• 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:
    An impact force producing apparatus that is described in connection with one particularly suitable use on a backhoe vehicle although it is usable on other vehicles and apparatus. A frame is provided which can be attached directly to the backhoe. A heavy ram is flexibly mounted to the frame in such a manner that it may freely oscillate relative to the frame. Attached to the ram is a hydraulic motor coupled with an eccentric weight to provoke vibrational movement in the ram. The relative inertias and locations of the components, the resilient mountings and the driving force of the eccentric weight are interrelated to create a vibratory motion in the ram which provides a unidirectional impact on a tool positioned on the frame and drives the ram near a resonance of the system. Guides may be provided to eliminate secondary harmonics and extraneous vibrations and movements.
    公开号:SU1194288A3
    申请号:SU742037100
    申请日:1974-06-10
    公开日:1985-11-23
    发明作者:Амос Сенчери Бернард
    申请人:Эллайд Стил Энд Трактор Продактс Инк (Фирма)；
    IPC主号:
    专利说明:

    The invention relates to the field of mechanical engineering and can be used as an attachment to construction and road machines for vibratory destruction of the soil.
    Known vibrohammers containing vibration exciter, fixed by means of two groups of elastic elements WITH
    The disadvantages of the known vibromogue include the low efficiency of soil development, which is due to the location of elastic elements perpendicular to the axis of rotation of the vibration exciter, as well as the absence of a guide J to protect the device from random vibrations caused by the heterogeneity of the material being processed and loads not aligned with the tool.
    The aim of the invention is to increase the efficiency of excavation. . .
    This goal is achieved by the fact that a vibrohammer containing a vibro-exciter, fixed by means of two groups of other elements, one of which is located above, and the other below the center of mass of the vibrator, is equipped with two sliders located in guides and connected to the fingers mounted in the lower part of the body the vibration exciter, the groups of elastic elements are parallel to the axis of rotation of the vibration exciter, the rigidity of the upper group of elastic elements is less than the rigidity of the lower group, and the elastic elements are made of elastic material.
    FIG. 1 shows the device, a general view; in fig. 2 shows section A-A in FIG. one; in fig. 3 shows a section B-B in FIG. 2; in fig. 4 - section C-C in Fig. 2; Fig. 5 is a diagram illustrating the movement paths of the housing of Fig. 5; 6 is an approximate curve of the dependence of the stroke on the frequency DT1Y of a linear spring-mass system with damping; in fig. 7 is an exemplary stroke versus frequency curve for a non-linear spring-mass system with damping; in fig. 8 is an approximate curve of the time path with non-linear preparative loading.
    Frame 1 consists of two side plates 1 SHIT 2 and 3. Side plates 2 and 3 may be the same to facilitate
    from cooking and are located in parallel planes. Support elements 4 and 5 are placed between plates 2 and 3 to increase: rigidity of frame 1. Transverse axes 6 and 7 run perpendicularly through parallel plates 2 and 3 near the upper edge of frame 1 and serve to mount the vibro-hammer on the backhoe shovel or on another hinged arm.
    Between the side plates 2 and 3 there is a shock part, consisting of a body 8, elastically mounted on the frame 1, and a driving eccentric 9. In the body 8 there is a window 10, in which an eccentric 9 is placed on axes x11 and 12. in bearings 13 and 14, with axis 12 having internal splines for coupling to motor shaft 15.
    Hydraulic valve 15 is fixed on housing 8. The hydraulic motor shaft has spitz pins extending into the slots of the holes in the axle 12. To balance the hydraulic motor 15 on the housing 8 on the side opposite to the hydraulic motor, a counterweight 16 is fixed. To accommodate the hydraulic motor 15 and the counterweight 16 in the side plates 2 and 3 there are openings .17,
    The housing 8 is provided with brackets 18 and 19. The bracket 18 ends with a lower bracket 20.
    The position of the eccentric 9 axis in the housing 8 is such that the horizontal oscillation assembly of the housing is formed in the location area of the lower bracket 20 .. The striker 21 is fixed to the lower bracket 20 by bolts 22. As the striker 21 is located in the horizontal beam assembly, only vertical movement. Due to the absence of any horizontal movement in the center of the surface of the striker, the wear of the striker 21 is prevented and the transverse shock loads of the shock part of the body 8 are eliminated, the total impact energy increases, and is directed longitudinally.
    The housing 8 is mounted on frame 1 by means of elastic elements 23 and 24 associated with Kronggein 18, and elastic elements 25 and 26 connected with lower bracket 20. Elements 23 and 24 are cylindrical rubber blocks, one side glued to the plate. 27 and 28. These plates are placed on the flat mounting surfaces 29 and 30 of the bracket 18 and bolted 31. On the other hand, the elements 23 and 2 are glued to the plates 32 and 33, which in turn are bolted to side plates 2 and 3 through spacer sleeves 34 and 35, Elastic elements 25 and 26 identical and. analogously connected to the housing 8 and the plates 2 and 3.. All elastic elements are oriented in such a way that they bend under lateral vibrations caused by the vibration created by the rotation of the eccentric 9. Static rigidity top-h. the elastic elements 23 and 24 in the transverse direction is 40.5 kgf / cm, and the static rigidity of the lower elastic elements 25 and 26 in the same direction is 125 kgf / s. The total stiffness of the elastic elements measured by pressing the case 8 downward in the direction to the striker 21 relative to the frame 1, it is 333 kgf / cm. The rubber used in this construction has an effective stiffness in the dynamic state, which differs from the actual static stiffness. The total dynamic stiffness for the case in question at the frequencies at which the proposed system works is 500 kgf / s. The result is that the motion is purely longitudinal, as shown by the linear trajectory L (Fig. 5), which. is the locus of a point in the center of the striker when vibrating. The diameter of the circular trajectory M in the center of gravity is equal to the length of the rectilinear trajectory L at the lower elastic elements 25 and 26, body B describes the elliptical trajectory N, the larger axis of which is directed along the axial line. This major axis of the elliptical trajectory N is equal to the diameter of the circular trajectory M and the length of the linear trajectory L. At the upper elastic elements 23 and 24, body 8 describes the elliptical trajectory P, the major axis of which is perpendicular to the axial line. The small axis of this elliptical path is equal to the length of the straight linear path L. The flow divider 36 is introduced to control the frequency of free oscillations. Flow divider 36 may direct flow to hydraulic motor 15. regardless of the pressure in the system. In addition to the flow separator 36., a pressure reducing valve 37 is inserted to adjust the pressure in the porous line. The holder 38 of the tool 39 is fixed in the lower part of the frame 1. The cylindrical tool 39 is fixed in the holder 38 by means of a locking pin 40, which enters the groove 41 in the body of the tool 39. The locking pin 40 of the tool passes through the tool holder 38 in the transverse direction so that it partially enters the hole 42 in the tool holder 38. The groove 41 has such a length that the tool 39 can be positioned outside the path of movement of the body 8. The length of the groove 41 ensures the contact of the body 8 with the tool 39 in its upper position. In order to limit the movement of the tool 39 within the limits of the path of movement of the body 8, the tool is made according to c. 43. C c is so positioned that it contacts the locking plate 44 of the tool in the set preloading position. The preloading position of the tool 39 is determined. limiting its movement within the path of movement of the housing 8. For example, setting tool 39 to a position in which elastic elements are not loaded during impact, at the moment of impact, the entire moment of inertia is realized into impact forces. When the tool position 43 is set at the unloaded position of the elastic elements 23-26, the frequency stroke characteristic is obtained to be substantially linear. This characteristic is shown in FIG. 6. When substantial preloading of the elastic elements in the shock position is maintained, the frequency-stroke characteristic is Nonlinear. Such a non-linear characteristic curve is shown in FIG. The most desirable characteristic curve should be determined by practical considerations. When the tool 39 installed on the object being processed creates significant resistance to motion, the curve of the path in time
    $.
    (For vertical oscillations, it varies from sinusoidal to cut wave-shaped, shown in Fig. 8. The frequency range of the device. Under the load directly depends on the pressure at the inlet to the hydraulic motor 15, the hardness and elasticity of the object being processed. To control the operating frequency of the system, there is a reduction valve 37 located downstream of the flow divider 36. By varying the response pressure of the pressure reducing valve 37, the operation of the system can be brought closer to the mode of the system's own oscillation frequencies or removed. Variations in the resistance exerted by the tool 39 can cause instantaneous load changes and unwanted random vibrations. To view these unwanted random vibrations, limiting means are placed on frame 1. The limiting means is executed in the form of two guides 45 and 46 fixed to frame 1 and located from both
    942886
    the sides of the vibrating housing 8 in the node horizontal oscillations.
    Both guides 45 and 46 are identical. The guide -45 has a main i, plate 47, which is fixed to the side plate 2. A resilient damper 48 is installed at the top of the plate 47. To firmly hold the damper 48, it is equipped with a corner 49: to the bottom bracket 20 has two pins 50 and 51. The cylindrical fingers 50 and 51 protrude outward from the bottom bracket 20 and center on each side of the impact surface of the striker 21. The fingers 50 and 51 are located in the horizontal oscillation unit of the housing 8. The finger 50 enters the slider 52 and the finger 51 goes into the slider 53. Sliders 52 and 53 are also identical. 20 Slider 52 is rectangular, movably seated in guide 45 and prevents lateral movement of the finger. 50. Using the invention will improve the efficiency of vibratory impact excavation: when carried out, the research institute for construction and road works.
    ff ii & m
    g X -A
    Fiel
    FIG. 6
    权利要求:
    Claims (1)
    [1]
    VIBROMOTER containing a vibration exciter fixed by means of two groups of elastic elements, one of which is located above, and the other below the center of mass of vib. pathogen distinguishing with the fact that, in order to increase the efficiency of soil development, it is equipped with two sliders located in the guides and connected to the fingers installed in the lower part of the vibration exciter case, the groups of elastic elements are parallel to the axis of rotation of the vibration exciter, the rigidity of the upper group of elastic elements is less than the rigidity of the lower groups, and elasticfrom Elements are made of elastic! S material.
    类似技术:
    公开号 | 公开日 | 专利标题
    SU1194288A3|1985-11-23|Vibrating hammer
    US4694650A|1987-09-22|Externally tuned vibration absorber
    US2958228A|1960-11-01|Resonant vibration exciter
    EP0178652B1|1990-05-09|Liquid-filled type vibration damping structure
    US4365771A|1982-12-28|Inplane nodalization system
    US3317041A|1967-05-02|Resonant screen
    US5051170A|1991-09-24|Two frame elastic screening appartaus having substantially linear relative movement
    EP0089140B1|1987-08-12|Synchronous vibratory impact hammer
    US3417630A|1968-12-24|Vibratory apparatus
    US5301814A|1994-04-12|Increasing the relative motion of a screen deck
    JPH1194691A|1999-04-09|Exciter
    RU95771U1|2010-07-10|Vibration damping device
    US2974798A|1961-03-14|Vibrating system
    US3834827A|1974-09-10|Vehicle mounted vibratory compactor
    KR102313320B1|2021-10-18|Moved back prevention device of vibration spring unit for aggregate sorter
    CA1142155A|1983-03-01|Inplane nodalization system
    US2741926A|1956-04-17|Oscillating device with two oscillating masses adapted periodically to approach each other and to recede from each other
    SU1184989A1|1985-10-15|Counter-vibration device
    SU780904A1|1980-11-23|Sieve
    RU45412U1|2005-05-10|DIGGER OF THE EARTH MACHINE EQUIPPED WITH A DYNAMIC OSCILLATOR OF OSCILLATIONS
    KR100895705B1|2009-04-30|Dynamic vibration asorber to lessen the vibration of the oil pressure cylinder of excavator
    SU437673A1|1974-07-30|Loader bucket
    JPH06117485A|1994-04-26|Frequency coping type vibration damper
    SU685581A1|1979-09-15|Vibrated feeder
    SU1680370A1|1991-09-30|Vibrating screen
    同族专利:
    公开号 | 公开日
    CH583341A5|1976-12-31|
    US3866693A|1975-02-18|
    ZA743256B|1975-05-28|
    JPS5053961A|1975-05-13|
    AR209071A1|1977-03-31|
    BR7404802D0|1975-01-07|
    FR2232410A1|1975-01-03|
    NL7407420A|1974-12-13|
    GB1464618A|1977-02-16|
    SE7407605L|1974-12-12|
    DE2428128A1|1975-01-02|
    ES427181A1|1976-08-01|
    IT1014888B|1977-04-30|
    AU6941074A|1975-11-27|
    JPS5815269B2|1983-03-24|
    CA1007143A|1977-03-22|
    FR2232410B1|1980-06-20|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US1556889A|1923-03-29|1925-10-13|Wright William Bruce|Means for cleaning, scaling, or chipping surfaces|
    US1657387A|1925-06-17|1928-01-24|Goldschmidt Rudolf|Mechanical hammer|
    US1672885A|1925-06-17|1928-06-12|Goldschmidt Rudolf|Mechanical hammer|
    GB565783A|1943-02-22|1944-11-28|Rubber Bonders Ltd|Improvements in and relating to fluid pressure operated tools|
    GB1060652A|1963-05-10|1967-03-08|Max Arnold Stutz|Improvements in or relating to percussive apparatus|
    US3467207A|1966-10-10|1969-09-16|Harley G Pyles|Universal drilling machine|
    US3682254A|1970-07-06|1972-08-08|Regus Ag|Spring-loaded hammer|US4265129A|1979-04-06|1981-05-05|Bodine Albert G|Orbiting mass oscillator with oil film cushioned bearings|
    US4257648A|1979-04-09|1981-03-24|Bodine Albert G|Non-resonant cyclic drive system employing rectification of the cyclic output|
    US4616716A|1982-03-01|1986-10-14|Allied Steel & Tractor Products, Inc.|Synchronous vibratory impact hammer|
    AU550165B2|1982-03-01|1986-03-06|Allied Steel and Tractor Products Inc.|Synchronous vibratory impact hammer|
    DE58903355D1|1989-01-11|1993-03-04|Sulzer Ag|HYDRAULIC DRILLING HAMMER.|
    US5409070A|1993-10-18|1995-04-25|Roussy; Raymond J.|Coupling for rotary-vibratory drills|
    US5787786A|1996-05-09|1998-08-04|Sauer-Sundstrand - Control Concepts|Dual hydraulic oscillator for the reciprocating cutter of an agricultural machine|
    US5988297A|1998-03-24|1999-11-23|Hydraulic Power Systems, Inc.|Variable eccentric vibratory hammer|
    US20060000124A1|2004-03-25|2006-01-05|Mark Nye|Resonant demolition tool|
    US8210281B2|2005-02-28|2012-07-03|Roussy Raymond|Method and system for installing geothermal transfer apparatuses with a sonic drill|
    US20060191719A1|2005-02-28|2006-08-31|Roussy Raymond J|Method of geothermal loop installation|
    US7647988B2|2005-02-28|2010-01-19|Raymond J. Roussy|Method and system for installing geothermal transfer apparatuses with a sonic drill|
    US8136611B2|2005-02-28|2012-03-20|Roussy Raymond|Method and system for installing micropiles with a sonic drill|
    SE528649C8|2005-05-23|2007-02-27|Atlas Copco Rock Drills Ab|Pulse generator, hydraulic pulse tool and pulse generating method|
    US7740085B2|2005-12-13|2010-06-22|Roussy Raymond J|Vibratory apparatus for a rotary-vibratory drill|
    US8118115B2|2008-02-22|2012-02-21|Roussy Raymond J|Method and system for installing geothermal heat exchangers, micropiles, and anchors using a sonic drill and a removable or retrievable drill bit|
    US7891440B2|2008-02-22|2011-02-22|Roussy Raymond J|Method and system for installing geothermal transfer apparatuses with a sonic drill and a removable or retrievable drill bit|
    WO2011120210A1|2010-03-30|2011-10-06|Tang Zhongsheng|Hydraulic and resonant breaking hammer|
    US8336643B2|2010-08-13|2012-12-25|Ronald Harleman|Vibratory drilling apparatus|
    CA2853643A1|2011-10-27|2013-05-02|QinetiQ North America, Inc.|Ground pressure detonation device|
    DE102013103722B4|2013-04-12|2016-10-13|Thyssenkrupp Tiefbautechnik Gmbh|Vibration ramming arrangement and method for operating the vibration ram assembly|
    CN105443592A|2015-12-16|2016-03-30|山东天瑞重工有限公司|High-frequency device driving shaft with embedded sleeve|
    GB201806098D0|2018-04-13|2018-05-30|Bemrose Darren|Vibrator Loader|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    US368463A|US3866693A|1973-06-11|1973-06-11|Vibratory impact hammer|
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