WO2017207852A1 - Défonceuse à actionnement linéaire - Google Patents

Défonceuse à actionnement linéaire Download PDF

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Publication number
WO2017207852A1
WO2017207852A1 PCT/ES2017/070379 ES2017070379W WO2017207852A1 WO 2017207852 A1 WO2017207852 A1 WO 2017207852A1 ES 2017070379 W ES2017070379 W ES 2017070379W WO 2017207852 A1 WO2017207852 A1 WO 2017207852A1
Authority
WO
WIPO (PCT)
Prior art keywords
ripper
linear drive
coupler
connecting rod
assembly
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.)
Ceased
Application number
PCT/ES2017/070379
Other languages
English (en)
Spanish (es)
Other versions
WO2017207852A4 (fr
Inventor
Juan Manuel ARGOTE
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.)
Talleres Betono Sa
Original Assignee
Talleres Betono Sa
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 Talleres Betono Sa filed Critical Talleres Betono Sa
Publication of WO2017207852A1 publication Critical patent/WO2017207852A1/fr
Publication of WO2017207852A4 publication Critical patent/WO2017207852A4/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F5/00—Dredgers or soil-shifting machines for special purposes
    • E02F5/30—Auxiliary apparatus, e.g. for thawing, cracking, blowing-up, or other preparatory treatment of the soil
    • E02F5/32—Rippers
    • E02F5/326—Rippers oscillating or vibrating
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F5/00—Dredgers or soil-shifting machines for special purposes
    • E02F5/30—Auxiliary apparatus, e.g. for thawing, cracking, blowing-up, or other preparatory treatment of the soil
    • E02F5/32—Rippers
    • E02F5/323—Percussion-type rippers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/066—Means for driving the impulse member using centrifugal or rotary impact elements
    • B25D11/068—Means for driving the impulse member using centrifugal or rotary impact elements in which the tool bit or anvil is hit by a rotary impulse member
    • 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
    • E01C23/124—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 moved rectilinearly, e.g. road-breaker apparatus with reciprocating tools, with drop-hammers
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/96—Dredgers; Soil-shifting machines mechanically-driven with arrangements for alternate or simultaneous use of different digging elements
    • E02F3/966—Dredgers; Soil-shifting machines mechanically-driven with arrangements for alternate or simultaneous use of different digging elements of hammer-type tools
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B1/00—Percussion drilling

Definitions

  • the present invention is part of the technical field of percussion tools. More specifically, it is a linear drive ripper with said drive arranged inside. In addition, the ripper is flat and the drive system it comprises generates a high frequency of vibration. BACKGROUND OF THE INVENTION
  • the vibration that must be produced on the ripper to produce the breakage of the rock is achieved by rotating two axes with off-center masses. When these masses coincide at their highest and lowest point, the movement of the ripper occurs. In addition, this movement occurs at high revolutions, thus achieving the necessary vibration for said rock breakage. During the rest of the eccentric mass race, the forces are compensated and it is not possible to harness their movement energy.
  • the present invention proposes a linear drive ripper that solves the previously raised technical problems associated with the state of the art ripper.
  • a linear drive ripper which comprises a flat grid, within which is a drive assembly that causes a high frequency of unidirectional vibration. So the ripper is shaped like a flat grating.
  • the ripper In the lower section of the ripper it comprises a wear boot or tip, attached to the grille.
  • the tip is the element that comes into contact and drills the ground, the rock, etc. Said tip is interchangeable by means of a tensioning shaft system that holds it and keeps it in permanent contact with the grille.
  • the ripper also comprises a coupler or housing that is a piece that allows the union with the carrier. It also comprises two damping assemblies between the coupler and the repository configured to absorb the vibrations of the repository and prevent them from passing to the carrier machine to which the ripper is attached.
  • the coupler is configured to receive bolts or shafts connecting to said carrier. Between the bolts and the coupler there are some damping elements.
  • the damping assemblies comprise at least one upper shock absorber disposed between an upper section of the recess and the coupler, and an additional shock absorber, disposed in the recess and linked to a stop that limits the forward movement of the ripper. These damping assemblies prevent the vibrations of the ripper from passing to the carrier equipment to which it joins for operation.
  • the specific configuration of the ripper that is proposed, by allowing a high frequency of vibration, allows to improve the behavior and efficiency of the ripper.
  • An essential advantage of the present invention is that the resulting force component that pushes the ripper down (towards the ground, rock, etc. that is to be drilled) is much greater than the magnitude of the resulting force component in the opposite direction. This allows more energy to be used.
  • the drive assembly comprises a crankshaft, and a connecting rod-counterweight assembly.
  • the connecting rod and the counterweight are two different parts linked to each other and in another embodiment it is a single piece.
  • the counterweight alone or with the connecting rod (if it forms a single piece with it), moves linearly along a receptacle inside the grille.
  • All the elements of the drive assembly are arranged inside the grille, without protruding from either side of the grille.
  • the linear movement of the connecting rod-counterweight assembly is carried out in the same direction in which the attack point is located, so that the force is transmitted completely in that direction, without dispersion and therefore without energy losses.
  • the ripper of the present invention may comprise a transmission assembly for connecting the crankshaft with an engine responsible for controlling its movement.
  • the ripper comprises a plurality of bearings, arranged in the recess in the area where the crankshaft is located and can comprise a system of lubrication for said bearings. In cases where there is a lubrication system, it can comprise ducts that run inside the connecting rod-counterweight assembly through which the oil in the receptacle passes to the bearings when the connecting rod-counterweight assembly moves downwards in said receptacle.
  • One of the advantages of the linear drive ripper of the present invention is that the drive assembly is disposed inside the grille and it moves in block. Therefore, there are no additional moving parts to the ripper since the moving parts of the drive assembly are completely housed inside said ripper.
  • the described ripper is free of gears, forks, carrier bolts and balls to absorb vibration energy. Neither distribution block nor vibration boxes are necessary. In addition, the proposed ripper has a low noise level associated with it.
  • the specific configuration of the ripper allows to reduce the weight of the ripper up to 25% compared to the ripper of the prior art.
  • this configuration allows the ripper to be manufactured with a more ergonomic design, less bulky and less than conventional rippers. A penetration length of the grating of 25% more is achieved.
  • the grating is lower from the coupler so that the lever arm necessary for the excavator in which it is used may be smaller. This also decreases fuel consumption.
  • Figure 1 Shows a perspective view of the linear drive ripper in an embodiment in which the damping assemblies comprise connecting bolts between the coupler and the grille, and damping elements arranged around the bolts.
  • Figure 2A shows a sectional view of the linear drive ripper in which the drive assembly arranged in the same grid can be seen in an embodiment where the connecting rod and the counterweight are two different parts.
  • Figure 2B Shows a sectional view of the linear drive ripper in which the drive assembly disposed in the same grid can be seen in an embodiment where the connecting rod-counterweight assembly is a single piece.
  • Figure 3A Shows a front view of the linear drive ripper in which it can be seen that the grid is completely flat.
  • Figure 3B. Shows a sectional view of the linear drive ripper shown in Figure 3A in which the fully integrated drive assembly can be seen inside the grille.
  • Figure 4.- Shows a sectional view of the linear drive ripper, similar to that shown in Figure 3B in which the lubrication system is appreciated.
  • Figure 5. Shows a sectional view of the linear drive ripper, by the plane of the bolts that connect the ripper to the coupler to appreciate the damping blocks.
  • Figure 6. Shows a sectional view of the linear drive ripper in an embodiment in which the damping assemblies comprise upper shock absorbers and an additional shock absorber.
  • the linear drive ripper (figure 1) comprises a reel (1) inside which is a drive assembly (2) that is responsible for generating the vibration movement of the reel itself (1) and a coupler (3).
  • the grille and the coupler (3) are joined together by two damping assemblies that are configured to absorb the vibrations of the grille (1) and prevent them from passing to the carrier machine to which the ripper is attached.
  • the damping assemblies are bolts (4) surrounded by damping elements (10).
  • the damping assemblies are at least one upper shock absorber (16) disposed between an upper section of the grate (1) and the coupler (3), and an additional shock absorber (18) disposed in the grate (1) linked to a stop (20) attached to the coupler (3) and configured to limit the forward movement of the grate (1).
  • Figure 2A-2B shows a section of the linear drive ripper in which the components of the drive assembly (2) can be seen.
  • Said components of the drive assembly (2) are a crankshaft (6) and a crank-counterweight assembly (12), linked to said crankshaft (6) and configured to move linearly along a receptacle (9) arranged in the grate (1). That is, the vibration generator is inscribed in the grid itself (1).
  • An exemplary embodiment is shown in Figure 2A in which the connecting rod-counterweight assembly (12) comprises a connecting rod (7) and a counterweight (8) which are two different elements, linked together to transmit the movement from one to the other. other.
  • An example of embodiment is shown in Figure 2B in which the connecting rod-counterweight assembly (12) is a single piece.
  • FIG. 3A another essential characteristic of the grid (1) is that it is completely flat.
  • the drive assembly (2) is fully integrated inside the recess (1) without protruding from any of the faces of this one. This makes it possible to greatly reduce the volume of the grating (1) and its weight and make it more ergonomic. This allows the ripper to penetrate more deeply.
  • the ripper also includes an attack point (5) with which the stone drills the ground or the corresponding surface on which it is working. Said attack tip (5) is arranged at the distal end of the grate (1).
  • the receptacle (9) is aligned with the attack tip (5) such that the movement of the connecting rod-counterweight assembly (12) is made in a direction coinciding with the attack tip (5).
  • the movement of movement of the crank- counterweight assembly (12) that generates the vibration of the grille (1) is transmitted entirely to the attack point (5). There is no loss of energy due to changes of direction in the application of force.
  • Figure 3B shows the drive assembly (2) from another perspective, obtained by sectioning the ripper in a direction perpendicular to that chosen in Figures 2A-2B.
  • An important advantage of the proposed configuration for the linear drive ripper of the present invention is that the energy losses associated with the rotational movement of the eccentric masses in the state of the art ripper are avoided.
  • the movement of the connecting rod-counterweight assembly (12) is completely linear, up and down, along the receptacle (9).
  • the total force with which the vibrations are generated is the weight of the crank-counterweight assembly (12) of the drive assembly.
  • the connecting rod-counterweight assembly (12) comprises an independent connecting rod (7) and a counterweight (8)
  • the weight is the sum of the mass of the counterweight (8) and of the mass of the connecting rod (7).
  • This drive assembly (2) allows obtaining high vibration frequencies that cannot be obtained with other prior art solutions such as those used by hydraulic breakers.
  • the linear drive ripper the drive assembly (2) is connected to a hydraulic motor that receives hydraulic power from the carrier.
  • the grid (1) comprises bearings (14).
  • the ripper preferably comprises two bearings (14), one on each side of the crankshaft (6) and placed on the sides of the grille (1) so that the breaking forces produced by the drive assembly (2) act directly over it and in the center of the attack point (5). Also, in an exemplary embodiment, the ripper comprises a third bearing (14) disposed under the receptacle (9).
  • FIG 4 An embodiment of the invention is shown in Figure 4 in which the connecting rod (7) additionally comprises conduits disposed therein that connect the receptacle (9) with the bearings (14). That is to say, the lubrication of the bearings (14) and the friction parts is carried out by means of the pressure exerted on the oil itself when the connecting rod-counterweight assembly (12) is lowered through the receptacle (9). This pressure is used to redirect the oil through some holes to all bearings (14).
  • FIG. 5 another embodiment of the invention is shown in which the ripper also comprises a plurality of damping elements (10). Said figure 5 represents the upper section of the ripper in which the coupler (3) for attachment of the ripper to the carrier equipment is appreciated.
  • the grate (1) comprises in its upper section two bolts (4) configured to make the connection between the grate (1) and the coupler (3).
  • said bolts (4) there are damping blocks (10).
  • These bolts (4) are preferably offset to increase the damping stroke.
  • This damping system with damping blocks (10) and off-center bolts allows the damping to be long, in every way, even in the air.
  • the coupler (3) preferably comprises two transverse tubes that form a lateral resistance cross and are crossed by two bolts (4), with the off-center ends, in which they adjust to the damping elements (10).
  • Said coupler has an arrow greater than the grid (1) due to the eccentricity of the ends of the bolts (4) When a vertical effort is made downwards or upwards of the carrier, the bolts (4) rotate through their eccentricity. This means that these reactions are not linear but that a torsion is created by increasing the damping power of the damping elements (10).
  • the damping of the vibrations is carried out by means of the offset of the bolts (4) that are adjusted by means of the damping elements (10) and in this way the reaction forces do not impact directly on the excavator but rather that these elements absorb them shock absorbers (10).
  • the coupler (3) is necessary to correctly absorb the vibrations and also to allow the ripper to be held from the carrier (excavator) by means of a standardized hat.
  • Figure 6 shows the exemplary embodiment of the ripper in which the two damping assemblies are respectively at least one upper shock absorber (16) disposed between an upper section of the ripper (1) and the coupler (3).
  • the invention has four upper shock absorbers (16). Said upper dampers (16) absorb the vibrations generated in the grid (1) to prevent them from reaching the carrier equipment.
  • the additional shock absorber (18) is a spring. As can be seen in Figure 6, the additional shock absorber (18) is arranged in the grille (1) and is connected to a stop (20) attached to the coupler (3) and configured to limit the forward movement of the grille (1) . Also, in this way, when the ripper is lifted with the carrier equipment, the grate (1) does not travel unlimitedly downwards.
  • the coupler (3) comprises a housing.
  • the upper shock absorbers (16), part of the upper section of the grate (1) and an upper section of the stop (20) are arranged inside the housing. In this way these elements are protected.
  • the stop (20) has a tubular body configuration, connected at its upper end to the coupler housing (3) and extending to a cavity, arranged in the recess (1) , where the additional shock absorber (18) is housed.
  • the tubular body comprises at its end that it is housed in the grille (1), a cylindrical projection, which has a larger diameter than the opening of the cavity.
  • the ripper additionally comprises at least one vertical guide (19) arranged in a vertical extension of the coupler (3) that faces a side section of the grid (1).
  • Said at least one vertical guide (19) is linked to said lateral section of the grid (1) such that it directs the movement of the grid (1).
  • the grid (1) always moves in the same longitudinal direction, coinciding with the movement of the connecting rod-counterweight assembly and therefore coinciding with the movement of the attack tip (5).
  • the ripper comprises vertical guides (19)
  • these are also arranged inside the coupler housing. This prevents, for example, the entry of dirt or particles produced during the ripper's work operations that may interfere with the correct movement of the grille (1).
  • the vertical guides (19) face one side of the grate (1) while the cavity in which the additional shock absorber (18) and the widest end of the stop (10) are located are arranged on the other side of the grate ( one).
  • any possible movement that unbalanced the grid (1) on the side where the stop (20) is, will always be compensated by the lateral guides (19).
  • Figure 6 also shows bearings (17), which are preferably bearings, and which are housed in the connecting rod-counterweight assembly (12) (in the element that acts as a counterweight) facing the walls of the receptacle (9 ).
  • bearings (17) facilitate the sliding of the element that acts as a counterweight in the connecting rod-counterweight assembly (12) inside the receptacle (9).

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  • Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Mechanical Engineering (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Physics & Mathematics (AREA)
  • Environmental & Geological Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)

Abstract

L'invention concerne une défonceuse à actionnement linéaire qui est plane et à l'intérieur de laquelle se situe un ensemble d'actionnement (2) avec un vilebrequin (6) et un ensemble bielle-contrepoids (12) relié au vilebrequin (6) et conçu pour se déplacer de manière linéaire le long d'un réceptacle (9) disposé dans une griffe (1). Ledit ensemble d'actionnement permet que la défonceuse se déplace à des fréquences de vibration élevées et permet de maintenir un volume de défonceuse considérablement réduit en raison de son état totalement plat et de la position interne de tous les éléments nécesaires pour son déplacement.
PCT/ES2017/070379 2016-05-31 2017-05-31 Défonceuse à actionnement linéaire Ceased WO2017207852A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ESP201630709 2016-05-31
ES201630709A ES2644886B1 (es) 2016-05-31 2016-05-31 Ripper de accionamiento lineal

Publications (2)

Publication Number Publication Date
WO2017207852A1 true WO2017207852A1 (fr) 2017-12-07
WO2017207852A4 WO2017207852A4 (fr) 2018-02-01

Family

ID=59485369

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/ES2017/070379 Ceased WO2017207852A1 (fr) 2016-05-31 2017-05-31 Défonceuse à actionnement linéaire

Country Status (2)

Country Link
ES (1) ES2644886B1 (fr)
WO (1) WO2017207852A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4257648A (en) * 1979-04-09 1981-03-24 Bodine Albert G Non-resonant cyclic drive system employing rectification of the cyclic output
EP0089140A2 (fr) * 1982-03-01 1983-09-21 Allied Steel & Tractor Products, Inc. Marteau vibrant synchrone
KR101025030B1 (ko) * 2010-09-15 2011-03-25 박정열 무소음 유압 브레이커 이를 이용한 파쇄공법
KR101236510B1 (ko) * 2012-08-27 2013-02-21 주식회사 자브 진동 리퍼의 충격흡수장치
KR101268417B1 (ko) * 2012-07-20 2013-05-28 박철민 중장비용 진동 리퍼
WO2013109085A1 (fr) * 2012-01-19 2013-07-25 Gb Industries Co., Ltd. Amortisseurs de chocs pour une défonceuse à vibrations

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4229044A (en) * 1979-02-12 1980-10-21 Caterpillar Tractor Co. Clevis-mounted impact ripper
DE3883436T2 (de) * 1987-06-17 1993-12-09 Yamada Juki Kk Rotierende Schlagvorrichtung.
FI122299B (fi) * 2010-01-29 2011-11-30 Sandvik Mining & Constr Oy Menetelmä ja järjestely kallioporakoneen poraniskan voitelemiseksi
ES1077883Y (es) * 2012-10-03 2013-01-18 Martinez De Lahidalga Javier Aracama Dispositivo percutor hidraulico para maquinas excavadoras

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4257648A (en) * 1979-04-09 1981-03-24 Bodine Albert G Non-resonant cyclic drive system employing rectification of the cyclic output
EP0089140A2 (fr) * 1982-03-01 1983-09-21 Allied Steel & Tractor Products, Inc. Marteau vibrant synchrone
KR101025030B1 (ko) * 2010-09-15 2011-03-25 박정열 무소음 유압 브레이커 이를 이용한 파쇄공법
WO2013109085A1 (fr) * 2012-01-19 2013-07-25 Gb Industries Co., Ltd. Amortisseurs de chocs pour une défonceuse à vibrations
KR101268417B1 (ko) * 2012-07-20 2013-05-28 박철민 중장비용 진동 리퍼
KR101236510B1 (ko) * 2012-08-27 2013-02-21 주식회사 자브 진동 리퍼의 충격흡수장치

Also Published As

Publication number Publication date
ES2644886A1 (es) 2017-11-30
WO2017207852A4 (fr) 2018-02-01
ES2644886B1 (es) 2018-09-13

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