EP0447837B1 - Verfahren und Vorrichtung zur Steuerung einer Rammeinrichtung - Google Patents

Verfahren und Vorrichtung zur Steuerung einer Rammeinrichtung Download PDF

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Publication number
EP0447837B1
EP0447837B1 EP91102730A EP91102730A EP0447837B1 EP 0447837 B1 EP0447837 B1 EP 0447837B1 EP 91102730 A EP91102730 A EP 91102730A EP 91102730 A EP91102730 A EP 91102730A EP 0447837 B1 EP0447837 B1 EP 0447837B1
Authority
EP
European Patent Office
Prior art keywords
rammer
control device
compressed air
ring
spur toothing
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.)
Expired - Lifetime
Application number
EP91102730A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0447837A3 (en
EP0447837A2 (de
Inventor
Dietmar Dipl.-Wi-Ing. Jenne
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Terra AG fuer Tiefbautechnik
Original Assignee
Terra AG fuer Tiefbautechnik
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Terra AG fuer Tiefbautechnik filed Critical Terra AG fuer Tiefbautechnik
Publication of EP0447837A2 publication Critical patent/EP0447837A2/de
Publication of EP0447837A3 publication Critical patent/EP0447837A3/de
Application granted granted Critical
Publication of EP0447837B1 publication Critical patent/EP0447837B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B4/00—Drives for drilling, used in the borehole
    • E21B4/06—Down-hole impacting means, e.g. hammers
    • E21B4/14—Fluid operated hammers
    • E21B4/145—Fluid operated hammers of the self propelled-type, e.g. with a reverse mode to retract the device from the hole

Definitions

  • the invention relates to a method for locking the control device of a compressed air driven ramming device for its control positions forward run or backward run according to the preamble of claim 1 and to a ramming device with a forward run and a backward run, in particular for carrying out the method according to claim 1 according to the preamble of Claim 2.
  • the control device of a compressed air driven ram boring device has a twist-and-turn reversal system which has a fixed control sleeve 24 in which an axially fixed bearing tube 14 is supported by means of radial webs 23, in which a multi-part, preferably two-part control tube 16, 19 [Fig. 6], which carries a compressed air hose at its outer end, is held by a locking clip 56 which engages radially in a groove, and is also axially immovable.
  • a two-part head tube 16, 19 its front head tube part 19 has a groove-shaped axial recess 31 at its end facing away from the axially fixed control sleeve 24, into which a single driving lug 32, which is arranged on the rear, axially displaceable head tube part 16, engages axially insertable.
  • the front head tube section 19 is only rotatable, whereas the rear head tube section 16 is rotatable and axially displaceable for reversing the direction of impact.
  • This rear head tube part 16 is also mounted in the fixed bearing tube 14 and delimits with it a pressure chamber 34 which is arranged axially adjoining the (front) end having the driving lug 32.
  • a locking device 35 is provided which is acted upon by the pressure prevailing in the pressure chamber and has two positions.
  • the pressure in the pressure chamber 34 can be applied by a spring 33, by compressed air or by both. To carry out the reversal, this locking device 35 must be unlocked against the pressure applied in the pressure chamber 34.
  • These two positions of the locking device 35 define two axial positions of the rear head tube section 16, which in turn correspond to the two switching positions of the rotary valve formed by the control sleeve 24 and the front head tube section 19 for the forward or reverse run of the ram boring device.
  • the locking device 35 essentially has a locking ring 39 which is connected in a rotationally fixed manner to the rear head tube part 16 by means of a key surface 36 and which has two axially extended lugs 37, 38 of different lengths. These lugs 37, 38 each engage in two of the four corresponding recesses 44, 45 of the rear end face 40 of the bearing tube 14. The two switching positions of the locking device 35 are achieved by the different lengths of these lugs 37, 38.
  • the two-part head tube 15; 16, 19 after unlocking the rear head tube part 16 by means of an axial pull on the compressed air hose, by turning it by about 90 ° either into the first switching position, corresponding to a first stop formed by the first outer edge 48 or into the second switching position , rotated corresponding to a stop formed by the second outer edge 47 of a recess 46 in the bearing tube 14 and thus the rotary slide control switched.
  • this turn-pull changeover during operation i.e. under the load of the compressed air.
  • the control device should also remain securely locked even when the borehole has collapsed.
  • control device should not unlock, even in the event of a collapse of the borehole and the very large axial tensile forces that occur on the compressed air hose, and thus be reversed or go into an undefined operating state that requires manual recovery of the ram drilling device or even hinders it.
  • the ram boring device should be provided with a damping, which is effective even at high operating pressures of the compressed air or improves it. This is in contrast to the damping devices of the prior art, in which the damping becomes worse as the operating pressure rises.
  • a method with the characterizing features of claim 1 and a device with the characterizing features of claim 2 are provided.
  • a device can have the combination of the features of claims 3 to 16.
  • the reversal is carried out by rotating the control device against a first predeterminable force when the operating compressed air is switched off, followed by an exact positioning of the control device according to this force and independent of the rotary movement, and a subsequent locking of the control device in the individual control positions by a second force that is essentially independent of the first in terms of effectiveness.
  • Force that can also be specified by means of design measures and operating data, which also dampens the transmission of vibrations from the ram housing to the control device and thereby reliably prevents reversing of the ramming device during the application of operating compressed air.
  • a ramming device has a ram housing 1 in which a partially tubular percussion piston 2 is arranged to be longitudinally displaceable. Between this and the housing 1 there is an annular space 2.1 along the jacket of the percussion piston, through which air can flow to the percussion piston tip 2.2.
  • One end of the ram housing 1 is closed with a removable cover 4, in which a control device 3 is seated, one end 3.2 of which protrudes outwards and has a hose connection 5 for a compressed air hose for supplying compressed air.
  • Another [inner] end 3.3 protrudes into the rear region 2.3 of the percussion piston 2 and slides along its inner surface 2.4.
  • This inner end 3.3 of the control device 3 has control edges 3.4 or 3.5 and control channels, for example as shown in DE 38 00 408 - TERRA, which interact with corresponding control openings 3.6 of the percussion piston and control its forward or reverse movement in the ram housing 1 .
  • the control device 3, which is essentially formed in one piece, has a central bore 9, which extends over its entire length and which ends at the outer end 3.2 of the control device 3 in the hose connection 5. In the area of its outer end 3.2, it is connected to a locking and damping device 7 arranged in the cover 4.
  • the locking and damping device 7 has an air chamber 7.1 which is variable in size and which is arranged essentially axially parallel to the control device 3.
  • the air chamber 7.1 has end walls 7.2, 7.3 which are axially displaceable relative to one another, a first end wall 7.2 being connected to the control device 3 and a second end wall 7.3 being connected to the cover 4 or the ram housing 1.
  • the first end wall 7.2 is essentially part of a rear end ring 7.2.1 which is fixedly and adjustably and releasably connected to the control device 3.
  • the second end wall 7.3 of the air chamber 7.1 is connected to the cover 4 by one and formed adjacent to this cylinder-like inner surface 4.1 and against the rear end ring 7.2.1, relatively displaceable front end ring 7.3.1.
  • a region of the outer jacket surface 3.1 of the control device 3 is used as the other axial wall of the air chamber 7.1.
  • At least one force storage element 7.4 pushing them apart sits between these end walls 7.2 and 7.3.
  • An embodiment of such an energy storage element is a helical spring. Another spring-elastic element can also be used.
  • the air chamber 7.1 is connected by a connecting line 8 to a space 9 carrying the compressed air, which in the present case is a central bore 9 in the control device 3, and can be filled or emptied with compressed air by the latter.
  • this connecting line 8 is designed as a connecting bore 8.1, the dimensions of the response time of the locking function can be influenced and defined.
  • the helical spring or the spring-elastic element brings the positioning force for a positioning device 7.5 and the compressed air in the air chamber 7.1 applies the locking force.
  • this compressed air acts as a damping element, which dampens the mostly very hard blows of the ram housing 1 evenly and not with a force dependent on the vibration path of the control device 3 relative to the cover 4, and thus the blows are not passed on to the control device 3.
  • the damping improves with increasing operating pressure of the compressed air. This is in contrast to a damping device with spring-elastic damping elements according to the prior art.
  • a positioning device 7.5 is provided for the interaction of the control device 3 and the locking and damping device 7.
  • This positioning device 7.5 has, on the one hand, a locking flange 7.5.4 on the front end ring 7.3.1 and, on the other hand, a locking flange 7.5.4 which is connected to the control device 3 and designed as a counterpart to the locking ring 7.5.3 and which is connected to the control device 3, both of which can abut one another.
  • Their contact surfaces are each designed as a normal or wave-shaped spur gear 7.5.2 that is opposite to each other.
  • a special spur toothing can also be provided [Fig. 5], which has essentially flat flank surfaces, the top edges of which are rounded in order to facilitate the reversing process.
  • each of the flanks is arranged both on the locking ring 7.5.3 and on the locking flange 7.5.4 in a central angle range of 10-45 °, preferably in a range of 20-25 °. I.e. a flank extends in an angular range of 10-45 or 20-25 degrees.
  • the flanks within each pair of flanks for each of the spur gears 7.5.1 or 7.5.2 can have the same or different absolute value of the flank pitch, of course, corresponding flanks of the locking ring 7.5.3 or the locking flange 7.5.4 must have a corresponding pitch .
  • the positioning device 7.5 can have a rotation limiter 11, which contains a groove 11.1, which is arranged on the geometrical jacket of the latching flange, and into which a pin 11.2 engages, which extends from the second end face 7.3 above the latching ring 7.5.3 protrudes.
  • the groove 11.1 extends over a Angular range of the circumference, which is somewhat larger than a quarter turn, preferably 110 °, so that when the control device rotates for ramming, the new control position can initially be passed over by a small amount by rotating the compressed air hose.
  • the control device 3 In a control position, assumed the forward run of the ramming device, the control device 3 is locked in a first position of the positioning device 7.5 according to the force of the spring 7.4 in the air chamber 7.1.
  • the compressed air passes through the central bore 9 to the control device 3 and thus drives the percussion piston and on the other hand through the connecting bore 8.1 into the air chamber 7.1 and keeps the control device 3 in the locked state.
  • the compressed air hose is rotated, for example by approximately 90 °, the compressed air being interrupted by a shut-off valve which is located at the end of the compressed air hose at the excavation pit.
  • This shut-off valve is preferably a three-way valve which interrupts the supply of further compressed air and at the same time enables the compressed air in the hose to exit.
  • the reversing rotation of the control device 3 will only be carried out against the force of the spring 7.4. Due to the small displacement path, the force is practically constant and can be chosen so that an optimal setting and usability can be guaranteed under all operating conditions.
  • this constructive coordination can be carried out to achieve the best operability in cooperation with the flank angle and the shape of the spur toothing.
  • the positioning device 7.5 has a rotary limiter 11, then it is easier to carry out the rotary movement because then it only has to be rotated as far as the limiter and it is not necessary to pay attention to when the positioning device 7.5 engages. This is of particular advantage in the rough construction site operation.
  • the air chamber as a damping element with the compressed air as a damping medium has a spring characteristic value that is practically constant from a possible vibration amplitude due to the size relationships. This is in contrast to conventional spring-elastic damping elements. However, this dampens a vibration regardless of the amplitude. In addition, this damping force can be easily adapted to temporary conditions at any time by changing the operating pressure, even during operation.
  • a locking and damping device 7 has at least one air chamber 7.1 which is also variable in size and which is likewise arranged essentially axially parallel to the control device 3, but not coaxially. Preferably two or more such air chambers are provided. Their structure and mode of operation essentially correspond to that of the coaxial air chamber.
  • the connection with a positioning device 7.5, which is set up on the one hand to interact with a component corresponding to the front end ring 7.3.1 and on the other hand with the control device 3 and fixes each of the control positions by latching the control device relative to the cover, corresponds functionally to the first variant described above .
  • the compressed air is provided or used in at least one of the air chambers 7.1 as a force storage element or as a damping element, and these air chambers as well as the connecting bore are matched to this function with regard to their dimensions.
  • Such a damping device which is independent of a progressive spring travel, ie of the vibration path / vibration amplitude, is particularly advantageous because it improves the damping of the control device compared to the ram housing by orders of magnitude.
  • the consequence of this is that the control edges of the control device are always geometrically in the correct place, that is to say the control of the percussion piston movement can be carried out much more precisely. This requires a substantial reduction in the resonance conditions of the ram boring device or the control device. As a result, the control device breaks much less than with other damping devices.
  • the damping becomes better the higher the operating pressure of the compressed air used for the damping.
  • a higher machine performance can be achieved by increasing the pressure thereof and on the other hand an improvement in the damping.
  • the devices of the prior art in which one always has a higher device performance with a higher vibration stress and thus usually earlier breakage of a device part, generally. the control device.

Landscapes

  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mining & Mineral Resources (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Earth Drilling (AREA)
  • Air Bags (AREA)
EP91102730A 1990-03-09 1991-02-25 Verfahren und Vorrichtung zur Steuerung einer Rammeinrichtung Expired - Lifetime EP0447837B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH774/90 1990-03-09
CH774/90A CH681817A5 (enrdf_load_stackoverflow) 1990-03-09 1990-03-09

Publications (3)

Publication Number Publication Date
EP0447837A2 EP0447837A2 (de) 1991-09-25
EP0447837A3 EP0447837A3 (en) 1992-03-11
EP0447837B1 true EP0447837B1 (de) 1993-06-16

Family

ID=4194871

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91102730A Expired - Lifetime EP0447837B1 (de) 1990-03-09 1991-02-25 Verfahren und Vorrichtung zur Steuerung einer Rammeinrichtung

Country Status (5)

Country Link
US (2) US5193627A (enrdf_load_stackoverflow)
EP (1) EP0447837B1 (enrdf_load_stackoverflow)
CH (1) CH681817A5 (enrdf_load_stackoverflow)
DE (1) DE4105201A1 (enrdf_load_stackoverflow)
ES (1) ES2043397T3 (enrdf_load_stackoverflow)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9110294D0 (en) * 1991-05-13 1991-07-03 Kayes Allan G Soil displacement hammer with movable head
KR940005811B1 (ko) * 1992-01-15 1994-06-23 주식회사 수산중공업 가스와 유압을 이용한 타격기구
US5603383A (en) * 1995-09-25 1997-02-18 Earth Tool Corporation Reversible pneumatic ground piercing tool
DE19548835C1 (de) * 1995-12-08 1997-04-30 Tracto Technik Rammbohrgerät
GB2313643A (en) * 1996-05-31 1997-12-03 Inst Gornogo Dela Sibirskogo O Apparatus for impact action
US6637522B2 (en) 1998-11-24 2003-10-28 J. H. Fletcher & Co., Inc. Enhanced computer control of in-situ drilling system
US6799641B1 (en) * 2003-06-20 2004-10-05 Atlas Copco Ab Percussive drill with adjustable flow control
US20060088384A1 (en) * 2004-10-22 2006-04-27 Putnam Samuel W Stored energy coupling and pipe bursting apparatus
EP1951984A1 (de) * 2005-11-16 2008-08-06 Tracto-Technik GmbH Rammbohrgerät mit pneumatischer umsteuerung
US20100059277A1 (en) * 2006-02-14 2010-03-11 R D Sankey Engineering Limited A reversible, percussive, ram-boring machine
DE102009017515A1 (de) 2009-04-20 2010-10-28 TERRA AG für Tiefbautechnik Rammvorrichtung für Erdbohrabreiten
DE102015008339A1 (de) * 2015-07-01 2017-01-05 Tracto-Technik Gmbh & Co. Kg "Rammbohrvorrichtung und Verfahren zum Umsteuern einer Rammbohrvorrichtung"

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3727701A (en) * 1971-02-08 1973-04-17 Inst Gornogo Dela Sibirskogo O Reversible air-punching mechanism for making holes in soil by compaction
DE2340751C2 (de) * 1973-08-11 1974-09-26 Tracto-Technik Paul Schmidt, 5940 Lennestadt Steuervorrichtung für den Vor- und Rücklauf von Rammbohrgeräten
DE2634066C3 (de) * 1976-07-29 1984-09-20 Paul 5940 Lennestadt Schmidt Vorrichtung für den Vor- und Rücklauf von selbstangetriebenen, pneumatischen Rammbohrgeräten
DE2911837C2 (de) * 1979-03-26 1986-09-11 Paul 5940 Lennestadt Schmidt Steuerung für selbstgetriebene Rammbohrgeräte
DE3104547C1 (de) * 1981-02-10 1982-11-04 Gustav Dr.-Ing. 4300 Essen Jenne Steuervorrichtung fuer den Vor- und Ruecklauf von selbstgetriebenen pneumatischen Rammbohrgeraeten
GB2111565B (en) * 1981-12-15 1985-10-02 British Telecomm Self propelled reversible boring ram
GB2134152B (en) * 1983-01-22 1986-05-08 Kayes Engineering Limited Improvements in and relating to impact-action self-propelled mechanism for driving holes in the earth
CH677806A5 (enrdf_load_stackoverflow) * 1987-12-30 1991-06-28 Terra Ag Tiefbautechnik
DE3807831C1 (enrdf_load_stackoverflow) * 1988-03-10 1989-05-11 Schmidt, Paul, 5940 Lennestadt, De
CH680937A5 (enrdf_load_stackoverflow) * 1989-01-12 1992-12-15 Terra Ag Tiefbautechnik
US5086848A (en) * 1990-10-19 1992-02-11 Hudak Donald M Reversible impact hole driller and method of reversing

Also Published As

Publication number Publication date
US5193627A (en) 1993-03-16
DE4105201A1 (de) 1991-09-12
DE4105201C2 (enrdf_load_stackoverflow) 1993-06-17
EP0447837A3 (en) 1992-03-11
US5307883A (en) 1994-05-03
ES2043397T3 (es) 1993-12-16
EP0447837A2 (de) 1991-09-25
CH681817A5 (enrdf_load_stackoverflow) 1993-05-28

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