EP0440399B1 - Améliorations des outils pneumatiques - Google Patents

Améliorations des outils pneumatiques Download PDF

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Publication number
EP0440399B1
EP0440399B1 EP19910300632 EP91300632A EP0440399B1 EP 0440399 B1 EP0440399 B1 EP 0440399B1 EP 19910300632 EP19910300632 EP 19910300632 EP 91300632 A EP91300632 A EP 91300632A EP 0440399 B1 EP0440399 B1 EP 0440399B1
Authority
EP
European Patent Office
Prior art keywords
cylinder body
tool
length
hollow section
structural hollow
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
EP19910300632
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German (de)
English (en)
Other versions
EP0440399A1 (fr
Inventor
David Thomson Allan
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.)
John MacDonald and Company Pneumatic Tools Ltd
Original Assignee
John MacDonald and Company Pneumatic Tools Ltd
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
Priority claimed from GB909001904A external-priority patent/GB9001904D0/en
Priority claimed from GB909005683A external-priority patent/GB9005683D0/en
Application filed by John MacDonald and Company Pneumatic Tools Ltd filed Critical John MacDonald and Company Pneumatic Tools Ltd
Publication of EP0440399A1 publication Critical patent/EP0440399A1/fr
Application granted granted Critical
Publication of EP0440399B1 publication Critical patent/EP0440399B1/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
    • B25D17/24—Damping the reaction force
    • 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

  • This invention relates to pneumatic tools, and more particularly but not exclusively to the silencing and/or vibration damping of pneumatic tools.
  • Pneumatic tools are powered by compressed gas, the gas usually but not necessarily being air.
  • references to “air” and to “air tools” are to be taken (unless the context prohibits) as references respectively to gases in general and to pneumatic tools in general.
  • Reciprocating air tool such as paving breakers, hammers, rivetters, and the like conventionally include a metal cylinder body and an air-operated piston which reciprocates within the cylinder body during sustained use of the tool.
  • the cylinder body has an exhaust port (or a group of exhaust ports) through which used air is exhausted during use of the tool.
  • the piston shuttles back and forth within the cylinder, and it is arranged that at or near one end of its travel, the kinetic energy of the piston is abruptly transferred to an axially mobile tool bit, for example a chisel or a spade.
  • Such reciprocating air tools are notoriously noisy, not least due to the highly impulsive exhaustion of used air into the ambient environment.
  • proposals have been made for the silencing of reciprocating air tools, generally in the form of a casing clamped around the tool body.
  • One such clamp-on silencer casing is illustrated in Fig 1 of the accompanying drawing, and detailed below.
  • This known form of silencer is fabricated of plastics material, and while adding relatively little to the gross weight of the tool, suffers from certain disadvantages; the plastics casing is less robust than the basic tool and is easily damaged by the rough handling such tools frequently receive. Further, the plastics material is susceptible to heat damage and degradation by temperature fluctuations and extremes.
  • silencing arrangements and vibration reduction arrangements for reciprocating air tools generally require specially shaped and fabricated components, thus incurring significant extra cost, particularly if they are to be made resistant to dirt, debris and damage.
  • Metallic structural hollow section is a standard engineering material, usually of steel, with a uniform cross-section which is square or rectangular but may alternatively have some other shape as circular or elliptical. As such, structural hollow section is an economic material in comparison to specially made metal castings or forgings while having inherent strength, impact resistance and temperature resistance.
  • a pneumatic tool in accordance with the invention and having a silencer arrangement comprising a length of metallic structural hollow section inherently provides a protective casing for an optional vibration reducing arrangement linking the cylinder body to the remainder of the tool, such that the vibration reducing arrangement (when provided) need only be designed for its vibration reducing function without also having to be inherently resistant to dirt, debris, and impacts.
  • a pneumatic tool in accordance with the invention and having a silencer arrangement comprising a length of metallic structural hollow section inherently provides a protective casing for the cylinder body itself (whether or not the optional vibration reducing arrangement is provided), thus enabling the cylinder body and any associated pneumatic conduit system to be fabricated of plain metal tubing in contrast to the usual specially shaped metal casting or forgings which are relatively expensive in comparison to equivalent lengths of plain tubing. Therefore the present invention enables a pneumatic reciprocating tool to be fabricated or relatively inexpensive standard engineering materials without compromising the necessary robustness and damage resistance of such tools.
  • Fig 1 shows a sectional elevation of a known form of paving breaker tool 10, which is fully described in UK Patent Specification GB2018904 (and in its USA equivalent US4526190).
  • the paving breaker tool 10 essentially comprises a cylinder body 12 within which a piston 14 reciprocates in use of the tool 10.
  • the piston 14 is driven by compressed air admitted through an air inlet 16 under the control of a manually operable throttle valve 18.
  • An automatic change-over valve 20 admits compressed air into the cylinder body 12 alternately above the piston 14 and (through an air transfer conduit 22) to the underside of the piston 14. This alternate air admission causes the piston 14 to undergo double-acting reciprocation within the cylinder body 12, used air being exhausted in both directions of piston motion through a central piston-controlled exhaust port 24 formed in the wall of the cylinder body 12.
  • the piston 14 collides with a tappet 26 which transfers the kinetic energy of the piston to a tool bit 28 slidingly retained in a chuck housing 30 by a latch retainer 32.
  • An integral combined cylinder end closure and tool handle 34 is clamped to the upper end of the cylinder body 12 to seal off the cylinder and also act as a handle for manipulation of the tool 10.
  • the handle 34 mounts a pivoted hand lever 36 for controlling the throttle valve 18 through a push rod 38, and incorporates an automatic oiler 40.
  • a hollow plastics silencer casing 42 is clamped around the lower end of the cylinder body 12 so as to enclose the exhaust port 24 and thus provide a measure of noise reduction in operation of the tool 10.
  • the plastics silencer casing 42 is not as robust as the remainder of the tool 10 (formed principally of thick alloy steel drop forgings), and the plastics material is also susceptible to degradation by extremes of heat and cold.
  • FIGs 2 and 3 show an air-powered paving breaker 100 constituting the first embodiment of the present invention.
  • the breaker 100 comprises a cylinder body 12 formed as a forging or machined from heavy-wall tubing so as to have a plain bore, an integral upper external shoulder 104, an integral lower external shoulder 106, and a central exhaust port 24.
  • a one-piece combined piston and tappet 110 reciprocates within the bore of the cylinder body 12 and the tappet portion is guided by a bush 112 retained in the bore by a circlip 114.
  • the upper end of the breaker 100 is closed off by the integral combined end closure and tool handle 34 which also serves as a valve housing for the automatic change-over valve 20 and is internally ported to provide requisite air passages.
  • the manually operable throttle valve (18) which actuates the breaker 100 is not shown in Fig 2).
  • Compressed air is ducted from the valve 20 to the underside of the piston/tappet 110 by a pipe 118 which is external to the cylinder body 12 (compare with Fig 1), and the air is conveyed into the lower end of the bore by a right-angle connection 120 clamped over a side port 122 in the wall of the cylinder body 102 by means of a steel band 124 tightly encircling both the connector 120 and the cylinder body 102.
  • a steel band 124 tightly encircling both the connector 120 and the cylinder body 102.
  • the vertical sectional plane of Fig 2 is angularly skewed (compare with Fig 3) for greater clarity of internal structural detail.
  • a silencer casing 126 comprising a length of steel SHS (Structural Hollow Section), which has a generally square cross-section (see Fig 3). Suitable dimensions for the casing 126 are 120 millimetres by 120 millimetres with a wall thickness of 5 millimetres.
  • the silencer casing 126 is mounted on the cylinder body 12 by means of an upper plate 128 and a lower plate 130, both plates 128 and 130 fitting within the internal section of the SHS forming the silencer casing 126.
  • the upper plate 128 is welded at its periphery to the inner surface of the silencer casing 126.
  • the upper plate 128 is centrally secured to the cylinder body 12 by being clamped between the upper external shoulder 104 and the combined end closure/tool handle 34.
  • the lower plate 130 is a clearance fit within the silencer casing 126 and (unlike the upper plate 128) is not peripherally attached to the silencer casing 126, but instead has peripheral clearance 132 from the inner surface of the silencer casing 126.
  • the lower plate 130 is centrally secured to the cylinder body 12 by being clamped between the lower external shoulder 106 and the chuck housing 30. An air exhaust vent 134 is cut in the lower plate 130.
  • the upper plate 128 secures the upper end of the silencer casing 126 to the cylinder body 102, while the lower plate 130 prevents substantial movement of the lower end of the silencer casing 126 radially about the longitudinal axis of the cylinder body 102.
  • Two bolts extend between the handle 34 and the chuck housing 30 to hold the tool components together, and also to transmit tool-turning torque from the handle 34 to the chuck housing 30.
  • used air impulsively discharged through the central exhaust port 24 has its pressure pulses damped within the internal volume of the surrounding silencer formed by the silencer casing 126 and the end plates 128, 130.
  • the used air is then relatively smoothly discharged, with consequent lower noise levels, through the exhaust vent 134 and the clearance 132 to the ambient environment.
  • silencer arrangement has the advantage of extreme simplicity, increased efficiency of air pulse damping, with consequently improved silencing, may be achieved by providing the interior of the silencer casing 126 with a permeable filling, for example mineral wool, and/or with suitable baffles which may be perforate or imperforate.
  • a permeable filling for example mineral wool, and/or with suitable baffles which may be perforate or imperforate.
  • silencer casing 126 is formed of a length of steel structural hollow section.
  • Such material which is a standard engineering material with consequent economy of primary cost, is inherently robust and hence resistant not only to temperature fluctuations but also to impact damage such as might be caused by the tool 100 being dropped or thrown onto rubble created by use of the tool 100.
  • the silencer casing 126 protects the internal components of the tool 100 from such damage.
  • This protective function of the silencer casing 126 enables, for example, the air transfer conduit 118 to be designed and fabricated with a strength suited to its pressure-withstand duty without also requiring extra robustness to withstand impact damage.
  • the air transfer conduit 118 and also the cylinder body 12 can be formed of ordinary metal tubing rather than the relatively heavy and expensive drop forging of the Fig 1 prior art paving breaker.
  • the air transfer conduit 118 may be replaced by a length of flexible hose.
  • a further advantageous factor in the Fig 2 and 3 design of pneumatic tool is that any dents or distortions in the silencer casing 126, such as may be caused by impact damage, will have little or no effect on the proper functioning of the tool 100.
  • FIG 4 this schematically depicts an air-powered paving breaker 200 constituting the second embodiment of the present invention. Since many of the components of the breaker 200 are conventional, these components are given the reference numerals of the same or functionally parts of the breaker 10 of Fig 1.
  • the cylinder body 12 of the breaker 200 is totally enclosed by a silencer casing 202 comprising a length of steel SHS which has a generally square cross-section (but which may alternatively have a rectangular or circular cross-section).
  • the silencer casing 202 is closed at its lower end by a welded-on plate 204 which also serves as a mounting plate by being clamped between the lower end of the cylinder body 12 and the chuck housing 30.
  • a rubber gasket 206 is clamped between the upper end of the silencer casing 202 and the combined upper end closure/tool handle 34.
  • the pulses of used air discharged from the cylinder 12 through the exhaust port 24 are damped inside the silencer formed by the casing 202, the end plate 204, and the gasket 206 backed by the closure/handle 34.
  • the used air is then relatively smoothly and relatively quietly discharged from the silencer through vents (not shown).
  • SHS for the silencer casing 202 provides the tool 200 with the same functional and structural advantages as previously described in relation to the tool 100 of Figs 2 and 3. These advantages include the provision of a simple and robust but economic silencer casing 202, and the ability to fabricate the cylinder body 12 and the air transfer conduit 22 of plain tubing.
  • FIG. 5 this depicts an air-powered paving breaker 300 constituting the third embodiment of the present invention.
  • the tool 300 is generally similar to the tool 100 of Figs 2 and 3, and besides the basic paving breaker components previously described with reference to Fig 1, the tool 300 comprises a silencer casing 302 enclosing the cylinder body 12 and the exhaust port 24.
  • the casing 302 comprises a length of steel SHS having a generally square cross-section.
  • the silencer casing 302 is closed at its lower end by a plate 304 located on the lower end of the casing 302 by pins (not shown), or by welds.
  • the plate 304 is centrally clamped between the lower end of the cylinder body 12 and the chuck housing 30, but may alternatively be welded to the body 12.
  • the upper end of the silencer casing 302 is closed by an upper plate 306 located to the inside of the casing 302 by downwardly projecting pins 308.
  • a sheet-rubber gasket 310 is sandwiched between the under-surface of the plate 306 and the upper rim of the casing 302.
  • the plates 304 and 306 respectively mount the lower and upper ends of the silencer casing 302 on the cylinder body 12 to form a mutually secured assembly of tool components.
  • air exhausted from the cylinder 12 through the exhaust port 24 has its impulses damped within the silencer casing 302, and is ultimately exhausted to the ambient environment through one or more holes 312 formed in the lower plate 304.
  • FIGs 6, 7, 8 and 9 depict a noise-reduced and vibration-reduced air-powered paving breaker 400 constituting the fourth embodiment of the present invention.
  • the basic breaker mechanism 410 is shown in chain-dash outline and is essentially similar to a conventional paving breaker mechanism, for example as shown in Fig 1.
  • Features of the breaker mechanism 410 which relate to the invention and/or differ from conventional features are detailed below.
  • the breaker cylinder body 412 is no longer closed at its upper end by a closure component which also serves as a handle, but instead is now upwardly continued by a columnar extension piece 414 having a smooth cylindrical exterior surface over the major part of its height, and a screw-threaded upper end.
  • the exterior piece 414 has a transverse passage 416 linking its smooth exterior portion to a hollow central bore 418 leading down to the automatic change-over valve 20.
  • the passage 416 opens into the hollow interior of a transverse handle 420 such that the arrangement functions as a short-range sliding air connection, for a purpose to be detailed below.
  • a resilient rubber bush 422 surmounted by a lock-nut 426 screwed onto the threaded upper end of the extension piece 414.
  • the breaker cylinder body 412 is further provided with a pair of laterally extending brackets 428.
  • An upper transverse support plate 430 bears against the underside of the handle 420 and is a clearance fit around the extension piece 414.
  • a pair of spring assemblies 432 extend between the brackets 428 and the support plate 430.
  • Each spring assembly 432 comprises a coiled compression spring 434 held between the plate 430 and a spring retainer cap 436 by a nut-and-bolt assembly 438.
  • Suitable spring rates for the springs 434 are in the range 5-30 kilogrammes per inch (1.97-11.8 kilogrammes per centimetre).
  • the bolt of each assembly 438 is a sliding fit in the support plate 430 such that the spring assemblies 432 can contract to allow the brackets 428 and hence the cylinder body 412 to move towards the plate 430.
  • the nut-and-bolt assemblies 438 prevents unlimited extension of each spring 434.
  • the lock-nut 426 similarly prevents unlimited downward movement of the cylinder body 412 relative to the support plate 430. During such relative movement, the previously described sliding air connection between the handle 420 and the extension piece 414 maintains a continuous and substantially leak-free compressed air supply from the interior of the handle 420 to the valve 20.
  • Fig 7 shows the hollow handle 420 provided with the conventional air inlet 16, throttle valve (not visible) and its operating push-rod 38, and the throttle control lever 36, all for supplying and controlling the operating air for the tool 400.
  • the breaker mechanism 410 including the breaker cylinder body 412 and the upper support plate 430 is shrouded by a silencer casing 440 formed by a suitable length of square-section SHS.
  • the casing 440 is mounted on the breaker 400 by being welded to the periphery of the support plate 430 (see Figs 6 and 8).
  • the breaker 400 further includes a lower transverse support plate 442 which is rigidly clamped to the lower end of the breaker mechanism 410.
  • the necessity of allowing the upper support plate 430 and the welded-on casing 440 to move relative to the breaker mechanism 410 for the proper operation of the resilient rubber bush 422 and the spring assemblies 432 requires that the casing 440 can move vertically past the periphery of the lower support plate 442 while being adequately supported against transverse movement and hence against excessive movement radially of the longitudinal axis of the breaker mechanism 410.
  • rollers 444 are mounted in each corner of the lower support plate 442 (see Fig 9), the rollers 444 being mounted and aligned to run vertically along the inside corners of the length of square SHS forming the casing 440. (Only one such roller is depicted in Fig 6). Although not shown it is also envisaged that the rollers 444 might be substituted by a rolling ball arrangement.
  • a part-conical cover 446 caps the breaker 400 as an upper end closure of the casing 440 to shield the upper parts of the breaker mechanism 410.
  • air exhausted from the cylinder body 412 enters the surrounding silencer formed by the casing 440, the upper support plate 430, and the lower support plate 442.
  • the air pulses are damped within the silencer, and are discharged relatively smoothly and with relatively little noise (as compared to unsilenced discharge) to the ambient environment through the clearance between the periphery of the lower support plate 442 and the encompassing silencer casing 440 (see Fig 9).
  • Additional air discharge ports are optionally formed in the lower support plate 442 and/or in the silencer casing 440.
  • the rubber bush 422 damps jarring on the rebound, for further reduction of vibration.
  • Fig 6-9 thus provides combined noise reduction and vibration reduction in a simple, robust, and economic assembly, with inherent protection of the resilient mountings which therefore do not require to be designed or fabricated per se in an impact-resistant form.
  • Figs 10, 11, and 12 illustrate three further arrangements each providing noise reduction combined with vibration reduction and damage resistance. These three arrangements are each generally similar to the arrangement shown in Fig 6 and detailed above with reference to Figs 6-9. Basic similarities arise in respect of the silencer casing being a length of square (or rectangular) structural hollow section mounted on an upper support plate around which it is welded, and further supported by a lower support plate which is secured to the breaker mechanism but unsecured to the silencer casing. In each case, the tool handle is clamped to the upper side of the upper support plate.
  • the breaker mechanism has an upwardly projecting extension piece with an internal air passage slidingly linking the automatic change-over valve to the hollow centre of the tool handle to form a sliding connection for compressed air.
  • the centrally mounted breaker mechanism is resiliently linked to the assembly of the handle, upper support plate, and silencer casing.
  • the resilient link forms the vibration reduction means and comprises one or more coiled compression springs, though other forms of resilient linkage can be employed, which may for example be metallic or non-metallic.
  • the resilient link in both arrangements further comprises an annular rubber bush through which the upper end of the extension piece holds down the tool handle. (A somewhat different form of vibration reduction is employed in the arrangement of Fig 12, and will be described below).
  • Fig 10 this schematically illustrates a paving breaker 500 forming the fifth embodiment of the present invention.
  • the extension piece 514 is formed with a shoulder near its lower end to bear against the lower end of the coiled compression spring 534.
  • the lower support plate 542 is roller-free and a sliding fit within the silencer casing 540 for lateral restraint and torsional linking of the casing 540 to the breaker mechanism 510.
  • the paving breaker 500 functions to provide noise reduction and vibration reduction in the same manner as the breaker 400 of Figs 6-9.
  • Fig 11 shows part of a paving breaker 600 constituting the sixth embodiment of the present invention.
  • the breaker 600 is largely identical to the breaker 400 (compare Fig 11 with Fig 4), substantive detail differences lying mainly in an asymmetrical arrangement within the breaker 600, and in the provision of tiebolts 650 (only one being visible in Fig 11) anchoring the extension piece 614 to the chuck holder 30.
  • Fig 12 shows a paving breaker 700 constituting a seventh embodiment of the present invention.
  • the breaker 700 is generally similar to the breaker 500 shown in Fig 10, but differs significantly in respect of the means provided for reducing vibration.
  • the combined upper-end cylinder closure and automatic change-over valve housing (715 in Fig 12) is a component which is now distinct from and relatively movable with respect to the extension piece 714.
  • the cylinder closure/valve housing 715 is slidingly sealed around the lower end of the extension piece 714.
  • the closure/housing 715 is prevented from being pulled or pushed off the lower end of the extension piece 714 by an integral shoulder or flange 760 provided thereon.
  • the extension piece 714 itself is also in two parts, a lower tubular component 762 providing the air passages 716 and 718, and an upper, screw-threaded stud 764 which has its lower end screwed into the upper end of the tubular component 762.
  • the nut 726 acts through the washer 724 and the resilient rubber bush 722 to resiliently restrain the extension piece 714 against all except a limited downward movement relative to the handle 720. Upward movement of the extension piece 714 relative to the handle 720 is entirely prevented by abutment of the upper end of the tubular component 762 with the portion of the handle 720 surrounding the bore for the stud 764.
  • closure/housing 715 slides on the relatively immobile tubular component 762 of the extension piece 714 in the manner of an inverted piston/cylinder arrangement, with the closure/housing 715 playing the part of the piston.
  • the cross-sectional area of the tubular component 762 subtracts from the up-facing area of the "piston" 715.
  • this internal pneumatic pressurisation of the closure/housing 715 acts on the differential "piston" areas theron to provide a net downward bias on the closure/housing 715 and the remainder of the breaker mechanism 710 attached thereto. Therefore upwardly impulsive movement of the breaker mechanism 710 is resiliently counteracted by the pneumatically -induced downward bias to produce the pneumatic equivalent of the mechanical spring 534 present in the breaker 500 of Fig 10, to provide vibration reduction. Downward rebound of the breaker mechanism 710 is resiliently limited and damped by the rubber bush 722 acting through the extension piece 716 and the shoulder 760 when the closure/housing 715 slides down the tubular component 762 into contact with the shoulder 760.
  • the silencer casing 740 is formed of a length of structural hollow section as in previously described embodiments, and provides noise reduction in the same manner.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Medicines That Contain Protein Lipid Enzymes And Other Medicines (AREA)

Claims (2)

  1. Outil pneumatique à mouvement alternatif (400), comprenant un corps de vérin (412) et un piston actionné par air gui se déplace de façon alternative à l'intérieur dudit corps de vérin pendant l'utilisation soutenue dudit outil, de l'air sortant d'un orifice de sortie dans ledit corps de vérin pendant une telle utilisation, ledit outil pneumatique comprenant en outre un ensemble amortisseur de bruit (440) entourant sensiblement totalement ledit corps de vérin (412), comprenant en lui-même ledit orifice de sortie, ledit ensemble amortisseur de bruit comprenant une longueur de tronçon métallique structurellement creux (440), dont l'axe longitudinal est généralement parallèle à l'axe longitudinal dudit corps de vérin (412), constituant un boîtier protecteur pour un dispositif de réduction de vibration (432) reliant le corps de vérin (412) au reste de l'outil, un moyen de montage pour monter ledit ensemble amortisseur de bruit (440) sur ledit outil pneumatique (400) comprenant deux plaques (430, 442) mutuellement espacées à l'écart l'une de l'autre le long de l'axe longitudinal de ladite longueur de tronçon métallique structurellement creux (440), caractérisé en ce que la première desdites plaques (430) est fixée à ladite longueur de tronçon structurellement creux (440) et l'autre desdites plaques (442) est non fixée à ladite longueur de tronçon structurellement creux (440) et adaptée de façon libre à l'intérieur tout en étant fixée de manière sensiblement rigide audit corps de vérin (412), la première desdites plaques (430) qui est fixée à ladite longueur de tronçon structurellement creux (440) étant reliée élastiquement par l'intermédiaire d'un moyen élastique de réduction de vibration (432) audit corps de vérin, l'autre desdites plaques (442), qui est non fixée à ladite longueur de tronçon structurellement creux (440), est couplée à roulement par un système à billes ou à rouleaux (444) à la surface intérieure de ladite longueur de tronçon structurellement creux (440) de façon à permettre le mouvement de l'autre desdites plaques (442) et du corps de vérin (412) le long de l'axe longitudinal de ladite longueur de tronçon structurellement creux (440) tout en empêchant sensiblement la rotation de ladite autre plaque (442) et du corps de vérin (412) autour de l'axe longitudinal de ladite longueur de tronçon structurellement creux (440) de telle façon que les forces de rotation d'outil appliquées par un opérateur d'outil à un manche d'outil (420) fixé à ladite longueur de tronçon structurellement creux (440) sont transmises audit corps de vérin (412) et à une broche d'outil (28) fixée à rotation sur lui malgré la liaison élastique de la première desdites plaques (430) et de la longueur de tronçon structurellement creux (440) qui lui est fixée avec le corps de vérin (412) par l'intermédiaire dudit moyen élastique de réduction de vibration (437).
  2. Outil pneumatique à mouvement alternatif selon la revendication 1, dans lequel le corps de vérin est fabriqué à partir d'un tube entièrement métallique.
EP19910300632 1990-01-27 1991-01-28 Améliorations des outils pneumatiques Expired - Lifetime EP0440399B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
GB909001904A GB9001904D0 (en) 1990-01-27 1990-01-27 Noise and vibration reduced air-tool
GB9001904 1990-01-27
GB9005683 1990-03-14
GB909005683A GB9005683D0 (en) 1990-03-14 1990-03-14 Improvements in or relating to pneumatic tools

Publications (2)

Publication Number Publication Date
EP0440399A1 EP0440399A1 (fr) 1991-08-07
EP0440399B1 true EP0440399B1 (fr) 1996-05-22

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EP19910300632 Expired - Lifetime EP0440399B1 (fr) 1990-01-27 1991-01-28 Améliorations des outils pneumatiques

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EP (1) EP0440399B1 (fr)
JP (1) JPH0679652A (fr)
AU (1) AU7009391A (fr)
CA (1) CA2034940A1 (fr)
DE (1) DE69119616T2 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003009974A1 (fr) * 2001-07-26 2003-02-06 Nicolaas Daniel Lombard Burger Appareil destine a attenuer le bruit d'une perforatrice de roche
GB2411375B (en) * 2004-02-26 2008-04-09 South West Highways Ltd Vibration reduction system
JP5147488B2 (ja) * 2008-03-27 2013-02-20 株式会社マキタ 作業工具
JP5849877B2 (ja) * 2012-07-13 2016-02-03 日立工機株式会社 携帯用作業機
CN109508490B (zh) * 2018-11-08 2023-03-24 中车青岛四方机车车辆股份有限公司 一种中空铝型材的声学模型等效方法

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1353634A (fr) * 1963-01-18 1964-02-28 Meudon Forges Atel équipement anti-bruit pour marteau pneumatique
BE649108A (fr) * 1963-06-10
FR2209311A5 (fr) * 1972-12-05 1974-06-28 Maco Meudon Sa
FR2388646A1 (fr) * 1977-04-29 1978-11-24 Maco Meudon Sa Marteau brise-beton equipe de dispositifs silencieux
DE3440530A1 (de) * 1983-11-02 1985-05-09 Heinrich 1000 Berlin Henze Hydraulischer aufbruchhammer
DE3447401A1 (de) * 1984-12-24 1986-07-03 Wacker-Werke Gmbh & Co Kg, 8077 Reichertshofen Hammer mit schutzhaube

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Publication number Publication date
DE69119616D1 (de) 1996-06-27
AU7009391A (en) 1991-08-01
CA2034940A1 (fr) 1991-07-28
JPH0679652A (ja) 1994-03-22
EP0440399A1 (fr) 1991-08-07
DE69119616T2 (de) 1997-01-23

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