FR2724854A1 - Generation and control of vibrations for vibratory plant, e.g. for separating, crushing or compacting materials - Google Patents

Abstract

The vibration generator is controlled by altering the relative position of two coaxial shafts (2,5), two plates (6,8) and an enclosure (7). The plates position sets of satellite gears (E) and toothed pinions (15). The pinions mesh directly or indirectly with gear wheels (3.1-5.1) fixed to the coaxial shafts. The coupling of these gears drives the satellites, and depending on the number and their positions generate a variety of vibrational forces. The displacement between the coaxial shafts can be altered manually by a handle (27) on the outside of the enclosure, altering the vibrational characteristics of the unit.

Description

DEVICE FOR AUDITING THE CONTROL AND ACTION OF VIBRATION EFFECTS
CONTROLS ON MACHINERY AND EQUIPMENT WITH A VIEW OF
TREATMENT OF PRODUCTS INTENDED TO BE VIBRATED, BROWNED, COMPACT,
SEPARATED
The invention relates to the technical field of equipment and materials for compacting, crushing, compacting, separating materials from vibratory effects of any kind operating in association with one or more phase shifters.

A device is known authorizing the control and the action of vibratory effects on machines and materials as defined in Patent Application PCT 92120467 or in the patent application.
FR 93/15659.

 As part of his personal research, the Applicant has been interested in devices of this kind by studying other ways and combinations for obtaining multiple vibratory effects with variation of force.

 From his personal work, the Applicant has thus developed a new device allowing and assuring according to the choices the different types of forces desired, this in a particular original design going against the knowledge, studies and achievements made previously.

 The advantages of the new device reside in particular in the compactness of the variable unbalance multimass system, which can be installed directly at the end of the shaft of a motor member, and its adaptability to be driven by an external phase shift member.

 For example, there exist according to current techniques vibration generating devices comprising a motor member with two ends of shafts each receiving eccentric vibration weights.

 These devices generate only a kind of vibration, multidirectional around the axis, and further it is necessary to stop the motor, disassemble the outer casings to arrange the weights to obtain a different vibration force.

In one of the particular applications given by way of example, it is possible to equip a motor with two ends of trees of the devices that are the subject of the invention, and to generate mulitdirectional vibration forces, either unidirectional or oscillatory. , or combined with the possibility of varying these forces by phase shifting means integrated into the device and in operation without stopping the engine.

 According to a first characteristic, the device allowing the control and the action of vibratory effects controlled on machines and equipment in particular for the treatment of products intended to be vibrated, crushed, compacted, separated, is remarkable in that it consists positioned from at least two coaxial axes two flanges, said flanges allowing the positioning'de several sets each composed of several unbalanced satellite lines and toothed pinions said sprockets meshing on integral gear wheels coaxial axes and commander either placing the unbalance satellite lines in angular position relative to one another or driving the system.

 According to another characteristic, the flanges are rotated, the integral toothed wheels of the coaxial axes are not driven.

 This rotation of the flanges causes eccentric masses whose toothed gears, which are connected to them> meshes on and around the toothed wheels.

 The phase shift is obtained by angular displacement of the coaxial axes.

 According to another characteristic, the flanges remain fixed and it is the coaxial axes which are rotated by an out-of-phase external motor.

 The rotation of the coaxial axes causes eccentric masses generating vibrational forces.

 According to another characteristic, the device generates a unidirectional vibration with variable force.

According to another feature, the device generates a unidirectional force and equipped with a variation and direction and force
According to another characteristic, the device for generating any kind of multidirectional vibration, unidirectional, oscillatory or mixed, with variation of force of each such.

 According to another characteristic, the eccentric masses are in the form of sectors at 90 '.

 According to another characteristic, the eccentric masses have concentric shapes.

 According to another characteristic, the devices equip the two shaft ends with a motor unit.

 These and other features are apparent from the remainder of the description.

For fixing the object of the invention illustrated, without limitation, to the drawing figures in which:
Figure 1 is a sectional view along line AA of Figure 2 of the vibrator device.

 Figure 2 is a front view of the device according to the invention according to Figure 1, the eccentric masses being positioned to produce a maximum vibration.

 Figure 3 is also a face of the device according to the invention Figure 1, the masses being positioned to produce zero vibration.

 Figure 4 is a front view of the device, the masses being positioned to produce zero oscillatory vibration.

 Figure 5 is a front view of the device, the masses being positioned to produce maximum oscillatory vibration.

 Figures 6 and 7 are views in coupc of the device Figures 8 and 9 producing a unidirectional vibration and the flanges being in rotation.

 Figure 8 is a view of the face of the device producing a unidirectional vibration of maximum force and rotating flanges.

 Figure 9 is a front view of the device shown in Figure 8, but the masses being positioned to produce a zero unidirectional vibration.

 FIG. 10 represents the phase shift system of the device represented in FIGS. 7-8 and 9.

FIGS. 11A-11B and 11C show off-center earth masses at 90.degree.
Figs. 12A-12B-12C show concentric eccentric axis shapes.

 Figures 13 - 14 -15 and 16 show a multivibratory device with rotating plates producing several kinds of vibration each being controllable from zero to the maximum.

Figures 17-18 and 19 show another vibrating device
Figures 20 and 21 show another vibrating device generating a unidirectional vibration.

 Figures 22 -23-24 A-24 B and 24 C show a device generating several types of vibrations.

 Figure 25 relates to a vibrating device with external drive and non-rotating flanges.

 Figure 26 relates to a multivibratory vibrating device with non-rotating flanges and multiple external drive.

 Figure 27 relates to a vibrating monobloc system with two vibrating devices.

The reference vibration generator (1) for the set is composed of several sets El
E2 ... In, eccentric masses forming unbalanced.

 In Figures 1 and 2, the generator is shown with two sets E2 and El, chaam comprising the eccentric masses forming unbalance (14.1) (14.2) and (17.1) (17.2) respectively.

 These eccentric masses are fixed on shafts (23) using means (24). These eccentric masses can also be fixed by gluing to the axes (23).

 Each axis (23) receives a toothed gear (16.1 and 16.2 for line E2 and 15.1 and 15.2 for line E1).

 These toothed gears (16.1 and 16.2) are secured to the axes (23) by any appropriate means, hooping-keying or gluing.

 Each line comprising: the pinion gear, the axis (23), the eccentric mass constitutes a satellite of the system, this satellite being mounted on bearings (11) and (18) in two flanges or plates (0) and.

 (8).

 These trays (6) and (8) are braced by an envelope (7) and fixed together by spacer columns (22) forming a cage.

In the axis XX 'of the device, a first axis (2) on which is fixed a sleeve (3) comprising a toothed wheel (3.1) meshes with the toothed gears (15.1) and (15.2) of the line (El) and a second axis (5) equipped with a toothed wheel (5.1) meshes with the pinions (16.1) and (16.2) of the line (EZ>
The flange (8) comprises a driving part (8.1) which coupled to a drive member rotates the entire cage (6-7 and 8).

 The cage causes in its movement that circular of the satellites (23) and which also rotate on themselves, the toothed gears (15) and (16) meshing on their respective wheels (3.1) and (5.1).

The eccentric masses of the satellites rotating at a speed n rpm with respect to their axis generate rotating forces around their axis, producing a so-called muItidirecLionneli vibration.
The total vibration force obtained is the sum of the forces of each of the satellites.

 In the representation (FIG. 2), the eccentric mass forces (14.1), (14.2), (17.1) and (17.2) are added and are represented in a vertical position, the resultant force F rotates about the axis XX to the speed Nt rpm.

 By varying the angular position of the axes (2) and (5), and therefore the toothed wheels (3.1) and (5.1) Qpi are related to one another, one causes a complementary rotation of the satellites dEm together compared to those of the other set. There is then phase shift of one set compared to the other.

 This complementary rotation is added or retracted at the speed of the satellites in the direction of rotation of the axis 2 relative to the axis 5.

 3 is a phase shift of the 180 satellites of the set E1 with respect to the set E2> which causes a zero resultant.

Any angular position of the axis 2 with respect to the axis 5 being possible, it is therefore possible very simply to obtain a variation of vibration force resulting from a value 0 to a maximum value
F.

 In addition, the axes 2 and 5 are not animated by movement when the cage is driven at the speed N rpm and the satellites at the speed n rpm with respect to their axis, and this variation of angular position can therefore to be done simply in operation.

 One of the arrangements provided for in FIG. 1 consists in fastening the axis 3 to the frame (20.1) (20.2) (203) by any appropriate means, here on the plane, a screw (5.2) between leather and flesh makes it possible to immobilize the '= e (3) with respect to the frame (20).

 Since the axis 5 is immobilized, the angular variation of the assembly E1 with respect to the assembly EZ can be done by action alone on the axis 2 which can be cut by a simple manual lever or motoeisê or by a system arm / cylinder or by a rotary motor that can be controlled remotely and in operation.

 One of these control systems is shown in Figure 1> the one comprising a manual lever (26) provided with an indexing finger (27).

 These control devices make it possible to remotely and operationally control the vibrational frequency from a value of 0 to a maximum value F.

If the drive of the flanges (8) is at a speed Ntr / min relative to the axis XX, it is shown that the speed of the satellites (23) relative to their axis ntr / min is
n = N x R2 R1
where R1 is the pitch diameter of the wheels 3.1 and 5.1> R2 is the pitch diameter of the sprockets 15 and the
The total speed of the satellites with respect to the XX 'axis is
Nt = N (1 + R2) R1
For identical primary diameters Ri = R2, n = N and Nt = 2N
In other words, in this case, if the drive is done at a speed of N = 3000 rpm, the speed of the satellites with respect to XX 'is twice as great, ie nt = 6000 rpm, and the vibration force varies. depending on the square of the speed will be multiplied by four in this device described.

If the vibration force of each satellite corresponds to a speed of 6000 flAnn, oe
the satellites (23) only rotate at 3000 rpm around their axis
- the cage (6, 7 and 8) only rotates at 3000 rpm around the axis XX '
The service life of the mechanical elements, and in particular of the bearings (11) (9) and (10), is therefore increased with respect to a single eccentric mass rotating about the axis XX producing the resultant m & e effort but turning to 6000 rpm around this same axis XX '.

It is represented in FIG. 4 and 5 a particular vibration modc, said oscillatory, the consecutive masses 14 and 17 are shifted by 90 *
There is a generation of a vibration torque, this torque passing from a maximum in one direction to a maximum in the other direction during a rotation of the satellites and passing through a zero value.

 In phase shift, the wheels 3.1 with respect to the wheel 5.1 the value of the oscillating vibration torque varies from zero to a maximum value.

 And the oscillatory vibration is null figure 4 and maximum figure 5.

 The device according to the invention can also generate unidirectional vibratory forces with the ability to adjust, in operation, the amplitude or the vibration force and the direction of the unidirectional vibration.

 The device shown in FIGS. 6-7-8 and 9 comprises two balanced sets E2 and E1 each consisting of eccentric unbalance masses (14.1) (14.2) and (17.1) (17.2).

It is possible to imagine assemblies E each comprising 3-4 ... n eccentric masses each
The eccentric masses (14.1.) And (14.2) rotate in one direction while the eccentric masses (17.1) and (17.2) rotate in opposite directions.

 The rotational speeds are such that the resultant force of all eccentric masses is always in the same direction and varies sinusoidally between a maximum and a minimum value through zero.

 The reversal of the eccentric masses (17.1) and (17.2) with respect to the eccentric masses (14.1) and (14.2) is obtained by inverter intermediate meshing> here presen of an intermediate gear (31) respectively meshing on the wheel 3.1 and the pinions (16.1) (16.2), the pinions (15.1) and (15.2) meshing directly on the wheel (5.1).

 The role of this gear (31) is on the one hand to reverse the direction of rotation of the driven eccentric masses but also to obtain a speed of the satellites (15.1) and (15.2), in relation to their axis, such that the component of eccentric masses (14.1) (14.2.) and (17.1) (17.2 always in the same direction.

 This speed adaptation is done by varying the diameter of the wheel (3.1) relative to the wheel (5.1).

If the speed of the eccentric masses (17) is Nt = N (1 + 9) R1
The speed Not of masses (15) will be invcrsée and equal to
Not = N (1 + 2 R2) R1
Where R1 is the pitch diameter of the wheel (5.1)
R2 is the pitch diameter of the pinion (16)
If R1 = R2 NT = 3 N
The gears (31) are integral with a shaft (30) mounted on bearings (33) in the flange (8).

 The phase shift of a set El with respect to the other set E2 is obtained by rotation of r axis 2 with respect to the axis 5.

 The phase shifter comprises a pinion (34) and (35) integral respectively axes 2 and 5 and an axis 38 which comprises the pinions (37) and (36) meshing respectively on the pinions (34) and (35) .

 This phase shift is done by action on the axis (38) in operation.

 The ratios of the gears (34) (37) and (35) (36) are such that the movement on the axis () causes a rotation of the axis 2 with respect to the axis 5 in the same ratio of rotation of the weights 15 with respect to the weights 17.

 Figure 9> The phase shift is such that the resulting force of the rotating mass of the eccentric masses (14) and (17) is zero.

 The mechanical arrangement of eccentric masses (14) and (17) and the arrangement of these same masses around the axis result in the absence of parasitic torque around the axis Xr, the system is perfectly balanced dynamically.

Any intermediate position of the phase shift can be obtained and the device makes it possible to obtain
very simply a variation of the unidirectional vibration force from a zero value to a value
maximum F
Figure 10, the control members of the vibration force variation device
unidirectional have been completed to also change direction and this still during
the operation.

The main control arm of the force variation is composed of a handle (46), a
arm (45), the assembly (45) and (46) being integral with the axis 38.

 An indexing device with its return spring (40) and (41) makes it possible to join or not the arm (45) to the pinion (37).

 The pinion (37) is also secured to another arm (43) provided with a handle (44).

 When the assembly is engaged, index (40) depressed, the arms (45) and (43) rotate integrally together resulting in the force variation explained above.

 When the assembly is disengaged, with the index (40) extended, the movement of one arm (43) relative to the other (45) makes it possible to intervene only on one set of eccentric mass, E1 or E2, and modify accordingly the direction of the resulting unidirectional force.

 The index (40) being replaced after a change of direction, a solidarity action on the arms (45) and (43) will vary the value of the resultant force from a zero value to a maximum value F.

 It is represented in FIG. 11A -B and C, a particular principle of eccentric mass.

The mass (71) is part of the wheel (70) and the mass (72) is part of the wheel (74>
The position of the wheels on the axis (76) and the shape of the masses (71) and (72) are such that the resultant of each of the forces obtained by the rotation of these eccentric masses passes through the same plane YY 'which allows to eliminate any parasitic torque and to be dynamically balanced.

 The wheel (70) is mounted on a bearing or other means (75) to allow its relative rotation relative to the wheel (74).

 The two masses (71) and (72) are in phase opposition, FIG. 11A, and the resultant force of the pair of eccentric masses (71) and (72) is zero.

 By bringing the mass (71) in relation to the mass (72) by 1/4 turn or 90> the masses are in phase and cause a maximum resulting effect in the plane YYt, Figure 11 B.

 The phase shift from 0 to 180 of the force is therefore done by relative rotation of the masses (71) and (72) of only 90, interesting feature for the mechanical dimensioning of the elements and response times of the phase shift system.

 Given the principle adopted, the wheels (70) and (74) can rotate in the same direction, however, the principle shown in Figure 12 allows a reverse rotation of the wheels relative to each other.

 Masses (77) and (78) and wheels (70) and (74) are secured by any fastening means.

The shape and size of the masses (77) and (78) are such that they can rotate 12th
the other on the bearing (79) and in any direction, but also to have a product M xr mass M multiplied by the distance r from the center of gravity of the mass to the axis of the wheel, identical
Moreover, the resultant of the forces of each of the masses and therefore of the whole passes through the same plane YY ', so there is no parasitic torque> the whole is dynamically balanced
Figure 12 A, the masses are in phase opposition, the resulting forces of each of the masses are in opposite directions and produce a zero resultant force.

 Figure 12 B> the masses are in phase and produce the maximum force, in the plane YY '.

 The different kinds of multidirectional vibration, unidirectional and oscillatory can be combined in the same device, each of the vibration forces can be variable from zero to a maximum force.

 This device for generating and controlling vibration is shown in FIGS. 13-14-15-16.

The sets E1 and E2 each comprise a scoop of eccentric masses (61.1) (61.2) and
(62.1) (62.2) generating a multidirectional vibration.

 The sets E3 and E4 each comprise two sets of eccentric mass pairs (63.1) (63.2) and (64.1) (64.2) generating a unidirectional vibration.

 The assemblies E5 and E6 each comprise a pair of eccentric masses (65.1) (65.2) and (66.1) (66.2) generating an oscillatory vibration.

 Compared to the elementary systems described above, this device comprises intermediate creepers (67) and (58) composed of gearing and whose purpose is to increase the meshing diameter of the toothed gears (51 to 56) carrying the eccentric masses, this increase diamic makes it possible to increase the number of eccentric masses.

 The masses (61 to 66) are fixed on the axes (68) of the satellites and are fixed on one side and one of the toothed gears (51 to 56).

 The size of the masses and this particular arrangement make it possible to center the forces generated by the rotation of these eccentric masses along the same plane YY '.

 The generation of unidirectional forces is obtained by the rotation of eccentric masses (63.1) (63.2) and (64.1) (64.2) which rotate in opposite directions but at the same speed with respect to the axis XX '.

 The directional variation of the unidirectional force is obtained by maneuvering U1 and U2.

 The force variation of the unidirectional force is obtained by intervening on one of the U1 or U2 kiss leaving fixed the other arm U2 or U1.

 The generation of the mullitdirectional forces is obtained by the rotation of the eccentric masses (61.1) (61.2) and (62.1) (62.2) which rotate in the same direction and at the same speed with respect to the axis XX '.

The force variation is made by maneuvering the arm M2 the common arm M01 remaining fixed
The generation of the oscillating forces is obtained by the rotation of the eccentric masses (65.1) (65.2) and (66.1) (66.2) which rotate in the same direction.

 The variation of the oscillating torque is done by maneuvering the arm 02; the common arm M01 remaining fixed.

 The wheels (70) and (74) of the device shown in Figure 17 are provided with teeth and mesh respectively on the wheels R1 and R2.

 The flanges supporting the planet carrier axes (76), the wheels (70) and (74) equipped with their masses (71) and (72), are driven by a motor member (80) fixed on the fixed part (20). .

 The wheels R1 and R2 are respectively linked to the levers L1 and L2 whose action relative to each other allows the phase shift in operation of the wheels R1 and R2 and thus unbalanced sets (71) and (72).

The number of unbalanced sets (71) and (72) can be multiple and the example described in FIGS. 17-18 and 19 comprises two sets of four sets (70) and (74) each equipped with unbalances (71) and (
The masses (71) and (72) rotate in the same direction, the vibration force obtained is multidirectional centered on the axis of the device.

 Any combination remains possible between twice two sets, twice three sets, twice n sets, the sets being arranged around the axis XX 'so that the efforts are centered on the axis.

 A device using masses (78) and (77) rotating in the opposite direction and producing a unidirectional force variation vibration is shown in FIGS. 20 and 21.

 A first set El comprising the wheels (70) equipped with their eccentric mass (meshes with the wheel R1 to which is attached a control lever L 20.

 A second set E2 comprising the wheels (74) equipped with their eccentric mass <78) mesh on gears (81) and themselves on the wheel R2.

 The intermediate pinion (81) allows both a reversal of direction relative to the other ligot and moreover the meshing ratios are such that the masses (78) rotate three times faster and in opposite directions relative to the masses. (77).

 Each satellite composed of the pair (77) and (78) generates a unidirectional vibration and the resulting unidirectional force passes through the axis of the system and into the YT plane dynamically balanced.

 The wheel R2 is secured to the fixed frame.

 By action of the lever L 20, there is variation from zero to 180 of the direction of the unidirectional force.

 The device 20 is shown driven by electric motor fixed to the frame, any other drive mode was possible.

 The device 22 and 23 allows any combination of mulitidirectional vibration and / or unidirectional, each being variable from zero to a maximum value and using wheels and masses (77) and (78).

 The device comprises four sets of gears (E1, E2, E3, E4) each comprising, for the model described, three sets of gears and eccentric masses.

 The assembly El comprises three toothed wheels (70) meshing with the toothed wheel R11 to which a lever L1 is fixed.

 The assembly E2 comprises three toothed wheels (74) meshing with the toothed wheel R12 to which the lever L12 is associated.

 The masses (78.1) are integral with the wheels (74) via the axes (78-2).

 This mounting principle allows to shift the drive members while maintaining the center of rotating masses in the same plane YY '.

 Similarly, the assemblies E3 and E4 each comprise three toothed wheels and the associated masses which mesh with the wheels R21 and R22 via the intermediate gears (81) whose role is to reverse the direction of rotation of the assemblies E3 and E4 with respect to the sets E1 and E2, and to obtain an identical but opposite speed with respect to the sets E1 and E2.

 The two wheels R21 and R22 are associated levers L21 and L22.

 The sets E1 and E2 are arranged symmetrically with respect to the axis XX and with respect to the assemblies E3 and E4, FIG. 24.

 By intervening on the different levers with respect to each other, it is possible to obtain different vibration regimes.

 Figure 24 A zero vibration Figure 24 B maximum multidirectional vibration for sets E1 and E2 and zero for sets E4 and E3.

This multidirectional vibration is variable from zero to maximum by acting on the levers L12 and L11
Figure 24 C maximum unidirectional vibration.

 The unidirectional force variation can be obtained by acting simultaneously on the levers L12 and L21 with respect to the levers L11 and L22.

 For the device represented in FIG. 25, the satellites are no longer rotated by the flanges (6-8) which rotate, but these satellites are driven by the wheels (3.1 and 5.1) themselves driven by the coupling means (82). -83) fixed integrally to the axes (2 and 5) and therefore am wheels (3.1 and 5.1).

 The flanges (6 and 8) are fixed.

 There are known systems of phase shift coaxial phase shifters in operation whose axes can rotate in the same direction or in the opposite direction.

The combination of a phase-shifter of this type makes it possible to generate multidirectional or oscillating vibrations, driving the two axes in the same direction, or unidirectional vibrations, driving the two axes in the opposite direction, the external phase shift allowing in each case ,
to vary the vibration force from zero to the maximum value.

 Figure 26 shows a device with flanges (6-8) fixed but capable of generating several modes of vibratory forces, unidirectional-multidirectional-oscillating-mixed, in the same device, each of the forces being variable from zero to a maximum value.

 The device is shown with four sets of satellites (E1, E2, E3, E4) each having two or three or four or ... n satellites equipped with masses (77-78).

The toothed gears or toothed wheels of the satellites of each set mesh with the wheels R11-R12-R21-R22 which are respectively driven externally by means of coupling means (86-87-84 and 85).
There are phase shifters capable of rotating mechanical members and comprising several coaxial axes and each axis can be out of phase with respect to the others.

 This type of phase shifter associated with the device of Figure 26 allows the generation of any kind of vibration with the ability to adjust the force of each from zero to a maximum value.

- Example 1
* Wheels R11 and R12 rotating in the same direction
* Wheels R21 and R22 rotating in the opposite direction to each other.

 In this case, there is generation of multidirectional vibration with the sets E1 and with force variation and generation of unidirectional forces with the sets E3 and E4 i directional variation by shifting R21 relative to R22.

- Example 2
t R11 and R12 wheels turning in the same direction
* Wheels R21 and R22 turn in the opposite direction.

In this case, there is generation of unidirectional vibration if the sets (E1-E2) and (E3-
E4) have the same phase shift and force variation by simultaneously phase shifting the sets (E1-E3) with respect to (E2-E4)
This example also makes it possible to generate a multidirectional vibration alone, the sets (E3 and E4) being out of phase at 180 and the variation of force being obtained by phase-shifting El with respect to
E2.

Similarly, it is possible to simultaneously have a dose of unidirectional force with a dose of multidirectional force
This description is not limiting and other combined cases remain possible.

It is represented in FIG. 27, an independent vibrating unit consisting of a motor with two shaft ends, the motor receiving at each end a device represented in FIG.
The vibration forces are doubled compared to a single device.

A connecting pin 2 passing through the assembly links the wheels (3.1) of the two devices together
The wheels (5.1) are secured to the frame 20, accordingly a single lever 26 controls and controls the phase shift or the force generated by the vibrating assembly.

 One can also imagine to mount at each end of the shaft more complex devices such as those shown in Figure 22.

Claims (9)

 1) Device allowing the control and the action of vibratory effects on machines and materials in particular for the treatment of products intended to be vibrated, crushed, compacted, separated, characterized in that it consists in positioning from at least two coaxial axes (2-5) two flanges (68) and an envelope (7), said flanges allowing the positioning of several sets of several satellites (El, E2, E3 .... En) unbalanced (17.1, 17.2 17.n) (14.1,14.2 14.n) and pinion gears (15.1, 15.2 15.n) (16.1, 16.2 16.n), said toothed gears meshing directly or indirectly with the gears (3.1 to 5.1) integral with the coaxial axes (2-5), meshing said toothed gears and said gears causing the rotation of the unbalance satellites to generate, depending on their number and opposition, unidirectional, multidirectional oscillatory or mixed vibratory forces, coaxial axes being associated with d phase-shifting means acting continuously or discontinuously. 2) Device according to claim 1, characterized in that the flanges (86) are rotating and driven by sleeve (8.1), the toothed gears (15-16) rotating by meshing on the coaxial gear wheels (3.1 to 5.1), said non-rotating toothed wheels being integral with the coaxial axes (2-5) which by angular displacement causes the phase shift of the satellites of the assemblies (El, EL .... En) 3) Device according to claim 1, characterized in that the toothed wheels (3.1-5.1) integral with the coaxial axes (2-5) are rotated and driven by drive means (82- 83-84-85-86). ) fixed in Icurs extremities, the flanges (8-6) fixed rst, and said coaxial axes and said drive means being associated with external phase shift means. 4) Device according to claim 2 characterized in that the satellites of a set E rotates in the opposite direction of that of the flanges (6-8) are driven by an intermediate gear (31) Qlpt reports allow to obtain an identical speed but inverse to that of the other satellites by another set E, with respect to the axis XX 'of the device and generating a unidirectional vibratory force, the speed adaptation being also done by adaptaion of the diameters of the wheels and gears. drive (3.1 - 5.1 - 15 - 16 ct 31) and in that the satellite phase shifter comprises a gear train (34-35-3 & 7) whose compensc ratio cclui the intermediate pignonneric (31) and allows phase shift conta in operation of the unidirectional vibratory force.  5) Device according to claim 4 characterized in that each satellite (E1, E2, E3 .............. En) comprising a toothed wheel (3.1-3.2 3.n) (5.1, 5.2 5.n) each connected to a phase shift lever (43-44-45-46) comprising an indexing device (40-41) and allowing either to change the direction of the unidirectional force or to vary the force unidirectional vibratory zero to the maximum value or both simultaneously. 6) Device according to claim 1 characterized cn that the different sets of satellites can generate different vibratory forces, multidirectional, unidirectional, oscillatory, but the degree of force can be controlled independently of one set compared to the others by action on separate phase shift levers (U1-U2-M01-M2-02)> intermediate gears (54 (67) to increase the spacing of the satellites and therefore their number. 7) Device according to any one of claims (1 to 6) characterized in that the eccentric masses being in the form of sectcurs 90 (71-72), fixed inside the pinions (70-74) One of the pinions being freely mounted on the axis (75-76),  and in that the phase shift of 180- of the masses (71-72) takes place by a rotation of only one of the gears with respect to the other (70-74) the shapes and size and position of the masses. and pinions (71-72) and (70-74) that there is complete absence of parasitic torque whatever the position of the masses, and a resultant force located in the median plane YY ', the masses (71-72) being dynamically balanced in the YY plane. 8) Device according to any one of claims (1 to 6) characterized in that the eccentric masses are in the form of concentric sectors (77-78) of shape and dimension such that the products of their mass by the distance dc center of gravity in the center of the gears are the same and in that these sectors can turn in the same direction or in the opposite direction, and thus generate multidirectional or unidirectional vibrations> each of the balanced gears being freely mounted on the axis (79) and the sizes and positions of the masses and gables (77-78) and (70-74) that there is no parasitic torque whatever the position of the masses, and a resultant plug located in the median plane YY ' the masses (77-78) being dynamically balanced in the plane YY '. 9) Device according to claim 2 characterized in that a motor member comprising two motor shafts, one at each end, is each equipped with a vibrating device with flanges (68) rotating and may comprise satellites generating unidirectional vibratory forcesmultidirectional or oscillating, separately or in combination,  and in that the two vibrating devices are interconnected by a central axis (2) or several, itself or themselves related to phase shift devices, this central axis or these coaxial axes acting synchronously on both devices.