Device and method for rock drilling

专利摘要:
The present invention relates to the control of a compressor in a rock drilling device, said rock drilling device comprising a power source for driving a wide rock drilling process, the said compressor, said compressor being arranged for operation according to a first mode and a second mode, wherein in said first mode the output of the compressor is arranged to be controlled by regulating the speed of said compressor, and in said second mode the output of the compressor is arranged to be controlled by regulating the air flow at the inlet of the compressor. The method comprises determining a parameter value representing a need for work said compressor, controlling the compressor according to said first mode when said parameter value representing a need work for said compressor exceeds a first need, and controlling the compressor according to said second mode when said parameter value value for work represents said compressor is less than said first need. The invention also relates to a system and a rock drilling device. Fig. 4
公开号:SE1000869A1
申请号:SE1000869
申请日:2010-08-26
公开日:2012-02-27
发明作者:Erik Alden；Erik Ahlstroem
申请人:Atlas Copco Rock Drills Ab；
IPC主号:

专利说明:

For this reason, a rinsing medium is usually used, such as e.g. compressed air, to flush the borehole clean from the crushed rock.
The compressed air is obtained from a compressor which, like other consumers present in a rock drilling device, is driven by a power source, such as e.g. an internal combustion engine.
In a rock drilling device, different consumers are usually driven by one and the same power source, which means that the power source must always be operated at at least a minimum speed, which is controlled by the consumers connected to the power source.
The speed of the power source must be high enough for the consumer who currently has the highest need to obtain sufficient power to ensure the desired function.
The advantage of such a solution is that one and the same power source can be used as a power source for all consumers present at the drilling rig, such as compressors, hydraulic pumps / motors, percussion instruments, etc.
However, this solution has the disadvantage that the current speed of the power source is often not optimal for all consumers.
For example. the power requirement of the compressor (the compressed air requirement of the rock drilling device) may be lower than the power requirement of the percussion device (the percussion drive hydraulic pump), which leads to more power than is necessary during a drilling process, with excess fuel consumption and heat and noise generation .
There is thus a need for improved control of consumers in a rock drilling process. SUMMARY OF THE INVENTION It is an object of the present invention to provide a method of controlling a compressor in a rock drilling device which solves the above problems. This object is achieved with a method according to claim 1.
The present invention relates to a method of controlling a compressor in a rock drilling device, said rock drilling device comprising a power source for driving a compressor operating in a rock drilling process, said compressor being arranged for operation according to a first mode and a second mode, wherein in the work delivered by said first mode compressor is arranged to be controlled by regulating the speed of said compressor, and where in said second mode the work delivered by the compressor is arranged to be controlled by regulating the air flow at the inlet of the compressor. The method comprises: - determining a parameter meter value representing a need for work for said compressor, - controlling the compressor according to said first mode when said parameter value value representing a need for work for said compressor exceeds a first need, and - controlling the compressor according to said second mode when said parameter meter value representing a need for work for said compressor is less than said first need.
This has the advantage that the compressor can always be controlled in a way that means that the compressor does not consume more power than is actually required, whereby excess fuel consumption, and associated generation of heat and noise can be reduced.
According to the invention, the compressor is controlled in such a way that it generates exactly, or substantially precisely, the work currently required, such as e.g. required purge air flow.
According to the invention, this is achieved by selectively rotationally controlling the compressor (power source) and controlling (throttling) the supply air flow at the compressor inlet, so that the work delivered by the compressor (eg the delivered flow) can be set to desired level.
The compressor's work is thus controlled by regulating the compressor's speed and / or regulating the air flow at its inlet. This means that a very precise control of delivered work can be obtained by throttling the compressor inlet from a given compressor speed to the exact extent required for the desired work to be delivered. The control of delivered work can also be performed independently of the current speed of the power source, as long as the power source speed results in a compressor speed where at least sufficient compressor flow can be delivered.
The operating mode of the compressor can constantly switch between said first mode and said second mode to ensure that the desired flow is delivered, independent of other factors. For example. the need for purge air flow can be substantially constant, at the same time as Søm andïâ consumers connected to the power source are switched on or off, whereby the speed of the power source can vary during operation, which means that control of the compressor is required to maintain the desired flow.
The compressor can be controlled in a way that generates a specific pressure on the high-pressure side of the compressor, where the flow emitted by the compressor is controlled by the set pressure. However, the flow on the high pressure side of the compressor will constantly vary, e.g. depending on the resistance to which the purge air is subjected during drilling.
The flow resistance (throttling) depends i.a. on the drill bit, type of drill rod, number of drill rods and whether the purge air holes in the crown start to become clogged or not. If the amount of drilling cuttings formed during drilling increases, the flow in the purge air circuit, in a pressure-controlled system, will decrease compared with when the amount of drilling cuttings formed is comparatively smaller.
Flow controlled systems therefore have the disadvantage that they have no control over the flow. The system strives to maintain a constant set pressure, with the result that the flow the compressor is set to deliver will constantly vary. The air flow required for a given secondary pressure depends entirely on the flow resistance of the subsequent system. This means that one and the same secondary pressure results in a varying amount of purge air. When the set control pressure has been reached, the purge air flow will be reduced as more rods are added to the drill string and the hole becomes deeper, which can lead to an increase in pressure which in turn leads to a reduction in flow, with an increased risk of clogging. sequence.
If the purge air holes in the crown begin to become clogged, the throttling, and thus the flow losses, will increase, which leads to the compressor system regulating down the flow and the situation worsens further.
Another basic idea of the present invention is therefore to control the flow of the compressor directly instead of controlling the flow delivered by the compressor in a rock drilling process based on a pressure level prevailing after the compressor. This has the advantage that the compressor can be controlled in a manner which results in a solution which is less sensitive to the pressure variations which occur in the purge air circuit during drilling.
This is achieved by controlling the compressor based on a signal representing a desired flow, where the desired flow is disconnected from the pressure after the compressor. The control of the purge air flow thus becomes independent of pressure variations according to the above, as long as the pressure in the purge air circuit does not exceed a maximum pressure value, which e.g. can be represented by a value at which drilling is considered to have occurred and whereby the drilling should be stopped. The maximum pressure value can also represent a maximum value that should not be exceeded so as not to risk component damage.
By regulating the air flow at the compressor inlet and the compressor speed, the purge air flow can be controlled independently of the actual pressure prevailing in the purge circuit. This means that the load of the compressor will vary depending on the pressure while the flow is kept at the desired level (at least up to the system's specified maximum load as above). This means that the desired purge air flow can be controlled very precisely and independently of load variations, whereby it can be ensured that the desired purge air flow delivered by the compressor is constantly maintained.
A flow-controlled system, unlike a pressure-controlled one, can deliver a constant flow (within the system's pressure limits) which is independent of the back pressure that closes etc. genere- rar. This means that the purge air flow will not vary with the number of rods and hole depth (unless an increase in the purge air flow with an increased number of drill rods, ie increased hole depth, is desirable, in which case such an increase can be set).
The pressure can thus vary with the flow and not vice versa, which makes it possible to read with the aid of the purge air pressure if any problems arise, e.g. if the crown is set again.
Additional features of the present invention and advantages thereof will become apparent from the following detailed description of exemplary embodiments and the accompanying drawings.
Brief Description of the Drawings Fig. 1 shows a rock drilling device to which the present invention can be advantageously applied. Figs. 2a-b show a device for controlling the compressor present in the rock drilling device in Fig. 1 according to an exemplary embodiment of the present invention.
Fig. 3 shows the efficiency of a compressor in speed control and control of the air flow at the compressor inlet.
Fig. 4 shows a flow chart of an exemplary method according to the present invention.
Detailed Description of Exemplary Embodiments Fig. 1 shows a rock drilling device according to a first exemplary embodiment of the present invention, for which a control of a compressor according to the invention will be described.
The rock drilling device shown in Fig. 1 comprises a drilling rig 1, in this example an above-ground drilling rig, which carries a drilling machine in the form of a top hammer drilling machine 11.
The drilling rig 1 is shown in use, drilling a hole 2 in rock, which begins at the earth's surface and where the drilling is currently at a depth Q. The hole is intended to result in a hole with the depth ß, which, depending on the application area, can vary greatly. from hole to hole and / or area of application to area of application. The completed hole is indicated by dashed lines. (The ratio shown between drilling rig height and hole depth is in no way intended to be proportional. The total height V of the drill can be, for example, 10 meters, while the hole depth ß can be both less than and substantially much greater than 10 meters, t .ex. 20 meters, 30 meters, 40 meters or more.) The top hammer drilling machine 11 is mounted on a feed beam 5 via a drill carriage 5. The feed beam 5 is in turn attached to a boom 19 10 15 20 25 30 via a feed beam holder 12 The top hammer drill 11 provides, via a drill string 6 supported by a drill string support 14, the impact action of a drilling tool in the form of a drill bit 3. A drill bit usually comprises inserts or pins of cemented carbide, diamond, etc., which transmit shock wave energy from the top hammer drill. to the mountain. For practical reasons (except possibly for very short holes) the drill string 6 does not consist of a drill rod in one piece, but usually consists of a number of drill rods. When the drilling has progressed corresponding to a length of drill rod, a new drill rod is joined to the one or more already joined drill rods, whereby the drilling can proceed another drilling rod length before a new drill rod is joined to existing drill rods.
The top hammer drill 11 is of the hydraulic type, it being powered by a hydraulic pump 10, which in turn is driven by a power source in the form of an internal combustion engine 9 (such as a diesel engine) via hoses (not shown) in the usual way. Alternatively, the power source 9 may consist of e.g. an electric motor.
In general, a drilling rig of the above type comprises a primary power source, such as the internal combustion engine 9, which provides power to several, or all, consumers present at the drilling rig, such as e.g. compressor, hydraulic pumps, as well as consumers driven by them, such as e.g. percussion, hydraulic motors.
During drilling, the rock is crushed, and the crushed rock forms drilling residues that must be evacuated from the borehole in order for the drilling to be carried out in an efficient manner.
For this reason, a flushing medium, in the present example compressed air, flushing air, is used to flush the boreholes from the drilling residues, also called drill cuttings, which are formed during drilling (instead of compressed air, other flushing medium can also be used, for example water , with or without additives). In the rock drilling device shown, the purge air is led through the drill rods, which consist of thick-walled pipes, e.g. steel. A channel formed in or through the walls of the rods in the longitudinal direction through the drill string is used to feed the purge air from the drilling rig 1 through the drill string 6 for discharge through purge air holes in the drill bit and then take the drill cuttings on their way out of the hole.
The flushing air flushes the drill cuttings upwards through and out of the hole 2 in the space between the drill rod and the heel wall, as indicated by the upward arrows in Fig. 1 (in an alternative embodiment the cuttings are flushed out of the hole through a channel in the drill string, the flushing medium being led down the hole in the space formed between the drill rod and the hole wall, alternatively through a second channel formed in the drill string).
Regardless of the flow path, in order for the drill cuttings to follow the purge air out of the hole, it is required that the purge air reaches at least a certain speed. This minimum speed required for the drill cuttings to follow up out of the hole, and not be left with clogging problems as a result, depends primarily on the size, shape and density of the drill cuttings. It is important that the air flow is large enough for the cuttings to follow up to the surface. Too little flow can impair drilling performance, and in the worst case lead to drilling. At the same time, it is important that the air flow on the other hand is not unnecessarily large, since an excessive flow leads to increased energy consumption and also to increased wear of e.g. the casting of the drill string due to the blasting effect the drill string is exposed to by the cuttings flushing air carries with it out of the hole.
To get air down to the drill bit, a compressor 8 is used, in the present example a screw compressor, which pushes the purge air through the duct in the drill rods down to the drill bit. The compressed air is supplied to the drill string 6 from the compressor 8, directly or via a tank (not shown), or via a hose 7. The compressor 8 is driven, as mentioned, by the internal combustion engine 9, and the compressor 8 function will be described in more detail below in connection with Fig. 2 ab.
The internal combustion engine 9 is the primary power supply unit of the drilling rig, and should therefore be powerful enough to simultaneously drive both the compressor 8 and other consumers connected to the internal combustion engine, such as the hydraulic pumps 10, 15, at full speed, as well as cooling fans and other consumers. These other consumers can e.g. consist of additional hydraulic pumps for driving other hydraulically controlled functions on the rock drilling device that are in operation at drilling conditions where maximum power output is required.
The drilling rig also comprises a control unit 18, which forms part of the drilling rig's control system, and which can be used for controlling various functions, such as e.g. control of the compressor 8 and the speed of the internal combustion engine 9 according to the present invention, and which is described below.
As mentioned above, the compressor 8 constitutes a screw compressor, i.e. a compressor with fixed displacement. Fig. 2a shows the compressor 8 directly connected to the internal combustion engine 9, ie. a change in the combustion engine speed is reflected directly by a corresponding change in the compressor's 8 speed.
The flow from a compressor with fixed displacement can in principle be controlled according to two different principles, one of which consists of a regulation of the compressor's speed. The flow from a compressor with fixed displacement is directly proportional to the compressor's speed, and in cases where the compressor's power source can be speed controlled freely, the flow emitted by the compressor can also be controlled to an arbitrary level between 0 and 100% of the compressor's. capacity by means of speed control. However, the compressor and / or the power source may have a minimum speed, whereby the practically possible lower limit for speed control often consists of a certain minimum speed, which also introduces a limitation for how little flow the compressor can emit using the speed control.
In many cases, however, completely free speed control is not possible, e.g. p.g.a. that a power source in the form of an internal combustion engine must pour at least a minimum (idle) speed in order to be able to start at all. In the case of rock drilling devices as above, there are also other consumers connected to the power source, such as the said hydraulic pumps 10, 15, which, in order to obtain sufficient power, may require a higher internal combustion engine speed than is currently required by the compressor.
The speed n of the internal combustion engine is therefore controlled by the control unit 18 by means of a control signal 24, which is determined by the control unit 18 based on signals 21-23 from e.g. other consumers, or another control unit existing at the rock drilling device, and where the control signals may represent a power requirement for the compressor and / or one or more other consumers.
The internal combustion engine 9 can also be arranged to be operated at any of a number of different, substantially constant speeds, which are adapted for different operating cases. Speed control according to the invention can thus include completely free speed control of the compressor (power source) as long as the speed does not fall below the lowest speed required by other consumers, but also control to any of a number of predetermined * fšïïft v.
According to the present invention, however, not only speed control of the compressor is used. Instead, a compressor control method is used where two different principles are applied alternately to control the compressor in order to thereby obtain a work delivered from the compressor such as a flow which corresponds to the desired flow / flow requirement. In addition to regulating the speed of the internal combustion engine 9 as above, the amount of air supplied to the compressor is also regulated. This is schematically illustrated in Fig. 2a by means of an inlet valve 25, the opening / closing of which is controlled by means of a control signal 26 emitted from the control unit 18.
The principle of regulating the emitted flow of the compressor 8 by means of the inlet valve 25 is shown in more detail in Fig. 2b.
The inlet valve 25 consists of an electrically controlled inlet valve. It should be understood that control of the compressor inlet can generally take place in different ways with different types of inlet valves. According to the exemplary embodiment shown, the valve is exemplified by an electrically controlled proportional valve in the inlet of the compressor.
According to the embodiment shown in Fig. 2b, the valve consists of a poppet valve with a valve plate 30, which is operated by means of a pneumatically controlled control piston 31. By moving the valve plate 30 up and down by means of the control piston, the opening area AA changes towards the compressor inlet 32, also changes the amount of air allowed to pass from the environment to the compressor inlet 32.
The inlet side 30a (ie the top side in Fig. 2b) of the valve plate 30 acts against the ambient pressure, which usually means atmospheric pressure pmm, while the opposite (lower) side is affected by the prevailing pressure pm_in the compressor inlet 32. The valve plate 30 functions as a throttle, whereby the pressure in the inlet of the compressor which at most will correspond to Pam, but as soon as air cannot flow freely into the inlet of the compressor, a negative pressure pk; pmm to prevail in the compressor inlet 32. 10 15 20 25 30 13 The air flow from a compressor at a given compressor speed is at least substantially linearly dependent on the absolute pressure in the inlet. In case the compressor works against atmospheric pressure, ie. when the inlet pressure pÜ, = pmm, 100% of the compressor's maximum flow capacity is therefore obtained at the current speed in prevailing circumstances. On the other hand, as soon as a negative pressure prevails at the compressor inlet, the flow emitted by the compressor will constitute a partial flow of maximum flow. By controlling the negative pressure in the compressor inlet in a controlled and desired manner by means of electrical control signals to the inlet valve, the flow emitted by the compressor can be controlled to exactly the desired flow.
The pressure difference to which the valve plate is subjected according to the above gives rise to a force (downward in Fig. 2b) which is linearly dependent on the negative pressure in the inlet. In order to control the poppet valve, a control piston 31 mechanically connected to the poppet valve is used in the embodiment shown.
The control piston 31 is pressure-controlled, and as long as the control piston is depressurized, the inlet of the compressor is kept open by means of a spring 33. If a force is applied to the control piston 31 via a channel 34, and thus the valve plate 30, the valve plate 30 will position way that there is a force balance between the flow forces, the spring force (the spring force can be small in relation to other prevailing forces, whereby this force can at least in applicable cases be disregarded) and the force applied by the control piston 31. Thus, the negative pressure that the valve plate gives rise to depends on the control force. Through knowledge of the spring characteristics of the spring 33, which e.g. can be measured or obtained from the spring manufacturer, the negative pressure can easily be regulated to the desired level by pressurizing the control piston, where the spring characteristics are taken into account when regulating. 10 15 20 25 30 14 Control of the inlet valve can be achieved in any applicable manner, and in the example exemplified here an electrically controlled pneumatic spring-loaded control piston is thus used for controlling the valve plate, but also e.g. fully electric or hydraulic solutions for controlling the valve plate are conceivable. The valve can also have a completely different basic structure than the one shown here.
The control piston pressure is controlled by an actuator, such as an electrically controlled valve, wherein control signals 26 from the control unit 18 control the electrically controlled valve 25, and thus the control piston, according to Figs. 2A-B.
Thus, it is possible to control the flow from a compressor according to two different principles. Although these two different principles provide the same function, ie. ability to regulate the delivered flow of the compressor to a desired flow in a desired manner, speed control and regulation of the pressure (flow) at the compressor inlet, respectively, shows a large difference in efficiency at partial loads.
This is illustrated in Fig. 3. Fig. 3 shows a diagram of the power requirement for the two control principles at 0-100% load on the compressor. 100% flow corresponds to a first speed nx.
The speed nx can be, but does not necessarily have to be, the maximum speed of the compressor.
Control by means of speed control thus means control of the compressor's speed from 0 (0% flow) to nx (100% flow). at the speed that gives 100% flow, ie. The curve represents- Control of the supply air, on the other hand, constitutes a control the control of the inlet valve in Fig. 3 constitutes a control where the speed of the compressor is constant nx. The condition shown is always valid, ie. the efficiency when controlling a certain given flow is always higher with speed control 10 15 20 25 30 15 compared with when controlling the supply air at the compressor inlet.
Thus, it would be preferable that the compressor could always be speed controlled over the entire (working) area where the compressor normally operates during operation. According to the above, however, this is usually not possible with rock drilling devices, since speed control over the entire operating range of the compressor is only possible in cases where no other consumers connected to the compressor power source (internal combustion engine 8) depend on the power source always maintaining at least a certain speed.
According to the present invention, therefore, the compressor according to the present invention is controlled either according to a first mode, where the compressor is speed controlled, or according to a second mode, where the air flow in the compressor inlet is regulated.
An exemplary method 400 according to the present invention is shown in Fig. 4.
The method starts in step 401, where a compressor flow demand qd is determined. The need for compressor flow qd can vary greatly, and can be determined in different ways. The need can e.g. is controlled based on a desired pressure after the compressor, in which case a pressure sensor downstream of the compressor can be used in determining whether the flow delivered by the compressor should be increased or decreased in order to obtain the desired pressure.
According to an embodiment of the present invention, control of the compressor 8 is purely flow controlled. In this case, the flow that the compressor is to deliver is determined, whereby the compressor is then controlled in such a way that the desired flow is obtained. Flow control of the compressor has the advantage that no feedback from the flow circuit downstream if the compressor is required, ie. since the compressor will always emit a certain flow at a certain speed and a certain valve position, it can always be ensured that the desired flow is controlled out.
Flow control also has the advantage that by controlling only the flow delivered by the compressor 8, the desired flow can be maintained independent of actual load (which depends, for example, on the actual number of drill rod components and the amount of drill cuttings currently released during drilling) and also the pressure actually required to achieve the desired flow. When the load of the purge air circuit increases, e.g. due to an increased amount of drill cuttings or as more and more drill rod components are added to the drill string as drilling progresses, the compressor will work harder, ie. still emit the flow determined by the control signal, but at a higher pressure, as long as the maximum permissible pressure is not exceeded as above.
The control of the compressor flow can thus be performed independently of the actual purge air pressure prevailing in the purge air circuit, whereby regulation of the purge air pressure is also not required for flow control. However, it is still advantageous to monitor the pressure in the purge air circuit, e.g. by means of a pressure sensor, so that the compressor flow can be stopped or reduced to a lower flow if the load becomes so high that a maximum pressure predetermined for the compressor or purge air circuit is exceeded. In this case, the drilling can also be stopped or reduced, since the pressure increase may be due to clogging of the purge air duct has taken place or is taking place.
When the appropriate compressor flow has been determined in step 401, the method proceeds to step 402, where it is determined whether the need for compressor flow qd exceeds a parameter value qm for determining the operating mode of the compressor. This determination is performed in one embodiment by a determination of whether the flow requirement qd 10 15 20 25 30 17 exceeds a first value, e.g. 40, 50, 60, 70 or 75% of the maximum deliverable flow of the compressor (it should be understood that this means the maximum deliverable flow of the compressor in the current installation. The compressor itself can be designed to deliver a higher flow if it were to be driven by another power source, such as a power source capable of operating the compressor at a higher speed).
If so, the method proceeds to step 403, wherein the compressor controls the compressor according to said first mode, i.e. speed controlled, and set for outputting a flow qd. If the internal combustion engine is adjustable to a number of fixed speeds and thus speed can not be controlled completely freely, the compressor can be set to deliver the flow obtained at the nearest fixed speed that exceeds the speed required for delivery of the flow qd.
If, on the other hand, the flow requirement qd is less than said first value, the method proceeds to step 404 for control according to said second mode, i.e. control of the flow at the compressor inlet, where the inlet valve is set to deliver the desired flow qd.
It should be understood that the regulation of the compressor can be continuous, and that switching between said first mode and said second mode can take place frequently. For example. determination of the required flow can be performed every second, every 5 seconds, every 10 seconds or at any other suitable interval. The method therefore returns from steps 403, 404, e.g. after a certain time as above has elapsed, to step 401 for new determination of flow requirements. Furthermore, it should be understood that the boundary between speed control and control of the flow at the compressor inlet may be governed by limitations such as that the power source must often be maintained. 18 1a minimum speed, this speed controlling the limit for the transition between control of the flow at the compressor inlet and speed control. For example. For example, the speed may be somewhere in the speed range that causes the compressor to deliver 40 ~ 95% of maximum flow.
Instead of using a fixed limit for said parameter value qw when selecting said first and second modes as above, according to an exemplary embodiment of the present invention, a variable value for q fl is used. According to this embodiment, the compressor is controlled as follows: The compressor will be operated in said first mode when the desired purge air flow qd [expressed in% of maximum flowable from the compressor] is equal to or exceeds a first value qm (expressed in% of the maximum flow of the compressor ), where: m. qdIZíJqOOI (l), B_maX and there: a¿Jmx = maximum motor (compressor) ~ speed, QLmn = lowest motor (compressor) speed, ie. the lowest speed required by other consumers, or the lowest internal combustion engine speed enabling compressor operation. This speed, and thus qm, can thus change during operation.
This thus means that the internal combustion engine will be operated at a higher speed than al as soon as qm exceeds the limit e_mín according to eq. (1) above.
The speed of the internal combustion engine is then controlled according to 10 15 20 l9 w: a) * EL e öm 100, at the same time as the flow in the compressor inlet is set to qi = 100, ie. fully open inlet. e_mín * 100 the internal combustion engine is controlled so that If, on the other hand, qd <6_IT121X á¿ == w ie. at the lowest possible (taking into account other consumers) speed for the power source, while the flow qi past the inlet valve [% of max] is controlled according to the said second mode so that the compressor flow becomes: qf-l- <2) (amy w6_m6X By controlling Depending on, for example, switching on / off of other loads / consumers driven by the power source, the speed w of the power source may vary. The power source may be arranged to be operated at e_min any of a plurality. predetermined substantially fixed speeds, where the different speeds are adapted to be able to deliver sufficient power to connected consumers in relation to the need that currently prevails.Examples of consumers whose power supply should not be affected by the speed control of the compressor consist of the percussion and rotation of the drill string. * _ one turn consists of f s Q (T H1 0 w FA sm (11 th ows W 51) s Q on W) a: I 0.
According to number a) where it can be ensured that the speed of the power source e _ aber f 10 15 20 25 20 can be changed without affecting the function of the rig, as long as the speed of the power source is not less than agvwr.
This can be achieved by dimensioning other consumers connected to the primary drive source in such a way that they become speed-independent for speeds exceeding all. By dimensioning and adapting the hydraulic system's pumps and their control, the hydraulic system can be obtained independently of the speed within the selected speed range. This means that other consumers connected to the power source can be operated at full power already at akßwr. For example. other consumers can be dimensioned so that at a speed á¿Jw, for the power source, e.g. 70-75% of the speed w_mM at which said compressor delivers maximum flow, can deliver full power. Thus, speed control of the compressor can take place from about 70-75% to 100% flow without affecting other consumers. agow, can also consist of other speeds, and can e.g. consists of a speed in the range 40-95% of said speed w eHmax ° In one embodiment a) is fixed, but as shown above, e - ab the speed range can be controlled by current demand. If all subsystems are run in an operating point that is lower than the maximum, the control system can constantly adapt the engine speed to the subsystem that currently has the greatest need, ie. a¿JM above, whereby the speed limit which constitutes the limit between speed control and flow control can vary according to what has been described above also in an embodiment where other consumers are speed dependent for a certain speed a¿ß @ ,.
In the control according to the said second mode, the control unit 18 takes into account the speed of the power source (internal combustion engine) in eq. (2), whereby the desired flow can be ensured independently of variations in the speed of the power source. The power source speed e.g. can be obtained by means of a speed sensor arranged at the output shaft of the power source or the input shaft of the compressor.
Determination of the flow that the compressor should deliver as above can be based on one or more different parameters.
For example. Determination of purge air flow can be based on the current depth of the borehole (it may be advantageous to increase the flow with increasing hole depth, but it should be understood that one and the same flow can also be used when drilling a hole).
The flow of the compressor can also, in whole or in part, be based on the percussion power of the drilling machine (percussion pressure and / or percussion frequency) so that, regardless of percussion effect, it can always be ensured that the flow is adapted to the drill cuttings generated during drilling. percussion frequency) often results in the generation of larger amounts of drill cuttings.
The purge air flow can of course also be controlled independently of the percussion pressure. The type of rock can also be taken into account, whereby the purge air flow can be regulated at least in part depending on the rock type in which drilling takes place.
The control of the flow delivered by the compressor can also be based on an arbitrary combination of the above, or further, control parameters such as a representation of the tool's rotational speed, hole diameter and / or drill rod diameters.
In the automatic control of the compressor above, an automatic determination of the desired purge air flow is also performed based on various parameters by means of a control unit. The desired purge air flow can alternatively be determined by the operator of the rock drilling device, whereby the desired flow can be input from the operator site 10 22 as a control cabin via e.g. an MMI interface, and where the entered value may be based on the operator's experience.
The invention has been described above in connection with an above-ground drilling rig, which carries a drilling machine in the form of a top hammer drilling machine. However, the invention is also applicable for controlling compressors in e.g. DTH (Down-The-Hole) ~ rock drilling rigs. With DTH rock drilling devices, it can be advantageous to control the pressure delivered rather than the flow because the compressor flow drives an air-driven percussion device in the hole, and where a desired working pressure for the percussion device is desired to be maintained, but still by controlling the flow as above.
There are also above-ground solutions of the type shown in Fig. 1 where the top hammer drilling machine is air-driven, whereby pressure control may be preferred for corresponding reasons.

权利要求:
Claims (21)
[1]
A method of controlling a compressor in a rock drilling device, said rock drilling device comprising a power source for driving a first consumer operating in a rock drilling process constituting a compressor, said compressor being arranged for operation according to a first mode and a second mode, where in said first mode the output of the compressor is arranged to be controlled by controlling the speed of said compressor, and where in said second mode the output of the compressor is arranged to be controlled by controlling the air flow at the inlet of the compressor, the method comprising: determining a parameter meter value representing a need for work for said compressor, - controlling the compressor according to said first mode when said parameter meter value representing a need for work for said compressor exceeds a first need, and - controlling the compressor according to said second mode when said parameter term value representing a need for work for said k repressor is less than said first need.
[2]
The method of claim 1, wherein said first parameter value represents a pressure or flow requirement.
[3]
A method according to claim 1, wherein said first parameter value represents a flow requirement, wherein said flow requirement is determined independently of the prevailing pressure in the flow circuit after the compressor.
[4]
A method according to claim 3, wherein, when the prevailing pressure in the flow circuit after the compressor is less than a first pressure, said flow requirement is determined independently of said prevailing pressure in the flow circuit after the compressor. 10 15 20 25 Lu CD 24
[5]
A method according to any one of claims 1-4, wherein said rock drilling device comprises at least one second consumer driven by said power source, the method further comprising determining the minimum speed of said power source required for operation of said at least one second consumers, wherein control according to said second mode is performed when said first parameter value is less than the work emitted by the compressor at said determined minimum speed for said power source.
[6]
A method according to any one of claims 1-4, wherein said rock drilling device comprises at least one second consumer driven by said power source, the method further comprising determining the minimum speed of said power source required for operation of said at least one second consumers, wherein control according to said first mode is performed when said first parameter value is equal to or exceeds the work done by the compressor at said determined minimum speed for said power source,
[7]
A method according to any one of claims 1-6, wherein the method further comprises changing said first need for work during operation.
[8]
A method according to any one of claims 1-7, wherein said rock drilling process includes at least the sub-processes flushing and at least one of stroke and rotation.
[9]
9. A system for controlling a compressor at a rock drilling rig, wherein the rock drilling device comprises a power source for driving a compressor acting as a first consumer acting in a rock drilling process, characterized in that the system comprises: 10 C 20 25 - control means for controlling said compressor according to a first mode and a second mode, where in said first mode the output of the compressor is arranged to be controlled by controlling the speed of said compressor, and where in said second mode the output of the compressor is arranged to be controlled by controlling the inlet of the compressor, and - determining means for determining a parameter meter value representing a need for work for said compressor, - means for controlling the compressor according to said first mode when said parameter meter value representing a need for work for said compressor exceeds a first needs, and means for controlling the compressor according to said second mode when said p arameter meter value representing a need for work for said compressor is less than said first need.
[10]
The system of claim 9, wherein said rock drilling device comprises at least a second consumer driven by said power source.
[11]
A system according to any one of claims 9-10, further comprising means for, when controlling according to said second mode, controlling the air flow at the inlet of the compressor.
[12]
A system according to any one of claims 9-11, further comprising means for, when controlling according to said second mode, controlling the flow at the inlet of the compressor by regulating the opening area of the compressor inlet towards the environment.
[13]
A system according to claim 12, wherein the pressure in the compressor interior is arranged to be controlled by regulating the compressor | m = OPP the opening area of the barrel towards the surroundings by means of an electrically controllable valve. 10 l5 20 25 30 26
[14]
A system according to any one of claims 9-13, further comprising means for, when controlling according to said first mode, controlling the speed of said compressor by controlling the speed of said power source.
[15]
A system according to any one of claims 9-14, further comprising control means for controlling the compressor according to said first or second mode based on a first electrical control signal, said first control signal comprising a representation of a desired work delivered from said compressor .
[16]
A system according to claim 15, wherein said control means consists of a control unit arranged to output a second electrical control signal to control means for controlling said compressor inlet and / or speed for said power source.
[17]
A system according to claim 15 or 16, wherein determining said first control signal is arranged to be performed at least in part based on one or more of the group: a pressure in the flow circuit, actual hole depth, a representation of the tool's rotational speed, a representation of a percussion effect, hole diameter, drill rod diameter, rock type.
[18]
A system according to claim 10, wherein said at least one second consumer driven by said power source is dimensioned such that said at least one second consumer is independent of the power source speed for speeds exceeding a speed where we _ uber å) e _ a _ f constitute a lower speed than the speed at which said compressor delivers maximum flow.
[19]
A system according to claim 18, wherein said speed a¿Jæ, 27 constitutes a speed in the range 40-95% of said speed a¿JmX at which said compressor emits maximum flow.
[20]
A system according to any one of claims 9-19, wherein said compressor is a fixed displacement compressor.
[21]
Rock drilling device, characterized in that it comprises a system according to any one of claims 9-20.

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同族专利:

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公开号 | 公开日

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EP2609281A4|2017-08-09|

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SE535418C2|2012-07-31|

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AU2011293948A1|2013-03-14|

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WO2012026875A1|2012-03-01|

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US20130140089A1|2013-06-06|

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EP2609281A1|2013-07-03|

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AU2011293948B2|2014-09-25|

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US9347285B2|2016-05-24|

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EP2609281B1|2019-10-23|

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CN103069101A|2013-04-24|

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CN103069101B|2016-08-10|

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法律状态:

优先权:

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申请号 | 申请日 | 专利标题

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SE1000869A|SE535418C2|2010-08-26|2010-08-26|Method and system for controlling a compressor at a rock drilling device and rock drilling device|SE1000869A| SE535418C2|2010-08-26|2010-08-26|Method and system for controlling a compressor at a rock drilling device and rock drilling device|

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US13/261,587| US9347285B2|2010-08-26|2011-08-25|Method and system for controlling a compressor at a rock drilling apparatus and a rock drilling apparatus|

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EP11820260.5A| EP2609281B1|2010-08-26|2011-08-25|Method and system for controlling a compressor at a rock drilling apparatus and a rock drilling apparatus|

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CN201180041455.2A| CN103069101B|2010-08-26|2011-08-25|Control method and system and the rock drilling equipment of the compressor of rock drilling equipment|

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AU2011293948A| AU2011293948B2|2010-08-26|2011-08-25|Method and system for controlling a compressor at a rock drilling apparatus and a rock drilling apparatus|

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PCT/SE2011/051027| WO2012026875A1|2010-08-26|2011-08-25|Method and system for controlling a compressor at a rock drilling apparatus and a rock drilling apparatus|