VIBRATORY SYSTEM HAVING AN OSCILLATING PLATE

Abstract

Some embodiments are directed to an oscillating system including at least one drive motor for driving a spindle about an axis of rotation, a first plate cooperating with a second plate, wherein the first plate is inclined with respect to the axis of rotation, in that the second plate is ball-jointed on a second axis that is offset with respect to the axis of rotation, creating an amplitude of oscillations in the spindle, in that at least one of the two plates is driven by the drive motor, and in that the two plates rotate at different speeds. The combination of the inclination of the first plate and the eccentricity of the center of rotation of the second plate makes it possible to create an oscillation in the spindle while it rotates.

Claims

1. An oscillating system, comprising: a spindle; at least one drive motor configured to drive the spindle about an axis of rotation; a first plate and a second plate, the first plate cooperating with the second plate, the first plate being inclined relative to the axis of rotation, the second plate being ball-jointed on a second axis, which is offset relative to the axis of rotation, thus creating an amplitude of oscillations in the spindle, such that at least one of the two plates are driven by the drive motor, and the two plates rotate at different speeds.

2. The oscillating system as claimed in claim 1, wherein the two plates are in contact by balls.

3. The oscillating system as claimed in claim 1, wherein the amplitude of the oscillations is adjustable.

4. The oscillating system as claimed in claim 1, wherein the inclination of the first plate is adjustable.

5. The oscillating system as claimed in claim 3, wherein the offsetting of the second axis relative to the axis of rotation is adjustable.

6. The oscillating system as claimed in claim 1, wherein the number of oscillations per rotation is adjustable.

7. The oscillating system as claimed in claim 1, wherein the plates are driven by different motors.

8. The oscillating system as claimed in claim 6, wherein the plates are driven by a gear train.

9. The oscillating system as claimed in claim 2, wherein the amplitude of the oscillations is adjustable.

10. The oscillating system as claimed in claim 2, wherein the inclination of the first plate is adjustable.

11. The oscillating system as claimed in claim 3, wherein the inclination of the first plate is adjustable.

12. The oscillating system as claimed in claim 4, wherein the offsetting of the second axis relative to the axis of rotation is adjustable.

13. The oscillating system as claimed in claim 2, wherein the number of oscillations per rotation is adjustable.

14. The oscillating system as claimed in claim 3, wherein the number of oscillations per rotation is adjustable.

15. The oscillating system as claimed in claim 4, wherein the number of oscillations per rotation is adjustable.

16. The oscillating system as claimed in claim 5, wherein the number of oscillations per rotation is adjustable.

17. The oscillating system as claimed in claim 2, wherein the plates are driven by different motors.

18. The oscillating system as claimed in claim 3, wherein the plates are driven by different motors.

19. The oscillating system as claimed in claim 4, wherein the plates are driven by different motors.

20. The oscillating system as claimed in claim 5, wherein the plates are driven by different motors.

Description

BRIEF DESCRIPTION OF THE FIGURES

[0027] Other advantages will also be able to become apparent to one of ordinary skill in the art from reading the following examples, illustrated by the appended figures, and given by way of example:

[0028] FIG. 1 represents a schematic view of the vibratory system according to some embodiments;

[0029] FIG. 2 is a view in perspective of the vibratory system;

[0030] FIG. 3 is a view in cross-section of FIG. 3.

DETAILED DESCRIPTION OF EXEMPLARY EMBODIMENTS

[0031] The diagram of the system 1 according to some embodiments illustrated in FIG. 1 includes: [0032] a first plate 2 placed on an axis of rotation 10 by use of a finger ball-joint connection 20; [0033] a spindle 4 secured on the axis 10; [0034] a second plate 3, which is placed opposite the first plate 2, and is ball-jointed around a center of rotation 30 in a ball joint support 31. The second plate 3 preferably has rounded edges 35 which slide freely in a rounded rim 310 of the ball-joint support 31.

[0035] The ball joint support 31 rotates around the axis 10, and in this case is driven by the ring of the epicyclic train 32. FIG. 3 shows that the satellite-holder 11 of the epicyclic train is fixed. The speed ratio between the input planetary gear and the output ring is equal to 0.5 in the present case.

[0036] The second plate 3 includes balls 33 which constitute a bearing, and remain in contact with the first plate 2.

[0037] The center of rotation 30 is placed on an axis 34 which is offset relative to the axis of rotation 10 by a distance .

[0038] The first plate 2 has inclination which can be regulated by an endless screw 21 which cooperates with teeth 50 arranged on a peripheral edge 52 of a regulation wheel 5. The latter has one of its two faces 51 inclined relative to the axis 10, and forms a maximum angle equal to half of . The plate 2 has two faces 22 and 23 which form between one another a maximum angle equal to half of . The finger ball-joint connection of the plate 2 to the axis 10 makes it possible to keep the two inclined faces 22, 51 parallel. Thus, the face 23 is itself inclined relative to the axis 10 by an angle equal to , which depends on the two inclinations and on the angular position of the wheel 5 relative to the plate 2, which can be up to a maximum of .

[0039] A description will now be provided of the operation of the vibratory system.

[0040] The spindle 4 is rotated by a drive motor (not represented) of the machine in which the vibratory system 1 is integrated. By rotating the regulation wheel 5 by use of the endless screw 21, it is possible to arrange the two inclined slopes 51, 22 staggered or with opposite inclinations. Thus, the face 23 of the plate 2 becomes perpendicular to the axis 10 (=0). Apart from this staggered arrangement of 51 and 22, the angle is non-zero. It is thus possible to regulate the inclination of the first plate 2, and maintain said the plate 2 in position. During operation, the first oscillating plate 2 is considered in complete connection with the spindle 4. The first plate 2 will then impart axial vibration to the spindle 4.

[0041] The second plate 3 includes balls 33 accommodated on its face 36 opposite the first plate 2, in order to transmit forces to the frame and to ensure that the oscillating plate 2 has a flat support, regardless of the inclination of the plate. The second plate 3 is accommodated in the ball-jointed support 31. In this configuration, the ball-jointed support 31 is in pivot connection with the satellite holder 11 or with a frame 11.

[0042] The advantage of this design is to have offset the center of ball-jointing of the second plate 3. Because of this offsetting, the axial position of the center of the ball joint 30 will be sensitive to the inclination of the oscillating plate 2. The resulting amplitude of the vibrations is provided by the following equation:

Amp.sub.vib (mm)=2.Math..Math.tan()

[0043] The amplitude of the oscillations can be adjusted by changing the inclination of the oscillating plate 2 or the value of the offsetting of the second plate 3.

[0044] The frequency of vibration is derived from the speed differential between the oscillating plate 2 and the second plate 3. When the latter is fixed relative to the frame 11, the number of oscillations per revolution of spindle is equal to 1. By use of the intervention of an epicyclic train, the second plate 3 can rotate at a speed different than that of the spindle 4. It is thus possible to modulate the frequency of the oscillations, or even to cancel them out. The number of oscillations per rotation is provided by the following equation:

[00001]${\mathrm{Fq}}_{\mathrm{vib}}\left(\mathrm{oscillations}.Math.\text{/}.Math.\mathrm{revolution}\right)=\frac{.Math.{\mathrm{Fq}}_{\mathrm{rotations}.Math..Math.\mathrm{of}.Math..Math.\mathrm{spindle}}-{\mathrm{Fq}}_{\mathrm{rotations}.Math..Math.\mathrm{of}.Math..Math.\mathrm{stop}.Math..Math.\mathrm{support}}.Math.}{{\mathrm{Fq}}_{\mathrm{rotations}.Math..Math.\mathrm{of}.Math..Math.\mathrm{spindle}}}$

[0045] A return spring (not represented) can be added to the system in order to maintain the contact between the different units in the absence of force on the spindle.

[0046] This system has the following advantages: simplicity of the vibratory system, reduced dimensions, and the possibility of modulating the amplitudes and frequency of the oscillations, without dismantling the system.