• 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:

    公开号:SE1000703A1
    申请号:SE1000703
    申请日:2010-06-30
    公开日:2011-12-31
    发明作者:Thomas Oestling；Linda Goethlin
    申请人:Atlas Copco Rock Drills Ab；
    IPC主号:
    专利说明:

    Figure 2 shows an enlarged section of one of the boom gaps 11 of the known driver 3, the neck adapter 2 of the drill steel 2 and the drill sleeve 5 from fi gur 1.
    At the bottom of the figure, the direction of rotation of the drill sleeve 5 is shown by an arrow.
    The carrier 3 is arranged so that the ratio between the diameter of the bottom circle 1d2 of the boom profile 4 and the top circle d1 is 1.38.
    The top circle diameter D2 for the neck adapter booms is adjusted so that it constitutes approximately 98% of the bottom circle diameter d2 for the carrier 3 boom profile 4. The arrangement and contact pressure between the neck adapter and the carrier 3 bars 10 causes small amounts of the carrier 3 material 12 to be pressed down to the transmission of torque. The pressed material constitutes fracture indications or degrees 13 on the radii 12 and thus spoils its function of protecting against fatigue fractures. The figure shows how these degrees 13 initiate cracking in the root radii 12. The object of the present invention is to, according to the claims, obtain a carrier in which the previously mentioned disadvantages are overcome. In the present invention, the polygon profile and the boom profile are arranged in a new way which reduces the stresses and distributes them symmetrically in the carrier. The boom profile of the carrier is designed so that, the degree resulting from the wear, is separated from the root radius. An additional advantage of the invention is that it can be introduced without appreciable increases in the external dimensions of the gear housing.
    The invention will be described in more detail with the aid of the accompanying figures 3-6. Figure 3 shows a reduced section of a carrier according to the present invention. Figure 4 shows an enlarged detail section of the driver from Figure 3, mounted in a rock drill gearbox. Figures 5 and 6 show alternative embodiments of the carrier's boom profile.
    Figure 3 shows a section of a carrier 3. The carrier 3 has substantially the same section along its entire length distribution. The length of the carrier 3 is adapted so that an acceptable contact pressure is obtained during the transmission of torque. The carrier 3 is made of bronze, but can also be made of ductile iron or other materials with similar friction properties.
    The section of the carrier 3 is limited outwards by curves, or more precisely arcs, connected to a closed geometry 6; The closed geometry 6 of the present invention comprises four sides 7 and four corners 8 and is approximated by a convex polygon. A polygon is by definition a plane figure bounded by straight lines, i.e. straight curves. If straight lines are drawn between the intersections of the imaginary extensions of the sides 7 of the closed geometry 6, a polygon is formed. (The extensions and the polygon 10 15 20 25 30 35 40 3 are shown with dashed lines in the fi clock.) This fact defines the meaning of the term “approximately” in this context.
    Each side 7 comprises an arc of a circle and the circular arcs of all the sides 7 have the same radius and length. The corners 8 are arranged in a similar manner. Each corner 8 comprises an arc of a circle and the circular arcs of all the corners 8 have the same radius and length. It is also possible to let the sides 7 or the corners 8 comprise other types of arcs and / or curves than circular arcs.
    The connection between the arcs is arranged at points where the keys to the connected arcs coincide. This means that high sputtering concentrations do not occur in the carrier 3.
    The section 3 of the carrier 3 is limited inwards by a boom profile 4 with eight booms 10 and eight boom hatches 11. It is also possible to arrange the boom profile 4 with twelve or sixteen booms 10. The boom profile 4 is arranged so that four of the bars 10 have a symmetrical distribution around imaginary symmetry line 9 extending from the center of the carrier 3 and through the closed geometry 6. The lines of symmetry 9 are drawn so that the geometry 6 is symmetrically distributed around the lines of symmetry 9. It is best to arrange the boom profile 4 with eight or twelve bars 10 and so that four of its barriers 10 have a symmetrical distribution around imaginary lines of symmetry 9 which extend from the center of the carrier 3 and through the corner 8 of the closed geometry 6. The arrangement means that the stresses are minimal and symmetrically distributed in the carrier 3.
    These positive properties are independent of the direction of rotation of the driver 3 and the risk of incorrect mounting is therefore small. It is also possible to distribute four of the boom profile 4 boom hatches 11l symmetrically around the lines of symmetry 9 through the corners 8. The stresses will then be slightly higher in the carrier 3, but still lower than in the previously described known carrier.
    The booms 10 or boom hatches 11 of the boom profile 4 can also be arranged asymmetrically around the lines of symmetry 9 through the corners 8. Although the stresses have a displaced symmetrical distribution in the driver 3 during the transmission of torque, the distribution can still be favorable for transmission in a specified rotation. The carrier 3 according to the latter embodiment must be mounted so that it obtains a specified direction of rotation.
    The ratio between the diameters of the boom circle 4, the bottom circle d2 and the top circle d1 is arranged larger than with previously known carriers. (d2 and dl are shown with dashed circles in fi guren.) This means advantages that will be described in detail in Figure 4. Good results can be achieved at a ratio of 1.39 or higher. However, it is best to arrange the boom profile 4 so that the ratio d2 / dl is 1.48. Conditions greater than 1.48 may require significant increases in the external dimensions of the gearbox. 10 15 20 25 30 35 40 4 Figure 4 shows how the new ratio d2 / d1 = 1.48 (see Figure 3) contributes to creating spaces 14 between the top of the neck adapter's booms (drill steel 2) and the bottom of the driver's 3 boom hatches 11. The drill steel 2 neck adapter will therefore be guided radially by the tops and anchors of the boom profile 4 booms 10. The figure also shows how the top circle diameter D2 for the neck adapter booms is about 95% of the bottom circle diameter d2 for the driver 3 boom profile 4. According to the same process, as previously described in Figure 2, a grade 13 is formed as a result of the wear. Thanks to the spaces 14, however, the degrees 13 are never pressed so deep into the bottoms of the boom hatches 11 that they reach the root radii 12 in the transition to the booms 10. The degrees 13 can therefore be said to be separated from the root radii 12 and the new carrier 3 is thus better protected against fatigue failure than the previously known one from Figure 1-2.
    The bottoms in the boom profile 4 boom hatches 11 are arranged in Figures 3-4 as circular arcs with the bottom circle diameter d2. Figure 5 and Figure 6 show alternative arrangements of the boom hatches 4 boom hatches 1 1. In Figure 5, the bottoms comprise an arc of a circle with a much smaller diameter than the bottom circle diameter d2. In Figure 6, the bottoms comprise a straight line and semicircular arcs in the transition to the booms 10. The tops of the boom profile 4 booms 10 are arranged as circular arcs with the top circle diameter dl.
    However, it is possible to arrange the peaks with other diameters and / or curves other than circular arcs. The bottom circle diameter d2 and the top circle diameter d1, respectively, shall in the above arrangements, and in similar embodiments, be defined as the diameters of the imaginary circles (shown dashed in the figures) which barely accommodate the curves in the area between the circles.
    In the description above, the new arrangement for the carriage 3 of the carrier 3 is introduced so that it comprises all the booms 10 of the boom 4 and boom 1 l. In certain circumstances, however, it is possible to arrange some of the booms 10 and boom 11 of the boom 4 according to the embodiment of the present invention and remaining according to the design for the boom profile in known carriers. Such a "combined" carrier shall be deemed to be covered by the patent claims of the present application.
    权利要求:
    Claims (2)
    [1]
    Carrier (3), for transmitting the torque and rotational movement from a drill sleeve (5) to a drill steel (2), the section of the carrier (3) being limited outwards by curves, in particular arcs, connected to a closed geometry (6) which approximately is described by a polygon, and is bounded inwards by a boom profile (4), characterized in that the geometry (6) comprises four sides (7) and four corners (8) and in that the boom profile (4) comprises 8, 12 or 16 bars (1 0). Carrier (3) according to claim 1, characterized in that four of the boom profile (4) booms (10) or boom hatches (1 1) are symmetrically distributed around lines of symmetry (9) through the geometry (6). . Carrier (3) according to Claim 1 or 2, characterized in that four of the boom profile (4)'s booms (10) are symmetrically distributed around the lines of symmetry (9) and in that the lines of symmetry (9) extend through the corners (8). . Carrier (3) according to one of Claims 1 to 3, characterized in that each side (7) comprises an arc of a circle and in that the circular arcs of all sides (7) have the same radius and length and in that each corner (8) comprises an arc of a circle and of that all the circular arcs of the corners (8) have the same radius and length. . Carrier (3) according to claim 4, characterized in that the connection between the arches is arranged at points where the keys to the connected arches coincide. Carrier (3) according to one of Claims 1 to 5, characterized in that the ratio between the bottom circle (d2) and the top circle (d1) of the boom profile (4) is 1.39 or higher. Carrier (3) according to one of Claims 1 to 6, characterized in that the ratio between the bottom circle (d2) and the top circle (d1) of the boom profile (4) is 1.48 = b0.0
    [2]
    Rock drilling machine, comprising a drill sleeve (5) and a driver (3) for transmitting torque and rotational movement from the sleeve (5) to a drill steel (2), characterized in that the driver (3) is designed according to any one of claims 1-7. .
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    同族专利:
    公开号 | 公开日
    EP2588706B1|2018-12-26|
    ZA201208893B|2014-01-29|
    JP2013531754A|2013-08-08|
    JP6061847B2|2017-01-18|
    AU2011271712B2|2015-11-26|
    CA2803297A1|2012-01-05|
    EP2588706A4|2017-12-06|
    CA2803297C|2018-08-21|
    EP2588706A1|2013-05-08|
    WO2012002876A1|2012-01-05|
    AU2011271712A1|2013-01-10|
    CN102985635B|2014-11-12|
    US20130114999A1|2013-05-09|
    SE534930C2|2012-02-21|
    ES2716556T3|2019-06-13|
    CN102985635A|2013-03-20|
    US10174565B2|2019-01-08|
    引用文献:
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    SE398066B|1975-03-18|1977-12-05|Atlas Copco Ab|METHOD AND DEVICE FOR STRIKING PROCESSING FOR DAMPING THE RECYCLE FROM A WORKING TOOL|
    US4194581A|1975-03-22|1980-03-25|Walter Hans P|Deep drill hammer|
    US4134460A|1976-05-15|1979-01-16|Firm. Ing. Gunter Klemm|Hydraulic drilling device|
    SE423253B|1976-11-04|1982-04-26|Atlas Copco Ab|Rock drilling equipment|
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    DE3242274C1|1982-11-15|1984-05-30|Danfoss A/S, Nordborg|Tooth coupling between pinion and cardan shaft of an internal-axis rotary piston machine|
    WO1986002694A1|1984-10-22|1986-05-09|Atlas Copco Aktiebolag|A rock drill|
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    DE102009024455A1|2009-06-10|2011-01-05|Audi Ag|Built-shaft element, in particular built camshaft for valve-controlled internal combustion engines|US10221887B2|2012-12-06|2019-03-05|The Hive Global, Inc|Self locking bearing preload adjuster|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    SE1000703A|SE534930C2|2010-06-30|2010-06-30|Carriers for transferring torque and rotation to a drill steel and rock drill|SE1000703A| SE534930C2|2010-06-30|2010-06-30|Carriers for transferring torque and rotation to a drill steel and rock drill|
    CA2803297A| CA2803297C|2010-06-30|2011-06-01|Driver for torque and rotation transfer from a rotational chuck to a drill steel|
    CN201180032053.6A| CN102985635B|2010-06-30|2011-06-01|Driver for torque and rotation transfer from a rotational chuck to a drill steel|
    EP11801233.5A| EP2588706B1|2010-06-30|2011-06-01|Driver for torque and rotation transfer from a rotational chuck to a drill steel|
    US13/261,539| US10174565B2|2010-06-30|2011-06-01|Driver for torque and rotation transfer from a rotational chuck to a drill steel|
    JP2013518324A| JP6061847B2|2010-06-30|2011-06-01|A driver that transmits torque and rotation from the rotating chuck to the drill steel|
    ES11801233T| ES2716556T3|2010-06-30|2011-06-01|Spindle for torque transfer and rotation from a rotating mandrel to a steel drill|
    AU2011271712A| AU2011271712B2|2010-06-30|2011-06-01|Driver for torque and rotation transfer from a rotational chuck to a drill steel|
    PCT/SE2011/050690| WO2012002876A1|2010-06-30|2011-06-01|Driver for torque and rotation transfer from a rotational chuck to a drill steel|
    ZA2012/08893A| ZA201208893B|2010-06-30|2012-11-26|Driver for torque and rotation transfer from a rotational chuck to a drill steel|
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