EP0411348A1 - Méthode et dispositif pour compacter le sol - Google Patents

Méthode et dispositif pour compacter le sol Download PDF

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Publication number
EP0411348A1
EP0411348A1 EP90113072A EP90113072A EP0411348A1 EP 0411348 A1 EP0411348 A1 EP 0411348A1 EP 90113072 A EP90113072 A EP 90113072A EP 90113072 A EP90113072 A EP 90113072A EP 0411348 A1 EP0411348 A1 EP 0411348A1
Authority
EP
European Patent Office
Prior art keywords
inertial
pressure
soil
force
bodies
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.)
Withdrawn
Application number
EP90113072A
Other languages
German (de)
English (en)
Inventor
Hans Ulrich Leibundgut
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.)
AMMANN-DUOMAT VERDICHTUNG AG
Original Assignee
AMMANN-DUOMAT VERDICHTUNG AG
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 CH287589A external-priority patent/CH679051A5/de
Priority claimed from CH287489A external-priority patent/CH678637A5/de
Application filed by AMMANN-DUOMAT VERDICHTUNG AG filed Critical AMMANN-DUOMAT VERDICHTUNG AG
Publication of EP0411348A1 publication Critical patent/EP0411348A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
    • B06B1/16—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving rotary unbalanced masses
    • B06B1/161—Adjustable systems, i.e. where amplitude or direction of frequency of vibration can be varied
    • B06B1/162—Making use of masses with adjustable amount of eccentricity
    • 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
    • E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
    • E01C19/22—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for consolidating or finishing laid-down unset materials
    • E01C19/23—Rollers therefor; Such rollers usable also for compacting soil
    • E01C19/28—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows
    • E01C19/286—Vibration or impact-imparting means; Arrangement, mounting or adjustment thereof; Construction or mounting of the rolling elements, transmission or drive thereto, e.g. to vibrator mounted inside the roll

Definitions

  • the invention relates to a method for soil compaction, in particular in earthworks and road construction, according to the preamble of patent claim 1 and a soil compaction device for carrying out the method according to the preamble of patent claim 10.
  • Devices of this type are known from DE-OS 1 634 474, AT-PS 250 423, US-PS 4,105,356, DE-PS 1 111 107 and DE-OS 1 634 246.
  • one or more rotating inertial bodies act or act periodically on a pressure-exerting member which, on account of its vibrational vibrations, compresses the ground beneath it when it rolls over or slides over it.
  • the compacting effect on the soil depends on the one hand on the vibrati onskraft and on the other hand from the vibration deflection of the pressure exerting member during its vibrations.
  • the deflection of the pressure exerting member and the vibration force or vibration frequency are coupled to one another and cannot be separated from one another.
  • the object of the invention is to provide a method and a device for soil compaction, in which or in which the periodic vibration deflection of the pressure exerting member can be changed independently of the vibration frequency and / or the vibration force.
  • a method or a device for soil compaction in which or with which advantageously large vibration forces and a low weight of the pressure-exerting member can be used, and wherein the inertial force directed in a given spatial direction, preferably towards the ground, can be set greater than in the opposite direction , is described by the subject matter of claims 4 and 5 or 10 to 12. Furthermore, during operation, the resulting vibration force acting on the soil to be compacted can be changed without changing the vibration frequency by the subject matter of claims 6 and 13, respectively. The change in the magnitude of the vibration force during the compression operation and the generation of a vibration force that acts strongly in different directions is the subject of claims 1 to 6 and 7 to 13, respectively.
  • the vibration force, its vibration frequency and the vibration deflection of the pressure exerting member relative to the ground are free and independently adjustable.
  • the effective mass of the pressure exerting member mentioned in the claims which in the detailed description below is a roller body of a road roller, is the sum of those masses which are rigidly and / or articulatedly connected to the pressure exerting member and are synchronized by the resulting inertial forces of the moving inertial masses and are excited with the pressure exerting organ without a time shift of the deflection maxima.
  • the effective mass in the example described below is therefore the sum of the mass of the pressure exerting element plus its mounting and the associated brackets plus a partial mass of the entire road roller, which is greatly reduced by vibration-damping elements and places a load on the pressure exerting element, plus a percentage of the additional masses between the center of gravity of the pressure exerting member and an almost non-vibrating part of the machine frame are movable.
  • the additional masses act between zero and one hundred percent of their total weight.
  • Vibration frequency, vibration force and vibration deflection denote the frequency or the frequency mixture, the force and the deflection of the pressure exerting element with which it acts on the soil to be compacted due to the excitation by the resulting inertial force.
  • Unbalanced inertial bodies are understood to be inertial bodies with an eccentric mass distribution with respect to their axis of rotation, only the centrifugal force caused by the unbalance acting as a so-called inertial force. Only the force acting on the pressure exerting member is understood as an inertial force.
  • the vibratory force transmitted from the pressure exerting member in the direction of the ground can be directed so that it takes any acute angle to the vertical on the floor surface.
  • the pressure exerting element shown in FIG. 1 is a hollow cylindrical roller body 1 , also called a bandage, of a road roller (not shown) and lies on a soil 3 to be compacted.
  • the roller body 1 is fastened to a frame part 7 , which is connected to the chassis of the road roller, not shown, by means of two damping elements 5 , which are only shown schematically, by means of a bearing holder designed as a yoke 4 .
  • a bearing holder designed as a yoke 4
  • one or more roller bodies 1 which can also be driven, are present.
  • the weight of the road roller is transferred to each frame part 7 per roller body 1 .
  • the inertial body 12 is designed as a hollow cylinder with an eccentric thickening 15 along a surface line.
  • the length of the hollow cylinder is smaller by a tolerance than the inner length of the hollow cylinder of the roller body 1 .
  • the inertial body 12 is mounted coaxially to the geometrical axis 20 of the roller body 1 with two bearings 22 and 23 within a flange 19 and 21 on each end face of the roller body 1 .
  • the two flanges 19 and 21 are each supported by a roller bearing 24a and 24b in the yoke 4 .
  • the inertial body 11 is plate-shaped and is eccentrically fastened to a shaft 27 lying in the geometric axis 20 .
  • the length of the plate 25 is smaller by a tolerance than the inner length of the inertial body 12 .
  • the inertial body 11 is rotatable within the inertial body 12 and this within the roller body 1 .
  • the shaft 27 is mounted with two bearings 29 and 30 in the end faces of the hollow cylinder of the inertial body 12 and is driven within the hollow shaft piece 17 together with the latter via a gear 32 by a drive 33 .
  • the gear 32 rotates the inertial body 11 at twice the speed of the inertial body 12 .
  • the value of the simple number of revolutions results from the desired soil compaction, which mainly depends on the nature of the soil 3 . Since the mass distribution of the inertial bodies 11 and 12 , as shown in Figure 2 , is eccentric, this results in circumferential forces (centrifugal forces) to the shaft 27 , which via the bearings 22 , 23 , 29 and 30 as the resulting force K c inertial force) Roller body 1 act.
  • the timing of the rotational movements of the two inertial bodies 11 and 12 is set by the gear 32 so that the plate 25 at every second revolution and the thickening 15 at every revolution on it Point closest to the ground lie on a straight line through axis 20 .
  • the eccentric mass distribution of the two inertial bodies 11 and 12 is now selected so that the centrifugal force K a of the inertial body 11 is the same at a standard speed as the centrifugal force K b of the inertial body 12 at twice the standard speed.
  • the mass distributions required for this, as well as their respective eccentric distance from the axis 20, can be determined using the laws of technical mechanics.
  • the two centrifugal forces K a and K b of the inertial bodies 11 and 12 overlap, as shown in FIG. 3 , with a maximum resulting force K c directed towards the ground and two approximately half as large resulting forces K c directed away from it per period.
  • the resulting force K c directed away from the bottom 3 can be chosen so large that it is smaller than the weight force (effective mass of the pressure exerting member) of the sum of the weights of the roller body 1 , the yoke 4 and the associated bearings 22 up to a tolerance , 23 , 24a , 24b , 29 and 30 , and a weight force of the road roller, which is greatly reduced by the damping elements 5 , but without the inertial bodies 11 and 12 , without fear of the roller body 1 being lifted off the ground 3 .
  • the toothed belt 38 is deflected via two rollers 39a and 39b fastened to the frame parts 7 , one additional body 37a being connected to one part of the toothed belt 38 and the other additional body 37b being connected to the deflected part of the toothed belt 38 .
  • the roller 39a is driven via a further toothed belt 40 by a schematically shown adjusting device 41 .
  • the additional bodies 37a and 37b are designed such that they bear with their entire weight on the guide rails 35a and 35b ; the toothed belt 38 is used only for horizontal displacement. They are attached to the toothed belt 38 so that their movement takes place in opposite directions.
  • the guide rails 35a and 35b are designed so that they do not vibrate naturally during vibration operation.
  • the additional bodies 37a and 37b are pushed against the joints 36a and 36d by means of the adjusting unit 41 , then they act on the roller body 1 only with a negligible weight, whereas they act with their entire weight as an additional mass when they are struck on the joints 36b and 36c . Between these two extremes, all values can be set via the position of the additional bodies 37a and 37b on the guide rails 35a and 35b .
  • the deflection is inversely proportional to the effective mass of the roller body 1 (pressure exerting element) and directly proportional to the resulting centrifugal force K c (inertial force) of the eccentric masses 15 and 25 .
  • the effective mass of the roller body 1 results from the sum of the masses of the roller body 1 , the yoke 4 , the support 34 , twice half the mass of the guide rail nen 35a and 35b and the percentage by weight acting on the roller body 1 of the additional bodies 37a and 37b .
  • the fastening of the guide rails 35a and 35b can be selected such that they can also be moved into the space outside the frame parts 7 . If the additional bodies 37a and 37b are located outside the frame parts 7 , the effective mass of the pressure application member 1 is reduced.
  • two piston-cylinder units 43a and 43b can also be used, an additional mass 44a or 44b on each the piston 45a or 45b is attached.
  • the pistons 45a and 45b are each moved in a cylinder 46a and 46b by means of hydraulic fluid, which are periodically pressed back and forth by a hydraulic control device 52 through two lines 47/48 and 49/50 .
  • actio reactio, in the case of a piston 45a or 45b accelerated upward, the pumped hydraulic oil results in a downward counterforce on the lower end face 53a or 53b of the cylinder 46a or 46b .
  • the hydraulic fluid located in the upper part of the cylinder 46a or 46b above the piston 45a or 45b can flow freely through the hydraulic line 48 or 50 , which results in only a small counterforce which is due to the frictional resistance in the tubes 48 and 50 .
  • the force on the lower end face 53a or 53b is transmitted via the cylinder 46a or 46b to the roller body 1 connected to it.
  • the forces are superimposed analogously to the rotating eccentric masses 15 (thickening) and 25 (plate) of the inertial bodies 11 and 12 . If the additional mass 44b is only half as large as the additional mass 44b and its oscillation frequency
  • the image shown in FIG. 3 is twice as large as that of the additional mass 44a .
  • the additional masses 44a and 44b can also be removed from the respective piston 45a or 45b and moved through the piston 45a or 45b via a connecting rod (not shown) and a lever arm (not shown). This allows the direction and the size of the force to be freely selected.
  • any number of moving masses can be used, depending on the space requirement, which masses with different numbers of revolutions, which are integer multiples of a desired basic vibration of the pressure exerting element 1 .
  • the optimal number of revolutions, as well as their assignments, can be determined with known mathematical approximation methods, such as e.g. B. an "approximate harmonic analysis", presented in Bronstein-Semendjajew, “Taschenbuch der Mathematik", BG Teubner Verlagsgesellschaft, Leipzig, 1963, page 480 ff.
  • the calculation is infinite Lich long trigonometric rows, which can be broken off after the first links with sufficient accuracy for the desired form of movement.
  • a plate or the like can also be used as the pressure exerting element.
  • an arbitrary angle can also be selected.
  • the angle of the maximum force effect only depends on the angle at which the forces of the individual vibrations are superimposed. This angle can be set via the gear 32 .
  • the gear part 62 has three meshing gears 62a , 62b and 62c .
  • the axes of the gear wheels 62a and 62c , as well as the axes 65 and 76 lie on a straight line and the axis of the gear wheel 62b intersects this straight line.
  • the axis 76 of the gearwheel 62c is connected to an eccentric mass distribution 75 by an inertial body constructed analogously to the inertial body 11 and can be rotated by it.
  • the toothed belt pulley 63 drives a toothed belt pulley 64 via a toothed belt 66 a shaft 67 moves a gear 69 which meshes with a gear 71 .
  • the gearwheel 71 is connected to an inertial body with the eccentric mass distribution 73 which is configured analogously to the inertial body 12 .
  • the axis of gear 62b is fixed, but can be rotated about axis 76 . If there is a rotation, the two eccentric masses 73 and 75 of the inertial bodies, ie their center of gravity are rotated towards or away from one another depending on the direction of rotation, ie their central angle is reduced or enlarged.
  • the resulting eccentrically acting centrifugal force thereby decreases or increases in the limits between the sum and the difference of the centrifugal forces of the individual eccentric mass distributions 73 and 75 , as can easily be seen due to the laws of technical mechanics.
  • the central angle of the two eccentric mass distributions 73 and 75 can be adjusted continuously or stepwise in the entire range between 0 ° according to a maximum resulting centrifugal force and 180 ° according to a minimal or no resulting centrifugal force.
  • the adjustment is possible during operation, ie during the rotation of the two inertial bodies with the eccentric masses 73 and 75 .
  • the deflection of the roller body 1 (pressure exerting member) can thus be changed once by adjusting the eccentricity, as already described above, and by moving the additional bodies 37a and 37b . Since a change in the eccentricity changes the amplitude, this change can be reversed by moving the additional bodies 37a and 37b .
  • the deflection of the pressure-exerting member can be adjusted relative to the floor by changing the mass.
  • the effective centrifugal forces can be changed by adjusting the eccentric center of gravity of a plurality of inertial bodies against one another or the center of gravity of the inertial body with respect to its axis of rotation by means of a planetary gear.
  • the method according to the invention increases the deflection of the pressure exerting element 1 that can be used for compaction and reduces the total drive power of the road roller with the same compaction effect. Not only can vertical forces be applied to the floor, but forces at any angle.
  • the magnitude of the vibration force, the direction of the maximum acting vibration force, its vibration frequency and its amplitude can be set independently of one another, as well as a vibration force acting in different directions with different strengths.
  • soil compaction can be optimally achieved depending on the nature of the soil.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Road Paving Machines (AREA)
  • Soil Working Implements (AREA)
  • Catching Or Destruction (AREA)
  • Sink And Installation For Waste Water (AREA)
  • Earth Drilling (AREA)
EP90113072A 1989-08-03 1990-07-09 Méthode et dispositif pour compacter le sol Withdrawn EP0411348A1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
CH2873/89 1989-08-03
CH2875/89 1989-08-03
CH287389 1989-08-03
CH2874/89 1989-08-03
CH287589A CH679051A5 (en) 1989-08-03 1989-08-03 Ground compacting for earth working and road construction
CH287489A CH678637A5 (en) 1989-08-03 1989-08-03 Ground compacting for earth working and road construction

Publications (1)

Publication Number Publication Date
EP0411348A1 true EP0411348A1 (fr) 1991-02-06

Family

ID=27173986

Family Applications (2)

Application Number Title Priority Date Filing Date
EP90113072A Withdrawn EP0411348A1 (fr) 1989-08-03 1990-07-09 Méthode et dispositif pour compacter le sol
EP90113073A Expired - Lifetime EP0411349B1 (fr) 1989-08-03 1990-07-09 Dispositif pour compacter le sol

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP90113073A Expired - Lifetime EP0411349B1 (fr) 1989-08-03 1990-07-09 Dispositif pour compacter le sol

Country Status (3)

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EP (2) EP0411348A1 (fr)
AT (1) ATE123319T1 (fr)
DE (1) DE59009174D1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993015373A1 (fr) * 1992-01-22 1993-08-05 Udo Winter Procede et dispositif de deminage pour eliminer des mines antichars adaptees a certains types de chars
CN110927257A (zh) * 2019-11-14 2020-03-27 深圳市土地投资开发中心 检测基础飞行区道面影响区压实质量的检测系统及方法

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6769838B2 (en) 2001-10-31 2004-08-03 Caterpillar Paving Products Inc Variable vibratory mechanism
DE102008008802B4 (de) * 2008-02-12 2011-12-15 Ammann Verdichtung Gmbh Bodenverdichtungsgerät mit einem Schwingungserreger
EP2710189B1 (fr) * 2011-05-20 2016-08-24 Volvo Construction Equipment AB Compacteur de surface et procédé de son fonctionnement

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1111107B (de) * 1955-03-14 1961-07-13 Dingler Werke Ag Vibrationswalze zur Verdichtung von Boeden und sonstigen Schuettmassen
AT250423B (de) * 1963-10-17 1966-11-10 Buckau Wolf Maschf R Selbstbewegliche Verdichtungsmaschine
DE1634246A1 (de) * 1965-06-08 1970-07-16 Bopparder Maschb Gmbh Vibrationswalze
DE1634474A1 (de) * 1966-02-24 1970-08-06 Buckau Wolf Maschf R Ruettelwalze
US3721129A (en) * 1971-08-13 1973-03-20 Ato Inc Eccentric system for vibratory earth compactor
US4105356A (en) * 1977-05-19 1978-08-08 Koehring Corporation Vibratory roller

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH425648A (de) * 1963-04-19 1966-11-30 Abg Werke Gmbh Vibrationsgerät zur Verdichtung von geschüttetem Boden und sonstigen Materialien
CS244465B1 (en) * 1984-02-23 1986-07-17 Lubos Dolezal Vibrations exciter with continuous variation of eccentric moment
AT389723B (de) * 1986-03-27 1990-01-25 Voest Alpine Ag Einrichtung zur erzeugung von vibrationen

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1111107B (de) * 1955-03-14 1961-07-13 Dingler Werke Ag Vibrationswalze zur Verdichtung von Boeden und sonstigen Schuettmassen
AT250423B (de) * 1963-10-17 1966-11-10 Buckau Wolf Maschf R Selbstbewegliche Verdichtungsmaschine
DE1634246A1 (de) * 1965-06-08 1970-07-16 Bopparder Maschb Gmbh Vibrationswalze
DE1634474A1 (de) * 1966-02-24 1970-08-06 Buckau Wolf Maschf R Ruettelwalze
US3721129A (en) * 1971-08-13 1973-03-20 Ato Inc Eccentric system for vibratory earth compactor
US4105356A (en) * 1977-05-19 1978-08-08 Koehring Corporation Vibratory roller

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993015373A1 (fr) * 1992-01-22 1993-08-05 Udo Winter Procede et dispositif de deminage pour eliminer des mines antichars adaptees a certains types de chars
CN110927257A (zh) * 2019-11-14 2020-03-27 深圳市土地投资开发中心 检测基础飞行区道面影响区压实质量的检测系统及方法

Also Published As

Publication number Publication date
EP0411349B1 (fr) 1995-05-31
EP0411349A1 (fr) 1991-02-06
DE59009174D1 (de) 1995-07-06
ATE123319T1 (de) 1995-06-15

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