EP0900635A2 - Guidage d' outil pour un dispositif de frappe pneumatique - Google Patents

Guidage d' outil pour un dispositif de frappe pneumatique Download PDF

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Publication number
EP0900635A2
EP0900635A2 EP98116390A EP98116390A EP0900635A2 EP 0900635 A2 EP0900635 A2 EP 0900635A2 EP 98116390 A EP98116390 A EP 98116390A EP 98116390 A EP98116390 A EP 98116390A EP 0900635 A2 EP0900635 A2 EP 0900635A2
Authority
EP
European Patent Office
Prior art keywords
guide
tiltable
longitudinal
bearing component
guide element
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
Application number
EP98116390A
Other languages
German (de)
English (en)
Other versions
EP0900635B1 (fr
EP0900635A3 (fr
Inventor
Karlheinz Fritz
Martin Schareina
Ferdinand Zumbach
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.)
Construction Tools GmbH
Original Assignee
Krupp Berco Bautechnik GmbH
Atlas Copco Construction Tools GmbH
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 Krupp Berco Bautechnik GmbH, Atlas Copco Construction Tools GmbH filed Critical Krupp Berco Bautechnik GmbH
Publication of EP0900635A2 publication Critical patent/EP0900635A2/fr
Publication of EP0900635A3 publication Critical patent/EP0900635A3/fr
Application granted granted Critical
Publication of EP0900635B1 publication Critical patent/EP0900635B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/08—Means for retaining and guiding the tool bit, e.g. chucks allowing axial oscillation of the tool bit

Definitions

  • the invention relates to a tool guide on a pressure medium-operated impact device, in particular Hydraulic hammer, with a housing in which the tool is in Movable in the longitudinal direction with at least one guide section in each case at least one bush-like guide element and one also bush-like bearing component elastic in the transverse direction supports, and which has a stop which the Tool freedom of movement against its Extending movement limited.
  • One of the two interacting leadership components - leadership element and Bearing component - has a tiltable longitudinal surface with a linear one Vertex diameter, on the side of which surface sections with deviating, changing in the longitudinal direction Connect the diameter.
  • the one facing the tool Inner surface of the guide element - viewed in longitudinal section - with Except for their front end sections, if necessary, straight educated.
  • Hydraulic-operated impact devices - which in particular for Serve to crush stone, concrete or other building material - are taken into account with regard to the high shredding capacity required in most cases as additional or add-on equipment for construction machines such as excavators, loaders or other carrier units used.
  • the Impact device attached to the boom of a hydraulic excavator and is supplied with energy from it.
  • the tool on which the impact device moves back and forth the impacted piston acts on the material to be shredded, is usually a chisel held movably in a housing educated.
  • the housing forms part or the Extension of the striking mechanism housing, which holds the percussion piston in addition to control and other facilities.
  • the Tool guide Due to the rough working conditions and the high Shredding performance is the tool guide considerable Exposed to stress, especially kicking - conditionally too due to the relatively large play of the tool in the transverse direction - high edge pressures; these not only affect the Shredding performance but lead to a significant Wear in the area of the tool itself and the Tool guide with the result that this and / or this under Is damaged or fails completely.
  • the Tool guidance from a continuous guide section or from several spatially separated guide sections exist over which or which the tool in Is supported in the transverse direction on its associated housing.
  • German patent specification 860 630 has already made the proposal for pneumatic hammers or the like to support the hammer part indirectly or directly on the housing via soft rubber intermediate layers.
  • this training is not suitable to absorb the transverse forces emanating from the tool itself and to withstand this for a long time due to the tendency of the chisel to tilt.
  • the invention has for its object to provide a tool guide on a pressure medium operated impact device, which is designed such that each associated guide section can adapt to the position of the tool within its housing without any canting. Furthermore, the tool guide should be such that its guide components are not substantially stressed by sliding friction even when large transverse forces occur. Moreover, the new design is intended to ensure that the play between the tool and each guide section can be compensated for without the occurrence of significant forces.
  • each leadership section sits down composed of a guide element and a bearing component, wherein the bearing component in contact with the guide element from a softer, elastic material than the guide element self.
  • apex diameter is to be understood as the linear area in which either a tiltable outer surface reaches its largest diameter or a tiltable inner surface reaches its smallest diameter.
  • the subject matter of the invention is designed in such a way that each tiltable longitudinal surface lies opposite a counter surface which, viewed in longitudinal section, runs essentially in a straight line.
  • the counter surface facing the tiltable longitudinal surface is designed in such a way that it allows the rolling tiltable longitudinal surface to roll.
  • the counter surface is straight in longitudinal section; however, it can also have a curvature permitting the rolling movement - in particular a relatively large radius of curvature in longitudinal section.
  • the basic idea of the invention is, after all, to form the longitudinal surface of one of the two interacting guide components, taking into account the progressive effect of Hertzian contact; this progressive effect consists in the fact that with increasing loading of the relevant guide component in the transverse direction, an ever larger area contributes to the power transmission. Furthermore, due to the above-mentioned design, only a movement with compressive stress, at least similar to a rolling process, occurs, but practically no stress due to sliding friction, which would result in a far higher material stress.
  • the eccentric position of the vertices has the effect that a tilting moment additionally acts on the guide section in question and thus supports its positional adaptation to the position of the tool.
  • the internal guide element can consist of a metallic material which on the one hand is sufficiently wear-resistant and on the other hand has the required lubricity, in particular steel with a sliding coating. Since the power transmission always takes place with the interposition of the elastic bearing component, this leads to a softer increase in force, which in particular also protects the tool and the respective guide element together with the bearing component.
  • the interacting management components as follows be formed, the one facing the tiltable longitudinal surface Longitudinal section of the opposite surface is straight or slightly curved:
  • the Vertices of the tiltable longitudinal surface in the direction of the Stop are shifted (claim 5).
  • the vertices of both tiltable longitudinal surfaces are expediently displaced in the direction of the center plane between the guide sections.
  • the tiltable longitudinal surface of only one guide section can also be arranged correspondingly off-center.
  • the longitudinal surface in question is preferably designed to be tiltable in such a way that its apex is displaced by a maximum of 45% of the axial length of the guide component (claim 7).
  • the vertices can be shifted off-center by 10% to 30% of the axis length of the guide component (claim 8).
  • the difference between the largest and smallest diameters of the tiltable longitudinal surface is at least 0.5 millimeters (claim 9).
  • the tiltable longitudinal surface can be spherical (claim 10).
  • spherical longitudinal surface "is to be understood as meaning a surface of the guide component in question which - seen in the longitudinal section of the guide component - is rounded.
  • the associated center of rounding can lie inside or outside the spherical guide component, so that the geometric conditions associated therewith can be largely freely adapted to the other structural requirements. In normal cases it will be sufficient for the spherical longitudinal surface to have a constant curvature.
  • curvature of the spherical longitudinal surface in the vicinity of the apex is smaller than in the adjoining areas (claim 11). Due to the larger radius of curvature in the vicinity of the apex or the apex diameter, the larger the surface that is involved in the Kratt transmission, the faster the load in the transverse direction becomes available.
  • the tiltable longitudinal surface can, however, also be composed of two longitudinal sections with opposite taper, which merge into one another in terms of the apex diameter (claim 12).
  • the respective longitudinal sections that belong together — viewed in the longitudinal section — are each formed in a straight line and form an angled longitudinal surface with one another.
  • the tiltable longitudinal surface can also have a different shape within the scope of the invention, provided that this does not hinder the tilting or pivoting movement of the guide section in question, which is necessary for the positional adjustment, and is suitable for absorbing the transverse forces caused by the tool.
  • the material for the bearing component should have a high compressive strength and toughness as well as a high temperature resistance with sufficient elasticity.
  • thermosets can be considered as bearing component materials.
  • elastomers such as, in particular, polyurethane
  • thermosets can be considered as bearing component materials.
  • PA 12 G twelve-fold cross-linked, cast polyamide
  • resin-based fabric composite materials claim 14.
  • the latter materials from the group of thermosets can consist of glass, carbon or natural fibers, which are impregnated with a suitable resin.
  • the guide sections can also be made from Individual segments exist that are movable relative to each other in the Tool housing are held. It is particularly so conceivable, the guide sections with a suitable design of the Tool cross-section and the tool housing from several to build plate-shaped individual segments that are relative to each other are mobile.
  • each guide section must be suitably fixed in the axial direction with respect to their housing; this fixation must be designed so that it does not affect the function of the guide section.
  • each existing guide section can be secured in its position with respect to the housing by means of a bolt or the like, which also engages in the inner guide element with suitable play.
  • the hydraulic excavator 1 shown in Fig. 1 is equipped with a supply unit 2 (consisting essentially of a diesel engine, not shown, and a hydraulic pump driven by this), which - as known for example from the document DE 40 36 918 A1 - via a pressure and a return line is connected to a pressure medium operated impact device 3.
  • the latter is held adjustable on the boom 4 of the hydraulic excavator.
  • the striking device 3 has, as a guide unit, a supporting frame 5 which is articulated with respect to the boom and in which a pressure medium-operated striking mechanism 6 (partially shown in FIG. 2) is supported.
  • a pressure medium-operated striking mechanism 6 partially shown in FIG. 2
  • a tool in the form of a chisel 7 protrudes from the supporting frame 5, on which the above-mentioned percussion mechanism acts via its percussion piston 8 in a manner known per se.
  • the latter is shown in Fig. 2 on the one hand in the return stroke position (left) and on the other hand in the impact position (right).
  • the striking mechanism 6 forming part of the striking device 3 can be of any desired design within the scope of the invention, in particular also with regard to its control.
  • the striking mechanism housing 9 - which, among other things, receives the striking piston 8 - is connected as an extension to a housing 10 in which the chisel 7 is supported in a longitudinally movable manner via two guide sections 11 and 12; these are each secured by a bolt 13 against displacement in the axial direction.
  • the guide sections 11 and 12 are only shown schematically in FIG. 2 for reasons of clarity; their structure and function will be explained in more detail below.
  • the holder by which the chisel 7 is secured against falling out of the housing 10 is also not shown in FIG. 2; in the simplest case, it consists of a bolt or projection which is arranged between the guide sections 11 and 12 and defines the freedom of movement of the chisel 7 in the direction of its extension movement (arrow 14).
  • each guide section 11 or 12 each has two interacting guide components, namely a bush-like guide element 16 which is internal to the chisel 7 and an outer bush-like bearing component 17 which also bears against the housing 10.
  • the latter consists of a softer material than the metallic guide element 16, namely from a twelve-times cross-linked, cast polyamide.
  • the guide components 16, 17 of each guide section 11, 12 are fixed in the axial direction in the manner already mentioned.
  • All of the embodiments of the The subject of the invention has in common that one of the two each cooperating guide components 16, 17 a crowned Has longitudinal surface and that the chisel 7 facing Inner surface 16a of the guide element 16 - viewed in longitudinal section - Except for their end portions 16b and 16c even trained, i.e. forms the shape of a cylinder.
  • the above Representations continue - just like FIGS. 7 and 8 - recognize that the facing the tiltable longitudinal surface Counter surface, so possibly also the inner wall of the housing 10, is linear in longitudinal section, so that a Rolling movement is made possible.
  • each guide element 16 is assigned a bearing component 17 in the form of a likewise cylindrical bushing, the outer surface 17b of which facing the housing 10 is spherical. This configuration enables the respective interacting guide components 16 and 17 to be fastened directly to one another.
  • the bearing sections 11 and 12 - due to the spherical design of an associated guide component 16 or 17 - can adapt to an inclination of the chisel 7 caused by the guide play, thereby causing canting processes between the parts 7 and 16 are practically excluded.
  • the spherical design of the longitudinal surfaces 16d, 17a and 17b also has the consequence that the surface cooperating in the power transmission becomes larger as the stress in the transverse direction of the chisel 7 increases.
  • FIGS. 3 to 5 correspond in that the vertices SP (cf. FIG. 6) of the respective spherical longitudinal surface of a guide component are arranged eccentrically with respect to the extent of the longitudinal surface in the longitudinal direction, that is, they lie around a distance e with respect to the transverse median plane 18 of the guide component in question.
  • the tool guide - as shown in FIGS. 2 to 5 - has two separate guide sections 11 and 12, the vertices SP of the spherical longitudinal surface 16d or 17a or 17b each lie in the direction of the central plane 19 (cf. FIG. 3 ) moved between the guide sections 11 and 12.
  • the vertices SP of the spherical longitudinal surface are shifted off-center in the direction of the stop 15 shown in FIG. 2, ie to the right in FIG. 6.
  • the degree of crowning corresponds to the difference between the Largest and smallest diameters of the spherical longitudinal surface in question 16d, 17a and 17b, respectively; it is - depending on the length of the Guide section and the size of the game between this and the tool - at least 0.5 millimeters.
  • the crowning (not shown to scale) corresponds to the difference between the largest diameter DG and the smallest diameter DK of the spherical outer surface 17b; it is several millimeters. Furthermore, the representation in question reveals that the distance e - based on the axis length L of the bearing component 17 - amounts to 10%.
  • the spherical longitudinal surface (cf. FIGS. 3 to 5) can in principle have a constant, constant curvature. Deviating from this, however, there is also the possibility of designing the spherical longitudinal surface 16d, 17a or 17b to be differently curved over its longitudinal extent. In this context, it can be seen from FIG. 6 that the spherical outer surface 17b has a smaller curvature in the vicinity of the vertices SP than in the regions adjoining it. This configuration is indicated by the radii of curvature RSP or R1 and R2, the radius of curvature RSP being greater than the radii of curvature R1 and R2.
  • the tool guide is equipped with two spatially separate guide sections, these can, if necessary, also be designed differently with regard to the configuration of the spherical longitudinal surface - in particular with regard to the size of the crown and the position of the vertices SP.
  • the tiltable or pivotable longitudinal surfaces ie the outer surface of the guide element 16 or the inner surface or the outer surface of the bearing component 17
  • the tiltable or pivotable longitudinal surface can be shaped or configured differently than shown in FIGS. 3 to 6.
  • 7 and 8 show in this connection an embodiment with a bearing component 17, the tiltable or pivotable longitudinal surface of which is composed of two longitudinal sections 17c and 17d with opposite taper; these longitudinal sections merge into one another in the apex diameter - on which the apex points SP are arranged (cf. FIG. 8).
  • the longitudinal sections 17c and 17d are then - viewed in the longitudinal section (FIG.
  • the distance e (shown in FIG. 8) is 20% of the axis length L of the guide section 12.
  • the distance between the vertices of the guide sections 11 and 12 is with LS “denotes the guide play between the guide elements 16 and the chisel 7 S ".
  • the tiltable or swiveling longitudinal surface in the present case: the bearing component 17
  • sinA S / LS you choose the angle at which the guide play between the chisel 7 and the guide sections 11, 12 is balanced and thus a linear contact between the parts 7 and 11 and 12 is achieved.
  • the inclination of the larger longitudinal section 17c is formed in accordance with the angle A.
  • the shorter longitudinal section 17d is formed inclined according to the angle B.
  • the angle B “larger than the angle A "so that the tilting or pivoting movement of the guide sections 11 and 12 is not hindered to adapt to the position of the chisel 7.
  • the relevant tiltable or pivotable longitudinal surface (as explained with reference to FIGS. 3 to 6) can also be spherical, the course of the crowning overall approximating the angle A "and B ". 8 therefore also shows the radii of curvature RSP, R1 and R2 for the case of a spherical longitudinal surface in question.
  • the tilting or swiveling longitudinal surfaces also from a larger number of sub-areas with different Radii of curvature or different inclinations (accordingly 7 and 8).
  • the tilting or swiveling design of the guide sections 11 and 12 with the participation of the elastically deformable bearing component 17 has the consequence that the latter under the influence of the chisel 7th outgoing lateral forces finally deformed so far that for the Power transmission in the direction of the housing 10 is sufficient large area is available.
  • the guide element 16 which interacts directly with the chisel 7, should consist of a highly wear-resistant, metallic material which can withstand an abrupt load and, in cooperation with the chisel 7, has sufficient sliding properties. If necessary, the guide element 16 can also have a sliding coating on its inner surface facing the chisel.
  • the invention is advantageous in that it uses simple means Care is taken that between the interacting Management components 16 and 17 on the occasion of the adjustment to the Inclined position of the tool 7 only with a kind of rolling motion Pressure load takes place, only the more wear-resistant Guide component directly with the moving tool is in contact.
  • the rolling motion is also thereby allows the facing the tiltable longitudinal surface Counter surface is designed accordingly, i.e. normally - in Seen longitudinal section - runs straight.
  • the bearing component 17 consisting of a softer material forms thereby a flexible covering of the inside Guide element 16; this configuration has the consequence that the area involved in the power transmission increases with increasing Stress in the transverse direction of the guide section accordingly enlarged.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Earth Drilling (AREA)
  • Portable Nailing Machines And Staplers (AREA)
  • Electrophonic Musical Instruments (AREA)
  • Constituent Portions Of Griding Lathes, Driving, Sensing And Control (AREA)
EP98116390A 1997-09-04 1998-08-29 Guidage d' outil pour un dispositif de frappe pneumatique Expired - Lifetime EP0900635B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19738660A DE19738660A1 (de) 1997-09-04 1997-09-04 Werkzeugführung an einer druckmittelbetriebenen Schlagvorrichtung
DE19738660 1997-09-04

Publications (3)

Publication Number Publication Date
EP0900635A2 true EP0900635A2 (fr) 1999-03-10
EP0900635A3 EP0900635A3 (fr) 2003-01-15
EP0900635B1 EP0900635B1 (fr) 2006-06-21

Family

ID=7841176

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98116390A Expired - Lifetime EP0900635B1 (fr) 1997-09-04 1998-08-29 Guidage d' outil pour un dispositif de frappe pneumatique

Country Status (3)

Country Link
EP (1) EP0900635B1 (fr)
AT (1) ATE330753T1 (fr)
DE (2) DE19738660A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3670758A1 (fr) * 2018-12-21 2020-06-24 Sandvik Mining and Construction Oy Agencement de douille d'insert, marteau de démolition et procédé associé
CN116658195A (zh) * 2023-05-31 2023-08-29 长沙理工大学 一种铁路隧道作业车

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB389492A (en) * 1931-09-11 1933-03-13 Forges & Ateliers De Meudon Improvements in or relating to pneumatic percussive tools
DE9011245U1 (de) * 1990-07-31 1990-10-04 Beuermann, Herbert, Dipl.-Ing., 5207 Winterscheid Druckmittelbetätigter Schlaghammer
CN1074728A (zh) * 1991-06-19 1993-07-28 俄罗斯科学院西伯利亚矿业分院 挖掘机铲斗有动力源的斗齿
FR2692187B1 (fr) * 1992-06-16 1997-06-20 Montabert Ets Dispositif de maintien de l'outil d'un brise roche hydraulique.

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3670758A1 (fr) * 2018-12-21 2020-06-24 Sandvik Mining and Construction Oy Agencement de douille d'insert, marteau de démolition et procédé associé
US11338424B2 (en) 2018-12-21 2022-05-24 Sandvik Mining And Construction Oy Insert bushing arrangement, breaking hammer and related method
CN116658195A (zh) * 2023-05-31 2023-08-29 长沙理工大学 一种铁路隧道作业车

Also Published As

Publication number Publication date
EP0900635B1 (fr) 2006-06-21
DE19738660A1 (de) 1999-03-18
EP0900635A3 (fr) 2003-01-15
ATE330753T1 (de) 2006-07-15
DE59813609D1 (de) 2006-08-03

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