DE102010046820A1 - Device for soil compaction - Google Patents

Abstract

The invention relates to a device for soil compaction and in particular to a vibratory tamper with a substructure (2) comprising a tamping foot (4) and a lower guide cylinder (6) arranged thereon, and a superstructure (8) comprising a housing (10), a Upper guide cylinder (12) arranged thereon and at least one drive unit (14) which is operatively connected via a drive train (16) to the pad foot (4) in the substructure (2) in such a way that it is relative to the superstructure (8) along at least one compression axis (AV) is movable with at least one compression amplitude (a), the upper guide cylinder (12) and the lower guide cylinder (6) being movable relative to one another in the direction of the compression axis (AV) to form at least one axial guide (18), and wherein between the superstructure (8) and the substructure (2) at least one stop element (20) is arranged, which moves when a maximum compression amplitude (amax) is exceeded movement of the substructure (2) relative to the superstructure (8) locked.

Description

The invention relates to a device for soil compaction and in particular a vibratory rammer with a substructure, comprising a padfoot and a lower guide cylinder arranged thereon, and a superstructure, comprising a housing, an upper guide cylinder arranged thereon and at least one drive unit, which via a drive train with the padfoot is operatively connected in the substructure such that it is movable relative to the superstructure along at least one compression axis with at least one compression amplitude, wherein the upper guide cylinder and the lower guide cylinder are movable relative to each other in the direction of the compression axis to form at least one axial guide.

Such soil compaction devices are known in the art. They are usually constructed in such a way that, via a drive device in a superstructure of the rammer, a padfoot arranged in a substructure and in particular a ramming plate can be driven in oscillating axial movements in order to introduce compacting load pulses into the substrate.

The engine is usually about a Exzentertrieb with the padfoot in conjunction, the eccentric drive is in operative connection with a drive train, which converts the mechanical work of the engine in an axial movement of the drive train and the padfoot coupled thereto.

In order to allow a free axial movement of the padfoot, is usually formed at the free end of the connecting rod in the region of the substructure arranged in a guide cylinder spring set, which allows an axial swinging movement of the padfoot.

Such a vibratory rammer is for example by the US 3,090,286 known. It comprises a motor, on whose rotating output shaft an eccentric gear is arranged. The eccentric gear is operatively connected to a sliding block with a link of a connecting rod, so that the rotational movement of the motor in an axial movement of the connecting rod and thus the entire drive train of the vibratory rammer can be added.

The connecting rod has at its free end a guide piston, which is axially reciprocable via a piston guide within a lower guide cylinder belonging to the substructure. This axial direction corresponds to the compression movement during the compression operation. Axially on both sides of the piston guide a spring set consisting of one or more springs is arranged, wherein the springs are each supported on their sides facing away from the piston guide sides against the lower guide cylinder fixed spring plates. The lower guide cylinder engages in a sliding guide in an upper guide cylinder, which is rigidly connected to the housing of the Vibratorstampfers.

In the compression operation moves, driven by the oscillating drive train, the lower guide cylinder together with the associated padfoot or a tamping plate in the axial direction, wherein the maximum compression amplitude in the compression mode u. a is defined by the used spring set, the relative play of the upper and lower guide cylinder and the size of the eccentric drive. With sufficient dimensioning, this results in a vibration tamper with good compaction performance.

Occasionally, however, it may happen that the vibratory rammer falls, for example, when unloading from a truck with its full weight on the padfoot. The result is, as in the compression mode, a movement of the substructure or the padfoot on the superstructure. Depending on the fall pulse, it may be that the amplitude of movement introduced by the substructure relative to the superstructure is greater than is the case in normal compression operation. In such a case, the falling energy is then introduced via the drive train of the vibration rammer into the transmission device or the drive device. This can sometimes lead to severe damage.

For this reason, the known from the prior art designs of gearbox bearings in vibration absorbers are very large. However, this has a negative impact on the machine weight and the weight distribution of the entire machine.

The object of the present invention is therefore to provide a vibratory rammers of the aforementioned type, which is better protected with lighter and cheaper construction from damage, especially during transport.

This object is achieved by a device for soil compaction, and in particular a vibration tamper, comprising a substructure comprising a padfoot and a lower guide cylinder arranged thereon, and a superstructure comprising a housing, an upper guide cylinder arranged thereon and at least one drive unit via a drive train is in operative connection with the padfoot in the substructure such that it is movable relative to the superstructure along at least one compression axis with at least one compression amplitude, wherein the upper guide cylinder and the lower guide cylinder to form at least one axial guide are movable relative to each other in the direction of the compression axis, and wherein between the superstructure and the substructure at least one stop element is arranged, which locks the movement of the substructure relative to the superstructure when exceeding a maximum compression amplitude.

Under guide cylinder is understood in the scope of the invention, any component that can serve the leadership between the superstructure and substructure and / or the leadership of a arranged inside the guide cylinder drive train and in particular a connecting rod with spring cassette or spring set. This means that the guide cylinder can not only have the geometric shape of a cylinder, but also any other shape. In this context, amplitude is understood as meaning any maximum movement or maximum deflection in a direction of the compression axis, as occurs when driving pad feet via eccentric drives.

According to the invention, the stop element is an element which arrests the degree of freedom of movement in a relative movement between the upper and lower construction as soon as the relative movement has a higher amplitude than during the compression operation, or if this movement amplitude is greater than a so-called maximum compression amplitude.

Compression amplitude here essentially means the two maximum deflections that the superstructure and the substructure undergo relative to one another during the compression operation. Thus, if a padfoot oscillates and contracts relative to the superstructure in the compression mode, the compression amplitude corresponds to half the distance between completely steady state and fully swung out state, ie half the peak-to-peak value.

As soon as this compression amplitude is exceeded, for example due to the falling of the vibration rammer on the padfoot, the pestfoot thus moves toward the superstructure via the amplitude which is usually present during the compression operation, the abutment element between the superstructure and substructure comes into action, so that the movement of the substructure locked relative to the superstructure and in particular a power dissipation is prevented by falling over the drive train in the drive unit.

Such a case in which the stop member locks the relative movement between the superstructure and substructure, is called stopper case in the scope of the invention.

Since the load dissipation does not run over the drive train, etc. in the event of an impact, u. a. the powertrain and the transmission parts are dimensioned smaller; the machine weight is reduced favorably.

Of course, the above application also applies to an embodiment in which an excessive rebound of the substructure from the superstructure is to be prevented accordingly. Even in such a case, the stopper element can be used to prevent this.

The stop element and the two guide cylinders that can be moved relative to one another are preferably designed so that the stop case only occurs when the normal compression amplitude, which is present during the compression operation, is exceeded by a safety value. Thus, for example, moves the base to the superstructure by a compression amplitude of 20 cm, the stop element preferably occurs in action if the "impact amplitude" would be more than 30 cm. This means that in such a case, the substructure on the superstructure can move by a maximum of 30 cm before the stop element stops this movement, since the maximum compression amplitude is reached.

An embodiment which is advantageous with regard to the geometry of the soil compacting device has a stop element which is designed and arranged such that it is urged by the lower guide cylinder against the housing and / or the upper guide cylinder when the maximum compression amplitude is exceeded. In this way, loads which are registered via the lower guide cylinder, for example, when falling of the compression rammer on the padfoot, without damaging the drive device, the drive train and the transmission device on the upper guide cylinder and / or the housing removed.

In order to achieve a possible damage-free load dissipation and in particular movement lock, the stop element is preferably designed as an elastic stop element. Here all known from the prior art embodiments for stopper and in particular damping elements can be used. In particular, the stop element may be formed as a rubber buffer, which is arranged between the relatively moving parts and in particular the lower and the upper guide cylinder or the housing.

In order to achieve a position assurance of the stop element, in particular in the direction of the compression axis, the stop element has at least one fastening element, via which it is held substantially stationary on the superstructure or substructure. In this way, in particular the acceleration load acting on the stop element during the compression operation or, of course, also during the stop event is absorbed. Such a fastener may for example also be a form or adhesion element. Thus, it is possible to form on the stop element at least one fastening groove or a similar effective receiving element, in the locking engages at least one complementarily formed extension element on the superstructure or substructure, or vice versa. Also, the stop element can be attached via a suitable form or adhesion or a press fit on the superstructure or substructure. This is especially true for elastic stop elements. In particular, friction elements can also find their application as fastening elements. However, such a fastening element can also be a locking screw which secures the fastening element against suitable components on the superstructure or on the substructure.

Structurally advantageous is an embodiment in which the stop element is held orthogonal to the compression axis by the upper guide cylinder or the lower guide cylinder substantially stationary. The upper or the lower guide cylinder serve in such a case so at least as an axial guide for the stop element.

In particular, in an embodiment in which the drive train is guided within the upper guide cylinder and the lower guide cylinder, the stop element preferably has a stop sleeve or the like ring element, which surrounds the drive train at least partially. This allows for a position securing the stop element on the upper or lower guide cylinder, on the other hand, the space-saving and in particular secured against mechanical stress positioning of the stop element.

In an embodiment in which the guide cylinders are relative to each other in an axial sliding guide, wherein the lower guide cylinder form an inner guide and the upper guide cylinder an external guide or vice versa, the stop element has at least one stop sleeve, which is slipped over the inner guide and at least when crossing the maximum compression amplitude, the relative movement between the inner guide and outer guide arresting occurs with an outer guide stop area on the outer guide and / or an inner guide abutment portion on the inner guide in operative engagement.

Such an axial sliding guide between the upper and the lower guide cylinder can therefore, and then the passage "or vice versa", both by a design with a lower inner guide and an overhead outer guide as well as with a lower outer guide and an overhead Internal guide are formed.

In principle, it is possible with such a "telescopic" guide cylinder to arrange the stop element in the form of a stop sleeve between the two guides so that they come into operative engagement via formed on the respective guide abutment areas on the intermediate stop element and so the relative movement to each other or away from each other lock. An attachment of the stop element is here u. a. possible via a frictional connection.

In particular, in this context, it should be noted that in principle the stop element, of course, not only can be designed so that it locks the movement of the substructure on the superstructure, but also arrests a movement of the substructure away from the superstructure, to damage the drive train etc. by to prevent excessive tensile loads. In the first case, the stop element is then loaded as a pressure element in the second case as a tension element.

The stop sleeve may be formed so that it is in press fit with the lower or the upper guide cylinder and is thus held stationary in the axial direction and / or orthogonal direction. It is also possible to provide suitable bearing or locking means on the outer guide or inner guide stop areas, which allow fixing of the stop element at least at one of these stop areas. Thus, for example, the inner guide stop area may be provided with a locking groove into which the stop element or its stop sleeve can be latched with a suitable locking extension. Basically, all locking means are applicable here to fix the stop element or its stop sleeve on the outer guide stop area or inner guide stop area.

In order to achieve a particularly effective storage of the stop sleeve on the guide cylinder, this preferably has suitable recesses on which the stop element is supported with complementary projections formed, or vice versa. In this way, in the event of an attack over the entire length of the stop element Transfer force between the lower guide cylinder and the upper guide cylinder or the housing.

In particular in pressing areas, where the stop element comes into contact with the outer guide stop areas and / or the inner guide stop areas, the guide element has reinforcements which ensure positive contact and reliable load transfer.

In a stop element arranged on the inner guide and in particular on an outer jacket of the inner guide, and in particular in a stop element designed as a stop sleeve, the complementary outer guide stop area is preferably formed on an end face region of the outer guide. This means that when the maximum compression amplitude is exceeded, the stop element arranged on the inner guide abuts against the end face region of the outer guide, thus arresting the relative movement between the outer guide and the inner guide.

In another embodiment, wherein the guide cylinder relative to each other in an axial sliding guide, the lower guide cylinder forming an inner guide and the upper guide cylinder form an external guide, or vice versa, the stop element is disposed within the outer guide, so that it exceeds the maximum compression amplitude, the relative movement between the inner guide and the outer guide arrives in operative engagement with an inner guide stop area on the inner guide. In such a case, the inner guide stop region is then preferably formed on an end face region of the inner guide.

In the above embodiment, the stop element is preferably arranged completely mechanically protected within the outer guide, and in particular positioned in permanent contact with the housing, so that when exceeding the maximum compression amplitude of the inner guide abutment portion meets against the stop element, and so the relative movement between the upper and the lower guide cylinder locked, with the resulting forces are derived directly into the housing.

Not only in such a case, it is possible to form the stop element as complementary to the internal geometry of the outer guide formed stop plate, which has in particular centrally a passage opening for the drive train. In this way, the stop element is guided through the inner wall of the outer guide and / or through the centrically extending drive train. In particular, the stop element can serve in such an embodiment to prevent the buckling of the drive train and in particular a connecting rod perpendicular to the punch axis. Here, for example, appropriate stabilizing elements may be provided in the stop element. It is also possible to provide the stop element in the region of the passage for the drive train with suitable storage means.

Further embodiments of the invention will become apparent from the dependent claims.

In the following the invention will be described with reference to two embodiments, which are explained in more detail by the accompanying drawings. Here are shown schematically:

1 a longitudinal section through an embodiment of the device according to the invention for soil compaction; and

2 a detailed representation of a longitudinal section accordingly 1 a second embodiment of the device for soil compaction.

In the following, the same reference numerals are used for the same and the same components, sometimes with the use of high indices to distinguish them.

1 shows a longitudinal section through an embodiment of the device according to the invention for soil compaction and in particular a Vibrationsstampfer 1 ,

The vibration tamper 1 includes a superstructure 8th and a substructure 2 which are movable relative to each other. This movement is guided by an upper guide cylinder 12 that with a lower guide cylinder 6 in an axial sliding connection coaxial with the compression axis A _V is. The upper guide cylinder 12 is stationary on a housing 10 of the superstructure 8th arranged while the lower guide cylinder 6 stationary with a stamping plate 5 connected, and a padfoot 4 forms. The two guide cylinders 6 . 12 In this case, they are movable relative to one another in such a way that a ramming movement for soil compaction in the circumference of a compression amplitude a along the compaction axis AV can be carried out.

In this embodiment, the upper guide cylinder forms 12 an outer guide into which the lower guide cylinder 6 telescopically in and out in the form of an inner guide. The inner guide 6 and the outside guide 12 together form an axial guide 18 for the padfoot 4 and the powertrain arranged inside 16 ,

To the two together in sliding guide upper or lower guide cylinder 6 . 12 To protect against mechanical shocks and especially against dust, outside is a bellows 30 arranged, the two guide cylinder 6 . 12 surrounds.

The vibration tamper is driven 1 via a drive unit 14 , in the superstructure and in particular on the housing 10 is stored, and over the drive train 16 with the stamp foot 4 is in active connection.

The drive unit 14 includes a motor 3 that has an output shaft 19 with a gear unit 15 and in particular an eccentric drive 34 the rotary motor movement in an axial movement of a connecting rod 38 of the drive train 16 along the compression axis A _V converts. The connecting rod 38 ends in a piston guide 13 inside the lower guide cylinder 6 axially along the compression axis A _V is performed.

To this piston guide 13 connected is a spring set 17 , the piston guide 13 resilient with the lower guide cylinder 6 connects and so a sprung axial movement of the stamping plate 5 or the peat foot 4 along the compression axis A allowed.

During the compacting operation, the padfoot oscillates 4 or the stamping plate 5 to the amplitude a shown here between the zero position shown here (indicated by the reference numeral 40 ) and a maximum deflection (indicated by the reference numeral 42 ) back and forth.

Once on the padfoot 4 a strain that affects him from the in 1 Moving position shown in the direction of the superstructure, there is a risk that loads on the drive train 16 and the gear unit 15 must be removed.

That's why in the interior 21 of the upper guide cylinder 12 or the external guide 12 a stop element 20 arranged, which is the movement of the lower guide cylinder 6 or the inner guide 6 on the superstructure 8th locked to when a maximum amplitude of motion a _{max is} exceeded.

This stop element 20 is designed so that it exceeds the maximum amplitude a _max with an inner guide stop area 36 the inner guide 6 enters into operative connection and the over this inner guide stop area 36 registered loads to the housing 10 forwards. The inside guide stop area 36 is in this embodiment on the front side area 28 the inner guide 6 arranged.

It can be seen that, in this embodiment, there is a difference between the "normal" compression amplitude a and the maximum compression amplitude a _max, and in particular a securing area b, which is the abutment against the stop element 20 allowed only when the compression amplitude a is significantly exceeded by the value b. Among other things, this securing area contributes to the swinging motion via the spring set 17 Bill.

The stop element 20 is formed in this embodiment, that it with the inner wall 11 the outside guide 12 in press fit. In addition, on the inner wall 11 a recording area 23 provided, which is complementary to the stop element 20 is formed and thus both a storage of the stop element 20 orthogonal to the compression axis A _V and coaxial to ensure.

The upper guide cylinder 12 is arranged so that it is the stop element 20 fixed laterally while axial forces, registered by the inner guide stop area 36 of the lower guide cylinder 6 directly into the housing 10 or an outer guide stop area 32 be derived.

In summary, the oscillation movement of the vibration rammer 1 as follows: The in 1 illustrated position of the padfoot 4 corresponds to the maximum raised position with static, that is not swinging, view of the padfoot 4 , The position also shown 42 corresponds to the zero position in the compression mode. The deflection represented by the value a _s results from the spring-elastic behavior of the spring set 17 that has a pounding foot free swinging 4 relative to the superstructure 8th allows, so the peat foot 4 with the compression amplitude a on the superstructure 8th moved. The likewise drawn amplitude a _max corresponds to the amplitude, the maximum through the two guide cylinder 6 . 12 can be passed through before the stop element 20 suppresses this relative movement. This can, for example, to cushion the falling of the vibrating cylinder 1 serve from a specific height. Once in particular during compression of the substructure 2 this maximum compression amplitude a _{max is} exceeded, locks the stop element 20 the compression movement, so in particular the drive train 16 and the gear unit 15 no loads have to be removed by this compression movement.

Shown is in addition to the amplitudes a _s , a and the maximum amplitude a _max a backup area b, which guarantees that it is not constantly for striking the stop element in particular in material fatigue or component inaccuracies 20 comes. Only after the compression amplitude a is significantly exceeded by this area b, the stop element locks 20 the relative movement of the substructure 2 to the superstructure 8th ,

In 2 is another embodiment of a vibration rammer 1 and in particular its substructure 2 is in a longitudinal section as shown 1 shown. Again, there is an upper guide cylinder 12 with a lower guide cylinder 6 of the substructure 2 in an axial guide 18 in operative connection, so that a padfoot 4 or a stamping plate 5 via a drive train 16 coaxial with the compression axis A _{V can be driven} in a compression movement. The lower guide cylinder 6 forms the inner guide and the upper guide cylinder 12 the outside guide.

Also, this embodiment has to lock the movement of the padfoot 4 or the inner guide 6 relative to the outer guide 12 via a stop element 20 Thats here as a stop sleeve 24 on the outer wall 25 of the lower guide cylinder 6 pushed. As a fastener 22 serve here form and frictional elements; the stop sleeve 24 is so complementary to the outer wall 25 formed the inner guide that its position is held by friction in the axial direction of the compression axis A. This attachment is reinforced by the elastic design of the stop element

The stop element 20 is at the foot area 7 of the peat foot 4 arranged, with an inner guide stop area 36 at the foot area 7 of the peat foot 4 supported. In addition, the stop element has 20 bearing projections 29 on, in the complementarily formed bearing recesses 31 on the inner guide 6 support.

The stop element 20 or its stop sleeve 24 are arranged so that when exceeding the maximum amplitude a _max and especially in case of too strong compression of the padfoot 4 this movement by the operative engagement between the stop sleeve 24 and an outer guide abutment area 32 on the outside guide 12 is locked. The outer guide abutment area is at the end face area in this embodiment 26 arranged the outer guide. In this respect, the operation of this embodiment corresponds to the above-described operation of the first embodiment.

The difference, however, is that by the positioning of the stop element 20 on the outer wall 25 of the lower guide cylinder 6 the introduction of force when exceeding the maximum compression amplitude a _max above the upper guide cylinder 12 or the outer guide 12 in the case 10 he follows. Again, forces from exceeding the maximum amplitude a _{max are} not in the drive train 16 or the transmission unit introduced, but removed directly through the housing.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• US 3,090,286 [0005]

Claims (10)

Device for soil compaction ( 1 ), in particular vibration tampers, with a substructure ( 2 ) comprising a padfoot ( 4 ) and a lower guide cylinder ( 6 ), and a superstructure ( 8th ), comprising a housing ( 10 ), an upper guide cylinder ( 12 ) and at least one drive unit ( 14 ), which via a drive train ( 16 ) with the padfoot ( 4 ) in the substructure ( 2 ) is operatively connected in such a way that this relative to the superstructure ( 8th ) along at least one compression axis (A _V ) with at least one compression amplitude (a) is movable, wherein the upper guide _cylinder ( 12 ) and the lower guide cylinder ( 6 ) forming at least one axial guide ( 18 ) are movable relative to each other in the direction of the compression axis (A _V ), characterized in that between the superstructure ( 8th ) and the substructure ( 2 ) at least one stop element ( 20 ) is arranged, which when exceeding a maximum compression amplitude (a _max ), the movement of the substructure ( 2 ) relative to the superstructure ( 8th ) arrested. Device according to claim 1, characterized in that the stop element ( 20 ) is designed and arranged such that when the maximum compression amplitude a _{max of} the lower guide cylinder ( 6 ) against the housing ( 10 ) and / or the upper guide cylinder ( 12 ) is urged. Device according to one of the preceding claims, characterized in that the stop element ( 20 ) is formed as an elastic stop element. Device according to one of the preceding claims, characterized in that the stop element ( 20 ) at least one fastening element ( 22 ), over which it is in particular in the direction of the compression axis A _V on the superstructure ( 8th ) or substructure ( 2 ) is held substantially stationary. Device according to one of the preceding claims, characterized in that the stop element ( 20 ) orthogonal to the compression axis A _V through the upper guide _cylinder ( 12 ) or the lower guide cylinder ( 6 ) is held substantially stationary. Device according to one of the preceding claims, wherein the drive train ( 16 ) within the upper guide cylinder ( 12 ) and the lower guide cylinder ( 6 ), characterized in that the stop element ( 20 ) as a stop sleeve ( 24 ) or the like ring element, the drive train ( 16 ) at least partially surrounds. Device according to one of the preceding claims, characterized in that the guide cylinders ( 6 . 12 ) are relative to each other in an axial sliding guide, wherein the lower guide cylinder ( 6 ) an inner guide and the upper guide cylinder ( 12 ) form an outer guide, or vice versa, and wherein the stop element ( 20 ) a stop sleeve ( 24 ), which via the inner guide ( 6 ) and at least when the maximum compression amplitude a _{max is} exceeded, the relative movement between the inner guide ( 6 ) and external guidance ( 12 ) arresting with an outer guide stop area ( 32 ) on the outer guide ( 12 ) and / or an inner guide stop area ( 36 ) on the inner guide ( 6 ) enters into operative engagement. Device according to one of the preceding claims, in particular claim 7, characterized in that the outer guide stop area ( 32 ) at a front side area ( 26 ) of the outer guide ( 12 ) is trained. Device according to one of the preceding claims, in particular one of claims 1 to 6, characterized in that the guide cylinder ( 6 . 12 ) are relative to each other in an axial sliding guide, wherein the lower guide cylinder ( 6 ) an inner guide and the upper guide cylinder ( 12 ) form an outer guide, or vice versa, and wherein the stop element ( 20 ) within the outer guide ( 12 ) is arranged and when the maximum compression amplitude a _max is exceeded, the relative movement between the inner guide ( 6 ) and external guidance ( 12 ) arresting with an inner guide stop area ( 36 ) on the inner guide ( 6 ) enters into operative engagement. Device according to one of the preceding claims, in particular claim 9, characterized in that the inner guide stop area ( 36 ) at a front side area ( 28 ) of the inner guide ( 6 ) is trained.

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