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Dokumentenidentifikation EP0796386 14.12.2000
EP-Veröffentlichungsnummer 0796386
Titel ANORDNUNG ZUM BEFESTIGEN VON SCHWENKZYLINDERN AN EINEN AUSLEGER IN EINER GESTEINBOHREINHEIT
Anmelder Sandvik Tamrock Oy, Tampere, FI
Erfinder LEMMETTY, Pauli, FIN-33540 Tampere, FI
Vertreter Abitz & Partner, 81679 München
DE-Aktenzeichen 69519390
Vertragsstaaten AT, CH, DE, ES, FR, GB, IE, IT, LI, SE
Sprache des Dokument EN
EP-Anmeldetag 28.08.1995
EP-Aktenzeichen 959291212
WO-Anmeldetag 28.08.1995
PCT-Aktenzeichen FI9500458
WO-Veröffentlichungsnummer 9607014
WO-Veröffentlichungsdatum 07.03.1996
EP-Offenlegungsdatum 24.09.1997
EP date of grant 08.11.2000
Veröffentlichungstag im Patentblatt 14.12.2000
IPC-Hauptklasse E21B 19/08

Beschreibung[en]

The invention relates to an arrangement for mounting swing cylinders in a boom for a rock drilling unit, comprising a frame, a boom pivotally connected about vertical and horizontal shafts, relative to the frame, a lift cylinder connected between the frame and the boom for vertical lifting and lowering of the boom, a swing cylinder connected between the frame and the boom for lateral turning of the boom relative to the frame, a support for a feed beam, connected to the other end of the boom pivotally about horizontal and vertical shafts, a tilt cylinder, connected between the support and the boom for turning the support relative to the boom about a horizontal shaft, and a transverse swing cylinder connected between the boom and the support for turning the support relative to the boom about a vertical shaft.

A problem with booms for rock drilling units is that when a feed beam is vertically turned when simultaneously being laterally deviated from its upright position to either side, the end of the boom moves so as to describe an arc. The greater the upward or downward movement of the boom, the greater the simultaneous lateral outward swing. This is caused by the articulated structures of a boom and the consequent structural geometry, the elimination of which has in practice proved impossible by mechanical means. A weakness of known solutions is also that the upward and downward swing angles of booms are not symmetrical; the downward angle is narrower than the upward angle for practical reasons. Consequently the lateral deviation in both angular positions of a boom is far too large to be handled and causes much inconvenience when the boom is used. When the boom is allowed to turn to its extreme lateral angles being in its upper angular position, the joints of the cylinders may shift to a position where the boom no longer can turn back, but is locked in place.

The object of this invention is to provide an arrangement with optimum elimination of the above problems and with as equal a lateral swing as possible in the upper and lower vertical positions of a boom. EP-A-140 873 describes an arrangement according to the preamble of claim 1. The swing movement of the boom in this document is obstructed to a certain extent because the swing cylinder and the boom are on the same plane. The arrangement of the invention is characterized in that a swing cylinder between a frame and a boom is coupled at an angle relative to the longitudinal axis of the boom so that the longitudinal axis of the swing cylinder has a vertical downward inclination from the frame toward the end of the boom, relative to the direction of the longitudinal axis of the boom.

An essential idea of the invention is that the swing cylinder is coupled vertically inclined relative to the longitudinal axis of the boom so that with the swing cylinder in the horizontal plane, the boom is in the middle of its vertical swing range, whereat the upward or downward swinging of the boom from this position causes an equal deviation in both the extreme upper and lower positions to the lateral swing of the boom because of the position of the swing cylinder. Correspondingly, the transverse swing cylinder needed for turning the feed beam is coupled at an angle to the longitudinal axis of the boom, whereat the turning of both the feed beam and the boom results in equal angular changes by the action of the vertical swing angle.

It is an advantage of the invention that the changes in the direction and lateral deviations of both the boom and the feed beam, when vertically turned, are essentially the same relative to the horizontal plane both above and below, as the angles between the longitudinal axis of the boom and the swing cylinder, and correspondingly the transverse swing cylinder, compensate for the vertical deviations of the boom.

The invention will be described in greater detail in the accompanying drawings, wherein

  • Figure 1a is a schematic top view of an arrangement of the invention,
  • Figure 1b is a schematic side view of an arrangement of the invention,
  • Figure 2 schematically shows the boom geometry of the arrangement of the invention by way of an example.

Figure 1a schematically shows a part of a frame 1, comprising a boom 2 for a rock drilling unit, pivotally connected about a vertical shaft 3 and a horizontal shaft 4. A lift cylinder 5, not shown in the Figure, is pivotally connected at both ends between the frame 1 and the boom 2, and is shown in Figure 1b, inclined from the boom 2 downward toward the frame 1. Between the boom 2 and the frame 1, a swing cylinder 6 is pivotally connected at the ends to the frame 1 and the boom 2. Cylinders 5 and 6 are both coupled so as to be able to turn relative to the frame 1 and the boom 2, in both the vertical and horizontal planes. Such an articulated coupling is generally known per se, and will not be described in any greater detail. A support 7 is at the end of the boom 2 for fixing a feed beam to the end of the boom 2. The support 7 is pivotally connected at the end of the boom 2 about a vertical shaft 8 and a horizontal shaft 9. Figure 1 further shows a tilt cylinder 10, pivotally connected between the boom 2 and the support 7 at both its ends for vertical lifting of the support 7 and, therewith the feed beam, relative to the boom 2. The Figure also shows a transverse swing cylinder 11, pivotally connected at its ends between the boom 2 and the support 7 for swinging the support 7 about the vertical shaft 8 irrespective of its vertical angle.

Figure 1b correspondingly shows a side view of the arrangement of Figure 1a. The Figure shows that the swing cylinder 6 and the transverse swing cylinder 11 are inclined toward the direction of the longitudinal axis of the boom 2 and further at a downward angle relative to the end of the boom 2. With the boom 2 in the horizontal plane, the vertical angular difference of the swing cylinder 6 is α, preferably, in a manner shown in greater detail in Figure 2, half the difference between the vertical uppermost and lowermost swing angles of the boom 2. Correspondingly, the vertical angle between the longitudinal axes of the transverse swing cylinder 11 and the boom 2, β, is half the difference between the vertically turnable extreme angles of the support 7. Typically the angles α and β are equal, but may also be unequal.

Figure 2 schematically shows the ratio between the vertical angles of the boom 2 and the angles of the swing cylinder 6. Line L2a refers to the direction of the longitudinal axis of the boom with the boom 2 in the horizontal plane, line L2b refers to the direction of the longitudinal axis of the boom with the boom 2 lifted vertically to the farthest possible upward position, and line L2c refers to the longitudinal axis of the boom with the boom 2 vertically turned to the farthest possible downward position. Typically the angle of elevation of the boom 2 upward is greater than downward, and this has been illustrated by allocating the value 50° to the upper angle of altitude γ1 and the value 30° to the lower angle of altitude γ2. In order to obtain equal lateral deviations of the end of the boom 2, irrespective of the lateral swing angle, in the extreme positions of both the upper and lower angles of altitude, the effect of the swing cylinder 6 must be made symmetrical. This is accomplished by an angle α, between the longitudinal axis L6 of the swing cylinder 6 and the longitudinal axis of the boom 2, being wide enough for the swing cylinder 6 to become essentially horizontal while the boom 2 is swung to the middle of the extreme limits L2b and L2c, to line L2d. Consequently, when completely equal deviations both in the upper and lower directions are required, the value of the angle α is half the difference between the upper swing angle γ1 and the lower swing angle γ2, i.e. in the case shown in the Figure, (50°-30°) : 2 = 10°. Thus, with the boom 2 in the horizontal plane in accordance with the line L2a, the downward position of the swing cylinder 6 below it, from the joint between the boom 2 and the frame, equals the value of the angle α, i.e. in the case shown in the Figure, 10°. Correspondingly, with the swing cylinder 6 horizontal, i.e. parallel with the line L2a, a resulting upward movement of the boom equals the value of the angle a, i.e. the boom is parallel with the line L2d. The inclination β of the transverse swing cylinder 11 of the support 7 supporting the feed beam is defined similarly, and is at its simplest implementation equal to α. As is evident from the Figures, the joints of the swing cylinder and the boom are essentially united relative to the frame 1 when the boom 2 faces straight ahead relative to the frame 1. Thus the centres of the horizontal joints at the base of the boom are essentially united with each other in this situation, although small structural differences may exist. Similarly, when the feed beam is required to turn correspondingly as precisely as possible, the measurements of the feed beam or its horizontal joints are arranged so that the centres of these horizontal joints are essentially united. It is naturally clear that when the boom turns laterally, the turning of the centres of the joints causes therein a certain deviation, relative to each other, from their original position, which results in a small error owing to the structure of the mechanism. This, however, has no essential significance as to the invention, as the movements of the boom are, however, essentially symmetric above and below the middle of the vertical swing angle of the boom.


Anspruch[de]
  1. Anordnung zur Anbringung von Schwenkzylindern in einem Ausleger für eine Gesteinsbohreinheit, umfassend einen Rahmen (1), einen in Bezug zum Rahmen (1) um eine vertikale und horizontale Achse (3, 4) schwenkbar verbundenen Ausleger (2), einen zwischen dem Rahmen (1) und dem Ausleger (2) verbundenen Hubzylinder (5), um den Ausleger (2) vertikal anzuheben und abzusenken, einen zwischen dem Rahmen (1) und dem Ausleger (2) verbundenen Schwenkzylinder (6), um den Ausleger (2) in Bezug zum Rahmen (1) seitwärts zu schwenken, eine um eine horizontale und vertikale Achse (9, 8) schwenkbar mit dem anderen Ende des Auslegers (2) verbundene Halterung (7) für ein Vorschubträgerelement, einen zwischen der Halterung (7) und dem Ausleger (2) verbundenen Kippzylinder (10), um die Halterung (7) in Bezug zum Ausleger (2) um eine horizontale Achse (9) zu schwenken, und einen zwischen dem Ausleger (2) und der Halterung (7) verbundenen Querschwenkzylinder (11), um die Halterung (7) in Bezug zum Ausleger (2) um eine vertikale Achse (8) zu schwenken, wobei die Mitten der horizontalen Gelenke, in Bezug zur Basis, des Schwenkzylinders (6) und des Auslegers (2) im wesentlichen an der Basis des Auslegers miteinander vereinigt sind, wenn der Ausleger in Bezug zum Rahmen (1) geradeaus weist, dadurch gekennzeichnet, dass der Schwenkzylinder (6) zwischen dem Rahmen (1) und dem Ausleger (2) unter einem Winkel (α) in Bezug zur Längsachse des Auslegers (2) gekoppelt ist, so dass die Längsachse des Schwenkzylinders (6) in Bezug zur Richtung der Längsachse des Auslegers (2) vom Rahmen (1) aus in Richtung auf das Ende des Auslegers (2) eine Vertikalneigung nach unten aufweist.
  2. Anordnung nach Anspruch 1, dadurch gekennzeichnet, dass der Winkel (α) zwischen den Längsachsen des Schwenkzylinders (6) und des Auslegers (2) in der Vertikalebene im wesentlichen die halbe Differenz zwischen dem oberen Schwenkwinkel (γ1) und dem unteren Schwenkwinkel des Auslegers (2) in Bezug zur Horizontalebene beträgt.
  3. Anordnung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Querschwenkzylinder (11) zwischen dem Ausleger (2) und der Halterung (7) in Bezug zur Längsachse des Auslegers (2) ähnlich unter einem Winkel (β) gekoppelt ist, der vom Rahmen (1) aus in Richtung auf das Ende des Auslegers (2) vertikal nach unten geneigt ist.
  4. Anordnung nach Anspruch 3, dadurch gekennzeichnet, dass der Winkel (β) zwischen den Längsachsen des Querschwenkzylinders (11) und des Auslegers (2) in der Vertikalebene die halbe Differenz zwischen den in Bezug zur Halterung (7) und zum Ausleger (2) nach oben und nach unten schwenkbaren Winkeln beträgt.
  5. Anordnung nach Anspruch 3 oder 4, dadurch gekennzeichnet, dass die Winkel des Schwenkzylinders (6) und des Querschwenkzylinders (11) (α, β) in Bezug zur Längsachse des Auslegers (2) gleich sind.
Anspruch[en]
  1. An arrangement for mounting swing cylinders in a boom for a rock drilling unit, comprising a frame (1), a boom (2) pivotally connected about vertical and horizontal shafts (3, 4) relative to the frame (1), a lift cylinder (5) connected between the frame (1) and the boom (2) for vertical lifting and lowering of the boom (2), a swing cylinder (6) connected between the frame (1) and the boom (2) for lateral turning of the boom (2) relative to the frame (1), a support (7) for a feed beam, connected to the other end of the boom (2) pivotally about horizontal and vertical shafts (9, 8), a tilt cylinder (10), connected between the support (7) and the boom (2) for turning the support (7) relative to the boom (2) about a horizontal shaft (9), and a transverse swing cylinder (11) connected between the boom (2) and the support (7) for turning the support (7) relative to the boom (2) about a vertical shaft (8), wherein the centres of the horizontal joints relative to the base of the swing cylinder (6) and the boom (2) are essentially united with each other at the base of the boom when the boom faces straight ahead relative to the frame (1) characterized in that the swing cylinder (6) between the frame (1) and the boom (2) is coupled at an angle (α) relative to the longitudinal axis of the boom (2) so that the longitudinal axis of the swing cylinder (6) has a vertical downward inclination from the frame (1) toward the end of the boom (2), relative to the direction of the longitudinal axis of the boom (2).
  2. An arrangement as claimed in claim 1, characterized in that the angle (α) between the longitudinal axes of the swing cylinder (6) and the boom (2) is in the vertical plane essentially half the difference between the upper swing angle (γ1) and the lower swing angle of the boom (2), relative the horizontal plane.
  3. An arrangement as claimed in claim 1 or 2, characterized in that the transverse swing cylinder (11) between the boom (2) and the support (7) is similarly coupled relative to the longitudinal axis of the boom (2) at a angle (β), vertically inclined from the frame (1) downward toward the end of the boom (2).
  4. An arrangement as claimed in claim 3, characterized in that the angle (β) between the longitudinal axes of the transverse swing cylinder (11) and the boom (2) is in the vertical plane half the difference between the angles turnable upward and downward relative to the support (7) and the boom (2).
  5. An arrangement as claimed in claim 3 or 4, characterized in that the angles of the swing cylinder (6) and the transverse swing cylinder (11) (α, β), relative to the longitudinal axis of the boom (2), are equal.
Anspruch[fr]
  1. Structure de montage de vérins de balancement dans un bras d'une unité perforatrice de roches, comportant un châssis (1), un bras (2) relié de manière pivotante à des arbres vertical et horizontal (3, 4) par rapport au châssis (1), un vérin de levage (5) relié au châssis (1) et au bras (2) pour lever et baisser verticalement le bras (2), un vérin de balancement (6) relié au châssis (1) et au bras (2) pour la rotation latérale du bras (2) par rapport au châssis (1), un support (7) pour une poutre d'alimentation, relié à l'autre extrémité du bras (2) de manière pivotante à des arbres horizontal et vertical, un vérin d'inclinaison (10) relié au support (7) et au bras (2) pour la rotation du support (7) par rapport au bras (2) autour d'un arbre horizontal (9), et un vérin de balancement transversal (11) relié au bras (2) et au support (7) pour la rotation du support (7) par rapport au bras (2) autour d'un arbre vertical (8), les centres des jonctions horizontales par rapport à la base du vérin de balancement (6) et du bras (2) étant pratiquement unifiés l'un avec l'autre au niveau de la base du bras lorsque le bras est dirigé droit en avant par rapport au châssis (1), caractérisée en ce que le vérin de balancement (6) situé entre le châssis (1) et le bras (2) est accouplé au niveau d'un angle (α) par rapport à l'axe longitudinal du bras (2) de sorte que l'axe longitudinal du vérin de balancement (6) a une inclinaison verticale vers le bas à partir du châssis (1) vers l'extrémité du bras (2), par rapport à la direction de l'axe longitudinal du bras (2) .
  2. Structure selon la revendication 1, caractérisée en ce que l'angle (α) entre les axes longitudinaux du vérin de balancement (6) et du bras (2) est, dans le plan vertical, pratiquement la moitié de la différence entre l'angle de balancement supérieur (γ1) et l'angle de balancement inférieur du bras (2), par rapport au plan horizontal.
  3. Structure selon la revendication 1 ou 2, caractérisée en ce que le vérin de balancement transversal (11) situé entre le bras (2) et le support (7) est accouplé de manière similaire par rapport à l'axe longitudinal du bras (2) selon un angle (β), incliné verticalement à partir du châssis (1) vers le bas en direction de l'extrémité du bras (2).
  4. Structure selon la revendication 3, caractérisée en ce que l'angle (β) situé entre les axes longitudinaux du vérin de balancement transversal (11) et du bras (2) est, dans le plan vertical, la moitié de la différence entre les angles de rotation vers le haut et vers le bas par rapport au support (7) et au bras (2).
  5. Structure selon la revendication 3 ou 4, caractérisée en ce que les angles du vérin de balancement (6) et du vérin de balancement transversal (11) (α, β), par rapport à l'axe longitudinal du bras (2), sont égaux.






IPC
A Täglicher Lebensbedarf
B Arbeitsverfahren; Transportieren
C Chemie; Hüttenwesen
D Textilien; Papier
E Bauwesen; Erdbohren; Bergbau
F Maschinenbau; Beleuchtung; Heizung; Waffen; Sprengen
G Physik
H Elektrotechnik

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