JP3827529B2 - A vibration compression device that compresses the molding material in the molding box using two unbalanced weights - Google Patents

A vibration compression device that compresses the molding material in the molding box using two unbalanced weights Download PDF

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JP3827529B2
JP3827529B2 JP2000540947A JP2000540947A JP3827529B2 JP 3827529 B2 JP3827529 B2 JP 3827529B2 JP 2000540947 A JP2000540947 A JP 2000540947A JP 2000540947 A JP2000540947 A JP 2000540947A JP 3827529 B2 JP3827529 B2 JP 3827529B2
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Prior art keywords
molding
unbalanced
unbalanced weight
centrifugal force
adjusting sleeve
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JP2002509799A (en
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シラー・グンター
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シュロッサー−プファイファー・ゲゼルシャフト・ミト・べシュレンクテル・ハフツング
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    • 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
    • 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

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Processing Of Solid Wastes (AREA)
  • Press Drives And Press Lines (AREA)
  • Moulds For Moulding Plastics Or The Like (AREA)
  • Dry Formation Of Fiberboard And The Like (AREA)
  • Manufacturing Of Tubular Articles Or Embedded Moulded Articles (AREA)
  • Casting Or Compression Moulding Of Plastics Or The Like (AREA)

Abstract

The invention relates to a vibration compression system for compressing and shaping molding materials into shaped bodies having a circumference and a length. Said molding materials are shaped in mold recesses of molding boxes. An outer unbalanced body (1) and an inner unbalanced body (2) having the same kinetic momentum are arranged one inside the another in a sleeve-like manner. The centers of gravity of both unbalanced bodies (1, 2) lie in a rotational plane. An adjusting bushing (7) permits the angular position of the centers of gravity to vary in relation to one another, and the shaft (3) is not subjected to stresses caused by bending due to the centrifugal force of the unbalanced bodies (1, 2).

Description

【０００１】
【発明の属する技術分野】
この発明は、請求項１の上位概念により、成形箱の成形みぞ内の成形材料を成形体に圧縮成形する振動圧縮装置に関する。
【０００２】
【従来の技術】
成形箱の成形みぞ内の成形材料を成形体に圧縮成形する振動圧縮装置は複数の不平衡重錘体から成ることが公知である。これら不平衡重錘体はこれら不平衡重錘体を回転させる軸上に位置していて、不平衡重錘体の各々は軸の角速度に依存して真直ぐでない個別遠心力を生じる。この個別遠心力の和は結果として生じる振動体遠心力となる。この結果として生じる振動体遠心力は軸を介して軸受に伝達されて、振動体ケ−シングと成形箱を介して成形体に引き渡される。不平衡重錘体の旋回点位置を互いに変更することにより結果として生じる振動体遠心力の大きさが変更され得る。特定の入り子式の場合には、零から最大遠心力までの調整が前記振動体において必要である。その際に結果として生じる振動体遠心力の作用は調整できない。
【０００３】
ドイツ特許出願公開第２０４６２４５号明細書には、偏心駆動部のそれ自体望まれない運動成分を出来るだけ過度に振動部材により捕獲して、望まれた運動方向に変形する振動駆動部が記載されている。この課題は、偏心駆動部が調整自在な往復行程を伴って、旋回ピンに対して振動部材の開口に移動自在に配置されている滑り部材内に配置されることによって解決される。そのような振動駆動部が一軸線のみにおいて真直な振動を発生して、ラム振動体として装置の地面への食い込みが緩和される。
【０００４】
【発明が解決しようとする課題】
成形箱の成形みぞ内の成形材料を成形体に圧縮成形する振動圧縮装置用のそのような解決手段は、上面と下面を備えた平らな成形部材にのみ適し、円周と長さを備えた成形部材には適しない。
【０００５】
更に、軸は回転力の伝達に使用されるばかりでなく、不平衡重錘体の遠心力にも使用される。
【０００６】
特許請求項１乃至３に記載された発明の課題は、成形箱の成形みぞ内の成形材料を円周と長さを備える成形体に、主として環状、丸い或いは楕円の成形部材に又は軸が不平衡重錘体の遠心力により曲げを受けない多角形の複雑な形材に圧縮成形する振動圧縮装置を開発することである。
【０００７】
【課題を解決するための手段】
この課題は、特許請求項１に記載された特徴部分により解決される。成形箱の成形みぞ内の成形材料を円周と長さを備える成形体に、主として環状、丸い或いは楕円の成形部材に圧縮成形する振動圧縮装置では、外部不平衡重錘体１と内部不平衡重錘体２は同じ運動モ−メントを備えてスリ−ブ形状に入り子式に配置されていて、二つの不平衡重錘体１、２の質量旋回点は一つの回転平面にあり、質量旋回点の角度位置は互いに一つの調整スリ−ブ７により変更されて、軸３は不平衡重錘体１、２の遠心力による曲げにより生じた応力を受けない。
【０００８】
その際に調整スリ−ブ７は一つの螺子と形状補完的な連結部を形成され、この場合に調整スリ−ブ７の軸方向移動により二つの不平衡重錘体１、２の相対運動が互いに達成されるか、或いは二つの逆方向螺子を形成しているので、不平衡重錘体１、２の相対運動は結果として生じる振動体遠心力の方向が軸３に関していつも一定のままであるように互いに強要される。
【０００９】
縦に拡張された成形部材を成形するために、この発明の好ましい構成では、一連の複数の振動体は軸端８、８’の継ぎ手により相前後して配置されて中央で駆動され、この場合にその個々の振動体にも別の遠心力が調整でき、各遠心力が個々に調整できる。
【００１０】
この発明により達成された利点は、特に不平衡重錘体１、２の質量旋回点が回転平面にあり、支持された構成部材の多軸方向曲げ応力が生じなく、軸３が不平衡重錘体１、２の遠心力による曲げ応力を受けないことにある。
【００１１】
特許請求項２に基づく二つの逆方向の螺子を備える調整スリ−ブ７の構成により、調整スリ−ブ７の軸方向移動による不平衡重錘体１、２の相対運動は、結果として生じる振動体遠心力の方向が軸３に関していつも一定のままであるように互いに強要されることを可能とする。
【００１２】
この発明の補助的な好ましい構成は特許請求項３に記載されている。軸端の継ぎ手により複数の振動体は相前後して配置されて同時に運転される。その各これらの振動体では別の遠心力が調整できる。特許請求項２に基づく特徴部分との関係において、結果として生じる振動体遠心力の方向を軸３に関して一定に調整することが初めてできる。
【００１３】
【発明の実施の形態】
この発明の若干の好ましい実施例は、図面に図示され、次に詳細に説明される。図１は、二つのスリ−ブ状に入り子式に配置された不平衡重錘体１、２の圧縮装置を通る縦断面を示す。内部不平衡重錘体２は外部不平衡重錘体１内で内部半径方向軸受４により支持され、外部不平衡重錘体１は振動体ケ−シグ５内に外部半径方向軸受６により支持されている。直通軸３は軸端８では振動体ケ−シグ５内に半径方向軸受１０により支持され、他の軸端８’では内部不平衡重錘体２内に半径方向軸受１２により支持されている。調整スリ−ブ７は外面上に二つの逆方向の螺子を形成して、内面上に一つのスプライン溝を形成している。一方の側では調整スリ−ブ７は二つの不平衡重錘体１、２により形状補完的且つ緊張的に形成され、他方の側では調整スリ−ブ７は調整装置９におけるブッシュ軸受１１により支持され、調整装置９は軸方向に調整できる。
【００１４】
図２には、簡略化された実施態様を通る縦断面が図示され、調整スリ−ブ７がその外面にはひとつの螺子のみを形成して、内面には一つのスプライン溝を形成している。一方の側では調整スリ−ブ７は外部不平衡重錘体１により形状補完的且つ緊張的に形成され、他方の側では調整スリ−ブ７は調整装置９におけるブッシュ軸受１１により支持され、調整装置９は軸方向に調整できる。直通軸３は軸端８では振動体ケ−シグ５内で半径方向軸受１０により支持され、他の軸端８’では内部不平衡重錘体２内で緊張的且つ形状補完的に支持されている。
内部不平衡重錘体２は図１における如く外部不平衡重錘体１内で内部半径方向軸受４により支持され、外部不平衡重錘体１は振動体ケ−シグ５内に外部半径方向軸受６により支持されている。
【００１５】
図３は、他の簡略化された実施態様を通る縦断面を示し、外部不平衡重錘体１は外部半径方向軸受６により直接に振動体ケ−シグ５内に支持されている。内部不平衡重錘体２は図２における如く直接に軸３に固定されている。
【００１６】
図１と図２に基づく成形箱の成形みぞ内の成形材料を円周と長さを備える成形体に圧縮成形する振動圧縮装置の運転の際には、軸の一方の軸端が駆動され、回転運動を軸の楔形材を介して調整スリ−ブに形状補完的に伝達する。調整スリ−ブはさらに運動をその外面上の二つの逆方向螺子を介して二つの回転体に伝達する。
【００１７】
図１に基づく調整装置による調整スリ−ブの軸方向移動により、不平衡重錘体の相対移動と質量旋回点の位置変更とは互いに強制される。調整過程における不平衡重錘体の互いの位置及び不平衡重錘体の相対移動は軸方向位置及び軸の角速度に無関係である。軸は振動体を貫通されている。軸端の継ぎ手により複数の振動体が相前後して配置されている。複数の振動体は同時に運転され得る。各これら振動体では別の遠心力が調整できる。
【００１８】
この発明の特殊な用途例では、コンクリ−ト管を製造するために振動中子が使用される。前記振動体の多くが一つの中央振動体に一体化されている。中子の振動はこの中央振動体により発生されて、この中央振動体は複数の個々の振動体から成り、互いに連結されて中央で駆動される。製造すべき製品への適用やそれぞれの製造観点、即ちコンクリ−ト調合、振動数（励磁周波数）、成形装置／機械のばね減衰システムに依存して、管の生産中に各個々の振動体層の振動遠心力が調整される。
【００１９】
【発明の効果】
不平衡重錘体の質量旋回点が回転平面にあり、支持された構成部材の多軸方向曲げ応力が生じなく、軸が不平衡重錘体の遠心力による曲げ応力を受けないことにある。
【００２０】
調整スリ−ブの軸方向移動による不平衡重錘体の相対運動は結果として生じる振動力の方向が軸に関していつも一定のままであるように互いに強要されることを可能とする。
【００２１】
軸端の継ぎ手により複数の振動体は相前後して配置されて同時に運転されるから、各これらの振動体では別の遠心力が調整できる。
【図面の簡単な説明】
【図１】 二つのスリ−ブ状に入り子式に配置された不平衡重錘体の圧縮装置を通る縦断面を示す。
【図２】 簡略化された実施態様を通る縦断面を示す。
【図３】 他の簡略化された実施態様を通る縦断面を示す。
【符号の説明】
１、２．．．不平衡重錘体
３．．．．．軸
４，６．．．半径方向軸受
５．．．．．振動体ケ−シグ
７．．．．．調整スリ−ブ
８，８’．．軸端
９．．．．．調整装置[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a vibration compression apparatus for compressing and molding a molding material in a molding groove of a molding box into a molded body according to the superordinate concept of claim 1.
[0002]
[Prior art]
It is known that a vibration compression apparatus for compressing and molding a molding material in a molding groove of a molding box into a molded body includes a plurality of unbalanced weight bodies. These unbalanced weights are located on an axis that rotates the unbalanced weights, and each of the unbalanced weights generates an individual centrifugal force that is not straight depending on the angular velocity of the shaft. The sum of the individual centrifugal forces is the resulting vibratory centrifugal force. The resulting vibrating body centrifugal force is transmitted to the bearing via the shaft and delivered to the formed body via the vibrating body casing and the forming box. The magnitude of the resulting vibrating body centrifugal force can be changed by changing the pivot point positions of the unbalanced weights relative to each other. In the case of a specific nested type, adjustment from zero to the maximum centrifugal force is necessary in the vibrating body. The action of the resulting vibrating body centrifugal force cannot be adjusted.
[0003]
German Patent Application No. 2046245 describes a vibration drive that captures as much of the undesired motion component of the eccentric drive as possible by the vibration member and deforms it in the desired direction of motion. Yes. This problem is solved by arranging the eccentric drive unit in a sliding member that is movably arranged in the opening of the vibration member with respect to the pivot pin with an adjustable reciprocating stroke. Such a vibration driving unit generates a straight vibration only in one axis, and the biting of the device into the ground as a ram vibrating body is alleviated.
[0004]
[Problems to be solved by the invention]
Such a solution for a vibration compression device that compresses the molding material in the molding groove of the molding box into a molded body is only suitable for flat molded parts with upper and lower surfaces and has a circumference and length. Not suitable for molded parts.
[0005]
Furthermore, the shaft is not only used for transmitting rotational force but also used for centrifugal force of unbalanced weight.
[0006]
The object of the invention described in claims 1 to 3 is that the molding material in the molding groove of the molding box is formed into a molded body having a circumference and a length, mainly into an annular, round or elliptical molded member, or the shaft is not suitable. The purpose of this study is to develop a vibration compression device that compresses and molds polygonal complex shapes that are not subjected to bending by the centrifugal force of the balance weight.
[0007]
[Means for Solving the Problems]
This problem is solved by the features described in claim 1. In a vibration compression apparatus that compresses a molding material in a molding groove of a molding box into a molded body having a circumference and a length, mainly into a ring, round or elliptical molded member, the external unbalanced weight body 1 and the internal unbalanced body The weight body 2 has the same motion moment and is arranged in a slave shape in a slave manner, and the mass pivot points of the two unbalanced weight bodies 1 and 2 are on one rotation plane, and the mass The angular position of the turning point is changed by one adjusting sleeve 7 so that the shaft 3 is not subjected to stress caused by bending of the unbalanced weight bodies 1 and 2 due to the centrifugal force.
[0008]
At this time, the adjusting sleeve 7 is formed with a shape complementary connection portion with one screw, and in this case, the relative movement of the two unbalanced weight bodies 1 and 2 is caused by the axial movement of the adjusting sleeve 7. The relative movement of the unbalanced weights 1, 2 is always achieved with respect to the axis 3 because the relative movement of the unbalanced weights 1, 2 is achieved because they are achieved with each other or form two reverse screws. So that they are coerced to each other.
[0009]
In order to form a vertically expanded forming member, in a preferred configuration of the invention, a series of vibrators are arranged one after the other by joints of shaft ends 8, 8 'and driven in the center, in this case In addition, different centrifugal forces can be adjusted for the individual vibrators, and each centrifugal force can be adjusted individually.
[0010]
The advantage achieved by the present invention is that, particularly, the mass pivot point of the unbalanced weight bodies 1 and 2 is in the plane of rotation, the bending stress of the supported components does not occur, and the shaft 3 is unbalanced weight. There is no bending stress due to the centrifugal force of the bodies 1 and 2.
[0011]
Due to the configuration of the adjusting sleeve 7 with two reverse screws according to claim 2, the relative movement of the unbalanced weight bodies 1, 2 due to the axial movement of the adjusting sleeve 7 results in vibrations. It is possible to force each other so that the direction of the body centrifugal force always remains constant with respect to the axis 3.
[0012]
An auxiliary preferred configuration of the present invention is described in claim 3. The plurality of vibrators are arranged one after the other by the joint at the shaft end and are operated simultaneously. Each of these vibrators can be adjusted for different centrifugal forces. In relation to the characterizing part according to claim 2, it is possible for the first time to adjust the direction of the resulting vibrating body centrifugal force uniformly with respect to the axis 3.
[0013]
DETAILED DESCRIPTION OF THE INVENTION
Some preferred embodiments of the invention are illustrated in the drawings and will now be described in detail. FIG. 1 shows a longitudinal section through a compression device of unbalanced weight bodies 1, 2 arranged in a two-sleeve concentric manner. The internal unbalanced weight body 2 is supported by the internal radial bearing 4 in the external unbalanced weight body 1, and the external unbalanced weight body 1 is supported by the external radial bearing 6 in the vibrating body casing 5. ing. The direct shaft 3 is supported by a radial bearing 10 in the vibrating body casing 5 at the shaft end 8 and supported by a radial bearing 12 in the internal unbalanced weight body 2 at the other shaft end 8 ′. The adjusting sleeve 7 has two opposite-direction screws formed on the outer surface, and a spline groove formed on the inner surface. On one side, the adjusting sleeve 7 is formed in a complementary manner and tensioned by two unbalanced weights 1 and 2, and on the other side, the adjusting sleeve 7 is supported by a bush bearing 11 in the adjusting device 9. The adjustment device 9 can be adjusted in the axial direction.
[0014]
FIG. 2 shows a longitudinal section through a simplified embodiment, in which the adjusting sleeve 7 has only one screw on its outer surface and one spline groove on its inner surface. . On one side, the adjusting sleeve 7 is formed in a complementary and tensional manner by the external unbalanced weight body 1, and on the other side, the adjusting sleeve 7 is supported by a bush bearing 11 in the adjusting device 9. The device 9 can be adjusted in the axial direction. The direct shaft 3 is supported at the shaft end 8 by the radial bearing 10 in the vibrating body casing 5, and is supported at the other shaft end 8 ′ in a tension and shape-complementary manner in the internal unbalanced weight body 2. Yes.
The internal unbalanced weight body 2 is supported by an internal radial bearing 4 in the external unbalanced weight body 1 as shown in FIG. 1, and the external unbalanced weight body 1 is provided in the vibrating body casing 5 by an external radial bearing. 6 is supported.
[0015]
FIG. 3 shows a longitudinal section through another simplified embodiment, in which the external unbalanced weight body 1 is supported directly in the vibrating body casing 5 by an external radial bearing 6. The internal unbalanced weight body 2 is directly fixed to the shaft 3 as shown in FIG.
[0016]
During the operation of the vibration compression apparatus for compressing and molding the molding material in the molding groove of the molding box based on FIGS. 1 and 2 into a molded body having a circumference and a length, one shaft end of the shaft is driven, Rotational motion is transmitted in a shape-complementary manner to the adjusting sleeve via the shaft wedge. The adjusting sleeve further transmits motion to the two rotating bodies via two reverse screws on its outer surface.
[0017]
Due to the axial movement of the adjustment sleeve by the adjustment device according to FIG. 1, the relative movement of the unbalanced weight body and the position change of the mass swivel point are forced together. The positions of the unbalanced weights and the relative movement of the unbalanced weights in the adjustment process are independent of the axial position and the angular velocity of the shaft. The shaft passes through the vibrating body. A plurality of vibrators are arranged one after the other by a joint at the shaft end. A plurality of vibrators can be operated simultaneously. Different centrifugal forces can be adjusted for each of these vibrators.
[0018]
In a special application example of the present invention, a vibrating core is used to manufacture a concrete tube. Most of the vibrators are integrated into one central vibrator. The vibration of the core is generated by the central vibrator, and the central vibrator is composed of a plurality of individual vibrators that are connected to each other and driven at the center. Each individual vibrator layer during tube production depends on the application to the product to be manufactured and the respective manufacturing point of view, i.e. concrete preparation, frequency (excitation frequency), forming device / mechanical spring damping system. The vibration centrifugal force of is adjusted.
[0019]
【The invention's effect】
The mass pivot point of the unbalanced weight body is on the plane of rotation, so that the multi-axial bending stress of the supported component does not occur, and the shaft is not subjected to bending stress due to the centrifugal force of the unbalanced weight body.
[0020]
The relative movement of the unbalanced weights due to the axial movement of the adjusting sleeve allows the resulting vibrational forces to be forced together so that the direction of the vibration force always remains constant with respect to the axis.
[0021]
Since the plurality of vibrators are arranged one after the other by the joint at the shaft end and are simultaneously operated, different centrifugal forces can be adjusted in each of these vibrators.
[Brief description of the drawings]
FIG. 1 shows a longitudinal section through a compression device of unbalanced weights arranged in two sleeve-like concentric arrangements.
FIG. 2 shows a longitudinal section through a simplified embodiment.
FIG. 3 shows a longitudinal section through another simplified embodiment.
[Explanation of symbols]
1,2. . . 2. Unbalanced weight body . . . . Axes 4,6. . . 4. Radial bearing . . . . 6. Vibration body casing 7. . . . . Adjusting sleeve 8, 8 '. . 8. Shaft end . . . . Adjustment device

Claims (3)

外部不平衡重錘体（１）と内部不平衡重錘体（２）は同じ運動モ−メントを備えてスリ−ブ形状に入り子式に配置されていて、二つの不平衡重錘体（１、２）の質量旋回点は一つの回転平面にあり、質量旋回点の角度位置は互いに一つの調整スリ−ブ（７）により変更されて、軸（３）は不平衡重錘体（１、２）の遠心力による曲げにより生じた応力を受けないことを特徴とする成形箱の成形みぞ内の成形材料を円周と長さを有する形成体に圧縮して形成する振動圧縮装置。The external unbalanced weight body (1) and the internal unbalanced weight body (2) have the same movement moment and are arranged in a slave shape in a child-type manner. 1 and 2) are on one plane of rotation, the angular positions of the mass swivel points are changed by one adjusting sleeve (7) and the shaft (3) is unbalanced weight (1 2) A vibration compression apparatus for compressing and forming a molding material in a molding groove of a molding box into a molded body having a circumference and a length, which is not subjected to stress caused by bending due to centrifugal force. 調整スリ−ブ（７）は二つの逆方向の螺子を形成されていて、調整スリ−ブ（７）の軸方向移動により二つの不平衡重錘体（１、２）の相対運動は、結果として生じる振動体遠心力の方向が軸（３）に関していつも一定のままであるように強要されることを特徴とする請求項１に記載の圧縮装置。The adjusting sleeve (7) is formed with two opposite-direction screws, and the relative movement of the two unbalanced weight bodies (1, 2) due to the axial movement of the adjusting sleeve (7) results in 2. The compression device according to claim 1, characterized in that the direction of the vibrational centrifugal force produced as follows is forced to remain constant with respect to the axis (3). 軸端（８、８’）の継ぎ手により相前後して配置されて中央で駆動される一連の複数の振動体の個々の振動体では別の遠心力が調整でき、各遠心力が個々に調整できることを特徴とする請求項１又は請求項２に記載の圧縮装置。Separate centrifugal forces can be adjusted in each vibrator of a series of vibrators that are arranged one after the other by a shaft end (8, 8 ') joint and driven in the center, and each centrifugal force is adjusted individually The compression apparatus according to claim 1 or 2, wherein the compression apparatus is capable.
JP2000540947A 1998-03-27 1999-03-20 A vibration compression device that compresses the molding material in the molding box using two unbalanced weights Expired - Fee Related JP3827529B2 (en)

Applications Claiming Priority (3)

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DE29805619U DE29805619U1 (en) 1998-03-27 1998-03-27 Vibration compression system for compressing molding compounds in molding boxes
DE29805619.4 1998-03-27
PCT/EP1999/001884 WO1999049992A1 (en) 1998-03-27 1999-03-20 Vibration compression system for compressing molding materials in molding boxes by using two unbalanced bodies

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JP3827529B2 true JP3827529B2 (en) 2006-09-27

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DE102010010037B4 (en) * 2010-03-03 2019-10-31 Bomag Gmbh Continuously adjustable vibration exciter
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DE1841635U (en) * 1958-01-02 1961-11-16 Kisha Seizo Kaisha Ltd VIBRATION DEVICE.
US3600957A (en) * 1969-09-18 1971-08-24 Stoffel Engineering Corp Oscillating power unit
DE2409417A1 (en) * 1974-02-27 1975-09-04 Wacker Werke Kg Oscillating device with adjustable balance weights - permitting continuous adjustment during operation
GB2017863A (en) * 1978-03-07 1979-10-10 Venanzetti Vibrazioni Adjusting amplitude of vibrations of eccentric mass vibrator
EP0092014A1 (en) * 1982-04-21 1983-10-26 Losenhausen Maschinenbau AG& Co Kommanditgesellschaft Regulator for a vibrations generator with unbalanced masses
CS244465B1 (en) * 1984-02-23 1986-07-17 Lubos Dolezal Vibrations exciter with continuous variation of eccentric moment
DE8704108U1 (de) * 1987-03-19 1987-05-07 Henke Maschinenfabrik Gmbh & Co Kg, 4952 Porta Westfalica Vorrichtung zum Herstellen von Betonteilen
DE19510562A1 (en) * 1995-03-23 1996-09-26 Baumgaertner Maschf Gmbh Concrete compaction vibrator
DE19539150A1 (en) * 1995-10-20 1996-03-14 Willy Laukemann Vibration drive for oscillators allowing variable oscillations during operation

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