HK1002435B

HK1002435B - Roadworking machine

Info

Publication number: HK1002435B
Application number: HK98101386.3A
Authority: HK
Inventors: Hahn Gunter; Simons Dieter; Busley Peter
Original assignee: Wirtgen Gmbh
Priority date: 1995-02-12
Filing date: 1996-02-09
Publication date: 1998-08-21

Description

The invention relates to a self-propelled roadwork machine, as defined in claim 1.

Such construction machinery is needed for material processing, e.g. stabilizing unsound floors, pulverizing hard asphalt to recycling of bound or unbound road surfaces.

The most common construction machines have a work roller which circulates in a work chamber and is usually adjustable in height and inclination to suit the surface to be worked.

This workspace is where the necessary processes take place, adapted to the application, such as the removal and crushing of the abrasive material, the addition of binders, the mixing and distribution of added materials, etc.

The process of the invention is also divided into a counter-rotation or a direct rotation process, depending on whether the rolling force, at the same rotation, counters or supports the driving force of the machine.

The work machines described above for road renewal have a work roller which is driven either one way or both ways, requiring very high power drives depending on the application at the selected roll speed.

The position of the roll axis relative to the axis of the chassis is quite different in the known machines. Extensive studies have shown that the position of the roll axis relative to the axis of the chassis is of particular importance for the roll behaviour. The working machines, which are usually equipped with two chassis axes, require the roll to be designed in such a way that the rolls bear considerable geometrical and compressive forces, which are determined by the maximum height of the whole machine during operation.

The distance required for safety reasons for the machines in question is problematic in that it increases the height of the machine, which is particularly detrimental to the transport of the machine.

The working process requires, depending on the nature of the surface to be worked, adjustment of the rolling axis in relation to the working depth, i.e. the relative vertical distance of the rolling axis from the surface to be worked and the absolute transverse inclination of the rolling axis.

The methods and devices currently known for the described work process have one or more of the following disadvantages, depending on the form of implementation:

The solutions for the working roller drive are characterized by an unfavourable efficiency with corresponding energy losses due to their hydraulic, hydraulic mechanical or indirect mechanical concepts.

The advantageous work area increase with increasing working depth is achieved in some embodiments of work equipment, but at the expense of the advantageous axis of the rolling axis relative to the axes of the chassis; this also applies to embodiments where the axis of the rolling axis is between the axes of the chassis, but the weight distribution (back or front axis) is so unfavourable that the above-described advantage of using the machine weight for the rotor's compressive forces cannot be used for the counter-rotation and parallel work process.

The advantages of a fixed arrangement are realized only in the case of known machines with the non-adjustable work chamber. Only with a fixed arrangement of the rolling casing are so-called crusher bars realized, since the shredding of material usually produces forces that are advantageously introduced into the machine frame. Adjustable crusher bars, i.e. devices in which the distance between the crusher bar and the working roller can be changed during operation, have not yet been realized.

The positioning of the stand is not satisfactorily solved in the case of familiar work equipment: either the overall machine is not visible when the stand is not in the centre or the height of the carrier, especially in the case of a cab, is so high that disassembly of components is necessary for transport from one site to another.

The measurement of the working depth is carried out on the machines known to date by means of the relative position between the rotor axis and the chassis axis. This means that the large-volume tyres frequently used on this type of machine inevitably lead to measurement and display errors for the working depth due to their spring action.

The high resistance of the material to be worked, for example, causes damage to the holders or other components fixed to the workpiece when a cutting tool breaks, which then causes significant disruption and interruption of work due to the necessary repairs.

This state of the art is evident, for example, in the US patents 5,259,692, 5,190,398 and 5,354,147.

The purpose of the invention, based on a generic state of the art as described in US Patent No. 5.259.692, is to create a road-repair machine of the type described at the outset which makes optimum use of the weight of the machine in both parallel and reverse operation.

The characteristics of claim 1 are used to solve this problem.

The invention provides in an advantageous way that a drive unit containing the drive motor is stored in a swinging frame and forms a rotatable component relative to the machine frame, that the working roller is also stored in the rotatable component and together with the component is rotatable relative to the hood fixed to the machine frame, and that the working roller is directly loaded by the weight of the component, with almost all the weight of the machine concentrated between the chassis axes and transferred to the rotatable component.

The position of the drive unit on the pivoting unit increases the direct load on the workpiece and the mass inertial resistance of the unit; the weight, which is otherwise relatively evenly distributed between the axes of the chassis, is thus concentrated on the pivoting unit placed in the middle between the axes of the chassis, resulting in a low-level centre of gravity equally advantageous for the counter- or parallel-working process.

The adjustability of the working roller in combination with the rotating unit makes it possible to increase the size of the working space, e.g. with increasing working depth. Depending on the set working depth, different quantities of material are required to be mixed in the work space. The greater the pre-selected working depth, the higher the amount of material to be processed.

The drive unit stored in the crankshaft has an internal combustion engine to generate the drive power for the working roller and the chassis. The combustion engine generates the overall drive power necessary for the operation of the machine, in particular the drive power for the working roller but also the drive power for the chassis. To this end, the drive unit can drive several hydropumps, with the hydraulic pressure of which hydromotors in the wheels of the chassis can be driven separately.

Preferably, the vertical reaction force of the cutting forces on the working roller shall be applied to the rotary unit in the continuous operation process by a lever arm equal to or smaller than the lever arm which acts on the rotary unit by the force of gravity, thus enabling the working roller to be operated with the maximum possible upward pressure.

In particular, it may be provided that the vertical plane of the resulting force of gravity corresponds essentially to the vertical plane of the resulting force of reaction on the shear forces of the cutting tools involved in the process of continuous rolling.

The rolling axis is in a vertical plane, which is at a horizontal distance from the common vertical plane of the resulting gravitational force and the resulting shear forces.

The invention is based on the integration of storage and gear into the working roller, which results in the zero side described at the beginning of the present invention, which allows the working roller to reach the track on one side of the machine, so that work can be done along a given line.

The low loss transmission of the propulsion energy of the combustion engine is achieved by minimizing the number of propulsion components and by arranging the components with direct force flow, adapted to the spatial constraints of the unit.

The invention provides for the adjustability of the working speed of the roller, for example by fixed transition rates of a mechanical gear, by several adjustable transition rates of a belt drive or by a combination thereof.

The invention also allows the positioning of the rolling axis between the chassis axes in such a way that the weight of the machine frame and the weight of the workpiece can be used optimally for the required forces of action. The fixed connection of the hood to the machine frame allows the introduction of reaction forces from the cutting process directly into the machine frames, for example by a fixed arrangement of a rotating rotating rotor coil parallel to the rolling axis at the port. A particularly advantageous functional design or integration of the rotor coil with the port is particularly realistic in the case of the most difficult material handling.

The positioning of the workstation is essential for the achievement of optimal work results. The invention is to place the workstation directly above the workstation, i.e. largely in the middle of the machine, giving the driver's machine overview for the counter-clockwise and parallel work process. The principle of integration of the workstation into the machines according to the invention allows the necessary space (machinery space) to be kept in such a position that, despite the cross-clockwise position, a minimum transport height is possible without dismantling the components.

In the case of the unit containing the working roller, the transverse adjustments of the working roller necessary for the working process with the components for adjusting the height of the machine frame are possible, for example by means of column guides or parallelogram guides.

The apparatus is designed to be used for measuring the working depth of the machine by measuring the working depth relative to the surface to be worked, for both sides of the machine. This can be done by means of non-contact measuring systems, such as an ultrasonic sensor placed side by side with the roll axis or several ultrasonic sensors placed side by side with the machine frame as distance sensors. Other non-contact or also contact measuring systems can be used instead of ultrasonic sensors.

The working roller of the machine according to the invention is equipped with cutting tools. The connection of the cutting tool to the working roller is made according to the invention with the help of tool holders. The connection of the tool holder to the working roller is preferably made as a dissolvable connection. A particularly advantageous, easily interchangeable design is a tool holder that is fixed to the working roller body by means of clamping screws.

Further features and advantages of the invention are shown by the following example of an embodiment of a machine according to the invention.

The drawings show: Figure 1 a schematic side view of the machine according to the invention,Figure 2 a schematic side view of the rotating unit,Figure 3 the working roller in the working space bounded by the hood,Figure 4 a schematic longitudinal section of the working roller,Figure 5 the machine in parallel operation, andFigure 6 the machine in reverse operation.

Fig. 1 shows the roadwork machine with a machine frame 1 supported by two chassis and a wheelbase consisting of a driver's cab 23. The driver's cab 23 is transversely moveable in the direction of travel on the machine frame. The lateral hydraulic displacement of the wheelbase meets the requirements for overview when driving forward, whether in working use or when transferring at high speed. The wheelbase can also be rotated 180° for reverse travel, with a reversal of the steering wheel axis 4 also possible. The driver's cab consists of a lower part 22 and an upper part 24 which can be rotated 180° for transport, thus reducing the height of the machine for transport.

The chassis has two axles 4 at the front and rear of the frame 1 which can be steered together or separately, each wheel being equipped with its own hydraulic drive in the form of a hydromotor and, if necessary, can be steered separately. Each wheel is fitted with a height adjustment device 25 so that the height of the frame and its inclination, if any, can be adjusted exactly to the working or transport height. The total weight of the machine is thus concentrated on the area between the chassis 4 and a hub 7 orts is fixed below the driver's cabin to the centre of the machine, which is used as a mixing work space for 28 rotary work spaces 8 limiting the area.

Below the machinery frame 1, a unit 2 at the machinery frame 1 can be rotated around a pivot axis 3 8 parallel to the work cylinder, which is located at the driver's cab 23 opposite the end of the machinery frame 1 approximately at the height of the chassis axis 4. With the help of piston cylinder units 60 placed on both sides of the machinery frame 1, the unit 2 can be lowered to the desired working depth 29, which simultaneously increases the working space 28 under the hood 7. The vertical piston cylinder units 60 intersect on the one hand in the middle of the upper length of the machinery frame 1 and on the other hand at the work cylinder 8 towards the base of the machinery frame 2 at the end. The force applied to each of the 60 piston points is approximately in the direction of the entire machine.

Unit 2 has a swivel frame 13 in which an internal combustion engine 9 with a cooling unit 52 and hydropumps for the hydraulic drive of the wheels, not shown in detail, a drawbar drive 10 for direct mechanical drive of the working roller 8 via a sub-gear 11 and the working roller 8 itself are stored.

The design of the cylinder drive in unit 2 ensures maximum efficiency. The engine power of the combustion engine 9 is transmitted directly to the sub-gear 11 in the working cylinder 8 via an unshifted clutch and the belt drive 10. The advantage of this drive unit integrated in unit 2 is that no hydraulic transformation with the associated adverse force loss is required and no extensive power transmission is required.

The advantageous relative position of the roll axis 5 of the working roller 8 with respect to the axis 4 of the chassis and the resulting advantageous weight distribution are shown in the drawings.

The fixed arrangement of the hood 7 on the machine frame 1 provides for hydraulically adjustable flaps 18,19 at the free end of the hood housing, which can be moved around the rotating axes 20 running parallel to the roll axis 5.

The valves 18,19 of hood 7 are used as adjustable crusher bars to prevent oversized grain or as material control valves and are operated by hydraulic piston units 64,66.

The hood 7 has, as is best shown in Figure 3, an application device 32 for a binder, so that the processed road material can be re-installed on the road as a recycled material 62 with a binder (cement, lime, emulsion, bitumen) in the direction of travel behind the working roller 8.

The working roller 8 extends transversely in the direction of travel over the entire width of the machine and is fitted with, on its perimeter, switch holders 16 which accommodate cutting tools 17 and are attached by means of a clamping screw 15.

Fig. 4 shows a longitudinal section through the working roller 8 with the cylinder 6 indicated in dashed circles. The working roller 8 is fitted with a sub-gear 11 located inside the working roller, which has a 30 axis shift to increase the possible working depth 29 of the working roller 8 so that the drive 10 of the working roller has a rotation axis shifted upwards vertically to the roll axis 5. The axis shift 30 of the roll drive allows an increase in the working depth 29 at the same working diameter or a reduction in the roll size at the same working depth 29.

The belt drive 10 allows direct transmission of power from the combustion engine 9 to the transverse gear 11 by means of power bands 14.

As can be seen from Fig. 4, the swinging frame 13 overlaps the hood 7, the hood having a groove 50 which allows the working roller 8 to be lowered, so that the working space 28 can also be increased in a beneficial way with increasing working depth.

Depending on the depth of work, different quantities of material must be mixed in the work area.

As can be seen from Figure 4, the inner support 12 of the work roller is placed on the side opposite the sub-gear 11 in such a way as to save space that a so-called zero side is created on this side of the work roller 8 which allows the road to be worked almost without the machine being overhead.

Fig. 5 illustrates the continuous-current operation, wherein the vertical shear forces and their distribution are shown within the cylinder 6 of the main vertical shear forces and their distribution within the cylinder 6 of the cutting circuit. From these vertical shear forces 40 in the area 44 of the cylindrical shell surface involved, a resultant vertical force 42 acting on the machine, running at a distance a from the roll axis 5 and opposite to the shear forces 40, can be determined, which is compensated by the weight of the machine, the resultant gravitational force of the structure 2 and the machine frame 1 being equally distributed in the same vertical plane, in the direction of the rolling machine, so that the reaction force 42 is not adversely affected by the resultant vertical shear force 42.

In the reverse-running process shown in Figure 6, horizontal forces 43 in the range of action 45 are generated as relevant force components of the cutting forces, so that these forces must essentially be compensated by the driving force 26 of the machine.

The horizontal distance between the roll axis 5 of the working roller 8 and the common vertical plane 41 is approximately 0.25 to 0.4 times, preferably 0.3 times, the diameter of the working roller.

The distance b between the pivot axis 3 of module 2 and the roll axis 5 shall be at least 1 1⁄2 to twice the diameter of the working roller.

The machine is not longitudinally overhanging the chassis, which allows almost complete application of the force of gravity to the swivel unit 2, which already has a high specific weight, which directly weighs the working roller 8 due to the aggregates placed in it.

Claims

A machine for the treatment of roadways, comprising
- a driver's platform (23) for an operator,

- an automotive drive carriage having two drive carriage axes (4),

- a working drum (8) supported to be pivoted relative to the machine frame (1) and surrounded by a cover (7) defining a working chamber, and

- a drive motor (9) generating the driving power required for driving the working drum (8) and for the traveling movement of the machine,
characterized in
- that a drive unit including the drive motor (9) is supported in a pivoting frame (13) and forms an assembly (2) pivotable relative to the machine frame (1),

- that also the working drum (8) is supported in said pivotable assembly (2) and can be pivoted together with the assembly (2) relative to the cover (7) which is fixed in position on the machine frame (1), and

- that the working drum (8) is directly acted on by the weight of the assembly (2), almost the complete machine weight being concentrated between the drive carriage axes (4) and being transmitted to the pivotable assembly (2).
The machine according to claim 1, characterized in that the drive unit comprises an internal combustion engine (9) with a cooling aggregate (52), for generating the driving power for the working drum (8) and the drive carriages.
The machine according to claim 1 or 2, characterized in that the pivoting frame (13) is mounted on the machine frame (1) to be pivoted about an axis (3) extending in parallel to the working drum axis (5).
The machine according to any one of claims 1 to 3, characterized in that the working drum (8) is driven via a reduction gear (11).
The machine according to claim 4, characterized in that the drive for the reduction gear (11), performed via a pulley (10), is provided eccentrically of the working drum axis (5).
The machine according to any one of claims 1 to 5, characterized in that the assembly (2) pivoted to the machine frame (1) can be lowered via recesses (50) on an end side of the cover (7).
The machine according to any one of claims 1 to 6, characterized in that the cover (7) fixedly connected to the machine frame (1) is provided with breaker bars (19) pivotable about an axis arranged in parallel to the working drum axis (5) of the working drum (8).
The machine according to any one of claims 1 to 7, characterized in that the driver's platform comprises a driver's cabin (23), the wall elements of said cabin being completely or partly foldable for transport purposes.
The machine according to claim 8, characterized in that the upper portion (24) of the driver's cabin (23) is arranged to be pivoted for transport purposes.
The machine according to any one of claims 1 to 9, characterized in that contactless or contacting measuring systems are arranged on one or both machine sides for indicating the working depth (29).
The machine according to claim 10, characterized in that ultrasonic sensors are provided for indicating the working depth (29).
The machine according to claim 10 or claim 11, characterized in that the signals obtained from the sensors are used for controlling the working depth (29).
The machine according to any one of claims 1 to 12, characterized in that the working drum (8) is provided with cutting tools (17) held in exchange holders (16) by means of a positive connection.
The machine according to any one of claims 1 to 13, characterized in that the cover (7) has provided therein injection means (32) for bituminous and/or hydraulic binding agents.
The machine according to any one of claims 1 to 14, characterized in that the vertical reaction force of the cutting forces on the working drum (8) in a co-rotational working process acts on the pivotable assembly (2) by a lever arm which is of the same length or shorter than the lever arm by which the weight force acts on the pivotable assembly (2), whereby the working drum (8) can be operated with the highest possible pressing force.
The machine according to any one of claims 1 to 15, characterized in that the vertical plane (41) of the resultant weight force substantially coincides with the vertical plane of the resultant reaction force (42) of the cutting forces (40) of the cutting tools (17) of the working drum (8) located in the engagement region (44) in co-rotational operation.
The machine according to claim 16, characterized in that the working drum axis (5) is arranged in a vertical plane extending at a horizontal distance (a) from the common vertical plane (41) of the resultant weight force and the resultant cutting forces.
The machine according to claim 17, characterized in that said distance (a) is 0.25 to 0.40 times, preferably about 0.3 times the diameter of the working drum (8).
The machine according to any one of claims 1 to 18, characterized in that the distance (b) of the pivot axis (3) of the assembly (2) from the working drum axis (5) is at least 1 ½ times up to twice the diameter of the working drum (8).