• 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:
    A circular cylindrical impact transfer member 2 for a drilling machine adapted to transfer kinetic energy to an impact receiving member 4. The impact transfer member has a diameter dmax, and includes a side surface 12 and an impact surface 6. The impact transfer member is adapted to transfer the kinetic energy to the impact receiving member is concentric with respect to the cross-sectional area of the percussion piston, has a diameter da, where da <dmax and has a width wa which at the moment of contact with the percussion receiving part is less than 0.2 dnaax. (Figure 4)
    公开号:SE535393C2
    申请号:SE1150383
    申请日:2011-05-03
    公开日:2012-07-24
    发明作者:Fredrik Saf；Thomas Oestling
    申请人:Atlas Copco Rock Drills Ab；
    IPC主号:
    专利说明:

    From the published patent application GB-2136725 a drilling machine with a percussion piston is known, where the percussion piston has a piston nose in the form of a truncated cone, i.e. the transition from the side surface of the percussion piston to the percussion surface is chamfered.
    U.S. Patent No. 6,273,199 discloses a rock drilling arrangement comprising a percussion piston and a neck adapter.
    And U.S. Patent Application US-2009 / 0133,893 discloses a hand-held tool with a reciprocating percussion piston. The striking piston has a spherically shaped striking surface.
    There are solid pistons and pistons with a central longitudinal hole.
    The neck adapter, to which the percussion piston transmits the shock wave, can be provided with a so-called stud hole on the surface which the percussion piston hits. The double hole is a centrally located hole and was added in connection with the manufacture of the neck adapter. The stud hole has a diameter which, for example, can be about 8 mm.
    The stud hole causes special stresses for the centrally located parts of the percussion impact surface. Due to the large forces to which the impact surface is subjected, it has been found that material movements take place in these central parts, which can simply be explained as the parts of the impact piston located above the stud heel "moving" in the direction of impact.
    In this context, it is important to mention that the neck adapter is a wear part that is replaced much more often than the percussion piston.
    Furthermore, it has been found that due to wear in bushings and so-called carriers, among other things, the percussion piston does not hit the neck adapter completely flat in every stroke. This causes high contact voltages in the contact surfaces.
    In view of the above review of the prior art, the object of the present invention is to provide an improved design of the front part of the stroke transfer member which minimizes the stress concentration and thus extends the life of the stroke transfer member which is economically advantageous.
    SUMMARY OF THE INVENTION The above objects are achieved by the invention defined by the independent claim.
    Preferred embodiments are defined by the dependent claims.
    The impact transfer member according to the present invention is thus provided with an annular active surface which is concentric with respect to the cross-sectional area of the impact transfer member, has a diameter which is smaller than the diameter of the impact piston, and that the active surface has a width which at the moment of contact . This applies to straight stops between the stroke transmission part and the stroke reception part.
    When using a stroke transfer member according to the present invention, experiments have shown that the stroke speed can be increased by more than 20%, from for example 10 in / s to more than 12 m / s.
    In addition, the advantage is achieved that when using the stroke transfer part according to the present invention at the stroke speeds normally used today, a longer service life is obtained, as well as a better resistance to oblique abutments.
    According to the present invention, the striking surface is designed with a shape that minimizes the stress concentration. Thanks to the annular active surface fl, the point of contact is moved away from the side surface and more towards the center of the impact surface, which is advantageous since a more even distribution of the forces to which the impact transfer part is subjected is then achieved. Even with an oblique stop between the stroke transfer part and the stroke receiving part, according to the invention, an advantageous reduction of the stress concentration is achieved, among other things, in that the contact surface is relatively larger and that the contact point is moved away from the side surface and more towards the center of the stroke surface. According to a preferred embodiment, the central parts of the striking surface are provided with a recess which in the most central parts may be provided with a central pin. By arranging a central patch, it has been found that the shock waves are spread away from the central parts of the stroke transfer part, which is advantageous as the central parts of the stroke transfer part are not exposed to extreme loads due to this design.
    Brief Description of the Drawings Figure 1 is a side view schematically illustrating parts of a drilling machine to which the present invention may be applied.
    Figures 2a-2c are side views schematically showing a number of known designs of the striking surface.
    Figure 3 is a side view schematically illustrating the front part of a percussion piston according to a first embodiment of the present invention.
    Figure 4 is a side view schematically illustrating the front of a percussion piston according to a second embodiment of the present invention.
    Figures 5a-5c are a view against the direction of impact which schematically illustrates the impact surface, at straight impact, according to the first embodiment of the invention.
    Figures 6a-6c are a view of the striking diagram schematically illustrating the striking surface, at straight impact, according to the second embodiment of the invention.
    Figures 7a and 7b illustrate a striking surface according to the prior art and according to the first embodiment of the present invention, respectively.
    Figures 8a and 8b illustrate a striking surface according to the prior art and according to the second embodiment of the present invention, respectively.
    Detailed Description of Preferred Embodiments of the Invention Figure 1 shows a schematic view of parts of a drilling machine to which the present invention may be applied.
    Figure 1 illustrates the invention by showing an impact transfer member in the form of an impact piston and how it cooperates with a neck adapter. However, the present winding is generally applicable to other parts of a drilling machine where the transmission of shock waves is to take place. For example, between the percussion piston and the neck adapter, between the neck adapter and the drill steel, and between the drill steel and the drill bit. The invention will be exemplified by describing in detail how it is implemented for a percussion piston.
    Figure 1 thus shows a percussion piston 2 arranged to perform a reciprocating movement which is illustrated by the double arrow. The percussion piston is arranged to transmit its kinetic energy in the form of shock waves to a neck adapter 4. The shock waves are formed at the contact between the front surface of the percussion piston, the striking surface 6, and the neck adapter.
    The percussion piston and neck adapter have a substantially circular cross-section and are arranged in a drilling machine housing (not shown) via a number of suitably designed bushings 8 to allow movement in the longitudinal direction. The bushings are only schematically drawn in the fi clock. The number and where they are arranged can of course vary depending on the type of drill.
    The neck adapter is applied to a rotation and then transmits this kinetic energy and the shock wave energy to a drill steel (not shown) which in turn is provided with a drill bit (not shown) for drilling in rock.
    The housing around the drill comprises at its front end and around the neck adapter a part which can be opened to be able to change the neck adapter if necessary. The rotation is generated by a motor (not shown) and is applied in a known manner to the neck adapter via a number of splines 10.
    The invention will now be described with reference to Figures 3-6.
    Figures 3 and 5 illustrate the first embodiment and Figures 4 and 6 illustrate the second embodiment. It should be noted that the striking surface shown in Figures 5 and 6 illustrates the change of the active surface during a straight impact.
    The present invention relates to a circular-cylindrical percussion transfer part 2, here illustrated as a percussion piston 2, for a drilling machine adapted to transfer kinetic energy to a percussion receiving part 4, here illustrated as a neck adapter 4 (see Figure 1). The striking piston has a diameter dmax, and comprises a side surface 12 and a striking surface 6.
    According to the invention, the percussion transmission part (percussion piston) is adapted to transmit the kinetic energy to the percussion receiving part (neck adapter) with an annular active surface 14 (see Figures 5 and 6). the impact receiving part. The annular active surface is concentric with respect to the cross-sectional area of the percussion transfer member (percussion piston), has a diameter da, where da <dmax, preferably da <0.75dmax. The active surface has a width w, which at the moment of contact with the impact receiving part is substantially less than dmax, and preferably less than 0.2 dmax. The diameter of the annular active surface da is the diameter of a circle placed so that it lies in the middle of the active surface in the radial direction.
    Figures 3 and 4 show the impact transfer part in a section along the center axis C. The impact surface 6 in this section forms a curve shape with a minimum value Fmi., In the area of the annular active surface. The impact surface can also be described as having a convex surface annular in the direction of impact.
    The diameter of the impact transfer part dnmx in connection with the impact surface is 10-200 mm, preferably 20-60 mm.
    The curve shape formed by the striking surface has a radius of curvature R1 which is in the range 50-5 00 mm.
    This can also be expressed as the curve having a radius of curvature R1, where R1 / dmax is in the range 1 - 50.
    The convex surface can of course have its radii of curvature, for example a first radius of curvature in the area of the active surface and a second radius of curvature in the transition surface between the striking surface and the side surface where the radius of curvature in the transition surface is in the order of 1-3 mm. Preferably, the radius of curvature in the area of the active surface is largest. Even more complicated shapes on the surface are possible, for example the surface can be partially flat, and the transition surface can for example be chamfered.
    The first embodiment relates to a hollow percussion transfer part (percussion piston) (Figures 3 and 5a-5c) and the second embodiment relates to a solid percussion transfer part (percussion piston) (Figures 4 and 6a-6c). According to the first embodiment, shown in Figures 3 and 5, the percussion piston has a longitudinal hole 20 which runs concentrically with the center axis of the percussion piston. The hole has a diameter di, where d; <dmaX / Z.
    The diameter dal defines the position of the active surface of the first embodiment, where da; is in the range 0.25 (dmax + d;) to 0.75 (dn, ax + d,). According to one example, the position of the active surface is located midway between d; and dmax, which may be expressed as da; = Oßdmw, + 0.5di.
    In the second embodiment, shown in Figures 4 and 6, where the striking piston is solid, the central parts of the striking surface have a recess 16 in the direction away from the striking direction, and that the recess has a diameter dc, where dc <dmax / Z. In Figure 2, parts of the depression 16 have been marked with a dash.
    Diameter da; defines the position of the active surface of the second embodiment, where da; is in the range 0.25 (dma fi dc) to 0.75 (dma fi- dc) According to an example, the position of the active surface is located midway between dc and dmax, which can be expressed as day = Oßdmax + 0.5dc.
    According to a variant of the second embodiment, the depression 16 in its center is provided with a convex central pin 18 directed in the direction of impact.
    In Figure 4, the position of the central pin 18 in the longitudinal direction has been marked with Cmm.
    The difference between Cmi., And F min is in the order of 0-1.5 mm, for example 0.1 mm, i.e. the active striking surface 14 is at the level of, or slightly further forward in the striking direction compared to the lower part of the central pin. The central pin may be provided with a recess (not shown) in its center point, which has been added for manufacturing technical reasons. Figures 5a-5c and 6a-6c schematically illustrate what happens to the active surface during a straight shock.
    Figures 5a and 6a show the striking surface with the active surface just at the moment of contact with the striking receiving part. The width of the active surface wa is then the narrowest. Figures 5b and 6b 'show how the width of the active surface increases during the impact, and Figures 5c and 6c show the width of the active surface at the end of the contact period. The figures show how the active surface, the contact surface between the parts, increases with time during the impact to reach a maximum value when the impact force is greatest. Then the contact surface decreases until the parts are no longer in contact with each other. The width, and thus the size, of the active surface is thus load dependent.
    An important aspect of the present invention is thus that the active surface at the moment of the first contact between the parts is small in relation to the size of the striking surface. This applies to a straight shock.
    Figures Sa-Sc and 6a-6c are an illustration of how the stroke transmission member of the present invention effectively absorbs and distributes the forces to which it is subjected during an impact.
    Figures 7a, 7b (with longitudinal holes 20) and 8a, 8b (solid) schematically illustrate the impact surface seen from the direction of impact when the impact transfer part does not hit the impact receiving part straight, ie. the case of oblique abutment which can occur when bearings and bushings are worn.
    Figures 7a and 5a illustrate the appearance of the contact surface 22 at a given time after first contact between the impact transfer member and the impact receiving member, where the impact transfer member is formed according to the prior art, where the radius of curvature at the transition between the side surface and the impact surface is 1-3 mm. As can be seen from Figures 7a and Sa, the contact surface becomes small and is close to the side surface, which means that the stroke transfer part is exposed to high contact voltages, which is not desirable because it can adversely affect the operating time.
    Figures 7b and 8b illustrate the size and position of the contact surface 22 at a given time after first contact between the stroke transfer member and the stroke receiving member, where the stroke transfer member is formed in accordance with the present invention and Figure 7b shows the first embodiment and Figure 8b shows the second embodiment. In these figures, the same reference numerals have been used as in the other figures. As can be seen from these figures, the contact surface 22 is considerably larger than it is in Figures 7a and 8a, and in addition is located much closer to the center of the striking surface, which together gives significantly lower contact stresses than when using the prior art.
    The invention also comprises a drilling machine comprising a stroke transfer part, e.g. a percussion piston, according to any of the embodiments described above. The stroke transfer part is preferably hydraulically driven, but of course the present invention is also applicable in pneumatically driven drilling machines.
    In the drill, the shock waves are transmitted to the impact receiving part, Lex. the neck adapter, preferably at a speed of 12-13 rn / s and with a frequency of 40-100 Hz. Other speeds and frequencies are of course possible within the scope of the present invention.
    The present invention is not limited to the above-described preferred embodiments.
    Various alternatives, modifications and equivalents can be used. The above embodiments are therefore not to be construed as limiting the scope of the invention, as defined by the appended claims.
    权利要求:
    Claims (14)
    [1]
    A circular cylindrical percussion transfer member (2) for a drilling machine adapted to transmit kinetic energy to an impact receiving member (4) by shock waves formed at the contact between the impact transfer member and the impact receiving member, the impact transfer member having a diameter dmax, and comprising a side surface (6) and a side surface (6) ), characterized in that the percussion transmission part is adapted to transmit the kinetic energy to the percussion receiving part with an annular active surface of the percussion surface, the annular active surface being concentric with respect to the cross-sectional area of the percussion transfer part, having a diameter da, where da <dmax, and having a width wa at the moment of contact with the impact receiving part is less than 0.2 dmaa.
    [2]
    The impact transfer member according to claim 1, wherein the annular active surface has a diameter da <0.75dma, a.
    [3]
    The impact transfer member according to claim 1 or 2, wherein the impact surface (6) forms in a section along the center axis C of the impact transfer member a curve with a minimum value Faa., In the region of the annular active surface (14).
    [4]
    The impact transfer part according to any one of claims 1-3, wherein the dmax is 10-200 mm, preferably 25-60 mm.
    [5]
    Impact guide part according to any one of claims 3 or 4, when dependent on claim 3, wherein the curve shape has a radius of curvature R1 which is in the range 10-500 mm.
    [6]
    The stroke transfer part according to any one of claims 3-5, when dependent on claim 3, wherein the curve shape has a radius of curvature R1, where R1 / dmaa is in the range 1-50
    [7]
    The impact transfer member according to any one of claims 1-6, wherein the impact transfer member is solid and the central parts of the impact surface have a depression (16) in the direction away from the impact direction, and that the depression has a diameter da, where da <dmaX / Z. LJ: IG .... “_41 535 393
    [8]
    8. 1.1). S, Slagövcrlöringsdclezi according to claim 7, 'wherein di, has a value: law as ši ggei' in írtervzillet (LZES (_i'l ,, w_ «¿¥ -_dc) to (l, '75 (flmax-lclc)).
    [9]
    The percussion transfer clamp according to claim 7 or 8, in which the jdjugiiiiiigezi (_ l 6) in its ccntruin is provided: down a convcx ccntral pin ('18) directed in Slaigriktizliigcxx. lO. The percussion axis according to: one of claims 1 to 6, wherein the percussion axis: shows a longitudinal hole (20) running through the center of the cam, nia-d
    [10]
    10. Slagkolvwzns itcntnnnaxcl, where iläiiiiida liâl has a Lliainetez 'dg, where il; <í d, - ,,,, - / 2.
    [11]
    11. l l. The percussion transfer part according to claim ll), ifarvicl you have a value dal which lies in
    [12]
    12. The stroke performance clause according to any one of the preceding claims, wherein the stroke member is part one. slaøkols' för110111111askinen: yclx att iiäliizidai slamnfnïtagiflinQsdc-l är k sa n.) n .. . x. a ziackadaiatci 'for horrmaskineii.
    [13]
    13. l3. A boiiiiniaskiii comprising a slagíxfcrfiiringsdel under any aiv crane / six 1- ll.
    [14]
    Borrinzisliincn: according to claim 13, wherein the shock wave (Sxierfâârs: iv slagößverlfiifsfírigsdaleiilill slaggnottagsii: xgsclelen nied en liasïlghet på lZ-lš iii / s och: mL-di en tfrekixens på 40--1.
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    同族专利:
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    CN103501964A|2014-01-08|
    US9937613B2|2018-04-10|
    CA2834226A1|2012-11-08|
    CA2834226C|2019-02-05|
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    CN103501964B|2016-03-23|
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    ZA201309023B|2015-03-25|
    JP2014516809A|2014-07-17|
    NO2704880T3|2018-05-05|
    WO2012150895A1|2012-11-08|
    AU2012251138B2|2016-11-03|
    ES2658895T3|2018-03-12|
    US20140041888A1|2014-02-13|
    SE1150383A1|2012-07-24|
    引用文献:
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    SE1150383A|SE1150383A1|2011-05-03|2011-05-03|A stroke transfer part, and a drill comprising such a stroke transfer part|SE1150383A| SE1150383A1|2011-05-03|2011-05-03|A stroke transfer part, and a drill comprising such a stroke transfer part|
    CA2834226A| CA2834226C|2011-05-03|2012-04-12|A striker member, and a drilling machine comprising a striker member|
    NO12779866A| NO2704880T3|2011-05-03|2012-04-12|
    PCT/SE2012/050391| WO2012150895A1|2011-05-03|2012-04-12|A striker member, and a drilling machine comprising a striker member|
    AU2012251138A| AU2012251138B2|2011-05-03|2012-04-12|A striker member, and a drilling machine comprising a striker member|
    JP2014509263A| JP5967842B2|2011-05-03|2012-04-12|Excavator with striking member and striking member|
    EP12779866.8A| EP2704880B1|2011-05-03|2012-04-12|A striker member, and a drilling machine comprising a striker member|
    CN201280020455.9A| CN103501964B|2011-05-03|2012-04-12|Impact structure and comprise the rig of impact structure|
    ES12779866.8T| ES2658895T3|2011-05-03|2012-04-12|A hammer member and a drilling machine comprising a hammer member|
    US13/261,746| US9937613B2|2011-05-03|2012-04-12|Striker member, and a drilling machine comprising a striker member|
    ZA2013/09023A| ZA201309023B|2011-05-03|2013-12-02|A striker member, and a drilling machine comprising a striker member|
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