Excavation machine for making excavations for creating diaphragm walls

Abstract

Excavation machine (1) for making excavations for creating diaphragm walls, comprising: - a base machine (2) comprising: - a truck (4); - a turret (5) rotating with respect to the truck (4) ; - at least one winder for at least one service line, positioned on the turret (5); - an arm (6, 36) hinged to the turret (5) at a base end of the arm (6, 36) so as to be rotatable and inclinable with respect to the turret (5), said arm (6, 36) supporting a plurality of head pulleys (19, 25, 29, 30) at a head end opposite to the base end; - an excavation tool (3) hanging from the arm (6, 36) and supported by at least one flexible suspension element (7) windable and unwindable on a winding / unwinding assembly (8) associated with the base machine (2); wherein the winding / unwinding assembly (8) comprises two drums (8A, 8B) coaxial with each other, from each of which a respective branch of the at least one flexible suspension element (7) originates, where each branch originates from the respective drum (8A, 8B), passes over at least one respective pulley (19, 25) of the head pulleys (19, 25, 29, 30), and is connected to the excavation tool (3).

Description

[0001] The present invention refers to an excavation machine for making excavations in the ground for creating diaphragm walls, particularly but not exclusively adapted to be used in urban environments.

[0002] "Diaphragm walls" mean to indicate temporary or permanent underground walls, which are made to contain or reinforce grounds during the construction of building foundations, such as buildings, bridges, and so on.

[0003] In order to make the diaphragm walls, excavation machines are generally used, provided with excavation heads such as for example the hydraulic bucket, the rope-operated bucket, the hydro-mill, and so on. Such excavation heads are generally moved, or at least hold during normal operation of the machine, by a bearing rope, which is wound and unwound around the drum of a motorized winch.

[0004] An example of a known excavation machine for making excavations in the ground for creating diaphragm walls is shown in figure 1. In such figure 1, the excavation machine is overall indicated by reference number 100. The excavation machine 100 is mainly dividable into a base machine 102 and an excavation tool 103 supported by the base machine 102. The base machine 102 generally comprises a tracked truck 104, a turret 105 rotating with respect to the tracked truck 104, and an arm 106, usually inclinable and hinged to the turret 105, where an excavation tool 103 is supported by the arm 106. Said arm 106 supports the excavation tool 103 through a flexible suspension element 107, for example a rope, which is windable and unwindable through a winch 108. In particular, the flexible suspension element 107, originating from the winch 108, is redirected to head pulleys 119 (referred to as lead sheaves) and then connected to the excavation tool 103. The head pulleys 119 are positioned at the end of the arm opposite to that hinged to the turret 105, therefore referred to as the head of the arm. The turret 105 comprises a turret frame 110, which has a structural function and is connected to the truck 104 through a slewing ring 111 which has a vertical rotation axis 120 around which the entire turret 105 rotates.

[0005] The turret frame 110, in its front part, comprises hinges (pin holes or attachments) in which the arm 106 is hinged. Also connected to the front part of the turret frame 110 is the winch 108, which in figure 1 is only partially visible and shown in dashed lines to highlight the hidden part. The turret frame 110 is further responsible for holding all components comprised in or connected to the turret 105.

[0006] The base machine 102 is responsible for manoeuvring the excavation tool 103, positioning it at the excavation point, and providing such excavation tool 103 with the power required to excavate the ground.

[0007] The base machine 102 further performs a plurality of service functions, among which the following are essential: the movement of the excavation machine 100; the movement of the arm 106 and the turret 105 for positioning the excavation tool 103 and rotating the winch 108 to wind or unwind the flexible suspension element 107 to raise or lower the excavation tool 103 in the excavation. The excavation tool 103 generally comprises a milling cutter, which comprises a bearing prismatic frame 109, at the base of which excavation means 112 are fixed, in particular rotating excavation drums. The excavation drums 112 break down, and specifically cut and grind, the ground, ensuring a rectangular section of the excavation. The debris broken down by the teeth into small enough pieces are expelled from the excavation through an immersed suction pump 114, also fixed to the bearing prismatic frame 109 of the excavation tool 103, which sucks such the debris together with the stabilizing mud or excavation fluid, which fills the excavation, conveying them to the surface through a mud tube 115. Once it reaches the surface through the mud tube 115, due to the pressure from the pump 114, the excavation fluid is sent to specific plants that separate the hanging solid part, while the liquid fraction is reintroduced into the excavation in order to keep it constantly full. In this way, the excavation tool 103 progresses by removing ground down to the design depth. Such mud tube 115 is wound and unwound on a winder 113, to follow the movement of the excavation tool during the excavation and lifting steps.

[0008] Such winder 113 for the mud tube 115 is positioned on the rotating turret 105 of the base machine 102. Referring to figure 1 of the prior art, it is possible to observe how the excavation tool 103 is also connected to the base machine 102 by support and guiding devices 116 of the power lines. Such support and guiding devices 116 are wound and unwound on a winder 117 to follow the movement of the excavation tool during the excavation and lifting steps. These support and guiding devices 116 of the power lines contain hydraulic pipes that allow the transmission of an oil flow rate and, generally, a hydraulic power from the base machine 102 to the hydraulic actuators and motors of the milling cutter. The support and guiding devices 116 of the power lines can also contain electric cables or signal cables. Such winder 117 for the support and guiding devices 116 is generally positioned on the turret 105 of the base machine 102. The hydraulic or electric power to supply the excavation tool is therefore generated in the base machine 102, which is on the ground level, outside the excavation.

[0009] Ground level means a small portion of ground surface taken as a reference for performing certain specific functions, for example related to building construction. In the present context, the ground level substantially corresponds to the resting plane of the truck 104.

[0010] Generally, the power for supplying the excavation tool is generated by a power lock, also referred to as power-pack 118, which comprises a hydraulic and / or electric power generator assembly, installed on the turret 105 of the base machine 102. Such power-pack 118 can generally comprise a power motor (Diesel or electric), hydraulic pumps, power lines for the tool and for the base machine. Depending on the size of the excavation machine 100 and the power requirements of the machine itself and the excavation tool, the power-pack can be inside the turret housings or positioned in a cantilevered manner, but however constrained to the turret frame 110.

[0011] Still with reference to figure 1, it is possible to define, for the excavation machine 100, the related dimensions radius, or more precisely the "swept radius", indicated as RS100. The radius RS100 indicates the distance between the rotation axis 120 of the turret and the part of the machine that is furthest, in the horizontal direction, from such rotation axis. In the example of figure 1, the turret 105 has at its rear part a shelf-shaped support, connected to the turret frame 110, which supports in a "cantilevered" manner the power-pack 118. The outer edge of this shelf-shaped support constitutes the point or edge of the machine furthest from the rotation axis 120, and thus defines the point of maximum dimensions of the machine. When the turret 105 rotates around the rotation axis 120, the point of maximum dimensions which is at a distance RS100, describes a circumference with radius RS100 around the rotation axis 120. The excavation machine 100 therefore, during a complete rotation of the turret 105, "sweeps" an area, hereinafter referred to as AS100, having a circular shape with a radius RS100. It follows that, in order for the machine 100 to operate safely, the swept area AS100 must be free of any object that could be struck by parts of the turret during its rotation. Likewise, it can be said that the excavation machine 100 shown in figure 1 can operate on construction sites where a "free" area is always ensured around the machine, having a size at least greater than the swept area AS100.

[0012] Still with reference to figure 1, it is also possible to define, for the excavation machine 100, the related "height dimensions", indicated in the figure by the size HH100. The height dimensions HH100 indicate the distance between the ground (or the resting plane of the tracks of the truck 104) and the highest point of the machine, which in the case of figure 1 is at the head of the arm. As in figure 1, the dimensions must be measured / evaluated when the machine is in a configuration that allows the excavation tool to be fully extracted from the excavation, and allows the excavation machine to translate to be positioned in a new excavation point without the tool scraping the ground during translation. It follows that, in order for the excavation machine 100 to operate safely, the area must be free of any object that could be struck by the uppermost parts of the excavation machine 100. Likewise, it can be said that the excavation machine 100 shown in figure 1 can operate on construction sites where a "free" height is always ensured around the machine, with a value at least greater than the height dimensions HH100 of the machine, in order to allow access and translation of the machine.

[0013] In light of the above, it results that the excavation machine 100 of figure 1 is particularly suitable for operating in construction sites where no building structures have yet been constructed. Indeed, due to its geometry and the disposition of its parts, the machine has a very large swept radius RS100 and a significant height HH100. The excavation machine 100 is suitable for situations where the construction site is on a free undeveloped ground, where foundation works are being initiated for buildings to be constructed later. Even in this case, however, the large swept radius RS100 forces the auxiliary plants of the machine to be positioned at a greater distance from the machine, in order to prevent them from being struck during rotation. Among these plants, there could be desanders, tanks, and other machineries for the treatment of excavation mud or debris extracted from the excavation.

[0014] In situations where foundation works, for example the excavation for diaphragm walls, must be carried out in areas that are already partially built, or in cities, it is preferable to use construction variants of the excavation machine 100, generally referred to as excavation machines for urban environment. In particular, these urban environment variants can be divided into two classes: the first is that of so-called "compact" machines, and the second is that of so-called "low-clearance" machines.

[0015] In "compact" type diaphragm wall excavation machines, the goal is to minimize the swept radius RS100 of the machine, and consequently to minimize the swept area AS100. Compact excavation machines are shaped to allow access into construction areas where passage space or available rotation space for the turret is limited. Since certain components present on the base machine 102 are essential for the functioning of the machine and cannot be eliminated, in particular the winders 113 and 117, the winch 108, and the power-pack 118, machine manufacturers, in order to reduce the swept radius, have attempted to reposition these components in different configurations on the base machine. Each of these configurations, however, has its disadvantages and limitations. For example, in some cases, the winders 113 and 117 have been positioned side by side, protruding laterally beyond the sides of the turret 105, and at the same time raised compared to the configuration shown in figure 1, in order to position the power-pack 118 further forward and reduce the rear dimensions. The risk in these cases is that, by increasing the side dimensions, the component of the machine furthest from the rotation axis 120 can be a component which is on the side of the machine rather than at the rear thereof. Therefore, by reducing the rear dimensions but increasing the side dimensions, the actual reduction of the swept radius RS100 and the swept area is only partial. As a further negative effect, the raised positioning of some components, such as the winders 113 and 117, can reduce the stability of the machine and increases the height dimensions of the turret 105.

[0016] In "low-clearance" or "Low Head" type diaphragm wall excavation machines, the objective is to minimize the height dimensions HH100 of the machine. Low-clearance excavation machines are shaped to allow access into construction areas where height passage spaces are limited, or where foundation excavations must be carried out beneath existing bridges, viaducts, or floors that are positioned at a reduced height above ground. Since certain components on the base machine 102 are essential for the functioning of the machine and cannot be eliminated, in particular the winders 113 and 117, the winch 108, and the power-pack 118, machine manufacturers have tried to reduce the maximum height dimensions by repositioning these components in different configurations on the base machine. Each of these configurations, however, have drawbacks and limitations. For example, in some cases a shortened arm 106 has been provided, so that the upper part of the arm does not exceed the height of the winders. However, in order to use this shortened arm, it is required that it is hinged to the turret frame 110 in a position that is further back than the solution shown in Figure 1, and also that an excavation tool 103 with a prismatic frame 109 of reduced height is used. In order to move the hinging point of the arm 106 backward on the turret frame 110, it is necessary to shift the positions of the two winders 113 and 117 to the rear of the turret, so as to free space in the front part and avoid interference with the arm. Although this backward shift of the winders allows the mounting of a modified arm that limits the height dimensions, it has the disadvantage that these winders protrude behind the turret, increasing the swept radius RS100.

[0017] Therefore, based on the above considerations regarding the "compact" and "low-clearance" variants, it becomes extremely complex to simultaneously achieve both the benefits of a reduced swept radius RS100 and a limited height HH100, because it becomes difficult to position the components (winch 108, winders 113, 117, power-pack 118) on the rotating turret.

[0018] A first drawback of known excavation machines, both those of the "compact" and the "low-clearance" type, lies in the fact that positioning the winch 108 on the base machine 102 is particularly complex, as it must comply with specific constraints regarding the correct winding of the flexible suspension element 107 on the winch 108. These constraints are imposed by both rope manufacturers and winch manufacturers, in order to ensure proper winding of the rope 107, to limit the wear of the rope 107, the sheaves, and the drum of the winch 108. These constraints will be explained in greater detail below, with reference to figures 2A and 2B.

[0019] Another drawback of known excavation machines for urban applications lies in the fact that a machine set up as a "compact" variant cannot be economically transformed into a machine set up as a "low-clearance" variant, and vice versa. This is mainly due to the fact that the winch 108, the arm 106, the winders 113, 117, and the power-pack 118 are arranged differently on the turret 105 in the two setups; therefore, the turret frame 110, to which these components are connected, is made differently for "compact" setup machines compared to "low-clearance" setup machines. In known excavation machines, if there is a turret frame 110 designed for a "compact" setup, it is not possible to reposition the components on such same turret frame to achieve the disposition required for a "low-clearance" setup. Figure 2A shows in a simplified manner a plan view of the drum of a known type of winch 108, such as for example that employed in the machine of figure 1, from which a rope branch is unwound and redirected at a certain angle, referred to in Italian as "angolo di deflessione" and in English as "fleet angle", onto a fixed pulley, and then directed to a load hanging from the free end of such rope (the load is not visible). The definition of "fleet angle" will be provided below. Such definition is applicable to any winch.

[0020] With reference to figures 2A and 2B, the winch 108 has a drum with a width L, intended to be measured between the two shoulders of the drum, i.e., between its two longitudinal ends of the drum. The drum of the winch 108 is moved in rotation by an actuator, not shown, which provides the torque required to wind or unwind the flexible suspension element to move the applied load; for simplicity, reference will be made to a rope as an example of a flexible suspension element. The rope 107 has a first end constrained to the drum and is wound to the drum with a certain number of turns. From the drum, the rope originates in a "branch" that is redirected onto at least a first head pulley 119, which has its own rotation axis 122 oriented parallel to the rotation axis of the drum of the winch 108. The first head pulley 119 is referred to as a "fixed pulley," meaning that it cannot slide axially along the rotation axis, but remains free to rotate in an idle manner around the rotation axis 122. In figure 2B, a second head pulley 125 is also provided, and the rope 107 is redirected from the first head pulley 119 to the second head pulley 125. The first head pulley 119 and the second head pulley 125 of Figure 2B are both mounted on the head of the arm 106 and are substantially coplanar; the rotation axes of such head pulleys 119, 125 are substantially parallel, and the distance between these axes is sufficient to allow to pass beyond the tip of the arm so that the rope does not interfere with the arm itself.

[0021] For the head pulleys 119, 125, it is possible to define a "mid-plane," which is a plane perpendicular to the respective rotation axis and positioned halfway (equidistant) between the two shoulders of the head pulleys 119, 125. Similarly, it is possible to define a mid-plane of the drum of the winch 108. The head pulleys 119, 125 are conveniently installed so that the mid-plane of the pulleys is approximately in the middle of the drum, that is, the mid-plane of the pulleys 119, 125 is coplanar with the mid-plane of the drum of the winch. The first head pulley 119 is at a distance "DLS1" from the drum of the winch in the configuration of figure 2A and in the configuration of figure 2B, where this distance is intended as the linear distance between the rotation axis 122 of the first head pulley 119 and the rotation axis of the drum. The rope branch 107 exiting the drum, being under tension, is arranged along a straight line connecting the drum to the first head pulley 119, and such straight line of the rope branch assumes a certain angle with respect to the mid-plane of the fixed pulley. This angle is referred to as the "fleet angle" and is indicated by letter α in Figure 2A and by α1 in Figure 2B. During winding or unwinding of the rope on the drum, the direction of the rope branch exiting the drum varies depending on the number of turns wound on the drum, and passes from a limit condition wherein the rope branch is tangent to a first shoulder of the drum to a second limit condition wherein the rope branch is tangent to a second shoulder of the drum. These two limit conditions recur for each rope layer during the winding or unwinding of the rope on the drum of the winch.

[0022] The value of the fleet angle α, α1 must not exceed a maximum limit, indicated as αMax, or "maximum admissible fleet angle," which is imposed by the rope manufacturer to ensure proper functioning of the rope and correct winding / unwinding with respect to the drum of the winch. Indeed, when the fleet angle exceeds permissible values, excessive and premature wear of the rope occurs, as it is subjected to bending and / or yielding, as well as premature wear of the fixed pulley, excessive side load on the shoulders of the fixed pulley, and difficulties in obtaining proper winding of the turns on the drum of the winch. Therefore, the sizes L, DLS1, and α in figure 2A, and L, DLS1, and α1 in figure 2B, are strictly correlated and interdependent, and thus cannot be selected arbitrarily. For example, once the position of the first head pulley 119 on the excavation machine 100 has been defined based on the geometry of the arm of the machine, and the width L of the drum of the winch 108 has been established based on the amount of rope required to perform the stroke of the excavation tool, then the positioning of the winch 108 on the machine cannot be arbitrary but must be positioned at a distance DLS1 that allows the rope to assume a fleet angle α smaller than the maximum admissible fleet angle αMax. In essence, once the position of the first head pulley 119 and the width L of the drum of the winch are fixed, the drum of the winch cannot be brought closer to the head of the arm beyond a certain limit, in other words, it cannot be positioned nearer than a certain distance DLS1, so as to avoid excessively high fleet angles, which would be inadmissible.

[0023] The configuration of Figure 2A can, for example, correspond to the embodiment of Figure 2C.

[0024] In the example of Figure 2C, the winch 108 comprises a single drum with width L; from the drum 108, a single rope branch 107 originates, having a first end constrained to the drum 108. The rope branch 107 passes through a first pair of head pulleys 119, 125, then descends to a first block 126 connected to the excavation tool 103. From the first block, it rises to an intermediate sheave 127 fixed to the tip of the arm. From the intermediate sheave 127, the rope branch 107 descends to a second block 128 connected to the tool, then rises to a second pair of head pulleys 129, 130, and finally descends to connect, at a second end, to a fixed point of the base machine 102, for example to the turret frame 110 or the arm 106. A certain length of rope is connected to the winch 108, depending on the maximum stroke intended for the excavation tool 103. The winch 108, the head pulleys 119, 125, 129, 130, the blocks 126, 128, the intermediate sheave 127, and the rope 107 are part of a system for moving the excavation tool 103.

[0025] By observing Figure 2C, it is understood that, since the second end of the rope 107 is fixed, during the movement of the excavation tool 103, the rope being wound or unwound from the drum must run on the intermediate sheave 127, which must therefore rotate around its own rotation axis. Since the rotation axis of the intermediate sheave 127 is perpendicular to the rotation axis of the drum of the winch 108 and also perpendicular to the rotation axis of the sheaves 119 and 125, when the rope passes over the intermediate sheave 127 results in side bending, which reduces the service life of the rope.

[0026] Furthermore, the rope branch 107 originating from the winch 108 must sweep the entire width L of the drum, and thus assumes high fleet angles, which forces the winch 108 to be positioned as far as possible from the head pulleys 119, 125, 129, 130 in order to prevent the fleet angle of the rope from exceeding the allowable limit.

[0027] If the intention is to reduce the distance DLS1 without exceeding the maximum allowable value for the fleet angle, the only possibility would be to reduce the width L of the drum, but this would have negative consequences. Indeed, in order to store the same length of rope on the drum, if L is reduced, it would be necessary to increase the number of layers wound on the drum, but increasing the number of layers leads to greater difficulty in winding, with the risk that the turns are not disposed properly on the drum, but instead overlap irregularly. Furthermore, increasing the number of rope layers on the drum causes higher stress on the lower layers, increasing the risk of damage. Therefore, there is a maximum number of layers that can be allowed to wind on the drum.

[0028] The relationships that must be respected between the sizes L, α, α1, and DLS1 make it difficult, in known excavation machines for the construction of diaphragm walls, to position the winch and other components on the base machine 102. In particular, in low-clearance excavation machines using a short arm, since the head pulley 119 is relatively close to the turret of the machine, in order to comply with the maximum admissible fleet angle for the rope, the winch must be positioned at the rear part of the base machine, which risks increasing both the swept radius of the machine and the height dimensions of the machine. In compact setup excavation machines, similarly, since the winders are mounted further advanced to avoid rear dimensions, the remaining space for installing the winch on the turret frame 110 is at the front part of the turret, i.e., the one closer to the fixed pulley of the head of the arm, therefore, even in this case, it becomes problematic to position the winch at a distance DLS1 sufficient to ensure compliance with the maximum admissible fleet angle.

[0029] The object of the present invention is to overcome the above-mentioned drawbacks and, in particular, to ideate an excavation machine for making excavations for creating diaphragm walls, particularly suitable for operating in urban environments, and which has reduced dimensions both in terms of swept radius and height dimensions, compared to the prior art.

[0030] Another object of the present invention is to provide an excavation machine for making excavations for creating diaphragm walls that can be easily and quickly transformed from a compact type machine to a low-clearance type machine, and vice versa.

[0031] These and other objects according to the present invention are achieved by making an excavation machine for making excavations for creating diaphragm walls as set forth in claim 1.

[0032] Further features of the excavation machine for making excavations for creating diaphragm walls are the subject of the dependent claims.

[0033] The features and advantages of an excavation machine for making excavations for creating diaphragm walls according to the present invention will become more apparent from the following non-limiting exemplary description, with reference to the attached schematic drawings, in which: Figure 1 is a schematic side view of an excavation machine according to the prior art; Figures 2A and 2B are two schemes of a part of a system for moving an excavation tool of the excavation machine according to the prior art; Figure 2C is a schematic perspective view of a system for moving an excavation tool of the excavation machine according to the prior art; Figures 3A and 3B are two schematic side and top views, respectively, of an excavation machine according to a first embodiment of the present invention; Figures 4A and 4B are two schemes of a system for moving an excavation tool of the excavation machine according to the present invention; Figures 4C, 4D, 4E, and 4F are schematic views of different embodiments of a system for moving an excavation tool of the excavation machine according to the present invention; Figures 5A and 5B are schematic side and top views, respectively, of an excavation machine according to a second embodiment of the present invention; Figure 6 is a schematic perspective view of a base machine without the arm, included in the excavation machine according to the present invention; Figures 7A and 7B are two schematic side detail views of the first and second embodiments of the excavation machine, without the power lock, according to the present invention; Figure 8A is a schematic top view of a base machine included in the excavation machine according to the present invention, with the power lock in a first operating position; Figures 8B and 8C are two schematic top views of two different configurations of the base machine with the power lock in a second and a third operating position, respectively; Figure 9 is a schematic perspective view of an excavation machine according to a second embodiment of the present invention.

[0034] With reference to the figures, an excavation machine for making excavations for creating diaphragm walls is shown, overall indicated by 1.

[0035] The excavation machine 1 comprises a base machine 2 and an excavation tool 3 supported by the base machine 2. The base machine 2 comprises a truck 4, a turret 5 rotating with respect to the truck 4, and an arm 6, 36 hinged to the turret 5 at one of its base ends, so as to be rotatable and inclinable with respect to the turret 5.

[0036] For example, the truck 4 is a tracked truck.

[0037] The arm 6, 36 can be selected from a first arm 6 for compact machines, or a second arm 36 for low-clearance machines, wherein the second arm 36 has a shorter length than the first arm 6 for compact machines.

[0038] In any case, the arm 6, 36 supports a plurality of head pulleys 19, 25, 29, 30 at its head end, opposite to the base end.

[0039] The excavation tool 3 is hanging from and supported by at least one flexible suspension element 7, which is windable and unwindable on a winding / unwinding assembly 8 associated with the base machine 2.

[0040] According to the present invention, the winding / unwinding assembly 8 comprises two drums 8A, 8B coaxial with each other, from each of which a respective branch of the at least one flexible suspension element 7 originates, where each of the branches originates from a respective drum, passes over at least one respective pulley 19, 25 of said head pulleys 19, 25, 29, 30, and is connected to the excavation tool 3.

[0041] The specific embodiment of the winding / unwinding assembly 8 and the particular path of the at least one flexible suspension element 7 allow the winding / unwinding assembly 8 to be positioned closer to the head pulleys 19, 25, 29, 30 than what is possible in the prior art, while still ensuring compliance with fleet angle constraints, in order to minimize the wear on the pulleys themselves and the flexible suspension element 7.

[0042] Preferably, the winding / unwinding assembly 8 comprises a winch comprising in turn the two drums 8A, 8B; in such case, the drums 8A, 8B are connected so as to be integral to each other and are drivable by the same motor (not illustrated).

[0043] Alternatively, the winding / unwinding assembly 8 can comprise two winches, each of which comprises a respective drum of the two drums 8A, 8B; in such case, the drums 8A, 8B are mechanically unconstrained from each other and are drivable by respective motors, which are commanded such that the two drums 8A, 8B are synchronized to rotate at the same speed, as if they were integrally connected and exerting the same force on the flexible suspension element.

[0044] For exposure simplicity, only embodiments of the winding / unwinding assembly 8 with a single winch comprising two drums have been illustrated.

[0045] Preferably, the excavation machine 1 can comprise two blocks 26, 28 connected to the excavation tool 3, which make the connection between each of the branches of the at least one flexible suspension element 7, 7' and the excavation tool 3.

[0046] Preferably, the head end of the arm 6, 36 is connected to a prolongation element 47, at the free end of which there is a support element 48 for the at least one flexible suspension element 7.

[0047] More preferably, the support element 48 comprises an intermediate sheave 27; in such case, each of the branches of the at least one flexible suspension element 7, 7' passes over the intermediate sheave 27 after the head pulleys 19, 25, 29, 30.

[0048] Preferably, the excavation machine 1 comprises two flexible suspension elements 7, 7', where each of the flexible suspension elements 7, 7' is windable and unwindable on a respective drum.

[0049] Alternatively, the at least one flexible suspension element 7, 7' is single and has a detachable section 7" intended to be disposed around said intermediate sheave 27.

[0050] Figure 4C shows the case where the flexible suspension element 7 is single, and the support element 48 comprises an intermediate sheave 27 over which the flexible suspension element 7 passes; further preferably, the connection between the flexible suspension element 7 and the excavation tool 3 is made by blocks 26, 28.

[0051] Figure 4D shows the case where two flexible suspension elements 7, 7' are provided, each of which has one end constrained to a respective drum 8A, 8B and the opposite end constrained to a balance arm 49 the support element 48 is provided with; further preferably, the connection between each of the two flexible suspension elements 7, 7' and the excavation tool 3 is made by a respective block 26, 28.

[0052] Figure 4E shows a case similar to that of Figure 4C, differing in that the flexible suspension element 7 has a detachable section 7" intended to be disposed around the intermediate sheave 27.

[0053] Figure 4F shows the case where two flexible suspension elements 7, 7' are provided, each of which has one end constrained to a respective drum 8A, 8B, and the opposite end directly constrained to the excavation tool 3; in such case, the support element 48 and the blocks 26, 28 are not present.

[0054] The turret 5 comprises a turret frame 10, which has a structural function and is connected to the truck 4 through a slewing ring 11, which has a vertical rotation axis 20 around which the turret 5 rotates. The turret frame 10, preferably in its front part, is arranged to be hinged to the arm 6, 36. The arm 6, 36 is arranged to be moved, in order to vary its inclination, through linear actuators 23, 33, which are also connected, directly or indirectly, to the turret frame 10. The actuators 23, 33, for example hydraulic cylinders, can be connected directly to the turret frame 10 by means of pins, or indirectly, if connected to supports which are in turn rigidly connected to the turret frame 10. The turret frame 10 is further responsible for holding all the components comprised in or supported by the turret 5.

[0055] The base machine 2 is arranged to manoeuvre the excavation tool 3 by positioning it at the excavation point and providing the required power to such excavation tool 3 to excavate the ground.

[0056] The base machine 2 further performs a plurality of service functions, among which the following are essential: the movement of the excavation machine 1; the movement of the arm 6, 36 and of the turret 5 for positioning the excavation tool 3 and the driving of the winding / unwinding assembly 8 to wind or unwind the at least one flexible suspension element 7, 7', 7" in order to raise or lower the excavation tool 3 in the excavation.

[0057] The base machine 2 further comprises at least one winder for at least one service line, positioned on the turret 5; service line means to indicate, for example, a pipe or conduit for suction or supply of a working fluid, a hydraulic power line, an electric power line or related cables, or an electric or electronic signal transmission line or related cables, wherein such pipes, lines, and cables can be supported in turn in support and guiding devices that are windable and unwindable.

[0058] For example, as in the illustrated embodiments, the excavation tool 3 can comprise a milling cutter, which comprises a bearing prismatic frame 9, at the base of which excavation means 12, for example rotating excavation drums, are fixed. The excavation drums 12 break down, and specifically cut and grind the ground, ensuring a rectangular section of the excavation. In such case, the debris crushed by the teeth into sufficiently small particles is expelled from the excavation by means of a suction pump 14, also fixed to the bearing prismatic frame 9 of the excavation tool 3, which sucks them together with the stabilizing mud or excavation fluid filling the excavation, and conveys them to the surface through a mud tube 15. Once it reaches the surface through the mud tube 15, due to the pressure by the pump 14, the excavation fluid is sent to dedicated plants that separate the solid part in suspension, while the liquid fraction is reintroduced into the excavation to keep it constantly full. In this way, the excavation tool 3 advances by removing ground down to the design depth. Such mud tube 15 is wound and unwound on a first winder 13, in order to follow the movement of the excavation tool during excavation and retrieval steps. Such first winder 13 for the mud tube 15 is positioned on the turret 5 of the base machine 2 and rigidly connected to the structural frame 10 of the turret.

[0059] The excavation tool 3 is further connected to the base machine 2 by means of support and guiding devices 16 of the power lines, as can be observed in figure 3A. Such support and guiding devices 16 are wound and unwound on a second winder 17 for the power lines of the excavation tool 3, so as to follow the movement of the excavation tool during excavation and retrieval steps. These support and guiding devices 16 of the power lines contain hydraulic pipes that allow the transmission of an oil flow rate and, more generally, of hydraulic power from the base machine 2 to the hydraulic actuators and motors of the excavation tool 3. The support and guiding devices 16 of the power lines can also contain electric or signal cables. The second winder 17 is positioned on the turret 5 of the base machine 2 and is rigidly constrained directly or indirectly to the turret frame 10 of the turret.

[0060] The hydraulic or electric power to supply the excavation tool 3 is therefore generated by the base machine 2, which is on the ground level, outside the excavation. The power for supplying the excavation tool is generated by a power lock 18, also referred to as a power-pack, which comprises a hydraulic or electric power generator and is installed on the turret 5. Such power lock 18 can generally comprise a power motor (Diesel or electric), hydraulic pumps, and power lines for both the tool and the base machine. Depending on the size of the excavation machine 1 and the power requirements of the machine and the excavation tool 3, the power lock 18 can be inside the enclosures of the turret 5, or it can be positioned in a "cantilevered" manner, but however constrained to the turret frame 10. Preferably, the turret frame 10 and the power lock 18 are provided with respective coupling elements arranged to constrain the power lock 18 to the turret frame 10 in a first operating position and / or in a second operating position.

[0061] In such case, preferably, the first operating position corresponds to the rear end portion of the base machine 2, which is the portion opposite to that towards which the arm 6, 36 extends, as visible in Figure 8C, and the second operating position corresponds to a side end portion of the base machine 2, as visible in Figure 8B. In a construction variant, the power lock 18 can be separated from the turret 5 and positioned on the ground near the machine 1, as in Figure 8A, in a third operating position. In this case, the power lock 18 is mechanically unconstrained from the turret, but remains electrically and hydraulically connected to the turret through cables and pipes for transmitting hydraulic and electric power, as well as signals.

[0062] This construction variant can be useful in construction sites where space is extremely limited.

[0063] The "swept radius" of the machine 1 is indicated as RS1. The radius RS1 indicates the distance between the vertical rotation axis 20 of the turret 5 and the furthest part of the machine in the horizontal direction from such rotation axis. In the example of Figure 3A, at the rear part of the turret 5, the turret frame 10 has a terminal portion, to which a counterweight 24 is fixed, shaped suitably. The outer edge of the suitably shaped counterweight 24 constitutes the point or edge of the machine furthest from the vertical rotation axis 20, and can be also defined as the maximum dimensions of the machine.

[0064] When the turret 5 rotates around the vertical rotation axis 20, the point of maximum dimensions, which is at a distance RS1, traces a circumference with radius RS1 around the vertical rotation axis 20. Therefore, during a full rotation of the turret 5, the excavation machine 1 "sweeps" an area, which will be referred to as AS1, having a circular shape with radius RS1.

[0065] Preferably, the winding / unwinding assembly 8 is fixed to the arm 6, 36.

[0066] This allows space to be saved on the turret frame 10, where it becomes possible to position the at least one winder for a service line, and in particular the first winder 13 and the second winder 17, so as to minimize the swept radius RS1.

[0067] In Figure 3B, the swept radius RS1 of the machine 1 is clearly visible. It can be noted that the first winder 13 for the mud tube 15 and the second winder 17 for the support and guiding devices of the power lines are appropriately arranged on the turret frame 10 so that their dimensions do not protrude beyond the swept radius RS1 and the swept area AS1. In particular, this advantageous positioning of the two winders 13 and 17 is allowed by the fact that the winding / unwinding assembly 8 is positioned on the arm 6, 36, which is closer to the head pulleys 19, 25, 29, 30 than what is possible in the prior art.

[0068] Preferably, at least one of the winders, in the illustrated case consisting of the second winder 17, is positioned on the turret frame 10 substantially in line with the arm 6, 36, in order to avoid undesirable torsions in the power lines. In particular, the mid-plane of such winder, perpendicular to its rotation axis, is substantially coplanar with the longitudinal mid-plane of the arm.

[0069] Preferably, at least one further winder, in the depicted case consisting of the first winder 13, is positioned alongside the other (i.e., the second winder 17) and advantageously inclined with respect to the arm 6, 36. In particular, the mid-plane of such further winder, perpendicular to its rotation axis, forms a non-zero angle with respect to the longitudinal mid-plane of the arm 6, 36.

[0070] In the particular embodiment of Figure 3A, the power lock 18 is positioned on one side of the turret frame 10, so that their dimensions do not protrude beyond the swept radius RS1 and the swept area AS1. Advantageously, the power lock 18 is positioned on the side opposite to the operator cab 50, so as not to obstruct access to the cab 50 and not to reduce the field of view of the operator.

[0071] In order for the excavation machine 1 to operate safely, the swept area AS1 must be free of any objects that could be struck by the parts of the turret 5 during rotation. Likewise, it can be stated that the excavation machine 1 according to the present invention can operate in construction sites where a "free" area is always ensured around the machine, having sizes at least greater than the swept area AS1.

[0072] The excavation machine 1, according to the present invention, has a swept radius RS1 smaller than the swept radius RS100 of the prior art excavation machine 100 of Figure 1. Therefore, the excavation machine 1 according to the present invention is much more suitable for operating in confined spaces or urban environments than the excavation machine 100.

[0073] The "height dimensions" of the excavation machine 1 according to the present invention is indicated by the quote HH1. The height dimensions HH1 indicates the distance between the ground or the resting plane of the truck 4 and the highest point of the excavation machine 1, which in the case of Figure 3A is at the head of the arm 6, 36. The height dimensions must be measured / evaluated when the excavation machine 1 is in a configuration that allows the excavation tool 3 to be fully extracted from the excavation and allows the excavation machine to translate to be positioned to a new excavation point without the excavation tool 3 scraping the ground during translation. It follows that, for the excavation machine 1 to operate safely, the area must be free of any objects that could be struck by the highest parts. Likewise, it can be stated that the excavation machine 1 according to the present invention can operate in construction sites where a "free" height is always ensured around the excavation machine, with a value at least greater than the height dimensions HH1 of the excavation machine 1, in order to allow access and translation of the excavation machine 1.

[0074] Figures 2B, 4A, and 4B allow comparison between the construction shape of a known winch 108 installed on a known excavation machine 100 and the construction shape of the winding / unwinding assembly 8 installed on the excavation machine 1 according to the present invention. In particular, the configurations of Figures 4A and 4B can correspond, for example, to the configuration of Figure 4C.

[0075] Figure 4A shows the winding / unwinding assembly 8 provided in the present invention, which includes a winch having a bearing frame 8C and two drums, particularly a first drum 8A and a second drum 8B, each with a respective width LA and LB. Each of the drums 8A and 8B comprises two shoulders 41, 42, 43, 44. The distance between the shoulders of the two drums 8A and 8B is substantially equal to the length L of the known winch 108 of Figure 2B, minus the thickness of the central / inner shoulders 42, 43 of the two drums and their mutual distance. The distance between the outer and inner shoulders of each of the drums 8A and 8B is approximately equal to L / 2, i.e., about half the length L of the known winch 108 of Figure 2B. The two drums 8A and 8B are arranged side by side and coaxial, rotating around the same axis of rotation. In the schematized embodiment, the two drums 8A and 8B are integral with each other both axially and angularly, being rigidly constrained through fastening members such as screws or plugs. As such, the two drums cannot rotate relative to one another or become angularly offset with respect to the axis of rotation, and therefore behave as a single monolithic body. In practice, the winding / unwinding assembly 8 in such case includes a single winch, which, through its bearing frame, is associated with the base machine 2, not shown in Figure 4A for simplicity, of the excavation machine 1 according to the present invention.

[0076] As mentioned earlier, in a possible alternative, the winding / unwinding assembly 8 can comprise two winches, each with its own drum, wherein the two drums are arranged coaxial with each other and mechanically unconstrained from each other, but driven in rotation synchronously by respective motors or actuators to rotate at the same speed.

[0077] Each of the two drums 8A and 8B winds and unwinds a respective branch of the at least one flexible suspension element 7, and each of the two branches has one end fixed to the respective drum. The winding or unwinding of each of the two branches on the respective drum occurs at the same speed.

[0078] From each of the two drums 8A and 8B a branch of the at least one flexible suspension element 7 originates, which is redirected onto a respective first fixed pulley 19, 29 and then to a second fixed pulley 25, 30, both installed at the head of the arm 6, 36. Each branch of the at least one flexible suspension element 7 is then connected to the excavation tool 3, which is hanging from such at least one flexible suspension element 7.

[0079] In order to better understand the path of the at least one flexible suspension element 7 in possible different embodiments, refer to Figures 4C, 4D, 4E, and 4F.

[0080] In Figure 4C, two branches of the same flexible suspension element 7 originate from the winding / unwinding assembly 8, each from a respective drum 8A, 8B. In this embodiment, only one flexible suspension element 7 is provided. The first branch of the flexible suspension element 7 has a first end constrained to the first drum 8A from which it originates and reaches a first pair of head pulleys 19 and 25, then descends to the first block 26 that is connected to the excavation tool 3. From the first block 26, it rises to an intermediate sheave 27, which is fixed to the tip of the arm by means of the support element 48; from such intermediate sheave 27, the flexible suspension element 7 descends to a second block 28 connected to the excavation tool 3, then rises to a second pair of head pulleys 29, 30 and finally descends to connect to the second drum 8B, forming the second branch. The overall length of the flexible suspension element 7, a certain amount of which is stored wrapped on the two drums, depends on the maximum stroke intended for the tool.

[0081] Figure 4D illustrates the case where there are two flexible suspension elements 7, 7'. Each respective branch originates from a respective drum 8A, 8B, passes over the head pulleys, is redirected by the respective block 26, 28, and is anchored to the support element 48. Advantageously, in this case, the support element 48 comprises a balance arm 49, comprising an upper pin for connection to the head and a central pin around which the body of the balance arm, provided with side attachments, can incline. Each flexible suspension element 7, 7' is connected, by the respective branch, to a respective side attachment of the balance arm 49. In this embodiment, if there is a slight difference in elongation or speed between the two flexible suspension elements 7, 7', the balance arm 49 can assume a slightly inclined configuration by rotating around the central pin, thereby temporarily compensating for such difference until a condition of perfect balance between the two flexible suspension elements 7, 7' is restored. Figure 4F shows a further construction variant in which two flexible suspension elements 7, 7' are provided. Each respective branch originates from a respective drum 8A, 8B, passes over the head pulleys 19, 25, 29, 30, and is anchored directly to the excavation tool 3, which will be arranged with appropriate attachment points for the ropes. In such case, neither the blocks nor the support element are present.

[0082] Figure 4E illustrate the case where there is a single flexible suspension element 7 that includes the intermediate detachable portion 7", which rests on the intermediate sheave 27. The intermediate portion 7" has at its two ends connection means that allow it to be removably connected to the two sections of the suspension element 7. This allows, in the case of wear of the detachable portion 7", only such portion, and not the entire flexible suspension element 7, to be replaced. Since the two drums 8A, 8B rotate at the same speed, the two branches 7 exiting the corresponding drums wind and unwind at the same speed, and therefore extend and retract at the same speed, allowing coordinated descent and ascent of the two blocks 26, 28. This means that the sheave 27, being midway along the path of the flexible element 7, is not placed in rotation by the rope. The sheave 27 performs only small angular oscillations to compensate for any differences in deformation or speed between the two branches 7. Therefore, since the sheave 27 tends not to rotate, it is always the intermediate portion 7" that rests on the sheave 27, while the two sections 7 do not come into contact with the sheave 27. As the intermediate section 7" is always subject to compression on the sheave 27 and side bending on the sheave 27, it is clear that the intermediate section 7" will wear out more quickly, and therefore, the solution of having an intermediate section 7" disconnectable from the two branches 7 allows for only the section 7" to be replaced.

[0083] In order to compare the systems for moving the excavation tool 3 of the prior art excavation machine 100 with that of the excavation machine of the excavation machine 1 according to the present invention, it is assumed that the length of the flexible suspension element is the same in both scenarios.

[0084] On the head of the arm 6, 36, there are therefore two first head pulleys 19, 29 that are coaxial and positioned at a certain distance from each other along such rotation axis. In particular, the first head pulleys 19 are positioned so that the mid-plane of each pulley 19 is approximately in the middle of the width of the respective drum 8A, 8B. The mid-plane of each head pulley 19, 29 substantially coincides with the mid-plane of the respective drum. On the head of the arm 6, 36, there are also two second head pulleys 25, 30, each coplanar with the respective first head pulley 19, 29. The second head pulleys 25, 30 are axially spaced from each other along the rotation axis.

[0085] The rotation axis of the first head pulleys 19, 29 and the rotation axis of the second head pulleys 25, 30 are substantially parallel to each other, and the distance between these axes is sufficient to allow the flexible suspension element 7 to pass beyond the tip of the arm so that the flexible suspension element 7 does not interfere with the arm itself.

[0086] During the unwinding or winding of each branch of the flexible suspension element 7 on the respective drum 8A, 8B, the exiting branch of the flexible suspension element takes on a different position along the width LA or LB of the respective drum, depending on how many rope turns have already been wound. The branch of the flexible suspension element 7 shifts across the respective drum between two end positions. For drum 8A, there is a first end position wherein the branch of the flexible suspension element is tangent to a first shoulder 41 and a second end position wherein the branch of the flexible suspension element is tangent to a second shoulder 42. Similarly, for drum 8B, the branch of the flexible suspension element takes on a first end position wherein it is tangent to the shoulder 43 and a second end position wherein it is tangent to the shoulder 44. From Figure 4A, it can be seen that when the exiting branch of the flexible suspension element is in one of these two end conditions, it forms an angle with respect to the mid-plane of the first head pulley 19, 29, which is referred to as fleet angle α2.

[0087] In Figure 4A, the winch has been placed at a distance from the first head pulleys 19, 29 that is equal to the distance between the winch 108 and the respective first head pulley 119 depicted in Figure 2B, and such distance is indicated by D1. For greater clarity, in Figure 4B, the rotation axes of the head pulleys 119, 125, 19, 29, 25, 30 have been aligned.

[0088] By comparing Figures 4A and 2B, it becomes apparent that by using a two-drum winding / unwinding assembly 8 according to the present invention, with the same distance D1, the resulting fleet angles α2 for the branches of the flexible suspension element of the two drums are smaller than the fleet angle α1 obtained using a known winch 108. In particular, the fleet angle α2 is less than the maximum allowable fleet angle αMax. As a result, the construction shape of the winding / unwinding assembly 8 allows the wear of the rope and the pulleys to be reduced, reducing the risk of improper winding of the branches of the flexible suspension element 7 on the respective drums.

[0089] Figure 4B shows the same winding / unwinding assembly 8 as in Figure 4A, in this case mounted on the base machine 2 in a position closer to the first head pulleys 19, 29. In Figure 4B, it is assumed that the position of the first head pulleys 19, 29 is unchanged from Figures 2B and 4A, since they are always positioned at the top of the arm 6, 36. In Figure 4B, the fleet angle α2 is equal to αMax and to α1, i.e., α2 = αMax = α1. In such case, the winding / unwinding assembly 8 is at a distance D2 between the drum axis and the first head pulleys 19, 29, which is lower than the distance DLS1 obtained in Figures 4A and 2B.

[0090] Therefore, the described construction solution makes it possible to mount the winding / unwinding assembly 8 in a position closer to the head, specifically at a distance that would not be allowed when using a traditional winch 108 provided with a single drum having a width L, as it would not comply with the allowable fleet angle limits of the rope 7. This is advantageous because by mounting the winding / unwinding assembly 8 further forward with respect to the fixed sheaves on the head, space is freed on the turret, and such space is used to achieve a more compact arrangement of components on the turret.

[0091] As visible in Figure 4C, according to the present invention, since the two drums 8A-8B are integral and coaxial with each other (or coaxial and driven in rotation at the same speed), when the two drums rotate, the amount of flexible suspension element being wound or unwound on or from them is identical. Therefore, the two branches of the flexible suspension element 7 always move at the same speed, and no offset ever occurs between the two branches.

[0092] In this way, when the two branches of the flexible suspension element 7 are wound or unwound, the head pulleys 19, 29, 25, 30 and the pulleys of the blocks 26, 28 rotate around their own axis, which is substantially parallel to the rotation axis of the drums 8A, 8B, dragged by the flexible suspension element. By contrast, the intermediate sheave 27 does not rotate around its rotation axis, which instead is substantially perpendicular to the rotation axis of the drums 8A, 8B, since the two branches of the flexible suspension element that reach the intermediate sheave 27 extend simultaneously at the same speed, and therefore do not generate rotation thereof. This has the advantage of preventing the flexible suspension element 7 from undergoing side bending on the intermediate sheave 27, thus extending the service life of the flexible suspension element 7.

[0093] Figures 5A and 5B show an embodiment of the excavation machine 1 according to the present invention, alternative to that of Figures 3A and 3B. In particular, the excavation machine 1 illustrated in Figures 3A and 3B is set up in a "compact" version, whereas the excavation machine of Figures 5A and 5B is set up in a "low-clearance" or "Low Head" version.

[0094] In the compact version of the excavation machine 1, the first arm 6 is associated with one or more first linear actuators 23 that control its movement. The arm 6 and the first linear actuators 23 are part of a first kinematic linkage.

[0095] In the "low-clearance" version of the excavation machine 1, the second arm 36 is associated with one or more second linear actuators 33 that control its movement, to a head element 31, and to at least one link rod 32.

[0096] The at least one link rod 32 is hinged to the turret frame 10 and to the head element 31 so that, together with the second arm 36 and the second linear actuators 33, it forms a second "parallelogram" type kinematic linkage. The parallelogram allows to keep the inclination of the head element 31 constant even as the inclination of the second arm 36 varies. Advantageously, the parallelogram kinematic linkage allows to keep the upper portion of the head element 31 parallel to the soil.

[0097] The second kinematic linkage allows to have a machine with particularly limited overall height dimensions, due to the use of a second arm 36 that is significantly shorter than the first arm 6 used in the first kinematic linkage. The frame 9 of the excavation tool 3 used in "low-clearance" excavation machines is shorter than that of the "compact" version machines.

[0098] The "low-clearance" version of the excavation machine 1 requires that the hinge point of the second arm 36 is further rearward on the turret frame 10 compared to the "compact" version of the machine.

[0099] Preferably, the turret frame 10 has a base portion 45 provided with first hooking elements 37, 40 arranged to be releasably constrained to a first kinematic linkage comprising a first arm 6 for compact machines, and second hooking elements 37, 38, 39 arranged to be releasably constrained to a second kinematic linkage comprising a second arm 36 for low-clearance machines. Preferably, the first hooking elements 37, 40 comprise first attachments 37 to constrain the first arm 6, which first attachments 37 are disposed at an end of the turret 5; the second hooking elements 37, 38, 39 comprise second attachments 38 to constrain the second arm 36, which second attachments 38 are disposed in a back position with respect to the first attachments 37. Figure 6 illustrates an excavation machine 1 according to the present invention, in which many components including the arm 6, 36 and the power lock 18 have been omitted for clarity, allowing the front part of the turret frame 10 to be displayed.

[0100] The embodiment where the winding / unwinding assembly 8 is fixed to the arm 6, 36 is advantageous, allowing to free space on the turret frame 10, and such space can be used to position the base portion 45 provided with first and second hooking elements.

[0101] The first hooking elements 37, 40 and the second hooking elements 37, 38, 39 allow either the first kinematic linkage or the second kinematic linkage to be installed on the same turret frame 10.

[0102] The first hooking elements 37, 40 comprise first hinges 37 (forming the first attachments) and second hinges 40.

[0103] Figure 7A shows that, in order to mount the first kinematic linkage, the first arm 6 is connected to the first hinges 37 through pins, and the first linear actuators 23 are connected to the second hinges 40, through pins. The other end of the first linear actuators 23 is connected to the first arm 6.

[0104] The second hooking elements 37, 38, 39 comprise the first hinges 37, third hinges 38 (forming the second attachments), and fourth hinges 39.

[0105] Figure 7A shows that, in order to mount the second kinematic linkage, the second arm 36 is connected to the third hinges 38 through pins, the link rods 32 are connected to the fourth hinges 39, and the second linear actuators 33 are connected to the first hinges 37. The other end of the second linear actuators 33 is connected to the second arm 36.

[0106] The simultaneous presence of both the first hooking elements 37, 40 and the second hooking elements 37, 38, 39 on the turret frame 10 allows a "compact" type excavation machine 1 to be quickly and easily transformed to a "low-clearance" type excavation machine 1, since it is sufficient to replace the arm 6, 36 while substantially maintaining the same disposition of the winders 13, 17 with respect to the arm 6, 36 and of the power lock 18 in both versions. In the compact version, it can be necessary to mount a support for the second hinges 40.

[0107] When transporting the machine 1, it is necessary to separate the arm 6, 36 from the frame 10 in order to reduce the weight and size of the base machine, bringing it within the limits imposed by road transport regulations. The construction shapes shown in Figures 7A and 7B, in which the winding / unwinding assembly 8 is fixed to the arm 6, 36, are advantageous because they make it easier and faster to disassemble the arm 6, 36 from the frame. Indeed, when the arm 6, 36 is separated from the frame 10, the winding / unwinding assembly 8 can remain fixed to the arm 6, 36, and the path of the at least one flexible suspension element 7, 7' on the pulleys does not need to be modified or disassembled. Furthermore, the winding / unwinding assembly 8 can be transported together with the arm 6, 36, keeping it constrained to the arm.

[0108] Preferably, as visible in Figure 6, the turret frame 10 also has fifth hinges 46 on the side, which allow the power lock 18 to be connected on the side position to the turret 5 during machine operation. The power lock 18 is in turn provided with connection elements adapted to be connected to the fifth hinges 46 by inserting pins.

[0109] Preferably, the turret frame 10 also has sixth hinges (not illustrated) at the rear, that allow the power lock 18 to be connected on rear position to the turret 5 during machine operation. The power lock 18 is also provided with connection elements adapted to be connected to the sixth hinges by inserting pins.

[0110] The power lock 18 in rear position reduces the width of the excavation machine 1 and improves the front stability of the machine, but increases the swept radius.

[0111] Advantageously, the power lock 18 can be moved from a first mounting position on the side of the turret to a second mounting position at the rear of the turret without requiring any modification to the position of the two winders 13 and 17. Such winders are therefore advantageously positioned since, in addition to limiting the dimensions of the machine, they do not need to be moved neither for replacing the kinematic linkage type nor for modifying the connecting position of the power lock 18 with respect to the turret.

[0112] In a constructive variant, the excavation tool 3 could be a bucket, also comprising a frame to which valves acting as excavation means are fixed. This variant still provides that the bucket is hanging on at least one flexible element 7, 7', moved by a winding / unwinding assembly 8, and that the actuators of the bucket are supplied through lines requiring at least one winder 13, 17 on the turret. Accordingly, all the advantages described also apply to this construction variant.

[0113] From the description provided, the features of the excavation machine 1 according to the present invention, as well as the related advantages, are clear.

[0114] Indeed, the excavation machine according to the present invention, due to the particular configuration of the winding / unwinding assembly, has an improved compactness, or a reduction of the swept angle, compared to "compact" versions of known machines, and such advantage can also be obtained in combination with reduced height dimensions.

[0115] This is particularly advantageous in the case where the excavation machine according to the present invention is set up in a "low-clearance" version; in such case, indeed, the position of the winders and the power lock does not vary with respect to the "compact" version setup, and therefore the advantage of reduced height dimensions is obtained simultaneously with that of having a reduced swept radius.

[0116] It is finally clear that the excavation machine 1 thus conceived is susceptible to numerous modifications and variants, all falling within the invention; furthermore, all details are replaceable by technically equivalent elements. In practice, the materials used, as well as the size, can be any according to the technical requirements.

Claims

1. Excavation machine (1) for making excavations for creating diaphragm walls, comprising: - a base machine (2) comprising: - a truck (4); - a turret (5) rotating with respect to the truck (4); - at least one winder for at least one service line positioned on the turret (5); - an arm (6, 36) hinged to the turret (5) at a base end of said arm (6, 36) so as to be rotatable and inclinable with respect to said turret (5), said arm (6, 36) supporting a plurality of head pulleys (19, 25, 29, 30) at a head end opposite to the base end; - an excavation tool (3) hanging from said arm (6, 36) and supported by at least one flexible suspension element (7) windable and unwindable on a winding / unwinding assembly (8) associated with said base machine (2); where said winding / unwinding assembly (8) comprises two drums (8A, 8B) coaxial with each other, from each of which a respective branch of said at least one flexible suspension element (7) originates, where each of said branches originates from said respective drum (8A, 8B), passes over at least one respective pulley (19, 25) of said head pulleys (19, 25, 29, 30), and is connected to said excavation tool (3).

2. Excavation machine (1) according to claim 1, wherein said winding / unwinding assembly (8) comprises a winch comprising in turn said two drums (8A, 8B), said drums (8A, 8B) being connected so as to be integral to each other and being drivable by the same motor.

3. Excavation machine (1) according to claim 1, wherein said winding / unwinding assembly (8) comprises two winches (8), each of which comprises a respective drum of said two drums (8A, 8B), said drums (8A, 8B) being drivable by respective motors so that said drums are synchronized to rotate at the same speed and exert the same force on the flexible suspension element.

4. Excavation machine (1) according to one or more of the preceding claims, wherein said winding / unwinding assembly (8) is fixed on said arm (6, 36).

5. Excavation machine (1) according to one or more of the preceding claims, comprising at least one winder (17) on which at least one power line of said excavation tool (3) is wound, wherein said at least one winder (17) is positioned on the turret (5) substantially aligned with the arm (6, 36), the mid-plane of said at least one winder (17), perpendicular to its rotation axis, being substantially coplanar with the longitudinal mid-plane of the arm.

6. Excavation machine (1) according to claim 5, comprising at least one further winder (13) on which a mud tube (15) is wound, wherein said further winder (13) is positioned alongside said at least one winder (17) on which said power line is wound and is inclined with respect to said arm (6, 36), the mid-plane of said further winder (13), perpendicular to its rotation axis, forming a not-zero angle with the longitudinal mid-plane of the arm (6, 36).

7. Excavation machine (1) according to one or more of the preceding claims, wherein said turret (5) comprises a turret frame (10) having a base portion (45) provided with first hooking elements (37, 40) arranged to be releasably constrained to a first kinematic linkage (6, 23) comprising a first arm (6) for compact machines and second hooking elements (37, 38, 39) configured to be releasably constrained to a second kinematic linkage (36, 32, 33, 31) comprising a second arm (36) for low-clearance machines.

8. Excavation machine (1) according to claim 7, wherein said first hooking elements (37, 40) comprise first attachments (37) to releasably constrain the first arm (6), said first attachments (37) being disposed at an end of said turret (5), said second hooking elements (37, 38, 39) comprising second attachments (38) to releasably constrain the second arm (36), said second attachments (38) being disposed in a back position with respect to said first attachments (37).

9. Excavation machine (1) according to one or more of the preceding claims, comprising a power lock (18) of said excavation tool (3), wherein said turret frame (10) and said power lock (18) are provided with respective coupling elements arranged to constrain the power lock (18) to the turret frame (10) in a first operating position and / or in a second operating position.

10. Excavation machine (1) according to claim 9, wherein said first operating position is defined at the rear end portion of said base machine (2), said rear end portion being the portion opposite to that towards which said arm (6, 36) extends, and said second operating position is defined at a side end portion of said base machine (2).

11. Excavation machine (1) according to one or more of claims 1 to 8, comprising a power lock (18) of said excavation tool (3) adapted to be positioned on the ground near said base machine (2) and electrically and hydraulically connected to the turret (5).

12. Excavation machine (1) according to one or more of the preceding claims, wherein said head end of said arm (6, 36) is connected to a prolongation element (47) at the free end of which there is a support element (48) for said at least one flexible suspension element (7).

13. Excavation machine (1) according to claim 12, wherein said support element (48) comprises an intermediate sheave (27), each of said branches of said flexible suspension element (7) passing over said intermediate sheave (27) after the head pulleys (19, 25, 29, 30).

14. Excavation machine (1) according to claim 13, wherein said at least one flexible suspension element (7) is only one and has a detachable section (7") intended to be disposed around said intermediate sheave (27).

15. Excavation machine (1) according to one or more of claims 1 to 12, comprising two of said flexible suspension elements (7, 7'), each of said flexible suspension elements (7, 7') being windable and unwindable on a respective drum.

16. Excavation machine (1) according to claim 15, wherein each of said flexible suspension elements (7, 7') has one end constrained to a respective drum (8A, 8B) and the opposite end constrained to a balance arm (49) the support element (48) is provided with.

17. Excavation machine (1) according to one or more of the preceding claims, comprising two blocks (26, 28) connected to said excavation tool (3), where said blocks (26, 28) make the connection between each of said branches of said flexible suspension element (7, 7') and said excavation tool (3).

18. Excavation machine according to one or more of the preceding claims, wherein said excavation tool (3) is a bucket comprising a frame to which valves acting as excavation means are fixed.

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