements.

Gemäss einer bevorzugten Ausführungsform der Erfindung sind die Gebereinrichtungen von hydraulischen Zylinder-Kolben-Aggregaten gebildet, deren einer Teil mit einem Teil der Schrämmaschine verbunden ist und deren anderer Teil an der Laderampe bzw. am Schrämarm, zumindest im unteren Bereich der Verschwenkung desselben, angreift, wobei die sich bei der Abwärtsbewegung des Schrämarmes bzw. bei der Aufwärtsbewegung der Laderampe verkleinernden Arbeitsräume der beiden Zylinder-Kolben-Aggregate mit dem Arbeitsraum eines die Empfängereinrichtung bildenden hydraulischen Zylinder-Kolben-Aggregats verbunden sind, mit dessen Kolben das Steuerorgan für die Unterbrechung der Bewegungen von Schrämarm und Laderampe verbunden ist. Dadurch, dass aus den die beiden Gebereinrichtungen bildenden Zylinder-Kolben-Aggregaten das hydraulische Medium in einen gemeinsamen Raum, nämlich in den Arbeitsraum des die Empfängereinrichtung bildenden hydraulischen Kolbens gedrückt wird, wird die Empfängereinrichtung in Abhängigkeit von der Summe der zueinandergerichteten Bewegungen von Schrämarm und Laderampe gesteuert, und diese Summe der zueinandergerichteten Bewegungen ist ausschlaggebend für die jeweilige Kollisionsstellung. Es ist lediglich erforderlich, dass die in diesen gemeinsamen Arbeitsraum gedrückte Menge des hydraulischen Mediums dem Weg des entsprechenden Teiles Schrämarm und Laderampe entspricht. Bei gleicher Kinematik der Angriffsstellen der beiden Zylinder-Kolben-Aggregate können die Kolbenquerschnitte gleich sein. Es kann aber auch der Kolbenquerschnitt und die Anlenkkinematik bei der Registrierung der Bewegungen des Schrämarmes und der Laderampe verschieden sein. Massgebend ist nur, dass die bei der Bewegung dieser beiden Teile in den Arbeitsraum des Kolbens der Empfängereinrichtung gedrückten Mengen des hydraulischen Mediums der Bewegung proportional sind.According to a preferred embodiment of the invention, the transmitter devices are formed by hydraulic cylinder-piston units, one part of which is connected to part of the cutting machine and the other part of which engages the loading ramp or the cutting arm, at least in the lower region of the pivoting thereof, the working spaces of the two cylinder-piston units, which become smaller during the downward movement of the cutting arm or the upward movement of the loading ramp, are connected to the working space of a hydraulic cylinder-piston unit forming the receiver device, with the piston of which the control element for the lower part Refraction of the movements of the cutter arm and loading ramp is connected. Characterized in that the hydraulic medium is pressed into a common space, namely into the working space of the hydraulic piston forming the receiver device, from the cylinder-piston units forming the two transmitter devices, the receiver device becomes dependent on the sum of the mutually directed movements of the cutting arm and loading ramp controlled, and this sum of the movements directed towards each other is decisive for the respective collision position. It is only necessary that the quantity of hydraulic medium pressed into this common working space corresponds to the path of the corresponding part, cutting arm and loading ramp. With the same kinematics of the points of attack of the two cylinder-piston units, the piston cross sections can be the same. However, the piston cross section and the articulation kinematics can also be different when registering the movements of the cutting arm and the loading ramp. It is only relevant that the quantities of the hydraulic medium pressed into the working space of the piston of the receiver device during the movement of these two parts are proportional to the movement.

Gemäss der Erfindung sind die Arbeitsräume der hydraulischen Zylinder-Kolben-Aggregate und des die Empfängereinrichtung bildenden Zylinder-Kolben-Aggregats mit einer empirisch bestimmten Menge eines hydraulischen Mediums, insbesondere Fett, gefüllt. Die Verwendung von Fett als hydraulisches Medium hat hiebei den Vorteil einer Vereinfachung der Dichtungen. Das Ausmass der eingefüllten Menge des hydraulischen Mediums kann in einfacher Weise empirisch so eingestellt werden, dass Schrämarm und Laderampe in eine Stellung knapp vor der Kollision gebracht werden und dann die betreffenden Arbeitsräume mit dem hydraulischen Medium gefüllt werden. Das Schwenkwerk des Schrämarmes kann, wie bereits erwähnt, erhöht werden. Diese Erhöhung kann bis zu 800 mm oder darüber betragen. Durch das Ausmass der Füllung kann dieser Erhöhung in einfacher Weise Rechnung getragen werden, so dass die Einstellung der die Kollision verhindernden Einrichtung bei einer Erhöhung des Schwenkwerkes äusserst einfach ist.According to the invention, the working spaces of the hydraulic cylinder-piston units and of the cylinder-piston unit forming the receiver device are filled with an empirically determined amount of a hydraulic medium, in particular grease. The use of grease as a hydraulic medium has the advantage of simplifying the seals. The extent of the amount of hydraulic medium filled can be set empirically in a simple manner in such a way that the cutting arm and loading ramp are brought into a position just before the collision and then the relevant working spaces are filled with the hydraulic medium. As already mentioned, the swiveling mechanism of the cutting arm can be increased. This increase can be up to 800 mm or more. Due to the extent of the filling, this increase can be taken into account in a simple manner, so that the setting of the device preventing the collision is extremely simple when the swivel mechanism is increased.

Vorzugsweise ist die Anordnung so getroffen, dass die dem Schrämarm zugeordnete Gebereinrichtung bzw. das Zylinder-Kolben-Aggregat einerseits an einem Teil der Schrämmaschine befestigt ist und anderseits mit einem Teil des Schrämarmes lediglich kraftschlüssig durch Anschlag angreift, wobei der Anschlag erst zur Wirkung gelangt, wenn sich der Schrämarm in der unteren Hälfte des vertikalen Verschwenkbereiches befindet. Der Schrämarm macht eine verhältnismässig grosse Verschwenkbewegung in der Höhenrichtung und erst im unteren Teil dieses Verschwenkbereiches ist die Gefahr einer Kollision gegeben. Die Laderampe hingegen führt eine verhältnismässig geringe Schwenkbewegung in der Höhenrichtung aus und in allen Schwenklagen der Laderampe ist die Kollisions- gefahr gegeben. Dadurch, dass die dem Schrämarm zugeordnete Gebereinrichtung erst im unteren Bereich des vertikalen Verschwenkweges des Schrämarmes zur Wirkung gelangt, kann der durch die Gebereinrichtung kontrollierte Verschwenkweg ungefähr gleich mit dem Verschwenkweg der Laderampe gehalten werden, so dass diese Verschwenkwege ohne weiteres summiert werden können.The arrangement is preferably such that the transmitter device or the cylinder-piston unit assigned to the cutting arm is attached on the one hand to a part of the cutting machine and on the other hand only engages non-positively with a part of the cutting arm by a stop, the stop only taking effect. when the cutter arm is in the lower half of the vertical swivel range. The cutting arm makes a relatively large pivoting movement in the vertical direction and only in the lower part of this pivoting area is there a risk of a collision. The loading ramp, on the other hand, carries out a relatively small swiveling movement in the vertical direction and there is a risk of collision in all swiveling positions of the loading ramp. Because the encoder device assigned to the cutting arm only comes into effect in the lower region of the vertical pivoting path of the cutting arm, the pivoting path controlled by the encoder device can be kept approximately the same as the pivoting path of the loading ramp, so that these pivoting paths can be easily summed up.

Bei hydraulischem Antrieb der Bewegung von Schrämarm und Laderampe ist das Schaltorgan vorzugsweise von einem Kolbenschieber mit Steuerausnehmungen gebildet, welche gleichzeitig die Verbindung der das Senken des Schrämarmes und das Heben der Laderampe bewirkenden hydraulischen Leitungen mit einer Rücklaufleitung herstellen. Hiebei ist zweckmässig der Kolbenschieber mit dem hydraulischen Kolben der Empfängereinrichtung gleichachsig verbunden oder besteht mit diesem aus einem Stück.When the movement of the cutting arm and loading ramp is hydraulically driven, the switching element is preferably formed by a piston slide with control recesses which simultaneously connect the hydraulic lines which cause the lowering of the cutting arm and the lifting of the loading ramp to a return line. The piston slide is expediently connected to the hydraulic piston of the receiver device coaxially or consists of one piece with it.

In der Zeichnung ist die Erfindung anhand eines Ausführungsbeispieles schematisch erläutert.In the drawing, the invention is explained schematically using an exemplary embodiment.

Fig.,1 zeigt eine Schrämmaschine. 'Fig. 2 zeigt die Anordnung der die Gebereinrichtungen bildenden hydraulischen Zylinder-Kolben-Aggregate und des die Empfängereinrichtung bildenden Kolbens. Fig. 3 zeigt den die Empfängereinrichtung bildenden hydraulischen Kolben mit dem Steuerschieber.Fig., 1 shows a cutting machine. 'Fig. 2 shows the arrangement of the hydraulic cylinder-piston units forming the transmitter devices and the piston forming the receiver device. Fig. 3 shows the hydraulic piston forming the receiver device with the control slide.

'Der Schrämarm 1 ist um die horizontale Achse 2 heb- und senkbar an der Schrämmaschine 3 angelenkt. Die Laderampe 4 ist um eine horizontale Achse '5 schwenkbar an der Schrämmaschine 3 angelenkt. Mittels eines Zylinder-Kolben-Aggregates '6, welches bei 7 am Schrämarm 1 angelenkt ist, wird der Schrämarm um die Achse 2 verschwenkt. Des weiteren ist der Schrämarm 1 um eine vertikale Achse 8 seitlich verschwenkbar. Ein hydraulisches Zylinder-Kolben-Aggregat9, welches bei 10 an der Laderampe 4 angreift, dient zur Verschwenkung der Laderampe 4 in der Höhenrichtung. ' The cutting arm 1 is articulated on the cutting machine 3 so that it can be raised and lowered about the horizontal axis 2. The loading ramp 4 '5 pivotably articulated about a horizontal axis at the cutting machine. 3 The cutter arm is pivoted about the axis 2 by means of a cylinder-piston unit 6, which is articulated at 7 on the cutter arm 1. Furthermore, the cutting arm 1 can be pivoted laterally about a vertical axis 8. A hydraulic cylinder-piston unit 9, which acts on the loading ramp 4 at 10, serves to pivot the loading ramp 4 in the vertical direction.

Dem Schrämarm ist eine von einem hydraulischen Zylinder-Kolben-Aggregat gebildete Gebereinrichtung 11 zugeordnet, und der Laderampe ist eine von einem hydraulischen Zylinder-Kolben-Aggregat gebildete Gebereinrichtung 12 zugeordnet. Diese Gebereinrichtungen sind in Fig. 2 in grösserem Massstab dargestellt.An encoder device 11 formed by a hydraulic cylinder-piston unit is assigned to the cutting arm, and an encoder device 12 formed by a hydraulic cylinder-piston unit is assigned to the loading ramp. These transmitter devices are shown on a larger scale in FIG. 2.

Die Gebereinrichtung 11 besteht aus einem Zylinder-Kolben-Aggregat, dessen Zylinder mit'1'3 und dessen Kolben mit 14 bezeichnet ist. Der Zylinder 13 ist an einem mit der Schrämmaschine verbundenen Teil festgelegt, wie dies durch 15 angedeutet ist. Der Schrämarm 1 weist einen Anschlag 1'6 auf, an welchen die Kolbenstange 17 des Kolbens 14 angreift. Durch eine Feder 18 wird der Kolben 14 in Richtung zum Anschlag 1'6 gedrückt. Der Weg des Kolbens 14 ist so begrenzt, dass die Kolbenstange 17 erst im unteren Teil des vertikalen Schwenkhubes des Schrämarmes an den Anschlag 16 gelangt. Der hydraulische Zylinder 9, welcher bei 10 an die Laderampe 4 angelenkt ist, ist an der Schrämmaschine festgelegt. Der Zylinder 19 des die Gebereinrichtung 12 bildenden Zylinder-Kolben-Aggregates ist am Zylinder 9 und damit auch an der Schrämmaschine selbst festgelegt. Die Kolbenstange 20 des Zylinder-Kolben-Aggregates 12 ist mit dem an der Laderampe angreifenden Auge 21 der Kolbenstange 22 des Zylinders des Zylinder-Kolben-Aggregates 9 unter Vermittlung eines an dieses Auge 21 angeschweissten Teiies 23 fest verbunden. Es ist daher hier keine Federbelastung erforderlich.The transmitter device 11 consists of a cylinder-piston unit, the cylinder of which is designated by '1'3 and the piston of which is designated by 14. The cylinder 13 is fixed to a part connected to the cutting machine, as indicated by 15. The cutting arm 1 has a stop 1 ' 6, on which the piston rod 17 of the piston 14 engages. The piston 14 is pressed in the direction of the stop 16 by a spring 18. The path of the piston 14 is limited so that the piston rod 17 only in the bottom Ren part of the vertical swivel stroke of the cutting arm reaches the stop 16. The hydraulic cylinder 9, which is articulated at 10 on the loading ramp 4, is fixed on the cutting machine. The cylinder 19 of the cylinder-piston unit forming the transmitter device 12 is fixed on the cylinder 9 and thus also on the cutting machine itself. The piston rod 20 of the cylinder-piston unit 12 is firmly connected to the eye 21 of the piston rod 22 of the cylinder of the cylinder-piston unit 9 acting on the loading ramp by means of a part 23 welded to this eye 21. No spring loading is therefore required here.

Bei einer Abwärtsverschwenkung des Schrämarmes 1 verkleinert sich der Kolbenraum 24 des Zylinder-Kolben-Aggregates 11 und drückt hydraulisches Medium, beispielsweise Fett, über eine Leitung 25, '26 in den Arbeitsraum 27 eines die Empfängereinrichtung bildenden Zylinder-Kolben-Aggregates 28. Wenn die Laderampe angehoben wird, verkleinert sich der Arbeitsraum 29 des Kolbens 21 des Zylinder-Kolben-Aggregates 12, welches die der Laderampe zugeordnete Gebereinrichtung darstellt. Das hydraulische Medium wird hiebei über die Leitung 30, 26 gleichfalls in den Arbeitsraum 27 des die Empfängereinrichtung bildenden Zylinder-Kolben-Aggregates gedrückt. Es wird somit beim Absenken des Schrämarmes 1 und beim Anheben der Laderampe 4 hydraulisches Medium in den Arbeitsraum 27 gedrückt und der Kolben 31 des die Empfängereinrichtung bildenden Zylinder-Kolben-Aggregates 28 wird durch die Summe der Volumina dieser verdrängten hydraulischen Medien nach rechts gedrückt. Es wird somit die Bewegung des Kolbens 31 nach rechts sowohl in Abhängigkeit von der Absenkbewegung des Schrämarmes, als auch in Abhängigkeit von der Aufwärtsbewegung der Laderampe nach rechts verlagert und wenn die Summe der Volumina dieser aus den Zylinder-Kolben-Aggregaten 11 und 12 verdrängten Medien ein Ausmass erreicht, bei welchem sich Schrämarm und Laderampe in gefährlichem Ausmass aneinander annähern, wird durch den Kolben 31 die Abwärtsbewegung des Schrämarmes und die Aufwärtsbewegung der Laderampe unterbrochen.When the cutter arm 1 swivels downward, the piston chamber 24 of the cylinder-piston unit 11 shrinks and presses hydraulic medium, for example grease, via a line 25, '26 into the working chamber 27 of a cylinder-piston unit 28 which forms the receiver device Loading ramp is raised, the working space 29 of the piston 21 of the cylinder-piston unit 12 is reduced, which represents the transmitter device assigned to the loading ramp. The hydraulic medium is also pressed via the line 30, 26 into the working space 27 of the cylinder-piston unit forming the receiver device. Hydraulic medium is thus pressed into the working space 27 when the cutter arm 1 is lowered and the loading ramp 4 is raised, and the piston 31 of the cylinder-piston unit 28 forming the receiver device is pressed to the right by the sum of the volumes of these displaced hydraulic media. The movement of the piston 31 to the right is thus shifted to the right both as a function of the lowering movement of the cutting arm and as a function of the upward movement of the loading ramp and when the sum of the volumes of these media displaced from the cylinder-piston units 11 and 12 reached a dimension at which the cutting arm and loading ramp approach each other to a dangerous extent, the piston 31 interrupts the downward movement of the cutting arm and the upward movement of the loading ramp.

Die diesbezügliche Anordnung ist in Fig. 3 dargestellt. Der Kolben 31 wird durch eine Feder 32 nach links gedrückt. In den Arbeitsraum 27 dieses Kolbens mündet über einen Anschluss 33 die Leitung 26. Mit dem Kolben 31 ist ein Steuerschieber 34 verbunden, der in einem Schieberspiegel 35 verschiebbar ist. Die Steueröffnung 36 steht mit derjenigen hydraulischen Leitung in Verbindung, welche die Senkung des Schrämarmes 1 bewirkt. Die Steueröffnung 37 steht mit derjenigen hydraulischen Leitung in Verbindung, welche das Anheben der Laderampe 4 bewirkt. Die Steueröffnung 38 steht mit einem Rücklauf in Verbindung. Der Steuerschieber 34 weist Steuernuten 39 und 40 auf, welche über radiale Bohrungen 41 und 42 mit einer zentralen Bohrung 43 des Steuerschiebers 34 verbunden sind. Sobald nun diese Steuernuten 39, 40 die Steuerausnehmungen 36 und 37 aufsteuern, gelangen diese Steuerausnehmungen über die Steuernuten 39, 40, die Bohrungen 41 und 42 und die zentrale Bohrung 43 in Verbindung mit der Steuerausnehmung 38. Hiebei werden die das Absenken des Schrämarmes und das Heben der Laderampe bewirkenden hydraulischen Leitungen über die Steuerausnehmung 38 mit dem Rückfluss verbunden und die Absenkbewegung des Schrämarmes und gleichzeitig auch die Hubbewegung der Laderampe wird unterbrochen, so dass eine Kollision vermieden wird.The relevant arrangement is shown in Fig. 3. The piston 31 is pressed to the left by a spring 32. The line 26 opens into the working space 27 of this piston via a connection 33. A control slide 34 is connected to the piston 31 and is displaceable in a slide mirror 35. The control opening 36 is connected to the hydraulic line which causes the cutting arm 1 to be lowered. The control opening 37 is connected to the hydraulic line which causes the loading ramp 4 to be raised. The control opening 38 is connected to a return. The control slide 34 has control grooves 39 and 40, which are connected via radial bores 41 and 42 to a central bore 43 of the control slide 34. As soon as these control grooves 39, 40 open the control recesses 36 and 37, these control recesses pass through the control grooves 39, 40, the bores 41 and 42 and the central bore 43 in connection with the control recess 38.Hiebei are the lowering of the cutting arm and that Hydraulic lines causing the loading ramp are connected to the return flow via the control recess 38 and the lowering movement of the cutting arm and at the same time also the lifting movement of the loading ramp is interrupted, so that a collision is avoided.

Claims (6)

1. Device to preclude physical contact between the cutter boom and the gathering arms of a cutting machine (3) comprising a cutting boom (1) pivotable at least arround a horizontal axis and carrying at least one cutting head and comprising a loading ramp (4) arranged below the cutting boom and being designed to be lifted and lowered, characterized in that for the cutting boom (1) there is provided a transmitter means (11) registering the position of the cutting boom (1) relative to the cutting machine and for the loading ramp (4) there is provided a transmitter means (12) registering the position of the loading ramp relative to the cutting machine, and in that said both transmitter means are connected with a common receiver means (28) controlling a controll member (34) interrupting the downward movement of the cutting boom ('1) and the upward movement of the loading ramp in dependence on a combination of the signals of said both transmitter means.
2. Device as claimed in claim 1, characterized in that said transmitter means (11, 12) are formed of hydraulic cylinder-piston-arrangements (13, 14; 19, 21), one part (19, 1'3) of which is connected with a part of the cutting machine and the other part (20, 17) of which is, at least within the lower portion of the pivotal area of the cutting boom, acting on the loading ramp (4) respectively on the cutting boom (1), and in that the working spaces (24, 29) of said both cytinder-piston-arrangements (1'1, 12) becoming reduced on downward movement of the cutting boom (1) and on upward movement of the loading ramp (4), respectively, are connected with the working space (27) of a hydraulic cylinder-piston-aggregate (28) forming the receiver means, the piston (31) of which is in connection with the control member (34) interrupting the movements of the cutting boom (1) and of the loading ramp (4).
3. Device as claimed in claim 2, characterized in that the working spaces (24, 29, 27) of the hydraulic cylinder-piston-arrangements (1'1, '1'2) and of the cylinder-piston-arrangement (28) forming the receiver means are filled with an empirically estblished amount of a hydraulic fluid, particularly grease.
4. Device as claimed in claims 2 or 3, characterized in that the transmitter means (1'1) associated with the cutting boom or the cylinder-piston-aggregate (1'3, 14), respectively, is, on the one hand, fixed on a part of the cutting machine (3) and is, on the other hand, positively acting on the cutting boom (1) by abutment (18) only, said abutment (1'6) only becoming effective with the cutting boom (1) being within the lower half of its vertical pivotal area.
5. Device as claimed in any of claims 2 to 4, characterized in that when hydraulically driving the movement of the cutting boom (1) and the loading ramp (4), the controll member is formed of a piston valve (34) provided with control recesses (39, 40) which simultaneously establish a connection of the hydraulic conduit for lowering the cutting boom and of the hydraulic conduit for lifting the loading ramp with a backflow conduit.
6. Device as claimed in claim 5, characterized in that the piston valve (34) is coaxially connected with the hydraulic piston (31) of the receiver means (28) or is forming one single part with said hydraulic piston (31) respectively.
EP80890126A 1979-11-05 1980-10-24 Device to preclude physical contact between the cutter boom and the gathering arm of a cutting machine Expired EP0028593B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT7097/79 1979-11-05
AT0709779A AT366773B (en) 1979-11-05 1979-11-05 DEVICE FOR PREVENTING A COLLISION BETWEEN CROSSING ARM AND LOADING RAMP OF A CROSSING MACHINE

Publications (2)

Publication Number Publication Date
EP0028593A1 EP0028593A1 (en) 1981-05-13
EP0028593B1 true EP0028593B1 (en) 1983-05-18

Family

ID=3592685

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80890126A Expired EP0028593B1 (en) 1979-11-05 1980-10-24 Device to preclude physical contact between the cutter boom and the gathering arm of a cutting machine

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US (1) US4351564A (en)
EP (1) EP0028593B1 (en)
JP (1) JPS5681796A (en)
AT (1) AT366773B (en)
AU (1) AU537334B2 (en)
BR (1) BR8007109A (en)
CA (1) CA1146181A (en)
CS (1) CS238369B2 (en)
DE (1) DE3063362D1 (en)
ES (1) ES8201259A1 (en)
IN (1) IN154086B (en)
MA (1) MA18986A1 (en)
MX (1) MX150725A (en)
NZ (1) NZ195347A (en)
PL (1) PL129211B1 (en)
SU (1) SU1213989A3 (en)
ZA (1) ZA806533B (en)

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Publication number Priority date Publication date Assignee Title
DE3434365A1 (en) * 1984-09-19 1986-03-20 Gewerkschaft Eisenhütte Westfalia, 4670 Lünen Device for preventing a collision between cutting arm and loading shovel in a continuous miner
AT384075B (en) * 1985-11-04 1987-09-25 Voest Alpine Ag DEVICE FOR PROTECTING THE LOADING DEVICE AND / OR THE CLEANING ARM OF A CUTTING MACHINE FROM COLLISION
AT383647B (en) * 1985-11-08 1987-07-27 Voest Alpine Ag DEVICE FOR PREVENTING THE COLLISION OF A LOADING LAMP OF A BREAKING MACHINE WITH A SWING ARM OR RELEASING TOOL THEREOF
US4858347A (en) * 1988-04-25 1989-08-22 R. A. Hanson Company, Inc. Continuous excavating apparatus and methods
CN101963059A (en) * 2010-09-20 2011-02-02 沈阳矿山机械有限公司 Cutting head of development machine and anti-interference device of shovel board
CN102839975A (en) * 2011-06-23 2012-12-26 三一重型装备有限公司 Hardrock tunneling machine
CN105443128A (en) * 2014-08-25 2016-03-30 洛阳金马电气科技有限公司 Main shovel plate of boom-type roadheader
US20180179892A1 (en) * 2016-12-22 2018-06-28 Caterpillar Global Mining Europe Gmbh Collision Avoidance Control Method and System

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US3282627A (en) * 1963-12-26 1966-11-01 Goodman Mfg Co Hydraulic tilt limiting control for continuous miner
FR1528673A (en) * 1967-03-09 1968-06-14 Eickhoff Geb Tunnel drilling machine usable in particular in mines
DE2458514C3 (en) * 1974-12-11 1978-12-07 Gebr. Eickhoff, Maschinenfabrik U. Eisengiesserei Mbh, 4630 Bochum Tunneling machine with a loosening tool mounted on a support arm that can be swiveled in all directions and a method for its operation
AT340350B (en) * 1975-09-02 1977-12-12 Voest Ag SCRAPING MACHINE
AT342537B (en) * 1976-05-13 1978-04-10 Voest Ag SCRAPING MACHINE

Also Published As

Publication number Publication date
AT366773B (en) 1982-05-10
MX150725A (en) 1984-07-05
NZ195347A (en) 1984-08-24
EP0028593A1 (en) 1981-05-13
IN154086B (en) 1984-09-15
PL129211B1 (en) 1984-04-30
CS238369B2 (en) 1985-11-13
ES496371A0 (en) 1981-12-01
ES8201259A1 (en) 1981-12-01
US4351564A (en) 1982-09-28
SU1213989A3 (en) 1986-02-23
DE3063362D1 (en) 1983-07-07
ZA806533B (en) 1981-10-28
AU537334B2 (en) 1984-06-21
ATA709779A (en) 1981-09-15
CA1146181A (en) 1983-05-10
BR8007109A (en) 1981-05-05
AU6362980A (en) 1981-05-14
MA18986A1 (en) 1981-07-01
JPS5681796A (en) 1981-07-04
PL227638A1 (en) 1981-08-21

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