DE2908393A1 - DEVICE FOR THE AMPLITUDE CHANGE OF IMPULSES THAT ARE TRANSFERRED FROM A MECHANICAL RUETTLER TO A RUETTEL MACHINE - Google Patents

Description

PATENT Attorney E. DR.-ING. H. H. WILHELM-DIPL.-ING. H. DAUSTER D-7000 STUTTGART 1 - G Y M N A S I U M S T R A S S E 31 B - TELEPHONE (0711) 291133

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Applicant :

VENANZETTI VIBRA.ZIOKI SpA
5, via Lazzaretto

Milan / Italy

Device for changing the amplitude of pulses transmitted from a mechanical vibrator to a vibrating machine

will

The present invention relates to a device for changing amplitudes the impulses given to a vibrating machine by a mechanical vibrator acting in one direction, of the type that there are at least two pairs of shafts arranged in parallel and rotating at the same speed and each individually provided with the same eccentric mass, with the shafts of each pair below them are connected by means of corresponding gears, at least one motor is connected to one of the wools of a pair and there is a kinematic connection between a shaft of one pair and a shaft of the other pair for the rotational movement to transfer from one to the other.

It is known that such mechanical, unidirectional

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Vibrators develop a force in the same direction, the amplitude of which changes from a positive maximum value to passes through a negative minimum value equal to zero.

Because of their structural and functional characteristics, they are widely used, especially in the field of Vibrating screens, as well as conveyor and feed vibrators for im general loose material.

Although such use is generally satisfactory, it has, on the other hand, been found in cases where a standstill and start-up of the jogger often follow one another (for certain types of sieves, for example, JO to Starts and stops per hour required) that the vibrators of the aforementioned type have a greater inertia imposes limits on their application. Since, in addition, the energy consumption of the motor, the drives the vibrator is higher, its use also entails higher energy costs in cases that require frequent shutdowns and require starting.

In addition, in the case of application to conveyor systems, a major functional limitation is found when e.g. such conveyors are used to load the loading hoppers of weighing devices. ·

In such cases it is known that after a rough loading With the material to be weighed, the desired weight is finally achieved by slowly feeding the material until loading is interrupted, even with the exact weight. For such applications the. with the conveyor connected vibrators can reduce the amplitude of the transmitted pulses in a controlled manner to suit the various To meet requirements that are normally not achieved with the known vibrators.

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The purpose of this invention is to enhance the performance of the to expand mechanical unidirectional vibrators so that they are particularly suitable for those applications in which for example frequent shutdowns and restarts or one Dosing of the material in conveyor vibrators for loading of weighing devices, volumetric dosing or even a control of the bed for the material to be conveyed required are.

In the invention it was assumed that in a vibrator, which is composed of two pairs of shafts arranged in parallel, which rotate together with corresponding eccentric masses of the same type attached to them at the same speed, different states of a resultant force acting on the vibrating machine can be generated if at one Pair of eccentric masses a phase shift is made with respect to the other pair.

In this way, resulting forces can then be generated, the intensity of which has a maximum value corresponding to the sum of all individual maximum forces up to the total reduction of the intensity is enough, if the individual resultants with regard to each of the rotating eccentric masses are opposed to each other.

The object on which the invention is based is therefore the mechanical, unidirectional vibrators Above-mentioned type a device, also mechanical, to be provided, which changes the amplitude of the vibrating machine impacting impulses of a maximum value are allowed until they are possibly canceled without shutting down the vibrator and whose drive motor would be required.

The object is achieved according to the invention in that the kinematics

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table connection between a shaft of a pair and a shaft of the other pair of a pair of engaged " There is gears, each of which is kinematically connected to the shaft of the corresponding pair of shafts with eccentric mass and thereby rotates therewith, one being arranged movably with respect to the other for rolling about their engagement surfaces.

The invention is based on a preferred embodiment shown in the drawings and described below. Show it

Pig. Figure 1 is a schematic perspective view of the device according to the invention, in position a maximum transmitted force;

Fig. 2 is a schematic perspective view of the same device as in Pig. 1, in the position a transmitted force equal to half of the maximum force;

Pig. 3 is a schematic, perspective view of the device according to the above figures, in the position of a transmitted force that is equal Is zero;

Pig. 4 is a schematic, perspective view of a variant the device according to the invention, in the position of a maximum transmitted force;

Pig. 5 is a schematic perspective view of the same Device as in Pig. 4, in the position of a transmitted force which is equal to zero;

Pig. 6 shows the plan view of a further variant of the device according to the invention and

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FIG. 7 shows a section along the line VII-VII of the device according to FIG. 6.

With reference to the "attached figures," 1 was the carrier a conventional vibrator marked with four shafts and the shafts themselves with 2, 3, 4 and 5. One such The vibrator is operated by means of the connecting elements or flanges 6 and 7 on a vibrating machine of conventional design, and therefore not shown attached. Such a jogger can be, for example, a vibrating table, a sieve or, in general, a vibrator conveying or feeding device.

On each shaft of the vibrator, corresponding eccentric masses 8, 9, ^ O and 11 equal weight are attached, which from Balance reasons in the example shown in two elements divided on opposite sides of the carrier 1 are arranged on the corresponding shafts. Waves 2 and 4- are Kinematically connected to each other via the gears 12 and 13, while the shafts 3 and 5 analogously by means of the gear pair 14- and 15 are connected to each other. The gears 12, 13, 14 and 15 ensure a synchronous rotary movement of the connected Waves. The vibrator shown can thus be viewed as a mechanical, unidirectional vibrator with four shafts or as a set of two unidirectional vibrators with two shafts that are coupled to one another can.

With reference to Figures 1, 2 and 3, shafts 2 and 3 are above Couplings 16 and 17 are correspondingly connected to the extension shafts 18 and 19, the shaft 18 in the embodiment shown telescopic type. Accordingly, the coupling 16 is an articulated coupling of the universal joint type. The shaft I9 is via the further coupling 20 with the pin 21, which is mounted in the fixed supports 22. At the

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Pin 21 is attached to a gear 23 which is set in rotation by an electric motor 24 at the desired speed whose shaft 25 is connected to the pin 21 via coupling 26. A lever 27 is rotatable on the same supports 22 stored, the axis of rotation of which coincides with the longitudinal axis of the pin 21 and that of the shafts 19 and 3. The lever 27 carries a second toothed wheel 28 which is fastened on the pin 29 mounted in the same lever 27. Said pin 29 is connected to the telescopic shaft 18 via a further cardan shaft 30 tied together.

The gears 23 and 28 are in mesh with one another, so that the rotary movement communicated by the motor 24 to the shaft 3 <ies Eüttler is also transferred to shaft 2 of the same vibrator. Correspondingly, shafts 4 and 5 also rotate offset.

At the free end of the lever 27 there is a rack 31 in the shape of a circular arc attached. This rack is in engagement with a pinion 32 which is mounted on a corresponding selector shaft 33 is arranged, this being done by hand via a conventional handwheel, not shown, or via a likewise not shown Auxiliary engine can be operated.

From what has been described above, it can be seen that the rotational movement of the shaft 33 and thus rotation of the pinion 32 the movement the rack 31 is determined and thus also the desired Angular displacement of the lever 27 about the axis of the Pin 21. The gear 28 is thereby depending on the amount of angular displacement of the lever 27 over the toothed circumference of the gear 23 is rolled. The telescopic shaft 18 can follow the movement of the lever 27 by becoming longer and shorter, corresponding to the positions assumed by this lever, as can be seen from FIGS. 1 and 3 with reference to FIG which the lever 27 has assumed a horizontal position. 3PoIg-

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The eccentric mass pairs 8 "and 10 on the shafts can be borrowed 2 and 4 assume different phase shifts with respect to the eccentric ones attached to shafts 3 and 5 Masses 9 and. 11 while the vibrator is constantly in motion. In particular, operating states can be realized in which (FIG. 1) the eccentric masses are in phase step with one another and the resulting amplitude of the pulses emitted to the vibrating machine via carrier 1 have a maximum value or the eccentric masses are in the opposite phase (Fig. 3) and the resulting amplitude of the transmitted Impulse is equal to KuIl, although the vibrator is constantly in motion.

Of course, all intermediate states can also be reached, such as the one in the Pig. 2 where the phase shift is shown of the eccentric masses is such that the resulting amplitude of the transmitted pulses is equal to half the maximum value is. The angular displacement made on the lever 27 results in an angle of 90 ° in the illustrated case, which is equal to Sections is subdivided with respect to the horizontal lever position, so that a resulting amplitude is obtained, the is equal to half the maximum value.

According to FIGS. 4- and 5, the shafts 2 and 3 are on the couplings 116 and 117a with the corresponding extension shafts 75 and 119 connected. The shafts 75 and 119 are connected to the shafts 77 and 121 via the couplings 76 and 120a, which are shown in here not shown, since conventional supports are mounted. A gear 123 is attached to the pin 121, with the desired Speed is set in rotation by an electric motor 124 and its shaft 125 via clutch 125a, shaft 125b and clutch 126 is connected to the pin 121. On the same pin 121 is a lever, designated globally as 127, is rotatably attached, its axis of rotation with the longitudinal axis of the pin 121 and that of the shafts 119 and 3 coincide. The lever 127 takes a second gear

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128 on, which is attached to the pin attached to the same lever 127

129 is attached.

The gearwheel 128 is kinematically connected to the shaft 77 via a gearwheel 70 which runs along and is therefore in engagement, which rotates accordingly, by means of a pinion 71 which is mounted on the same shaft 77. The running one Gear 70 is with its pin 72 in the corresponding Center distances held with respect to gear 128 and pinion 71 by means of corresponding coupling rods 73 and 74- * one of which End 73a and 74a rotatably mounted on pin 129 and shaft 77, respectively is, while its other end 73b and 74-b on the pin 72 is rotatably mounted. The gears 123 and 128 are among themselves in engagement, so that the rotary movement communicated by the motor 124 of the shaft 3 of the vibrator is also transmitted to the shaft 2 of the same vibrator is transmitted. Correspondingly, the shafts 4 and 5 are also set in rotation.

At the free end of the lever 127, two elongated slots 127a and 127b are carved out, in which one on a runner 61 fixed pin 50 slides. The runner 61 is straight in the plane in which the lever 127 moves, and it is guided by a rod 62, the support thereof is not shown because of its conventional design, the rotor 61 by means of a spindle nut attached to it 64 is moved by a spindle 63. The spindle 63, which via the bearings 63a and 63b in a holder is conventional Art, and therefore not shown, is supported, is provided with a crank 65.

From what has been described above it can be seen that upon rotation of the spindle 63 and thus displacement of the rotor 61 the desired Angle! Displacement of the lever 127 about the axis of the pin 121 is achieved. According to the amount of angular displacement of the lever 127, the gear 128 is thereby over the toothed

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Scope of the tooth number ads 123 passed on. The rotating gear 70 follows, due to the action of the coupling rod 73, <ier movement of the gear 128 arranged on the lever 127, as from its position in Pig. 5 compared to the position in FIG. 4 emerges. The phase shift that the gear 128 experiences with respect to gear 123 due to the movement of the lever 127 is transmitted via the rotating gear 70 to the pin 71 and thus to the eccentric mass pair 8 and 10, while the vibrator itself is constantly in motion.

In particular, operating states can be achieved in which (Fig. 4-) the eccentric masses among themselves in phase step and the resulting amplitude of the pulses emitted to the vibrating machine via carrier 1 have a maximum value has or the eccentric masses are in the opposite phase step (Fig. 5) and. the resulting amplitude of the transmitted impulses is equal to KuIl, although the vibrator is constantly in motion. Of course, all intermediate states can also be used can be achieved, such as the state in which the phase shift of the eccentric masses is such is. that the resulting amplitude of the transmitted pulses is equal to half the maximum value.

The angular displacement of the lever 127 can also be done by other means can be achieved, e.g. with a hydraulic cylinder in a version with connecting pieces, without the area the present invention is departed from. According to the above For example, a second motor which is the same with respect to motor 124, albeit a counter-rotating motor, can be attached to journal 77 in order to to act directly on the eccentric masses 8 and 10. Under these conditions, gears 123, 128, 70 and 71 no drive power transmitted, they only serve the purpose of keeping the shafts 77 and 121 below them in phase opposition.

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Referring now to Figures 6 and 7, a modified version of the phase change mechanics the eccentric masses of the Eüttler is shown, with 34 and 35 two waves are marked, the waves and 19 of the Pig remarks. 1, 2 and 3 or the shafts 75 and 119 of the embodiments according to FIGS. 4 and 5. These Shafts are via the clutches 36 and 37 corresponding to the clutches 20 and 30 of FIGS. 1, 2 and 3 connected to the pins 38 and 39, which are mounted in opposite walls 40 and 41 of a housing-like receptacle 42. On the pins 38 and 39 are mounts the meshing gears 43 and 44, which correspond to the gears 23 and 28.

The assembly of these gears on the corresponding journals is achieved by means of a spiral groove coupling 45 and 46. The slope the spiral of the coupling element 45 is that of the coupling element 46 opposite, so that with an axial displacement of the gears 43 and 44 on the corresponding pin 38 and this perform an angular displacement with rolling over their toothed circumference. This development can occur during rotation of the gears 43 and 44 take place together with the corresponding pins, in the example shown the one with the reference number 39 provided pin is driven by means of a belt pulley 47 which can be conventionally connected to an engine, not shown, which is generally the engine 24 of the embodiments according to FIGS. 1, 2 and 3 corresponds.

Also with reference to Figs. 6 and .7 is inside the housing 42 housed a shaft 48 on which a fork-shaped element is mounted, which at the same time the flanks the gears 43 and 44 includes. The fork element 49 is received on the shaft 48 by means of a spindle nut in a conventional manner Kind, namely in such a way that an axial displacement of the fork element 49 is achieved when the shaft is rotated, and thus a displacement of the two gears 43 and 44. To their

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Actuation is the shaft 4-8 with part 50 to the outside of the housing 4-2 so that it can be fitted with a handwheel or connected to an auxiliary motor. To a To prevent twisting of the fork element 4-9 during its displacement, it is provided with a nose 51, which is attached to a rod arranged parallel to the shaft 4-8 and supported at the ends in the walls 4-0 and 4-1 of the housing 4-2.

With the mechanics shown in this way, phase changes in the eccentric masses of the vibrator can be exactly the same can be achieved, as has already been done for the device according to FIGS. 1, 2 and 3, or for the variant according to FIGS. 4 and 5 also with the the same results already mentioned was described. The particular advantage of the designs according to FIGS. 6 and 7 consists in the fact that here the relative development between the gears 4-3 and 44- without Winkelvers chi ebung one of the rotating shafts Gears themselves is achieved, as is done on the other hand in the proposed solutions according to FIGS. 1, 2 and 3. This allows a more compact design and greater reliability in operation .

Of course, the device according to the invention is also suitable for changing the frequency of the vibrator to the vibrating machine emitted pulses without affecting the change in amplitude. For this purpose it is indeed sufficient if the The speed of the motor 24- is changed by conventional means. With the device according to the invention, the Advantage achieved, regulate the amplitude of the resultant from the pulses delivered by the vibrator to the vibrating machine to be able to and still keep the vibrator constantly in motion.

In the event that a large number of starts and shutdowns (for example 30 to 60 starts per hour) from the

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Direction according to the invention is required, this operating mode can can be achieved without difficulty, since when regulating the phase position of the rotating eccentric masses without If the vibrator is stopped, the sieve can be quickly stopped and started again without the inertia being eliminated must be, as is the case with an effective shutdown of the rotating parts of the vibrator according to the known technology the pail would be. In addition, energy savings are also the result, since the considerably higher power consumption in the start-up phase of the motors driving the vibrator is no longer required. In case of In addition to the advantages of the device according to the invention already described, there is also another application in conveyor vibrators The advantage given that the amount of material conveyed can be dosed when the amplitude of the resultant from the Vibrator transmitted to the conveyor pulses is gradually reduced. This option is particularly useful in the case of vibrator feeds in devices for weighing or volumetric dosing.

The combined performances of the device are therefore largely able to meet the various demands placed on the vibrators. The dimensions can also be accordingly be adapted to the requirements and the performance required by the vibrator.

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Claims (9)

Expectations 1. Device for changing the amplitude of the pulses from a mechanical, unidirectional vibrator to be transmitted to a vibrating machine, consisting of at least two pairs of parallel shafts rotating at the same speed, each with a corresponding and equal eccentric mass is provided, the shafts of each pair having respective ones Gears are interconnected and at least one motor connected to one of the shafts of a pair is provided is as well as a kinematic connection between a shaft of one pair and a shaft of the other pair, to transmit the rotary motion from one to the other, characterized in that the kinematic connection consists of a pair of meshing gears (23, 28; 123, 128; 43, 44) of which each kinematically with the shaft · (2, 3) of the relevant one Shaft pair with eccentric mass is rotationally fixed and one relative to the other movable is arranged so that a relative rolling can take place over their engagement surfaces. §09838 / 0684 • 2- ^ 900393 2. Apparatus according to claim 1, characterized in that one (28, 128) of the gears (23, 28; 123, 128) of a lever (27, 127) is held, which is arranged pivotably about the axis of rotation of the other gear (23, 123) is, and means are provided to this lever (27, 127) with the gearwheel (28, 128) swivel at an angle and the gearwheel (28, 128) on the coupled gearwheel (23, 123) to be able to shift, so that a phase change is achieved between the gears themselves, with the on the gear attached to the lever kinematically is connected to the shaft of the corresponding pair, whereby this also runs. 3. Apparatus according to claim 2, characterized in that the gear (28) which is attached to the lever (27), kinematically is in connection with the shaft (2) of the corresponding pair, which by means of a telescopic shaft (18) runs along. 4. Apparatus according to claim 2, characterized in that the gear (128) fastened to the lever (127) is kinematically is connected to the shaft (2) of the corresponding pair and this rotates as a result of an intermediate gear (70), which with it and a pinion (71) on shaft (2) in the Is engaged, this revolving gear (70) by coupling rods (74- and 75) in the corresponding The center distance is maintained by this gear (28) on the lever (127) and the corresponding pinion (7Ό 5. Apparatus according to claim 2, characterized in that the means for the angular displacement of the lever (27) with the gear (28) consist of a circular-arc-shaped rack (31) which is attached to the free end of the lever (27) is, as well as from a tickle (32) that deals with the 909838/0684 -3- Rack (3I) is in engagement ", this pinion (32) is attached to an adjusting shaft (33) ″. 6. Apparatus according to claim 2, characterized in that the means for the angular displacement of the lever (127) with the gearwheel (128) from an axially in the plane of the Lever (127) displaceable and with this lever via an elongated hole (127a, 127b) there are engaged rotors (61) which are displaced by means of a spindle (63) and spindle nut (64) can be. 7. The device according to claim 1, characterized in that each of the gears (43, 44)> from which the kinematic connection is composed, by means of a spiral groove coupling (45, 46) on the corresponding pin (38, 39) is mounted, the direction of rotation of the spiral of a coupling opposite to the direction of rotation of the spiral of the other coupling is and actuating means are provided to simultaneously the gears for the relative Ehasenzustandswechsel to move in the axial direction on the corresponding pin. 8. Apparatus according to claim 7 »characterized in that as an actuating means for the simultaneous axial displacement of the gears on the corresponding pin a fork (49) is provided, the prongs of which rest on both sides of the side walls of the gears and these is arranged axially displaceably on a shaft (48) parallel to the journals of the gears themselves, with actuating elements are provided to move the fork on this shaft. 9. Apparatus according to claim 8, characterized in that the actuating elements for the displacement of the fork §09838 / 0684 -4- on the corresponding shaft from a coupling of the threaded spindle - Spindle nuts exist between the shaft (48) and fork (49), as well as a stop rod (52) which part of the fork circumference (49) is supported and thus blocking rotation of the fork. 909838/0684 -5-