• 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:
    Improvements in pneumatic percussion tools, of the type comprising a body having an elongated hole with an end adapted to receive a part of a tool in its interior, whose tool extends to the outside of said body, a piston displaceable alternately within of said hole to provide impacts to said tool, a set of steps having at least a part inside said body to allow the hydraulic fluid to cause the reciprocating movement of said piston, said part of the fluid passages arranging less a chamber located laterally and outward of said hole with an open area on the outer surface of said body and also a housing having an elongated hole therein.
    公开号:SU784805A3
    申请号:SU772477061
    申请日:1977-04-28
    公开日:1980-11-30
    发明作者:Аллен Хиббард Джордж；Даффи Моррисон Ворд
    申请人:Джой Мануфакчуринг Компани (Фирма)；
    IPC主号:
    专利说明:

    (54) HYDRAULIC IMPACT TOOL
    The invention relates to a valveless hydraulic percussion instrument in which the drummer performs reciprocating movements of fluid pressure to impart blows to the shank of the working tool. A hydraulic percussion instrument is known that contains a head located in a cylinder, for reciprocating which movement there are cocking and working plungers arranged at the respective ends of the cylinder and displaced under the action of fluid pressure in the hydroaccumulator periodically communicated with the cylinder cavities of said pistons i . In the described tool design, the efficiency of energy transfer from the hammer to the working tool is reduced due to the presence of plungers. Some of the hydraulic impact tools are sensitive to small changes in the pressure of the injected fluid or to the location of the end of the working tool shank. Other tools are very difficult to get started and are quite complex in manufacturing. The closest technical solution to the image is a hydraulic percussion instrument that includes a housing with an axial cylindrical bore, a hammer placed inside it with the possibility of returnable displacement to communicate the blows of the working tool, the shank of which is located in this bore, a shell located around the casing and forming with it at least two hydraulic accumulating chambers communicated with two driven hydraulic chambers of the cylindrical bore 2. However, this To the hydraulic percussion instrument, these disadvantages are inherent to another degree, which leads to a decrease in the performance and reliability of the tool. The purpose of the invention is to create a hydraulic percussion instrument with enhanced performance and reliability. The goal is achieved due to the fact that the axial cylindrical opening of the housing has an annular chamber of larger diameter with outlets for the liquid in the side wall. A drummer is equipped with a piston head placed in this chamber, dividing its space in the axial direction into two hydraulic driven chambers and cooperating with the outlets in it to selectively release fluid from the drive chambers. In this case, the piston head of the striker has axially located parts adjacent to its ends, which ensure the regulation of the flow rate of the fluid during its discharge from the drive chambers. In addition, the impactor piston has parts axially located relative to the piston head, which maintain the fluid pressure in the driven chambers. The torsion of the head of the striker has an axial length equal to the axial length, the outlet of the chamber, or a longer Fuse length of the outlet. In this case, each hydraulically actuated camera communicates with an individual. Noah. Hydraulic accumulating chamber through the inlet. The inlets of the driven hydraulic chambers are connected to a common supply channel and interact with the end portions of the piston for the selection of the sub-liquid in the ripi Siofly chambers “In FIG. 1 shows a percussion instrument in a perspective view, FIG. 2 the same, vertical section, on. FIG. 3 shows section A-A in FIG. 2 in FIG. 4 shows the piston head of a firing pin in FIG. 5 is a diagram of the relationship between the fluid pressure at the piston head and the position of the striker during its course. . The hydraulic impact tool contains a impact head 1 (see Fig. 1 coaxially connected to the front bow head 2. The disk-shaped elements, cops 3 and 4 are coaxially connected to the rear end of the impact head 1 and to the front end of the bow head 2, respectively. Fasteners, For example, several longitudinally extending rods 5 are rigidly joined together in these parts to form a single drilling device b, which is installed with possible translational movement on the feeding frame 7. The frame 7 is mounted on adjustments on any movable base, for example, on a frame with a caterpillar drive and with a hinge by an articulated boom (shown). The device 6 is driven by the working fluid supplied through the hoses. 8. A bow 2 (see Fig.2) has an annular body 9, having an elongated annular chuck 10 coaxially mounted therein rotatably with a p-helm of roller bearings 11. The chuck 10 includes
    784805; a plurality of circumferentially spaced teeth 12 for engaging with a drive gear (not shown J located inside housing 9. In cartridge 10, along with it, an elongated annular rear sleeve 13 and an annular drive element 14 adjoining the front sleeve 13 are fitted. The sleeve 13 and the drive element 14 are centered coaxially with an annular front sleeve 15 fixed in the inner peripheral part 16 of the element 3, for example by means of a nut 17, resulting in a shock bar 18 passing coaxially inside the cartridge 1Q and element 4, Anchored with the possibility of longitudinal sliding inside the sleeves 13 and 15. The intermediate part 19 of the shock, the rod 18 with the outside cut slots is in engagement with the corresponding slots on the inner peripheral part 20 of the drive element 14, which is permanently connected to the spline 21 with the sprint connection 10. Furthermore, the shock bar 18 is mounted with the possibility of axial rotation, for example, by means of a hydraulic motor 22. As indicated, the shock bar 18 has the possibility of axial sliding inside the cartridge 10. In its extreme In this position (see Fig. 2), determined by the number 1 of the corresponding end parts 23, 24 of the intermediate part 19 of the shock bar 18 and the sleeve 13, the rear end 25 of the shock bar 18 is located at the front end of the shock head 1 to receive blows from it .,. Impact head 1 (see fig. 2 ij 3) comprises a cylinder body 2 b, for example, a machined steel casting, and an elongated cylindrical shell 27, coaxially and rigidly enclosing the cylinder 26 along its entire length. The impacting head 1 has several chambers 28, which are made in the form of several annular cavities 29 arranged axially, extending radially inward from the outer periphery of the cylinder 26 so that the adjacent periphery of the shell 27 forms a radial outer wall of the chambers 28. The chambers 28 are separated radial partitions 31, each of which has an outer annular periphery, tightly adjacent to the inner periphery 30, the envelope 37 to prevent fluid communication between adjacent chambers 28. Shell 27 and the cylinder 26 are preferably communicated by compressing the fit, for example, initially by forming a press fit between them at ambient temperature. For assembly, shell. 27 is heated and cylinder 26
    cooled to form a gap in diameter between them. After assembly, the temperature of the shell 27 and the cylinder 26 is straightened to the ambient temperature, as a result, the diametrical gap between them is eliminated and a fluid-tight seal is obtained by post-burning without the aid of the known elastomer sealing elements of 1t.
    The cylinder 26 has an annular sleeve 32 held inside the stepped coaxial bore 33 and comprising a sleeve 34 and a buffer ring 35, a mounted coaxial inside the rear peripheral portion 36 of the sleeve 34 .. The inner periphery of the buffer ring 35 and the sleeve 34 form a through hole; 37, which houses the stepped cylindrical drummer 3
    In the opening 37, the front 39 and rear 40 bearing parts are located, in which the front 41 and rear 42 core parts of the striker 38 are installed with the possibility of sliding. In the intermediate part 43 of the hole is E7 of larger diameter, which is a ring chamber located between the bearing parts 39, 40, placed the stepped cylindrical head 44 of the striker 38. To drive the striker 38 near the front and rear ends of its head 44, the upper 45 and lower 46 drive chambers of variable pressure are formed. The drummer 38 interacts with the hole 37 to allow the passage of fluid under pressure or into the drive chambers 45, 46, or one of them, to self-excite the drummer 38.
    The disc-shaped element 4 with side rods 5 is tightly pressed against coaxially located bearing struts 47 and 48 formed by the front parts of the cylinder 26 and shell 27. Element 4 likewise interacts with the rear end 49 of the buffer ring 35, which has a front annular part 50 interacting in axial direction with an annular rear shoulder 51, made on the inner periphery of the sleeve 34, the sleeve 34 is installed inside the bore 33 by means of the respective axial stop parts 52 of the shoulder. As a consequence, the clamping forces of the side rods 5 serve to rigidly install the sleeve 32 inside the bore 33. The sleeve 34 and the buffer ring 35 are fixed fixed to rotation relative to each other and the cylinder body 26 by means of keys or shear pins (not shown) installed in the corresponding im keyways.
    1 In addition, the drilling device b contains flushing means 53. It contains a tube 54, reported
    ic are supply channels that run coaxially inside element 4, drummer 38 and impact bar 18, and. the opening 55 for the inlet of the washing liquid in the disc-shaped element 4.
    The drilling device 6 also has a means for supplying liquid, which actuates the hammer 38. The liquid inlet pipe 56 passes annually through the shell and is connected to conduit 57,
    0 which communicates an external source of fluid, for example a pump 58, and a chamber 28, which is a reservoir for a fluid, under the pressure supplied to supply the drive chambers
    five
    45.46 .. When moving fluid is supplied to the respective drive chambers 45, 46, the response reaction is created mainly by the chamber 28, as a result of which the shock head 1 is not directly dependent on the pump 58 to immediately trigger the fluid flow, and thus exclude . There are large deviations of pressure in the pipeline 57. When all the inlets in the chambers 45, 46 are blocked,
    5, the pump 58 recharges the chamber 28 to further open the inlet. The chamber 28 is communicated by means of a plurality of circumferentially arranged radial holes 59.
    0 with the lower annular groove 60. The radial holes 59 intersect with a plurality of axial channels 61 in the cylinder 26, which communicate through another plurality of radial holes
    5 62 with inlet groove
    63, whereby the fluid communication between the chamber 28 and the corresponding one by the inlet annular groove 60 (63) is kept constant.
    0 In a similar way, the annular chambers 28 are in constant fluid communication with the driving chambers.
    46.45 through a plurality of circumferentially radial holes
    64.65 to get the bottom and
    5, the upper batteries of the fluid energy for the purpose of storing and releasing the energy of the fluid under pressure, and the remaining chambers 28 communicate through similarly arranged radial
    0 holes 66, the outlet annular groove 67 extending radially outward from the intermediate portion 43 of the hole 37 between its ends along the axis. Volume of chambers 45, 46
    five
    and associated chambers 28 are changed by moving the impactor 38 to either chambers 45, 46, or one of them. The percentage change in volume is very small, for example, within 1-5%, meaning limited fluid compression. The limits of the percentage change in volume can vary depending on the particular type of fluid. To ensure proper fluid flow between the axial
    five
    channels 61 (see FIG. 3) around the circumference there are corresponding radial and apertures 64-66. The discharge pipe 68 communicates in the radial direction through the casing 27 with the discharge chamber 28 and has a pipe 69 attached to it through which the discharged liquid can flow in the liquid tank 70.
    Due to the fact that the impactor 38 (see Fig. 4) is symmetric about its mid-transverse plane P-P, only one axial half, top, of the impactor is described below.
    The lower half of the hammer is a mirror image of the upper half. The symbols, designated lower half, correspond to the lower parts of the upper half of the striker 38 below. The head 44 of the striker 38 contains a central, axially extending annular guide along juice 71, mounted slidably in the intermediate part 43 of the hole 37 and interacting with the outlet annular groove 67, the discharge or flow control is provided during the reciprocating motion of the striker 38. The conical guideline 72 is made with an end portion of a larger diameter and tapers from it along the axis of the striker 38 with a taper angle relative to its central longitudinal axis within 5-15 (preferably 10 °) to ensure a controlled passage of the discharged liquid nyteM to evenly increase its outflow as the outlet annular groove 67 opens. As a result, Ba3W (3 KH6cts) causes the occurrence of excessive fluid cavitation, which may occur as a result of an uncontrolled decrease in the pressure of the discharged liquid. In addition, the cone on guideline 72 facilitates the creation of a non-turbulent fluid flow under pressure when the drive chambers 45, 46 are released as the head 44 of the striker 38 moves into each chamber 45, 46 during its reciprocating motion, squeezing the tendency of the fluid in the chambers 45, 46 to inhibit the movement of the striker 38 in them.
    Along the axis, at some distance from the outer end, the guide along ska 72 has an annular guide for juice 73, which interacts with the annular cavity 74 to receive a liquid cushion in the event of excessive overrun of the striker during its reciprocating motion. Mevdatrah Nairavl ykh across the 72 and 73th thun. T hem of the talted part 74a, which can be of the same diameter depending on the
    The diameters of the guide portions 72 and 73. The juice guide 73 extends axially outward, with a final part close to the stem portion 41. In portion 41, a radial inlet groove 75 is provided to allow the passage of fluid or flow control during reciprocating The piston movements along with the inlet annular groove 63. The tail part of the groove 75 works mainly as an inlet valve seat in cooperation with the corresponding part of the boring. The shank portion 41 in the axial direction of the groove 75 interacts with the rest of the bore 39 to provide a sliding support of the striker 38 inside the hole 37. Since the striker 38 is symmetrical, the device 6 can be assembled forward with either end of the stripper 38 , resulting in increased service life. For
    The bearing parts 40 and 39 are made with axis lengths equal to the corresponding core parts 4
    42 blows 38.
    The drilling device 6 includes drainage means 76 (see figs, 2 and 3 used in conjunction with annular drying glands 77, covering parts 41, 42 of the striker 38 between the axial ends of each corresponding part 39, 40. Pass-pcs through the glands 77 in limited quantities the fluid gradually collects near the end parts of the striker 38 in the cavity 78, which must be ventilated in order to prevent fluid accumulation. Together with: each gland 77, an annular drain cavity 79 for receiving fluid is made of each The orifices flow out along the periphery of the tail portions 41, 42 of the respective chambers 45, 46. These fluid leaks are drained from each drain cavity 79 through one or more radial channels 80 into the cylinder 81 located along the cylinder. 26 Channel 81 communicates with the annular drain cavity 82 which includes at least a radially arranged lase 83. Cavity 82 is isolated from the adjacent cavity 78 by means of an axial stuffing box 84 located between the disk-shaped, element 3 and the buffer ring 35. At the bottom of element 3
    a drain pipe 85 is installed to communicate with the drain line 86 from the reservoir 70 to the cavity 82, as a result of which
     to drain fluid leaks. RadialCLEANING channel 80, co-communicating with the front drain ring; ng) (channel 79, incl. The B1 along the axis of the cobalt B7 cavity between the sleeve 34 n cylinder 26, where fluid can be collected to lubricate various parts of the device For example, a network of channels 88 (see Fig. 2) extends from annular cavity 87 through cylinder 26, body 9 and element 4. and serves to divert fluid leaks from cavity 87 to lubricate rotating relative to each other front end portions of cartridge 10 and disc-shaped element 4.
    In the pipelines 57, 69, a four-way open central valve 89 (see Fig. 2) is installed between the drilling device by the pump 58 and the reservoir 70 (see Fig. 2) to control the flow of the working fluid. The crane 89 is set selectively to position B (see RG, 2) for connecting the pump 58 to the inlet 56 and to the outlet 68 of the reservoir-70, or to position B to connect the pump 58 to the outlet 68 and the inlet 56 of the reservoir 70. The valve 89 also provides a third position D (optionally between positions B and C), in which the drop flow flows freely from the pump 58 to all parts of the crane 89 and back to the tank 70 to equalize the fluid pressure at the inlet and in the chambers 28. Position B provides a neutral or single Operating modes for removing air or blockages from a fluid in a drilling device 6.
    However, as the striker 38 reciprocates inside the opening 37, the upper and lower along the piston piston inlet grooves 75 alternately provide for communication of the corresponding inlet annular grooves 63, 60 with the corresponding chambers 45 and chambers 28, (hereinafter referred to as the upper the side and the bottom side of the impactor to affect the differential areas, formed by the difference in diameters between the guide 71 and the distant parts 41, 42. In a similar way, with reciprocating SG striker motion guide rib 71 alternately performs communication between the groove 67 and the upper and lower sides of the striker 38 for discharging fluid under The pressure of.
    The device 6 is of valveless type, in which the grooves 75 and the guide for the juice 71 of the impactor 38 interact with the corresponding annular grooves 63, 60 for transferring the liquid to and from the upper and lower sides} 38. creep 38 with GVO go. : The corresponding intake and exhaust ducts thus developed. provide control of the flow rate of the fluid in a constant range from the fully open position to the fully closed position, as noted with the constant-changing resistances R, -R to the flow in FIG. four.
    Thanks to the peripheral gaps
    o between the hammer 38 and the hole 37 near the corresponding inlet and outlet channels, the degree of fluid flow is kept uniform when the channels are closed such as
    5 marked with the symbol Ry.
    The ssshansirovannoe or equilibrium position of the striker, shown as the average position (.4), is determined for the impactor 38, when
    0, the upper and lower sides of the piston head 44 are subjected to equal and oppositely directed forces of the motive fluid. From the point of view of the indicated flow resistance, the equilibrium position of the impactor 38
    5 is defined as the position where the ratio R / Rij is equal to the ratio Ro, / R4 In other words, the ratio of the pressure drop at the inlet to the pressure drop at the outlet on the lower side; not the piston head 44 is the ratio of the pressure drop at the inlet to the pressure drop at exit on the top side. While maintaining these relationships for equilibrium
    5 the position of the impactor does not require the usual equality between any of the resistances R (-ND to flow. For example, suppose that RJ exceeds R-, and R4 exceeds R. the equilibrium position
    0 drummer. From this it follows that R + Nd is greater than R + R, and, consequently, a greater ratio of the total fluid flow from the inlet to the outlet will pass through the upper side. However, until drummer 38 passes
    5 E equilibrium position, when R / Rrj is equal, on each side of the piston head 44 will act, develop a net net effective pressure regardless of equal flow, and
    O drummer 38 will not press the fluid pressure up or down.
    The described ratio of the flow resistance does not depend on the particular dimensions, measures, or shape of the impactor 38 and
    5 Threat 32.
    权利要求:
    Claims (2)
    [1]
    An additional requirement is that fij is not equal to Rg. for equilibrium imposition, facilitates easy starting. In the initial period, the pump 58 delivers fluid with a full flow rate for neutral operation when the kpaH 89 is in the in position, as a result of which the fluid circulates freely from the pump 58 through valve 89 and back to tank 70 and, in addition, in the input and output cameras. 28 to completely fill all fluid channels and exert pressure on the fluid passing through the drilling device b. In order to initiate the reciprocating motion of the striker, the crane 89 is shifted from position B to position A and Sdl of passing the entire fluid flow through the device. In position A, one chamber 28 is under pressure from pump 58, and the other chamber 28 is discharged into reservoir 70, as a result of which drummer 38 will be forced to its neutral position by means of differential pressure at the inlet and outlet. As an example, suppose that first the drummer 38 is located in the upper position from the equilibrium position, with This the crane 89 is in the positions A. From this it follows that the resistances RI and R2 are greater (the windows are closed more completely), and the resistances R2 and Rj are smaller (the windows are open more fully than their value when finding nick 38 in equilibrium position. Accordingly, the RI / RO ratio will be greater than the ratio (the ratio of the total pressure drop at the inlet on the upper side exceeds the total pressure drop at the inlet on the bottom side), as a result of which, without resistance, the pressure component down to push the impactor in the direction of the stroke down to its equilibrium position. Similar reasoning applies if the impactor 38 is first below its equilibrium position when the ratio is less than Rj / R and the pressure set thus acts on the upper part of pushing the impactor 38 to its equilibrium position. In a case 13, when the striker 38 reaches its equal position, the pressure R / Rrj approaches equality, and the pure, without resistance, component of the fluid pressure acting on the piston head 44 approaches zero. So, if the impactor 38 goes over the equilibrium cBOfe from either side under the influence of the impulse from the component pressure of the fluid, then the opposite pressure component of the fluid acting on the impactor 38 in the opposite direction towards the equilibrium position will be created. Such a repetition of the cadmium transition of the striker 38 from the equilibrium position, either in the direction of its downward movement or in the direction of its upward movement, is the usual form of self-oscillating reciprocating movement of the striker. Thus, when the valve 89 is in position A, the striker 38 can immediately start moving back and forth. In this case, starting the device ends or stopping the striker at the equilibrium position may occur. If this happens, the device can be started by moving the crane 89 to position C to create pressure in the outlet chamber 28 and connect the inlet chamber 28 to the reservoir 70. Since the resistance R / j and R4 are not equal in the equilibrium position, as mentioned above (in this case, R is greater than R), the initial pressure of the fluid from chamber 28 will be created in the upper side of the piston head 44, thereby prompting drummer 3 8 move upward from the equilibrium position. When one chamber 28 is under pressure and the other chamber 28 is discharged, the ratio R -; / R / is equal to the ratio Rji / R since the equilibrium of the impactor is still maintained. However, in this case, the equilibrium is very unstable, in which the deviation of the striker 38 from it leads to the appearance of a pure, without resistance, component pressure of the fluid in the direction of this deviation, which increases with increasing deviation, pushing the striker farther from the equilibrium position. Accordingly, when the valve 89 is in position C, the initial push of pressure and the chamber 28 causes the hammer 38 to move upwards, as a result of which the ratio increases and the ratio Rti / R4 decreases due to IT on the upper side The net pressure component of the fluid that removes the hammer from the equilibrium position is contained. As the impactor 38 deviates from the equilibrium position, the upward pressure component of the fluid increases to bring it to the highest position, in which the ratio is much higher than the ratio. Accordingly, when the valve 89 is turned to position A, the large pressure component to act on the lower side, moving the striker 38 in the direction of the equilibrium position and further, as a result of which self-excitation is established, the reciprocating movement of the striker. After the launch, the drummer 38 will continue its self-excited return, but the forward movement along the cycle shown in FIG. 5. Drummer 38 begins its downward movement from the extreme upper position 90 (left ordinate of the communication scheme, phi1.5), in which the bottom side is fully open into the inlet chamber 2 and is under pressure close to the maximum inlet pressure, for example 17.5775 kg /cm. The stroke side of the piston piston upward is opened into the outlet chamber 28 and is provided by a reverse exhaust pressure, for example 14.0602 kg / cm, as indicated by 91. The outlet reverse pressure is maintained by various obstacles to the flow between the annular groove 67 and the reservoir 70. As As the striker 38 begins an accelerated motion in the direction of the blow (to the right in FIG. 5), the pressure on the downward stroke of the striker starts to fall along line 92 when the head is moving from the piston. 44 releases the chamber 46 with an increase in its volume. At the same time, the impactor reduces the volume of chamber 45, however, because the output remains open for the sides of the stroke of the impactor down during this cycle, part of the fluid pressure in chambers 45 and 28 does not increase significantly, but remains fairly constant, as marked by line 93. When the striker 38 reaches point 94 on the line -92 during its downward movement, the rear edge of the can 75 passes the leading edge of the annular groove 60 and the entrance to the direction of the striker's movement downwards closes (R increases significantly). Thereafter, a permanently running pump 58 charges the inlet chamber 28 to the maximum pressure through line 95 during the dead portion of the inlet cylinder while the striker continues to accelerate under the influence of a liquid pressure energy pulse stored on the side of the piston downward chambers 46 and 28. Due to this that the volume of chamber 46 continues to increase as the piston head 44 emerges from it, the pressure of the fluid in it and in the chamber 28 communicating with it continues to fall along line 96. At the same time, the fluid pressure on the stroke side of the impactor is up (chambers 45 and 28) begins to increase along line 97, while the volume of chamber 45 continues to decrease before entering the piston head 4.4, and the outlet flow area opened towards the upward stroke of the hammer decreases (resistance to flow R increases). At point 98 on line 9.6, the juice guide is centered on an annular groove 67 (R), and therefore, as the striker continues to move, the outlet to the chamber 28 is open in the direction of the striker downward and simultaneously closed in the direction of the piston downward of the piston head 44. Natural , The downstream pressure of the Fluid | of the firing pin downward quickly drops along line 99 to the back pressure, while the residual energy of the fluid in chambers 46 and 28 is discharged into chamber 28. The indicated back pressure upon discharge, although it is only a part maximum drive pressure continues to move the hammer in the direction of the impact. Also, almost simultaneously with the cycle point 98 or slightly beyond this point, the inlet cycle zone ends dead when the chamber 28 is open in the direction of the striker upwards to charge the energy of the input fluid pressure of the chambers 45 and 28 /, after which the pressure in the chamber 28 drops from its maximum value 100 and almost compares with pressure 101 on the upstream stroke side. As the volume of the chamber 45 continues to decrease and the filling of the upward stroke side of the striker continues with liquid, the fluid pressure on the upward stroke side of the striker rises along line 102 to its maximum value when the striker strikes rod 18, marked with 103 on the right ordinate of FIG. .five. The axial movement of the impactor 38 upon impact is not a fixed parameter and can vary within relatively wide limits, because as the impactor travels down the chamber 28 absorbs most of the energy created by the piston head 44 as it moves in, the chamber 45 and chrntoka; fluid under pressure from chamber 28, thereby reducing the net pressure resistance of the fluid to further move the hammer down. If this resistance is not reduced, then it will absorb a significant part of the kinetic energy of the striker before the impact and makes the drilling device much more sensitive to the location of the point of impact. The storage of fluid energy in chamber 28 while the striker moves down also increases the holding time or contact time between the piston by the impactor 38 and the rod 18 upon impact to more efficiently deliver the impact energy and, moreover, provides an initial supply of energy for accelerating the impactor upwards after the impact. As the cycle continues, the impactor bounces off rod 18 and begins to move with acceleration to its extreme upper position under the influence of fluid energy into chamber 28, simultaneously coming from chamber 28 through the open inlet in the direction of the stroke of the impactor. After the piston head 44 leaves the chamber 45 to increase its volume, the pressure in it drops along line 104 to point 105, after which the entrance in the direction of the stroke of the striker upwards closes. Almost simultaneously or immediately after point 106, the discharge chamber 28 opens on the side of the stroke of the striker up and closes on the side of the stroke of the striker down, and, accordingly, the pressure on the side of the stroke of the striker up sharply drops along line 107, while the residual energy of the fluid in chambers 45 and 28 is discharged. Chambers 46 and 28, in which pressure was gradually generated through line 108 to point 106 as the hammer went up, continued to be charged further along line 109 when piston head 44 enters chamber 46 through the dead part of the intake cycle. Also during the dead part of the cycle the inlet chamber 28 is re-pressurized by supplying fluid from pump 58 through 110 110 to the maximum inlet pressure at point 111. After the impactor reaches point 112 as it moves upwards, which is the end of the dead portion of the inlet cycle, the fluid inlet opens at downward to recharge it from chamber 28, the pressure in which drops along line 113 and is equalized with the pressure on the stroke side downwards, which continues to increase along line 114. Pressure on the stroke side upwards that remains open in the outlet chamber 28, continues to decrease along the line 107 to the back pressure of the release, when the impact of the nick 38 moves to the extreme upper position. Under the influence of the pressure of the fluid accumulated in chambers 28, 45, the movement of the impactor slows down to Stop its extreme upper position with the maximum inlet pressure that prevents further movement of the impactor up, as indicated by the position 90, and immediately accelerates in the direction of the next blow to start the next cycle. Claim 1. Hydraulic percussion instrument, including a body with an axial cylindrical bore, UdCryic, placed in it with the possibility of reciprocating movement to communicate blows to the working tool, the shank of which is located in this hole, shell, located around the body and forming with it at least two hydraulic accumulator chambers communicated with two driven hydraulic chambers of a cylindrical bore, characterized in that, in order to increase it, Kopityca's axial cylindrical bore has an annular chamber of larger diameter with outlets for liquid in the side wall, and the Drummer is equipped with a piston head placed in this chamber that divides its space in the axial direction into two hydraulic driven chambers and interacting with outlet holes in it for selective release of fluid from the drive chambers. 2. The tool of claim 1, wherein the piston head of the striker has axially located parts at its ends, which regulate the flow rate of the fluid during its discharge from the drive chambers. 3. The tool according to Claims 1 and 2, which is characterized by the fact that the piston of the striker has parts axially located relative to the piston head, which maintain the pressure of the fluid in the drive chambers. 4. A tool according to claims 1-3, characterized in that the piston head of the striker has an axial length equal to the axial length of the outlet of the chamber. 5. A tool according to any one of claims 1-3, characterized in that the piston head of the striker has an axial length greater than the axial length of the outlet of the chamber. 6. The tool according to w1-1-5, in which each driven hydraulic chamber communicates with an individual hydraulic accumulating chamber through the inlets. 7. A tool according to claims 1 to 6, characterized in that the inlets of the driving hydraulic chambers are connected to a common supply channel and interact with the face n of the piston to selectively supply fluid to the driving chambers. Sources of information taken into account in the examination 1. The author's certificate of the USSR 447506, cl. E 21 C 3/20, 1971.
    [2]
    2. USSR author's certificate №560978, cl. E 21 C 3/20, 1975. CI a / and
    类似技术:
    公开号 | 公开日 | 专利标题
    FI90582C|1994-02-25|Hydraulic submersible drilling machine
    US4283991A|1981-08-18|Percussion mechanism
    SU845796A3|1981-07-07|Shocking hydraulic device
    US4062411A|1977-12-13|Hydraulic percussion tool with impact blow and frequency control
    FI74898C|1988-04-11|Hydraulic percussion.
    US3887019A|1975-06-03|Hydraulic percussive implement
    US4070949A|1978-01-31|Hydraulic striking apparatus
    KR102337090B1|2021-12-08|Multi-accumulator arrangement for hydraulic percussion mechanism
    SE509682C2|1999-02-22|Cyclic and hydraulic actuator
    SU784805A3|1980-11-30|Hydraulic shocking tool
    US4343368A|1982-08-10|Idle stroke braking unit for an impact device
    US4290496A|1981-09-22|Combination impact and pressure liquid rock drill
    US4006665A|1977-02-08|Percussion tool
    US4020747A|1977-05-03|Hydraulically-operated devices
    US4282937A|1981-08-11|Hammer
    JP3393139B2|2003-04-07|Hydraulic shock motor
    US4370916A|1983-02-01|Percussive device
    US2684055A|1954-07-20|Rock-drill having an engine assembled therewith
    JP3588467B2|2004-11-10|Borehole drill
    SU1689605A1|1991-11-07|Pneumatic plunger
    SU1218095A2|1986-03-15|Pneumatic percussive mechanism
    SU848615A1|1981-07-23|Pneumatic percussive mechanism
    RU187066U1|2019-02-18|Submersible hammer
    US4653596A|1987-03-31|Percussive air tool
    RU2104148C1|1998-02-10|Hydraulic hammer
    同族专利:
    公开号 | 公开日
    IT1076743B|1985-04-27|
    DE2719002A1|1977-11-10|
    AU2438877A|1978-10-26|
    SE7704440L|1977-10-29|
    JPS52133001A|1977-11-08|
    GB1588525A|1981-04-23|
    ES458572A1|1978-10-16|
    BR7702614A|1978-02-28|
    FI771344A|1977-10-29|
    YU109877A|1983-01-21|
    FR2349747A1|1977-11-25|
    AU520326B2|1982-01-28|
    MX147859A|1983-01-25|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    FR1579334A|1968-09-06|1969-08-22|
    US3592109A|1969-03-05|1971-07-13|Chance Co Ab|Reciprocating fluid motor|
    US3701386A|1970-12-11|1972-10-31|Dresser Ind|Hydraulic drifter|
    GB1450972A|1974-06-11|1976-09-29|Klemm G|Percussive tool|
    FR2279962B1|1974-07-26|1978-06-09|Zahnradfabrik Friedrichshafen|
    US4026193A|1974-09-19|1977-05-31|Raymond International Inc.|Hydraulically driven hammer system|
    CA1071946A|1975-10-24|1980-02-19|George A. Hibbard|Rock drill|GB8606645D0|1986-03-18|1986-04-23|Dowty Mining Machinery Ltd|Rock drill assembly|
    SE535149C2|2010-08-31|2012-05-02|Atlas Copco Rock Drills Ab|Hydraulic percussion for use in rock or concrete cutting equipment|
    SE536289C2|2011-04-05|2013-08-06|Atlas Copco Rock Drills Ab|Hydraulic percussion for rock or concrete cutting equipment as well as drilling and breaking equipment|
    SE535757C2|2011-04-05|2012-12-11|Atlas Copco Rock Drills Ab|Device and method for rock and concrete machining|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    US68082276A| true| 1976-04-28|1976-04-28|
    US68082376A| true| 1976-04-28|1976-04-28|
    [返回顶部]