EP0780164A2 - Vibrateur à action dirigée - Google Patents

Vibrateur à action dirigée Download PDF

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Publication number
EP0780164A2
EP0780164A2 EP96120175A EP96120175A EP0780164A2 EP 0780164 A2 EP0780164 A2 EP 0780164A2 EP 96120175 A EP96120175 A EP 96120175A EP 96120175 A EP96120175 A EP 96120175A EP 0780164 A2 EP0780164 A2 EP 0780164A2
Authority
EP
European Patent Office
Prior art keywords
unbalanced
shaft
vibration exciter
unbalance
shafts
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Withdrawn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
EP96120175A
Other languages
German (de)
English (en)
Other versions
EP0780164A3 (fr
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.)
Wacker Construction Equipment AG
Original Assignee
Wacker Werke GmbH and Co KG
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 Wacker Werke GmbH and Co KG filed Critical Wacker Werke GmbH and Co KG
Publication of EP0780164A2 publication Critical patent/EP0780164A2/fr
Publication of EP0780164A3 publication Critical patent/EP0780164A3/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Withdrawn legal-status Critical Current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
    • B06B1/166—Where the phase-angle of masses mounted on counter-rotating shafts can be varied, e.g. variation of the vibration phase
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18344—Unbalanced weights
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18544—Rotary to gyratory
    • Y10T74/18552—Unbalanced weight

Definitions

  • the invention relates to a vibration exciter according to the introductory part of patent claim 1.
  • Vibrations of this type are e.g. known from DE 38 06 897 A1.
  • the unbalance shafts are coupled by two meshing gears, one of which is mounted on the one unbalanced shaft and the other on the other unbalanced shaft concentrically to the respective axis of rotation.
  • the change in the mutual phase position of the unbalanced shafts positively coupled via the gear wheels can be changed in a controlled manner in that at least one of the two gear wheels can be adjusted in its angular position in a controlled manner with respect to its shaft.
  • the known vibration exciters are usually driven by means of a drive motor which acts on a gear or a pulley via a transmission which is fastened to one end of one of the two unbalanced shafts which is led out of the vibrator housing.
  • the phase position of the two unbalanced shafts in relation to one another can be changed by means of a control mechanism in such a way that the vector of the directional vibration generated by the vibration exciter can be adjusted in a plane parallel to the direction of movement over an angular range with respect to the center of gravity of the compacting device standing on a flat floor, in which it is more or less inclined with respect to the center of gravity in or against the direction of movement or extends parallel to the center of gravity.
  • the centrifugal weights exert not only the propulsive force but also a tilting moment on the vibrator housing and the compression device connected to it, which, however, at the known devices according to DE 38 06 897 A1 because of the desired distance between the two unbalanced shafts is vehemently small and therefore has little influence on the movement behavior of the compression device equipped with the vibration exciter.
  • the invention is based on the finding that the effectiveness of the compacting device can be significantly improved in cohesive soils by an increased tilting moment, because this results in a pronounced peeling effect which considerably increases the advance and thus the off-road capability of the compacting device, in particular a vibrating plate, in the cohesive soil .
  • a first part of the invention is therefore to provide a vibration exciter of the type according to the preamble of claim 1, which has an increased tilting moment especially in the lead, but is nevertheless characterized by a low overall height comparable to the known vibration exciters.
  • a second part of the invention is to design vibration exciters of the type according to DE 38 06 897 A1 so that the structural design of the phase adjustment mechanism is largely independent of the structural design of the unbalances.
  • one of the two intermediate shafts could now be used for the installation of the adjusting mechanism for adjusting the phase position between the unbalances instead of an unbalanced shaft, so that the unbalanced shaft are no longer forcibly installed and there is therefore sufficient space available for special designs on them. so that they e.g. B. according to claims 7-13 can be equipped with unbalance weights without difficulty, which are divided and whose parts are adjustable in relation to each other to change the m.r value frequency-dependent automatically or parameter-dependent.
  • the further subclaims relate to further preferred configurations of the vibration exciter according to claim 1.
  • a device for changing the phase position of two unbalances in which the unbalances are arranged at a relatively large mutual distance on the ground contact plate of a vibrator and are driven in opposite directions by means of toothed belts attached to them by means of a toothed belt.
  • the toothed belt is guided over four deflection wheels, two of which can be shifted in opposite, mutually parallel directions in such a way that the phase shift of the unbalances in relation to one another is adjusted by the associated displacement of the toothed belt.
  • a drive for generating vibrations of a spring-loaded device in particular a sieve, in which two at their ends located outside a housing with unbalanced masses, parallel to each other in the housing mounted shafts via in the housing gears arranged on them and two intermediate gears inserted between them and intermeshing intermeshing gears are coupled with one another in opposite directions.
  • the axes of rotation of the unbalanced shafts and the intermediate gearwheels lie in the same plane, and the gearwheels are supported in the housing by means of axle journals.
  • the distance between the unbalanced shafts is increased for the purpose of being able to use unbalances that are at a large radial distance from the axes of rotation of the shafts carrying them, so that large centrifugal forces are generated, even at relatively low speeds, such as this is particularly necessary with seven.
  • the intermediate gears and their bearings are used exclusively for the transmission of force between the shafts occupied by the unbalances and have only a sufficient length in the direction of the axis of rotation for the gears to be supported against tilting and for a perfect transmission of force.
  • the vibration exciter shown in different variants in the drawing has, in all embodiments, a vibrator housing 1 which surrounds the interior with the unbalanced shafts 3a, 3b on all sides, in which the two unbalanced shafts 3a, 3b, which in the usual way have at least one unbalanced weight with respect to the axis of rotation 3c , are mounted parallel to each other by means of roller bearings 2.
  • two intermediate shafts 4 and 5 are rotatably mounted in the vibrator housing 1 by means of further roller bearings 6 with axes of rotation 4c, 5c parallel to the axes of rotation 3c of the unbalanced shafts 3a, 3b.
  • the intermediate shafts 4 and 5 are arranged in the vibrator housing 1 so that their respective axes of rotation 4c and 5c are each in the same plane as the axes of rotation 3c of the unbalanced shafts 3a, 3b.
  • this is not an absolute requirement. Rather, the shafts do not necessarily have to lie in a common plane in view of the machine-specific center distances of the intermediate shafts 4 and 5.
  • the unbalanced shaft 3a and the intermediate shaft 4 are directly coupled to each other via a gear 7 and 8, which is coaxially fixed on them.
  • the gearwheel 8 on the intermediate shaft 4 further meshes with a gearwheel 9 seated on the intermediate shaft 5 in a rotationally fixed manner.
  • a further gearwheel 10 is arranged on the intermediate shaft 5 coaxially with its axis of rotation 5c and has a hub 10a enclosing the intermediate shaft 5 with a sliding fit.
  • a spiral double groove 10b is worked into the inner wall of this hub 10a, in each of which a pin 11 engages in the sections offset from each other by 180 °, which pin projects somewhat from the intermediate shaft 5 on both sides through an axial longitudinal slot 5a in the intermediate shaft 5.
  • the pin 11 extends perpendicular to the axis of rotation 5c of the intermediate shaft 5 and passes through an actuating slider 12 which is axially slidable in the intermediate shaft 5 in the form of a hollow shaft and can be adjusted in a controlled manner by means of an actuating member 13.
  • the actuator 13 is axially fixed but rotatably connected to the slide 12 so that the intermediate shaft 5 can rotate with the slide 12 without taking the actuator 13 with it.
  • the actuating member 13 runs into a piston 14, which is sealed in a cylinder 15 and is guided parallel to the axis of rotation 5c and can be acted upon from the outside with pressure medium D in a controlled manner on the side facing away from the slider 12.
  • the piston 14 When the piston 14 is pressurized in the position shown in Fig. 1, it shifts to the viewer of Fig. 1 to the left, which in turn displaces the pin 11 in the direction of the axis of rotation 5c, with the result that the Angular position of the gear 10 with respect to the intermediate shaft 5 is changed. If the piston 14 is relieved of the pressure medium, it moves back to its starting position under the restoring force exerted on it by the slider.
  • the gearwheel 10 meshes directly with a further gearwheel 16, which is mounted in a rotationally fixed manner on the other unbalanced shaft 3b concentrically with its axis of rotation 3c.
  • the intermediate shaft 4 can be driven by means of a hydraulic motor 17, which is coupled to the intermediate shaft 4 on the left end side of the intermediate shaft 4 for the viewer.
  • the hydraulic motor 17 can be pressurized with pressure medium via pressure medium connections 18 and drives the intermediate shaft 4 in one or the other direction of rotation depending on the direction of the pressure medium flowing through it on.
  • the rotating intermediate shaft 4 sets the unbalanced shaft 3a on the one hand via the gear 8 and the gear 7 and the other intermediate shaft 5 rotates via the gear 8 and the gear 9 and this in turn via the gear 10 and the gear 16 the other Unbalanced shaft 3b.
  • FIG. 2 shows a variant of the vibration exciter according to FIG. 1, in which the hydraulic motor 17 ′ which drives the vibration exciter does not act on the intermediate shaft 4 but on the unbalanced shaft 3a.
  • the design of the vibration exciter according to FIGS. 1 and 2 has the advantage that the two unbalanced shafts 3a and 3b do not need to include a phase adjustment mechanism and are therefore free for the installation of other adjustment mechanisms, in particular for those shown in FIGS. 3 to 5 Devices for changing the mr value of the unbalanced shafts 3a 'and 3b'.
  • two flyweights 20b are seated on the unbalanced shaft 3b 'in a rotationally fixed manner and, between them, an unbalanced part 20a which can be rotated in its angular position relative to the fixed unbalanced parts 20b is rotatable with a sliding fit.
  • the unbalance part 20a is adjustable relative to the unbalanced shaft 3b 'by means of a mechanism which is similar to that by means of which the gear wheel hub 10a is adjustable relative to the intermediate shaft 5 and which functions like this.
  • a spiral double groove 22 is also machined into the inner wall of the adjustable unbalance part 20a, in each of which a pin 24 engages in the sections offset from one another by 180 °, which pin passes through an axial longitudinal slot 23 in the unbalanced shaft 3b ' something protrudes from this on both sides.
  • the pin 24 extends perpendicular to the axis of rotation of the unbalanced shaft 3b 'and passes through an actuating slide 28 which is axially slidable in the unbalanced shaft 3b' and which is designed as a hollow shaft and can be adjusted in a controlled manner by means of an actuating member 25.
  • the actuator 25 is axially fixed but rotatably connected to the slider 28 so that the unbalanced shaft 2b 'can rotate with the slider 28 without the Take actuator 25 with you.
  • the actuating member 25 ends in a piston 26, which is sealed in a cylinder 27 and is guided parallel to the axis of rotation of the unbalanced shaft 3b 'and can be acted upon with pressure medium D in a controlled manner on the side facing away from the slide 28.
  • the resulting total unbalance can be continuously adjusted between a minimum value and a maximum value.
  • the m.r value can also be continuously changed in the unbalanced shaft 3a', which is not shown, the adjustment of both unbalanced shafts taking place in synchronism. 3 are thus freely selectable in terms of their m.r value, and the m.r value can also be used to optimally control the tilting moment mentioned above in order to achieve the desired peeling effect.
  • the unbalanced mass consists of two fixed parts 20b 'and an adjustable unbalanced part 20a' arranged between them, which, however, unlike the embodiment according to FIG. 3, cannot be rotated against the fixed unbalanced parts 20b but in the radial direction is movable.
  • the adjustable Unbalance part 20a encloses the unbalanced shaft 3b 'provided with mutually parallel sliding surfaces 32 as a U-piece and is held in the starting position shown in FIG.
  • a plate spring assembly 30 on the unbalanced shaft 3b'.
  • This plate spring assembly 30 surrounds a clamping screw 31 which slidably passes through the unbalanced shaft 3b 'and is screwed into a threaded bore in the crosspiece of the adjustable unbalanced member 20a.
  • the adjustable unbalanced part 20a exerts a growing, radially directed force on the screw 31, which in turn transmits this to the end of the spring assembly 30 facing away from the unbalanced shaft 3b'.
  • the spring assembly 30 is compressed more and more with increasing rotational speed, which is caused by a displacement of the adjustable unbalance part 20a radially outward from the unbalanced shaft 3b 'and thus a change in the resulting total unbalance, that is to say a change in the mr value , goes along. 4 and 5, the mr value is reduced with increasing speed, which is also the aim in the embodiment according to FIG. 3.
  • the m.r value of the unbalanced shaft 3a ' can be changed in the same way as for the unbalanced shaft 3b'.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
EP96120175A 1995-12-18 1996-12-17 Vibrateur à action dirigée Withdrawn EP0780164A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19547043A DE19547043C2 (de) 1995-12-18 1995-12-18 Schwingungserreger zum Erzeugen einer gerichteten Schwingung
DE19547043 1995-12-18

Publications (2)

Publication Number Publication Date
EP0780164A2 true EP0780164A2 (fr) 1997-06-25
EP0780164A3 EP0780164A3 (fr) 1999-03-03

Family

ID=7780324

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96120175A Withdrawn EP0780164A3 (fr) 1995-12-18 1996-12-17 Vibrateur à action dirigée

Country Status (4)

Country Link
US (1) US5818135A (fr)
EP (1) EP0780164A3 (fr)
JP (1) JPH09206683A (fr)
DE (1) DE19547043C2 (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29723617U1 (de) 1997-05-27 1998-11-26 AMMANN Verdichtung GmbH, 53773 Hennef Vibrationsplatte zur Verdichtung des Bodens
US5988297A (en) * 1998-03-24 1999-11-23 Hydraulic Power Systems, Inc. Variable eccentric vibratory hammer
DE29805361U1 (de) 1998-03-25 1998-06-04 Bomag GmbH, 56154 Boppard Verdichtungsvorrichtung mit Vibrationsantrieb
US6224293B1 (en) 1999-04-19 2001-05-01 Compaction America, Inc. Variable amplitude vibration generator for compaction machine
DE20008496U1 (de) 2000-05-11 2000-09-21 Rammax Maschinenbau GmbH, 72555 Metzingen Vorrichtung zur Verdichtung
DE10038206C2 (de) * 2000-08-04 2002-09-26 Wacker Werke Kg Regelbarer Schwingungserreger
DE10147957B4 (de) * 2001-09-28 2006-11-02 Wacker Construction Equipment Ag Schwingungserreger für eine Bodenverdichtungsvorrichtung
US6769838B2 (en) 2001-10-31 2004-08-03 Caterpillar Paving Products Inc Variable vibratory mechanism
DE10306791A1 (de) * 2003-02-18 2004-08-26 Bomag Gmbh Schwingungserregervorrichtung
US7165469B2 (en) 2003-04-10 2007-01-23 M-B-W Inc. Shift rod piston seal arrangement for a vibratory plate compactor
US7705500B2 (en) * 2007-01-17 2010-04-27 Brookstone Purchasing, Inc. Vibration apparatus and motor assembly therefore
DE102012025376A1 (de) * 2012-12-27 2014-07-03 Wacker Neuson Produktion GmbH & Co. KG Schwingungserreger für lenkbare bodenverdichtungsvorrichtungen
DE102012025378A1 (de) * 2012-12-27 2014-07-03 Wacker Neuson Produktion GmbH & Co. KG Schwingungserreger für bodenverdichtungsvorrichtungen
USD770977S1 (en) * 2014-09-26 2016-11-08 Chuan Liang Industrial Co., Ltd. Vibration generator with clamping fixture

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0070343A1 (fr) * 1981-07-18 1983-01-26 Losenhausen Maschinenbau AG& Co Kommanditgesellschaft Vibrateur à masse déséquilibrée en fonction de la vitesse de rotation
DE3806897A1 (de) * 1988-03-03 1989-09-14 Wacker Werke Kg Schwingungserreger
EP0467758A1 (fr) * 1990-07-20 1992-01-22 Procedes Techniques De Construction Vibrateur multi-fréquence
EP0473449A1 (fr) * 1990-08-30 1992-03-04 Kencho Kobe Co., Ltd. Générateur de vibrations
DE4118069A1 (de) * 1991-06-01 1992-12-03 Udo Halbrock Vibrator fuer eine vibrationsramme

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1565988A (fr) * 1967-05-27 1969-05-02
SE365433B (fr) * 1972-07-07 1974-03-25 Morgaardshammar Ab
FR2311596A1 (fr) * 1975-04-23 1976-12-17 Procedes Tech Const Perfectionnement aux appareils d'enfoncement ou d'arrachage dits vibrofonceurs

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0070343A1 (fr) * 1981-07-18 1983-01-26 Losenhausen Maschinenbau AG& Co Kommanditgesellschaft Vibrateur à masse déséquilibrée en fonction de la vitesse de rotation
DE3806897A1 (de) * 1988-03-03 1989-09-14 Wacker Werke Kg Schwingungserreger
EP0467758A1 (fr) * 1990-07-20 1992-01-22 Procedes Techniques De Construction Vibrateur multi-fréquence
EP0473449A1 (fr) * 1990-08-30 1992-03-04 Kencho Kobe Co., Ltd. Générateur de vibrations
DE4118069A1 (de) * 1991-06-01 1992-12-03 Udo Halbrock Vibrator fuer eine vibrationsramme

Also Published As

Publication number Publication date
US5818135A (en) 1998-10-06
JPH09206683A (ja) 1997-08-12
DE19547043A1 (de) 1997-06-19
EP0780164A3 (fr) 1999-03-03
DE19547043C2 (de) 1997-10-02

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