The present invention relates to a method of compacting or densifying a material layer and a compacting machine for carrying out the method. A method and means are particularly intended here in which at least one drum acts on the material layer with a gravitational force and an oscillating force.

In conventional vibratory rollers or compactors, the vibration is obtained by means of a rotating eccentric means e.g. inside a drum or roller, the drum being given a substantially circular or elliptic path. In the prior art there is also apparatus with several coacting eccentric means for obtaining improved performance and decreased bearing stresses.

Other contributions to the art have been made, for example, by the Swiss patent 384019, which teaches arranging two eccentric means having opposing directions of rotation, so that the forces caused by the rotation will balance each other in the horizontal direction but supplement each other vertically. The purpose is to provide a directed effect with substantially vertical compacting force from the drum and substantially vertic¬ al drum movement.

The French patent 1166681 relates to a vibrating roller with at least two vibrators attached to the cylindrical

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surface of the drum. Each vibrator contains an eccentric mass which rotates in the same direction by means of power transmission from a central drive shaft in the drum. Harmonic frequencies are generated in the vibrat- ing movement of the drum by means of slipping or gliding in the power transmission.

Trials have shown that the number of alternations in the shear stress direction in a layer of material which is compacted has great importance for the degree of compac¬ tion achieved in the layer.

A conventional vibratory roller usually generates large, varying, vertical, downward force. This vertical force, per se, gives rise to shear stresses in the material layer, which vary in magnitude with the frequency at ^• which the eccentric means operates (referred to here¬ inafter as the "eccentric frequency"). However, the shear stresses do not change direction with the eccentric frequency, since no appreciable tensile stress can occur at the contact surface between roller and ground- A change in shear stresses direction occurs due to the static load, but only once per roller pass, when the roller slowly moves over the material layer.

In the article "A cyclic simple shear apparatus for dry granular material" in "Geotechnical Testing Journal", ASTM, Vol. 1, No. 2, 1978, Ansell and Brown have de¬ scribed simple laboratory equipment for testing purpose, where a static load is applied and where rapid alterna¬ tion in direction of the shear stresses in a material is achieved. Trials made with the equipment show that a better compaction effect is obtained than by convention¬ al techniσues.

The US Patent 3543656 relates to a vibratory roller with two drums, each supported in a yoke connected to a frame via vibration - damping material. An eccentric mass is

arranged in each yoke for rotating about a horizontal axis above the respective drum. This results in that a yoke, the drum mounted therein and the rotating eccentric mass are caused to move about• a horizontal axis situated between the axis of the drum and that of the excentric mass, which gives the lower portion of the drum a movement including a reciprocating component along the material layer.

An object of the present invention is to provide shear stresses during compacting a material layer, such that the stresses repeatedly and rapidly change direction in the material layer as the roller passes over the material.

A second object of the invention is to provide a compacting machine with a drum where the stresses from the drum on its mounting and on the rest of the machine will be comparatively small.

A third object of the invention is to provide a compact¬ ing machine where the movements in the material layer which is compacted will be substantially limited to a comparatively small volume in the material layer close to the machine.

A fourth object of the invention is to enable the con¬ struction of a compacting machine which consumes com¬ paratively little energy in order to achieve a pre- scribed degree of compaction in a material layer.

The invention is based on the idea of compacting or densifying a layer of material with '•the aid of a drum rolling on the material layer, said drum chiefly sub- jecting the material layer to downward gravitational forces of substantially constant magnitude and simul¬ taneously alternating forces of rapidly warying magnitude in the tangential direction of the drum. These

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alternating forces of rapidly varying magnitude are according to the invention achieved by applying a sub¬ stantially pure rapidly alternating torque to the drum about its shaft. Due to reaction forces from the material layer on the drum and when the drum is slowly moved or propelled conventionally along the material layer, the total absolute movements of the drum will be more complicated than a pure alternating turning motion about the drum axis. What is important to the invention and to the compaction, however is that a substantially pure alternating torque is applied to the drum about its axis, and that this torque causes rapidly alternating forces on the surface of the material substantially parallel to the surface irrespective of the rolling of the drum provided that the alternating frequency and torque magnitude are high enough in relation to the speed of rolling.

The novel and particularly distinguishing features of the invention, and the advantages thereof, as well as a more practical implementation of a compaction method and a compacting machine in accordance with the invention will now be described with reference to the appended drawings, where Figure 1 illustrates the compaction principle according to the abovementioned article by Ansell and Brown.

Figure 2 illustrates the principle of providing directed effect with substantially vertical compaction force and motion of the drum, with the aid of two eccentric means having opposing directions of rotationg, e.g. according to the above - mentioned Swiss Patent 384019.

Figure 3 is an attempt to illustrate compaction with two eccentric means in a compactor drum according to the above-mentioned French Patent 1166681.

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In conjunction with the previously mentioned laboratory experiments, Ansell and Brown have proposed a principle for compaction according to Figure 1, in which the whole drum is caused to vibrate horizontally for providing rapidly alternating shear stress. No further information is offered on how the horizontal vibration is to be provided in practice. ^•

There are many ways of generating the drum motion de- sired in compacting a material layer conventionally or in accordance with the invention. In describing the basic principles and ideas behind compacting machines according to the above-mentioned article and the patent specifications, as well as in accordance with .the invention, it is assumed for the sake of simplicity that the drum movement in Figure 2-5 is provided with the aid

^: of rotating eccentric masses.

As illustrated in Figure 2, vertically directed force and drum movement, e.g. according to the Swiss Patent 384019, is provided with the aid of two eccentric masses 2a, 2b each attached to, and rotating with a shaft 3a, 3b in the drum 1. The shafts 3a, 3b are mounted so that they only accompany the translation movements of the drum but not the turning movements thereof about its center.

The masses are the same and the shafts are at equal spacing from the axis of the drum. With their respective shafts 3a and 3b the eccentric masses 2a and 2b respec¬ tively, rotate synchronously at the same rate but in opposite directions. Accordingly, 2a and 3a rotate clockwise, while 2b and 3b rotate ^" -anticlockwise syn¬ chronously and with the same rpm as 2a and 3a.

This rotation causes the masses and drum to exercise forces on each other via the shafts. This interplay of

^- ^' forces is illustrated in the figure by vectors from the

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Figure 4 attempts to illustrate in a somewhat simplified form compaction according to the above-mentioned US Patent 3543656.

Figures 5A-D illustrate the basic idea behind the present invention and the application of a substantially pure alternating torque to a drum about its axis.

Figure 6 illustrates, heavily simplified, a self propelled compacting machine with propulsion on the rear wheels and forwardly provided with a compacting drum in accordance with the invention.

Figure 7 illustrates, heavily simplified, a method and means for applying a substantially pure alternating torque to a drum about its axis.

Figure 8 is a side view of a compacting machine in accordance with the invention, intended for towing by a vehicle.

Figure 9 is a partial section through an embodiment of a compactor in accordance with the invention.

Figures 10A-B are heavily simplified illustrations of how a compacting .machine in accordance with the inven¬ tion can be formed so that it can be optionally set for conventional compaction or compaction in accordance with the invention.

Figures 11 and 12 illustrates an alternative embodiment of the invention.

Figures 13-18 are graphs illustrating measured results and quantities in compaction tests with an embodiment of the compacting machine in accordance with the invention.

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centres of the respective masses directed outwardly from the centers of the respective shafts. The direction of the forces varies synchronously with the angular posi¬ tion of the masses during rotation. The mutual orienta- tion of the 'masses 2a and 2b during their synchronous rotation at the same rpm, i.e. their phase position relative each other, is intentionally selected so that the forces on the drum coact vertically but counteract each other horizontally. On rotation, the eccentrically mounted masses do not affect the drum with any resulting oscillating torque about the drum axis.

Figure 3 is an attempt to illustrate the principle of generating motion for a compacting drum according to.the

French Patent 1166681. The drum motion is provided by one or more pairs of vibrators attached to the inside cylindrical surface of the drum. The two vibrators in a pair are on opposing sides of a drive shaft in the centre of the drum, and are axially displaced in relative each other on either side of the drum center. Each vibrator contains a mass eccentrically attached to and rotating with a shaft. The shafts are caused to rotate by power transmission from the drive shaft at the centre of the drum.

It is not entirely clear from the French Patent whether the eccentrically attached masses in a pair of vibrators are equally as great. Neither is it apparent whether power and movement transmission from the drive shaft to the shafts of the eccentric means is formed such that the shafts get identical, or nearly the same rpm.

On the other hand, it is stated in the patent specifica- tion that phase displacement takes place between the eccentrics means due to gliding or slipping in the transmission. This phase displacement is said to give

<t raise to a vibration freαuency of the drum which is ^ different from the frequencies of the vibrators . • c

Figure 3 illustrates a mass attached to a shaft 3a rotating clockwise. A force vector from the centre of the mass is directed away from the shaft 3a. A second- mass suspended on a shaft 3b and rotating asynchronously with the mass 2a is illustrated by the dashed circle 2b. A force vector rotating synchronously with the mass 2b is illustrated by a plurality of dashed arrows-

Although it is not clearly stated in the French patent, both vibrators in a pair exert a complicated combination of translation forces and torques on the drum, due to said slip and phase shift, as well as the different locations of the eccentric means along the ^* axial exten¬ sion of the drive shaft. The torques act about --the central drive shaft as well as about an axis through the centre of the drum and at right angles to the axes of

^■ the eccentric means.. Thus according to the French patent no substantially pure alternating torque is applied to the drum about its axis.

The US patent 3543656 describes a soil compacting machine with two drums, each being vibrated with the aid of its own eccentric means arranged above the respective drum. The respective drum and eccentric means is rotatably mounted in a yoke which is in turn resiliently suspended ^' in the frame sections. The respective eccentric means provides a vibratory motion, not only of the drum but also of itself and the yoke. As depicted in Figure 4, the motion, which is a combination of translation and turning motion takes place relative to a point x between the shaft 3 and the central axis +, of the drum. If the compacting machine were freely suspended in the air, the respective eccentric means would not provide any torque to the respective drum about its central axis, but when the machine compacts a layer of material, forces from the layer will cause a alternating turning motion when the eccentric means displaces the drum relative the ooint x. Thus according

to said US patent no substantially pure alternating torque is applied to the drums about their axes by the excentric means.

The generation of compacting motion in a drum for a compacting machine in accordance with the invention is different in principle from what has been described above in respect of the prior art.

Since a substantially pure alternating torque is applied to the drum about its axis, oscillating forces to the material tangential to the circumference of the drum may be provided, without any translation forces directly caused by the eccentric means affecting the drum shaft. The advantages of such an arrangement are obvious, especially regarding the insulation of the drum motion

^• from the chassis of the compacting machine, which in conventional vibratory rollers constitutes a problem which is difficult to solve. It will be most clearly seen from Figures 5A-D how the alternating torque in accordance with the invention can be generated, these Figures illustrating the principle of the invention using two eccentric masses 2a, 2b rotating synchronously and in the same direction, and also illustrating the masses in four different angular positions. It is clear¬ ly apparent from the Figures that the torque M on the axis of the drum 1, caused by the eccentric masses 2a and 2b is zero in Figures- 5A and 5C, while it has its greatest value in one direction in Figure 5B and this value in the other direction in Figure 5D. It is also apparent that the eccentric masses together do not give any translation force of note at the drum axis in any position.

Although one skilled in the art naturally understands this, it is pointed out that there is no significance for the torque if the shafts 3a and 3b are in a plane through the drum centre which is vertical, horizontal or

along any other diagonal. What is essential is that the force vectors rotate synchronously and with the same rpm and direction of rotation as illustrated in Figures 5A-5D.

A compacting machine 20 is illustrated in Figure 6, and provided with a drum 1 having eccentric means in accordance with the invention. The compacting machine 20 is conventionally constructed with two sections 21 and 22, the forward section 21 constructed as a frame carry¬ ing the drum 1 and articulated with the rear section 22 for steering. The rear section 22 carries the driving seat 24 and possibly a cabin for the driver, as well as the power unit 25 for propelling the compactor *via rubbertired wheels 23 and for providing power to the hydraulic motor 19 'driving the eccentric means. The drum 1 can further be conventionally provided with a hydrual- ic motor (not shown) for propulsion. The described compactor illustrated in Figure 6 is only to be regarded as an example of the application of the invention, and not as a detailed description of how the compacting machine is constructed in general.

Figure 7 illustrates how an apparatus in accordance with the invention, as principly illustrated in Figures 5A-D, may be constructed. It comprises a conventional drum 1 accommodating two pairs of eccentric masses 2a and 2b, arranged for rotation in the same direction and at the same velocity. The pairs of eccentric masses 2a and 2b are rigidly attached to shafts 3a and 3b mounted in the end walls 8a and 8b of the drum 1, at given equal spac¬ ing from the central axis of the drum, so that the axes of the shafts 3 are in the same plane as said axis. A drive shaft 10 for the axes 3a and 3b is mounted in the center of the drum. The drive shaft 10 is provided with a motor 9, placed outside one end wall. In turn, the motor 9 is resiliently suspended in the frame 21 via conventionally arranged bearing, housing and resilient

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means (not shown in the figure). Suitable power trans¬ mission from the drive shaft to the shafts 3a and 3b is also arranged, in Figure 7 taking the form of chain or toothed belt transmission 4a, 5a, 6a and 4b, 5b and 6b. it is also possible to use gear wheels. On the other hand, transmission members permitting slip, such as vee belts or the like may not be used since it is essential that the phase relationship between the pairs of eccentric masses is kept unchanged at 180°. Minor devia- tions from this phase displacement in the practical embodiment does not notably affect the intended function however.

Apart from the eccentric masses 2a and 2b shown near _, one end wall 8a of the drum, the shafts 3a and 3b carry similar eccentric masses near the other end wall 8b of the drum. Several eccentric masses may be placed on the respective shaft in a manner known per se, or as an alternative each shaft can carry a uniformly distributed eccentric mass along the whole or a major portion of its available length.

The shape of the eccentric masses 2a and 2b given to them in Figure 7 only constitutes an example for the purpose of illustrating the inventive concept. Every other form of eccentric mass involving a displacement of the centre of gravity from the shaft, and which can withstand the stresses occuring in the application can be utilized within the scope of the invention. A condi- tion is, of course, that the eccentric masses are formed to provide a substantially pure oscillating torque on the drum about its axis.

In the described apparatus, the eccentric masses provide a sinusoidally varying torque resultant on the drum about its axis, which gives rise to oscillating shear stress variations in the material layer affected by the drum. When the drum bears against a substructure which

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is to be compacted or consolidated, the forces at the contact surface between drum and substructure will constitute in addition to an oscillating horizontal force a vertical force arising from the weight of the 5 compacting machine.

Slower shear stress alternations would be possible per se, and depend on the rate at which the compactor is passed over the substructure, by repeatedly moving the

10 compacting machine backwards and forwards over the sub¬ structure. Due to the weight of the compacting machine, material compaction carried out thus will be demanding in energy, and the frequency at which the travel of the compactor can be reversed will be low compared with-the

15 frequency with which the eccentric means in a compacting machine in accordance with the invention can cause the ^' drum to give shear stress variations.

The invention can also be realized with more than two

^■ 20 eccentric means in the drum. If these eccentric means are commonly alike excepting the angular positions of their masses and have their shafts arranged parallel to the rotational axis of the drum, their axes may be uniformly distributed along a circle concentric with the

25 drum axis. The eccentric means will' rotate synchronously in the same direction, and -the phase difference between the eccentric masses on adjacent shafts will be equal to the angle between planes through the respective shaft axes and the drum axis, so that all the forces from the

30 eccentric masses are directed radially outwards from the drum axis at instances corresponding to figure 5A.

The invention has many applications, e.g. in machines with several drums, one or more of which is provided 35 with eccentric means in accordance with the invention, or in machines intended for propelling with the aid of a towing vehicle. Figure 8 illustrates such a trailer, seen from one side. This trailing compacting machine

weighing about 900 kg is built up with a frame or chassis 61 fabricated from hollow sections and also formed with a towing bar carrier 40. A drum 1 is suspended from the chassis, which carries a tank 57 and pump 58 for hydraulic fluid- A pulling force transducer

45 is arranged on the underside of the forward end of the carrier 40. The pulling force transducer is joined to a towing bar 44 at the free end of which a conventional towing coupling 41 with releasing handle 42 is attached by means of a bolted joint 43, for connect¬ ing the compactor to the towing ball of a vehicle. The carrier 40 is fabricated from two rectangular hollow sections,, welded together at the end carrying the transducer ^' 45 and diverging backwards in an accute angle to each other. The rear -ends of the carrier have welded flanges connected to the chasses 61 by means of bolted joints. The chassis 61 includes a forward frame section

46 and a partially similar rear frame section 48. These frame ^• sections comprise hollow rectangular sections welded to form a rectangular frame with welded-on flanges 55 at mutually opposing corners for connection by means of bolted joints 56 to longitudinal weldments.

> The forward frame section 46 differs from the rear one

48 only in that at a distance from each forward corner it has a flange welded on for connection to the carrier 40. The two frame sections 46 and 48 are united by the two weldments extending in the longitudinal direction of the machine, each of the former being fabricated from an upper hollow section 47 and a lower hollow section 49, which are provided with welded-on flanges at either end and are mutually connected by means of vertical hollow section stiffeners 50 and 51. Between said stiffeners, the lower beam formed by the hollow section 49 is provided with a shallow portion by means of a depression in its upper edge line.

On the upper side of the chassis 61 there is a base structure 59 for mounting a pump 58, which is of the J>

radial piston type for hydraulic fluid compressed by a motor (not shown) suppied from a tank 57, thus forming a hydraulic unit of conventional type. As will be seen in detail from Figure 9, which is a partial section along the line B-B in Figure 8, the drum of the compactor is suspended in the chassis 61 by a suspension plate 60, 70 on either side. The suspension plate 60 is attached by bolted joints to three rubber shock absorbers, there being a forward shock absorber 72 and a rear shock absorber 71 mounted on either side of the centre axis of the drum 1, and an upper rubber shock absorber (not shown) mounted vertically above the centre axis of the drum 1. The three rubber shock absorbers are of conven¬ tional type, and are cylindrical, with the availability of screw connection of both end surfaces to form a resilient connection therebetween- The end surfaces of the shock absorbers facing away from the suspension plates 70 are screwed to one longitudinal frame of the chassis 61 by the forward shock absorber 72 being screw- ed to a fastening plate 76 forming a weldment with spacers 81 and 82 on the stiffener 50, the rear shock absorber 71 being screwed to an attachment plate 75 forming a weldment with spacers 79 and 80 on the stiffener 51. In a corresponding, not illustrated, manner the upper shock absorber is attached to the upper beam 47. To facilitate fitting the shock absorbers, holes 52, 53 and 54 (see Figure 8) have been made in both stiffeners 50, 51 and the upper beam 47.

The suspension plate 70 on the other side of the drum 1 is resiliently suspended in the same manner via the forward shock absorber 73 on the attachment plate 77, the rear shock absorber 74 on the attachment plate 78 and via an upper shock absorber (not shown) attached to its associated upper beam. The drum diameter is 60 cm and its width is 85 cm. The weight of the drum with contents is 310 kg.

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The contents of the drum 1 conform in principle with what is disclosed in conjunction with Figure 7, where applicable. Accordingly, a central drive shaft 10 is direct-driven by a driving motor 9 screwed on to the suspension plate 70 for the purpose of driving the eccentric means. The driving motor 9 is hydraulic and is connected conventionally to the pump 58 with hoses (not shown). The drive shaft 10 is conventionally mounted in bearing housings 88 and 90 screwed into the respective end wall 8a, 8b. The housing 88 and 90 are furthermore rotatably mounted in bearing housing 87 and 89, which are screwed onto the suspension plates 70 and 60 respectively, thus allowing rotation of the drive shaft 10 independent of the rotation of drum 1. The drive shaft 10 rotation is transferred synchronously to the shafts 3a and 3b, carrying the eccentric masses, by means of toothed belts 6a and 6b and four like toothed wheels 5a, 4a and 5b, 4b. The shafts 3a and 3b are mounted in the drum end walls 8a and 8b on either- side of the drive shaft 10 by means of the bearing housings 83, ^' 86 and 84, 85 screwed onto the drum end walls 8a and 8b , respectively. The housings 83, 84, 85, 86 are of standard type containing roller bearings, which are also utilized in the bearing housings 87, 88, 89, 90. For the sake of symmetry, the shafts 3a and 3b are each provided with a toothed wheel 91, 92 the same as the toothed transmission wheels 4a, 4b the wheels 91, 92 being mounted symmetrically on the respective shaft at the same distance from the centre of the drum as the respective toothed transmission wheel. The shaft 3a is provided with one eccentric mass 2a screwed onto the shaft 3a close to the bearing housing 83, and a like eccentric mass 2c in register with the mass 2a and screwed to the shaft close to the other bearing housing 84. In a corresponding mode, the other shaft ^• 3b is provided with two like eccentric masses 2b and 2d, driving of the shafts 3a and 3b being arranged such that both eccentric masses on one shaft always have the same

rate of revolutions and are displaced 180 , i.e. with a phase shift of 180°, in relation to the eccentric masses on the other shaft.

It is advantageous if the compacting machine can be formed so that it can be directed between two or more alternative modes of operation, e.g. with the oscilla¬ tion mode according to the invention and with conven¬ tional vibration mode with force substantially vertical 0 to the substructure. This can be arranged comparatively simply with the eccentric means arrangement described by changing the phase angle between the eccentric masses on one of two shafts from 180° to 0°.

5 An example of such a change in practice would be by having the eccentric masses on at least one of the shafts carrying them made rotatable between two end positions in relation to said shaft- The end positions in each direction are selected such that when the shafts 0 rotate in one direction the relative phase angle is 180° and when they rotate in the other direction the relative phase- angle is 0°. A corresponding result can also be achieved with more than two shafts and their associated eccentric masses, but then the phase angles between the 5 different eccentric masses, in the case of operation in accordance with the inventive concept, must depend on the geometric relationship of their shafts to each other, so that the resulting translation force in the radial direction of the drum is always zero. 0

In the case of translation force, i.e. conventional operation, the phase angles between all the eccentric means must be zero, so that they coact to give an effect corresponding to a centrically placed shaft with its 5 eccentric masses and with an eccentric moment equal to the sum of the eccentric moments of the masses.

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In Figures lOa-b there is illustrated a portion of the drive shaft 10 and shafts 3a and 3b with their eccentric masses, the embodiment being such that driving the shafts is arranged to take place synchronously as in Figure. 7. Figure 10a is a partial view from one side while Figure 10b is a section along the line A-A in Figure 10a. The main portion of the eccentric masses 30a and 30b in this case occupy 90° of a circular ring about the respective shaft 3a or 3b. The eccentric mass 30a is mounted rotatably about the shaft 3a with the aid of the smaller annular portion 31a, surrounding the remander of the shaft 3a. At the side of the annular portion 31a there are stops 32 and 33 adapted rigidly attached to the shaft 3a. Each stop constitutes a portion of a ring taking up 90° of the circumference of the shaft, and its location is such that it allows 180° angular movement of the eccentric mass 30a about its shaft when the rotational direction of the shafts is reversed. The other eccentric mass 33 is mounted on the shaft 3b with the aid of the annular portion 31b, substantially corresponding to the portion 31a, but is rigidly attached to the shaft 3b. _. In the position of the ^■ eccentric masses 30a and 30b illustrated in Figure 10, it is assumed that driving of the shafts thereof is anticlockwise, thus obtaining oscillating turning motion on the drum. When the direction is reversed so that both shafts 3a and 3b are driven clockwise the shaft 3a turns 180 in relation to the eccentric mass 30a, while the eccentric mass 30b remains fixed on the shaft 3b, the eccentric masses 30a and 30b rotating in phase with each other to obtain conventional vibratory operation of the drum.

For providing and applying the substantially pure oscillating torque in accordance with the invention on the drum of an inventive compacting machine, it is not absolutely necessary to have shafts with eccentric masses arranged inside the drum according to Figures 7 til

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or 9. There are of course other methods and means for generating the pure alternating torque on the drum about its axis. Figures 11 and 12 illustrate an alternative particularly developed for such compacting machines where propulsion for the travel of the machine backwards and forwards over the layer of material is provided by driving the drum. Propulsion of such machines is done by applying a torque to the drum about its axis. This torque which is intended for moving the machine by rolling the drum, changes direction when the direction of travel of the machine over the material layer is reversed. Since reversing the machine movement backwards and forwards over the material layer cannot take place particularly rapidly due to the vehicle speed during compaction and weight of the compacting machine, it will be appreciated that the torque intended for propelling the machine changes direction very slowly compared with the alternating frequency of the torque in accordance with the invention-

Somewhat simplified, Figure 11 illustrates a convention¬ al differential gear used for superposing a rapidly reciprocating torque on a constant or slowly varying torque. The differential gear has a housing 100 in which an input shaft 101 and an output shaft 102 are journall¬ ed in bearings 103 and 104, respectively. A first gear

105 is attached to the input shaft and a similar gear

106 is attached to the output shaft. Two further gears 107a, and 107b are identical with gears 105 and 106 and in mesh therewith in the housing. The gears 107a and 107b are provided with journals 108a and 108b for mount¬ ing in bearings 109a and 109b in the housing- If the input shaft is rotated in a given direction, e.g. clock¬ wise, while the housing is prevented from turning, then the output shaft rotates just as much in the opposite direction, in this case anticlockwise- On the other hand, if the housing is turned in the same or the opposite direction in relation to that of the inout

shaft, the output shaft is turned more or less, respectively, than when the housing is kept stationary.

Figure 12 is a block diagram of an arrangement facilitating a method of driving a drum 113, and simultaneously giving it a substantially pure oscillat¬ ing torque, a differential gear 112 according to Figure 11 being used. For travel of the whole compacting machine backwards and forwards over the material layer there is a travel motor 110, driving the input shaft of the differential gear 112 via a reduction gear 111. The output shaft of the differential gear is conected to the drum for conventionally providing its turning movement about its centre.

A rotating movement translation means 115 is connected to the housing of the differential gear to provide a reciprocating torque to the housing about the input and output shafts. The movement translation means, which can conventionally convert a continuous input turning move¬ ment to a reciprocating turning motion or torque is driven by an oscillator motor 114. The rpm of the oscillator drive motor 114 is high compared with the rpm of the differential gear input shaft.

The arrangement according to the block diagram in Figure 12 provides a torque for total movement of the drum which comprises a comparatively slow rotational movement and a superposed comparatively rapidly by alternating torque. The arrangement thus provides approximately the same movements at the centre of the drum and its cir¬ cumference, respectively, as are provided by the embodi¬ ments in Figures 6-9 when the drum ^' is rolling on the material layer.

If it is desirable or preferred, it is naturally con¬ ceivable to allow the motor 110 also to drive the rotat¬ ing movement translation means 115 instead of the motor

114. In the arrangement according to Figure 12, there is suitably included resilient means between the different parts of the compacting machine, but these as well as mounting the parts of the arrangement on the machine have been excluded for the sake of simplicity.

Compaction trials have been carried out with a compact¬ ing machine embodiment according to Figures 8-9. For reference in compaction, the same embodiment has been used, but the arrangement of the eccentric masses and shafts and their driving has been altered so that in Figure 9 the shaft 3a has been turned half a revolution in relation to shaft 3b. The relative phase positions of the eccentric masses thus became such that the drum obtained a conventional vibratory movement. To obtain different amplitude and frequency of the oscillating torque on the drum about its- centre in accordance with the invention, experiments have been made with different sized eccentric masses and different frequencies in the range 25-70 Hz.

The compaction trials have been carried out on a sub¬ structure comprising about 2 m natural base gravel with a grain size of 0-32 mm which was well compacted with a vibrating plate compactor in 40 cm layers. Over this was placed 80 cm crushed base gravel with a grain size of 0-32 mm which was well compacted. The uppermost layer of 25 cm was loosened within an area of 1.5 m width and 5 m length. The upper surface was smoothed off, after which the surface was compacted with 16 passes of the compact¬ ing machine embodiment. The latter was towed backwards and forwards and in the same path the whole time. The speed of travel was constant at about 0.8 m/s.

Two different trial series will be compared in the following, one with an oscillating mode in accordance with the invention and one with conventional vibratory mode of operation of the drum. For the latter case, a

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trial series have been selected with typical parameters for a conventional vibrating compacting machine with a similar drum as the one on the inventive embodiment, namely a frequency of 50 Hz and a collected eccentric moment of 0.12 kgm, corresponding to a nominal vibration amplitude of about 0.4 mm.

Preparatory trials with the embodiment arranged for oscillating mode of operation showed that a comparable compaction result could be expected with a greater eccentric moment and lower frequency. As a case com¬ parative with the oscillating mode there was thus selected a trial series with a collected eccentric moment of 0.24 kgm, corresponding to a nominal tangential amplitude at the drum cylindrical surface of about 0.8 mm. In this trial series, the oscillating frequency was 40 Hz.

Compaction results achieved in the trials have been estimated using conventional methods such, as levelling, plate bearing tests, isotope measurement and also with the aid of a transducer buried in the material layer - being compacted, this transducer being affected by move¬ ments in the material layer. Furthermore, the power consumption of the hydraulic motor has been measured and the horizontal and vertical acceleration of the drum shaft, ^" as well as other quantities, have been sensed. Some interesting results and conclusions with reference to compaction in accordance with the invention are described in the following with reference to Figures 13-18.

Determination of the level of the compacted surface has been carried out by levelling in three sections at a spacing of one meter. A straight steel beam with a cross section of 50 x 50 mm and a length of 0.5 was placed on the compacted surface in the middle of the respective section and at right angles to the direction of travel

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of the compacting machine. In the middle of the steel beam and on its upper side there was a spherical surface on which a millimeter-graduated levelling staff was placed. Level readings was taken after every second pass, the first time after two passes. The levels relative the level after two passes are shown in Figure 13. On the abscissa there is given the number of passes in a logarithmic scale and on the ordinate the amount of settle in millimeters- In the diagrams there is given the mean value for the three measuring sections as well as the spread- The lower curve shows the results for the case of the oscillating mode of operation in accordance with the invention and the upper curve for a convention¬ al vibratory mode of operation. These curves show -the total amount of settle, including the integrated effect of compaction of the loosened 0.25 thick upper layer, possible compaction of the layers lying beneath and the effect of possible lateral displacement of material. As will be seen from the results, the oscillating mode of operation gave a significantly greater total amount of settle.

Apart from the total amount of settle at the surface, the deformation in the earth layer was measured with the aid of a device called a deformation meter. The deforma¬ tion meter comprises two parallel horizontal cylindrical bodies with rounded-off ends united by a vertical thin flexible rod- The rod is connected to a length measuring device built into the lower cylindrical body. An altera- tion of the distance between both cylindrical bodies can be detected electrically to an accuracy of 0.01 mm. The centres distance between the cylindrical bodies was 75 mm in these trials. The deformation meter was placed in an extended condition in the loosened surface layer with its centre at a depth of about 0.2 m. The results from such a deformation meter, which was placed in an equivalent way in both the trial series is shown in Figure 14. On the abscissa there is given the number of

passes on a logarithmic scale and on the ordinate the percentage deformation based on the measuring length of the meter, i.e. 75 mm. The meter was zeroed after the first pass. The results thus relate to percentage mean deformation in a layer 75 mm thick, the centre of which was at a depth of 0.2' m under the ground surface- The result indicates somewhat higher deformation for the series with the oscillating mode of operation, but the difference is not significant, taking into account the expected spread in measurements of this type in natural soil material- After terminated compaction in each trial series, a plate loading test was carried out using a stiff disk, 300 mm in diameter. The plate loading test was carried out in six cycles with loading and unloading twice each to 10 kN, 20 kN and 50 kN. Moduli of elasticity were calculated for the first and the second loading respectively according to

or E ₂ = 75.D. 2- Δs

where D = disc diameter

Aσ~ stress increase as an average value over the disc surface for the loading case in question As - amount of settle for stress increase in question.

The results from the plate loading tests from both trial series are shown in Figure 15. Calculated moduli have been set off on the ordinate against the maximum loading as abscissa. The modulus at the first loading (E, ) as well as the modulus at the second loading (E ₂ ) are shown. The moduli of elasticity obta ned are all some¬ what lower after compacting with an oscillating drum in accordance with the invention.

Measurements were also carried out by indirect measure¬ ment of the compacted soil layer density with the aid of

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an isotope meter manufactured by DECCA, type HDM-5. As a mean value for two measuring points the isotope meter

3 gave a volumetric density of 2 250 kg/m after compact-

3 ing with the oscillating drum and 2 240 kg/m after compacting with a conventional vibratory drum.

The different measuring methods gave no unambiguous result concerning the compaction results achieved- The levelling results indicate considerably higher coπφac- tion effect for oscillating mode of operation whereas the plate loading tests show somewhat higher compaction effect, for vibrating mode of operation, and two other measuring methods show somewhat higher effect for oscillating mode of operation.

Other conditions for the machine and surroundings have been documented for both trial series described above, namely the power requirement for driving the eccentric means, vibrations in the drum suspension plates and in the chassis-, as well as vibrations in the ground surface at a distance from the compacting machine.

The power requirement for driving the eccentric masses has been calculated with the aid of measured pressure drop over the motor driving the eccentric masses, and measured rpm. The power thus registered and supplied to the driving motor of the eccentric masses is utilized to some extent for useful compaction work, but is also consumed in the form of internal losses in the hydraulic motor, the bearings of the shafts and in the belt transmissions. At special measurements, without the eccentric masses being fitted, the loss effects have been measured as being about 800 w at 40 Hz and about 1 000 W at 50 Hz.

The graph in Figure 16 illustrates the power supplied to the eccentric drive motor during the two trial series described above. The number of compacting machine passes

are given on the abscissa and the total power on the ordinate. The upper graph relates to conventional vibrating compaction and the lower graph to oscillating compaction. The power consumption was fairly constant for the respective series and for the oscillating case it was about 60% of that corresponding to the conventional vibration case. Keeping in mind that the compaction results are comparable this shows that the efficiency is appreciably higher for the oscillating case and to a greater extent than what is apparent from Figure 16, if consideration is given to the power losses in the respective case.

The results obatined from registered accelerations, in vertical and horizontal directions on the suspension plates 60 are shown in Figure 17. Polar curves for the acceleration vector tip movement during one period have been drawn up for the conventional vibration mode of operation as well as for the oscillating mode of opera- tion. As will be seen, the vertical amplitude which is the most important for undesired frame movements, is in the oscillating mode about 20% of the corresponding amount for the conventional mode. The horizontal amplitude for the oscillating mode was about 30% of the corresponding value for the conventional mode.

In the oscillating drum case, it is possible and also suitable to reduce the horizontal acceleration amplitude further by increasing the mass which is not resiliently cushioned, e.g. some section of the chassing being rigidly connected to the suspension plates . This further¬ more affords the advantage that the amplitude of tangential motion at the drum circumference along the contact surface with the material layer increases, which increases the compaction effect, providing that the friction between drum and material layer is sufficient to prevent slipping. The corresponding measure can not suitably be utilized for the conventional vibrating

compacting machine since this leads to the substantially radial oscillations of the drum being heavily dampened in this case, and if this dampening is compensated by an increase of the eccentric moment, a higher vibration amplitude for the remaining portion of the chassis would occur-

In Figure 18 there are shown results from a separate investigation of vibration amplitudes at the ground surface at a greater distance from the compactor- The investigation was carried out with a stationary compact¬ ing machine on a large, flat, horizontal, asphalted surface. The substructure comprised from below, clay, a layer of gravel of unknown thickness, and asphalt. The measuring points were marked out on the asphalt surface at distances, of 1, -2, 4 and 8 m from the centre of the drum along lines at 0°, 45°, 90°, 135° and 180° to the centre line of the compacting machine path as it travels forwards. A dual axis accelerometer with the measuring directions radially and vertically was placed at the measuring points in turn. The r s value of the accelera¬ tions in the respective direction was registered while the eccentric masses were rotating. On the abscissa axis in Figure 18 the distance has been set out to a logarithmic scale and on the ordinate axis the accelera- tion amplitude m a logarithmic scale converted to m/s 2 top value assuming sinusoidal oscillation with one frequency component. The results indicate the magnitude of the resultant. The five radial directions are shown as separate lines. The same eccentric masses were used as in both the comparative trial series described above. In the case of the oscillating mode of operation the frequency was 40 Hz, as with the comparative series. In the case with a vibrating mode of operation, such a high frequency as 50 Hz could not be used, since the machine was then shifted laterally by the heavy vibrations- The results are therefore given for the frequency of 40 Hz in this case as well. The upper group of curves in

Figure 18 apply to the conventional vibrating drum and the lower group to the oscillating drum. It will be seen from the diagram that the vibration levels are 8 to 10 times lower for the oscillating case, and also that the directional characteristic differs. In the oscillating case the amplitude laterally to the drum (the 90° curve) is considerably lower than forwards (0 ) or backwards (180°). The reverse is true in the conventional vibra¬ tion case at less distances than about 3 m from the machine.

After trials with the compacting machine embodiment it was found that its drum had a very smooth surface. This indicates that the surface had slipped during compaction against the material layer, and had not been capable of _. transferring the whole of its movement to the material ^; layer. It is therefore conceivable that better compac¬ tion results could be obtained with a drum with which there is greater friction to the substructure, e.g. a drum with rubber coating.

In summary it may be said that the trial results show that the object of the invention can be achieved by a compacting machine according to Figures 8-9. _This embodiment, as well as the embodiments illustrated in Figures 6-7 and Figures 11-12 are only to be regarded as examples of how the objects of the invention can be realized, and the invention is not restricted to these embodiments.

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