• 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:
    1507605 Recoil damped percussion tool ATLAS COPCO AB 12 March 1976 [18 March 1975] 09962/76 Heading B4C [Also in Division B3] A recoil damped percussion tool comprises a work tool 22, a machine housing coupled to the work tool and adapted to apply a feeding force to the work tool in a working direction, a hammer piston 17 which reciprocates in the machine housing to deliver impact energy to work tool 22, the work tool recoiling after an impact, and a recoil damping device comprising a retard chamber 70 in the machine housing containing pressurized hydraulic fluid, and a retard piston 68 which recoils with the work tool 22 and is acted upon by the hydraulic fluid in the retard chamber. Preferably, the retard piston has a piston surface 69 which forms the forward end of retard chamber 70 and the increase in pressure in chamber 70 when tool 22 recoils is damped by hydraulic fluid pressure reservoir 48 which is connected to retard chamber 70 by conduits 47 and 71. Driving means.-Hammer piston 17 is reciprocated to strike work tool 22 by hydraulic fluid supplied by inlet conduit 47 and controlled by distributing valve slide 46. In the position shown in Fig. 3 slide 46 allows fluid to enter conduit 55 and rear pressure chamber 39 to drive piston 17, whilst fluid driven from forward pressure chamber 43 flows through conduits 56 and 52 to a sump (not shown). Fluid from conduit 55 blows through passage 64 in slide 46 to act on annular piston surface 63 and maintains slide 46 in its left hand position. When the piston 17 has moved far enough to the left to allow high pressure fluid in conduit 55 to reach control line 62 via expanded rear chamber 39 and for control line 61 to be drained via middle chamber 15, valve slide 46 is pushed to the right. Chamber 43 is supplied with high pressure fluid and chamber 39 is drained to produce a return stroke of piston 17 until control line 61 is pressurized, control line 62 is drained and slide 46 shifted to the left to repeat the driving stroke. The length of the driving stroke is adjusted by blocking some of the branches of control line 61 by pin 67. Pressure reservoirs 48, 54 minimize pressure variations. Drill rotation. As shown work tool 22 is an adaptor intended to be connected to a drill string. A rotation chuck 23 is rotatably journalled in a gear housing 13 by roller bearings 24, 25. Chuck 23 is provided with a gear ring 26 which co-operates with a gear wheel 27 splined to a shaft 35 journalled in bushings 36, 37 and rotated by a hydraulic motor 38. A driver 28 transmits the rotation of chuck 23 to adaptor 22 which is axially movable relative to the driver. A rotational chuck bushing 33 has a collar 34 resting against a rear end of chuck 23 and retard piston 68. When the tool is pushed against, e.g. a rock, the fluid pressure on the retard piston exceeds the feeding force. Drill clearing.-Flushing fluid is applied to the axial hole of adaptor 22 and the drill string through flushing head 31. A stop ring 32 is mounted between the flushing head and driver 28.
    公开号:SU738501A3
    申请号:SU762337512
    申请日:1976-03-18
    公开日:1980-05-30
    发明作者:Торстен Эклеф Оке；Таге Аллан Фенгсборн Пер；Вигг Рисс Ромелл Гуннар
    申请人:Атлас Конко Актиеболаг (Фирма)；
    IPC主号:
    专利说明:

    (54) IMPACT HYDRAULIC MACHINE
    one
    The invention relates to percussion instruments, such as percussion drilling heads for rock drilling, slotting machines, and relates to a kickback device for impacting a percussion working tool in mechanisms of this type.
    A percussion mechanism is known, which contains a cylindrical barrel in which a percussion piston is placed, which acts on a working tool under the action of hydraulic rigidity, pneumoaccumulator 1 is included in the pressure line.
    A disadvantage of the known device is its low vibration protection.
    The closest to the invention in its technical essence is a hydraulic shock machine, comprising a cylindrical body with annular grooves in the front and rear parts, a drummer placed therein with annular grooves, forming the front and rear compression chambers with the annular grooves of the body with compression chambers 2.
    The disadvantage of the known machine is its lack of vibration protection.
    The aim of the invention is to increase the efficiency of vibration isolation.
    This goal is achieved by the fact that the known machine is equipped with a shock-absorbing piston, and the housing and the piston are made with additional annular grooves placed on the side of the working tool and forming a damping chamber, which acts as a hydraulic bearing and communicates with the battery.
    10 FIG. 1 shows the front part of a percussion machine, a longitudinal section; in fig. 2 - rear part of the machine, longitudinal section; in fig. 3 - schematic diagram of the hydraulic shock maschiny.
    The impact hydraulic machine consists of a front head 1 with a cover 2, leather 3, an intermediate part 4 of the casing, a cylindrical body 5 and a rear head 6.
    Inside the housing 5 there is a drummer 7 with the possibility of reciprocating 20 movement along the longitudinal axis of the housing b.
    The drummer 7 consists of a cylindrical rod with two pistons 8 and 9 having end surfaces 10 and 1. In addition, the drummer 7 has annular grooves 12 and 13 located on both sides of the pistons 8 and 9, and between pistons 8 and 9 An annular groove 14 is located. The piston piston 8 creates 15 shock loads on the working tool. In leather Xe 3 in roller bearings 16, 17, a rotating chuck 18 is fixed. Vrashak, the chuck 18 is provided with a gear crown 19, which interacts with the gear wheel 20. Rotation from the chuck 18 is transmitted to the working tool 15 through the driving element 21, the working tool 15 is displaced axially relative to the carrier element 21. The front end of the working tool is mounted in the front head 1 in the guide 22 and the ball bearing 23. The washing liquid enters the axial opening of the working tool 15 through the The internal head 24. Between the head 24 and the driver element 21 is mounted a stop ring 25. There is a sleeve 26 in the rear part of the rotating chuck 18. The sleeve 26 is provided with a projection against the rear end of the cartridge 18. The gear wheel 20 sits on slots on the shaft 27 which is mounted in sleeves 28 to 29, which are located in casing 3. Shaft 27 is driven by a hydraulic motor 30 mounted on housing 5. Housing 5, annular groove 13 of drummer 7, front surface 11 and annular groove 31 of housing 5 form the rear annular compressor Sion chamber 32. Similarly, the annular groove 12 of the striker, 7, the end surface 10 and the annular groove 33 of the housing 5, forms the front annular compression chamber 34. The flow rate of the hydraulic medium coming from the supply line 35 is regulated by the distribution spool 36. With supply line 35 a permanently connected accumulator 37. A supply line 3 communicates with an annular inlet chamber 38 located in the cylinder of the distribution valve. The pilot of this valve has, in addition, two annular outlet chambers 39, 40 with which the exhaust channels 41, 42 are connected. These outlet channels go to the sump (not shown in the drawing :), from where the hydraulic fluid is pumped out by a piston pump (not shown ) so that the constant pressure of hydraulic fluid, which is set by the control valve (not shown), is maintained in the supply line 35. The accumulator 43 is permanently connected to the exhaust manifolds 41, 42 and warns of the appearance of shock waves in the hydraulic system. The accumulators 37, 43 smooth the peak pressures in the system and on the firing pin. The compression chambers 32, 34 communicate with the battery 43 via the corresponding channels 44 and 45. The spool 36 has end projections 46, 47, the end surfaces 48, 49 of which are under pressure m created in the control channels 50, 51, extending from L: impactor 7. The end protrusion 46 has an annular cy. tine-shaped surface 32, which is affected by pressure in channel 45, which communicates through channel 53 in the spool 36. The end protrusion 47 has a similar cylindrical surface 54 on reported pressure in channel 44 Available with a .55 channel located in spool 36. The cylindrical surfaces 52, 54 form an auxiliary stop, therefore they have a smaller area than the end surfaces 48, 49, which are the main biased surfaces that perceive hydraulic pressure . Channel 56 is connected to the reservoir and provides for the necessary time drainage of hydraulic fluid from the volume between the cylindrical parts 8, 9. As a result, one of the control channels 50, 5 will always be drained through the specified channel 56, when differently from these the channels are injected into the floor; pressure hydraulic fluid. A control channel 51 and more. Four branches or sleeves 57 that terminate on the wall of the hammer 7. One or more of these branches can be blocked by a displaceable adjustment cap 58. This design decision allows the maximum stroke of the hammer 7 to be adjusted, which means that a different number can be obtained passes and impact energy for each hit. In the intermediate part 4 there is a brake or a shock-absorbing piston 59, which can be moved in the axial direction and rotated around an axis. The rear surface 60 of this front forms a movable end face with a shock-absorbing ion gauge 61, which is bounded by an annular groove 62 of the housing 5 and communicates with the supply line 35 and the battery 37 through the channel 63. In addition. Shock absorbing pad 61 performs the role of hydraulics. Shock machine works as follows. The spool 36 is in the position shown in FIG. 3, when a hydraulic fluid is supplied to the back compression chamber 32 of the increased pressure and a hydraulic fluid from the front pressure chamber 34; -: the fluid is discharged. Drummer 7 moves forward. The adjusting plug 5th overlaps the two right coen. 3, control channel
    50 is drained through the drainage channel. The spool 36 is in the same position, since the pressure in the supply line 35 is transmitted to the thrust surface 52 of the spool. When the hammer 7 is displaced forward (in Fig. 3 to the left), the control channel 51 reopens. In this case, the hydraulic fluid is drained into the drainage channel 56. Then, as the impactor 9 of the striker 7 passes through the opening of the control channel 50, it opens this hole into the rear compression chamber 32, from which pressure is transmitted through the control channel 50 to the end face. surface 48 spool. As a result, the spool moves to the second (not shown) working position (to the right in FIG. 3), while the pressure of the hydraulic fluid in the front compression chamber 34 increases and the pressure in the rear compression chamber 32 drops. This takes place immediately before the impact of the hammer 7 with the working tool 15. The spool is held in the right position, as the pressure of hydraulic fluid from the supply line is transmitted to the thrust surface 54 of the spool 36. The control channel 50 is connected to the drainage channel 56 when the surface 10 The port 8 passes through the control channel sleeve 57. As a result, the pressure of the hydraulic fluid from the front compression chamber 34 is transmitted through the control channel 51 to the end surface 49 of the spool. For this reason, the spool moves to the left position shown in FIG. 3, in which it remains, since the corresponding pressure acts on the surface 52
    hydraulic fluid. The hydraulic fluid under pressure now enters the rear chamber 32 of the increased pressure, while the hammer 7 slows down due to the influence of the hydraulic pressure on its surface 11. At the same time, the hydraulic fluid is displaced by the hammer 7 from the rear chamber 32, which decreases the volume in the process of moving. specified camera. Displaced in this way from the chamber 32, the liquid enters the accumulator 43 during the first part of the stroke of the striker 7. However, as soon as the striker 7 reaches a speed corresponding to the flow rate of the supplied fluid, the accumulator 43 begins to supply hydraulic fluid to the chamber 32, thus drummer moving speed 7.
    When the working tool 15 is displaced to the sleeve 26 of the rotating chuck, which is held in the position shown in FIG. 1, since the force directed in the positive direction to the surface 54 is greater than the displacement force of the striker.
    When the working tool 15 bounces off the rock during shock drilling, it hits the sleeve 26. Recoil impulse loads are transmitted to the shock absorbing piston 59 and then absorbed by the hydraulic fluid in the shock absorber chamber 61. Thus, the hydraulic fluid in the shock absorber acts as a link recoil pulses. With hydraulic shock absorber constantly
    The battery 37 is connected. This connection is carried out through a column of hydraulic fluid in the channel 63. If the recoil force of the tool exceeds a certain value, the sleeve 26 and, therefore, the damping shaft 59 are displaced relative to the rotating chuck 18. Such a constructive decision allows to damp the recoil shock maschiny. When the drill is lifted, the accumulator 37 equalizes the pressure peaks of the hydraulic fluid that are created in the shock absorber. Then, the working tool 15 is returned under the action of pressure in the damping chamber 61 to its original position.
    The rotation of the chuck 18 is transmitted to the damping carrier 59 through the sleeve 26.
    Thus, the hydraulic fluid located in the damping chamber 61 serves as a kind of hydraulic support for the working tool 15.
    The pressure drops that occur in the damping chamber 61 when lifting the damping shell 59 relative to the rotating chuck 18 are compensated by the battery 37.
    权利要求:
    Claims (2)
    [1]
    1. USSR author's certificate
    No. 340775, cl. E 21 C 3/20, 1965.
    [2]
    2. USSR author's certificate No. 365435, cl. E 21 C 3/22, 1970 (prototype). / 313ii 17 2S IS .Ai / 23 / f „// - / L / 7 /////// and. ss f
    2.
    类似技术:
    公开号 | 公开日 | 专利标题
    SU738501A3|1980-05-30|Shock hydraulic machine
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    GB1588525A|1981-04-23|Hydraulic drive
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    同族专利:
    公开号 | 公开日
    SE457936B|1989-02-13|
    BR7601574A|1976-09-14|
    AT344644B|1978-08-10|
    FR2304449A1|1976-10-15|
    GB1507605A|1978-04-19|
    ATA186676A|1977-12-15|
    JPS51116101A|1976-10-13|
    AU1208376A|1977-09-22|
    CA1048372A|1979-02-13|
    IT1057986B|1982-03-30|
    US4073350A|1978-02-14|
    DE2610619A1|1976-09-23|
    ZA761349B|1977-02-23|
    FI760664A|1976-09-19|
    SE7605327L|1976-09-19|
    PL112912B1|1980-11-29|
    FR2304449B1|1982-12-10|
    SE7503097L|1976-09-19|
    JPS613633B2|1986-02-03|
    SE392830B|1977-04-25|
    DE2610619B2|1979-11-29|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    FR884602A|1941-08-02|1943-08-23|Demag Drucklufttech|Device for damping recoil of compressed air tools|
    US2558165A|1947-10-17|1951-06-26|Ingersoll Rand Co|Cushioning device for rock drills|
    US3168324A|1963-02-15|1965-02-02|Ingersoll Rand Co|Chuck|
    US3266581A|1963-11-01|1966-08-16|Mechanical Res Corp|Vibrationless power tool|
    GB1152119A|1966-11-29|1969-05-14|Atlas Copco Ab|Improvements in Recoil Vibration Damped Percussive Machine|
    US3741072A|1971-02-17|1973-06-26|G Romell|Hydraulic fluid actuated percussion tool|
    JPS5414276B2|1971-10-13|1979-06-06|
    US3866690A|1972-09-25|1975-02-18|Technology Inc Const|Hydraulically powered impact device|
    SE391666B|1973-05-23|1977-02-28|Atlas Copco Ab|RECOMMENDATION DEVICES FOR STRIKING MACHINES|DE2738956B2|1977-08-30|1979-11-29|Frank 3380 Goslar Habsick|Drill rod pretensioning device for rotary percussion drills|
    GB2027483B|1978-07-29|1982-09-02|Kawasaki Heavy Ind Ltd|Hydraulic reciprocating motor|
    SU947419A2|1978-09-26|1982-07-30|Ордена Трудового Красного Знамени институт гидродинамики СО АН СССР|Entry-driving machine|
    SE429111B|1978-10-19|1983-08-15|Atlas Copco Ab|HYDRAULIC DRIVES|
    SE440873B|1981-02-11|1985-08-26|Atlas Copco Ab|HYDRAULIC SUSPENSION WITH REFLEX DUMPERS INCLUDING LOCK SPLACES IN SERIES WITH CUTTING NOZZLE|
    FR2504606B1|1981-04-27|1985-06-21|Mo Aviat I|PNEUMOHYDRAULIC PUMPING SYSTEM|
    FR2509652B1|1981-07-17|1984-04-20|Montabert Ets|
    SE8106907L|1981-11-20|1983-05-21|Atlas Copco Ab|WAY TO CONTROL A PERFORMANCE AND PERFORMANCE|
    FR2531138B1|1982-07-29|1985-03-01|Inst Avtomatiki Akademii|
    CH664730A5|1983-07-21|1988-03-31|Sig Schweiz Industrieges|METHOD AND DEVICE FOR DAMPING THE BALL Bounce IN DRUMMING TOOLS.|
    WO1986002694A1|1984-10-22|1986-05-09|Atlas Copco Aktiebolag|A rock drill|
    US4648468A|1985-06-26|1987-03-10|Honsa Technologies|Portable powered tool with vibration damping|
    FI861851A|1986-05-02|1987-11-03|Tampella Oy Ab|ANORDNING FOER ETT AXIALLAGER I EN BORRMASKIN.|
    FI78158C|1986-05-09|1989-06-12|Tampella Oy Ab|ANORDING VID EN BORRMASKIN FOER LAGRING AV ETT ROTATIONSSTYCKE.|
    FI84701C|1990-02-23|1992-01-10|Tampella Oy Ab|ANORDNING FOER AXIALLAGRET I EN BORRMASKIN.|
    SE508064C2|1993-10-15|1998-08-17|Atlas Copco Rock Drills Ab|Rock drilling device with reflex damper|
    AU5981294A|1993-11-12|1995-05-29|Individualnoe Chastnoe Predriyatie 'krot'|Pneumatic percussion device|
    US5893419A|1997-01-08|1999-04-13|Fm Industries, Inc.|Hydraulic impact tool|
    US5944120A|1997-11-10|1999-08-31|Caterpillar Inc.|Hydraulic hammer assembly having low vibration characteristics|
    DK1162037T3|2000-06-06|2005-12-12|Andrea Linard Mathis|Rotary impact device for a drill string|
    FI110804B|2000-06-27|2003-03-31|Sandvik Tamrock Oy|Method for opening joints of drilling components and rock drill|
    SE529416C2|2005-12-22|2007-08-07|Atlas Copco Rock Drills Ab|Damping device and drilling machine including such damping device|
    SE537838C2|2014-02-14|2015-11-03|Atlas Copco Rock Drills Ab|Damping device for percussion, percussion and rock drill|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    SE7503097A|SE392830B|1975-03-18|1975-03-18|MOUNTAIN DRILLING DEVICE FOR DAMPING THE RECYCLE FROM A WORK CONNECTED TO THE MACHINE|
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