US3903972A - Impact tools - Google Patents

Impact tools Download PDF

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Publication number
US3903972A
US3903972A US463625A US46362574A US3903972A US 3903972 A US3903972 A US 3903972A US 463625 A US463625 A US 463625A US 46362574 A US46362574 A US 46362574A US 3903972 A US3903972 A US 3903972A
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United States
Prior art keywords
cavity
piston
bore
return
supply
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Expired - Lifetime
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US463625A
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English (en)
Inventor
John V Bouyoucos
Roger L Selsam
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Hydroacoustics Inc
Cooper Industries LLC
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Hydroacoustics Inc
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Application filed by Hydroacoustics Inc filed Critical Hydroacoustics Inc
Priority to US463625A priority Critical patent/US3903972A/en
Priority to ZA00752428A priority patent/ZA752428B/xx
Priority to AU80245/75A priority patent/AU476939B2/en
Priority to GB1589375A priority patent/GB1460556A/en
Priority to SE7504440A priority patent/SE405693B/sv
Priority to DE2518240A priority patent/DE2518240C2/de
Priority to CA225,243A priority patent/CA1018864A/en
Priority to FR7512781A priority patent/FR2268573B1/fr
Priority to JP5020875A priority patent/JPS5432987B2/ja
Application granted granted Critical
Publication of US3903972A publication Critical patent/US3903972A/en
Assigned to COOPER INDUSTRIES, INC., A CORP. OF OHIO reassignment COOPER INDUSTRIES, INC., A CORP. OF OHIO ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: HYDROACOUSTICS INC., 321 NORTHLAND AVE., ROCHESTER, N.Y. 14609, A CORP. OF N.Y.
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/06—Means for driving the impulse member
    • B25D9/12—Means for driving the impulse member comprising a built-in liquid motor, i.e. the tool being driven by hydraulic pressure

Definitions

  • ABSTRACT Hydraulic impact tools which develop percussive forces for rock drilling and other repetitive high force applications.
  • a self-excited oscillator is disclosed which includes a hammer and a valve coaxial with and actuated by the hammer for controlling the flow of pressurized hydraulic fluid, The hammer is ac' celerated away from an impact position to store energy in an energy storage system. The stored energy in the system is eventually returned to the hammer to drive it at increasing velocity back to its impact position.
  • Accumulators forming part of the oscillator are closely coupled to the hammer by way of hydraulic galleries or channels and operate in concert with the hammer to provide energy storage characteristics for oscillator operation and to reduce fluctuations in the flow of hydraulic fluid and to provide for efficient op eration of the oscillator.
  • PATEN TED SEP 9 75 saw u o a PATENTED SEP 91975 SHEET 5 BF 8 A x, n xP v, TO DRIVE CAVITY(94) VNHTHROUGH pomuuz) v THROUGH GALLERY (I08) v As sEEN BY RETURN CHANNEL (I46) TIME PATENTEDSEP 9191s V TO DRIVE CAVITY (330) VNETTHROUGH PORT (356) m v As seen 52 A, BY RETURN g CHANNEL (370) f v TO secouo AAA CAVITY (332) X A PATENTEDSEP :915
  • the present invention relates to impact tools and particularly to hydraulically operated impact tools which generate percussive energy.
  • This invention is related to the invention described in US. patent application Ser. No. 285,240, filed in the US. Patent Office in the name of John V. Bouyoucos. on Aug. 3 l, 1972. and is an improvement thereon, and also to a patent application filed in the US. Patent Office in the name of John V. Bouyoucos simultaneously with this application, all of which applications having a common assignee.
  • This invention is especially suitable for use in rock drilling, pile driving, demolition and rock ripping work, in construction, mining and the like fields.
  • the invention is particularly applicable for providing small size, high efficiency rock drills for use in mining and construction.
  • the invention is also applicable to apparatus for generating high blow energies at high repetition rates (i.e., high power levels) and with high efficiency, thereby to obtain improved performance in any application where percussive energy at high power levels is needed.
  • the related application describes tools for generating percussive forces at a load in which a hammer provides a mass which is part of a mass spring oscillator system.
  • the motion of the mass is coupled to a valving mechanism in a hydraulic fluid-filled cavity, switching the pressure of the hydraulic fluid in that cavity abruptly between return and supply pressures to obtain driving forces which accelerate the mass with respect to the spring system.
  • the energy of the accelerated mass is transferred to the spring system which, when the valve mechanism subsequently switches the pressure in the cavity to remove the accelcrating force, decelerates the mass to zero velocity and then drives the mass with increasing acceleration in the opposite direction towards the load.
  • Percussive energy is generated upon impact of the mass with the load.
  • the spring system is provided by a further hydraulic fluid filled cavity, the dynamic spring rate or stiffness of which may be selected to tailor the motion of the ham mcr mass and the energy transfer characteristics of the tool.
  • the spring cavity may, for example, be divided into a pressurized gas filled region and a hydraulic fluid filled region; the pressurized gas operating to reduce the dynamic spring rate or stiffness of the spring portion of the system towards zero so as to provide a constant force upon the hammer and to obtain a relaxation oscillation cycle. This oscillation cycle is especially useful in generating high percussive forces in small tools as are frequently desired in rock drilling.
  • an impact tool embodying the invention includes a housing in which a piston which provides a hammer can oscillate longitudinally in a direction toward or away from a position where it may im pact a load.
  • the piston defines at least a first and a sec ond cavity in the housing. The volume of these cavities vary in opposite senses with the movement of the piston in the same direction.
  • the area of the face of the piston which varies the volume of the first cavity when it moves is larger than the area of the moving face of the piston which varies the volume of the second cavity.
  • the first cavity has a valve mechanism associated therewith which includes a valve clement moved by the piston which alternately opens and closes supply and discharge ports into the first cavity for establishing alternating fluid pressures upon the piston at a frequency determined in part by the mass of the piston and the pressure and compliance of the fluid presented to the mass in the cavities.
  • a third cavity is provided which is in communication with the second cavity.
  • the third cavity is also associated with energy storage means which provides the spring portion of the system and may include an accumulator containing a region of compressible gas which affords a pressure release.
  • This third cavity communicates not only with the second cavity, but also with the first cavity, through the supply port, and with the supply of the pressurized hydraulic fluid. Accordingly, the third cavity maintains substantially constant pressure in the second cavity and in the first cavity when the supply port is open, and simultaneously stores energy which is by draulically coupled thereto from one of the first and second cavities.
  • the third cavity and its communicating channels provide a direct path for the circulation of hydraulic fluid between the first and second cavities due to the difference in areas presented by the faces of the piston presented to the two cavities, thereby to reduce the net fluid volume displacement required of the third cavity and its associated accumulator.
  • the accumulator ca pacity requirement is thereby reduced.
  • the third cavity may conveniently be mounted in a laterally displaced position from the piston, thus enabling an impact tool design which is reduced in size.
  • the piston mass oscillates in a self-excited mode at a frequency determined by the mechanical and acoustical characteristics of the spring, mass and valve mechanism elements associated therewith.
  • This self-excited oscillator is therefore a hydroacoustic oscillator.
  • FIG. 1 is a plan view of a hydraulically operated impact tool of the above mentioned application of John V. Bouyoucos which is filed simultaneously with this application, the view being broken away to illustrate the internal construction of the tool;
  • FIG. 2 is a top end view of the tool shown in FlG. 1;
  • FIGS. 3A and 3B are fragmentary sectional views of the tool shown in PK]. 1, the views being taken along the lines 3A-3A and 3B3B in FIG. 1;
  • FIGS. 4, 5, 6 and 7 are fragmentary views ofthe tool shown in HO. 1 each in a different position during the cycle of oscillation; the various portions of the cycle depicted in each of the views being shown in curves im mediatcly above each view;
  • FIG. 8 is a fragmentary plan view illustrating another hydraulically operated impact tool embodying this in vention.
  • FIG. 9 is a series of curves illustrating the displacement and flow characteristics of the tools illustrated in FIGS. 1 7, and ll.
  • FIG. is a series of curves illustrating the displacement and flow characteristics of the tool illustrated in FIG. 8.
  • FIGS. ll. l2. l3 and 14 are transverse sectional views schematically illustrating tools in accordance with different embodiments of the invention of the ap plication of John V. Bouyoucos and filed simultaneously herewith.
  • FIGS. 1, 2 and 3A and B there is shown an impact tool especially adapted for generating percussive forces for drilling blast holes as in mining. construction. and quarrying work.
  • the tool has a housing 10 in which a piston 12 can execute oscillatory motion along the longitudinal axis of the housing.
  • the piston 12 serves as a hammer which impacts a shank l4.
  • the shank 14 is part of an anvil system which transmits force pulses created by the impact of the lower end of the piston 12 thereon to a load which may consist of a drill steel and rock bit engaged with a rock interface.
  • a chuck assembly 16 holds the shank 14 for rotation by means of a hydraulic motor 18 which is coupled by gearing 20 to the chuck 16.
  • Hydraulic fluid for operating the motor 18 is supplied and discharged through supply and return lines 22 and 24 (FIG. 2).
  • a tube 30 is located for the passage of cleansing fluid. suitably air or water. for flushing and cleaning the holes drilled by the tool.
  • cleansing fluid suitably air or water.
  • Ucup seals 32 are located around the tube 30 in the shank [4.
  • the upper end of the tube 30 may be flanged and sealed in the upper end cap 34 of the housing 10 by means of a hose coupling 36 which compresses a washer 38 to seal the upper end of the tube 30.
  • the housing 10 is made up of a central member 40, an upper end cap 34 and lower end 42 which may be assembled together by suitable bolts and screw arrangements; only the bolts 46 in the upper end cap 34 being shown to simplify the illustration.
  • a central member 40 Internal of the central member is a sleeve 48 which defines a central housing bore 50 in which the piston 12 oscillates. 0" rings or other suitable seals 52 are provided between the interfaces of the sleeve 48 and the central housing member 40 as well as elsewhere between the interfaces of the other housing members and parts to provide fluid seals.
  • the seals between interfaces which slide or rotate with respect to each other are preferably of the U-cup type.
  • a supply accumulator S4 Attached to the central housing member 40 and lat crally offset with respect to the axis of the housing are a supply accumulator S4 and a return or discharge ac cumulator 56.
  • hydraulic fluid is pressurizcd by a suitable pump having a supply and a return which may be connected by hoses or other lines to the tool in a closed loop circuit.
  • fluid may be discharged as to a sump. instead of going to the return side of the pump.
  • discharge and return should be taken as comprehending flow to the pump return side or otherwise to discharge.
  • the accumulators are shown disposed immediately above the hydraulic rotation motor 18. They may also be located in other locations as illustrated in FIGS. 8 and lll4. It is a feature of the invention to facilitate the location of the accumulators 54 and 56 in a manner as shown in order to reduce the envelope (size) and particularly the length of the tool.
  • the accumulators themselves have two sections 60 and 62 which are clamped together as by bolts 66 which also clamp a flexible diaphragm 56 therebetwcen. Holes 76 in the front wall of the section 60 provide a channel for the entry of fluid into the accumulator and retainment of the diaphragm by the front wall. The diaphragm sepa rates the interior of the accumulator into two regions 70 and 72.
  • the outer region 72 may be filled with a compressible fluid (eg. a gas such as air) through a valve 74.
  • the inner region 70 is filled with hydraulic fluid during operation of the tool which fluid enters through the array of holes 76 in the inner wall of the accumulator parts 60.
  • the diaphragm 68 assumes the position shown in dashed lines in the drawing.
  • the accumulators act as energy storage means. as will be explained more fully hereinafter.
  • the lower end 42 of the housing and the interior of the upper end cap 34 are both vented to the atmosphere.
  • An opening 93 in the end cap vents the region 92 and minimizes the compression of the air therein when the hammer 12 moves upwardly away from the impact point.
  • the piston 12 has an upper section 78 adjacent to which is a center section 80 which is of a diameter larger than the upper section 78 so as to form a step 82 therebetween.
  • the piston 12 also has a lower section 84.
  • the lower section 84 has a diameter smaller than the center section 80 and defines another area which is presented by a step which. together with the step 82, defines the differential area of the piston.
  • the step 90 may suitably have twice the area of the step 82. Other area ratios may be employed to achieve different force balance conditions. While the differential area is shown as provided by the steps 82 and 90, it may be presented by other surfaces which may be made up of a plurality of steps or may e of curved shape. such areas or surfaces nevertheless have forces thereon the net total of which depend upon the pressure levels and the net projected areas in a plane normal to the axis of piston motion, such net projected areas being referred to generally by the term faces herein.
  • the lower section of the piston 12 is formed with a ring 86 and another ring 88 which is spaced therefrom, which rings operate the valve mechanism 85 and will be described in detail hereinafter.
  • the end faces of center section 80 of the piston 12 define two variable volume cavities 94 and 96 within the bore 50.
  • the cavity 94 is a first or drive cavity, the volume of which increases by virtue of the movement of the face defined by the step 90 in a direction away from the impact position at the shank 14, while the second or upper cavity 96 decreases in volume for movement in the same direction due to the movement of the face defined by the step 82.
  • the upper cavity 96 is effectively sealed by the U-eup seals 98 around the section 78 of the piston 12. These seals 98 may be located in an upper part 99 of the sleeve 48; the part 99 facilitating assembly of the piston in the housing 10.
  • the lower or drive cavity 94 is sealed by U-cup seals 100 disposed in the sleeve 48, around the lower section 84 of the piston 12.
  • the sleeve 48 and the outer member 40 of the housing also form a third cavity 106 which is in the form of a cylindrical gallery encompassing the bore 50 and laterally displaced therefrom.
  • the valve mechanism 85 is associated with the drive cavity 94.
  • Supply and return or discharge ports 102 and 104 respectively are provided by peripheral internal grooves 105 and 107 in the sleeve 48. These grooves are in communication with the galleries 106 and 108 through lateral passages 109 which occupy a substantial portion of the periphery of the sleeve 48 (see FIG. 38) to present a low inertance to the flow through the ports 102 and 104.
  • the gallery [06 extends between the supply port 102 and an opening 110 to the upper cavity 96 and thus communicates the upper cavity 96 and the drive cavity 94 when the supply port 102 is open.
  • the holes 76 in the inner part 60 of the supply accumulator 54 also provide an essentially unrestricted channel which communicates directly with the gallery 106 and therefore via the gallery with the upper cavity 96 and drive cavity 94.
  • the supply accumulator holes 76 are disposed opposite to an opening 112 in the housing section 40 which is directly adjacent the opening 110 and extends between these holes and the gallery 106.
  • a channel 114 connects the opening 112 to a coupling 116 through which the supply line from a source of pressurized hydraulic fluid, say a hydraulic pump which supplies fluid pressures in the range of 2000 to 3000 psi. may be connected.
  • the return accumulator 56 also has the holes 76 which provide the entry channel, in the front wall of its inner part 60 in direct communication with the lower gallery 108 such that the accumulator 56 is connected to the drive cavity 94 when the return port 104 is open.
  • the return line for the hydraulic pump is connected to a coupling 118 to which a return line 120 extends downwardly into the gallery 108 (see FIG. 2), the return line 120 being disposed behind the supply line 114.
  • valve mechanism in addition to the ports 102 and 104, the valve mechanism includes a valve element 122 in the form of a hollow cylindrical member or sleeve which is coaxial to lower section 84 of the piston which is located between the rings 86 and 88 and which is slidably mounted with respect to the bore 50.
  • the valve element is shown having longitudi nal dimension essentially equal to the distance between the outer edges 123 and 125 of the grooves providing the supply and return ports 102 and 104.
  • the inner periphery of the valve element is also formed with longitudinally extending slots I24, (cusp-shaped in crosssection as shown in FIG. 3) which provide an unrestricted passage for the hydraulic fluid therethrough.
  • the lower edge of the ring 86 engages the upper end of the valve element 122 as the piston moves down so as to open the supply port 102 and close the return port 104.
  • the ring 88 engages the lower end of the valve element 122 as the piston moves up so as to open the return port 104 and close the supply port 102.
  • the upper and lower ends of the valve element are preferably provided with damping means such as steps which effectively form dash pots with the rings as more fully described in the above referenced Bouyoucos application Ser. No. 285,240.
  • the large diameter (equal to the maximum piston diameter) of the valve element 122 and its coaxial arrangement with respect to the large area galleries 106 and 108 reduces inertance in the dynamic flow path and increases power (I) nversion efficiency. This feature is especially advantageous at high output power levels (i.e., high flows) where inertance becomes even more significant.
  • the large diameter valve enables the pressure drop across the ports to be maintained at a low value until the last instant of valve closure, thereby reducing hydraulic power losses and providing high efficiency.
  • FIG. 4 shows the piston 12 at the beginning of the cycle of oscillation with the piston in its displaced position at impact with the shank [4. This is indicated as time I T
  • the upper ring 86 has moved the valve element I22 so that both the supply port 102 and the return port 104 are momentarily closed. After the piston reaches the impact position, the valve element may move, due to its own inertia. to a position below that shown in FIG.
  • the supply port is open and the return port closedv Pressurized fluid is supplied to the drive cavity 94 and accelerating forces are applied to the drive face formed by the step 90.
  • the pressurized fluid is also applied to the upper cavity 96.
  • the piston 12 has its differential area A,- presented to the pressurized fluid in these cavities 94 and 96; the area of the face formed by the step being larger than the area of the face formed by the step 82.
  • the net force applied to the differential area is therefore in the upward direction and accelerates the piston upwardly.
  • the supply accumulator 54 tends to keep the pressure in the drive cavity 94 constant since the compressed gas in the region 72 thereof acts as a pressure release.
  • the piston 12 then moves upwardly a distance X equal to the difference between the distance between the opposing faces of the rings 86 and 88 and the length of the valve element 122.
  • the accelerating forces are applied until the lower ring 88 moves the valve element 122 to the position shown in FIG. 5, immediately after which the valve element closes the supply port I02 and opens the return port 104. This occurs at a time in the cycle 1",.
  • the pressure in the drive cavity 94 is then switched from supply to return and the direction of force on the piston is switched to decelerate the piston motion as shown in FIG. 6. Energy has been transferred during the period from T to T to the piston mass to give the piston kinetic energy.
  • the piston 12 After the piston 12 has travelled over a time period I T- T, the piston has decelerated to zero velocity and has transferred its kinetic energy to the spring system presented by the hydraulic fluid in the cavity 96 as well as in gallery 106 and in the supply accumulator 54.
  • the accumulator 54 includes the pressure release region 72 which affords a constant spring force (viz., the dynamic spring rate or stiffness being reduced toward zero) a relaxation oscillator characteristic is obtained as shown in waveform (u) of FIG. 9 and in the waveforms at the tops of FIGS. 4 through 7.
  • the energy introduced by the accelerating forces applied to the piston during the time period T to T as well as its displacement over that interval is then transferred back to the piston to drive it downwardly towards impact. As shown in FIG.
  • the discharge port 104 remains open while the supply port I02 remains closed. Port switching occurs immediately after impact, and the impact reaction force assists the supply pressure in driving the piston upwardly to begin the next cycle of oscillation.
  • the force on the average which is in the upward direction due to the impact event and also in the upward direction during the time interval T is balanced by forces in the downward direction during the time interval from T to T.
  • the ratio of the areas presented by the steps 90 and 82 may nominally be 2:l, but may also be adjusted to provide a specific force balanced condition on average. The forces due to the impact events as well as the losses in the system are considered in providing the exact ratio.
  • the blow energy E applied to the shank 14 at the end of each cycle is proportional to the potential energy possessed by the piston at the top of its stroke at time I T
  • This energy may be expressed by the following equationz ll l s F I') (I) where k, is a constant, P is the supply pressure and )2 is the total piston travel to the top of its trajectory.
  • k is a constant
  • P is the supply pressure
  • )2 is the total piston travel to the top of its trajectory.
  • the total piston travel distance to the top of its trajectory is approximately twice the distance travelled over the time interval T to T,.
  • the total piston travel is then given by:
  • the frequencyufm of oscillation may be derived from the kinetic and potential energy relationships and may be expressed as where k is a constant and M P is the mass of the piston.
  • the arrangement of the supply port 102, the opening 110 and the gallery 106 provides a direct path and permits the fluid to flow back and forth (viz. exchange) between the upper cavity 96 and the drive cavity 94, so as with the aid of the supply accumulator 54, to provide the dynamic flow requirements of the tool and to reduce pressure fluctuations in the supply region which might otherwise interfere with the oscillation cycle, Curve (1)) of HG.
  • 9 shows the volume V,-,, transferred to the drive cavity 94 through the supply port 102. This volume transfer occurs during the time interval T to T, and is equal to X,,A,, over the interval T to T A, is the area presented by the step 90 to the drive cavity 94. A,; is the area presented by the step 82 to the upper cavity 96.
  • volume changes due to the compressibility of the hydraulic fluid and the elasticity of the sleeve 48 and other housing members is neglected for purposes of explanation. Since the total piston travel in the upward direction is X, which is twice X for this exemplary case, the following relationships respecting the volume displacement V,, in the drive cavity 94 and the volume displacement V in the upper cavity 96 exist.
  • the net volume supply to both the drive cavity and the upper cavity over the time interval T to T during which interval the port to the drive cavity is open is therefore Hm N I-' 1,] 'tt' 'r' iil 4 1
  • the net input volume displacement over the time interval T,T is half the volume supplied to the drive area A (via, to the drive cavity 94) alone.
  • the joining of the drive cavity and upper cavity through the gallery, during the time interval T,T creates less of an instantaneous demand on the supply than would the requirements of the drive cavity alone, and reduces the flow requirement from the accumulator 54.
  • the accumulator is better able to maintain the supply pressure constant over the entire cycle of oscillation.
  • the supply port 102 is closed so that the volume handled by the supply accumulator 54 is the difference between the input volume passing through the channel 114 and the volume displaced by the area A of the step 82. Over the first portion of this interval (between T, and T the area A is expelling fluid from the upper cavity 96 back into the supply accumulator 54.
  • the upper cavity 96 accepts flow from the accumulator 54 and from the supply in an amount equal to X A which amount is one-half the volume displaced from the drive cavity into the return accumulator 56.
  • the dashed lines represent the average dis placement rate. This is also the case in FIG. 10.
  • the displacement curves of FIG. 9 (c) illustrate that when the common channel (gallery 106) interconnects the accumulator 54 and the drive and upper cavities, the fluctuation or ripple in the flow is reduced over the ripple which would exist if the upper cavity 96 was fed from a separate accumulator which would then have to supply the displacement shown in curve (b).
  • Curve (d) of FIG. 9 shows the volume displacement as seen by the discharge accumulator 56.
  • the discharge or return port I04 is closed, such that the volume does not change.
  • the port 104 opens, and the piston I2 is continuing its upward trajectory. Flow is therefore backwards through the port 104 and into the drive cavity 94. This flow is supplied by the discharge accumulator 56. From time T to impact at time T,. the flow is out of the port 104 and the accumulator accepts a peak volume displacement X A
  • the ripple or fluctuation as seen by the discharge accumulator 56 is greater than the ripple or fluctuations as seen by the supply accumulator and shown in curve (c) of FIG. 9.
  • FIG. 8 there is shown another impact tool having a housing 300.
  • the piston 3I0 thus acts as a hammer for providing percussive forces upon impact with the shank 312.
  • the shank may be connected to a drill steel and a bit for drilling holes in a formation. say for construction, quarrying or mining purposes.
  • the piston 310 has a central section 320 which is of greater diameter than the diameter of the lower section 322 as well as the diameter of an upper section 324 of the piston 310.
  • the lower section 322 has a larger diameter than the upper section 324, such that opposite faces 326 and 328 of the center section 320 respectively present a larger area and a smaller area to a first cavity 330 and a second cavity 332, the end boundaries of which are defined by the faces 326 and 328. While these faces 326 and 328 are shown in the form of steps, other boundary surfaces of other shape may be provided, the term face being used to define any such boundary surface in general.
  • the first cavity 330 provides a drive cavity for the piston and includes the valve mechanism for switching the fluid pressure from supply to return therein, while the second cavity 332 is exposed to the supply pressure at all times.
  • a valve mechanism 334 consisting of a supply port 336, a return port 338, a valve element 340, and spaced rings 342 and 344 on the piston 310 which engage the valve element 340, is located in drive cavity 330.
  • the ports 336 and 338 are provided by peripheral grooves which extend circumferentially around the inner wall of the bore 308 as in a manner similar to that shown in FIG. 3B
  • the opposite edges of the valve element 340 provide porting edges which afford full peripheral porting to which efficiency advantages mentioned above are attendant.
  • the valve element is slidably mounted within the bore 308 coaxial to the piston 310 and has channels 346 which extend longitudinally thereof as was described in connection with the valve element 122 (FIG. I).
  • the second cavity as well as the supply port 336 are in communication by way of lateral channels 348 and 350 with a circumferential gallery 352 which extends therebetween.
  • This gallery 352 is also in communication with a supply accumulator 354 by way of a large lateral opening 356 and a multiplicity of channels 358 in the wall of the accumulator 354 which is adjacent to the opening 356.
  • the accumulator 354 may be of a design similar to the accumulator 54 (FIG. I).
  • Another gallery encompasses the upper end of the drive cavity 330 and is in communication with the return port 338 via a lateral channel 362.
  • the gallery 360 is connected by way of a large opening 364 to a return accumulator 366.
  • a multiplicity of channels 368 in the wall of the accumulator 366 adjacent the opening 364 provides direct communication between the return accumulator 366 and the gallery 360.
  • the return accumulator 366 may be similar to the return accumulator 56 (FIG. I
  • the return of the supply of pressurized hydraulic fluid is connected by way of a channel 370 to the return gallery 360.
  • a similar channel 37I into the lateral opening 356 provides for connection of the supply for the source of pressurized fluid to the supply gallery 352.
  • U-cups and O-ring seals respectively for sliding sur faces and stationary surfaces are shown to seal the cavities and fluid channels in the housing. Cleansing fluid, such as compressed air. may be communicated through the piston 310 and the shank 312 by way of a pipe 372 which extends through bores therein. as was described in connection with FIG. I.
  • FIG. 8 depicts the position of the piston 310 and the valve element 340 just at the instant of impact with the shank (viz, when the piston reaches the impact position).
  • the length of the valve 340 with respect to the return and supply ports 338 and 336, and the position of the ring 342 on piston 310 is such that the return port 338 will immediately become opened and the supply port 336 closed as the valve element 340 travels downward somewhat from the position shown in FIG. 8. Then, during the first portion of the cycle of oscillation, from T, to T (see FIG.
  • pressurized fluid is applied to the second cavity 332 but the drive cavity 330 is open to return by the valve mechanism.
  • the ratio of the areas of the faces 326 to 328 is preferably of the order of 2:l.
  • the pressurized fluid acting on the face 328 drives the piston upwardly in a direction away from the impact position.
  • the characteristics of the massive piston. the springlike fluid in the cavities. galleries and channels as well as the accumulator. define a relaxation oscillator which develops percussive forces especially adapted for timedependent loads such as are encountered in rock drilling.
  • the flow into the drive cavity 330 is cut off during the initial portion of the cycle from 'I], to T,. Then flow during the second part of the cycle from T, to T is outward from the drive cavity as the kinetic energy of the hammer is stored in the fluid, springs. and accumulator 354.
  • the displacement of fluid into the second cavity 332 increases from T. to T and then decreases (outward from the cavity) during the remainder of the cycle from T to T,..
  • the flow from the second cavity is communicated with the gallery 352 and. when combined with the flow to the first cavity. tends to reduce the net dynamic flow requirements from the accumulator.
  • the net dynamic flow from the accumulator 354 is illustrated in curve (1') of FIG. 10. It will be seen from this curve that the net flow fluctuations are reduced from those associated with the first or drive cavity.
  • FIG. ll. there is shown an impact tool having a hammer 130 movable in a bore within a hous ing 132.
  • the housing has also mounted thereon a sup ply accumulator I40 and a return accumulator 142.
  • the supply line 144 from the source of pressurized hydraulic fluid enters into the supply accumulator 140.
  • a return line I46 enters the return or discharge accumulator 142.
  • a gallery 156 communicates the second and first cavities I52 and 154 when the supply port I58 is opened by the valve element 160.
  • the valve element I60 also switches the fluid pressure in the first cavity I54 from supply pressure to return pressure by closing the supply port 158 and opening the return port I62.
  • the impact tool as shown in FIG. 11 thus operates like (ill the tool shown in FIG. 1. and the supply pressure fluctuation is minimized by virtue of the interconnection of the first and second cavities, as was explained in connection with FIGS. 1 through 8.
  • the impact tool shown in FIG. 1] is equipped with a lower piston section 164, which with the piston section I66 adjacent thereto forms a step 168.
  • the piston section 164 has the same area as the section of the piston providing the step I50.
  • This step 168 bounds one end of a lower cavity 170 which varies in volume. as the piston [30 moves. in a sense opposite to the variation in volume ofthe first cavity 154. Accordingly. the pressurized fluid can flow back and forth between the first cavity and the cavity 170 by way of a gallery 174 which provides communication therebetween.
  • the discharge accumulator also opens into the gallery 174 by way of an unrestricted passage 176.
  • a housing is provided with a bore 182 in which the hammer of the tool. provided by a piston 184, oscillates.
  • a supply accumulator I86 and a return accumulator 188 are shown located on opposite sides of the housing 180. While such location provides a more balanced size and weight relation which may be desired in some applications for impact tools. other accumulator locations may be used.
  • the tool has a first cavity 190 and a second cavity 192. The first cavity performs the same function as the first cavity 94 of FIG. I while the second cavity 192 performs the same function as the cavity 96 of FIG. I. however their positions are reversed. Such reversal provides the feature of simplification of the construction of the piston 184.
  • the piston may be a two-part structure con sisting of a lower part I94, the upper end of which I96 is threaded.
  • the upper part 198 of the piston is in the form of an internally threaded disc having an axially extending rim 200. The entire part 198 may be screwed onto the threaded end 196 in a manner of a nut.
  • valve element 202 can. by virtue of the two-part construction of the piston 184. be assembled on the piston in the first cavity 190.
  • the same two-part construction feature can be implemented in connection with the configuration shown in the other FIGS. of the drawing, including FIGS. 1 and 8.
  • the valve element 202 in FIG. 12 is provided with a centrally disposed lip 204 which is engaged between the rim 200 and a shoulder 206 of the piston I84.
  • the rim 200 and shoulder 206 are spaced longitudinally from each other a distance relative to the length of the lip 204 of the valve 202 to provide the desired delay displacement and free stroke X of the valve 202.
  • the valve element 202 is also vented by way of holes 208 which extend longitudinally therethrough. A number of such holes, which perform the same function as the groove 90 in the valve element 122 (FIG. 1) are distributed around the valve element 202.
  • the second cavity 192 is connected to the first cavity 190 by way of a channel 210.
  • the supply line 212 also communicates with the channel 210.
  • the supply accumulator 186 opens into the channel 210 through a port 214. Accordingly, when the supply port 216 is open, volume flow from the second cavity 192 to the first cavity 190 partly compensates for the first cavity requirements, thereby minimizing the total volume displacement required from the supply accumulator 186.
  • the accumulator 186 provides flow to the second cavity 192 when the return or discharge port 218 is opened and the supply port 216 is closed. Accordingly, the fluctuations are minimized and maintenance of constant prcssure aided as was explained in connection with FIG. 1.
  • the discharge port 218 is connected to the discharge accumulator 188 via an opening 219.
  • the return line 220 also enters into this opening. The discharge fluctuations are similar to those depicted in FIG. 9 (d).
  • the impact tool shown in FIG. 13 is similar to the tool shown in FIG. 12, like parts being identified with like reference numerals.
  • An additional cavity 230 is partially bounded by a piston step 232 of the same area as the piston step 234 which defines and varies the volume of the first cavity 190.
  • the step 234 has a larger area than the step 236 which defines and varies the volume of the second cavity 192.
  • a channel 240 is provided which extends longitudinally between the discharge port 218 and the additional cavity 230.
  • the return accumulator also is connected to the channel 240 by way of an opening 242.
  • the return line 220 also enters the channel.
  • FIG. 14 there is shown an impact tool which is similar, insofar as the construction of its piston 184 is concerned, with the tool shown in FIG. 12 and like parts of these tools identified with like referenced numerals.
  • the valve element 202 is provided with a pcripheral slot 250 which is centrally located between the upper and lower ends of the valve element 202.
  • the slot communicates with the vents 208.
  • the porting between the supply and return ports 216 and 218 is therefore through the slot 250.
  • the effective length of the valve ele ment 208 is therefore the width (in the vertical direction) of the slot 250.
  • the supply port 216 is now located below the return port 218. This permits the channel 210 (FIG. 12) to be provided by a gallery 252 which extends circumferentially around the housing and encircles the piston 184. The use of this gallery simplifies the construction of the housing and assures unrestricted communication between the first cavity 190 and the second cavity 192.
  • An impact tool for generating percussive forces comprising:
  • a housing have a bore
  • a piston disposed for oscillatory movement in said bore over a forward stroke toward and over a return stroke away from an impact position during each cycle of oscillation of said piston
  • said piston having faces which define the end bound aries of first and second variable column cavities in said bore, the volumes of which vary in opposite senses when said piston moves in said bore,
  • the area of the one of said faces which defines said first cavity being greater than the area of the other of said faces which defines said second cavity.
  • valve mechanism associated with said first cavity having ports in said first cavity spaced from each other axially with respect to said bore and respectively in communication with said supply and said return of said last-named means, a valve element in said first cavity extending axially between said ports and movable with said piston for closing said supply port and opening said return port after displacement of said piston over a first predetermined distance in one direction during said forward stroke and for opening said supply port and closing said return port after displacement of said piston over a second predetermined distance in the opposite direction during said return stroke, said second predetermined displacement being substantially less than said return stroke whereby said return port is open for a shorter period of time than said supply port is open during each said cycle, and
  • means in said housing providing communication between said supply and said second cavity for apply ing forces to said other piston face to drive it in a direction away from said impact position when said valve element opens said return port and closes said supply port.
  • said piston has a section of cross-sectional shape and size substantially equal to the cross-sectional shape and size of said bore, said faces being opposite ends of said piston section, said other of said faces being closer to said impact position than said one face.
  • valve element is a tubular member coaxial with said bore and encompassing said piston and is slidable along said bore across said ports, projections extending from one of said tubular member and said piston for directly engaging applying force to said tubular member for moving said tubular member.
  • said cavities are generally cylindrical chambers provided in said housing, and said ports are separate peripheral grooves in said chamber for said first cavity which are opened and closed by porting edges of said tubular member.
  • said fluid is a hydraulic fluid and said accumulator has a fluid filled region and an adjoining region filled with a confined gas. said regions being separated by a yieldable member, said fluid filled region being in communication with said second cavity and said first cavity when said supply port is open.
  • An impact tool for applying percussive forces to a load comprising a housing having a bore therein.
  • a piston mounted in said bore for oscillatory movement axially of said bore in a first direction toward said load and in a second direction away from said load.
  • said piston having a section having first and second faces at opposite ends of said section, said first face facing away from said load and defining the end boundary of a first cavity in said bore, said second face facing toward said load and defining the end boundary of a second cavity in said bore. the volumes of said cavities changing in opposite sense with movement of said piston in either of said directions, said first face being larger in area than said second face,
  • pressurized hydraulic fluid supply and return passages in said housing being in communication with the supply passage for filling said second cavity with pressurized fluid which ex erts force on said second face in the direction away from said load
  • a valve mechanism in said first cavity including a sleeve slidably mounted in said bore for movement axially thereof.
  • means providing for moving said sleeve with said piston during final portions of its displacement in said first direction and during final portions of its displacement in said second direction for respectively communicating said first cavity with said return passage for causing said forces applied to said second face to move said piston in the direction away from said load and with said supply passage for applying forces to said first face in the direction toward said load.
  • said final portion of said displacement in said second direction being a substantial portion of said displacement in said second direction
  • said communicating means communicating said energy storage means with said second cavity. with said supply means and also with said first cavity, when said valve mechanism communicates said supply with said first cavity, and for storing energy in said storage means when said piston is moving away from said load. thereby to bring said piston movement to a stop. said energy being returned to said piston as said piston accelerates back in the direction toward said load for applying said percussive forces thereto.
  • said communicating means also providing an unrestricted passage for the exchange of fluid between said first and second cavities for reducing fluctuations in flow with respect to said storage means.

Landscapes

  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Earth Drilling (AREA)
  • Placing Or Removing Of Piles Or Sheet Piles, Or Accessories Thereof (AREA)
  • Drilling And Exploitation, And Mining Machines And Methods (AREA)
US463625A 1974-04-24 1974-04-24 Impact tools Expired - Lifetime US3903972A (en)

Priority Applications (9)

Application Number Priority Date Filing Date Title
US463625A US3903972A (en) 1974-04-24 1974-04-24 Impact tools
ZA00752428A ZA752428B (en) 1974-04-24 1975-04-16 Impact tool generating percussive forces
GB1589375A GB1460556A (en) 1974-04-24 1975-04-17 Impact tool for generating percussive forces
SE7504440A SE405693B (sv) 1974-04-24 1975-04-17 Slagverktyg for alstring av slag-tryckkrafter
AU80245/75A AU476939B2 (en) 1974-04-24 1975-04-17 Impact tool for generating percussive forces
DE2518240A DE2518240C2 (de) 1974-04-24 1975-04-22 Hydraulisches Schlagwerk für ein Werkzeug
CA225,243A CA1018864A (en) 1974-04-24 1975-04-23 Impact tool for generating percussive forces
FR7512781A FR2268573B1 (sv) 1974-04-24 1975-04-24
JP5020875A JPS5432987B2 (sv) 1974-04-24 1975-04-24

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US463625A US3903972A (en) 1974-04-24 1974-04-24 Impact tools

Publications (1)

Publication Number Publication Date
US3903972A true US3903972A (en) 1975-09-09

Family

ID=23840754

Family Applications (1)

Application Number Title Priority Date Filing Date
US463625A Expired - Lifetime US3903972A (en) 1974-04-24 1974-04-24 Impact tools

Country Status (9)

Country Link
US (1) US3903972A (sv)
JP (1) JPS5432987B2 (sv)
AU (1) AU476939B2 (sv)
CA (1) CA1018864A (sv)
DE (1) DE2518240C2 (sv)
FR (1) FR2268573B1 (sv)
GB (1) GB1460556A (sv)
SE (1) SE405693B (sv)
ZA (1) ZA752428B (sv)

Cited By (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4039033A (en) * 1975-01-16 1977-08-02 Oy Tampella Ab Hydraulic rock drill
US4062411A (en) * 1975-12-05 1977-12-13 Gardner-Denver Company Hydraulic percussion tool with impact blow and frequency control
US4265321A (en) * 1975-11-12 1981-05-05 Joy Manufacturing Company Rock drill
US4282937A (en) * 1976-04-28 1981-08-11 Joy Manufacturing Company Hammer
US4409368A (en) * 1981-07-13 1983-10-11 The General Tire & Rubber Company Preparation of star polymers
US4550785A (en) * 1976-04-28 1985-11-05 Consolidated Technologies Corporation Hammer
US4569412A (en) * 1982-05-26 1986-02-11 Hydroacoustics Inc. Seismic source
US4828048A (en) * 1986-11-10 1989-05-09 Mayer James R Hydraulic Percussion tool
US4858701A (en) * 1987-11-30 1989-08-22 Weyer Paul P Fluid-powered impact device and tool therefor
FR2657806A1 (fr) * 1990-02-02 1991-08-09 Karagandin Politekhn Marteau hydraulique a main.
US5305841A (en) * 1990-04-11 1994-04-26 Sandvik Ab Hammer device
US5511626A (en) * 1994-01-11 1996-04-30 Breakers A/S Hydraulically operated subsoil displacement apparatus
US5680904A (en) * 1995-11-30 1997-10-28 Patterson; William N. In-the-hole percussion rock drill
EP0885694A1 (en) * 1997-06-11 1998-12-23 Hyup Sung Heavy Industries Co. Ltd. Hydraulic hammer having improved seal ring
US6105686A (en) * 1998-03-30 2000-08-22 Tamrock Oy Pressure accumulator arrangement in connection with a hydraulically operated impact device, such as a breaking apparatus
US6110045A (en) * 1997-06-09 2000-08-29 Atlas Copco Tools Ab Hydraulic torque impulse generator
US6155361A (en) * 1999-01-27 2000-12-05 Patterson; William N. Hydraulic in-the-hole percussion rock drill
US6293357B1 (en) 1999-01-27 2001-09-25 William N. Patterson Hydraulic in-the-hole percussion rock drill
US6464023B2 (en) 1999-01-27 2002-10-15 William N. Patterson Hydraulic in-the-hole percussion rock drill
WO2005087444A1 (en) * 2004-03-12 2005-09-22 Atlas Copco Construction Tools Ab Hydraulic pressure accumulator
US7156190B2 (en) 2003-12-19 2007-01-02 Clark Equipment Company Impact tool
US20090223720A1 (en) * 2008-03-06 2009-09-10 Patterson William N Internally dampened percussion rock drill
US20100155096A1 (en) * 2007-02-01 2010-06-24 Morrison Ward D Fail-resistant hammer assembly for a valveless percussive drill
KR200466458Y1 (ko) * 2009-11-11 2013-04-18 주식회사수산중공업 유압 타격장치용 어큐뮬레이터의 비정상 압력 해소장치
US8474363B2 (en) 2011-07-03 2013-07-02 Vincent M. Kelly Axial piston and valve shaft fluid engine
US20130186667A1 (en) * 2010-08-31 2013-07-25 Maria Pettersson Hydraulic impact mechanism for use in equipment for treating rock and concrete
WO2013174359A1 (de) * 2012-05-23 2013-11-28 Atlas Copco Construction Tools Gmbh Schlagvorrichtung
US20150053076A1 (en) * 2012-02-17 2015-02-26 Construction Tools Pc Ab Pressure accumulator and percussion device
NO337771B1 (en) * 2015-03-18 2016-06-20 Resonator As Percussive hammering assembly
CN110984843A (zh) * 2019-12-29 2020-04-10 东莞海特帕沃液压科技有限公司 一种液压冲击钻动力装置
WO2021062483A1 (en) * 2019-10-03 2021-04-08 Warren Strange Liquid hammer drill

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Publication number Priority date Publication date Assignee Title
US2749886A (en) * 1954-06-07 1956-06-12 Richard M Densmore Fluid pressure self-reciprocating actuator
US3322210A (en) * 1963-09-06 1967-05-30 Beteiligungs & Patentverw Gmbh Impact tool
US3411592A (en) * 1965-01-28 1968-11-19 Montabert Roger Percussion apparatus
US3468222A (en) * 1966-07-06 1969-09-23 Hugo H Cordes Control for a ramming hammer with hydraulic drive

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1230386B (de) * 1964-11-19 1966-12-15 Salzgitter Maschinen Ag Hydrobohrhammer
DE6602835U (de) * 1965-10-11 1969-07-03 Heinz Callsen Mit druckfluessigkeit betriebenes schlaggeraet

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2749886A (en) * 1954-06-07 1956-06-12 Richard M Densmore Fluid pressure self-reciprocating actuator
US3322210A (en) * 1963-09-06 1967-05-30 Beteiligungs & Patentverw Gmbh Impact tool
US3411592A (en) * 1965-01-28 1968-11-19 Montabert Roger Percussion apparatus
US3468222A (en) * 1966-07-06 1969-09-23 Hugo H Cordes Control for a ramming hammer with hydraulic drive

Cited By (43)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4039033A (en) * 1975-01-16 1977-08-02 Oy Tampella Ab Hydraulic rock drill
US4265321A (en) * 1975-11-12 1981-05-05 Joy Manufacturing Company Rock drill
US4062411A (en) * 1975-12-05 1977-12-13 Gardner-Denver Company Hydraulic percussion tool with impact blow and frequency control
US4282937A (en) * 1976-04-28 1981-08-11 Joy Manufacturing Company Hammer
US4550785A (en) * 1976-04-28 1985-11-05 Consolidated Technologies Corporation Hammer
US4409368A (en) * 1981-07-13 1983-10-11 The General Tire & Rubber Company Preparation of star polymers
US4569412A (en) * 1982-05-26 1986-02-11 Hydroacoustics Inc. Seismic source
US4828048A (en) * 1986-11-10 1989-05-09 Mayer James R Hydraulic Percussion tool
US4858701A (en) * 1987-11-30 1989-08-22 Weyer Paul P Fluid-powered impact device and tool therefor
FR2657806A1 (fr) * 1990-02-02 1991-08-09 Karagandin Politekhn Marteau hydraulique a main.
US5305841A (en) * 1990-04-11 1994-04-26 Sandvik Ab Hammer device
US5511626A (en) * 1994-01-11 1996-04-30 Breakers A/S Hydraulically operated subsoil displacement apparatus
US5680904A (en) * 1995-11-30 1997-10-28 Patterson; William N. In-the-hole percussion rock drill
US6110045A (en) * 1997-06-09 2000-08-29 Atlas Copco Tools Ab Hydraulic torque impulse generator
EP0885694A1 (en) * 1997-06-11 1998-12-23 Hyup Sung Heavy Industries Co. Ltd. Hydraulic hammer having improved seal ring
US6105686A (en) * 1998-03-30 2000-08-22 Tamrock Oy Pressure accumulator arrangement in connection with a hydraulically operated impact device, such as a breaking apparatus
US6155361A (en) * 1999-01-27 2000-12-05 Patterson; William N. Hydraulic in-the-hole percussion rock drill
US6293357B1 (en) 1999-01-27 2001-09-25 William N. Patterson Hydraulic in-the-hole percussion rock drill
US6464023B2 (en) 1999-01-27 2002-10-15 William N. Patterson Hydraulic in-the-hole percussion rock drill
US7156190B2 (en) 2003-12-19 2007-01-02 Clark Equipment Company Impact tool
WO2005087444A1 (en) * 2004-03-12 2005-09-22 Atlas Copco Construction Tools Ab Hydraulic pressure accumulator
US20070199724A1 (en) * 2004-03-12 2007-08-30 Lundgren Anders W Hydraulic Pressure Accumulator
US7478648B2 (en) 2004-03-12 2009-01-20 Atlas Copco Construction Tools Ab Hydraulic pressure accumulator
US20100155096A1 (en) * 2007-02-01 2010-06-24 Morrison Ward D Fail-resistant hammer assembly for a valveless percussive drill
US8991515B2 (en) * 2007-02-01 2015-03-31 J.H. Fletcher & Co. Fail-resistant hammer assembly for a valveless percussive drill
US20090223720A1 (en) * 2008-03-06 2009-09-10 Patterson William N Internally dampened percussion rock drill
US7681664B2 (en) 2008-03-06 2010-03-23 Patterson William N Internally dampened percussion rock drill
US20100116520A1 (en) * 2008-03-06 2010-05-13 Patterson William N Internally dampened percussion rock drill
US8028772B2 (en) 2008-03-06 2011-10-04 Patterson William N Internally dampened percussion rock drill
KR200466458Y1 (ko) * 2009-11-11 2013-04-18 주식회사수산중공업 유압 타격장치용 어큐뮬레이터의 비정상 압력 해소장치
US20130186667A1 (en) * 2010-08-31 2013-07-25 Maria Pettersson Hydraulic impact mechanism for use in equipment for treating rock and concrete
US9289889B2 (en) * 2010-08-31 2016-03-22 Atlas Copco Rock Drills Ab Hydraulic impact mechanism for use in equipment for treating rock and concrete
US8474363B2 (en) 2011-07-03 2013-07-02 Vincent M. Kelly Axial piston and valve shaft fluid engine
US20150053076A1 (en) * 2012-02-17 2015-02-26 Construction Tools Pc Ab Pressure accumulator and percussion device
US9630306B2 (en) * 2012-02-17 2017-04-25 Construction Tools Pc Ab Pressure accumulator and percussion device
WO2013174359A1 (de) * 2012-05-23 2013-11-28 Atlas Copco Construction Tools Gmbh Schlagvorrichtung
US20150068782A1 (en) * 2012-05-23 2015-03-12 Markus Mellwig Percussion device
NO337771B1 (en) * 2015-03-18 2016-06-20 Resonator As Percussive hammering assembly
NO20150341A1 (en) * 2015-03-18 2016-06-20 Resonator As Percussive hammering assembly
WO2016148575A1 (en) * 2015-03-18 2016-09-22 Resonator As Percussive hammering assembly
WO2021062483A1 (en) * 2019-10-03 2021-04-08 Warren Strange Liquid hammer drill
CN110984843A (zh) * 2019-12-29 2020-04-10 东莞海特帕沃液压科技有限公司 一种液压冲击钻动力装置
CN110984843B (zh) * 2019-12-29 2021-09-10 东台市高科技术创业园有限公司 一种液压冲击钻动力装置

Also Published As

Publication number Publication date
DE2518240C2 (de) 1985-09-05
JPS5432987B2 (sv) 1979-10-17
AU8024575A (en) 1976-10-07
JPS50148202A (sv) 1975-11-27
FR2268573A1 (sv) 1975-11-21
SE405693B (sv) 1978-12-27
DE2518240A1 (de) 1975-11-20
AU476939B2 (en) 1976-10-07
SE7504440L (sv) 1975-10-27
CA1018864A (en) 1977-10-11
ZA752428B (en) 1976-03-31
GB1460556A (en) 1977-01-06
FR2268573B1 (sv) 1980-10-17

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