FI60982C - MOTVIKTSANORDNING - Google Patents

Description

[ΰ5τ * 1 M (H) MONTH, UL, tA, * u 60982

I lJ 1 'utlKggninosskrift C .... Patent ayönrselty 10 05 1902 • »uv {45}

Patent issued '(51) Kv.ik.3 / int.ci.3 B 06 B 1/16 »E 01 C 19/38

FINLAND —FINLAND (21) P «* nttlh» k «im» -Paunttn.eknln | 80011U

(22) Htk «mltptlvi - Antöknlnpdag 15-01.80 ^ ^ (23) Aikupilvi - Gllcl (h« t * d «f 15-01.80 (41) Tullut luikituksi - Bllvlt offuntllg l6.07 · 8l

After the patent and registrar administration, the blanket was stacked on the date of the stack. -

Patent · och registeratyralsan · Antttktn utbfd och utUkrMtun puMicurad 29 - 01.82 (32) (33) (31) Wiped Uterity — Bigird prlorltut (71) Insinööritoimisto Ilkka Hämäläinen Oy, Hämeentie 6 A, 00530 Helsinki 53 (Finland-Finland) 72) Ilkka Hämäläinen, Helsinki, Finland-Finland (FI) (7 ^) Papula Rein Lahtela Oy (5M Counterweight arrangement - Motviktsanordning

The invention relates to a counterweight arrangement for changing the center of gravity of a rotating machine member of a vibrator and adjusting the amplitude of the vibrator, in comparison to each other.

The compaction effect of dynamic soil compaction machines and vibrators is based on the static surface pressure caused by the machine's own weight and the dynamic vibration transmitted from the machine to the ground. The depth of action of static surface pressure can reach up to 30 cm and the depth effect of dynamic vibration up to 100 cm. The effect of dynamic vibration reduces the friction between the earth particles, causing the earth particles to move to a more compact state due to the static surface pressure of the machine. The internal friction of the earth particles is most effectively reduced by the oscillation frequency. with at least the characteristic vibration of the material to be compacted Λ • »· ♦ 2 60982 L, with different soil types 1100 - 2200 1 / min. The effect of the depth of the dynamic vibration depends on the weight and amplitude of the machine used. Achieving the best possible sealing power requires adjustment of the oscillation frequency and amplitude. Thus, for example, effective compaction of asphalt requires a change in amplitude according to the thickness of the layer to be compacted, for example a layer thickness of more than 6 cm requires a high oscillation frequency and a high amplitude.

The oscillation frequency of the soil compaction machines currently in use is adjusted by adjusting the oscillation frequency of the motor rotating the vibrating shaft, which gives the vibrating roller a vibrating motion, e.g. between 0 and 2000 1 / min. The amplitude of the vibrator can be changed by changing the eccentric or counterweight giving the vibrating roller an oscillating motion according to the desired oscillation amplitude.

German Offenlegungsschrift No. 1,245,188 discloses an eccentric oscillating motor in which an inner shaft is provided inside the motor shaft, provided with counterweights and means for transmitting a back pressure at a phase angle relative to one another. The design requires a hollow drive shaft of the drive motor and a complex shaft system with actuators. German application 2,545,539 discloses an oscillating motor in which the motor shaft is provided with a fixed, eccentric counterweight and a rotatable, as well as eccentric counterweight which can be rotated relative to a fixed counterweight by means of an actuator. The actuator turns and moves the latter counterweight while the engine is running and / or stopped. The drive is very complex in structure. U.S. Patent Nos. 3,172,303 and 3,468,189 disclose counter-30 weight arrangements for balancing drive motors. The arrangements require special, mono-complex drive equipment with separate drive and adjusting screws (US 3,172,303) and a hollow drive shaft as well as complex drive equipment (US 3,468,129).

It is an object of the present invention to provide a counterweight arrangement for adjusting the amplitude of a vibrator so that the adjustment can be performed while the vibrator is in use. It is a further object to provide a counterweight arrangement which does not include a hollow drive shaft and which is substantially simpler in construction and reliable in operation.

With regard to the features characteristic of the invention, reference is made to the characterizing part of the main claim.

The invention is based on a shaft provided with two different pitches, the counterweights of which are supported by means of guides. When the shaft is moved in its axial direction and the counterweights are supported in place in their axial direction, the guides rotate the counterweights relative to each other in a certain phase angle. Thus, the position of the counterweights, i. the phase angle with respect to each other can be changed and adjusted from the shaft, e.g. by means of a drive member.

The counterweight arrangement according to the invention makes it possible to change the center of gravity of the counterweights placed eccentrically on the axis of the vibratory roller of the vibrator, i. adjusting the amplitude of the vibration motion of the vibrator with its counterweights' to form a rotating vibrator providing vibration to the vibrator.

The invention will now be described in detail by means of exemplary embodiments with reference to the accompanying drawing, in which Figure 1 schematically shows a counterweight arrangement according to the invention, Figure 2 shows a vibrating roller with counterweight arrangement according to the invention, and Figure 3

The counterweight arrangement shown in Fig. 1 comprises an axle 30 provided with a former and a latter counterweight eccentric 2 and 3 to the shaft. The shaft 1 is formed with threads 4 and 5 having different angles of inclination. 6 and'7 (not shown). When the shaft 1 is movable in its axial direction, the threads are forced to guide the counterweights to the phase angle with respect to each other. The structure is simple and reliable.

«4 60982

Figure 2 shows a vibrating roller incorporating the counterweight arrangement of Figure 1. In this case, the movement of the counterweights 2, 3 and 2 ', 3' in the axial direction of the shaft 1 is prevented by the constraints 8, 9, and 8 'and 9' 5 formed by the bearing housings of the roller 11. When moving the axis 1 in the axial direction, e.g. by means of the drive member 17, the shaft moves under the control of the parallel displacement joints 14, 14 ', whereby the differential pitch threads 4 and 5 of the shaft force the counterweights 2, 3 and 2', 3 'to a certain phase angle with respect to each other by means of guides (not shown) . The displacement of the counterweights 2, 3 and 2 ', 3' in the axial direction of the shaft 1 is prevented by the stops 8, 9 and 8 ', 9', respectively, against which the counterweights are pressed as the shaft 1 rotates.

The guides 6 and 7 of the counterweights 2 and 3 supported on the threads 4 and 5 of the vibrating roller shaft 1 shown in Fig. 2 are shown in Fig. 15 in a partially sectioned view. Threads 4 and 5 have different pitch angles, in this application the thread 4 is right-handed and the thread 5 is left-handed. The threads 4 and 5 form guide grooves of rectangular cross-section on the surface of the shaft, on the side walls of which the shoulder-shaped guides 6 and 7 20 of the counterweights 2 and 3 rest.

As the phase angle of the counterweights 2, 3 changes, the mass of both counterweights and the total mass of the counterweights remain constant. Instead, the position of the center of gravity of the whole system, the counterweights 2 and 3, i. the distance of the center of gravity from the axis 1 changes. As the counter-weights 2 and 3 rotate about the support axis 1, the counterweights cause a centrifugal force Ä and B. The sum of the centrifugal forces Ä and B, i.e. the resultant R, is determined by the centrifugal forces, i. as the sum of the vectors A and B, i.e. R = Ä + B i.e. 30.

/ ** 35 The central phase angle 0 <of the counterweights can vary between 0 and 180 °, in practice e.g. 0 - 90 °.

The roller shown in Fig. 2 comprises a vibratory roller 11 supported by vibration dampers 15 and 15 'of a vibratory roller size (not shown). The vibratory roller 11 further comprises a drive motor 10, e.g. a vibrating shaft 1 rotatable by bearings by means of a hydraulic motor according to the invention. with a counterweight arrangement, i.e. with counterweights 2, 3 and 2 '3'. When rotating an eccentric shaft 1 of eccentricity, this eccentricity causes an oscillating force corresponding to the rotational speed of the rotational movement transmitted to the vibrating roller 11 by means of bearings 13. rotating counterweights 2, 3 and 2 ', 3' to a phase angle corresponding to the displacement of the shaft with respect to each other by means of guides 6, 7. The changed phase angle of the counterweights 2, 3 and 2 ', 3', respectively, causes a change in the centrifugal force generated by the common mass of the counterweights with respect to the axis 1, which changes the amplitude of the oscillation axis and thus the vibration roller.

The drive member 17 by means of which the shaft 20 is moved in the axial direction can consist, for example, of a hydraulic, pneumatic, mechanical or any other power device, such as known as shaft transfer devices. Further, the drive member 17 may include a locking member or device to prevent unwanted self-displacement of the shaft in the axial direction. The eccentrics 2, 3 and 2 ', 3' are immobilized suitably in the axial direction of the shaft 1.

The working examples are intended to illustrate the invention without limiting it in any way.

30 35 «

Claims (3)

60982 6 A counterweight arrangement for changing the center of gravity of a rotating vibrating machine member and adjusting the vibration amplitude, the counterweight arrangement comprising a shaft (1) provided with an eccentric counterweight (2, 3) rotatable relative to the axis and at least one of the counterweights rotatable relative to the axis and the arrangement comprises means for moving the counterweights to a phase angle with respect to each other, characterized in that the shaft (1) is provided with two threads (4, 5) of different pitches, the counterweights (2, 3) are each provided with a guide (6) supported on the pitch thread of the shaft , 7), and that the shaft is movable in its axial direction so that the differential pitches of the shaft forcibly guide the counter-weights to move to the phase angle with respect to each other by means of guides. Counterweight arrangement according to Claim 1, characterized in that the threads (4, 5) of the shaft are of different hands. Counterweight arrangement according to Claim 1 or 2, characterized in that the movement of the counterweights (2, 3) in the axial direction of the shaft 1 (1) is limited by stops (8, 9) and that the shaft is provided with a drive element (17). 25 30 t • · 35 4. ♦