PatentDe  


Dokumentenidentifikation EP0772729 27.04.2000
EP-Veröffentlichungsnummer 0772729
Titel ANORDNUNG IN EINER HYDRAULISCH ANGETRIEBENEN GESTEINBOHRAUSRÜSTUNG
Anmelder Sandvik Tamrock Oy, Tampere, FI
Erfinder NIEMI, Jaakko, FIN-33580 Tampere, FI
Vertreter Abitz & Partner, 81679 München
DE-Aktenzeichen 69515878
Vertragsstaaten AT, CH, DE, FR, GB, IT, LI, SE
Sprache des Dokument EN
EP-Anmeldetag 04.04.1995
EP-Aktenzeichen 959143793
WO-Anmeldetag 04.04.1995
PCT-Aktenzeichen FI9500183
WO-Veröffentlichungsnummer 9528549
WO-Veröffentlichungsdatum 26.10.1995
EP-Offenlegungsdatum 14.05.1997
EP date of grant 22.03.2000
Veröffentlichungstag im Patentblatt 27.04.2000
IPC-Hauptklasse E21B 19/08

Beschreibung[en]

The invention relates to an arrangement in a hydraulically operated rock drilling equipment, comprising a rock drill provided with a percussion device; a feed motor for feeding the rock drill in the drilling direction and back, respectively; a hydraulic pump; a percussion pressure line and a feed pressure line both connected to the pump for feeding hydraulic fluid to the percussion device and the feed motor, respectively; a return line from the percussion device and the feed motor for returning hydraulic fluid to a tank for hydraulic fluid; a feed regulation valve and a feed regulator for regulating the flow of hydraulic fluid to the feed motor, the feed regulation valve being a signal-controlled proportional valve and the feed regulator being connected to control the feed regulation valve by means of at least one feed regulation line.

In rock drilling, collaring a hole has to be performed by using set values lower than the normal set values used in drilling, such as percussion pressure and feed, until the hole formed in the surface of the rock is deep enough to ensure that the drill bit stays in the hole. This has usually been done in such a way that the driller adjusts set values for collaring manually and then turns the controls to their maximum position.

US Patent 4,074,771 discloses a solution where the feed pressure of the feed machinery is adjusted by means of a control lever operated by the driller. In this patent the percussion operation of the percussion machinery is arranged to be controlled by the pressure of the hydraulic fluid of the feed motor in such a way that when the pressure exceeds a predetermined lower limit, the feed of hydraulic fluid into the percussion machinery increases with increasing feed pressure. Correspondingly, the flow of hydraulic fluid into the percussion machinery decreases with decreasing feed pressure. Accordingly, the percussion power can be adjusted at the same time as the pressure of the feed machinery is adjusted by means of a control valve connected to the control lever. It is also known from the patent that normal drilling is switched on after collaring by pushing the control lever for feed pressure to its extreme position, whereby both the feed and the percussion will be set at maximum power. In this situation, the rotation and percussion machineries are connected to follow the pressure of the feed machinery in such a way that when the feed pressure decreases, the rotation power and the power of the percussion machinery also decrease.

The solution disclosed in the US patent is very complicated and difficult to realize, in addition to which its use in drilling is not optimal from the driller's point of view. The simultaneous adjustment of the feed pressure and the power of the percussion machinery and the rotation motor causes problems and makes collaring more difficult.

The object of the present invention is to provide an arrangement for controlling a rock drilling equipment, which allows the driller to control the collaring easily and efficiently while also allowing efficient normal drilling. The arrangement according to the invention is characterized in that the arrangement further comprises a first pressure relief valve having a lower preset pressure value than the highest allowable operating pressure of the percussion device; a pressure difference valve in communication with the feed pressure line; and a signal-controlled control valve connected between the percussion pressure line and the first pressure relief valve on one hand and the pressure difference valve on the other hand and being controlled by the feed regulation line controlling the forward operation of the feed motor in such a way that when the value of the control signal of said feed regulation line is below a predetermined switching value, the first pressure relief valve is switched in communication with the percussion pressure line through the control valve and keeps the pressure of hydraulic fluid applied to the percussion device at said preset pressure value, and when the value of the control signal of the feed regulation line exceeds said switching value, the control valve changes its position and connects the pressure difference valve in communication with the percussion pressure line in place of the first pressure relief valve, the pressure difference preset for the pressure difference valve prevailing between the percussion pressure line and the feed motor line.

An essential aspect of the invention is that the percussion power is set to a suitable predetermined level below the normal percussion power during collaring by setting the pressure of the hydraulic fluid supplied to the percussion device to a level below the pressure prevailing at full percussion power and adjusting solely the feed by means of a control connected to the control lever and having a control signal proportional to the turning angle of the control lever. The control regulates the flow amount of the hydraulic fluid of the feed motor in proportion to the control signal. In this way the driller is able to adjust the feed rate in a desired way during collaring. Another essential aspect of the invention is that when the value of the control signal exceeds a preset value, the pressure of the hydraulic fluid of the percussion device is increased to a normal percussion pressure. An essential feature of the preferred embodiment of the invention is that the difference between the pressures of the hydraulic fluids of the percussion device and the feed machinery is kept constant during normal drilling.

The invention will be described more fully with reference to the attached drawings, in which

  • Figure 1 is a general hydraulic diagram for the arrangement according to the invention;
  • Figure 2 is a general hydroelectric diagram for the arrangement according to the invention;
  • Figure 3 is a more detailed hydraulic diagram for the arrangement according to the invention; and
  • Figure 4 is a diagram illustrating the pressures of the hydraulic fluid of the percussion machinery and the feed device relative to each other as a function of time.

Figure 1 shows a hydraulic diagram for a rock drilling equipment. The diagram comprises a hydraulic pump 1, preferably a pressure-controlled volume-flow pump, and a percussion device 2 connected to be operated by the pump, and a feed motor 3. The feed motor 3 may be either a hydraulic motor or hydraulic cylinder, depending on the application. In the present patent application and claims, the term feed motor is used generally to refer to both of them. In the drawings, the same numerals are used for similar parts, and they will be explained later in greater detail only if needed. To control the operation of the feed motor, a pressure reducing valve 4 is connected to a hydraulic line from the hydraulic pump 1 so as to reduce the pressure of the hydraulic fluid supplied by the hydraulic pump 1 to a level suitable for control valves. From the pressure reducing valve 4, a control pressure line 5 passes to a feed regulator 6, i.e. a feed regulation valve, which regulates the pressure of the flow of hydraulic fluid from the control pressure line 5 so as to adjust the flow of hydraulic fluid to the feed motor 3. The feed regulator 6 is a pressure regulation valve known per se, comprising a control lever 6a. The control lever 6a can be turned from its neutral position in two opposite directions, as shown by arrow A in the figure, so as to regulate the control pressure for the feed rate both when forwarding and retracting the drill rod. The feed regulator 6 has two associated feed regulation lines 7a and 7b, which are connected to a shuttle valve 7c. A line 7d from the shuttle valve 7c is further connected to a feed regulation valve 8. The feed regulation valve 8 is a pressure-controlled proportional valve, the flow of hydraulic fluid through the valve being proportional to a control pressure acting on it. The hydraulic pump 1 is connected to the feed regulation valve 8 by means of a feed pressure line 9. Both hydraulic lines of the feed motor 3 are connected to a directional control valve 11, which is connected to one of the feed regulation lines, i.e. the line 7b intended for regulating the return movement. From the directional control valve 11, a feed motor line 12 leads to the feed regulation valve 8 and one of the lines connected to the feed motor 3 through the directional control valve 11 leads to a tank 10 for hydraulic fluid so as to recycle the hydraulic fluid returning from the feed motor 3. Through the shuttle valve 7c the hydraulic fluid from the pressurized feed regulation line 7a or 7b is able to control the feed regulation valve 8. If the feed regulator 6 applies a pressure to the feed regulation line 7a, it controls the feed regulation valve 8 in proportion to the pressure value, and the shuttle valve 11 remains in the position shown in the figure. If the direction of movement of the feed motor is to be reversed, the feed regulator 6 applies a pressure to the feed regulation line 7b, whereby it will act on the feed regulation valve 8 through the shuttle valve 7c and at the same time changes the position of the directional control valve 11 so that the lines of the feed motor 3 cross each other, as a result of which the direction of movement is reversed. Depending on which one of the feed regulation lines 7a and 7b the feed control pressure is applied by means of the feed regulator 6, the feed motor 3 operates either forwards in the feed direction or in the reverse direction so that the amount of hydraulic fluid to the feed motor 3 and that from the feed motor are proportional to the control pressure.

From the hydraulic pump 1, a percussion pressure line 13 passes through a percussion valve 14 to the percussion device 2; from the percussion device 2 a return line for hydraulic fluid passes to the tank 10 for hydraulic fluid. The percussion valve 14 can be switched by means of a percussion control valve 15 connected to the control pressure line 5, i.e. by turning its control lever 15a in the direction of arrow B, from its rest position shown in the figure to a position where the hydraulic fluid from the hydraulic pump 1 flows through the percussion pressure line 13 to the percussion device 2 and further onwards.

To control the percussion pressure, a first throttle 16 is connected to the percussion pressure line 13. The throttle 16 in turn is connected through a pressure-controlled pressure control valve 17 on one hand to a first pressure relief valve 18 for adjusting the percussion pressure during collaring and on the other hand through a control line 19 alternatively to a pressure difference valve 20. A pressure indication line 21 connected between the throttle 16 and the pressure control valve 17 is further connected through a second shuttle valve 22 to a flow control line 23 for the hydraulic pump 1.

The feed motor line 12 of the feed motor 3 is connected through a second throttle 24 by means of a line 25 to the above-mentioned second shuttle valve 22, wherethrough it acts on the flow control line 23 of the hydraulic pump 1. The line 25 is further connected to the pressure difference valve 20 on the side opposite to its line 19. A feed pressure regulation valve 26 is further connected to the feed motor line 12, and it is connected on the other side in communication with the tank 10. The feed regulation line 7a controlling the forward feed is further connected to control the pressure control valve 17, whereby when the control pressure in the line 7a exceeds a predetermined limit value, the pressure control valve 17 changes its position.

The connection operates in the following way. On starting the drilling, the percussion control pressure is switched on by means of the percussion control valve 15, as a result of which the percussion valve 14 changes its position and admits the hydraulic fluid supplied by the hydraulic pump 1 through the percussion pressure line 13 to the percussion device 2. At the same time, hydraulic fluid flows in the percussion pressure line 13 through the first throttle 16 to the pressure control valve 17 and further to the first pressure relief valve 18, the set value of which can be adjusted and which can set a desired percussion pressure for collaring. Through the pressure indication line 21 connected between the throttle 16 and the pressure control valve 17, the pressure prevailing at this point is able to act through the second shuttle valve 22 on the flow control line 23 and thus to keep the output of hydraulic fluid from the hydraulic pump 1 on a level corresponding to the demand. At the same time, hydraulic fluid is able to enter the control pressure line 5 through the pressure reducing valve 4 to the feed regulator 6. When the control lever 6a of the feed regulator 6 is turned forwards in the feed direction, the pressure increases in the feed pressure line 7a, whereby the feed regulation valve 8 moves under the control of the pressure in the figure in a direction such that the hydraulic fluid starts to flow from the hydraulic pump 1 through the feed pressure line 9 via the feed regulation valve 8 and further through the feed motor line 12 to the feed motor 3. Correspondingly, hydraulic fluid flows from the feed motor 3 backwards and further through the directional control valve 11 to the tank 10. The feed pressure regulation valve 26 is able to set the feed pressure at which the feed motor 3 is to be operated. In order that the consumption of hydraulic fluid and the pressure level in the equipment would remain on a suitable level, the pressure of the feed motor acts through the line 25 via the second shuttle valve 22 on the hydraulic pump 1, and so it will limit the feed of hydraulic fluid from the hydraulic pump if the pressure increases excessively either in the percussion pressure line 13 of the percussion device or in the feed motor line 12 to the feed motor 3. The flow of hydraulic fluid to the feed motor 3 is regulated by the feed regulator 6 by turning its control lever 6a, whereby the flow of hydraulic fluid through the feed motor 3 increases with increasing turning angle. When the pressure of the hydraulic fluid in the feed regulation line 7a exceeds the switching pressure value of the pressure control valve 17, the pressure control valve 17 changes its position. The first pressure relief valve 18 is thereby switched off, and the throttle 16 is connected through the control line 19 to the pressure difference valve 20, which maintains a constant pressure difference between the percussion pressure line 13 of the percussion device 2 and the feed motor line 12 of the feed motor.

Figure 2 shows a hydroelectric switching diagram corresponding to the diagram of Figure 1. The feed regulator 6' is an electric control, i.e. a joystick, which is able to control two movements simultaneously along mutually crossing paths of movement shown with arrows A' and B' in the figure. Correspondingly, the directional control valve 11', the feed regulation valve 8', the percussion valve 14' and the pressure control valve 17' are electrically controllable. In this embodiment, an electric control signal applied to the feed regulation line 7a' controls the pressure control valve 17', and a separate control signal 7d' controls the feed regulation valve 8' in both the feed and the return direction. When the control signal increases to a predetermined switching value, the pressure control valve 17' changes its position, and the switching arrangement operates otherwise hydraulically in the same way as in the switching diagram shown in Figure 1. Correspondingly, when the feed motor 3 is controlled in the backward direction, the directional control valve 11' is switched to another position under the influence of a control signal applied to the feed regulation line 7b', as described in connection with Figure 1.

Figure 3 illustrates a detailed embodiment of the invention, which mainly corresponds to the switching diagram shown in Figure 1, but is shown more completely in some portions. In this embodiment, the feed regulation valve 8'' is a two-way proportional valve, both of the feed regulation lines 7a and 7b being connected to control it. Correspondingly, both of the feed motor lines 12a and 12b of the feed motor are connected to the feed regulation valve 8'', to which the feed pressure line is connected and from which a line passes to the tank 10. One line of the feed pressure regulation valve 26 is connected to the pressure-controlled control valve 27, which, depending on the feed direction, selects the so-called zero line for the feed pressure regulation valve, i.e. it selects that one of the feed motor lines 12a and 12b, in which hydraulic fluid returning from the feed motor 3 flows unpressurized to the tank 10 for hydraulic fluid. The pressure-controlled control valve 27 in turn is connected to the feed regulation line 7b effecting the return movement. Consequently, when the rock drill is fed forwards, the control valve 27 remains in the position shown in the figure; correspondingly, when the rock drill is retracted, the control valve changes its position and at the same time switches the feed pressure regulation valve 26 in communication with the feed motor line 12a. The figure also shows a second pressure relief valve 28, which is connected between the pressure indication line 21 and a line passing to the tank 10 for hydraulic fluid. In the situation shown in the figure, the pressure prevailing in the pressure indication line 21 is lower than the highest allowable operating pressure value of the percussion pressure set in the second pressure relief valve 28, and the valve 28 is not operative in this situation. Through the pressure indication lines from the feed regulation valve, the pressure of the hydraulic fluid prevailing in the feed motor line 12a is able to act via the second throttle 24 on the feed pressure regulation valve 26, which in turn is connected to the other feed motor line 12b. When the control pressure in the feed regulation line 7a exceeds a preset limit value, the percussion pressure is able to rise. Correspondingly, the second pressure relief valve 28 is switched on, limiting the percussion pressure when it increases with the pressure of the feed motor so that the pressure will not exceed a preset maximum value, which the pressure prevailing in the percussion pressure line is not allowed to exceed for safety reasons. If there occurred nothing exceptional or no varying conditions, the percussion pressure would remain all the time in the value set by the second pressure relief valve 28, and the feed pressure of the feed motor 3 would be lower than the percussion pressure by the value determined by the pressure difference valve 20. In practice, the pressure of the feed motor varies, as the structure and hardness of the rock material to be drilled vary. When the feed pressure decreases for some reason as the feed proceeds more rapidly than usually, the machinery would be damaged if the percussion operation continued unchanged. If the feed pressure decreases suddenly for some reason, it may also cause the reference pressure of the pressure difference valve 20 to decrease so that it will correspondingly reduce the pressure of the percussion pressure line 13 of the percussion device so that the pressure difference remains constant even in this case. When the pressure in the feed motor line 12a again rises, the pressure in the percussion pressure line of the percussion device rises correspondingly.

Figure 4 shows pressure curves for the percussion pressure and feed pressure by way of example as a function of time when the drilling is started with collaring and then continued with normal drilling. Figure 4 shows a coordinate system, where the vertical axis represents the pressure and the horizonal axis the time. The upper curve A describes the percussion pressure, i.e. the pressure of hydraulic fluid in the percussion pressure line 13, and the lower curve B describes the feed pressure, i.e. the pressure of hydraulic fluid passing to the feed motor 3 in the feed motor line 12a. When drilling is started at time 0, the percussion pressure has been set at a so-called half-operation value, e.g. 100 bar, at which value it remains throughout the collaring up to the termination of collaring indicated with the dashed line. The feed pressure in turn is lower than the percussion pressure; depending on the conditions, it may vary as long as the control pressure of the feed pressure line 7a remains below a predetermined pressure value, i.e. the switching pressure of the pressure control valve 17. When the feed rate is increased, the pressure rises in the feed regulation line 7a. When the collaring ends, the control lever 6a is turned forwards to its extreme position, whereby the pressure of the feed regulation line 7a exceeds the switching pressure of the pressure control valve 17. In this situation, the second pressure relief valve 28 and the pressure difference valve 20 are switched on, and the percussion pressure in the percussion pressure line 13 follows the feed pressure so that there is the constant pressure different ΔP between them. If the feed pressure falls below its highest value due to soft rock, a cavity or the like, as illustrated in the figure within area C, the percussion pressure correspondingly follows the feed pressure and rises back to the value determined by the second pressure relief valve 28 when the feed pressure again rises. When drilling is ended or when the drill rod is retracted for some other reason by pulling the control lever of the feed regulator 6 backwards, the pressure control valve 17 returns to the position shown in Figure 1, and the pressure-controlled control valve 27 changes its position so that the feed pressure regulation valve 26 is switched between the feed motor lines 12a and 12b in the opposite direction, thus keeping the pressure at the feed motor 3 at a desired value.

The invention has been described above and shown in the attached drawings only by way of example and it is not in any way limited to this, except within the scope of the appended claims. In the switching diagram shown in Figure 3, it is possible to utilize the so-called anti-jamming automatics in such a way that the pressure limiting effect of the valve 26 in the pressure lines of the feed motor 3 will be eliminated at the same time. This is necessary when the drill rod tends to get stuck, and it has to be possible to withdraw it with a force as high as possible. This solution can be realized simply by connecting a control valve to the regulation lines 7a and 7b, by means of which the lines can be connected mutually crosswise. In a jamming situation the feed pressure is thus switched by means of this control valve to control the feed regulation valve 8 in the opposite direction while the valve 27 remains in the position shown in the figure. In this way the valve 26 is connected on both sides to a pressurized line, wherefore it is not able to affect the pressure acting on the feed motor. Various pressure relief valves normally used for protection purposes and shut-off valves and control valves associated with the operation of the actuating means can be connected to the arrangement according to the invention in a manner known per se without affecting the invention and its operability. Similarly, the circuit of the feed motor can be connected in different ways to control the arrangement according to the invention. For instance, when the pressure of the rotation motor rises as the drill gets stuck or for some other similar reason, the feed direction of the feed motor can be reversed by a separate valve. The hydraulic connection of the arrangement thereby operates similarly as when the feed direction is reversed by means of the feed regulator 6.


Anspruch[de]
  1. Anordnung in einer hydraulisch betriebenen Gesteinsbohreinrichtung, umfassend einen mit einer Schlagvorrichtung (2) versehenen Gesteinsbohrer; einen Vorschubmotor (3), um den Gesteinsbohrer in Bohrrichtung vor- bzw. zurückzubewegen; eine Hydraulikpumpe (1); eine Schlagdruckleitung (13) und eine Vorschubdruckleitung (9), die beide mit der Pumpe verbunden sind, um der Schlagvorrichtung (2) bzw. dem Vorschubmotor (3) Hydraulikfluid zuzuführen; eine Rückführleitung von der Schlagvorrichtung und dem Vorschubmotor, um Hydraulikfluid zu einem Behälter (10) für Hydraulikfluid zurückzuführen; ein Vorschubregelventil (8,8',8'') und einen Vorschubregler (6,6') zum Regeln des Stroms von Hydraulikfluid zum Vorschubmotor (3), wobei das Vorschubregelventil (8,8',8'') ein signalgesteuertes Proportionalventil ist und der Vorschubregler (6,6') angeschlossen ist, um das Vorschubregelventil (8,8',8'') mittels mindestens einer Vorschubregelleitung (7a,7a',7b,7b') zu steuern, dadurch gekennzeichnet, daß die Anordnung weiter umfaßt: ein erstes Druckbegrenzungsventil (18) mit einem kleineren voreingestellten Druckwert als dem höchsten zulässigen Betriebsdruck der Schlagvorrichtung (2); ein Druckdifferenzventil (20) in Verbindung mit der Vorschubdruckleitung (9); und ein signalgesteuertes Steuerventil (17,17'), das zwischen der Schlagdruckleitung (13) und dem ersten Druckbegrenzungsventil (18) einerseits und dem Druckdifferenzventil (20) andererseits angeschlossen ist und durch die Vorschubregelleitung (7a,7a') gesteuert wird, die den Vorwärtsbetrieb des Vorschubmotors (3) auf eine derartige Weise steuert, daß, wenn der Wert des Steuersignals der Vorschubregelleitung (7a,7b) unter einem vorbestimmten Umschaltwert liegt, das erste Druckbegrenzungsventil (18) durch das Steuerventil (17,17') in Verbindung mit der Schlagdruckleitung (13) geschaltet wird und den Druck des Hydraulikfluids, mit dem die Schlagvorrichtung (2) beaufschlagt ist, auf dem voreingestellten Druckwert hält, und wenn der Wert des Steuersignals der Vorschubregelleitung (7a,7b) den Umschaltwert überschreitet, das Steuerventil (17,17') seine Stellung ändert und an Stelle des ersten Druckbegrenzungsventils (18) das Druckdifferenzventil (20) in Verbindung mit der Schlagdruckleitung (13) verbindet, wobei die für das Druckdifferenzventil (20) voreingestellte Druckdifferenz zwischen der Schlagdruckleitung (13) und einer Vorschubmotorleitung (12) herrscht.
  2. Anordnung nach Anspruch 1, dadurch gekennzeichnet, daß sie umfaßt: ein Vorschubdruckregelventil (26), das zwischen der dem Vorschubmotor (3) Hydraulikfluid zuführenden Vorschubmotorleitung (12) und einer zum Behälter (10) für Hydraulikfluid führenden drucklosen Hydraulikleitung auf eine derartige Weise angeschlossen ist, daß es den Druck des Hydraulikfluids, mit dem der Vorschubmotor (3) beaufschlagt ist, auf einem Wert hält, der nicht höher ist, als ein Grenzwert, der für das Vorschubdruckregelventil (26) voreingestellt worden ist.
  3. Anordnung nach Anspruch 2, dadurch gekennzeichnet, daß das Vorschubdruckregelventil (26) ein einstellbares Druckdifferenzventil ist.
  4. Anordnung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß das Vorschubregelventil (8'') ein Zweiwege-Proportionalventil ist, das mittels zweier Vorschubmotorleitungen (12a,12b) in Verbindung mit dem Vorschubmotor (3) angeschlossen ist, wobei wechselweise eine der Vorschubmotorleitungen mit der Vorschubdruckleitung (9) in Verbindung steht, so daß unter Druck stehendes Hydraulikfluid durch sie zum Vorschubmotor (3) fließt und durch die andere Leitung zum Behälter (10) für Hydraulikfluid zurückkehrt.
  5. Anordnung nach Anspruch 4, dadurch gekennzeichnet, daß das Vorschubdruckregelventil (26) zwischen den Vorschubmotorleitungen (12a,12b) angeschlossen ist.
  6. Anordnung nach Anspruch 5, dadurch gekennzeichnet, daß das Vorschubdruckregelventil (26) mit den Vorschubmotorleitungen (12a,12b) einerseits durch das Vorschubregelventil (8'') auf eine derartige Weise verbunden ist, daß es mit der Vorschubmotorleitung (12a;12b) in Verbindung steht, die einen höheren Druck aufweist, und andererseits durch ein drucksteuerbares Steuerventil (27), das angeschlossen ist, um durch die Vorschubregelleitung (7b) gesteuert zu werden, die den Rückwärtsbetrieb des Vorschubmotors (3) steuert, auf eine derartige Weise, daß, wenn der Gesteinsbohrer vorgeschoben wird, das Steuerventil (27) das Vorschubdruckregelventil (26) mit derjenigen Vorschubmotorleitung (12b), die in Verbindung mit dem Behälter (10) steht, verbunden hält, und wenn der Gesteinsbohrer zurückbewegt wird, das Steuerventil (27) das Vorschubdruckregelventil (26) in Verbindung mit der Vorschubmotorleitung (12a) verbindet, die unter der Rückkehrbewegung drucklos ist.
  7. Anordnung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß der Vorschubregler (6) ein Hydraulikdruckregelventil ist und das Richtungssteuerventil (11), das Vorschubregelventil (8,8''), das Schlagventil (14) und das Drucksteuerventil (17) hydraulisch steuerbar sind.
  8. Anordnung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß der Vorschubregler (6') eine elektrische Steuerung ist und das Richtungssteuerventil (11'), das Vorschubregelventil (8'), das Schlagventil (14') und das Drucksteuerventil (17') elektrisch steuerbare Hydraulikventile sind.
  9. Anordnung nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß die Hydraulikpumpe (1) eine drucksteuerbare Volumenstrompumpe ist und daß die Schlagdruckleitung (13) bzw. die Vorschubdruckleitung (9) durch ein zweites Wechselventil (22) auf eine derartige Weise in Verbindung mit der Steuerleitung (23) der Hydraulikpumpe (1) angeschlossen sind, daß der höhere der in den Leitungen vorherrschenden Drücke zugeschaltet wird, um die Zufuhr von Hydraulikfluid durch die Hydraulikpumpe (1) zu steuern.
Anspruch[en]
  1. Arrangement in a hydraulically operated rock drilling equipment, comprising a rock drill provided with a percussion device (2); a feed motor (3) for feeding the rock drill in the drilling direction and back, respectively; a hydraulic pump (1); a percussion pressure line (13) and a feed pressure line (9) both connected to the pump for feeding hydraulic fluid to the percussion device (2) and the feed motor (3) respectively; a return line from the percussion device and the feed motor for returning hydraulic fluid to a tank (10) for hydraulic fluid; a feed regulation valve (8, 8', 8'') and a feed regulator (6, 6') for regulating the flow of hydraulic fluid to the feed motor (3), the feed regulation valve (8, 8', 8'') being a signal-controlled proportional valve and the feed regulator (6, 6') being connected to control the feed regulation valve (8, 8', 8'') by means of at least one feed regulation line (7a, 7a', 7b, 7b'), characterized in that the arrangement further comprises a first pressure relief valve (18) having a lower preset pressure value than the highest allowable operating pressure of the percussion device (2); a pressure difference valve (20) in communication with the feed pressure line (9); and a signal-controlled control valve (17, 17') connected between the percussion pressure line (13) and the first pressure relief valve (18) on one hand and the pressure difference valve (20) on the other hand and being controlled by the feed regulation line (7a, 7a') controlling the forward operation of the feed motor (3) in such a way that when the value of the control signal of said feed regulation line (7a, 7b) is below a predetermined switching value, the first pressure relief valve (18) is switched in communication with the percussion pressure line (13) through the control valve (17, 17') and keeps the pressure of hydraulic fluid applied to the percussion device (2) at said preset pressure value, and when the value of the control signal of the feed regulation line (7a, 7b) exceeds said switching value, the control valve (17, 17') changes its position and connects the pressure difference valve (20) in communication with the percussion pressure line (13) in place of the first pressure relief valve (18), the pressure difference preset for the pressure difference valve (20) prevailing between the percussion pressure line (13) and a feed motor line (12).
  2. Arrangement according to claim 1, characterized in that it comprises a feed pressure regulation valve (26) connected between the feed motor line (12) supplying hydraulic fluid to the feed motor (3) and an unpressurized hydraulic line passing to the tank (10) for hydraulic fluid in such a way that it keeps the pressure of the hydraulic fluid applied to the feed motor (3) at a value no higher than a limit value preset for the feed pressure regulation valve (26).
  3. Arrangement according to claim 2, characterized in that the feed pressure regulation valve (26) is an adjustable pressure-difference valve.
  4. Arrangement according to any of claims 1 to 3, characterized in that the feed regulation valve (8'') is a two-directional proportional valve connected in communication with the feed motor (3) by means of two feed motor lines (12a, 12b), one of the feed motor lines being alternatively in communication with the feed pressure line (9) so that pressurized hydraulic fluid flows through it to the feed motor (3) and returns through the other line to the tank (10) for hydraulic fluid.
  5. Arrangement according to claim 4, characterized in that the feed pressure regulation valve (26) is connected between the feed motor lines (12a, 12b).
  6. Arrangement according to claim 5, characterized in that the feed pressure regulation valve (26) is connected to the feed motor lines (12a, 12b) on one hand through the feed regulation valve (8'') in such way that it communicates with the feed motor line (12a; 12b) having a higher pressure and on the other hand through a pressure-controllable control valve (27) connected to be controlled by the feed regulation line (7b) controlling the backward operation of the feed motor (3) in such a way that when the rock drill is fed forwards, the control valve (27) keeps the feed pressure regulation valve (26) connected to that feed motor line (12b) which is in communication with the tank (10), and when the rock drill is fed backwards, the control valve (27) connects the feed pressure regulation valve (26) in communication with the feed motor line (12a) being unpressurized under the return movement.
  7. Arrangement according to any of claims 1 to 6, characterized in that the feed regulator (6) is a hydraulic pressure regulation valve, and the directional control valve (11), the feed regulation valve (8, 8''), the percussion valve (14) and the pressure control valve (17) are hydraulically controllable.
  8. Arrangement according to any of claims 1 to 6, characterized in that the feed regulator (6') is an electric control, and the directional control valve (11'), the feed regulation valve (8'), the percussion valve (14') and the pressure control valve (17') are electrically controllable hydraulic valves.
  9. Arrangement according to any of the preceding claims, characterized in that the hydraulic pump (1) is a pressure-controllable volume flow pump, and that the percussion pressure line (13) and the feed pressure line (9), respectively, are connected through a second shuttle valve (22) in communication with the control line (23) of the hydraulic pump (1) in such a way that the higher one of the pressures prevailing in the lines is connected to control the supply of hydraulic fluid by the hydraulic pump (1).
Anspruch[fr]
  1. Agencement dans un équipement de perforation de roche actionné hydrauliquement, comportant une perforatrice munie d'un dispositif de percussion (2) ; un moteur d'acheminement (3) pour acheminer la perforatrice dans le sens de perforation et en arrière, respectivement ; une pompe hydraulique (1) ; une ligne de pression de percussion (13) et une ligne de pression d'acheminement (9) toutes deux reliées à la pompe pour acheminer du fluide hydraulique vers le dispositif de percussion (2) et le moteur d'acheminement (3), respectivement ; une ligne de retour à partir du dispositif de percussion et du moteur d'acheminement pour renvoyer le fluide hydraulique vers un réservoir (10) de fluide hydraulique ; une vanne de régulation d'acheminement (8, 8', 8'') et un régulateur d'acheminement (6, 6') pour réguler l'écoulement de fluide hydraulique vers le moteur d'acheminement (3), la vanne de régulation d'acheminement (8, 8', 8'') étant une vanne proportionnelle commandée par signal et le régulateur d'acheminement (6, 6') étant relié pour commander la vanne de régulation d'acheminement (8, 8', 8'') par l'intermédiaire d'au moins une ligne de régulation d'acheminement (7a, 7a', 7b, 7b'), caractérisé en ce que l'agencement comporte en outre une première soupape de surpression (18) ayant une valeur de pression préétablie inférieure à la pression de fonctionnement la plus élevée permise du dispositif de percussion (2), une soupape de différence de pression (20) en communication avec la ligne de pression d'acheminement (9), et une vanne de commande commandée par signal (17, 17') reliée entre la ligne de pression de percussion (13) et la première soupape de surpression (18) d'une part et la soupape de différence de pression (20) d'autre part et commandée par la ligne de régulation d'acheminement (7a, 7a') commandant le fonctionnement vers l'avant du moteur d'acheminement (3) de manière telle que lorsque la valeur du signal de commande de ladite ligne de régulation d'acheminement (7a, 7b) est en dessous d'une valeur de commutation prédéterminée, la première soupape de surpression (18) est commutée en communication avec la ligne de pression de percussion (13) à travers la vanne de commande (17, 17') et maintient la pression de fluide hydraulique appliqué au dispositif de percussion (2) au niveau de ladite valeur de pression préétablie, et lorsque la valeur du signal de commande de la ligne de régulation d'acheminement (7a, 7b) dépasse ladite valeur de commutation, la vanne de commande (17, 17') change sa position et relie la soupape de différence de pression (20) en communication avec la ligne de pression de percussion (13) à la place de la première soupape de surpression (18), la différence de pression préétablie pour la soupape de différence de pression (20) prévalant entre la ligne de pression de percussion (13) et la ligne de moteur d'acheminement (12).
  2. Agencement selon la revendication 1, caractérisé en ce qu'il comporte une vanne de régulation de pression d'acheminement (26) reliée entre la ligne de moteur d'acheminement (12) alimentant du fluide hydraulique vers le moteur d'acheminement (3) et une ligne qui n'est pas sous pression passant vers le réservoir (10) de fluide hydraulique de manière telle qu'elle garde la pression du fluide hydraulique appliqué au moteur d'acheminement (3) à une valeur qui n'est pas plus élevée qu'une valeur limite préétablie pour la vanne de régulation de pression d'acheminement (26).
  3. Agencement selon la revendication 2, caractérisé en ce que la vanne de régulation de pression d'acheminement (26) est une soupape de différence de pression pouvant être ajustée.
  4. Agencement selon l'une quelconque des revendications 1 à 3, caractérisé en ce que la vanne de régulation d'acheminement (8'') est une vanne proportionnelle bidirectionnelle reliée en communication avec le moteur d'acheminement (3) par l'intermédiaire de deux lignes de moteur d'acheminement (12a, 12b), une première des lignes de moteur d'acheminement étant alternativement en communication avec la ligne de pression d'acheminement (9) de sorte que du fluide hydraulique sous pression s'écoule à travers celle-ci vers le moteur d'acheminement (3) et retourne à travers l'autre ligne vers le réservoir (10) de fluide hydraulique.
  5. Agencement selon la revendication 4, caractérisé en ce que la vanne de régulation de pression d'acheminement (26) est reliée entre les lignes de moteur d'acheminement (12a, 12b).
  6. Agencement selon la revendication 5, caractérisé en ce que la vanne de régulation de pression d'acheminement (26) est reliée aux lignes de moteur d'acheminement (12a, 12b) d'une part à travers la vanne de régulation d'acheminement (8'') de telle sorte qu'elle communique avec la ligne de moteur d'acheminement (12a ; 12b) ayant une pression plus élevée et d'autre part à travers une vanne de commande commandée par une pression (27) reliée pour être commandée par la ligne de régulation d'acheminement (7b) commandant le fonctionnement vers l'arrière du moteur d'acheminement (3) de manière telle que lorsque la perforatrice est acheminée vers l'avant, la vanne de commande (27) maintient la vanne de régulation de pression d'acheminement (26) reliée à la ligne de moteur d'acheminement (12b) qui est en communication avec le réservoir (10), et lorsque la perforatrice et acheminée vers l'arrière, la vanne de commande (27) est reliée à la vanne de régulation de pression d'acheminement (26) en communication avec la ligne de moteur d'acheminement (12a) qui n'est pas sous pression lors du déplacement de retour.
  7. Agencement selon l'une quelconque des revendications 1 à 6, caractérisé en ce que le régulateur d'acheminement (6) est une vanne de régulation de pression hydraulique, et la vanne de commande de direction (11), la vanne de régulation d'acheminement (8, 8''), la vanne de percussion (14) et la vanne de commande de pression (17) peuvent être commandées hydrauliquement.
  8. Agencement selon l'une quelconque des revendications 1 à 6, caractérisé en ce que le régulateur d'acheminement (6') est une commande électrique, et la vanne de commande de direction (11'), la vanne de régulation d'acheminement (8'), la vanne de percussion (14') et la vanne de commande de pression (17') sont des vannes hydrauliques pouvant être commandées électriquement.
  9. Agencement selon l'une quelconque des revendications précédentes, caractérisé en ce que la pompe hydraulique (1) est une pompe volumétrique pouvant être commandée par une pression et en ce que la ligne de pression de percussion (13) et la ligne de pression d'acheminement (9), respectivement, sont reliées à travers une seconde soupape de commutation (22) en communication avec la ligne de commande (23) de la pompe hydraulique (1) de manière telle que la pression plus élevée parmi les pressions prévalant dans les lignes est reliée pour commander l'alimentation de fluide hydraulique par la pompe hydraulique (1).






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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