EP0843760A1 - Ramme - Google Patents
RammeInfo
- Publication number
- EP0843760A1 EP0843760A1 EP96929212A EP96929212A EP0843760A1 EP 0843760 A1 EP0843760 A1 EP 0843760A1 EP 96929212 A EP96929212 A EP 96929212A EP 96929212 A EP96929212 A EP 96929212A EP 0843760 A1 EP0843760 A1 EP 0843760A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- compressed air
- ram according
- pressure
- cylinder
- working
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
- E02D7/00—Methods or apparatus for placing sheet pile bulkheads, piles, mouldpipes, or other moulds
- E02D7/26—Placing by using several means simultaneously
Definitions
- the invention relates to a ram according to the preamble of claim 1.
- the working gas supply device has means for supplying fuel and air to the working space. This means that an ignitable mixture is generated in the work area, which is ignited when the percussion piston falls.
- the stroke of the percussion piston can be adjusted via the amount of fuel injected.
- the blows struck by the hammer on an object to be driven into the ground are hard overall.
- the basic structure of the diesel rams and the hydraulic rams are very different. If you want to have both the advantages of hard ramming and the advantages of soft ramming at the same construction site, you have to provide both types of ramming. This means a considerable effort.
- the present invention is intended to develop a ram in accordance with the preamble of claim 1 in such a way that its mode of operation can be switched between hard and soft ramming.
- the ram according to the invention can optionally be supplied by one of at least two working gas supply devices with pressurized working gas, which lifts the percussion piston in the cylinder under expansion.
- a working gas supply device has a simple structure compared to a ram, so that considerable savings are obtained with the invention compared to the simultaneous provision of two different ram types. It is also possible to switch from one operating mode to the other during operation and when driving in the same pile or other pile material. In this way, one can easily take into account the different properties of the subsurface at different depths without retrofitting the ram.
- the working mode of the ram set when it is activated is a particularly soft and gentle ramming.
- Such a working gas supply device requires additional provision on a diesel ram requires only a few and inexpensive measures.
- a compressor required to feed the compressed air reservoir is usually found anyway on construction places.
- the percussion piston is first accelerated out of the rest position by opening a servo valve assigned to a lower connection of the working space and then the main quantity of the compressed air contained in the compressed air store is acted upon by opening a further servo valve. This is advantageous in terms of optimal lifting of the percussion piston.
- the desired synchronization of the two servo valves is obtained in a simple manner, via which compressed air is supplied to the ram at axially spaced locations of the cylinder.
- Air flowing out associated with the servo valve is released into the ambient atmosphere, at the same time ensuring that no gas under pressure flows back from the working space of the ram to the servo valve.
- an operating mode "hard ramming according to the diesel principle” can optionally be set, in which the fuel is injected into a fuel trough which is formed in the top of the striking piece.
- a mode of operation “soft ramming according to the diesel principle”, in which the high-pressure fuel injection device that puts atomized fuel under high pressure into the work area.
- the ram shown in the drawing has a cylinder 10, in the lower end of which an impact piece 12 is tightly displaceable. This has an upper piston section 14, in the upper end face of which a fuel trough 16 is formed. A central cylindrical intermediate portion 18 of the striker
- the intermediate section 18 carries a plate-like striking section 24 with a convexly curved lower end face.
- a percussion piston 26 is guided in the upper section of the cylinder 10 and has a lower piston section 28 and an upper piston section 30 as well as a middle piston section 32 with a somewhat reduced diameter.
- the lower end face of the piston section 28 carries a flat elevation 34 which can engage in the fuel trough 16.
- the cylinder 10 is provided with a working slot 36. forms over which the ram sucks in air or emits combustion gases in diesel operation.
- two injection units designated in total by 38 or 40 and only shown schematically, are inserted into the cylinder wall. Each of these injection units has an actuating lever 42 or 44 which cooperates with the peripheral surface of the percussion piston 26.
- Nozzles of the injection units 38, 40 not shown in detail, emit a fuel jet 46 or a fuel mist 48.
- the fuel jet 46 is provided by the injection unit 38 under low pressure and is guided so that it gets into the fuel well 16. When the percussion piston 26 falls down, the fuel in the fuel trough is then atomized into the air heated during the compression.
- the fuel mist 48 is emitted from the injection unit 40 under high pressure and is led directly into the compressed hot air.
- high-pressure injection the combustion starts earlier with respect to the bottom dead center of the percussion piston than with low-pressure injection. This results in a softer stroke exerted by the striker 26 on the striker 12.
- low-pressure injection the mixture is ignited only after the impact piston 26 has hit the impact piece 12 hard.
- the injection units 38 and 40 are shown at axially spaced locations of the cylinder 10 for the sake of clarity. It goes without saying that in practice they can also be offset in the circumferential direction (with the same axial position) or can also be offset in the axial direction and circumferential direction. It goes without saying Furthermore, the injection units can also consist of spatially separate pump units and nozzle units, in which case one pump unit can also supply a plurality of nozzle units offset in the circumferential direction and / or in the axial direction.
- the injection units 38, 40 are connected to the outlet of a fuel pump 54 via solenoid valves 50, 52.
- the latter draws diesel fuel from a storage tank 56.
- the two injection units 38, 40 can optionally be activated by controlling the one of the solenoid valves 50, 52 assigned to them. This is optionally done by a control circuit 58 with a mode selector switch 60.
- the control circuit 58 outputs a further activation signal "a" at a third output terminal, which is used to set compressed air operation of the ram, as will now be described in more detail below.
- a connecting part 64 which has a plurality of connecting channels 66, is connected to the cylinder 10 at a lower section of the working space 62, which is delimited by the inner cylinder wall, the striking piece 12 and the striking piston 26. These lead into the interior of a large compressed air reservoir 68.
- the end face of the connecting part 64 located in the compressed air reservoir 68 contains control openings formed by the ends of the connecting channels 66, which cooperate with the end face of a plate-shaped slide 70 located on the left in FIG.
- the slide 70 is connected to the piston rod 72 of an actuating Motors 74 connected, which is placed on the top of an end plate 76 of the compressed air reservoir 68.
- a piston 78 is displaceable in its cylinder bore and is biased into the lower end position by a spring 80.
- the working space of the servomotor 74 which is delimited by the underside of the piston is connected to the outlet of a servo tile 86 via two adjustable throttles 82, 84 connected in series.
- a check valve 88 which opens in the direction of the servomotor is connected via the throttle 82, while the throttle 84 is bridged by a check valve 90 which blocks in the direction of the servomotor.
- the throttle 84 throttles the working fluid supplied to the servomotor 74, the throttle 82 the working fluid flowing out of the servomotor 74 when the pressure is released, and by adjusting the throttle 84 the opening speed of the slide 70 can be adjusted by adjusting the throttle 82 Set the closing speed.
- a servomotor 94 of the servo valve 86 can be connected to the interior of the compressed air reservoir 68 via a 2/2 solenoid valve 96, specifically at a point remote from the connection point of the line 93, so that the pressurization of the servomotor 94 is independent of dynamic ones Effects at the mouth of line 93 takes place.
- the solenoid valve 96 is actuated by the activation signal "a".
- the servomotor 94 attempts to set the working position of the servo valve 86.
- a further servo motor 98 of the servo valve 86 acts in the opposite direction and also a biasing spring 100 connected in parallel to it.
- the servomotor 98 is connected via an adjustable pressure regulator 102 to a feed line 104, into which a compressor 106 via a check valve 108 promotes and which is connected via a further line 110 to the compressed air reservoir 68.
- the working connection of the servo valve 86 is also connected via a working line 112, which contains a check valve 114 opening towards the cylinder 10, to a connection opening 116 of the cylinder, which communicates with the lowermost section of the working chamber 26.
- the percussion piston 26 sits on the percussion piece 12.
- the compressor 106 continuously conveys air into the compressed air store 68.
- the servomotor 98 which has a small cross section, and the biasing spring 100 are exerted on the slide of the servo valve 86 Force greater than the force generated by the actuator 94.
- the servo valve 86 thus initially remains in the idle state shown in FIG.
- the force provided by the servomotor 94 is greater than the combined force of the servomotor 98 and the biasing spring 100, and the servo valve 86 is switched to its working position.
- the lower compressed air connection opening 116 of the cylinder 10 is now connected to the interior of the compressed air reservoir 68 via the now opening check valve 114 and the servo valve 86, and the impact piston 26 is raised by a first distance by pressurized air, the cylinder-side ends the connection channels 66 are now released.
- the period of time that has elapsed up to this point corresponds to the period of time that the pressure present at the outlet of the servo valve 86 needs to lift the piston 78 against the force of the spring 80 via the throttle 84 and the check valve 88.
- the compressed air contained in the compressed air accumulator 68 can now suddenly be emptied into the working space of the cylinder 10, as a result of which the percussion piston 26 is thrown up.
- the distance by which the percussion piston 26 is raised obviously depends on the pressure prevailing in the pressure accumulator 68, the latter in turn depending on the switching pressure of the servo valve 86. This can be set via the adjustable pressure regulator 102.
- the servo valve 86 is moved back into the rest position shown in the drawing under the force of the servo motor 98 and the biasing spring 100.
- the compressed air located under the piston 78 can then flow to the environment via the throttle 82 and the check valve 90 be dismantled so that the slide 70 closes the connecting channels 66 again.
- the selector switch 60 can then be moved into the middle working position, in which soft ramming takes place according to the diesel principle by opening the solenoid valve 52. Now a fuel mist 48 is injected into the working space of the cylinder each time the percussion piston 26 approaches the striking piece 12. The ignition of the mixture produced in this way takes place shortly after the bottom dead center of the percussion piston 26. The percussion piston 26 is raised again by the ignition of the mixture, and the combustion gases flow out via the working slot 36.
- the percussion piston 26 sucks in fresh air via the working slot 36, and when the percussion piston falls downwards, the air in the cylinder is compressed by the percussion piston 26 after passing through the working slot.
- the percussion piston 26 then actuates the injection unit 38, and the cycle described above begins again.
- the injection unit 40 is supplied with fuel instead of the injection unit 38, since the solenoid valve 50 is now opened.
- the diesel cycle then proceeds in a similar way to that described above for high-pressure injection, with the only exception that the injection of the fuel into the fuel trough 16 takes place and the ignition of the mixture takes place after the percussion piston 26 strikes the striking piece 12.
- the ram according to the invention can optionally be used in three different operating modes in order to generate beats of different intensities and different time profiles. Switching can also take place while the ram is running.
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19529538 | 1995-08-11 | ||
DE19529538A DE19529538A1 (de) | 1995-08-11 | 1995-08-11 | Ramme |
PCT/EP1996/003470 WO1997007293A1 (de) | 1995-08-11 | 1996-08-06 | Ramme |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0843760A1 true EP0843760A1 (de) | 1998-05-27 |
EP0843760B1 EP0843760B1 (de) | 2000-12-27 |
Family
ID=7769242
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP96929212A Expired - Lifetime EP0843760B1 (de) | 1995-08-11 | 1996-08-06 | Ramme |
Country Status (6)
Country | Link |
---|---|
US (1) | US6102133A (de) |
EP (1) | EP0843760B1 (de) |
CN (1) | CN1192794A (de) |
DE (2) | DE19529538A1 (de) |
TW (1) | TW323309B (de) |
WO (1) | WO1997007293A1 (de) |
Families Citing this family (26)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10013270A1 (de) * | 2000-03-17 | 2001-09-20 | Krupp Berco Bautechnik Gmbh | Fluidbetriebenes Schlagwerk |
DE10115681A1 (de) * | 2001-03-29 | 2002-10-10 | Delmag Gmbh & Co Kg | Dieselbär |
US6736218B1 (en) * | 2001-04-16 | 2004-05-18 | American Piledriving Equipment, Inc. | Diesel hammer systems and methods |
DE10123202A1 (de) * | 2001-05-12 | 2002-11-14 | Krupp Berco Bautechnik Gmbh | Verfahren und Vorrichtung zur Absicherung eines fluidbetriebenen Schlagwerks gegen Leerschläge |
US20040045727A1 (en) * | 2002-09-11 | 2004-03-11 | Allums Jeromy T. | Safe starting fluid hammer |
US7694747B1 (en) | 2002-09-17 | 2010-04-13 | American Piledriving Equipment, Inc. | Preloaded drop hammer for driving piles |
DE102004062043A1 (de) * | 2004-12-23 | 2006-07-13 | Delmag Gmbh & Co. Kg | Dieselhammer |
US7854571B1 (en) | 2005-07-20 | 2010-12-21 | American Piledriving Equipment, Inc. | Systems and methods for handling piles |
NL1033528C2 (nl) * | 2007-03-09 | 2008-09-10 | Univ Eindhoven Tech | Hei-inrichting met dubbele ontbranding en werkwijze voor het werken met een dergelijke hei-inrichting. |
US20100303552A1 (en) | 2009-05-27 | 2010-12-02 | American Piledriving Equipment, Inc. | Helmet adapter for pile drivers |
US8763719B2 (en) | 2010-01-06 | 2014-07-01 | American Piledriving Equipment, Inc. | Pile driving systems and methods employing preloaded drop hammer |
US8434969B2 (en) | 2010-04-02 | 2013-05-07 | American Piledriving Equipment, Inc. | Internal pipe clamp |
US20120292062A1 (en) * | 2011-05-20 | 2012-11-22 | American Piledriving Equipment, Inc. | Systems and methods for controlling diesel hammers |
US20130199813A1 (en) * | 2013-03-04 | 2013-08-08 | Global Piling Solutions, L.L.C. | Hydraulic Hammer |
NL2011166C2 (nl) * | 2013-07-15 | 2015-01-21 | Fistuca B V | Hei-inrichting en werkwijze voor de toepassing daarvan. |
EP2871286B1 (de) * | 2013-11-12 | 2016-03-23 | Delmag GmbH & Co. KG | Rammhammer |
EP2871287B1 (de) * | 2013-11-12 | 2016-06-08 | Delmag GmbH & Co. KG | Dieselramme |
EP2924170A1 (de) * | 2014-03-28 | 2015-09-30 | Delmag GmbH & Co. KG | Rammhammer |
EP2924171B1 (de) * | 2014-03-28 | 2016-07-13 | Delmag GmbH & Co. KG | Rammhammer |
US9724811B2 (en) * | 2014-07-24 | 2017-08-08 | Taizhou Dajiang Ind. Co., Ltd. | Steam powered nailing gun |
US9777725B2 (en) * | 2014-07-24 | 2017-10-03 | Taizhou Dajiang Ind. Co., Ltd. | High pressure water pump |
US20160023336A1 (en) * | 2014-07-24 | 2016-01-28 | Taizhou Dajiang Ind. Co., Ltd. | Phase transition heat storage device |
US20160221171A1 (en) * | 2015-02-02 | 2016-08-04 | Caterpillar Inc. | Hydraulic hammer having dual valve acceleration control system |
US10273646B2 (en) | 2015-12-14 | 2019-04-30 | American Piledriving Equipment, Inc. | Guide systems and methods for diesel hammers |
US10538892B2 (en) * | 2016-06-30 | 2020-01-21 | American Piledriving Equipment, Inc. | Hydraulic impact hammer systems and methods |
CN113339342B (zh) * | 2021-06-08 | 2023-02-07 | 山东临工工程机械有限公司 | 一种打桩机辅具液压系统及液压打桩机 |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2755783A (en) * | 1953-06-18 | 1956-07-24 | Mckiernan Terry Corp | Free piston internal combustion pile hammer |
US3721095A (en) * | 1971-08-23 | 1973-03-20 | Bolt Associates Inc | Controllable force method and system of driving piles |
US4033139A (en) * | 1974-02-08 | 1977-07-05 | Frederick Leonard L | Pile driving hammer, apparatus and method |
NL172579C (nl) * | 1974-03-13 | 1983-09-16 | Delmag Maschinenfabrik | Dieselheiblok met slagverstuiving van de brandstof tussen heiblokzuiger en slagstuk. |
US4109475A (en) * | 1974-12-10 | 1978-08-29 | Van Kooten B.V. | Pile-driving ram and method of controlling the same |
US4007803A (en) * | 1976-01-19 | 1977-02-15 | Atlantic Richfield Company | Expanding detonation chamber multi-shot gas exploder |
GB1572349A (en) * | 1976-05-21 | 1980-07-30 | Bsp Int Foundation | Drop hammers |
US4131164A (en) * | 1977-11-23 | 1978-12-26 | Chambersburg Engineering Company | Adaptive valve control system for an impact device |
US4187917A (en) * | 1977-11-30 | 1980-02-12 | Hydroacoustics, Inc. | Pile driver |
US4580641A (en) * | 1983-04-28 | 1986-04-08 | Raymond International Builders, Inc. | Method and apparatus for starting diesel type hammers |
DE4414190C1 (de) * | 1994-04-24 | 1995-07-06 | Delmag Maschinenfabrik | Dieselramme |
-
1995
- 1995-08-11 DE DE19529538A patent/DE19529538A1/de not_active Withdrawn
-
1996
- 1996-08-06 US US09/000,322 patent/US6102133A/en not_active Expired - Fee Related
- 1996-08-06 EP EP96929212A patent/EP0843760B1/de not_active Expired - Lifetime
- 1996-08-06 DE DE59606259T patent/DE59606259D1/de not_active Expired - Fee Related
- 1996-08-06 WO PCT/EP1996/003470 patent/WO1997007293A1/de active IP Right Grant
- 1996-08-06 CN CN96196148A patent/CN1192794A/zh active Pending
- 1996-08-09 TW TW085109668A patent/TW323309B/zh active
Non-Patent Citations (1)
Title |
---|
See references of WO9707293A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO1997007293A1 (de) | 1997-02-27 |
CN1192794A (zh) | 1998-09-09 |
EP0843760B1 (de) | 2000-12-27 |
DE59606259D1 (de) | 2001-02-01 |
TW323309B (de) | 1997-12-21 |
DE19529538A1 (de) | 1997-02-13 |
US6102133A (en) | 2000-08-15 |
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