EP0086240A1 - Défonceuse actionnée par des oscillations de résonance - Google Patents

Défonceuse actionnée par des oscillations de résonance Download PDF

Info

Publication number
EP0086240A1
EP0086240A1 EP82101032A EP82101032A EP0086240A1 EP 0086240 A1 EP0086240 A1 EP 0086240A1 EP 82101032 A EP82101032 A EP 82101032A EP 82101032 A EP82101032 A EP 82101032A EP 0086240 A1 EP0086240 A1 EP 0086240A1
Authority
EP
European Patent Office
Prior art keywords
tool
weight
vehicle
node
breaker
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
EP82101032A
Other languages
German (de)
English (en)
Other versions
EP0086240B1 (fr
Inventor
Raymond Albert Gurries
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.)
Reno Salvage Co Te Sparks Nevada Ver St V Am
Original Assignee
Resonant Technology Co
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 Resonant Technology Co filed Critical Resonant Technology Co
Priority to AT82101032T priority Critical patent/ATE16409T1/de
Priority to DE8282101032T priority patent/DE3267218D1/de
Priority to EP82101032A priority patent/EP0086240B1/fr
Publication of EP0086240A1 publication Critical patent/EP0086240A1/fr
Application granted granted Critical
Publication of EP0086240B1 publication Critical patent/EP0086240B1/fr
Expired legal-status Critical Current

Links

Images

Classifications

    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
    • E01C23/00—Auxiliary devices or arrangements for constructing, repairing, reconditioning, or taking-up road or like surfaces
    • E01C23/06—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road
    • E01C23/12—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road for taking-up, tearing-up, or full-depth breaking-up paving, e.g. sett extractor
    • E01C23/122—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road for taking-up, tearing-up, or full-depth breaking-up paving, e.g. sett extractor with power-driven tools, e.g. oscillated hammer apparatus

Definitions

  • the present invention relates to a vertical impact system, and in particular to a resonantly driven system for breaking up a pavement surface using a specially adapted pavement breaking tool.
  • a variety of different pavement breaking and other types of surface impact tools are in use at the present time.
  • such tools employ a heavy weight which is lifted and allowed to fall to provide the power stroke of the tool.
  • Lifting of the weight for each stroke is generally inefficient, but more efficient solutions have not been available to date where large forces are necessary.
  • Pneumatic and hydraulic tools are often used, but such tools are limited as to the amount of force that can be applied because the reaction forces on the tool are equal to those applied to the surface.
  • the present invention provides a surface impact system including a pavement breaking tool particularly adapted to function with a resonant drive system.
  • a resonant beam having anti-nodes at each end and one or more nodes therebetween is supported at said node(s) on a mobile carrier vehicle.
  • An oscillator is fixed to an input anti-node of the beam to vibrate the beam at at least near its resonant frequency.
  • the pavement breaking tool is rigidly attached to the output anti-node of the beam, located at one end thereof.
  • the tool can be a pick or other sharpened implement designed to penetrate the pavement.
  • the tool includes a substantially flat surface oriented parallel to the beam and lying substantially in the horizontal plane.
  • An upwardly-inclined flange projects forward (with respect to the direction of travel) of the horizontal surface and is contiguous thereto.
  • the preferred angle of inclination depends on the angle of motion of the tool relative to the ground, as will be described thoroughly hereinafter.
  • the width of the tool may vary depending on the desired width of the swath to be cut.
  • the tool moves at an angle relative to the pavement determined by its location relative to the forward node of the beam, the forward node acting as a center of rotation.
  • the tool is located both forward and downward with respect to the node, and as the forward distance increases relative to the downward distance, the angle of motion approaches vertical.
  • the tool strikes the pavement at an angle in the range from about 30° to 60° relative to the plane of the work face, more usually in the range from 35° to 55°.
  • the forward flange is also inclined relative to the plane of the work face (typically horizontal), as the tool is reciprocated the forward flange strikes the ground at a "closing angle" which depends on both the angle of inclination of the flange and on the angle of motion of the tool. Selection of a closing angle in the range from 6° to 18°, preferably from 8° to 16°, assures that the tool will break off the edge of the pavement, resulting in a far more efficient fracturing of the pavement. Moreover, it has been found that the horizontal surface also aids in crushing the broken fragments of pavement or concrete and moving them away from the area where breaking is taking place. Such combination of high breaking force and ability to clear the work area leads to a highly efficient pavement breaking system.
  • the closing angle is defined as the difference between the angle of motion of the tool and the angle of inclination of the flange. With both angles measured from horizontal, the angle of motion will always be greater than the angle of inclination so that the flange impacts the pavement on the downstroke. The amount greater (i.e., the size of the closing angle) is selected to maximize the breaking action of the tool.
  • the beam is mounted to the carrier vehicle at a node near the input end of the beam.
  • a weight is superimposed over the beam at a node near the output end, and has a bearing surface adapted to bear downwardly against the beam at that node.
  • the weight is coupled to the vehicle to control the vertical position of the weight.
  • a tool depends from the output end of the beam, and strikes the surface on which the vehicle rests at the vibration frequency of the beam as the tool vibrates responsively to vibrations of the beam.
  • the reaction force generated by the tool is substantially absorbed by the weight and not transmitted to the carrier vehicle.
  • resonant systems are supported at their nodes so that the input oscillatory forces are not transmitted to the supporting frame.
  • the impact forces of the tool attached to the resonant system causes a reaction force which, at the resonant frequencies employed, is substantially constant.
  • the reaction force is transmitted directly to the supporting frame.
  • the transmission of such a force to the frame is unacceptable for the relatively large forces generated by a surface impact tool such as that disclosed herein.
  • the weight provided in the system of the present invention substantially absorbs the reaction force so that it is not transmitted to the frame.
  • the weight is supported by a single acting cylinder to further isolate reaction forces from the cariiei vehicle.
  • the weight be significantly less than the input forces of the oscillator. Accordingly, if the tool encounters an obstacle which it is unable to penetrate, the weight will be lifted, moving the forward node position upwardly and allowing the system to continue to vibrate in a resonant mode. This flexibility avoids a forced vibration mode resulting in transmission of the oscillator forces directly to the frame with potential catastrophic consequences.
  • the oscillator motor is mounted on a frame which pivots along with the beam to preserve proper alignment.
  • the tool will include a second flange similar to the first but attached to the opposite side of the horizontal surface.
  • the second flange which lies at the rear of the tool as the vehicle is driven forward, does not contribute to the breaking action. Rather, it is provided so that the mounting of the tool may be reversed to extend its useful life.
  • Impact system 10 includes a carrier vehicle with a forward frame 12 connected to a rear frame 14 by an articulating joint 16 (Fig. 2). Hydraulic actuators 17, 18 extend between forward and rear frames 12, 14 to control articulation of the vehicle.
  • the carrier vehicle rides on wheels 20 over a paved surface 22 comprised of concrete, asphalt, cement or the like.
  • the vertical impact forces applied by the impact system 10 are intended to break up the pavement, typically to facilitate its removal.
  • An engine 24 is mounted on rear frame 14.
  • Engine 24 drives a hydraulic output 26 (Fig. 2) operating three hydraulic pumps 28, 29, and 30.
  • a reservior 32 for hydraulic fluid is provided adjacent pumps 28-30.
  • One of the pumps 28-30 drives wheels 20 to propel the vehicle, one of the pumps is used to control the vehicle and operate its articulating cylinders 17, 18 and other control systems, and the third pump operates an eccentric weight oscillator to be described hereinafter.
  • the forward portion 12 of the vehicle includes a large fuel tank 34 located remote from engine 24.
  • the operator of the vehicle rides in a control cab 36 projecting forwardly and to one side of the remainder of the vehicle.
  • a solid, homogeneous resonant beam 38 is supported by the carrier vehicle, as depicted in more detail by way of reference to Fig. 3.
  • Beam 38 has a resonant frequency with forward and aft nodes spaced inwardly from its ends, and anti-nodes (locations of maximum amplitude) at its opposite ends and approximately at its center.
  • Resonant beam 38 is supported at its aft node by a shaft 40 penetrating the beam transversely at the location of the aft node.
  • Shaft 40 is fixed to beam 38 and thus rotates with the beam.
  • Shaft 40 is supported by resilient members such as 42 on opposite sides of the beam to isolate vibrations of the beam at the node from the surrounding frame.
  • Resilient supports 42 are mounted on an extension 44 from forward frame 12 of the carrier vehicle which projects rearwardly beyond articulating joint 16.
  • Eccentric weight oscillator 46 (Figs. 1 and 3) is attached to the aft end of beam 38 by plates 48.
  • a motor mount 50 is rotatably mounted to shaft 40, and projects rearwardly to a position to the side of oscillator 46.
  • a hydraulic motor 52 powered by one of the pumps 28-30 is supported by motor mount 50, and drives eccentric oscillator 46 to apply eccentric forces to resonant beam 38.
  • motor 52 drives oscillator 46 at a frequency slightly below the resonant frequency of the beam.
  • eccentric weight oscillator 46 rotates, it applies a force to beam 38 which moves in a rotational fashion about the axis of the oscillator.
  • the components of force applied axially to beam 38 are absorbed by the weight of the beam.
  • Components of force normal to the axis of beam 38 cause the aft end of the beam to vibrate in an up and down motion, inducing a near resonant vibration of the entire beam about its node locations.
  • a massive weight 54 is superimposed over beam 38 toward its forward end.
  • An aperture 56 is provided in the weight through which beam 38 passes.
  • Weight 54 includes a bearing surface 58 bearing downwardly on the beam at its forward node location.
  • the weight of the beam is supported by a transverse resilient strip 60 on the bottom surface of aperture 56.
  • Weight 54 is mounted on a pivot arm 62 pivotably mounted to forward frame 12 on shaft 64. Shaft 64 is fixed to arm 62 and rotates therewith.
  • the vertical position of weight 54 is controlled by a single acting hydraulic cylinder 66 (Figs. 2 and 3) suspended from support 68 projecting upwardly from forward frame 12. Hydraulic cylinder 66 is single acting in that it is capable of supporting weight 54, but incapable of transmitting forces from the weight to support 68.
  • a bell crank arm 70 (Figs. 1 and 3) is nonrotatably mounted to shaft 64 supporting pivot arm 62.
  • a similar bell crank arm 72 is nonrotatably mounted to motor mount 50.
  • a rod 74 interconnects bell crank arms 70 and 72 so that the rotational positions of motor mount 50 and shaft 64 coupled to the forward node of the beam by weight 54 are interdependent. As a result, vertical movement of the forward node of resonant beam 38 is transmitted through arm 74 to rotate motor mount 50 to maintain motor 52 aligned with the axis of oscillator 46.
  • a tool 76 is supported on a shank 78 terminating in a flange 80.
  • Flange 80 is bolted to a corresponding flange 82 depending from the underside of the forward end of resonant beam 38. At the neutral or rest position of tool 76, it is slightly above surface 22.
  • the tool 76 of the present invention is specially adapted for breaking pavement, such as cement, concrete, asphalt and the like, to facilitate pavement removal in a variety of circumstances.
  • the tool 76a is typically bolted to the lower end of the shank 78 and comprises a plate having a central section 84 which lies substantially parallel to the ground 22 (Figs. 1 and 3) when the resonant beam 36 is at rest, a forward flanged portion 86 inclined generally upward from the central section 84 and a rear flanged portion 88 also inclined generally upward from the central section 84.
  • the forward flanged portion 86 is inclined upward at an angle a relative to the horizontal, where a lines in the range from approximately 25° to 35°, with a presently preferred orientation of approximately 30°.
  • the rear flanged portion 86 will be inclined upward at an angle ⁇ which is equal to a.
  • the angle p does not have to equal a and, in fact, the rear portion of the tool 76a need not be inclined upward at all.
  • a rear flange 88 is provided only so that the tool 76a may be reversed as the forward flange 86 suffers wear.
  • the contact area between the lower surfaces of the tool should be large enough to break a substantial swath in the concrete so that the job may be completed in a reasonable time yet not so large that the applied force per unit area is reduced beyond that necessary to break the pavement.
  • a tool having an overall length A (Fig. 4) of approximately 16" and a width w (Fig. 5) of approximately 12" has been found successful with a constant input force of approximately 10,000 pounds.
  • Figs. 6 and 7 illustrate an alternate embodiment 76b of the tool 76 specially adapted for cutting pavement, concrete and the like along a relatively narrow line.
  • the cutting tool 76b is bolted to the lower end of the shank 78 and comprises a central section 90, a forward flange 92 inclined upward at an angle a from the plate of the central section 90, and a rear section 94 inclined upward at an angle ⁇ from the plane of the central section 90.
  • the width w (Fig. 7) of the cutting tool 76b will be substantially less than that of the breaking tool 76a. Otherwise, the dimensions may be similar.
  • the overall length £ (Fig. 6) may vary within wide limits, as can the relative lengths of the sections 90, 92 and 94.
  • the angle a preferrably lies in the range from 20° to 35°, while the angle p will normally be equal to a so that the tool 76b may be reversed.
  • Either embodiment 76a or 76b of the tool of the present invention would function in the absence of the rear flanged portion (88 and 94, respectively). It is desirable to provide the rear flange, however, so that the mounting of the tool may be reversed when the leading portion, i.e., the region between sections 84 and 86 or sections 90 and 92, becomes worn. In that case, the angle p should equal a as selected for best performance.
  • a situation to be avoided in the operation of a resonant system is one which downward movement of tool 76 relative to its neutral position is prevented, such as when system 10 encounters an upwardly inclined surface. If tool 76 cannot move downwardly from its neutral position, it essentially becomes locked in place, converting the forward end of beam 38 to a node and changing the vibrational characteristics of the beam. To prevent this situation from occurring, the size of weight 54 is significantly less than the input forces of oscillator 46. Accordingly, when tool 76 encounters such an obstacle, the reaction forces will overpower weight 54, causing the weight to lift, shifting the forward node location upwardly and allowing the resonant beam to continue to vibrate in its near resonant mode.
  • oscillator 46 supplies forces to resonant beam 38 to cause the resonant beam to vibrate at least near its resonant frequency. At that frequency, the beam exhibits two nodes, an aft node at the location of support shaft 40, and a forward node underlying bearing surface 58 of weight 54. Tool 76 vibrates vertically about its neutral position, and strikes the underlying surface 22 on its downward stroke to perform the desired function.
  • resonant beam 38 is supported only at two positions, namely, at its aft node on shaft 40 and at its forward node by weight 54. Since the node locations are basically stationary when the beam is operating in its near resonant mode, the fact that the beam is vibrating does not cause significant vibrational forces to be transmitted from the beam to the supporting vehicle.
  • the operation of the tool 76 (including both embodiments 76a and 76b) in breaking or cutting pavement may be understood by reference to Figs. 8, 9A and 9B.
  • the tool 76 reciprocates about a neutral position which corresponds to the position of the tool when the resonant beam 38 is stationary.
  • the motion of the tool 76 is not truly vertical and depends on the length of the portion of the resonant beam 38 forward of the forward node, shown generally as distance dl on Fig. 8, relative to the length of the tool sleeve 78 shown generally as distance d 2 .
  • the lengths d l and d 2 be substantially equal so that the motion of the tool 76 will describe an arc having an angle of motion, indicated by tangent 100 at the neutral position, lying at approximately 45° to the plane of the work face which is typically horizontal.
  • the angle of motion may vary, however, as d 1 and d 2 are adjusted for particular applications.
  • the resulting angle of motion may vary widely, typically within the range from 20° to 70°, more usually between 30° to 60°, relative to the plane of the work face without degrading the performance of the system, so long as the proper closing angle is maintained, as discussed hereinafter.
  • the closing angle is defined as (y - 0), which is the difference between the angle of motion (e) of the tool and the angle of inclination (y) of the flange.
  • (y - e) lies in the range between 6° and 18°, preferably from 8° to 16°, more preferably at approximately 12°, operation of the pavement breaker will be successful. The reasons for such successful operation will now be set forth.
  • the forward flange (86 or 92) is best understood in reference to Figs. 9A and 9B.
  • the forward flange (86 or 92) is inclined upward at y from the central section (84 or 90).
  • the junction between the flange and the central portion of the tool 76 strikes the pavement 22, on the downstroke, at point a. Since the angle of motion 6 of the tool 76 is less than y (by 15° as illustrated), as the tool continues its downward movement, contact between the flange and the pavement moves forward to point a'. Thus, an incremental portion b of pavement will be broken by each downstroke.
  • the distance between a and a' results only in small part from the forward movement of the vehicle 10. Rather, the distance depends on the relative inclinations of the surface of the flange and the tangential direction of motion of the tool 76.
  • the breaking tool 76a With the breaking tool 76a, by driving the vehicle forward at a relatively slow speed in the range from 0.5 to 1 foot per second, the pavement is typically broken into very small chunks which can easily be reused in making concrete and other composite materials. It is possible, however, to drive the vehicle at a much higher rate, in the range from 1 to 3 feet per second when it is desired to complete the job rapidly. The broken pieces resulting from the latter method of operation are much larger and must be broken down further prior to reuse.
  • the pavement may be broken by running the machine over parallel, spaced-apart strips with substantial fracturing occurring in the areas between said strips without the direct application of force.
  • the vehicle may be driven at a rapid rate, typically in excess of 1 foot per second, without any deterioration in the cut achieved.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Road Repair (AREA)
  • Road Paving Machines (AREA)
  • Disintegrating Or Milling (AREA)
EP82101032A 1982-02-11 1982-02-11 Défonceuse actionnée par des oscillations de résonance Expired EP0086240B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
AT82101032T ATE16409T1 (de) 1982-02-11 1982-02-11 Mit resonanzschwingungen arbeitendes strassenaufbruchgeraet.
DE8282101032T DE3267218D1 (en) 1982-02-11 1982-02-11 Resonantly driven pavement crusher
EP82101032A EP0086240B1 (fr) 1982-02-11 1982-02-11 Défonceuse actionnée par des oscillations de résonance

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP82101032A EP0086240B1 (fr) 1982-02-11 1982-02-11 Défonceuse actionnée par des oscillations de résonance

Publications (2)

Publication Number Publication Date
EP0086240A1 true EP0086240A1 (fr) 1983-08-24
EP0086240B1 EP0086240B1 (fr) 1985-11-06

Family

ID=8188869

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82101032A Expired EP0086240B1 (fr) 1982-02-11 1982-02-11 Défonceuse actionnée par des oscillations de résonance

Country Status (3)

Country Link
EP (1) EP0086240B1 (fr)
AT (1) ATE16409T1 (fr)
DE (1) DE3267218D1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0662544A1 (fr) * 1994-01-07 1995-07-12 Inco Limited Dispositif de profilage d'une couche de base d'une route
CN102561166A (zh) * 2012-02-03 2012-07-11 安迈路面技术(上海)有限公司 水泥路面共振破碎方法及装置
CN109403194A (zh) * 2018-12-17 2019-03-01 南方高科工程技术有限公司 一种偏置大梁共振破碎机
CN109629390A (zh) * 2018-12-18 2019-04-16 宜昌江峡船用机械有限责任公司 一种混凝土路面共振破碎车激振频率自动控制装置及方法
CN110593070A (zh) * 2019-09-27 2019-12-20 宜昌江峡船用机械有限责任公司 激振梁及采用该激振梁的水泥路面破碎车
CN114575231A (zh) * 2022-03-26 2022-06-03 南方高科工程技术有限公司 一种合金钢共振大梁

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1841802A (en) * 1929-11-22 1932-01-19 Gettelman Frederick Picking and tamping device
US3150724A (en) * 1963-04-01 1964-09-29 Alfred H Oelkers Eccentric mass actuator for power hammer
US3232669A (en) * 1962-05-03 1966-02-01 Jr Albert G Bodine Sonic machine for cutting pavement
US3367716A (en) * 1967-03-31 1968-02-06 Albert G. Bodine Sonic rectifier coupling for rock cutting apparatus
US4229046A (en) * 1978-12-26 1980-10-21 The Gurries Company Tool driving apparatus and method

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1841802A (en) * 1929-11-22 1932-01-19 Gettelman Frederick Picking and tamping device
US3232669A (en) * 1962-05-03 1966-02-01 Jr Albert G Bodine Sonic machine for cutting pavement
US3150724A (en) * 1963-04-01 1964-09-29 Alfred H Oelkers Eccentric mass actuator for power hammer
US3367716A (en) * 1967-03-31 1968-02-06 Albert G. Bodine Sonic rectifier coupling for rock cutting apparatus
US4229046A (en) * 1978-12-26 1980-10-21 The Gurries Company Tool driving apparatus and method

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0662544A1 (fr) * 1994-01-07 1995-07-12 Inco Limited Dispositif de profilage d'une couche de base d'une route
AU676105B2 (en) * 1994-01-07 1997-02-27 Inco Limited Roadbed profiler
CN102561166A (zh) * 2012-02-03 2012-07-11 安迈路面技术(上海)有限公司 水泥路面共振破碎方法及装置
CN109403194A (zh) * 2018-12-17 2019-03-01 南方高科工程技术有限公司 一种偏置大梁共振破碎机
CN109403194B (zh) * 2018-12-17 2023-12-22 南方高科工程技术有限公司 一种偏置大梁共振破碎机
CN109629390A (zh) * 2018-12-18 2019-04-16 宜昌江峡船用机械有限责任公司 一种混凝土路面共振破碎车激振频率自动控制装置及方法
CN110593070A (zh) * 2019-09-27 2019-12-20 宜昌江峡船用机械有限责任公司 激振梁及采用该激振梁的水泥路面破碎车
CN114575231A (zh) * 2022-03-26 2022-06-03 南方高科工程技术有限公司 一种合金钢共振大梁
CN114575231B (zh) * 2022-03-26 2024-03-12 南方高科工程技术有限公司 一种合金钢共振大梁

Also Published As

Publication number Publication date
DE3267218D1 (en) 1985-12-12
EP0086240B1 (fr) 1985-11-06
ATE16409T1 (de) 1985-11-15

Similar Documents

Publication Publication Date Title
US4402629A (en) Resonantly driven pavement crusher
US6378951B1 (en) Vibratory pavement breaker
US3396642A (en) Subgrading machine
EP0086240A1 (fr) Défonceuse actionnée par des oscillations de résonance
US4229046A (en) Tool driving apparatus and method
US5203101A (en) Digging chain vibratory system
CN206052519U (zh) 水泥混凝土路面共振破碎机
US4374602A (en) Pavement cutter
US4250760A (en) Drive assembly for pavement planing apparatus
US4340255A (en) Resonantly driven vertical impact system
CA1179541A (fr) Appareil vibratoire pour briser les revetements de chaussees
US4511282A (en) Pavement penetrating tool
US4230369A (en) Pavement planing method and apparatus
US4444434A (en) Continuous miner
EP0039373B1 (fr) Entraînement résonnant compact pour équipement de terrassement
AU2002243245B2 (en) Method and apparatus for vibratory kinetic energy generation and application thereof
US6609576B1 (en) Method and apparatus for vibratory kinetic energy generation and applications thereof
US4330156A (en) Resonant system speed control
US4506740A (en) Vibrating earth ripping apparatus
US20060000124A1 (en) Resonant demolition tool
RU2683477C1 (ru) Устройство для очистки дорожных покрытий от наледи и снега
JPH0220766B2 (fr)
CA1123251A (fr) Methode et dispositif de rabotage des vetements routiers
EP0010105B1 (fr) Machine pour dépaver un revêtement
EP0023930B1 (fr) Machine pour travailler un matériau, en particulier une décapeuse de revêtement routier

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19821222

AK Designated contracting states

Designated state(s): AT BE CH DE FR GB IT LI LU NL SE

ITF It: translation for a ep patent filed

Owner name: DE DOMINICIS & MAYER S.R.L.

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Designated state(s): AT BE CH DE FR GB IT LI LU NL SE

REF Corresponds to:

Ref document number: 16409

Country of ref document: AT

Date of ref document: 19851115

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3267218

Country of ref document: DE

Date of ref document: 19851212

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: 732

NLS Nl: assignments of ep-patents

Owner name: RENO SALVAGE CO. TE SPARKS, NEVADA, VER. ST. V. AM

REG Reference to a national code

Ref country code: FR

Ref legal event code: TP

ITTA It: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 19930228

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 19930311

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 19930315

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19930316

Year of fee payment: 12

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: LU

Payment date: 19930329

Year of fee payment: 12

Ref country code: BE

Payment date: 19930329

Year of fee payment: 12

EPTA Lu: last paid annual fee
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19940211

Ref country code: AT

Effective date: 19940211

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19940212

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Effective date: 19940228

Ref country code: CH

Effective date: 19940228

Ref country code: BE

Effective date: 19940228

BERE Be: lapsed

Owner name: RENO SALVAGE CO.

Effective date: 19940228

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Effective date: 19940901

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee
REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

EUG Se: european patent has lapsed

Ref document number: 82101032.9

Effective date: 19940910

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19960118

Year of fee payment: 15

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19960119

Year of fee payment: 15

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19960129

Year of fee payment: 15

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19970211

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19970211

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19971030

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19971101

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST