• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    12 SUMMARY Hydraulic percussion, of the valveless percussion type, comprising a pre-charged gas accumulator connected to a working chamber to enable lighter, cheaper and, from a fatigue aspect, sustainable percussion for rock drilling equipment and hydraulic skewers. Furthermore, piston with gas accumulator of piston type with built-in brake chamber, suitable for such brake chamber.
    公开号:SE1000885A1
    申请号:SE1000885
    申请日:2010-08-31
    公开日:2012-03-01
    发明作者:Maria Pettersson；Anders Johansson
    申请人:Atlas Copco Rock Drills Ab；
    IPC主号:
    专利说明:

    2 percussion instruments also perform the work of the changeover valve by opening and closing during their movement in the cylinder bore for supply and drainage of pressurized propellant in a manner which gives an alternating pressure as above in at least one of two drive chambers separated by a propellant on the piston. A prerequisite for this to work is that ducts, arranged in the machine housing for pressurization and drainage of a chamber, open towards the cylinder bore so that the orifices are separated in such a way that short-circuited connection does not occur directly between supply duct and drainage duct at any position below the piston front. and return movement. Connection between supply duct and drainage duct normally exists only via the gap seal formed between the drive part and the cylinder bore. Otherwise, large losses would occur, as the propellant had to pass directly from the high-pressure pump to the tank without any useful work being done.
    In order for the piston to be able to continue its movement from the time a channel for draining a drive chamber is closed, until a channel for pressurizing the same drive chamber is opened, it is required that the pressure in the drive chamber changes slowly as a result of a change in volume.
    This can be done by making the volume of at least one drive chamber large in relation to what is normal for traditional percussion type percussion instruments. The volume needs to be large because the commonly used hydraulic oil has low compressibility. We then define the compressibility K as the ratio between the relative volume change and the pressure change according to K = (dv / V) / dP. However, it is more common to use the compression module ß as a quantity for the compressibility, which is the inverse of the compressibility as we defined it above, ie ß = dP / (dV / V). The unit for the compression module is Pascal. 10 15 20 25 3 The volume must be large enough so that the pressure in the chamber during the volume change that the chamber undergoes during the movement of the percussion piston towards the opening of the channel for pressurizing the chamber, will not be sufficient to reverse the piston movement before the channel is opened.
    U.S. Pat. No. 4,282,937 discloses a wear-free hydraulic percussion device with two drive chambers, where the pressure changes in both of these chambers. Both drive chambers have large effective volumes in that they are in constant communication with volumes adjacent to the cylinder bore.
    By SU 1068591 A a wear-free hydraulic percussion is known according to another principle, namely alternating pressure in the upper drive chamber, and constant pressure in the lower, ie. the nearest connection for the tool. Here is the upper drive chamber, ie. the one where the pressure changes, of a substantially larger volume than the lower one, which has a constant pressure.
    A problem with large drive chambers with constant pressure fluctuations between system pressure and return pressure, ie. approximately atmospheric pressure, is that the engine house itself tends to suffer from cracking due to material fatigue. To avoid this, constructions with thick and complex castings with partitions have hitherto been required, and the consequent high cost and weight.
    OBJECTS AND MAIN FEATURES OF THE INVENTION An object of the present invention is to provide a design of wear-free hydraulic percussion devices which makes it possible to counteract the above problems, and enable lighter and at the same time more durable constructions with respect to cracking in the machine housing itself. This is achieved by means described in the independent claims. Further advantageous embodiments are described in the dependent claims.
    SU 1068591 not only discloses an alternative embodiment consisting of constant pressure in the lower drive chamber and alternating pressure in the upper.
    In addition, two accumulators are connected directly to the drive chamber with alternating pressure. The purpose of this is to improve efficiency. Our problem with cracking in the engine house due to. material fatigue is not mentioned at all. Furthermore, it is obvious that the diaphragm accumulators disclosed in SU 1068591 must have a very limited service life, since the diaphragms with the stroke frequency will bottom inside the accumulators. This does not constitute a practically useful construction.
    However, it has been found that a gas accumulator connected directly to a working chamber in a hydraulic percussion device for rock drilling or in hydraulic skewers for demolition has a markedly positive effect with regard to the risk of material fatigue with accompanying freight cracking. The invention constitutes a solution of this kind. In order for the gas accumulator to withstand the extremely difficult conditions with pressure pulsations between system pressures, e.g. 250 bar and return pressure eg 5 bar, and with frequencies in the order of up to 150 Hz it is required that the elastic membrane is replaced by a solid body such as a piston mounted back and forth in a cylinder bore inside a gas accumulator.
    It is further advantageous that the gas accumulator has means for braking the accumulator piston at least in front of one of its turning positions. Such a means can be a brake chamber, which the accumulator piston with a good fit e.g. less than 0.1 mm, preferably 0.05 mm, may run into.
    The invention provides a solution which is applicable to percussion instruments which have alternating pressures on only one side, as well as those with alternating pressures on both sides. In this latter case, a gas accumulator is connected to each drive chamber.
    However, a preferred embodiment is a percussion operating with constant pressure in one chamber achieved usually by the chamber being connected during the whole, or at least substantially the whole, percussion cycle to a constant pressure source, usually directly to the source of system pressure or percussion pressure.
    Percussion of the type described above can be included as an integral part of rock and / or concrete felling equipment such as rock drills or hydraulic skewers. During operation, these machines or skewers should usually be mounted on a carrier which may comprise one or more of the following means: means for alignment, means for positioning and means for feeding drilling machine / skewers against machined rock or concrete elements and further means for controlling and monitoring the processing process. Furthermore, means for propelling and guiding the carrier itself may be included. Such a carrier can be a rock drilling rig.
    Brief Description of the Drawings Fig. 1 shows a schematic diagram of a hydraulic percussion instrument with alternating pressure in the chamber to the right. Fig. 2. Shows a piston-type gas accumulator with brake chamber at the two turning positions of the accumulator piston 10 15 20 25 6 Fig. 3 Shows a piston-type gas accumulator with brake chamber at the turning position of the accumulator piston on the hydraulic side.
    Detailed Description of Preferred Embodiments A number of exemplary embodiments of the invention are described in the following with reference to the accompanying drawings.
    The scope of the invention should not be construed as limited to these embodiments, but defined by the claims.
    Fig. 1 schematically shows a hydraulic percussion device with alternating pressure on the top of the piston and constant pressure on its underside, ie the side facing the connectable tool. The first drive chamber 105 is connected via pressure duct 140 to system pressure e.g. 250 bar. As Fig. 1 is drawn, the second chamber 120 is at the moment depicted connected via the return channel 135 to return pressure. Thus, the force acting on the drive surface 110 will move the percussion piston to the right. This causes the channel 135 to close and a pressure to build up in the chamber 120. As the pressure builds up slowly, the piston will reach so far that the connecting channel 170 opens the connection between drive chambers 1 and 2 and the system pressure takes over in the second chamber 120. is larger than the driving surface 110, the percussion piston will now be driven to the left. In this case, the connecting channel 110 is first closed and later the return channel is opened and the pressure drops in the second chamber 120. A new cycle is thus started with the piston being driven again to the right by the system pressure acting on the driving surface 110.
    The drive chambers do not have to be large now, as the compressibility comes from the precharged gas accumulators. Chamber 120 is dimensioned based on the space requirements for the ducts and connections to the gas accumulators. A volume that without gas accumulators would have been several liters is now only a few deciliters.
    A working machine can have the following essential dimensions: The diameter of the drive part 165 on the percussion piston 44 mm. Piston rod diameter: 36 mm. Drive part length: 100 mm. Distance from the right edge of the return channel 135 in the mouth of the cylinder bore to the corresponding left edge of the left mouth of the connecting channel 170: 93 mm. Piston weight 4.5 kg. System pressure 230 bar. Finally, the total volume of the accumulators is 90 cubic centimeters each and a preload pressure of l90x105PA for one accumulator and 15x105PA for the other.
    If only one accumulator is used, will the volume be 74 cm Charging of the accumulators' gas pressure takes place through the connection 230; 330. The connection to the hydraulic oil in the working chamber takes place via 290; 390.
    It is advantageous to have grooves 260; 360 for seals 370 formed in the cylinder bore 210; 31O of the accumulators.
    A drainage channel 280; 380 is advantageous to insert between the seals to avoid mixing gas and oil.
    Brake chambers 240, 250; 340 are designed in the accumulator housing.
    The accumulator piston 220; 320 is received in these brake chambers on a battery accumulator 220; 32O is received in these brake chambers in a manner which reduces the speed before turning. This significantly increases the life of the accumulator piston.
    From an efficiency point of view, it is advantageous to have double accumulators connected as described above. A high pressure with precharge pressure <system pressure and a low pressure accumulator with precharge pressure> return pressure, but << system pressure.
    权利要求:
    Claims (1)
    [1]
    1. 0 15 20 25 l. PATENT REQUIREMENT Hydraulic percussion device for use in rock and / or concrete cutting equipment comprising a machine housing with a first cylinder bore, a piston mounted therein arranged to repeatedly perform a reciprocating movement relative to the machine housing during operation. exert blows directly or indirectly against a rock and / or concrete cutting tool connectable to the equipment, and where the piston includes a drive part separating a first and a second drive chamber formed between the piston and the engine housing and where these drive chambers are arranged to include a pressurized drive medium during operation , and further wherein the machine housing includes channels opening into the first cylinder bore and arranged to include the drive medium during operation and to, by means of the piston during its movement in the first cylinder bore, open and close towards at least the second drive chamber so that at least this second drive chamber has a periodically changing pressure to maintain d reciprocating piston movement, and that positions for the mouth of the channels axially in the first cylinder bore and the expansion of opening and closing piston parts are adapted to keep this second drive chamber closed for supply or drainage of drive medium present in the chamber for a distance between a first channel opening in connection to a first turning position of the piston and the opening of a second channel in connection with a second turning position of the piston and that the movement of the piston during this distance continues during compression or expansion of this drive chamber volume, where the size of this volume is further adjusted to obtain slow pressure change during said distance so that the hydraulic percussion thereby constitutes a so-called valveless hydraulic percussion, characterized in that said second drive chamber is designed to comprise during operation a gas accumulator, said gas accumulator comprising a second cylinder bore with a movable cylinder in this second cylinder bore monter ad accumulator piston, wherein said accumulator piston separates the propellant in the second propulsion chamber from a pressurized gas enclosed in a closed space of the gas accumulator, and where the volume of said space during operation varies with the frequency of the percussion due to the reciprocating movement of the accumulator piston. Hydraulic percussion device according to claim 1, wherein the gas accumulator is designed with a brake chamber to accelerate the braking of the accumulator piston before the turning position of the accumulator piston. Hydraulic percussion device according to claim 2, wherein the accumulator piston and brake chamber are designed so that, upon penetration of the accumulator piston into the brake chamber, a gap less than 0.5 mm occurs between them, this gap constituting a gap seal between the brake chamber and the other drive chamber. Hydraulic percussion device according to one of the preceding claims, comprising at least two sealing elements for sealing between the accumulator piston and the second cylinder bore. Hydraulic percussion device according to claim 4, wherein the second cylinder bore comprises at least two grooves for mounting said sealing elements. Hydraulic percussion device according to claim 4 or 5, wherein the gas accumulator comprises a channel opening into the second cylinder passage between the two sealing elements for draining propellant to a tank for propellant. 5 10 10. Rock drilling rig comprising rock drilling machine according to claim 7. 8. '9. ll. Gas accumulator housing for connection to work chamber 11 Rock drilling machine comprising hydraulic percussion device according to one of the preceding claims. Hydraulic skewers comprising percussion instruments according to any one of claims 1 to 6. Carriers comprising rock drilling machines according to claim 7 or hydraulic skewers according to claim 8, further comprising one or more of the following means: means for alignment, means for positioning and means for feeding rock drills or hydraulic skewers to machined rock or concrete element. In hydraulic percussion according to claim 1, during operation including a pressurized drive medium, the pressure of which continuously pulsates between system pressure and return pressure, said gas accumulator housing comprising a cylinder bore for mounting an accumulator piston for reciprocating movement in said cylinder bore, further comprising a brake chamber for receiving the accumulator piston causes a deceleration of the accumulator piston before one of its turning positions. Accumulator piston intended to be mounted in a gas accumulator housing according to claim 11, the accumulator piston comprising part for penetrating said brake chamber with a gap of less than 0.1 mm. A gas accumulator comprising a gas accumulator housing according to claim 11 and an accumulator piston according to claim 12.
    类似技术:
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    引用文献:
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    法律状态:
    优先权:
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    JP2013527035A| JP5822406B2|2010-08-31|2011-07-01|Fluid pressure shock mechanism used in equipment for processing rock and concrete|
    CA2809789A| CA2809789C|2010-08-31|2011-07-01|Hydraulic impact mechanism for use in equipment for treating rock and concrete|
    PCT/SE2011/050898| WO2012030272A1|2010-08-31|2011-07-01|Hydraulic impact mechanism for use in equipment for treating rock and concrete|
    ZA2013/00919A| ZA201300919B|2010-08-31|2013-02-04|Hydraulic impact mechanism for use in equipment for treating rock and concrete|
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