EP0144282A1 - Marteau hydraulique - Google Patents

Marteau hydraulique Download PDF

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Publication number
EP0144282A1
EP0144282A1 EP84730117A EP84730117A EP0144282A1 EP 0144282 A1 EP0144282 A1 EP 0144282A1 EP 84730117 A EP84730117 A EP 84730117A EP 84730117 A EP84730117 A EP 84730117A EP 0144282 A1 EP0144282 A1 EP 0144282A1
Authority
EP
European Patent Office
Prior art keywords
housing
elastic
chisel
insulating material
hammer according
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
EP84730117A
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German (de)
English (en)
Other versions
EP0144282B1 (fr
Inventor
Heinrich Henze
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.)
Individual
Original Assignee
Individual
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Filing date
Publication date
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6213517&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0144282(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Individual filed Critical Individual
Priority to AT84730117T priority Critical patent/ATE35929T1/de
Publication of EP0144282A1 publication Critical patent/EP0144282A1/fr
Application granted granted Critical
Publication of EP0144282B1 publication Critical patent/EP0144282B1/fr
Expired 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
    • B25D17/11—Arrangements of noise-damping means

Definitions

  • the invention relates to a demolition hammer specified in the preamble of claim 1.
  • breakers also called rock breakers or rock chisels or chisel hammers or hydraulic chisels and provided with a hydraulic drive
  • a holding device in particular by earthworks or other carrier devices.
  • Such a breaker is known for example from US Pat. No. 3,827,507 or US Pat. No. 3,889,762.
  • the disadvantage here is that the operation is associated with considerable noise pollution, so that use is not possible in all cases, since certain sound levels may not be exceeded during construction work due to environmental protection regulations.
  • the noise generated by the pulsating drive at high speed and by the impact on the chisel or the workpiece and the vibrations produced reach the atmosphere unhindered and are transmitted through the holding devices to the carrier device.
  • the object of the invention which is characterized by the measures specified in the characterizing part of claim 1, is to considerably reduce the amount of radiation emitted to the outside in such a breaker S challanmaschine to achieve without reducing the overall usability of the hammer.
  • the holding device should be such that the noise radiation and the vibrations are considerably reduced.
  • the housing is constructed in two parts without a stable mutual connection and thus does not form a unitary part which can be used as an additional device without further external support measures, for example on the boom of an excavator.
  • damping elements are designed such that the transverse force loads which occur when the chisel is used in the manner of a crowbar when the limit load of the damping elements is reached, in particular by means of projecting metallic stops, are introduced directly into the housing. In this way, overloading of the damping elements can be avoided.
  • the damping elements forming the soundproofing means are preloaded in such a way that, even at maximum load on the opposite side as a result of the chisel-like use of the chisel, they are able to transmit a sufficient holding force that fixes the tool to the drive unit and with the opposite wall maintain a mechanical contact of the housing which is sufficient to prevent uncontrolled movements (displacement and the like) of the drive part.
  • a cellular polyurethane-based plastic is preferably used as the insulation material, which has the necessary resettability and high volume compressibility with low material fatigue. Furthermore, the aging, temperature and oil resistance are great. Due to the high compressibility - with a suitable pre-tensioning of the material - also relatively large vibration amplitudes of the drive unit can be absorbed, which results in a reduction of the sound radiation as well as a reduction in the shock loads to be borne by the suspension during normal operation. The strong non-linearity caused by the strong progression of the spring constants is also favorable.
  • Insulating and insulating materials therefore have a leading effect and give the arrangement a certain amount of prestress.
  • the pretension is necessary in order to initially avoid metallic contact between the housing and drive unit due to the preferably progressive spring action. This bias is achieved when the insulating and insulating material, fixed by guide parts, is pressed against the drive unit within the housing of the housing.
  • the elastic region of the damping elements should be able to be overcome from a certain load, and should have rigid - or almost rigid - properties.
  • the resilience of the damping elements in the elastic range need not be designed for the maximum load that occurs.
  • the insulating and insulating materials were designed in such a way that they could absorb such a stress within the range of their elastic deformation, they would not be able to fulfill their task of reducing the transmission of structure-borne noise, since they are too rigid should have, if such a design is possible at all.
  • the closed design of the housing which is favorable for the purpose of sound insulation, is also maintained in the area of the drive element.
  • An elastic connection between The housing, drive and chisel compensate for the movements occurring in the axial and radial directions.
  • the elastic material is attached to the housing by means of a metallic frame. It is provided with an opening for the passage of the chisel and lies sealingly against the shaft of the housing in the region of this opening. At the points of contact, a sealing lip is preferably attached for better effectiveness.
  • the frame is easy to disassemble, so that at this point particularly heavy use can be quickly replaced by easily changing the elastic material and the frame.
  • the chisel shaft is provided with a fixed collar which is limited on the drive part by means of a thickening or device provided in the direction of the housing.
  • the elastic material disk made of fabric rubber
  • the elastic material is pressed together in the operating state and thus provides the necessary sealing effect together with the housing at this point.
  • An axial displaceability of the tool for example in renovation or repair of the drive is not embedding - tr planted possible.
  • Protect the waistband or the washer due to its size, the elastic material is protected from damage.
  • noise-reducing plastic disks can be inserted into the tool or the percussion piston or an intermediate part, in order to reduce the noise at the point at which it occurs.
  • the measures described so far for reducing noise include the drive unit, but a not insignificant part of the noise is also emitted by the chisel itself.
  • an elastic material is guided in the aforementioned frame, which encloses the chisel in its shank area - but allows free access at the point of contact with the workpiece.
  • the elastic foam material compresses, because its properties change its volume under pressure. Due to its shape, the named frame absorbs part of the insulation material and protects it from destruction by protruding edges.
  • the supply openings for the working medium (compressed oil or compressed air), which must necessarily be fed through the housing by means of pipes or hoses to the drive part, are padded with elastic material at this point to ensure that the housing is closed.
  • Sealing lips provided in the area prevent leakage and the penetration of dirt.
  • the articulation points for the attachment are separated from one another by means of damping buffers. This in particular prevents the arm of the carrier device from acting as a resonance body.
  • the ductility can be increased locally such that the drive unit can be pushed easily Gepatiuse.-under compression of the D elements in the ämpfungsele-.
  • Another advantageous way to produce the desirable compression is that the damping elements have an oversize in the axial direction, whereby compression of the elements to their nominal dimensions within the housing produces a compression effect in the axial direction, which produces the required bias to Introduce the appropriate forces of the drive unit into the housing while maintaining sound insulation when strong bending moments are exerted on the chisel.
  • the compression of the sealing elements is applied in a favorable manner in that the cover for the assembly opening for receiving the drive unit compresses the insulation elements protruding from this opening with excess when closing.
  • the drive part 1, which generates a movement of the percussion piston 2 is almost completely surrounded by a housing 3.
  • the housing 3 is lined with sound-absorbing material (insulating elements 4 or 4 'and 6).
  • the sound-absorbing material preferably consists of a rubber-elastic material which, with good load-bearing capacity, has a sound absorption behavior that reduces mechanical sound radiation having.
  • the soundproofing elements 4 and 4 ' are circumferentially formed within the cylindrical housing as a hollow cylinder, the internal dimensions of the hollow cylinder being adapted to the external dimensions of the cylindrical drive element 1 in this area.
  • the illustration with respect to the sound insulation elements 4 in the right part of the drawing and the sound insulation elements 4 'in the left part represent two different embodiments, which for the sake of simplicity are shown in a single figure (separated by double lines).
  • the cylindrical insulating element 4 can be inserted into the cylindrical housing 3 at the bottom (in the drawing) and at the same time forms the carrier element for the drive part 1 with regard to radially directed forces.
  • Another insulation element 6 in the form of a block lies against the bottom of the housing 3, which is closed at the top, and absorbs forces originating from the drive part 1, which are directed axially.
  • This block 6 can also be inserted into the housing 3 in front of the drive part 1 and fastened there. After the insulation elements 4 and 6 have been introduced, the drive part 1 is also pushed into the housing from below and lies against the inner surface of the insulation elements 4 and 6.
  • the cylindrical insulating element 4 is supported in the axial direction by metallic ring elements 5 and 5a. These ring elements 5 and 5a can be inserted into the cylindrical housing from the lower opening side and are screwed in place. In the axial direction they are dimensioned such that the insulation element 4 is held. In the radial direction it is dimensioned such that it supports the drive element 1 when loaded in the radial direction when the insulation elements are compressed in such a way that their linearity range is exceeded. Since the drive part 1 is generally switched off when the tool is used as a crowbar, and since a pulsating drive of the chisel is not required in this case, no noise pollution is associated with this operating state, so that the direct metallic contact of the drive part 1 and housing 3 is harmless.
  • the insulation element 4 is inserted under radial prestress and the insulation block 6 under axial prestress, so that compression of the insulation element 4 is present even when the chisel and the central position of the drive part 1 are unloaded in the transverse direction. In this way it is achieved that with radial loading during operation - if the stop surfaces of the ring elements 5 and 5a have not yet been reached - contact between the insulating elements and the drive part 1 is guaranteed, so that on the one hand a stable contact due to the mechanical contact and the resulting frictional engagement Position of the drive part is achieved and on the other hand, even with radial deflection, the non-loaded side exerts a damping effect and thus helps to effectively reduce vibrations of the drive part, which can contribute to the disturbing sound radiation.
  • the lower opening of the housing 3 is surrounded by a flange part 7 ′ which, in operation, adjoins an annular support frame 8 which has a membrane-like disk 9 made of fabric rubber, which is in the form of a clamped elastic disc and is clamped with its outer edge in the annular frame part 8.
  • the elastic disc holds the chisel 10 in a relaxed central position, in which there is a distance from the percussion piston 2 with respect to the rear surface of the chisel 10, so that it only acts on the chisel when it is excited by the drive part 1 to pulsate vibration.
  • the chisel 10 is also provided with a collar 11, which rests against the elastic disk 9 by means of sealing lips 12 and thus prevents the escape of liquid (drive medium) from the housing 3.
  • the disc 9 holds the chisel centering and at the same time forms an insulation measure against noise components emerging directly from the housing 3.
  • the collar 11 lies in the operating state on the disc 9, which consists of fabric rubber - or other corresponding elastic material - so that an optimal seal is given.
  • the main force which is absorbed by the chisel 10 and transferred to the housing, is not absorbed by the collar 11, but by stops 27, which limit the movement of the chisel end in the housing 3 in such a way that the disk 9 through the collar 11 is already under sufficient prestress for sufficient compression, so that the necessary sealing is ensured.
  • the insulating effect of the pane 9 is additionally supported by a block 13 made of a flexible material (Foam or the like), which surrounds the chisel 10 in its areas protruding from the housing 3 (with the exception of the chisel tip) and absorbs vibrations which are radiated from the chisel itself by radial vibrations.
  • the block 13 is shown in the left part of the drawing in a relaxed position, while it is shown compressed under load in the right part, so that an enlarged part of the chisel 10 is released.
  • the block 13 is pressed into an annular insert of the frame part 8 during compression, so that it is securely held and guided there and, in the compressed state, provides increased resistance to external loads.
  • the insulation elements 4 ' are inserted in the radial direction through openings provided within the housing 3.
  • the steel parts 5 ', 5a' and 5b 'surrounding the elements 4' are adapted to the dimensions of the insulation elements 4 'with respect to their inner surfaces - which are adjacent to the insulation elements 4'.
  • the cover parts are tightened by means of screws, the excess dimension of the insulating elements 4 'being dimensioned in the radial direction in such a way that when the cover parts 5c' and 5d 'are tightened they receive the correct prestressing - as described above.
  • the insulation elements 4 ' are preferably vulcanized onto the cover parts 5c' and 5d 'and point to the Cover parts on the opposite side each have a vulcanized metal plate 5c 'and 5d', which increases the resistance of the insulation elements on the inner surfaces.
  • the structure of the insulation elements 4 and 4 ' corresponds to elements such as are available as "metal-rubber elements" or "silent blocks".
  • the breaker is shown in the figure in the loaded state, the rear (top) of the drive part 1 exerting a compressive force on the insulating block 6.
  • an extension 14 of the drive part 1 is supported on locking elements 15 and 16, which are introduced laterally into the housing and prevent the drive part 1 from falling out in the downward direction. If the drive part 1 together with the chisel are to be removed from the housing 3, the blocking elements 15 and 16 can be removed to the outside and release the drive part 1. Accordingly, the ring frame 8 can be removed so that the drive part 1 is accessible without difficulty.
  • a feed opening 17 in the housing 3 allows the passage of a pressure hose 18 for the working medium driving the chisel.
  • the housing carrying the drive part 1 can be screwed onto the carrier device (excavator or the like) via articulation points 19 and 20.
  • additional damping elements 21 to 24 are provided at the articulation points 19 and 20, which are designed as buffers.
  • damping material 25 which consists of a corresponding foam or a sandwich system of rubber and outer metal layers and is able to reduce the transmission of disturbing vibrations to this housing on the one hand and damping for To form natural vibrations of the housing.
  • a support made of plastic 26 reduces the noises when the impact piston 2 strikes the rear chisel surface.
  • a fixed ring 27 limits the movement of the percussion piston by means of an edge provided thereon.
  • the housing is additionally protected in the area of its openings by sealing lips, as is shown in the example of ring 9.
  • sealing lips 28 are also provided on the lead-through opening for the hydraulic line 18 or at corresponding other locations.
  • a plastic sleeve 29 surrounding the casing 13 is relatively rigid.
  • the cuff is movable and, when the cuff is compressed as a result of being placed on the workpiece, is pushed back into the position denoted by 19 ', so that it forms protection and guidance at the same time.
  • FIG. 2 another embodiment of the invention is shown in section, the arrangement as a whole is shortened in length for reasons of clarity.
  • the reference numerals have each been increased by "100" compared to the exemplary embodiment shown in FIG. 1 for corresponding components.
  • the drive unit 101 was inserted into the cylindrical housing - standing from the side wall 103 and the bottom part 108 - from above.
  • the annular damping elements 104 and 104a have an oversize in the radial direction, the required axial forces being overcome when the drive unit 101 is inserted by corresponding pressing tools.
  • the upper damping element 104a has recesses 104b which are machined into the inner surface and bring about a continuous compression of the damping material in the radial direction towards the outside, so that the resistance to compression in this direction - and thus the non-linearity - correspondingly increases. Dodge in the axial direction is prevented by elements 105 and 105a.
  • the oversize of the annular damping element 106a in the axial direction is larger than the corresponding oversize of the circular disk-shaped damping element 106, so that the lateral guidance due to compression of the elements 106a is particularly large, when the drive unit is loaded from the chisel and pushes upward in the housing in the axial direction with compression of the disk 106.
  • the annular element 106 can only move to a reduced extent into the space accommodated by the disk 106 under load, so that the resistance of the ring 106a to compression is now also increased and a particularly rigid guidance takes place in the radial direction, the sound-absorbing Effect is slightly reduced, but the drive element does not yet strike the metal limiting element 105b.
  • the bottom part of the "pot” or “cup” has a circular disk-shaped damping element 109, which is supported on the bottom part 108 and cushions the drive unit 101 toward the interior of the housing.
  • the collar III 'of the chisel 110' rests on the base part 108 against a further circular disk 109a which is inserted into a corresponding recess and forms a damping element, so that there is a sound element propagating from the interior of the housing through the elements 109, 108 and 109a results in a sandwich-like arrangement, which produces effective sound absorption.
  • a seal with great rigidity is obtained at the same time, since the middle ring of the sandwich construction is rigid, so that uncontrolled movements of the drive unit and the bit in relation to the housing are reliably prevented.
  • the embodiment of the invention is not limited to the examples shown and can have many other configurations. That's the way it is In the case of advantageous alternatives, it is particularly advantageous to insert the insulation elements into rails running in the longitudinal direction, which can be provided on the inside of the housing or on the outside of the drive part 1. It is left to the respective practical embodiment to arrange the insulating elements 4 or 4 'or 6 such that they remain connected to the housing or to the drive part when the drive part 1 is removed from the housing 3.
  • the stop rings 105 to 105b can be omitted in the case of smaller hammer designs, namely because the damping elements, because of their non-linearities, can all absorb the forces themselves.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Saccharide Compounds (AREA)
  • Earth Drilling (AREA)
EP84730117A 1983-11-02 1984-11-02 Marteau hydraulique Expired EP0144282B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84730117T ATE35929T1 (de) 1983-11-02 1984-11-02 Hydraulischer aufbruchhammer.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3339999 1983-11-02
DE3339999 1983-11-02

Publications (2)

Publication Number Publication Date
EP0144282A1 true EP0144282A1 (fr) 1985-06-12
EP0144282B1 EP0144282B1 (fr) 1988-07-27

Family

ID=6213517

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84730117A Expired EP0144282B1 (fr) 1983-11-02 1984-11-02 Marteau hydraulique

Country Status (3)

Country Link
EP (1) EP0144282B1 (fr)
AT (1) ATE35929T1 (fr)
DE (1) DE3472909D1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1991017870A1 (fr) * 1990-05-23 1991-11-28 Outokumpu Oy Marteau a percussion hydraulique
EP0482327A2 (fr) * 1990-09-24 1992-04-29 Krupp Maschinentechnik Gesellschaft Mit Beschränkter Haftung Unité motrice hydraulique avec dispositif de silencieux
US5419404A (en) * 1990-05-23 1995-05-30 Bretec Oy Hydraulic impact hammer
EP0922539A2 (fr) * 1997-12-11 1999-06-16 Tamrock Oy Dispositif en liaison avec un appareil hydraulique d' abattage
FR2783867A1 (fr) * 1998-09-29 2000-03-31 Sandvik An Enceinte, et equipement associe a cette enceinte, servant a l'attenuation du bruit dans un engin de forage de roche

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD7502U (fr) *
BE664295A (fr) *
US2128742A (en) * 1937-04-09 1938-08-30 Ingersoll Rand Co Muffling device
DE860630C (de) * 1951-04-21 1952-12-22 Wilhelm Dipl-Ing Schmitt Stossdaempfer fuer Drucklufthaemmer od. dgl. mit zwischen dem Handgriff und dem den Rueckstoss erzeugenden Hammerteil angeordneter Weichgummizwischenlage
FR1353634A (fr) * 1963-01-18 1964-02-28 Meudon Forges Atel équipement anti-bruit pour marteau pneumatique
CH378820A (de) * 1960-03-18 1964-06-15 Sig Schweiz Industrieges Schalldämpfer an Pressluftwerkzeug
DE1300477B (de) * 1963-06-10 1969-07-31 Clarke Ronald Albert William Schalldaempfer fuer mit Gas betriebene Werkzeuge
US3481411A (en) * 1968-02-19 1969-12-02 Black & Decker Mfg Co Sonic tool with means for reducing noise level
CH605044A5 (fr) * 1977-03-28 1978-09-29 Mekafor

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD7502U (fr) *
BE664295A (fr) *
US2128742A (en) * 1937-04-09 1938-08-30 Ingersoll Rand Co Muffling device
DE860630C (de) * 1951-04-21 1952-12-22 Wilhelm Dipl-Ing Schmitt Stossdaempfer fuer Drucklufthaemmer od. dgl. mit zwischen dem Handgriff und dem den Rueckstoss erzeugenden Hammerteil angeordneter Weichgummizwischenlage
CH378820A (de) * 1960-03-18 1964-06-15 Sig Schweiz Industrieges Schalldämpfer an Pressluftwerkzeug
FR1353634A (fr) * 1963-01-18 1964-02-28 Meudon Forges Atel équipement anti-bruit pour marteau pneumatique
DE1300477B (de) * 1963-06-10 1969-07-31 Clarke Ronald Albert William Schalldaempfer fuer mit Gas betriebene Werkzeuge
US3481411A (en) * 1968-02-19 1969-12-02 Black & Decker Mfg Co Sonic tool with means for reducing noise level
CH605044A5 (fr) * 1977-03-28 1978-09-29 Mekafor

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1991017870A1 (fr) * 1990-05-23 1991-11-28 Outokumpu Oy Marteau a percussion hydraulique
JPH05507031A (ja) * 1990-05-23 1993-10-14 ブレテック　オサケ　ユキチュア 液圧インパクトハンマー
US5419404A (en) * 1990-05-23 1995-05-30 Bretec Oy Hydraulic impact hammer
EP0482327A2 (fr) * 1990-09-24 1992-04-29 Krupp Maschinentechnik Gesellschaft Mit Beschränkter Haftung Unité motrice hydraulique avec dispositif de silencieux
EP0482327A3 (en) * 1990-09-24 1993-02-24 Krupp Maschinentechnik Gesellschaft Mit Beschraenkter Haftung Sound damping device for hydraulically operated power circuit
EP0922539A2 (fr) * 1997-12-11 1999-06-16 Tamrock Oy Dispositif en liaison avec un appareil hydraulique d' abattage
US6328116B1 (en) 1997-12-11 2001-12-11 Sandvik Tamrock Oy Arrangement in connection with a hydraulic breaking apparatus
EP0922539A3 (fr) * 1997-12-11 2002-11-20 Sandvik Tamrock Oy Dispositif en liaison avec un appareil hydraulique d' abattage
KR100562957B1 (ko) * 1997-12-11 2006-07-19 산드빅 탐로크 오와이 유압식 파괴장치에 관한 설비
FR2783867A1 (fr) * 1998-09-29 2000-03-31 Sandvik An Enceinte, et equipement associe a cette enceinte, servant a l'attenuation du bruit dans un engin de forage de roche

Also Published As

Publication number Publication date
ATE35929T1 (de) 1988-08-15
DE3472909D1 (en) 1988-09-01
EP0144282B1 (fr) 1988-07-27

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