EP2558649B1 - Arrangement for providing a pulsing compressive force - Google Patents

Description

TECHNICAL AREA

The invention relates to an arrangement for providing a pulsating compressive force, a soil compacting device comprising such an arrangement, a method for operating such an arrangement or such a soil compacting device and the use of such a device for soil compaction according to the preambles of the independent claims.

STATE OF TECHNOLOGY

In particular in the soil compaction compression devices are used, which work according to the so-called absorber principle. Here, a flat plate or a roller body (bandage), which forms the ground contact surface, excited by means of an unbalance exciter to vibrate. The plate or the roller body is connected via a spring-damper system with an absorber mass arranged above it, which is also excited via the spring-damper system to vibrate. If the absorber mass oscillates in phase with the same frequency (1: 1 resonance) or half the frequency (2: 1 resonance) of the plate or the roller body, this machine concept (absorber principle) results in a maximum soil compaction force, which significantly increases or even reduces the power Machines without absorber mass corresponds.

Due to the system, however, the problem arises in such soil compaction equipment that the vibration behavior of the plate or the roller body, which or which excites the absorber mass to vibrate, is influenced by the rigidity of the soil to be compacted, which may be locally different and also changes during compacting of the soil. In practice, this means that simpler devices with fixed excitation frequencies can seldom be operated at the optimum operating point (1: 1 or 2: 1 resonance) and thus can not exploit their performance potential. Also, prolonged operation in the sub-optimal range can result in premature wear or even destruction of the devices.

In technically more complex devices with controllable unbalance exciters, the desired resonance state can be produced by changing the excitation frequency in a wide range, so that at least the latter problem can be avoided. However, this results in the disadvantage that the exciter frequency required to produce the resonant state is often energetically sub-optimal, which in turn means that even these devices can not fully exploit their performance potential.

Out DE 10 2008 011 208 B3 a vibration plate for soil compaction is known in which the superstructure with the drive motor is substantially vibration coupled from the bottom plate. Such vibration plates react less sensitive to changing soil conditions with respect to their operating behavior, but also have a much lower maximum soil compaction force than equally heavy vibrating plates, which operate on the absorber principle.

PRESENTATION OF THE INVENTION

It is therefore the object to provide technical means available with which the previously described disadvantages of the prior art can be at least partially overcome.

This object is solved by the subject matter of claim 1.

Accordingly, a first aspect of the invention relates to an arrangement for providing a pulsating Compressive force. The arrangement comprises an exciter part with an unbalance exciter for generating an intermittent excitation force and with a contact surface for transmitting a perpendicular to the contact surface force component of the excitation force as a pulsating pressure force on a tool or on a force to be acted upon by the pressure working surface. Furthermore, the arrangement comprises a Tilgerteil, which is connected to the exciter part via a spring-damper unit, for forming a oscillatory system excitable by the unbalance exciter to resonant oscillations.

According to the invention, the arrangement is such that the spring stiffness (also called the spring constant) of the spring-damper unit, the damping of the spring-damper unit, the spring preload of the spring-damper unit, the mass of the absorber part, at the spring Damper unit becoming effective mass moment of inertia of Tilgerteils, the mass of the excitation part and / or acting on the spring-damper unit mass moment of inertia of the excitation part is changed in operation or are.

This makes it possible to keep the oscillatory system formed of excitation part, spring-damper unit and Tilgerteil at a given excitation frequency for different coupling stiffness of the contact surface to a tool or a work surface in resonance and thus an energetically optimal operation with a maximum at the To provide contact surface provided pulsating pressure force at different or changing conditions of use. Accordingly, with the arrangement according to the invention, it becomes possible for the first time to provide functioning soil compaction equipment according to the absorber principle, which can always be operated at optimum operating point for different soil types and progressive compaction, with corresponding advantages in terms of compaction performance and durability of the equipment.

Preferably, the unbalance exciter of the inventive arrangement is designed as a directional oscillator or as a circular oscillator. Depending on the intended use, one or the other alternative may be more advantageous. So it is for example in the event that with the arrangement of a vibrating plate is to be formed for soil compaction, advantageous if the unbalance exciter is designed as a directional oscillator, because so By tilting the direction of vibration relative to the vertical at the same time the drive of the vibrating plate can be realized. If, however, a compactor with a separate drive to be formed with the arrangement, it is preferable to perform the unbalance exciter as a simple circular oscillator, since such unbalance exciters are structurally simple to implement and are correspondingly robust and inexpensive.

In a preferred embodiment, the arrangement is designed such that the Tilgerteil the arrangement during normal operation in the direction of gravity exclusively on the exciter part is supported by the spring-damper unit. Preferably, the Tilgerteil this is arranged over the exciter part, so that there is a simple structure. Such embodiments of the arrangement are preferably used for the formation of vibrating plates for soil compaction, in which the entire device unit is supported exclusively on the bottom plate on the ground.

In another preferred embodiment, the arrangement is designed such that the Tilgerteil part of the intended operation is partially supported by the spring-damper unit on the exciter part and partly on support means, which are formed separately from the excitation part. In this way, the Tilgerteil performs the intended operation, an intermittent tilting oscillation about a tilt axis in the region of the vibration moderately decoupled from the exciter part support means around. In such an embodiment, the mass moment of inertia of the absorber part that becomes effective on the spring-damper unit and the spring preload of the spring-damper unit can be changed in a simple manner and thus influence the oscillation behavior of the arrangement by the weight distribution between that of the exciter part to be carried weight fraction of the absorber part and that of the support means to be carried weight fraction of the absorber part is changed. This can be done for example by moving a weight on the absorber part and is possible with simple means, such as a motor spindle, even during operation.

In yet a further preferred embodiment, the arrangement comprises a rest part, which is connected to the excitation part or the absorber part, such that it forms a coherent unit with this part, but is substantially decoupled from it in terms of vibration. This results in the advantage that the arrangement has a partial area which is exposed during operation only relatively low accelerations and is therefore suitable as a mechanical interface to the operator and as an installation location for any control components.

It is provided in a first preferred variant of this embodiment that the rest part is fully worn during normal operation as intended by the exciter part or by the Tilgerteil. For example, if the inventive arrangement is designed as a hand-held vibrating plate for soil compaction, the guide shaft of the vibrating plate, which also carries the controls, such a rest part by being mounted with a vibration isolating bearing assembly on Tilgerteil or on the exciter part and is supported by this.

In a second preferred variant of this embodiment, the rest part is worn during intended operation completely by support means, which are substantially decoupled from the excitation part and the absorber part in terms of vibration. Thus, it is provided, for example, the inventive arrangement as a soil compaction device consisting of a soil compaction attachment and an associated wheel loader or excavator, which in the normal operation exclusively the leadership and the drive of the arrangement in horizontal direction but takes over in the vertical direction, the arrangement neither supports nor exerts a force on them to train. The soil compacting attachment can be designed as a vibrating plate or as a vibration-excited roller body.

In a third preferred variant of this embodiment, it is provided that the rest part is partially carried by the exciter part or the absorber part during normal operation and partly by suspension elements which are substantially decoupled from the excitation part and the absorber part in terms of vibration. If, for example, the arrangement according to the invention is designed as a compactor for compacting the soil, the drive unit with the driver's cab forms such a resting part by supporting itself on one end with vibration-isolating bearings on the exciter part designed as a roller body or on the absorber part and on the other end via drive wheels the floor.

It is in this third preferred embodiment of advantage that the arrangement is designed such that in operation, a change in the weight distribution between the exciter part or the absorber part to be supported weight portion of the rest portion and the weight of the rest part to be supported by the support means possible is, preferably by shifting a weight on the rest part. As a result, it is easy to influence the vibration behavior of the arrangement.

Further, it is preferred in embodiments of the inventive arrangement with rest part, that the arrangement is designed such that a change in the mass of the absorber part, the moment of inertia of the absorber part, the mass of the excitation part and / or the moment of inertia of the excitation part is possible in that a or a plurality of liquid volumes between the rest portion and the excitation part and / or the absorber part is or will be replaced. In this way can be influenced in many areas on the vibration behavior of the arrangement. Likewise, it is also conceivable to change the mass moment of inertia of the exciter part and / or of the absorber part in that one or more liquid volumes are respectively displaced within the excitation part and / or inside the absorber part.

If the arrangement according to the invention is designed such that a change in the mass of the absorber part, the mass moment of inertia of the absorber part, the mass of the excitation part and / or the mass moment of inertia of the exciter part is possible because one or more liquid volumes are exchanged between the absorber part and the exciter part , which is preferred, it can be influenced in many areas without the presence of a rest part on the vibration behavior of the arrangement.

In a further preferred embodiment, the arrangement according to the invention is designed such that the absorber part and / or the excitation part has at least two masses which are movable against one another when the absorber part or excitation part is accelerated in a direction perpendicular to the contact surface, wherein the spring force is changeable during operation. As a result, at a constant mass of the absorber or excitation part in a simple manner, the mass moment of inertia of the absorber part or of the exciter part, which is effective on the spring-damper system, can be changed.

In yet another preferred embodiment, the inventive arrangement is designed such that a change in the spring stiffness of the spring-damper unit by stiffening of spring elements of the spring-damper unit and / or by changing the application of force in spring elements of the spring-damper unit possible is. In the former case, it is for example intended to use elastomeric hollow springs whose spring stiffness by applying their Interior can be changed with a pressurized fluid via a change in the fluid pressure. In the latter case, the change of the force is preferably carried out by changing a translation of the introduced forces, eg by means of length-variable toggle.

If the arrangement according to the invention is designed in such a way that the frequency of the excitation force, the magnitude of the excitation force and / or the effective direction of the excitation force of the unbalance exciter can be changed during operation, which is likewise preferred, the advantage arises that the arrangement has a maximum Has flexibility to adapt to different or changing operating conditions.

Further, it is preferred that the arrangement comprises a particular electronic control unit, with which the spring stiffness of the spring-damper unit, the damping of the spring-damper unit, the spring bias of the spring-damper unit, the mass of Tilgerteils, the mass moment of inertia of Tilgerteils, the mass of the excitation part and / or the moment of inertia of the excitation part in operation is automatically adjustable depending on measured system variables or are, preferably such that the Tilgerteil resonates with the exciter part, advantageously with the same Frequency or at half the frequency of the excitation part.

If the arrangement according to the invention is designed in such a way that the frequency of the excitation force, the magnitude of the excitation force and / or the effective direction of the excitation force of the unbalance exciter can be changed during operation, which is preferred, then it is advantageous that the control In addition, the frequency of the excitation force, the magnitude of the excitation force and / or the effective direction of the excitation force of the unbalance exciter in operation automatically adjustable in dependence on measured system variables or control unit is or are, preferably, such that the Tilgerteil resonates with the exciter part, advantageously with the same frequency or with half the frequency of the excitation part.

Such arrangements according to the invention make it possible to provide soil compaction devices which automatically always operate at the optimum operating point.

A second aspect of the invention relates to a soil compaction device with an arrangement according to the first aspect of the invention, in which the claimed contact surface of the arrangement serves as a tool for compaction of the soil during normal operation. In such devices, the advantages of the invention are particularly evident.

In a preferred embodiment, the soil compaction device is a vibrating plate or a roller, in particular a roller with one or two vibratory roller bodies (bandages) arranged one behind the other in the unwinding direction.

A third aspect relates to a method of operating the arrangement according to the first aspect of the invention or the soil compacting device according to the second aspect of the invention. According to the method, the arrangement is intended with the contact surface in contact with a work performing tool or a work surface to be processed, preferably to be compacted, such as e.g. a floor area to be compacted.

Here, the spring stiffness (also called spring constant) of the spring-damper unit, the damping of the spring-damper unit, the spring preload of the spring-damper unit, the mass of the absorber part, the moment of inertia of the absorber part, the mass of the excitation part and / or the mass moment of inertia of the exciter part changed, so that the vibration behavior of the oscillatory system formed by exciter part, spring-damper unit and Tilgerteil changed. In this way it is possible to optimize the arrangement or the soil compaction device for a wide variety of applications or operating situations.

In a preferred embodiment of the method, the frequency of the excitation force, the magnitude of the excitation force and / or the effective direction of the excitation force of the unbalance exciter is additionally changed during normal operation, whereby an even better adaptation of the arrangement or soil compaction device to a variety of operating conditions is possible.

Preferably, in the inventive method, the spring stiffness of the spring-damper unit, the damping of the spring-damper unit, the spring preload of the spring-damper unit, the mass of the Tilgerteils, the moment of inertia of the absorber part, the mass of the excitation part and / or the mass moment of inertia of the exciter part, and / or, where applicable, the frequency of the excitation force, the magnitude of the excitation force and / or the effective direction of the excitation force of the unbalance exciter changed such that the absorber part resonates with the exciter part, preferably with the same frequency or with half the frequency of the excitation part. As a result, a pulsating pressure force of maximum size can be made available at the contact surface of the arrangement according to the invention.

In a further preferred embodiment of the method, during the intended operation of the arrangement, system parameters of the system excited by the unbalance exciter to form oscillations formed from excitation part, spring-damper unit and Tilgerteil, in particular the accelerations of the exciter part and / or the absorber part in the direction perpendicular to Contact surface and the rotational frequency of the unbalance exciter. Changing the spring stiffness of the spring-damper unit, the damping of the spring-damper unit, the spring preload the spring-damper unit, the mass of the absorber part, the mass moment of inertia of the absorber part, the mass of the exciter part and / or the moment of inertia of the exciter part, and / or, where applicable, the frequency of the excitation force, the size of the excitation force and / or The effective direction of the excitation force of the unbalance exciter takes place as a function of one or more of the determined system parameters. In this way, a specific vibration behavior of the oscillatory system formed from exciter part, spring-damper unit and Tilgerteil can be set specifically.

Preferably, in the inventive method, the changing of the spring stiffness of the spring-damper unit, the damping of the spring-damper unit, the spring preload of the spring-damper unit, the mass of the absorber part, the moment of inertia of the absorber part, the mass of the exciter part and / or the mass moment of inertia of the exciter part and / or, where applicable, the frequency of the excitation force, the magnitude of the excitation force and / or the effective direction of the excitation force of the unbalance exciter and, where applicable, the determination of the system parameters automatically via a particular electronic control unit. This makes it possible to design the arrangement or the soil compaction device in such a way that it automatically adapts to the operating situation encountered during normal operation, for example, always adjusted in such a way that the absorber part resonates with the exciter part, with the highest possible exciter frequency.

A fourth aspect of the invention relates to the use of the arrangement according to the first aspect of the invention for soil compaction. In such use, the advantages of the invention are particularly evident.

SHORT DESCRIPTION THE DRAWINGS

• Fig. 1 eine Seitenansicht einer ersten erfindungsgemässen Vibrationsplatte zur Bodenverdichtung;
• Fig. 2 das schwingungstechnische Modell des schwingfähigen Systems der Vibrationsplatte aus Fig. 1;
• die Figuren 3a bis 3c Schnitte durch eine Elastomer-Hohlfeder des schwingfähigen Systems der Vibrationsplatte aus Fig. 1 bei verschiedenen Hohlraum-Innendrücken;
• Fig. 4 eine Seitenansicht einer zweiten erfindungsgemässen Vibrationsplatte zur Bodenverdichtung;
• Fig. 5 das schwingungstechnische Modell des schwingfähigen Systems der Vibrationsplatte aus Fig. 4;
• Fig. 6 eine Seitenansicht eines ersten erfindungsgemässen Walzenzugs zur Bodenverdichtung;
• Fig. 7 das schwingungstechnische Modell des schwingfähigen Systems des Walzenzugs aus Fig. 6;
• Fig. 8 eine Seitenansicht eines zweiten erfindungsgemässen Walzenzugs zur Bodenverdichtung;
• Fig. 9 eine Seitenansicht eines dritten erfindungsgemässen Walzenzugs zur Bodenverdichtung;
• Fig. 10 eine schematische Darstellung eines Feder-Dämpfer-Systems mit verstellbarer Federsteifigkeit; und
• Fig. 11 einen Schnitt durch einen Tilgerteil mit verstellbarem Massenträgheitsmoment.

Further embodiments, advantages and applications of the invention will become apparent from the dependent claims and from the following description with reference to FIGS. Showing:

• Fig. 1 a side view of a first inventive vibrating plate for soil compaction;
• Fig. 2 the vibrational model of the oscillatory system of the vibrating plate Fig. 1 ;
• the FIGS. 3a to 3c Cut through an elastomeric hollow spring of the vibratory system of the vibrating plate Fig. 1 at various cavity internal pressures;
• Fig. 4 a side view of a second inventive vibrating plate for soil compaction;
• Fig. 5 the vibrational model of the oscillatory system of the vibrating plate Fig. 4 ;
• Fig. 6 a side view of a first inventive compactor for soil compaction;
• Fig. 7 the vibrational model of the oscillatory system of the pulley Fig. 6 ;
• Fig. 8 a side view of a second inventive roller compactor for soil compaction;
• Fig. 9 a side view of a third inventive roller compactor for soil compaction;
• Fig. 10 a schematic representation of a spring-damper system with adjustable spring stiffness; and
• Fig. 11 a section through a Tilgerteil with adjustable mass moment of inertia.

WAYS TO PERFORM THE EARNING

Fig. 1 shows a first inventive, designed as a vibrating plate soil compacting device in side view. Fig. 2 schematically shows the vibrational model of the oscillatory system of this vibrating plate.

As can be seen, the vibrating plate on an undercarriage 1 (demanding Erregerteil) and a superstructure 5 (claims Tilgerteil) on.

The undercarriage 1 comprises a ground contact plate 13, which has on its underside a contact surface 3 for the initiation of the vibrating plate generated by the pulsating pressure force in the bottom 4 to be compacted, and designed as a directional vibrator unbalance exciter 2 with a hydraulic motor, which is a substantially vertically directed generates intermittent excitation force, which is introduced into the ground contact plate 13.

The uppercarriage 5 comprises a drive unit 14 with a diesel engine which drives a hydraulic pump and an air compressor. The hydraulic pump supplies via hydraulic hoses the hydraulic motor of the unbalance exciter 2 with a stream of pressurized hydraulic fluid, for driving the unbalance exciter 2. The chassis of the superstructure 5 is weighted dimensioned such that together with the drive unit 14 results in a certain total mass of the superstructure as absorber mass ,

The superstructure 5 is supported in the direction of gravity via four in their spring stiffness and their damping behavior changeable elastomeric hollow springs 15 (claimed spring-damper unit) on the undercarriage 1 from. Another support of the superstructure 5 in the direction of gravity does not exist.

In the vibration control model according to Fig. 2 the elastomeric hollow springs 15 are represented by the spring 15a with the spring stiffness k2 and the damper 15b with the damping d2. The mass of the superstructure 5 is designated m2g and that of the undercarriage 1 m1g, the movements of the upper and lower carriage in the vertical direction x2 and x1. The spring stiffness of the bottom 4 is denoted by k1 and its damping by d1. Next is in Fig. 2 the rotational frequency of the unbalance exciter 2 with Ω1 and its excitation force denoted by F1.

The structure of the elastomeric hollow springs 15 is from the FIGS. 3a to 3c It can be seen which sections through one of the elastomeric hollow springs 15 at an overpressure in the interior 16 of 0 bar ( Fig. 3a ), from 2 bar ( Fig. 3b ) and 4 bar ( Fig. 3c ) demonstrate. As can be seen, the elastomeric body 17 of the elastomeric hollow spring 15 increasingly stretches in the axial direction (loading direction) with increasing pressure in the interior 16 and bulges progressively in the radial direction. It increases with increasing pressure in the interior 16, the stiffness of the elastomeric hollow spring 15.

At the in Fig. 1 shown vibration plate, the interiors 16 of the elastomeric spring elements 15 are connected via lines and control valves to the air compressor of the drive unit 14 and can be targeted so with an overpressure between 0 bar and 6 bar, to change the spring stiffness of the elastomeric spring elements 15th

Attached to the superstructure 5 by means of vibration-isolating fastening elements 8 is a guide tongue 9 (demanding rest part) which carries the operating elements and serves to guide the vibration plate by an operator. The vibration-isolating fasteners 8 are designed such that the guide tongue 9 forms a coherent unit with the superstructure 5, but is substantially decoupled from this vibrationally.

Furthermore, the vibration plate comprises an electronic control unit, by means of which in operation the accelerations of the undercarriage 1 and the undercarriage 1 in the vertical direction, ie perpendicular to the contact surface 3, as well as the rotational frequency Ω1 of the unbalance exciter 2 can be determined and in dependence thereon determined system parameters, the rigidity and damping of the elastomeric spring elements 15 by Change in the pressure in the interior 16 can be changed automatically such that the superstructure 5 always resonates with the undercarriage 1. In addition, the control or regulation unit automatically regulate the rotational frequency of the unbalance exciter 2 during operation in such a way that a maximum compaction power is achieved.

Fig. 4 shows a second invention, designed as a vibrating plate soil compaction device in side view and Fig. 5 schematically the vibration model of the oscillatory system of this second vibrating plate.

As can be seen, this vibrating plate, apart from a few details, has the same structure as the first vibrating plate in accordance with FIGS Figures 1 and 2 , An essential difference, however, is that in the vibrating plate shown here, the superstructure 5 is supported on the stiffness not changeable elastomer springs 18 on the undercarriage 1. In the vibration control model according to Fig. 5 the elastomer springs 18 are represented by the spring 18a with the spring stiffness k2 and the damper 18b with the damping d2.

Another essential difference is that in this case the masses m1g, m2g of the undercarriage 1 and the uppercarriage 5 can be selectively changed during operation by exchanging liquid between the upper 5 and the lowercarriage 1 via a connecting hose 12. For this purpose, ballast tanks designed as piston accumulators are provided both in the undercarriage 1 and in the superstructure 5, the volume of which can be selectively and oppositely changed by means of hydraulic drives and an associated control or regulation unit.

In the present case, the electronic control unit is also designed such that in operation, the accelerations of the upper carriage 5 and the lower carriage 1 in the vertical direction, ie perpendicular to the contact surface 3, as well as the rotational frequency Ω1 of the unbalance exciter can determine. In contrast to the control unit of the vibration plate according to the Figures 1 and 2 In this case, however, the control or regulation unit changes the masses m1g, m2g of the undercarriage 1 and the uppercarriage 5 automatically in operation as a function of these determined system parameters in such a way that the uppercarriage 5 resonates with the undercarriage 1.

Fig. 6 shows a first embodiment of a trained as a compactor invention soil compaction device in side view and Fig. 7 schematically the vibrational model of the oscillatory system of this compactor.

As can be seen, the compactor comprises a front part 19 and a rear part 20, which are connected to one another via an articulated joint 21.

The front part 19 of the roller compactor consists essentially of a roller body 23 (demanding Erregerteil) and a chassis frame 25 (claim damper Tilgerteil).

The roller body 23 comprises a bandage 11, which has the contact surface 3 for the initiation of the generated pulsating pressure force in the bottom 4 to be compacted, and formed as a circular vibrator unbalance exciter 2 with a hydraulic motor which generates a respect to their direction of action intermittent excitation force in the Bandage 11 is initiated.

The chassis frame 25 is supported in the direction of gravity via two spring-damper assemblies 22 (claimed spring-damper unit) with fixed stiffness and damping on the two end-side bearings of the roller body 23 and is connected via vibration-isolating fasteners 8 with the articulated joint 21 which is carried by the rear part 20 of the compactor. The vibration isolating fasteners 8 are designed such that the rear part 20 of the compactor with the chassis frame 25 forms a coherent unit, but is vibrationally decoupled substantially from this and thus represents a claim according Ruheteil.

The rear part 20 of the roller compactor consists essentially of a drive unit 14 with a diesel engine, which drives a hydraulic pump, and a driver's cab 6. It is supported by two drive wheels 10 driven by hydraulic motors on the floor 4. In operation, the hydraulic pump supplies the hydraulic motor of the unbalance exciter 2 of the roller body 23 via hydraulic hoses and the hydraulic motors of the drive wheels 10 each with a flow of pressurized hydraulic fluid for driving the drive wheels 10 and the unbalance exciter 2 of the roller body 23.

In the rear part 20 and in the chassis frame 25 of the front part 19 of the drum liquid tanks are arranged, between which liquid can be exchanged via a hose 7. This makes it possible to change the mass m2g of the chassis frame 25 during operation.

Depending on the weight distribution, the chassis frame 25 is additionally supported via the articulated joint 21 on the rear part 20 of the compactor, or the rear part 20 is additionally supported on the chassis frame 25 via the articulated joint 21.

In the vibration control model according to Fig. 7 For example, spring-damper assemblies 22 are represented by spring 22a having spring stiffness k2 and damper 22b having damping d2. The mass of the chassis frame 25 is designated by m2g and that of the roller body 23 by m1g. The movement of the chassis frame 25 is indicated by x2 and that of the roller body 23 by x1. The spring stiffness of the bottom 4 is denoted by k1 and its damping by d1. Moreover, in Fig. 7 the rotational frequency of the unbalance exciter 2 with Ω1 and its excitation force denoted by F1.

Next, the compactor is equipped with an electronic control unit, which makes it possible to determine during operation, the accelerations of the chassis frame 25 and the roller body 23 in the vertical direction and the rotational frequency Ω1 of the unbalance exciter and in dependence on these determined system parameters Mass m2g of the chassis frame 25 automatically adjust such that the chassis frame 25 always resonates with the roller body 23.

Fig. 8 shows a second embodiment of a trained as a compactor invention soil compaction device in side view.

This second compactor is different from the one in Fig. 6 shown only by the fact that the rear part 20 of the roller is formed by a wheel loader which is completely supported on four drive wheels 10a, 10b of two successively arranged axes and is so connected to the chassis frame 25, that he only in normal operation in the horizontal direction and drives, but does not absorb any forces acting in the vertical direction of this or transmits to this. Again, the rear part 20 is vibrationally decoupled from the chassis frame 25 and of the roller body 23 of the front part 19 of the drum and thus forms a claimed rest part.

Fig. 9 shows a third embodiment of a trained as a compactor according to the invention Bodenverdichtungsvorrichtung in side view. This is an unmanned compactor, which is operated via a radio remote control.

As can be seen, this third compactor comprises a roller body 23 (damper energizing part) and a chassis frame 25 (damper damper part), which in the direction of gravity at one end via two spring-damper assemblies 22 (spring-damper assembly according to claim) with constant rigidity and damping on the two end-side bearings of the roller body 23 is supported and at its other end on two driven by hydraulic motors drive wheels 10th

The roller body 23 comprises a bandage 11, which has the contact surface 3 for the initiation of the generated pulsating pressure force in the bottom 4 to be compacted, and formed as a circular vibrator unbalance exciter 2 with a hydraulic motor which generates a respect to their direction of action intermittent excitation force in the Bandage 11 is initiated.

The chassis frame 25 carries in the area in which it is supported on the drive wheels 10, a drive unit 14 with a diesel engine, which drives a hydraulic pump. In operation, the hydraulic pump supplies the hydraulic motor of the unbalance exciter 2 of the roller body 23 via hydraulic hoses and the hydraulic motors of the drive wheels 10 each with a flow of pressurized hydraulic fluid for driving the drive wheels 10 and the unbalance exciter 2 of the roller body 23.

In the area between the drive unit 14 and the roller body 23, the chassis frame 25 carries a trim weight 26 which can be displaced in operation in the longitudinal direction L by means of a hydraulic motor and a threaded spindle. As a result, the mass moment of inertia of the chassis frame 25 which becomes active on the spring-damper arrangements 22 and which during operation performs a tilting oscillation around an axis of rotation in the area of the contact surfaces of the drive wheels 10 can be changed and the supporting load of the spring-damper arrangements 22 , whereby the spring bias changes.

Also, this third compactor is equipped with an electronic control unit, which makes it possible, in operation, the accelerations of the chassis frame 25 and the roller body 23 in vertical direction and the rotational frequency Ω1 of the unbalance exciter to determine and, depending on these determined system parameters, the mass m2g of the chassis frame 25 automatically such that the chassis frame 25 always resonates with the roller body 23.

Fig. 10 shows in a conceptual representation of a spring-damper assembly 31, the spring stiffness can be changed by changing the application of force in the spring-damper unit. As can be seen, the spring-damper unit of this arrangement 31 is formed by two polymer spring elements 18, which are attached at one end tilted relative to the intended loading direction B to a first connection plate 27. At its other end, the polymer spring elements 18 are pivotally attached to spindle nuts 28, which can be moved towards or away from each other by means of an adjusting spindle 29 in a direction perpendicular to the loading direction B, so that the polymer spring elements 18 are inclined by a desired angle α with respect to the loading direction B. can be. The spindle nuts 28 are arranged in a guide 32 in a second connection plate 30, such that when the second connection plate 30 is loaded with a force acting in the intended loading direction B, this force is introduced into the polymer spring elements 18 and transmitted to the first connection plate 27. The greater the set angle of inclination α of the polymer spring elements 18 with respect to the intended loading direction B, the lower the spring stiffness of this spring-damper arrangement 31.

Fig. 11 shows a section through a Tilgerteil with variable moment of inertia. The absorber part comprises a base plate 33 and a cover 34, which together form a closed space 35. Arranged in this space 35 are two absorber weights 36 each having a constant mass, which via joint arrangements 37 and pneumatic spring elements 38 are connected to each other and to the base plate 33 in such a way that, when the absorber part is accelerated in and against the direction of gravity S, they are movable relative to one another against the spring force of the spring elements 38. The spring force of the spring elements 38 can be changed during operation by the pressure in the cylinder chambers via compressed air hoses (not shown) is changed. As a result, the mass moment of inertia of this absorber part can be changed in and against the direction of gravity.

While preferred embodiments of the invention are described in the present application, it should be clearly understood that the invention is not limited to these and may be practiced otherwise within the scope of the following claims.

Claims (24)

1. Arrangement for providing a pulsing compressive force, comprising

   a) an exciter part (1, 23) with an unbalance exciter (2) for producing an intermittent exciter force and with a contact surface (3) for transmitting a force component of the exciter force, directed perpendicularly to the contact surface, as a pulsing compressive force, to a tool or a work surface (4) to be impinged with the compressive force, and

   b) a vibration damper part (5, 25) which is connected to the exciter part (1, 23) by means of a spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), for forming a system capable of being excited to resonant oscillations by the unbalance exciter (2), characterized in that the arrangement is adapted to vary during operation the spring stiffness (k2) of the spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), the damping (d2) of the spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), the spring pre-load of the spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), the mass (m2) of the vibration damper part (5, 25), the mass moment of inertia of the vibration damper part (5, 25), the mass (m1) of the exciter part (1, 23), and/or the mass moment of inertia of the exciter part (1, 23).
2. Arrangement according to claim 1, characterized in that the unbalance exciter (2) is formed as directed vibrator or as circular vibrator, in order to generate an intermittent exciter force.
3. Arrangement according to one of the preceding claims, characterized in that the arrangement is formed in such a way that the vibration damper part (5, 25) is exclusively supported on the exciter part (1, 23) in the direction of gravity via the spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), when operated as intended.
4. Arrangement according to one of the claims 1 to 2, characterized in that the arrangement is formed in such a way that the vibration damper part (5, 25) is partially supported on the exciter part (1, 23) via the spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b) and on supporting means (8, 10) which are formed separately from the exciter part (1, 23), when operated as intended.
5. Arrangement according to one of the preceding claims, characterized in that the arrangement has an idle part (9, 20) which is connected to the exciter part (1, 23) or to the vibration damper part (5, 25) in such a way that it forms a contiguous unit with the exciter part (1, 23) or the vibration damper part (5, 25), but is however substantially decoupled from them in terms of oscillations.
6. Arrangement according to claim 5, characterized in that the idle part (9, 20) is supported entirely by the exciter part (1, 23) or by the vibration damper part (5, 25), when operated as intended.
7. Arrangement according to claim 5, characterized in that the idle part (9, 20) is supported entirely by supporting means (10a, 10b) which are substantially decoupled from the exciter part (1, 23) and the vibration damper part (5, 25) in terms of oscillations, when operated as intended.
8. Arrangement according to claim 5, characterized in that the idle part (9, 20) is supported partially by the exciter part (1, 23) or by the vibration damper part (5, 25), and partially by supporting means (10) which are substantially decoupled from the exciter part (1, 23) and the vibration damper part (5, 25) in terms of oscillations, when operated as intended.
9. Arrangement according to claim 8, characterized in that the arrangement is formed in such a way that in operation a variation of the weight distribution between the weight portion of the idle part (9, 20) which has to be supported by the exciter part (1, 23) or the vibration damper part (5, 25), and the weight portion of the idle part (9, 20) which has to be supported by the supporting means (10) is possible, particularly by shifting a weight on the idle part (9, 20).
10. Arrangement according to one of the claims 5 to 9, characterized in that the arrangement is formed in such a way that a variation of the mass (m2) of the vibration damper part (5, 25), the mass moment of inertia of the vibration damper part (5, 25), the mass (m1) of the exciter part (1, 23), and/or the mass moment of inertia of the exciter part (1, 23) is possible by exchanging one or more liquid volumes between the idle part (9, 20) and the exciter part (1, 23) and/or the vibration damper part (5, 25).
11. Arrangement according to one of the preceding claims, characterized in that the arrangement is formed in such a way that a variation of the mass (m2) of the vibration damper part (5, 25), the mass moment of inertia of the vibration damper part (5, 25), the mass (m1) of the exciter part (1, 23), and/or the mass moment of inertia of the exciter part (1, 23) is possible by exchanging one or more liquid volumes between the vibration damper part (5, 25) and the exciter part (1, 23).
12. Arrangement according to one of the preceding claims, characterized in that the vibration damper part (5, 25) and/or the exciter part (1, 23) has at least two masses which are movable towards one another when accelerating the vibration damper part (5, 25) or the exciter part (1, 23) respectively, in a direction perpendicular to the contact surface (3) against a spring force, wherein the spring force is variable in operation, for changing the mass moment of inertia of the vibration damper part (5, 25) or of the exciter part (1, 23) respectively.
13. Arrangement according to one of the preceding claims, characterized in that the arrangement is formed in such a way that a variation of the spring stiffness (k2) of the spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b) is possible by stiffening spring elements (6) of the spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b) and/or by varying the force introduction in spring elements (6) of the spring damper unit (15, 15a, 15b, 18a, 18b, 22, 22a, 22b), particularly by varying a transmission of the introduced forces.
14. Arrangement according to one of the preceding claims, characterized in that the arrangement is formed in such a way that the frequency (Ω1) of the exciter force (F1), the quantity of the exciter force (F1) and/or the direction of action of the exciter force (F1) of the unbalance exciter (2) are variable during operation.
15. Arrangement according to one of the preceding claims, characterized in that it comprises a controlling unit or regulating unit respectively, by means of which the spring stiffness (k2) of the spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), the damping (d2) of the spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), the spring pre-load of the spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), the mass (m2) of the vibration damper part (5, 25), the mass moment of inertia of the vibration damper part (5, 25), the mass (m1) of the exciter part (1, 23), and/or the mass moment of inertia of the exciter part (1, 23) is or are automatically adjustable in operation depending on measured system variables, particularly in such a way that the vibration damper part (5, 25) oscillates in resonance with the exciter part (1, 23), particularly with the same frequency or with half of the frequency of the exciter part (1, 23).
16. Arrangement according to claim 14 and 15, characterized in that additionally the frequency (Ω1) of the exciter force (F1), the quantity of the exciter force (F1) and/or the direction of action of the exciter force (F1) of the unbalance exciter (2) is or are automatically adjustable in operation depending on measured system variables, particularly in such a way that the vibration damper part (5, 25) oscillates in resonance with the exciter part (1, 23), particularly with the same frequency or with half of the frequency of the exciter part (1, 23), by means of the controlling unit or regulating unit respectively.
17. Soil compacting device, comprising an arrangement according to one of the preceding claims.
18. Soil compacting device according to claim 17, characterized in that it is a vibration plate or roller, particularly a roller with one or two vibration-excited drums (11).
19. Method for operating an arrangement or a soil compacting device according to one of the preceding claims, characterized by the steps of:

    a) operating as intended the arrangement with the contact surface (3) in contact with a tool performing an action or a work surface (4) to be processed, particularly to be compacted;

    b) varying the spring stiffness (k2) of the spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), the damping (d2) of the spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), the spring pre-load of the spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), the mass (m2) of the vibration damper part (5, 25), the mass moment of inertia of the vibration damper part (5, 25), the mass (m1) of the exciter part (1, 23), and/or the mass moment of inertia of the exciter part (1, 23) while operating the arrangement in the intended way.
20. Method according to claim 19, characterized in that the frequency (Ω1) of the exciter force (F1), the quantity of the exciter force (F1) and/or the direction of action of the exciter force (F1) of the unbalance exciter (2) is or are adjustable in operation of the arrangement as intended.
21. Method according to one of the claims 19 to 20, characterized in that the spring stiffness (k2) of the spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), the damping (d2) of the spring damper unit (15, 15a, 15b, 18a, 18b, 22, 22a, 22b), the spring pre-load of the spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), the mass (m2) of the vibration damper part (5, 25), the mass moment of inertia of the vibration damper part (5, 25), the mass (m1) of the exciter part (1, 23), and/or the mass moment of inertia of the exciter part (1, 23) and/or, where applicable, the frequency (Ω1) of the exciter force (F1), the quantity of the exciter force (F1) and/or the direction of action of the exciter force (F1) of the unbalance exciter (2) is or are adjustable in such a way that the vibration damper part (5, 25) oscillates in resonance with the exciter part (1, 23), particularly with the same frequency or with half of the frequency of the exciter part (1, 23).
22. Method according to one of the claims 19 to 21, characterized in that, during the operation as intended of the arrangement, system parameters of the system excited to oscillations by the unbalance exciter (2), formed by the exciter part (1, 23), the spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b) and the vibration damper part (5, 25) are determined, particularly the acceleration of the exciter part (1, 23) and/or of the vibration damper part (5, 25) in a direction perpendicular to the contact surface (3) as well as the rotation frequency (Ω1) of the unbalance exciter (2), and in that the variation of the spring stiffness (k2) of the spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), the damping (d2) of the spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), the spring pre-load of the spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), the mass (m2) of the vibration damper part (5, 25), the mass moment of inertia of the vibration damper part (5, 25), the mass (m1) of the exciter part (1, 23), and/or, where applicable, the frequency (Ω1) of the exciter force (F1), the quantity of the exciter force (F1) and/or the direction of action of the exciter force (F1) of the unbalance exciter (2) is carried out depending on one or more of the determined system parameters.
23. Method according to one of the claims 19 to 22, characterized in that the variation of the spring stiffness (k2) of the spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), the damping (d2) of the spring-damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), the spring pre-load of the spring damper unit (15, 15a, 15b, 18, 18a, 18b, 22, 22a, 22b), the mass (m2) of the vibration damper part (5, 25), the mass moment of inertia of the vibration damper part (5, 25), the mass (m1) of the exciter part (1, 23) and/or the mass moment of inertia of the exciter part (1, 23) and/or, where applicable, the frequency (Ω1) of the exciter force (F1), the quantity of the exciter force (F1) and/or the direction of action of the exciter force (F1) of the unbalance exciter (2) is carried out automatically by means of a controlling unit or regulating unit respectively.
24. Use of the arrangement according to one of the claims 1 to 16 for compacting soil.

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