EP3450631B1 - Deep vibration apparatus with an adjustable unbalance mass body - Google Patents

Description

The invention relates to a deep vibrator for compacting a soil by means of a rotating unbalance. The rotating unbalance creates vibrations that compress the soil vibrator and possible additional material.

Deep vibrators are generally used in three subsoil improvement methods that differ in terms of operation and load transfer. With the Rütteldruckverfahren coarse-grained soils are compressed in itself. In the vibratory tamping method load-bearing columns made of gravel or crushed stone are placed in mixed and fine grained, non-compactible soils. With the third method pile-like foundation elements are produced over which relatively high loads can be removed, if a permanent load-bearing composite with Stopfsäulen is not guaranteed. The different Tiefenrüttelverfahren are also described in the brochure "Die Tiefenrüttelverfahren" (Prospectus 10-02D) of the applicant.

All methods have in common that the vibrator is sunk to the intended improvement depth in the ground, and then compacted depending on the type of process from bottom to top soil, constructed a Stopfsäule or a pile-like foundation element is made.

As an essential element of the vibrator contains a motor driven unbalance, which puts the vibrator in horizontal vibrations. The deep vibrator is adapted to the intended working depth with attachment tubes and thereby guided by cranes, excavators or specially developed carrier devices (carrying crawlers).

From the DE 10 2014 019 139 A1 is a deep vibrator for compacting a soil with a first imbalance weight and a fastener for interchangeable receiving a second imbalance weight known. The first imbalance weight and the second imbalance weight can be driven in rotation about the longitudinal axis of the deep vibrator. The fastening element is arranged such that the imbalance of the deep vibrator can be reduced by the recorded second imbalance weight.

From the DE 199 30 884 A1 is a deep vibrator for compacting soils with an elongated housing having a longitudinal axis and a coaxially mounted in the housing motor-driven axis of rotation and a revolving with the axis of rotation unbalanced mass known. Means are provided for varying the radial distance of the center of gravity of the imbalance mass from the longitudinal axis and a variable-speed drive for the axis of rotation. By changing the size of the imbalance mass, the effective impact force during lowering and / or pulling is changed.

For deep vibrators, where the eccentric is unadjustable, it must already be determined during assembly which centrifugal forces and amplitude the vibrator should have. During operation, it is very difficult to respond to changing soil properties by changing the speed.

Deep vibrators with adjustable eccentric need a mechanical device for adjusting the imbalance masses. However, the adjustment mechanism is subjected to high loads due to the strong vibrations, which can lead to failure of individual mechanical parts.

The present invention is therefore based on the object to propose a vibrator with adjustable unbalanced mass, which is simple and robust and thus has a long life. It should also be proposed a corresponding method for compacting ground, that allows a change in the imbalance mass during operation.

To solve a deep vibrator for compacting soil is proposed, comprising: a rotary drive which is rotationally driven in two directions, a drive shaft which is drivingly connected to the rotary drive, a primary mass body, which is rotatably connected to the drive shaft and together with this order rotating the rotational axis, a secondary mass body limitedly rotatable relative to the primary mass body and assuming a first rotational position relative to the primary mass body upon rotation of the drive shaft in the first rotational direction, in which a center of gravity of the secondary mass body approximates a center of gravity of the primary mass body; and when rotating the drive shaft in the second direction of rotation occupies a second rotational position relative to the primary mass body, in which the center of gravity of the secondary mass body is spaced from the center of gravity of the primary mass body, wherein the center of mass of the secondary mass body pers and the center of mass of the primary mass body have different radial distances from the axis of rotation.

One advantage is that the imbalance is variable by simply reversing the rotational direction of the rotary drive between two sizes, which can be due to the design of the first and secondary mass body such that their focal points on different radii can achieve particularly high imbalances or given a large variability in terms of adjustable imbalances is. This causes the amplitude of the deep vibrator is adjustable by the adjustment in particularly large areas. Depending on the mass and shape of the secondary mass body, the amplitude in the first rotational position compared to the second rotational position can be more than doubled. To adjust the imbalance, only the direction of rotation of the rotary drive must be changed, for which it must be stopped briefly.

With regard to the design of the mass body and, accordingly, the position of the respective center of gravity of the rotationally fixed to the drive shaft connected primary mass body on the one hand and the relatively rotatable relative to the drive shaft secondary mass body on the other hand, various possibilities are conceivable. After a the first possibility, the rotatable secondary mass body has a greater radial distance from the axis of rotation, as the rotationally fixed primary mass body. Alternatively, the reversal is possible, that is, the rotatably connected to the shaft primary mass body has a greater radial distance from the axis of rotation, as the rotatable secondary mass body.

The rotary drive can have any configuration which is suitable for generating a rotational movement in two directions of rotation. For example, the rotary drive can be designed in the form of an electric motor or a hydraulic drive. An electric motor may have a stator which is non-rotatably connected to a housing of the deep vibrator or is supported with respect to this in the sense of rotation, and a rotor which is connected to a motor shaft in order to drive them.

The drive shaft, which carries the primary and secondary mass bodies, is drive-connected to the rotary drive. In the context of the present disclosure, the term "drive-connected" is intended to encompass an indirect connection of said drive parts, ie the possibility that one or more further components or components may be interposed between the rotary drive and the drive shaft in the power path, for example a clutch or a gearbox.

By the term "primary mass body" is meant in particular present at least one mass body which is rotatably connected to the drive shaft. In the present case, a "mass body", in particular, refers to a mass body which is adjustable relative to the primary mass body, so that the center of gravity of the total mass changes. One or more primary and secondary mass bodies may be provided. Accordingly, it should be understood that within the context of the present disclosure, any reference to a primary or secondary mass body may apply to any other corresponding primary or secondary mass body.

The masses of the primary and secondary mass bodies can be selected as needed and the desired amplitude of the deep vibrator. A big variability can be achieved in particular if the primary and secondary mass body have different sized masses. In this case, the primary mass body may have a greater or lesser mass compared with the secondary mass body. It is favorable for a large oscillation amplitude if the mass body whose center of gravity has the greater distance from the axis of rotation also has the larger mass. This may be the primary or secondary mass body. It is also conceivable that the masses of the primary and secondary mass body are the same size.

It is specifically contemplated that the center of mass resulting from the primary mass body and the secondary mass body in the first rotational position has a greater distance from the axis of rotation than the center of mass resulting from the primary mass body and the secondary mass body in the second rotational position. Preferably, the center of gravity of the primary and secondary mass bodies are in the first rotational position on a common side and in the second rotational position on opposite sides with respect to the axis of rotation of the drive shaft.

According to a preferred embodiment, a first stop is provided, against which the secondary mass body is supported upon rotation of the rotary drive in the first rotational direction, and a second stop against which the secondary mass body is supported in rotation of the rotary drive in the second rotational direction. A particularly simple structure is achieved in that the first and second stop are formed on a common stop element, for example, as two effective in opposite circumferential directions stop surfaces of the stop element. Preferably, for an imbalance assembly comprising a primary mass body and a secondary mass body, exactly one stop element per secondary mass body is provided which forms the first rotational stop and the second rotational stop.

After a possible concretization, the stop element may be provided on the primary mass body, in particular be firmly connected thereto. In this case, the connection of the stop element on the primary mass body, for example be realized by a screw, with other compounds such as a welded joint are also conceivable. The abutment member may be configured, for example, in the form of an abutment bar fixedly connected to the primary mass body and extending parallel to the rotation axis along an outer peripheral surface of the primary mass body.

According to one possible embodiment, the first mass body comprises a cylinder segment, which preferably extends through approximately 180 ° about the axis of rotation. The mass body can be made in one piece with the drive shaft. Alternatively, the mass body can also initially be manufactured separately and then connected to the drive shaft rotationally fixed and axially fixed, for example by means of a shaft toothing or shaft-hub connection with suitable axial securing means.

The secondary mass body may comprise a ring segment which is rotatably mounted about the drive shaft. The ring segment may, for example, extend by more than 160 ° and / or less than 180 ° about the axis of rotation.

According to a first possibility, the secondary mass body can be arranged with axial overlap to the primary mass body. The mass bodies are preferably designed so that a smallest inner radius of a ring segment of the secondary mass body is greater than a largest outer radius of the primary mass body. In other words, in the first rotational position, the secondary mass body lies radially outside the primary mass body. According to a favorable development of the secondary mass body comprises in this embodiment, an upper lid part which is fixedly connected to an upper end of the ring segment, and a lower lid part, which is fixedly connected to a lower end of the ring segment, wherein the two lid parts radially inwardly at least indirectly are rotatably mounted on the drive shaft. In this embodiment, the primary mass body is spatially accommodated in the first rotational position in the secondary mass body. The fact that the ring segment of the secondary mass body is located radially outside of the primary mass body, a particular large imbalance and, accordingly, a large amplitude of vibration generated.

According to a second possibility, the secondary mass body can also be arranged with axial offset to the primary mass body, that is to say above and / or below a respective axial end of the primary mass body. This embodiment is particularly suitable for applications in which only a small additional imbalance or amplitude increase is needed.

For both possibilities applies that the secondary mass body is at least partially disposed radially outside of the primary mass body or that the center of mass of the secondary mass body has a greater radial distance from the axis of rotation than the center of mass of the primary mass body. The stop element is designed according to the configuration of the secondary mass body. In particular, in the first possibility, the stop element may be radially projecting with respect to an outer peripheral surface of the primary mass body to act as a driver for the secondary mass body upon rotation of the drive shaft. For a particularly large stop surface, the stop element may extend in the axial direction over at least one third of the height of the primary mass body. In the second possibility, the stop element can protrude axially, in particular with respect to an axial end side of the primary mass body.

In order to produce a particularly large imbalance mass, at least one of the primary and the secondary mass body may include Schmermetall. Furthermore, a plurality of primary and / or secondary mass bodies can also be provided.

An imbalance assembly, which is to be stored as a unit in a housing of the deep vibrator, may each comprise at least one shaft part, a primary and a secondary mass body. The shaft part is rotatably supported in the housing of the deep vibrator by means of an upper bearing, which is arranged above the primary mass body, and by means of a lower bearing, which is arranged below the primary mass body.

According to one embodiment for particularly large vibration amplitudes, a plurality of imbalance assemblies may be provided which are arranged one below the other. The individual imbalance assemblies are preferably driven by a single rotary drive. For this purpose, the motor shaft of the rotary drive can be rotatably connected to the drive shaft of a first assembly and the first drive shaft further rotatably connected to the drive shaft of an underlying second assembly. Any number of further imbalance modules are possible. The non-rotatable connection of the individual shaft parts with each other can be realized for example by means of a flange connection, shaft toothing or other shaft-hub connection. Each individual assembly preferably has separate bearings for supporting the respective shaft part, so that the total bearing load is low. In this way, it is ensured that the deep vibrator withstands permanent large forces and vibrations even when designed with several imbalance assemblies.

A method of compacting soil by means of such a deep vibrator may include the steps of shaking the depth vibrator into the ground to a desired depth by rotating the rotary drive in a first or second rotational direction and compacting the soil by rotating the rotary drive in the second rotational direction. By turning the rotary drive in the second direction of rotation large vibration amplitudes and thus a high compression are generated. The shaking to the desired depth can be done with small or large amplitude.

Figur 1

einen Tiefenrüttler in einer ersten Ausführungsform im Längsschnitt;

Figur 2

den Tiefenrüttler aus Figur 1 im Querschnitt gemäß Schnittlinie II-II aus Figur 1;

Figur 3

einen Tiefenrüttler in einer zweiten Ausführungsform im Längsschnitt;

Figur 4

den Tiefenrüttler aus Figur 3 im Querschnitt gemäß Schnittlinie IV-IV aus Figur 3;

Figur 5

einen Tiefenrüttler in einer dritten Ausführungsform im Längsschnitt;

Figur 6

einen Tiefenrüttler in einer weiteren Ausführungsform im Längsschnitt; und

Figur 7

den Tiefenrüttler aus Figur 6 im Querschnitt gemäß Schnittlinie II-II aus Figur 6.

Preferred embodiments will be explained below with reference to the drawing figures. Hereby shows:

FIG. 1

a deep vibrator in a first embodiment in longitudinal section;

FIG. 2

the deep vibrator FIG. 1 in cross-section along section line II-II of Figure 1;

FIG. 3

a deep vibrator in a second embodiment in longitudinal section;

FIG. 4

the deep vibrator FIG. 3 in cross section according to section line IV-IV FIG. 3 ;

FIG. 5

a deep vibrator in a third embodiment in longitudinal section;

FIG. 6

a deep vibrator in a further embodiment in longitudinal section; and

FIG. 7

the deep vibrator FIG. 6 in cross section along section line II-II of Figure 6.

The FIGS. 1 to 7 their common features are described below together.

A section of a deep vibrator 2 is shown. A deep vibrator serves to compact soil by means of an imbalance. Imbalance is understood to mean a rotating body whose mass is not distributed rotationally symmetrically. The mass inertia axis of the mass body is offset from the axis of rotation, so that the imbalance generated during rotation oscillations, with which the soil and possible addition material is compacted.

The deep vibrator 2 accordingly comprises a rotary drive 3, a drive shaft 4 which can be driven in rotation therewith, a first mass body 5 which is non-rotatably connected to the drive shaft 4, and a second mass body 6 which is adjustable in rotation relative to the first mass body 5. The components mentioned are accommodated in a housing 7 of the deep vibrator 2, or mounted rotatably in this. It is envisaged that the first and second mass body 5, 6 with respect to their shape and / or mass and / or their respective center of gravity distance to the drive shaft 4 from each other.

In the present case, the rotary drive 3 is designed in the form of an electric motor which comprises a stator 8 supported in rotation with respect to the housing 7 and a rotor 9 which is rotatable relative thereto. It is understood, however, that other engines are used, such as a hydraulic drive. The rotor 9 of the electric motor 3 is connected to a motor shaft 10 for driving it in rotation. The motor shaft 10 is in the housing 7 by means of a first bearing 12, which is arranged above the rotary drive 3, and a second bearing 13, which is arranged below the rotary drive 3 rotatably mounted about a rotation axis A. The rotary drive 3 is designed so that it can drive the motor shaft 10 in two directions, ie clockwise and counterclockwise.

The motor shaft 10 is rotatably connected by means of suitable connecting means 14 with the underlying drive shaft 4 for transmitting a torque. The connecting means 14 are in the present case designed in the form of a flange connection, it being understood that other shaft couplings for non-rotatable connection are also possible.

The drive shaft 4 is rotatably supported by means of suitable bearing means 15, 16 in the housing 7, for example by means of rolling bearings or plain bearings. The first mass body 6, which may also be referred to as primary mass body, is rotatably connected to the drive shaft 4. The rotationally fixed connection can be realized by known means, for example by means of a form-fitting shaft-hub connection and / or cohesively by means of welded connection. It is also possible that the drive shaft 4 is made in one piece with the first mass body 6.

The second mass body 6, which may also be referred to as a secondary mass body, is limitedly rotatable relative to the first mass body 5. It is provided that the secondary mass body 6 when rotating the drive shaft 4 in the first direction of rotation R1 assumes a first rotational position P1 and when turning the drive shaft 4 in the opposite second rotational direction R2, a second rotational position P2 relative to the first mass body 5. In the first rotational position P1, which in the FIGS. 1 to 5 can be seen in the left half of the picture, the secondary mass body 6 is approximated to the primary mass body 5, or, the two mass body 5, 6 are located with respect to the axis of rotation A on the same half page. In the second rotational position P2 of the pivotable mass body 6, which in the FIGS. 1 to 5 each dashed line in the right half is shown (reference numeral 6 '), the secondary mass body 6 is spaced from the primary mass body 5, or the two mass body 5, 6 are located with respect to the axis of rotation A on opposite half sides. Due to this configuration, in that the resulting center of gravity Sres1 formed by the first and second mass bodies 5, 6 in the first position P1 of the mass body 6 has a greater radial distance from the axis of rotation A than the resulting center of mass Sres2 resulting from the first and second mass bodies 5, 6 when the secondary mass body (6 ') is in the second position P2. It follows that the size of the imbalance can be changed by simply reversing the direction of rotation (R1, R2) of the rotary drive 3 between two sizes. To adjust the imbalance, only the direction of rotation R1, R2 of the rotary drive 3 has to be changed, for which purpose it must be stopped briefly.

A special feature of the present invention is that the center of gravity S6 of the pivotable mass body 6 has a greater radial distance from the axis of rotation A than the center of mass S5 of the rotatably connected to the shaft 4 mass body 5, or that the pivotable mass body 6 relative to the rotationally fixed mass body 5 at least partially protruding radially. By means of this configuration, particularly high imbalances can be achieved in the first rotational position P1, or the amplitude of the deep vibrator 2 can be adjusted in particularly large areas. Depending on the mass and shape of the secondary mass body 6, the amplitude in the first rotational position P1 compared to the second rotational position P2 can be more than doubled.

In the in the Figures 1 and 2 In the embodiment shown, the primary mass body 5 comprises a cylinder segment which extends through 180 ° about the axis of rotation A. The secondary mass body 6 is arranged in this embodiment with axial overlap to the primary mass body 5 and has a ring segment 17 with an upper lid portion 18 and a lower lid portion 19. Upper cover part 18, ring segment 17 and lower cover part 19 form a half-shell, which is dimensioned so that the first mass body 5 can be accommodated therein when the second mass body 6 is in the first rotational position P1. For this purpose, a smallest inner radius of the ring segment 17 of the secondary mass body 6 is greater than a largest outer radius of the primary mass body 6. In the first rotational position P1 of the secondary mass body 6 is radially outside of the primary mass body 5 and surrounds it. Due to the fact that the ring segment 17 of the secondary mass body 6 lies radially outside the primary mass body 5, a particular large unbalance and correspondingly also a large oscillation amplitude are generated.

The half-shell-shaped mass body 5 is mounted on the drive shaft 4 via two bearings 20, 21. The upper cover part 18 is arranged via a first bearing 20, which is arranged axially above the first mass body 5, and the lower cover part 19 via a second bearing 21 , which is arranged axially below the first mass body 5, rotatably mounted on the shaft 4. It is especially in FIG. 2 recognizable that the ring segment 17 extends over an angular range of slightly less than 180 ° about the axis of rotation A.

The relative rotational positions P1, P2 are each defined by a stop element 22 against which the secondary mass body 6 abuts upon rotation of the rotary drive 3 and is thus arranged in a defined rotational position relative to the primary mass body 5. In the present case, exactly one stop element 22 is provided which forms both a stop in the first direction of rotation R1 and a stop in the second direction of rotation R2. The stop element 22 is presently designed in the form of a bar or a bar, which is fixedly connected to the primary mass body 5, for example non-positively by means of screw or materially by means of welding. The stopper member 22 protrudes radially beyond an outer circumferential surface of the primary mass body 5 and extends in the axial direction, such as in particular FIG. 1 recognizable over at least half the axial length of the primary mass body 5, so that the most uniform possible force introduction or support of the secondary mass body 6 is given. A first side surface 23 of the strip 22 forms a first stop in the first direction of rotation R1 of the pivotable mass body 6, while an opposite second side surface 24 of the bar 22 forms a second stop in the opposite direction R1 of the mass body 6.

In the embodiments according to the FIGS. 1 and 3 Further optional additional masses 25, 26 are provided, which are fixedly connected to the drive shaft 4. In the present case, a first additional mass 25 above the upper bearing 15 and a second Additional mass 26 disposed below the second bearing 16. The rotationally fixed connection with the shaft 4 can be produced for example by means of a positive shaft-hub connection. It can be provided that at least one of the mass bodies 5, 6, 25, 26 includes Schmermetall. Incidentally, the mass bodies may be made of a metallic material such as steel.

The FIGS. 3 and 4 show a deep vibrator 2 in a slightly modified second embodiment. This corresponds largely to the embodiment FIGS. 1 and 2 , so that reference is made to the above description in terms of similarities. The same or modified details are provided with the same reference numerals as in the Figures 1 and 2 ,

In contrast to the above embodiment are present in the embodiment according to FIGS. 3 and 4 two pivotable secondary mass body 6 ₁ , 6 _{2 are} provided, which are rotatably mounted on the drive shaft 4 respectively. In this case, a first pivotable mass body 6 _{1 is} disposed above the primary mass body 5 and mounted by means of a connecting web 27 and the upper bearing 20 on the shaft 4. A second pivotable mass body 6 ₂ is arranged below the primary mass body 5 and pivotally connected to the shaft 4 by means of a connecting web 28 and a lower bearing 21. The two secondary mass body 6 ₁ , 6 ₂ are designed in the form of ring segments which extend over approximately 180 ° about the axis of rotation A. It is especially in FIG. 3 recognizable that an outer peripheral surface of the secondary mass body 6 ₁ , 6 ₂ protrude radially relative to an outer peripheral surface of the primary mass body 5. It follows that the center of gravity S6 ₁ , S6 _{2 of} the secondary mass body 6 ₁ , 6 _{2 have} a greater radial distance from the axis of rotation A than the center of gravity S5 of the primary mass body. 5

In the present embodiment, two stops 22 ₁ , 22 _{2 are} provided corresponding to the number of pivotable masses 6 ₁ , 6 ₂ , which are each connected to the primary mass body 5. The stops 22 ₁ , 22 ₂ are in each case axially beyond an end-side end face and radially beyond an outer peripheral surface 29 of the primary mass body 5. They are designed in the form of shorter beams, by the way as in the embodiment described above may be connected to the mass body 5. The present embodiment builds radially slightly smaller, since a radial overlap between the pivotable mass body 6 ₁ , 6 ₂ and the rotationally fixed mass body 5 is given. Incidentally, construction and operation of the above embodiment correspond to the description thereof in order to avoid repetition.

The FIG. 5 shows a deep vibrator 2 in another embodiment. This corresponds largely to the embodiment FIGS. 1 and 2 , so that reference is made to the above description in terms of similarities. The same or modified details are provided with the same reference numerals as in the Figures 1 and 2 or in the FIGS. 3 and 4 ,

A special feature of the present embodiment is that the deep vibrator 2 comprises a plurality of imbalance assemblies 11 ₁ , 11 ₂ , which are each received as a unit in the housing 7. Each unbalance assembly 11 ₁ , 11 ₂ each comprises a shaft part 4 ₁ , 4 ₂ , each by means of two bearings 12 ₁ , 13 ₁ ; 12 ₂ , 13 ₂ rotatably supported in the housing 7 and is rotatably driven by the rotary drive 3, and a primary and a secondary mass body 5, 6. In each case, a first bearing 12 ₁ , 12 ₂ above and a second bearing 13 ₁ , 13 ₂ below the associated mass body 5, 6 arranged to ensure a secure radial bearing over the entire length of the shaft. The individual shaft parts 4 ₁ , 4 ₂ are connected to each other via suitable shaft connections 14 ₁ , 14 ₂ , such as flange connections, wherein other connecting means are also conceivable. In the present case, two imbalance assemblies 11 ₁ , 11 _{2 are} provided, which are driven by a single rotary drive. It will be appreciated that three or more imbalance assemblies may also be used to produce even greater vibration amplitudes. These are drive-connected with each other via further shaft connections (14).

The FIGS. 6 and 7 show a deep vibrator 2 in another embodiment. This corresponds largely to the embodiment FIGS. 1 and 2 , so that reference is made to the above description in terms of similarities.

The same or modified details are provided with the same reference numerals as in the Figures 1 and 2 ,

A difference of the present embodiment from that after FIGS. 1 and 2 lies in the assignment of the two mass body 5, 6, which is reversed in the present case. It can be seen that in the present embodiment FIGS. 6 and 7 the primary mass body 5, which is non-rotatably connected to the drive shaft 4, that with a greater distance of the center of mass S5, while the pivotable about the drive shaft 4 mass body 6, the one whose center of gravity S6 is located on a smaller radius. The non-rotatable mass body 5 comprises a ring segment 17, an upper lid 18 and a lower lid 19, which are fixedly connected to each other. For the rotationally fixed connection can be provided between the upper and lower cover 18, 19 on the one hand and the drive shaft 4 on the other shaft splines 30, 30 'or other conventional shaft-hub connection. An axial support can be made via a thrust bearing. The pivotable mass body 6 can be rotatably mounted on the drive shaft 4, for example by means of a sliding bearing 20 and a slide bushing.

The relative rotational positions P1, P2 of the pivotable mass body 6 are defined by a stop element 22, against which the mass body 6 strike upon rotation of the rotary drive 3 and is thus arranged in a defined rotational position relative to the rotationally fixed mass body 5. The rotation stopper 22 is configured as a ledge or beam which is connected to the primary mass body 5 and protrudes radially inward from an inner circumferential surface. Otherwise, the embodiment corresponds to FIG. 6 in terms of structure and functioning of those according to FIGS. 1 and 2 , to the description of which reference is made.

It is understood that other embodiments are conceivable, which are not all disclosed in the present case. In particular, it is possible that the embodiments according to the FIGS. 3 to 5 can be designed with the reverse assignment of the first and second mass body 5, 6, that is external mass body rotatably connected to the drive shaft 4 and inside mass body mounted pivotably about the drive shaft 4.

LIST OF REFERENCE NUMBERS

2

deep vibrator

3

rotary drive

4

drive shaft

5

mass body

6

mass body

7

casing

8th

stator

9

rotor

10

motor shaft

11

Unbalance assembly

12, 13

camp

14

connecting means

15, 16

camp

17

ring segment

18

cover part

19

cover part

20, 21

camp

22

stop element

23

side surface

24

side surface

25

additional mass

26

additional mass

27

connecting web

28

connecting web

29

peripheral surface

30

connection

A

axis of rotation

P

position

R

direction

S

main emphasis

Claims (15)

1. A depth vibrator for compacting soil, comprising:

   a rotary drive (3);

   a drive shaft (4), which is rotatingly drivable about a rotary axis (A) by the rotary drive (3) in a first rotation direction (R1) and in an opposite second rotation direction (R2);

   a primary mass body (5), which is connected to the drive shaft (4) in a rotationally fixed manner and rotates together with same about the rotary axis (A);

   a secondary mass body (6), which is movable into a first rotation position (P1) relative to the primary mass body (5) by rotation of the drive shaft (4) in the first rotation direction (R1), in which first rotation position a centre of gravity (S6) of the secondary mass body (6) is approximate to a centre of gravity (S5) of the primary mass body (5), and which secondary mass body (6) is movable into a second rotation position (P2) relative to the primary mass body (5) by rotation of the drive shaft (4) in the second rotation direction (R2), in which second rotation position the centre of gravity (S6) of the secondary mass body (6) is further distanced from the centre of gravity (S5) of the primary mass body (5), wherein the secondary mass body (6) in the first and second rotation position (P1) is jointly rotatable together with the primary mass body (5) about the rotary axis (A);

   characterised in that

   the centre of gravity (S6) of the secondary mass body (6) and the centre of gravity (S5) of the primary mass body (5) have different radial distances from the rotary axis (A).
2. The depth vibrator according to claim 1,
   characterised in that
   the centre of gravity (S6) of the secondary mass body (6) has a greater radial distance from the rotary axis (A) than the centre of gravity (S5) of the primary mass body (5).
3. The depth vibrator according to claim 1 or 2,
   characterised in that
   the secondary mass body (6) is movable relative to the primary mass body (5) by a reversal of the rotation direction of the rotary drive (3), wherein a first resultant centre of gravity (Sres1) resulting from the primary mass body (5) and the secondary mass body (6) in the first rotation position (P1) has a first distance from the rotary axis (A) which is greater than a second distance from the rotary axis (A) which a second resultant centre of mass (Sres2) resulting from the primary mass body (5) and the secondary mass body (6) has in the second rotation position (P2).
4. The depth vibrator according to any one of claims 1 to 3,
   characterised in that
   a first rotation stop (23) is provided, against which the secondary mass body (6) is supported when the rotary drive (3) is rotated in the first rotation direction (R1), and that a second rotation stop (24) is provided, against which the secondary mass body (6) is supported when the rotary drive (3) is rotated in the second rotation direction (R2).
5. The depth vibrator according to any one of claims 1 to 4,
   characterised in that
   at least one of the first and the second rotation stop (23, 24) is provided on the primary mass body (5).
6. The depth vibrator according to any one of claims 4 to 5,
   characterised in that
   at least one of the first and the second rotation stop (23, 24) is part of a stop element (22), which is fixedly connected to the primary mass body (5).
7. The depth vibrator according to claim 6,
   characterised in that
   exactly one stop element (22) is provided, which comprises the first rotation stop (23) and the second rotation stop (24).
8. The depth vibrator according to any one of claims 6 or 7,
   characterised in that
   the stop element (22) can be designed in the form of a stop bar, which is fixedly connected to the primary mass body (5) and protrudes radially with respect to an outer circumferential surface (29) of the primary mass body (5) and extends in the axial direction over at least a third of the height of the primary mass body (5).
9. The depth vibrator according to any one of claims 1 to 8,
   characterised in that
   the primary mass body (5) is designed in the form of a cylindrical segment, which extends in particular over 180° about the rotary axis (A).
10. The depth vibrator according to any one of claims 1 to 9,
    characterised in that
    the secondary mass body (6) comprises an annular segment (17), which is mounted rotatably about the drive shaft (4), wherein the annular segment (17) extends in particular over more than 160° and/or less than 180° about the rotary axis (A).
11. The depth vibrator according to any one of claims 1 to 10,
    characterised in that
    the secondary mass body (6) is arranged with an axial overlap or with an axial offset with respect to the primary mass body (5).
12. The depth vibrator according to any one of claims 1 to 11,
    characterised in that
    the secondary mass body (6) is arranged at least partially radially outside the primary mass body (5).
13. The depth vibrator according to any one of claims 1 to 12,
    characterised in that
    at least one of the primary and the secondary mass bodies (5, 6) contains heavy metal.
14. The depth vibrator according to any one of claims 1 to 13,
    characterised in that
    the primary mass body (5) and the secondary mass body (6) are arranged on a shaft portion (4), wherein the shaft portion (4) is mounted rotatably in a housing part (7) of the depth vibrator by means of an upper bearing (15), which is arranged above the primary mass body (5), and by means of a lower bearing (16), which is arranged below the primary mass body (5).
15. The depth vibrator according to claim 14,
    characterised in that
    the shaft portion (4) is connected to a further shaft portion (4) for transmitting torque, wherein the further shaft portion (4) carries a further primary mass body (5) and a further secondary mass body (6), wherein the further shaft portion (4) is mounted rotatably in a housing part (7) of the depth vibrator by means of an upper bearing (15₂) and a lower bearing (16₂).

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