DE2400925A1 - IMPACT DEVICE - Google Patents

Description

9272-73 /Dr.G./tu
US Serial No.322.11ο
Piling date:
January 9,1973

RAPIDEX ₁ INC. ', Boxford, Massachusetts, V.St.A.

Slack device

The invention relates to a striking device with a striking body, which is used for the return and for the execution of the stroke is movable, with a work content to store potential energy during the return and for driving the impactor upon execution of the impact, with a device comprising a hydraulic chamber has to hydraulic the impactor by attacking Pressure can be attributed to a surface of the impact body, while a driver part is one of these surfaces opposite surface of the impactor in the chamber shields from pressure, with a device to the execution of the Trigger the impact by canceling or equalizing the return pressure acting on the impact body, whereby the impact body moves away from the driver text, as well as with a hydraulic device to the driver part for. Tripping of a new cycle to bring it back into contact with the impact body.

will
Such arrangements / for breaking up pavement,

for forging, for sinking piles and piles

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learning, used for bump keys and so on, in particular such arrangements are made by hydraulic work equipment driven under high pressure.

There are striking devices known with which one successive Can perform impacts in different directions and positions in straight or rotary motion. The striking devices, to which the present invention relates, work with elastic or expansive drive or working media, for example with an enclosed volume of compressed air, or a spring that acts on the impactor ^ to drive him. Hydraulic equalization or counter pressures that are controlled by a driver part, are used to hit the impact body during the work cycle to return to the starting position and .the developing drive medium before the next one is triggered To compress the shock again. It is known to return the driver part with the impact body and. automatic • Use release devices. In one of these known devices, the hydraulic reversing working medium is omitted, when the impactor reaches the reverse position, thereby compressing the expanding drive means is suddenly removed.

Although these tekannten arrangements work well, they exist but for large and expensive items and have regard to the ^s chlaggeschwindigkeit and training unwanted restrictions and other difficulties.

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■ - 3 -

^It is an object of the present invention to create an arrangement in which the disadvantages mentioned of known arrangements do not occur or are reduced.

In an arrangement of the type mentioned, this object is achieved in that the driver part has a The sealing area protrudes from the chamber and an auxiliary hydraulic chamber is provided to apply pressure to a surface of the To let the driver part act outside the main chamber, so that the driver part during the movement to bring it back into contact is gradually pressed into the main chamber, the driver part being the hydraulic working medium gradually displaced from the main chamber as the re-contacting movement progresses.

Further preferred embodiments are set out in the subclaims described.

In connection with the advantages of the invention, it should be noted that that certain, already known hydraulic impact devices with a flow of the fluid a very uneven Have flow, especially in the outlet line, where the flow rate between zero and can fluctuate twice or more than twice the mean value. Such arrangements use an expansive one Working medium (for example compressed gas) to a driver part or a pipe socket in the lower layer to be brought back in order to be able to carry out another work cycle. According to the present invention, it is found that such arrangements unnecessarily limit the effectiveness of such a device (the energy, through the elastic part bsi the movement of the driver pipe socket expended is lost) and the case

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and
speed / thus also the beat frequency remains low. A gas chamber, which is used as an energy storage part, must remain under the pressure of the hydraulic working medium in such arrangements.

In contrast, it is possible with an arrangement according to the present invention, both constant flow rates in the inlet as well as in the outlet lines to reach at any time · Their pipe socket or valve unit, the is driven in both directions, allows a higher work rate. One can use gas or other energy storage Use working media at pressures that are higher than the pressure of the hydraulic working medium, whereby only one smaller energy storage device or chamber is required.

The invention is explained in more detail with reference to the drawings, for example. Show it"

Figure 1 shows a cross section of a preferred embodiment of the invention,

Figures 2 a - d the same cross-sections at different times within the work cycle,

Figure 3 shows the same cross section for the special case a piston override,

Figure 4 is a partial view of another embodiment of the upper part of the unit according to FIG. 1.

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The one in Pig. The arrangement shown in FIG. 1 has a housing 11, a piston 10 and a pipe socket 12. As can be seen from the illustration, the piston is usually rod-shaped and has a uniform diameter with the exception of a widening 10 a in the middle. A relatively thin-walled tube 13 is attached to the housing 11 and the inner surface of this tube 13 forms a sliding seal with the upper part of the piston 10. In the chamber 14, which is formed by the tube 13t, the housing 11 and the upper surface of the piston 10, gas is contained. The gas inlet valve 15 serves to let gas into the chamber lk at time intervals in order to compensate for leakage losses in the chamber l4. The movable pipe socket 12 forms a sliding seal with the outer surface of the tube 13 and the inner surface of the housing 11 The pipe socket 12 is widened outwards at its lower end 12 a and is shaped in such a way that it rests sealingly on the piston widening at point l6. The pipe socket 12 contains a number of inner, longitudinally extending bores 17 which are radially connected via the short bores 17 a with the outer surface of the pipe socket 12 at point l8. A number of outer, short, axially extending slots 19 are attached to the pipe socket 12 in such a position that 'they are not connected to the bores 17. The piston 10, the piston enlargement 10 a, the. The pipe socket 12 and the pipe 13 define an annular fluid volume 20.

The housing 11 has an upper bore 11 a, which is designed such that it with the pipe socket 12 a Forms sliding seal. Furthermore, a second, next deeper bore 11 b is provided, which is an enlarged Has inner diameter, and does not form a seal with any of the moving parts. A third, next lower

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Bore 11 c with a short axial extension is in turn designed so that it forms a sliding seal with the pipe socket 12 forms, and with the outer wall of the pipe socket and the upper part of the housing 11 an annular volume 22 sets.

Under the bore 11 c, the housing 11 has a bore 11 e, the inner diameter of which is greater than that of the the aforementioned bores and which form an area in which the widening 10 a of the piston 10 and the outwardly widened end 12 a of the pipe socket 12 in the axial Direction is freely movable, with a sufficiently large space S to displace the fluid around these parts provided when these parts move. The lowest The outer bore 11 f of the housing 11 forms a sliding seal with the piston 10.

The housing includes a lower opening 23, which with the larger lower housing cavity 23 '' in communication, an outlet opening 24 which communicates with the cavity 22 and an upper opening 25, which is connected to the cavity 25 * ', that is, it is in communication with the cavity above the pipe socket 12. The cavity l4 is under a certain pressure with Gas filled. With the exception of leaky texts, this process is not repeated.

In Pig · 2a, the unit described above is connected to an ordinary two-position switch valve (26). This switching valve 26 contains an inner, reciprocating part or a slide 27 which is urged upwards by springs 28. The valve 26 is connected to a positive displacement pump 29 with a constant flow rate via the line 30 and via the line 31 "ax a (not shown)

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set) return tank connected. All opposite ends of the valve slide 27 are pressurized by these two lines via lines 30 'and 31'. The valve is connected via the line 23 ′ to the opening 23 and the cavity 23, and via the line 25 ′ to the opening 25 and the cavity 25 ″ of the striking device. The outlet opening 24 is connected via the line 24 'to the line 31 j which leads to the return tank.

In the description of the operation of this arrangement one starts from the position, as it is shown in Fig _# 2a, and also as shown in Fig. 1, The fluid flows from the pump into the cavity 23 " pipe socket 12 and the piston 10 has a lower pressure which is from the cavity 23 "at point l6 (see Fig. ^F ig. 1) sealed, and the volume is on the ■ bores 17, 17 a, l8, further through the cavity 22 , the opening 24 and the line 24 · diverted to the return tank. The volume 25 ″ is also diverted to the return tank. The outer diameter of the ** _aU p-shaped body from the pipe socket 12 is smaller than the diameter of the seal at point 16. In this way, a resultant downward force arises which acts on the upper surface of the outwardly bent part 12 a and the pipe socket 12 keeps in connection with the piston 10, as indicated by the parts 32 in FIG. 2 a. By flowing the fluid through the conduit 23 'into the cavity 23 "under high pressure, the combination of pipe socket and piston is pushed upwards as a unit, and fluid is diverted from the cavity 25" and from the annular cavity 20. The same high pressure of the pump fluid (the pressure is determined by the resistance of the gas pressure in the cavity l4 and the corresponding piston areas). acts via the line 30 'on the valve 26, whereby the valve 26 in the

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lower position shown in Fig. 2a is held, with simultaneous encounter of the spring 28. The upward movement of the piston 10 continues until the position shown in Figure 2b is reached. In this position, the slots 19 cause the seal at the lower part of the cavity 22 to "short-circuit", allowing the fluid to flow from the main cavity 23 ″ into the cavity 22 and then into the cavity 20 and via the line 2k ' . In this way, the pressure in the cavity 23 'is reduced and the pressure in the cavity 20 is increased until the force acting on the piston enlargement 10 a is no longer sufficient to hold the piston 10 against the gas pressure in the cavity l4, regardless that the pipe socket 12 continues to move upwards as a result of the differential pressure applied to it, because the fluid continues to flow into the cavity 23 ″. The seal at point l6 is therefore canceled and the differential pressure occurring over the widening 10 a is also completely canceled. In this way, the piston 10 is "notched" and moves rapidly downward under the influence of the gas pressure in the cavity Ik , without displacing the hydraulic working medium from the cavity 23 ', because the two ends of the piston have the same diameter. Once the seal 16 is released, the pressures in the cavities 23 ″ and 25 ″ tend to equalize over the same surface ends of the pipe socket 12. In this way the pressure in the lines 30 and 31 becomes equal, which corresponds to the outlet pressure. The pressure in the lines 30 'and 31 becomes the same, so that the valve slide 27 switches over into the position shown in FIG. 2b due to the spring 28. ^{As shown in Fig. 2c,} fluid flows into the hollow space 25 and presses the pipe socket 12 downwards (the piston 10 has already moved quickly downwards and performed the blow),

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The downward movement of the pipe socket 12 pushes fluid out of the cavity 23 ″ via the line 23 ′ (some fluid is also exit via the bores 17 and the line 24 '). The outflow via the line 31 is compared to the inflow via the Line 30 the same · Because the front surface of the pipe socket 12 is smaller than the effective area during the upward movement of the piston in this embodiment (through the front surface of the pipes 13), the downward speed of the pipe socket becomes 12 can be greater than the upward when using the same flow rate in the two different phases speed of the piston-pipe socket unit · The Prints in the cavities 23 "and 25" are made during the Downward movement of the pipe socket 12 be approximately the same, and the valve 26 is during the entire downward movement in the Remain position as shown in Fig. 2c.

If the pipe socket 12 rests on the piston 10 during the downward movement, as shown in FIG. Holding power of the whole unit in firm connection with the rock or rock). Fluid can no longer get into the cavity 25 ″, and there is no space otherwise where the fluid can flow. it will flow via the line 30 ', whereby a pressure is built up which is sufficient to move the valve slide 27 and to depress the spring 28. In this way, the pipe socket 12 sits firmly on the piston 10 and seals the cavity 20 at point 16, the pressure in the cavity 20 returning to lower values. By switching the valve 26 of FIG. 2 d then fluid flows into the cavity 23 ^LF, where as a result of by-residual gas pressure in the cavity lk existing resistance to the up-

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Local movement of the piston and pipe socket occurs immediately relatively high pressure forms in the cavity 23 ″, whereby the Valve 26 is held in the position as this' for the upward movement was shown. Then a new cycle begins.

3 shows a particular embodiment of the present invention. When the drilling or hot Elan set 50 is dropped on the piston end, or has been removed, and when the piston due to its outlet and the actual end point of the downward movement addition downwards a position shown in FIG. 3 assumes, ^the piston by a mechanical Anhaltevorri is -chtung (with rebound effect) stopped, as shown schematically with the reference symbol kO . In most applications it is desirable to prevent the pendulum movement of the piston when such a process occurs. This can be done, as shown, in that the upper part of the pipe socket 12 comes to lie under the upper part (4l) of the cavity 22 before the pipe socket 12 moves down enough to create a seal with the at point l6 now depressed piston can arise. The fluid flowing in at 25 'is now at the outlet opening 24 ^! , and also through the bores 17> the cavity 20, the open seal l6, the cavity 23 ^fl and the line 23 'flow out. In this way, no pressure can be built up in the cavity 25 and the tube 26 will not switch over. To start work again, the drill or chisel attachment 50 must be pushed back enough on the piston (ie, relatively, the housing is brought further down) to obtain a seal at point 16 and at point kl to close the gap. Thereafter, a pressure is built up in the cavity 25 ″ and the tube 26 switches over, as a result of which a new cycle begins.

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In an embodiment according to FIG. 4 has a uniform Housing casting 11 ·, which contains the bores 11 a, 11 b, etc., an uppermost bore 11 g, the is above the other bores and has a smaller diameter than the bore 11 a. Am part of the Piston designed with the same diameter protrudes all the way through the pipe socket 12 and stands during the entire Working process with the bore 11 g in sealing contact, whereby a chamber l4 for compressed gas is formed will. With this construction it is not necessary to use the pipe socket or the tube 13 according to FIG. 1.

The dashed lines of Fig. K represent an automatic table filling arrangement, which is used with advantage when the cavity l4 is designed to receive a hydraulic working medium, whereby a hydraulic suspension for driving the impact part is obtained. For filling or for refilling necessary due to losses, fluid is supplied from the pump (line 30) through the check valve lk ^{1 via the upper, dashed line.} The lower, dashed line is used for discharge. This outlet port is located just below the top edge of the piston when the piston is in its normal impact position. This causes the fluid in the cavity tk to flow out when the piston is listening back from an abnormally low position (as shown in FIG. 3), thereby determining the maximum amount of the hydraulic working medium which is trapped in the cavity lk. In this way it is avoided that too great a pressure builds up in the cavity lk during operation. The arrangement according to Fig%., In which the cavity ik is formed through the housing, may be formed very contact and stable and is therefore suitable for prints, which in conjunction with hydraulic working media as a drive

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means for "the impactor are used.

Instead of these embodiments, for example, a radially buffering, separately manufactured solid tube 13 could be used; Instead of compressed gas, another compressible material or another mechanism for acting on the piston could also be used; a hydraulic working medium, as indicated above, is also suitable for this purpose. The piston ends could be configured in various ways to allow for the drainage of the displaced fluids. The entire structure with up and down or back and forth movement could also be designed in the form of a rotary arrangement instead of a linear arrangement. It can also be provided that all of the fluid from the chamber 23 '* via the bores 17 and Opening 2k exits; In addition, there are many other possibilities for designing an arrangement according to the present invention in detail without exceeding the scope and concept of the present invention.

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Claims (1)

Impact device with an impact body that is movable for the return and for the execution of the blow, with a work content for storing potential energy walerend of the return and for driving the impact body when executing the blow, with a device that has a hydraulic chamber around the Impact body returned by applying hydraulic pressure to a surface of the impact body, while a driver part shields a surface of the impact body in the chamber opposite this surface from the pressure, with a device to trigger the execution of the impact by canceling or equalizing the acting return pressure on the impact body, wherein the impact body moves away from the driver part, and with a hydraulic device to bring the driver part back into contact with the impact body to trigger a new cycle, characterized in that the driver part (12) has a sealing area ( 11 c) protrudes from the chamber (23 ¹¹ ) and a hydraulic auxiliary chamber Ϊ25 ¹ ') is provided to allow pressure to act on a surface of the driver part outside the main chamber (23 *'), so that the driver part (12) during the Movement for bringing back into contact is gradually pushed into the main chamber (23 * '), the driver part (12) gradually displacing the hydraulic working medium from the main chamber (23'') to the extent that the movement for re-contacting. progresses. 409829/0816 2) Impact device according to. Claim 1, characterized in that g e flag lehne t that during the return process a region (20) with low pressure is formed between the end of the driver part (12) and the impact body (10) is, and means are provided to the driver part (12) a high hydraulic pressure in Direction of contacting, whereby during of the return process a pressure-shielding connection of the driver part (12) is maintained over the impact body (10). 3) Impact body according to claim 2, characterized thereby that means are provided to reduce the pressure in the hammer (23 ") on the driver part (12) to maintain this connection. k) ^{Impact device} according to claim 3 "dacl urc hg _e _ indicates that the cross-section of the driver part (12) at the point (lic) at which it leaves the chamber (23") is smaller than the cross-section through the line (l6) is defined, on which the driver part (12) is in connection with the impact body (10), the area of the driver part (12), which corresponds to the difference between the said cross-sections, the pressure in the chamber (23 ") is exposed, so that a juice (line 32) occurs, which presses the driver part (12) against the impactor (l0). 409829/0816 2A00925 5) Impact device according to at least one of claims 1 to k _t, characterized in that the driver part (12) consists of a cylindrical body which is concentric to the inner end of the impact body (10) and surrounds it, the impact body (10) has a widened part (10 a) outside of the driver part (12), whereby a surface is formed on which the pressure for the return line acts, and wherein the corresponding end of the driver part (12) has a circular area (at l6) on which the driver part (12) is connected to the widened area of the impact body (10), whereby the passage of the fluid in the chamber (23 * ') around the widened area of the driver part (12) during the return does not hinder the course will. 6) impact device according to at least one of claims 1 to 5, characterized in that that the corresponding end of the driver part (12) is widened, the contact line to the impactor (10) is larger in diameter than the outer diameter of the cylinder body 7) impact device according to claim 5 or 6, characterized g e k e η nz e i chne t that the driver part (12) surrounds a chamber (l4) with compressed fluid, which represents the energy storage device the driver part (12) being separated from this chamber by a tubular wall (13) is, wherein the hydraulic auxiliary chamber (25 ") a Has a ring shape, the inner radius of which is limited by the tube wall (13) 409829/0816 8) Impact device according to at least one of claims 5 or 6, characterized in that the driver (12) is directly connected to the inner end of the impact body (10) in sliding connection, the impact body (10) beyond the driver (12) in the chamber ( lk ) protrudes with a compressed fluid, which represents the energy accumulation device, and wherein the hydraulic auxiliary chamber (25 ″) is annular, and surrounds the impact body (10), and the inner radius of the chamber through the impact body (10) is limited (see Figure k ). 9) impact device according to at least one of the preceding claims, characterized shows that the part of the driver (12) to which the hydraulic pressure (at 25 '') is applied and the part of the driver (12) that goes into the hydraulic main chamber (at the sealing area 11c) occurs, has the same cross-section, with equal amounts of the hydraulic working medium are introduced and displaced during the movement of the driver (12). ^{10) Impact device} according to at least one of the preceding claims, characterized in that flow openings (23, 25) are provided to supply ^{the hydraulic working medium to the main chamber (23 lf) and to divert it from the auxiliary chamber (25 1} '), whereby the impact body ( 10) and the driver (12) are moved together during the return process, and around TT then divert the hydraulic working medium from the aup chamber (23 '') and transfer it to the auxiliary chamber 409829/0816 (25 ^11. ) To initiate, whereby the driver part (12) is moved towards the impact body (10) in order to re-establish a connection after the blow has been executed. 11) impact device according to claim 10, characterized in that one on the. Fluid pressure in the impact device responding valve (26) acts in such a way that the hydraulic working medium .during the return process is directed by a pump to the main chamber (23 ") and then to the auxiliary chamber (25 ¹¹ ). 12) impact device according to claim 11, characterized characterized in that the valve (26) acts such that the auxiliary chamber (25 * ') during the Return process and then 'the main chamber (23' ') is emptied. 13) impact device according to at least one of the preceding claims, characterized marked e i c hn et that the combined movement of the impact body (10) and the driver (12) on inner end of the return stroke causes the fluid channel arrangement to change in a manner known per se, wherein the fluid pressure increases over the area of the impact body (10) which is shielded from the pressure, whereby the execution of the blow is triggered. 409829/0816 Impact device according to claim 13, characterized characterized in that the combined movement opens a channel (19) creating pressure from the chamber (23 ··) to the shielded surface to be led. 15) Impact device according to claim 13 or 14, characterized in that a valve, which depends on the pressure effects generated by changes in the channel directions, acts in such a way that the main chamber (23 ') is emptied in order to reduce pressure in the auxiliary chamber (25 " ), which means that you can take away:
is moved. TT the driver part (12) in the main chamber (23 '') 16) Impact device according to at least one of the claims 13 to 15, characterized in that the increase in the fluid pressure in the area of shielded surface acts at the same time in such a way that the driver part (12) from the impact body (10) is pushed away and that it is allowed that the striking movement can begin, with the combined Movement is used to prevent the main chamber pressure from reaching the previously shielded surface of the impactor (10) to enlarge. 17) Impact device according to one of the preceding claims, characterized in that a trigger is provided which causes both that the impact body driven by the energy storage arrangement (10) is triggered, and that the movement of the driver part (10) to again -in-contact is triggered, the trigger having an opening of the main chamber (23 ″) which 409829/0816 is opened by the impact body (10), and the driver part (12) comes into the return position _{18) Impact} device according to claim 17, characterized in that a valve is provided which is held in a first position by the pressure in the main chamber (23 ''), the valve causing the fluid to enter the main chamber (23 ¹¹ ) can flow back and fluid flows out of the auxiliary chamber (25 ¹¹ ), and wherein the opening by overpressure or counter pressure in the _main chamber causes the valve to be brought into a second position to increase hydraulic pressure in the auxiliary chamber (25 '') to put on. 19) impact device according to claim l8 ^! , characterized in that the valve (26) works in the second position in such a way that the pressure of the auxiliary chamber (25 * ') is applied to the valve (26) when a pressure is formed in the chamber associated with the driver part (12) is in communication, which reaches the impactor (10), the pressure acting in such a way that it switches the valve (26) into the first position, 20) Impact device according to at least one of the preceding claims, characterized in that a housing (11) forms the following devices: the main chamber (23) into which the impact body (10) and one end of the driver part (12) protrude, and with a first hydraulic line (23) an auxiliary chamber (25 ''), i is connected to * ¹ freili.egt of an oppositely directed surface of the driver (12), and with a second hydraulic line (25). connected to the driver part (12) 409829/081 6 To drive, a third chamber (22), which lies between the main and auxiliary chambers (23 ''> 25 ^f '), and is normally sealed off from them, the third chamber (22) with a third liydraulisehen line (24) to Discharge is connected, a passage opening (17 j l8) which extends from the third chamber (22) into the space (20) between the end of the driver part (12) and a widened area (10 a) of the impactor (10), and a passage opening (19) on the outer surface of the driver part (12), which is arranged so that the main chamber (23 ") is in communication with the third chamber (22) when the driver part (12) is in the return position 21) Impact device according to at least one of the preceding claims, characterized by geken nz eich net, that the impact body (10) has a linear piston (10), with a housing, which the lower position of the impact body (10) in the absence of a workpiece in the position in which the impact was received is determined, wherein the driver part (12) and the housing are formed in relation to one another in such a way that the pressure is released from the auxiliary chamber (25 ''), before the driver part (12) reaches the impact body (10) located in the lowest position, whereby it is avoided that the driver part (12) reaches the position in which the opposing forces act on the piston can attack. 409829/081 6 Empty soap