EP0975839B1 - Compactor for compacting soil - Google Patents

Description

The invention relates to a ramming device for soil compaction according to the preamble of claim 1.

Such devices, which are supported on the ground solely by the pest foot, be by an operator through direct transfer of executives by means of a guide bracket or about a drawbar during the Swinging movement of the padfoot in the desired direction out. at switched off drive, the device is difficult to transport, it must be worn or with a suitable device, such as a cart.

Due to the manual operation, the weight of such devices is limited, which is why z. As the equipment with relatively heavy diesel engines to difficulties encounters.

In JP-A-04312603 a ramming device for soil compaction is described, with a ramming tool in which a working mass via a crank mechanism linear reciprocating drivable. The ramming tool is over a chassis additionally supported against the ground. Between the crank mechanism and the working mass is arranged a spring set. The ramming tool can be pivoted relative to the chassis using a worm gear.

The invention is based on the object, a ramming device of the type described above To design a way such that generated by the rammer Vibrations as low as possible on the chassis or an operator of the Ramming device can be transmitted.

According to the invention the object is achieved by a ramming device according to claim 1 solved.

Due to the chassis of the rammer is also switched off Rammer drive easily movable without additional tools. During the rammer operation are due to the rolling Support of essential weight components of the device required executives noticeably reduced. Furthermore offers the possibility of the total weight of the rammer beyond the previously considered acceptable limit to increase and, for example, the rammer with a heavy To provide diesel engine.

A very advantageous embodiment provides that the additional Suspension carries the combustion engine.

Another very advantageous embodiment is to provide the landing gear with a self-propelled, preferably for generating the ramming movement and the chassis drive a common power source is provided. Of the Self-propelled chassis can be advantageous as a hydraulic drive be formed or done via a drive chain. Conveniently, the suspension drive between front and Reverse switchable.

At any time with the rammer off a secure state To ensure the device, the suspension can be beneficial by an additional support wheel on the of the drivable Axis facing away from the padfoot as a three-point landing gear be educated.

To wear the suspension under the influence of the Stampers generated vibrations due to the chassis as possible To keep it low, it is very beneficial to those with the chassis stabilize associated upper mass of the rammer, i. their movement during the Stampferbetriebs as low as possible to keep.

Known, hand-guided rammers are designed to that the upper mass is about two-thirds and the beating work- or lower mass one third of the total rammer mass while that of the upper mass and the working mass each path traveled in inverse proportion to each other stand. The upper mass moves in the order of magnitude from 25 to 30 mm.

This movement of the upper mass at a frequency of 10 - 11 Hz has many negative effects because these vibrations not just on the body of the implement over a Guide bracket leading person, especially on hand and Poor, transmitted, but because also high loads of attached drive motor regardless of its design and equally result of the inventively provided suspension.

The output power of the ramming system is largely of the Upper mass dependent because too much work mass or too high speed of the working mass the upper mass oversized moves and amplifies the problems described above.

By a substantial increase in the upper mass could indeed these harmful effects are partially contained. Thereby but the total weight of the rammer would be greatly increased, which not only increase the power requirement of the drive motor but also the ease of operation by the chassis would compensate again.

To the upper mass without significant weight increase of the device to stabilize and thereby the life of the device increase its handling and improve the operator from the harmful effects of vibrations To better protect, there is a particularly advantageous Embodiment of the device according to the invention in that it is in Area of the upper mass with one together with the working mass, but in the opposite direction to the movement of the working mass of Motor driven countermass is provided.

The upper mass is from one himself to his case supporting crank drive pushed in the moment up, in which the crank drive via its connecting rod, a guide piston and a spring set the working mass and thus the padfoot pushes down. The Federsatz has the consequence that at the Downward movement of the guide piston initially under these springs Energy intake are curious, what they do with one conditional delay then the stored Return energy to the downward movement of the pest foot. This delay must be taken into account when the movement the counterweight matched to the movement of the working mass becomes. When the working mass through the crank pin of the crank mechanism is pulled up again, the upper mass moved down.

An advantageous embodiment is that the Drive the counterweight is derived from the crank mechanism and the Movement of the connected to the crank mechanism end of the spring set and the movement of the counterweight relative to the crank angle by 180 ° minus one of the design parameters the spring set derived phase shift against each other are offset.

When connected to the crank gear end of the spring set exceeds the lower end point of its linear motion is the energy previously stored in the spring set as ramming or Released impact energy, so that only to this Time the countermovement of the counterweight for damping the Movement of the upper mass is desired, or in other words: the movement of the countermass into the top dead center is supposed to be the first take place when connected to the crank mechanism end of the Federsatzes has already reached its bottom dead center. This is due to the phase shift described above at least approximately in practice Design parameters must be coordinated.

After an expedient embodiment, the counterweight is on the upper mass parallel to the direction of movement of the working mass is guided. There is an advantageous embodiment in that the counterweight of a Ausgleichsexzenter on the crank mechanism is driven, for example via a Connecting rod. According to another advantageous embodiment can the connection between the countermass and the Balancing eccentric be designed as a crank loop.

According to another expedient variant, the counterweight exists of two each on one side or the other of the crank mechanism at about the same height with respect to the axis of rotation of Crankshaft arranged sub-masses and each sub-mass is from an eccentric on an associated, with the Crank drive rotatably coupled eccentric disc, the connection between the eccentric pin and the associated Part mass is executed in each case as a crank loop.

A further advantageous variant is that the counterweight from at the upper mass around mutually parallel axes rotatably mounted, driven in opposite directions by the crank mechanism driven Imbalance exists whose momentum and mutual momentum Phase are set up so that they are one of the Work mass counteracting directed vibration, wherein a further embodiment is that the counterweight from two symmetrical to the direction of movement of the working mass next to each other at about the same height in this direction arranged, in opposite directions rotatably coupled directly to each other, consists of crank mechanism driven flyweights.

Another expedient embodiment for avoiding Seitenkräften is that the counterweight from a direct on the shaft of the crank mechanism sitting first flyweight and two symmetrical to the direction of movement of the working mass next to each other at about the same height in this Direction arranged second flyweights of each other same momentum exists, in the opposite direction to the first Flyweight are rotatably driven by the crank mechanism and their Momentum each about half as large as that Moment of inertia of the first centrifugal weight.

Yet another variant is that the counterweight from a sitting directly on the axis of rotation of the crank mechanism first flyweight and a second arranged behind it Flyweight exists, which has approximately the same moment of inertia like the first flyweight and one against the axis of rotation of the crank mechanism parallel to the direction of movement of Working mass slightly offset axis of rotation in the opposite direction to the first Flyweight is driven.

Based on the following description in the drawing illustrated embodiments of the innovation is this explained in more detail.

Fig. 1

eine Seitenansicht eines neuerungsgemäß ausgebildeten Stampfers mit Hydraulikantrieb des Einachs-Fahrwerks,

Fig. 2

eine Ansicht auf das in Fig. 1 gezeigte Gerät von rechts,

Fig. 3

eine der Fig. 1 ähnliche Seitenansicht eines Stampfers mit Kettenantrieb des Fahrwerks und einem zusätzlichen Stützrad,

Fig. 4

eine Ansicht auf das in Fig. 3 gezeigte Gerät von rechts,

Fig. 5

eine Schnittansicht einer ersten Ausführungsform des Kurbeltriebs zur Erzeugung der Stampfbewegung mit Gegenmasse, quer zur Kurbelachse gesehen und teilweise geschnitten in einer die Kurbelachse enthaltenden Ebene,

Fig. 6

einen Detailschnitt durch das Gehäuse des Kurbeltriebs der in Fig. 5 gezeigten Ausführungsform in einer zur Kurbelachse rechtwinkligen Ebene,

Fig. 7

eine der Fig. 5 ähnliche Ansicht nach einer zweiten Ausführungsform,

Fig. 8

eine der Fig. 6 ähnliche Schnittansicht der zweiten Ausführungsform,

Fig. 9

eine der Fig. 8 ähnliche Schnittansicht bei einer dritten Ausführungsform,

Fig. 10

eine der Fig. 8 ähnliche Schnittansicht bei einer vierten Ausführungsform,

Fig. 11

eine der Fig. 8 ähnliche Schnittansicht bei einer fünften Ausführungsform,

Fig. 12

eine der Fig. 7 ähnliche Ansicht nach einer sechsten Ausführungsform und

Fig. 13

eine der Fig. 8 ähnliche Schnittansicht der zweiten Ausführungsform.

It shows:

Fig. 1

a side view of a renewal trained rammer with hydraulic drive of the single-axle chassis,

Fig. 2

a view of the device shown in Fig. 1 from the right,

Fig. 3

1 similar side view of a rammer with chain drive of the chassis and an additional support wheel,

Fig. 4

3 is a view of the device shown in FIG. 3 from the right,

Fig. 5

3 a sectional view of a first embodiment of the crank mechanism for generating the ramming movement with counterweight, viewed transversely to the crank axis and partially cut in a plane containing the crank axle,

Fig. 6

a detail section through the housing of the crank mechanism of the embodiment shown in Figure 5 in a plane perpendicular to the crank axis,

Fig. 7

5 similar view according to a second embodiment,

Fig. 8

6 is a sectional view of the second embodiment similar to FIG.

Fig. 9

8 is a sectional view similar to FIG. 8 in a third embodiment,

Fig. 10

8 is a sectional view similar to FIG. 8 in a fourth embodiment,

Fig. 11

8 is a sectional view similar to FIG. 8 in a fifth embodiment,

Fig. 12

a view similar to FIG. 7 according to a sixth embodiment and

Fig. 13

one of the Fig. 8 similar sectional view of the second embodiment.

The renewal trained ramming device is in a first, in particular with 100a designated embodiment in the Figs. 1 and 2 and in a second, generally designated 100b Embodiment shown in Figs. 3 and 4, wherein usually by hand on a guide bracket or a Drawbar guided ramming tool referred to as 110a and 110b is. The ramming tool 110a is about parallel links 112 and 114 connected to a single-axle chassis 116a, the two wheels 118 and 120, whose track is the width of the padfoot 12th of the ramming tool 110a does not exceed.

In the variant according to Figures 3 and 4, the ramming tool 110b is approximately rigidly connected to the chassis 116b, i. it Only a slight relative movement by elastic attenuators 124 and 126 between the ramming tool 110b and the chassis 116b allows the transmission of vibrations to counteract the chassis 116b. Another, striking difference is that the suspension 116b by a third jockey wheel 128 to a three-point suspension is added to the stability, especially at off ramming tool 110b to improve. This third jockey wheel 128 is supported by a crankcase 14 of the Tamping tool 110b mounted arm 130 is worn.

On the chassis 116a or 116b is otherwise directly with the Stamping tool 110a and 110b connected guide bracket 132nd appropriate.

To operate the Stampffußes 12 serves in the crankcase 14 of the ramming tool 110a and 110b arranged crank drive, which will be explained in more detail with reference to FIGS. 5 to 13. To drive the crank mechanism rammed 100a or 100b provided with an internal combustion engine, by the chassis 116a and 116b is supported and arranged in the area 134 is.

In the embodiment of FIGS. 1 and 2 is a Oscillation between the ramming tool 110a and the chassis 116a possible with a relatively large angular deflection. This device 100a is therefore equipped with a hydraulic drive, the one with the engine, not shown in the area 134 connected hydraulic pressure source includes. On the crankcase 14 is a hydraulic motor 136 for operating the crank mechanism attached, via supply lines 138 to the pressure source connected is. Supply lines 140 lead in the area of the chassis 116a to a hydraulic drive 142 of the Landing wheels.

At the relatively low movement between the ramming tool 110b and the chassis 116b may be a direct drive connection between the arranged in the region 134 internal combustion engine and arranged in the crankcase 14 crank mechanism be provided, with only a small compensation of the axial offset is required, the expert no difficulties prepares. It can therefore rely on a hydraulic drive waived and provided to drive the wheels a chain drive 144 become.

The ramming tool 110a or 110b is dynamic from one associated with the padfoot 12 Working mass over one of a bellows fairing section 18 hidden spring set with a crank mechanism is connected, which is stored in the so-called. Upper mass, represented by the crankcase 14 in FIGS becomes. By the crank mechanism is a vibration between Built up and working mass. To improve the Handling and the life of the device should be the movement the upper mass are kept as small as possible. Serve this purpose the measures described below with reference to FIGS. 5 to 13.

As shown in Fig. 5 shows the crank mechanism via an engine output shaft 22 supplied with drive energy, with a Pinion 24 is provided with a crank 26 in Intervention is. The crank pulley 26 carries two by about 180 ° offset crankpins 28 and 30 (Figure 6). The crank pin 28 is about a bow-shaped, the output shaft 22 encompassing Connecting rod 32 connected to a guide piston 34 which in a connected to the crankcase 14 piston guide 36 in the direction the axis 16 is arranged to be movable and - in Fig. 5th obscured by the bellows-like section 18 - over the Federsatz with the padfoot 12 is connected. With the crankpin 30 is connected via a connecting rod 38, a piston 40 which also in the direction of the axis 16 movable in a piston guide 42 is arranged and together with the connecting rod 38 a Countermass to working mass forms.

In Fig. 6 is between the crank pin 28 and 30 an angle kelabstand of 180 ° shown. This would the piston or the Counter mass 40 reach the top dead center when the with the Not shown spring set associated guide piston 34 its bottom dead center reached. For the reasons already described but the piston 40 is dependent on design features of the spring set the top dead center delayed reach, which is why the angular distance by a certain phase shift angle less than 180 ° must be selected. In In practice, this phase shift angle can be 50-70 °.

When in Figs. 7 and 8 variant illustrated with the pinion gear 24 ₁ to the output shaft 22 ₁ engaged crank disk 26 ₁ is provided with a for forming the crankpin 28 ₁ and 30 ₁ cranked crank 29, wherein the free end the crank 29 forming crank pin 28 ₁ engages in a sliding block 31 which is slidably disposed in a guide slot 33 which is formed in a piston serving as counterweight 40 ₁ . The piston 40 ₁ is movably guided parallel to the movement axis 16 in a guide 42 ₁ formed on the crankcase 14 ₁ . On the crank pin 28 ₁ , the connecting rod 32 _{1 is} mounted for connection to the guide piston, not shown, the movement transmission to the spring set serving. The operation of this Varriante largely corresponds to the construction of FIGS. 5 and 6, but allows because of the drive of the counterweight by a crank grinding a shortened in the direction of the movement axis 16 construction.

In Fig. 9, a variant is shown, which also provides a crank grinding for the counterweight, the arrangement allows a further reduction. The provided with the crank pin 28 ₂ for the connecting rod 32 ₂ for transmitting motion on the spring set crank 26 ₂ is rotatably connected to a coaxially arranged gear 35, with both sides of the movement axis 16 and with respect to this at the same height two toothed on the circumference Eccentric discs 37 and 39 are engaged. The eccentric discs each carry an eccentric pin 30a ₂ and 30b ₂ , the guide slots 33a ₂ and 33b _{2 of} two identically formed pistons 40a ₂ and 40b ₂ which together form the counterweight and the associated ones in them, on the crankcase 14 ₂ trained guides 42a ₂ and 42b ₂ are slidably mounted parallel to the axis of movement.

The following variants replace the linearly movable countermass by rotating imbalances.

In the variant according to FIG. 10, a toothed wheel 35 _{3 is} non-rotatably connected to the crank disk 26 ₃ for the actuation of the connecting rod 32 ₃ and coaxial with it. On both sides of the movement axis 16 and with the same distance from this and at the same height in relation to these two intermeshing toothed disks 37 ₃ and 39 _{3 of the} same size and number of teeth are arranged, which are each provided with a flyweight 41 and 43 respectively. The toothed disc 37 ₃ is rotatably and coaxially connected to a gear 45 which is in engagement with the gear 35 _{3 of the} same number of teeth, so that the two flyweights 41 and 43 in a predetermined phase position for movement of the connecting rod 32 ₃ move in opposite directions. The centrifugal weights 41 and 43 are arranged such that their respective positions are mirror images of the movement axis 16. As a result, both side forces are avoided, as they are caused in the embodiments of FIGS. 5 and 6 by the inclined connecting rod 38, as well as friction losses in the guides 33, 33a ₂ and 33b _{2 shown} in FIGS. 7 to 9 avoided.

The variant according to FIG. 11 shows an unbalance acting on the crank mechanism in only one direction and two counterbalancing imbalances which create a mass balance and thus also prevent any lateral movement. The imbalance on the crank mechanism is represented by the flyweight 47 on the crank disk 26 ₄ . Two in diameter with the crank disc 26 ₄ matching, provided with centrifugal weights 41 ₄ and 43 ₄ discs 37 ₄ and 39 ₄ are arranged symmetrically to the movement axis. The three disks 26 _4, 37 ₄ and 39 ₄ are connected by a slip-free transmission connection, for example a chain 51 to move together such that the two discs 37 ₄ and 39 _4, but move in the same direction of rotation opposite to the crank disk 26. ₄

12 and 13 show a final variant, which is a development of the variant of FIG. 11 in that the two co-rotating discs 37 ₄ and 39 _{4 are} now replaced by a single disc 53, in the direction of the output shaft 22 _fifth is offset from the crank pulley 26 ₅ and driven by the output shaft 22 ₅ via its own pinion 55 and an intermediate gear 57 in opposite directions to the crank pulley 26 ₅ and is provided with a flyweight 59.

Claims (24)

1. Stamping device (100a, 100b) for ground compaction which can be manually guided by means of a guide bracket or the like and has a stamping tool (110a, 110b), wherein a working mass (12) can be driven in a linearly reciprocating manner by an internal combustion engine via a crank drive (26, 28, 30), wherein

   the stamping tool (110a, 110b) is additionally supported against the ground via an at least single-axle running gear (116a, 116b),

   a spring assembly is disposed between the crank drive (26, 28, 30) and the working mass (12),

   the stamping tool (110a, 110b) having the running gear (116a, 116b)
      is moveable to a limited extent via resilient connecting elements (124, 126), or
      is connected in a movable manner via parallel guide bars (112, 114); and wherein

   the stamping tool (110a, 110b) is movable relative to the running gear (116a, 116b) when the stamping device (100a, 100b) is being operated in order to counteract the transfer of vibrations.
2. Stamping device as claimed in Claim 1, characterised in that the additional running gear supports the internal combustion engine.
3. Stamping device as claimed in Claim 1 or 2, characterised in that the running gear (116a, 116b) is provided with a dedicated drive (142, 144).
4. Stamping device as claimed in Claim 3, characterised in that the running gear drive (142, 144) can be switched between forward and reverse motion
5. Stamping device as claimed in any one of Claims 3 or 4, characterised in that a common power source is provided for generating the stamping movement and for the dedicated drive.
6. Stamping device as claimed in Claim 5, characterised in that a hydraulic power transmission (136, 138) is provided at least for driving the crank drive.
7. Stamping device as claimed in any one of Claims 3 to 6, characterised in that the power is transmitted to the running gear via a chain drive (144).
8. Stamping device as claimed in any one of the preceding Claims, characterised in that an upper mass supporting the crank drive is connected to the running gear (116b) in an at least approximately rigid manner.
9. Stamping device as claimed in Claim 8, characterised in that the upper mass is connected to the running gear in a limited movable manner via resilient connecting elements (124, 126).
10. Stamping device as claimed in any one of Claims 8 or 9, characterised in that the running gear (116b) is supplemented by an additional, supporting wheel (128) on the side of the stamping foot (12) remote from the drivable axle to form a three-point running gear.
11. Stamping device as claimed in Claim 6 or as claimed in Claims 6 and 7, characterised in that an upper mass supporting the crank drive is connected to the running gear (116a) in a movable manner via a joint system (112, 114).
12. Stamping device as claimed in Claim 11, characterised in that the joint system consists of parallel guide bars (112, 114).
13. Stamping device as claimed in any one of the preceding Claims, characterised by a countermass (40: 40₁: 40a₂, 40b₂; 41, 43; 41₄, 43₄. 47; 59, 61) which can be driven by the engine at least over a large part of the range of movement of the working mass in the opposite direction to the movement of said working mass.
14. Stamping device as claimed in Claim 13, characterised in that the crank drive serves to drive the countermass (40: 40₁: 40a₂, 40b₂; 41, 43; 41₄, 43₄. 47; 59, 61).
15. Stamping device as claimed in any one of Claims 13 or 14, characterised in that the movement of the end (34) of the spring assembly connected to the crank drive and the movement of the countermass (40: 40₁: 40a₂, 40b₂; 41, 43; 41₄, 43₄. 47; 59, 61) are offset with respect to one another in relation to the crank angle by 180° minus a phase shift derived from the constructional parameters of the spring assembly.
16. Stamping device as claimed in any one of Claims 13 to 15, characterised in that the countermass (40: 40₁: 40a₂, 40b₂) is guided on the upper mass in parallel with the direction of movement of the working mass.
17. Stamping device as claimed in Claim 16, characterised in that the countermass is driven by a compensating eccentric (30; 30₁; 30a₂, 30b₂) on the crank drive.
18. Stamping device as claimed in Claim 17, characterised in that the compensating eccentric (30) drives the countermass (40) via a connecting rod (38).
19. Stamping device as claimed in Claim 17, characterised in that the connection between the countermass (40₁: 40a₂, 40b₂) and the compensating eccentric (30₁; 30a₂, 30b₂) is designed as a sliding crank.
20. Stamping device as claimed in any one of Claims 14 or 15, characterised in that the countermass consists of two partial masses (40a₂, 40b₂) each disposed on one side or the other of the crank drive at approximately the same height with respect to the axis of rotation of the crank drive, and each partial mass is driven by an eccentric pin (30a₂, 30b₁) on an eccentric disk (37,39) which is allocated thereto and is coupled to the crank drive in a rotatable manner, wherein the connection between the eccentric pin and the associated partial mass is designed as a sliding crank in each case.
21. Stamping device as claimed in any one of Claims 14 or 15, characterised in that the countermass consists of unbalanced masses (41, 43; 41₄, 43₄. 47; 59, 61) which are mounted on the upper mass so as to be rotatable about mutually parallel axes and are rotationally driven by the crank drive in opposite directions, wherein the inertia moment and the mutual phase position of the unbalanced masses are arranged such that they produce a vibration which is directed so as to counteract the working mass.
22. Stamping device as claimed in Claim 21, characterised in that the countermass consists of two centrifugal weights (41, 43) which are disposed next to each other in a symmetrical manner with respect to the direction of movement of the working mass at approximately the same height in this direction, are directly coupled to each other so as to be rotatable in opposite directions, and are driven by the crank drive.
23. Stamping device as claimed in Claim 21, characterised in that the countermass consists of a first centrifugal weight (47) which sits directly on the shaft of the crank drive and of two second centrifugal weights (41₄, 43₄) which have the same inertia moment, are disposed next to each other in a symmetrical manner with respect to the direction of movement of the working mass at approximately the same height in this direction, and are driven by the crank drive so as to be rotatable in the opposite direction to the first centrifugal weight (47), and wherein the inertia moment of each of the two second centrifugal weights is approximately half of the inertia moment of the first centrifugal weight (47).
24. Stamping device as claimed in Claim 21, characterised in that the counter mass consists of a first centrifugal weight (61) which sits directly on the axis of rotation of the crank drive and of a second centrifugal weight (59) which is disposed behind the first centrifugal weight, has approximately the same inertia moment as the first centrifugal weight (61), and is driven in the opposite direction to the first centrifugal weight (61) about an axis of rotation which is somewhat offset with respect to the axis of rotation of the crank drive in parallel with the direction of movement of the working mass.

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