EP0406480B1 - Vibrateur à masses tournantes - Google Patents

Vibrateur à masses tournantes Download PDF

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Publication number
EP0406480B1
EP0406480B1 EP89119697A EP89119697A EP0406480B1 EP 0406480 B1 EP0406480 B1 EP 0406480B1 EP 89119697 A EP89119697 A EP 89119697A EP 89119697 A EP89119697 A EP 89119697A EP 0406480 B1 EP0406480 B1 EP 0406480B1
Authority
EP
European Patent Office
Prior art keywords
shafts
rotary vibrator
gear train
vibrator according
hollow 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.)
Expired - Lifetime
Application number
EP89119697A
Other languages
German (de)
English (en)
Other versions
EP0406480A3 (en
EP0406480A2 (fr
Inventor
Heinrich Haake
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.)
Mueller Herne Pumpen Maschinen Stahlbau GmbH
Original Assignee
Mueller Herne Pumpen Maschinen Stahlbau GmbH
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 Mueller Herne Pumpen Maschinen Stahlbau GmbH filed Critical Mueller Herne Pumpen Maschinen Stahlbau GmbH
Publication of EP0406480A2 publication Critical patent/EP0406480A2/fr
Publication of EP0406480A3 publication Critical patent/EP0406480A3/de
Application granted granted Critical
Publication of EP0406480B1 publication Critical patent/EP0406480B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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

Definitions

  • the invention relates to a rotary vibrator according to the preamble of claim 1.
  • the invention relates in particular to rotary vibrators which serve to drive vibrating troughs whose delivery capacity can be adjusted as a result of the adjustability of the rotary vibrator.
  • Such rotary vibrators work with two imbalances, the masses of which can be adjusted in their eccentricity to the inner shafts in such a way that the amplitudes of the vibrations can be adjusted between a maximum value and a minimum value.
  • the adjustment enables the use of mechanical gears, which, compared to electric or hydraulic adjustment gears, can transmit considerably greater forces largely without wear and with little maintenance.
  • such rotary vibrators are suitable for the rational drive of high-performance conveyors, for example in the mining of mountain and coal vibrating troughs, which are used under the foothills of bunkers and form an adjustable intermediate conveyor for belt conveying.
  • the invention is based on a rotary vibrator of a known type according to EP-A-0 201 050 (DE-OS 35 16 145).
  • the inner shafts which are synchronously driven at one end via a spur gear, run in opposite directions in a housing, on which the unbalances are arranged in a rotationally fixed manner.
  • the standing hollow shafts can be moved on the inner shafts with a slide that is axially adjustable from the other side of the housing and thereby form the drive of an adjusting gear assigned to an imbalance.
  • the input of each of these gears consists of a rack fixed on the hollow shaft, which eccentrically adjusts the unbalance guided on the inner shaft via a pinion.
  • Each unbalance must be mounted and guided radially displaceably on one side of the inner shaft. Both adjustment gears are subject to the mass accelerations of the unbalances and are therefore heavily loaded.
  • the storage and the drive required for the unbalance adjustment take up a considerable amount of space. This results in unfavorable housing dimensions, in particular if the driven machine demands considerable energy from the rotary vibrator and can only provide a limited space. This is particularly the case with vibratory conveyors, sieves or the like. Machines the case.
  • the invention has for its object to provide a powerful and handy rotary compressor of the type described.
  • the guidance of the unbalance is shifted to the inner shaft eccentric so that, depending on the angle of rotation of the unbalance, the eccentricity of the shaft eccentric increases or decreases according to the mass of the unbalance, e.g. is reduced to zero.
  • the adjustment and setting of the vibration amplitudes takes place during the rotation of the masses by the rotating hollow shafts with the help of the planetary gear via which the synchronism of the hollow shafts and the inner shafts is disturbed, so that both hollow shafts with respect to the inner shafts or vice versa the inner shafts with respect to the hollow shafts Change the angular position and change or adjust the vibration amplitude.
  • the rotary vibrator according to the invention can be restricted radially and axially to the shafts to extremely small dimensions despite considerable masses in the unbalance.
  • the planetary gear is seated outside the imbalance. It allows the smallest adjustment paths and thus enables sensitive regulation of the vibration amplitudes. Machines provided with the rotary vibrator according to the invention, in particular vibrating troughs, can therefore be adjusted accordingly, in particular regulated in their respective delivery capacity.
  • the unbalances are nested inside one another at maximum vibration amplitude, the nested unbalance being roller-shaped, while the mass of the other unbalances is distributed over the two disks. This makes it possible to axially stretch the housing if larger masses are required in the unbalance, but to keep the housing narrow radially to the shafts.
  • Such housing shapes can be used particularly cheaply on frame constructions, such as are present on the above-mentioned vibrating channels.
  • the hollow shafts rotate at the same speed as the inner shafts. If the vibration amplitudes are set, the hollow and inner shafts must be adjusted relative to each other by the same arc angle. The easiest way to achieve this is with the features of claim 3.
  • the connection of the sun gear with the two shafts is also favorable because it includes the trains of the planetary gear in the hollow shaft drive and smaller gear wheel diameters can be used to reduce the size.
  • the moving parts of a rotary vibrator (5) are accommodated in a housing (3) consisting of two halves (1, 2) with a screwed-on housing cover (4).
  • a drive acts on a stub shaft (6) via a pinion on a spur gear (7, 8) each of a hollow shaft (9, 10).
  • the hollow shaft (10) is rotatably mounted in the housing at (12) with a stub (11) of an inner shaft.
  • the hollow shaft end is designed as a pinion (14) which rotates the planet gears (15) of a stationary planet carrier (16).
  • the sun gear (17) rotates, which drives an inner shaft (19) via a pinion (18), which is arranged concentrically in the hollow shaft (9).
  • An internal shaft (22) is rotated in opposite directions to the internal shaft (19) via a spur gear (20, 21), which is housed concentrically in the hollow shaft (10).
  • the inner shaft (19) is provided with a pair of disk-shaped shaft eccentrics (23, 24).
  • the two unbalanced masses (25, 26) are rotatably mounted on the circumference of the two disc eccentrics. These are entrained by a radial arm (27), which is attached to the hollow shaft (9) in a rotationally fixed manner and has a slot guide (28) for an entraining finger (29) which is fastened in the end face of the unbalanced mass (25).
  • the unbalanced mass (26) is carried along by the unbalanced mass (25) via a half-shell (30).
  • the inner shaft (22) also has a rotating shaft eccentric (31).
  • the unbalanced mass (32) is rotatably mounted on it and is carried by two radial arms (33, 34) via a respective front finger (35, 36). These driving fingers run according to the driving finger (29) of the unbalanced mass (25, 26) in a radial guide of the arms (33, 34). As can be seen from FIG. 1, the roller-shaped unbalanced mass (32) is nested between the two disc-shaped unbalanced masses (25, 26) and their eccentric (23, 24) with their eccentric (31).
  • the unbalanced mass (32) and the shaft eccentric (31) have a common center of gravity at (37) in Fig. 3, in the dashed line the extent of the unbalanced mass and its maximum eccentricity and vibration amplitude.
  • the unbalanced masses (25, 26) and shaft eccentrics (23, 24) have their focus at (38) in Fig. 3, in dashed lines the extent of these two masses is shown. Since the bores of the three unbalanced masses or centrifugal masses are arranged eccentrically to the circumference, a relative rotation of the inner shafts (19, 22) increases the eccentricity of the shaft eccentrics (23, 24 and 31) with the aid of the centrifugal masses (25, 26, 32) or to compensate for the eccentricity, in which case all shafts rotate without vibrations. Due to the gear connection of the inner and hollow shafts, the eccentricities of all unbalanced masses are adjusted uniformly.
  • the described moving parts of the rotary vibrator (5) run in the oil mist, which is generated with the rotating parts from an oil sump in the housing. Radial bores supply the shaft bearings that are not directly in the oil mist with lubricant, which largely eliminates wear problems.
  • the housing is attached to a machine via housing bores and can transmit directional vibrations.

Claims (8)

  1. Vibrateur à masses tournantes (5) dont les balourds (25, 26, 32) sont montés sur des arbres internes, parallèles, tournant en sens opposé (19, 22) et dont l'excentricité est réglable par l'intermédiaire d'arbres creux externes concentriquement (9, 10), caractérisé en ce que les balourds (25, 26, 32) sont rotatifs, excentriquement sur des excentriques (23, 24, 31) qui sont montés sur les arbres internes (19, 22) d'une manière résistante à la torsion, et sont guidés par des bras radiaux (27, 33, 34) qui sont montés d'une manière résistante à la rotation avec leurs arbres internes (19, 22) sur des arbres creux tournant dans le même sens (9, 10), les arbres creux (9, 10) étant rotatifs par l'intermédiaire d'un engrenage planétaire (15, 17) en opposition aux arbres internes (19, 22).
  2. Vibrateur à masses tournantes selon la revendication 1, caractérisé en ce que l'un des balourds (25, 26, 32) se présente sous la forme d'un cylindre et l'autre balourd est réparti sur des disques de balourd (25, 26) qui incluent le balourd en forme de cylindre (32).
  3. Vibrateur à masses tournantes selon l'une des revendications 1 ou 2, caractérisé en ce que les arbres creux (9, 10) et les arbres internes (19, 22) comportent une commande ou entraînement commun (6), l'énergie d'entraînement ou de commande étant transmise par l'intermédiaire d'un réducteur ou engrenage droit (7, 8) aux arbres creux (9, 10) et par l'intermédiaire de l'engrenage planétaire (15, 17) à un arbre creux (19) ainsi que par l'intermédiaire d'un réducteur ou engrenage droit (20, 21) à l'autre arbre creux (22).
  4. Vibrateur à masses tournantes selon l'une des revendications 2 ou 3, caractérisé en ce que l'un des arbres creux (10) est conçu sous forme de pignon (14) qui entraîne les roues planétaires (15) du support planétaire vertical (16) de l'engrenage planétaire (15, 17) d'une manière rotative avec la commande de réglage.
  5. Vibrateur à masses tournantes selon l'une des revendications 2 à 4, caractérisé en ce que pour la rotation du support planétaire (16) de l'engrenage planétaire (15, 17) il est prévu une denture de vis sans fin (38) et une vis sans fin (39) sur un arbre (40) sortant de l'un des carters (1, 2) renfermant les parties tournantes du vibrateur à masses tournantes (5).
  6. Vibrateur à masses tournantes selon les revendications 2 à 5, caractérisé en ce que, les balourds en forme de disque (25, 26) sont raccordés entre eux par l'intermédiaire d'une semi-coque (30) dans laquelle tourne le balourd en forme de cylindre (32).
  7. Vibrateur à masses tournantes selon l'une des revendications 2 à 6, caractérisé en ce que le support planétaire (16) et la roue solaire (17) dc l'engrenage planétaire (15, 17) sont logés sur l'un des arbres creux (10) et sur un autre arbre creux (11) qui tourne dans un palier (12) solidaire du carter.
  8. Vibrateur à masses tournantes selon l'une des revendications 2 à 7, caractérisé en ce que la roue solaire (17) s'engrène dans un pignon (18) qui est fixé sur l'un des arbres creux (19).
EP89119697A 1989-07-06 1989-10-24 Vibrateur à masses tournantes Expired - Lifetime EP0406480B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3922169A DE3922169A1 (de) 1989-07-06 1989-07-06 Rotationsvibrator
DE3922169 1989-07-06

Publications (3)

Publication Number Publication Date
EP0406480A2 EP0406480A2 (fr) 1991-01-09
EP0406480A3 EP0406480A3 (en) 1991-12-11
EP0406480B1 true EP0406480B1 (fr) 1994-10-19

Family

ID=6384383

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89119697A Expired - Lifetime EP0406480B1 (fr) 1989-07-06 1989-10-24 Vibrateur à masses tournantes

Country Status (4)

Country Link
EP (1) EP0406480B1 (fr)
AT (1) ATE112985T1 (fr)
DE (2) DE3922169A1 (fr)
ES (1) ES2063800T3 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT395929B (de) * 1991-07-12 1993-04-26 Koenig Helmut Vorrichtung zum wirken portionierter teigstuecke
US6769838B2 (en) 2001-10-31 2004-08-03 Caterpillar Paving Products Inc Variable vibratory mechanism
DE102015009698B4 (de) * 2015-07-30 2017-05-04 Schenck Process Europe Gmbh Richterreger und Schwingmaschine mit Richterreger

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1236842B (de) * 1965-10-22 1967-03-16 Delmag Maschinenfabrik Vorrichtung, insbesondere fuer ein Ruettelgeraet, zum AEndern der Phasenlage zweier Unwuchten
DE3148437A1 (de) * 1981-12-08 1983-07-21 Weber Maschinentechnik Gmbh, 5928 Laasphe Schwingungserreger fuer mechanische schwingungen
DE3516145A1 (de) * 1985-05-04 1986-11-06 Müller GmbH Herne Pumpen-Maschinen-Stahlbau, 4690 Herne Schwingungserreger mit mehreren unwuchten in einem gehaeuse, insbesondere fuer schwingfoerderrinnen des untertagebetriebes
DE3708922A1 (de) * 1987-03-19 1988-09-29 Henke Maschf Gmbh Vorrichtung zum herstellen von betonteilen
DE8800592U1 (fr) * 1988-01-20 1988-03-10 Rhein-Getriebe Gmbh, 4005 Meerbusch, De

Also Published As

Publication number Publication date
DE58908541D1 (de) 1994-11-24
EP0406480A3 (en) 1991-12-11
ES2063800T3 (es) 1995-01-16
ATE112985T1 (de) 1994-11-15
EP0406480A2 (fr) 1991-01-09
DE3922169A1 (de) 1991-01-17

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