WO2024038150A1

WO2024038150A1 - Dipper for an excavator

Info

Publication number: WO2024038150A1
Application number: PCT/EP2023/072702
Authority: WO
Inventors: Felix HORNSTEIN
Original assignee: Kiesel Technology Gmbh
Priority date: 2022-08-18
Filing date: 2023-08-17
Publication date: 2024-02-22
Also published as: DE102022120933A1

Abstract

The invention relates to a dipper(14) for an excavator, comprising a dipper section (51) provided at the dipper end (48), provided in a dipper main section (50), comprising an attachment axis (17) provided at a dipper end (48) of the dipper section (51), on which an attachment device (21) is pivotally mounted about the attachment axis (17) with an attachment bearing point (38) of a coupling unit (33), comprising a deflector fulcrum (29) provided adjacent to the attachment axis (17) at the dipper end (48), comprising a pivot kinematics system (27), having a pivot fulcrum (35), on which a deflector (28) and a coupler (31) are mounted together, wherein the deflector (28) engages the deflector fulcrum (29) at the opposite end from the pivot fulcrum (35) and the coupler (31) engages a coupler bearing point (37) on the coupling unit (33) at the opposite end, wherein a fork-type link (20) is provided between the dipper (14) and the attachment device (21) and/or between the pivot kinematics system (27) and the attachment device (21).

Description

Stick for an excavator

The invention relates to a stick for an excavator, on which a mounting device with a coupling device can be arranged pivotably about a mounting axis on the stick.

From DE 20 2011 100 482 U1 an excavator is known which pivotally accommodates a mounting device at the free end of the stick, which is pivotally connected to a coupling device of the mounting device about a mounting axis on the stick. A swivel drive is provided on the coupling device, which in turn has a coupling for receiving a working device opposite the coupling device. To control a pivoting movement of the attachment device about the attachment axis of the handle, a pressure cylinder is provided on an upper side of the handle. A piston rod of the printing cylinder engages a swivel kinematics. This pivoting kinematics includes a coupling and a deflector, which are pivotally arranged in a common axis on which the printing cylinder engages, the deflector engaging at the opposite end in a deflecting axis of the handle and the coupling engaging at the opposite end on the coupling device. An upper side and a lower side of the handle are tapered in the direction of the cultivation axis. The design of such a handle with a connection of the attachment to the attachment axis arranged at the end of the handle enables a wide range of applications. However, there are applications in which the pivoting mobility of the attachment to the handle is not sufficient.

The invention is based on the object of creating a stick for an excavator in order to reduce a breakaway force from an attachment to a stick.

This task is solved by a stick for an excavator, in which a fork-shaped connection is provided between the stick and the attachment device and/or between the swivel kinematics and the attachment device. This fork-shaped connection enables the attachment device to be positioned closer to a attachment axis on the handle is. This fork-shaped connection also makes it possible for the attachment to be positioned closer to the base machine. This allows the distance between connecting the attachment to the handle to be reduced. This allows the effective lever arms to be shortened and leads to a reduction in the breakaway force. This can also enable improved handling and an increased pivoting range of a working device around the attachment axis at the handle end of the handle.

It is preferably provided that a distance from the attachment bearing point of the coupling device to an end face or an incline of the attachment device and/or a distance from the coupling bearing point of the coupling device to a top surface of the attachment device is equal to or smaller than 2.5 times a bolt diameter of the attachment bearing point and/ or the coupling bearing point of the coupling device. This has the advantage that the effective lever arms between the work tool and the handle are shortened. This can also reduce the breakaway force. At the same time, the process forces can also be increased.

According to a first embodiment, it is preferably provided that the fork-shaped connection between the handle and the attachment device is formed by a fork-shaped handle section pointing towards the end of the handle, which has two fork arms arranged at a distance from one another. This design of the fork-shaped handle section allows part of the attachment device to be positioned between the two fork arms for connection to the handle end.

It is preferably provided that the mounting axis and the deflector axis are provided in the fork arms of the fork-shaped handle section. As a result, a compact and shortened arrangement can be provided for accommodating the attachment device and/or the pivoting kinematics.

The fork-shaped stem section can be designed as a straight stem section. A connection can be made under a straight stem section of the handle section to the main handle section, in which the top and / or bottom of the handle section and the main handle section lie in a common plane. Alternatively, it can be provided that the fork-shaped handle section is designed to be cranked relative to the main handle section. With a cranked arrangement of the handle section relative to the main handle section, the offset handle section is oriented upwards at an angle relative to the main handle section.

In the embodiment with the fork-shaped stem section, it is preferably provided that one deflector is positioned on an inside of the fork arms and is mounted on the deflector axis in the fork arm. The coupling is preferably rod-shaped and preferably engages between two cheeks of the coupling device. This means that the pivoting range towards the top of the handle can be further increased.

According to an alternative embodiment, it is provided that the fork-shaped connection between the pivoting kinematics and the attachment device comprises a fork-shaped coupling with two coupling arms, the coupling arms being connected in an articulated manner to the coupling device. Preferably, a coupling stem can be formed opposite the coupling arms.

The pivoting kinematics, which preferably includes the fork-shaped coupling, can be provided on a fork-free handle section that is aligned with the handle end. A fork-free handle section can be understood to mean that the handle section and the main handle section form a unit and, for example, the side cheeks and/or the top and/or bottom lie in one plane. This embodiment with the fork-free handle end and the fork-shaped coupling of the swivel kinematics has the advantage that the attachment device can be shortened in the connection to the handle. This also enables an increased swivel angle. The fork-shaped coupling of the pivoting kinematics preferably engages with each coupling arm on an outside of the cheeks of the coupling device. Alternatively, the coupling arms can also be aligned to an inside of the cheeks.

When designing the fork-free handle section towards the handle end, a deflector preferably engages the deflector axis of the handle section on each outside of the handle section, with the deflector being mounted opposite the pivot axis, preferably on each outside of the paddock. This can result in an increased pivoting movement of the pivoting kinematics.

The fork-free handle section, on which the pivoting kinematics with the fork-shaped coupling is preferably provided, can be designed straight to the main handle section. An upper side and/or a lower side of the stem section and the main stem section can lie in one plane. Alternatively, the fork-free stem section can be designed to be cranked relative to the main stem section. In the case of a cranked handle section, this can be angled at an angle of less than 180° to the top of the main handle section. With regard to the straight and cranked design, reference can be made to the above statements.

Furthermore, it is preferably provided that a coupling device of the attachment device is articulated to a mounting bolt in the attachment axis of the handle section and a coupling bolt is provided on the coupling device, on which a coupling of the swivel kinematics engages, the swivel kinematics having a deflector which is on the deflector axis of the handle and the pivoting kinematics are pivotally controlled by the pressure cylinder. The coupling and the deflector of the pivoting kinematics are coordinated with one another in such a way that when the attachment device is pivoted to the top of the handle, the coupling bolt from the coupling device can be arranged adjacent to the deflector axis of the handle. By connecting the attachment to the With a bent handle, an increased swivel range can be achieved.

Furthermore, it is preferably provided that the mounting bolt and the coupling bolt of the coupling device are arranged offset in height from one another and preferably the attachment bearing point is arranged offset in the direction of a rotary drive of the attachment device. As a result, the coupling pin can lie above the rotary drive and the mounting bearing point can be offset in the direction of the rotary drive, i.e. recessed.

Furthermore, it is preferably provided that the attachment bearing point and the coupling pin of the coupling device are arranged at an angle to the attachment device, which is formed by two fictitious straight lines, the first or one fictitious straight line extending through the attachment bearing point and the coupling pin and the second or the other fictitious straight line extends offset in a plane of rotation or parallel to a plane of rotation of a rotating device of the attachment. This offset arrangement of the coupling pin and the attachment bearing point of the coupling device allows the attachment bearing point of the coupling device to be offset in the direction of the plane of rotation of the rotating device of the attachment device, which enables a reduction in the height of the attachment device relative to the handle. This increases the swivel angle range towards the underside of the handle in particular.

It is advantageously provided that the fictitious straight lines of the attachment device are provided at an angle β of 15° to 45°, preferably 25° to 35°. This in turn enables an advantageous connection of the attachment device to the cranked handle section of the handle.

It is advantageously provided that the cranked stem section lies at an angle a between two fictitious straight lines, the first or one fictitious straight line extending through the mounting axis and the deflector axis and the second or the other fictitious straight line extends through the deflector axis and a handle connection axis of the handle. This area at the end of the handle is sufficient to form the cranked handle section in order to increase the swivel angle range of the attachment.

Preferably, the cranked stem section is angled at an angle a of 15° to 45°, preferably at an angle a of 25° to 35°, towards the top of the stem. This area has proven to be advantageous for the use and connection of the attachment.

It is preferably provided that the angular range of the fictitious straight line of the attachment device and the angular range of the fictitious straight line on the cranked stem section are the same. This allows the largest swivel range or the largest opening angle to be achieved. This opening angle can be 200°, within which the attachment device can be pivoted to the cranked handle section.

Preferably, the height between the coupling pin and the mounting bearing point of the coupling device on the one hand and the height between the mounting axis on the cranked stem section and the deflector axis on the stem on the other hand are designed to be the same.

A deflection axis for the pivoting kinematics is preferably provided in the transition area between the main stem section and the cranked stem section. Alternatively, it can also be provided that the deflector axis is provided in the cranked stem section, i.e. lies outside the transition region between the main stem section and the cranked stem section. Alternatively, the deflector axis can also be provided in the handle.

Furthermore, it is preferably provided that the length of the handle section has a length of less than 20% in relation to the total length of the handle. Preferably the length of the cranked extends Handle section from the deflector axis to the free end of the cranked handle section. This cranked and short handle section can be sufficient to increase the pivoting mobility.

The invention and further advantageous embodiments and developments thereof are described and explained in more detail below using the examples shown in the drawings. The features that can be found in the description and the drawings can be used individually or in groups in any combination according to the invention. Show it :

Figure 1 shows a schematic side view of an excavator with a stick, an attachment and a working device,

Figure 2 is a schematic side view of a stick for an excavator with a cranked stick section,

Figure 3 is a perspective view of the handle according to Figure 2,

Figure 4 is a perspective view of a mounting device for connection to the handle according to Figure 2,

Figure 5 is a schematic side view of the attachment device according to Figure 4,

Figure 6 is a schematic sectional view of the attachment device along line IV-IV in Figure 4,

7 shows a perspective view of the handle according to FIG. 2 with an attachment device according to FIG. 4 in a working position, 8 shows a schematic side view of the handle according to FIG. 3 with an attachment device according to FIG. 4 in a first working position,

9 shows a schematic side view of the arrangement according to FIG. 6 in a further working position,

Figure 10 is a perspective view of an alternative embodiment of the handle to Figure 3,

11 shows a perspective view of the handle according to FIG. 9 with an attachment device according to FIG. 4 in a working position,

Figure 12 is a perspective view of an alternative embodiment of the handle to Figure 3,

13 shows a perspective view of the handle according to FIG. 11 with a mounting device according to FIG. 4 in a working position,

Figure 14 is a perspective view of an alternative embodiment of the handle to Figure 11, and

Figure 15 is a perspective view of the handle according to Figure 13 with a mounting device according to Figure 4 in a working position.

A schematic side view of an excavator 11 is shown in FIG. The excavator 11 includes a basic machine 13 with a boom 12, which is articulated to one another at the end with a stick 14. The boom 12 is moved up and down with a lifting cylinder 19. The boom 12 includes at least one stick cylinder 18 for controlling a pivoting movement of the stick 14. On the stick 14 is at least a pressure cylinder 16 is provided, through which a mounting device 21 provided on the handle 14 can be controlled. At the end of the handle 14, the attachment device 21 is pivotally mounted in a mounting axis 17. This attachment 21 can include a rotating device 22 with a rotary drive 24 and a clutch 23, in particular a quick-change clutch. The rotating device 22 includes a drive housing 66. The clutch can be rotated relative to the drive housing 66 in an axis of rotation 26 by the rotary drive 24. An interchangeable implement 25 is provided on the coupling 23. To control a pivoting movement of the attachment 21, a pivoting kinematics 27 is provided. This comprises a deflector 28, which is connected to the handle 14 in an articulated manner at one end on a deflector axis 29. Furthermore, the pivot kinematics 27 includes a coupling 31, which is connected at one end to the deflector 28 via a common pivot axis 35. At the opposite end, the coupling 31 engages a coupling device 33. This coupling device 33 is a component of the attachment device 21 or is mounted on the attachment device 21. The drive housing 66 preferably has a top surface 67 which extends at least in sections and on which the coupling device 33 is provided. The pressure cylinder 16, in particular a piston rod of the pressure cylinder 16, engages on the pivot axis 35 of the pivot kinematics 27.

A schematically enlarged side view of the handle 14 is shown in FIG. Figure 3 shows a perspective view of the handle 14 according to Figure 2.

The handle 14 has a main handle section 50. At one end of the main arm section 50 there is a arm bearing point 41, through which the arm 14 is mounted in an articulated manner to the boom arm 12. Adjacent to this is an arm cylinder axis 42, in which the arm cylinder 18 of the boom arm 12 engages. An underside 43, which is designed as a lower flange, extends from the handle bearing point 41 to the front handle end 48. Opposite, the handle 14 includes a top 45, which is designed as a top flange. At the top 45 there is a pressure cylinder bearing 46 is provided for receiving the printing cylinder 16. The top 45 and the bottom 43 are aligned at an acute angle to one another in the direction of the deflector axis 29.

The stem 14 has a cranked stem section 51. This cranked handle section 51 is provided at the handle end 48. The handle 14 includes a main handle section 50 with the handle bearing point 41 and 42 and the cranked handle section 51. The mounting axis 17 is provided in the cranked handle section 51. The cranked handle section 51 extends from the deflector axis 29 towards the top 45 of the handle 14. The offset handle section 51 is cranked upwards at an angle a of, for example, 30° to the bottom 43 of the handle 14. The angle for the bend of the handle section 21 is determined by two fictitious straight lines 52, 53. The straight line 52 extends through the mounting axis 17 and deflection axis 29 of the cranked stem section 51. The straight line 52 extends through the deflection axis 29 and preferably runs parallel to the underside 43 of the stem 14. The straight line 53 can also extend through the deflection axis 29 and the stem bearing point 41 extend.

The length of the cranked handle section 51 can be determined from the angle a and a height HS between the mounting axis 17 and the deflector axis 29. The distance between the mounting axis 17 and the deflector axis 29 includes the height HS.

The cranked handle section 51 is the same width as the main section 50 of the handle 14. With very long handles 14, the main handle section 50 can taper to the beheaded handle section 51. The width of the cranked stem section 51 and the distance between the cheeks 36 coupling device 33 are adapted to one another.

A perspective view of the attachment device 21 is shown in FIG. Figure 5 shows a schematic side view of the attachment device 21 according to Figure 4. The coupling device 33 consists of two cheeks 36 arranged at a distance from one another. The cheeks 36 can be connected to at least one connection plate 34 which extends between the cheeks 36. The at least one connection plate 34 can rest on an upper side of the rotating device 22 and can preferably be releasably attached thereto. A connection level 65 is formed between the top of the rotating device 22, to which the coupling device 33 is attached, and the coupling device 33, in particular the connection plate 34 of the coupling device 33. Each cheek 36 includes a coupling bearing point 37 and an attachment bearing point 38. The coupling bearing point 37 and the attachment bearing point 38 are arranged offset from one another at the height HK. The attachment bearing point 38 is recessed relative to the coupling bearing point 37. The attachment bearing point 38 of the coupling device 33 lies, for example, in the connection plane 65. Alternatively, the attachment bearing point 38 can also be offset in the direction of a rotation plane 39 of the rotation device 22 or lie in this rotation plane 39. The mounting bearing point 38 is offset laterally outwards relative to the mounting device 21, in particular the rotating device 22, or is assigned to an end face of the rotating device 22.

A distance HA is preferably provided between the connection level 65 of the attachment device 21 and the coupling bearing point 37, which is equal to or smaller than 2.5 times the diameter of a bearing pin of the coupling bearing point 37. The coupling bearing point 37 is preferably provided adjacent to the connection level 65. Furthermore, it can be provided that the attachment bearing point 38 is positioned at a distance HB from the attachment device 21, which is equal to or smaller than 2.5 times the diameter of a bearing pin of the attachment bearing point 38. The bearing pins of the coupling bearing point 37 and the add-on bearing point 38 are preferably of the same diameter. In particular, it is provided that the mounting bearing point 38 adjoins an end face of the rotary drive 24 or adjoins an incline 69 which is adjacent to an end face of the rotary drive 24. The distances HA and/or HB are preferably designed to be the same, which makes it possible to reduce the lever arms and thus the breakaway force between the handle and the tool is reduced. Breakaway force is understood to mean, for example, a force that is necessary to overcome static friction in a bearing and that initiates the transition to sliding friction. The breakaway force is therefore the force that is required to convert a bearing from a static to a dynamic state.

The height HK between the coupling bearing actuator 37 and the add-on bearing point 38 can be the same as the distance HA or can differ from one another.

The coupling bearing point 37 and the add-on bearing point 38 are arranged at an angle β to the plane of rotation 39, which is determined by two fictitious straight lines 56, 57. The fictitious straight line 56 extends through the coupling bearing point 37 and the add-on bearing point 38. The fictitious straight line 57 extends through the plane of rotation 39 or is aligned parallel to it. This can also lie in the at least partially formed top surface 67 of the drive housing 66 of the rotating device 22. The mounting bearing point 38 can lie on the straight line 57 or lower in the direction of the plane of rotation 39, preferably within a height formed by the straight line 57 and the plane of rotation 39. The angle β between the straight lines 56, 57 is preferably provided in a range from 15° to 60°. In particular, an angle β of 30° is provided. This angle β preferably corresponds to the angle a.

A schematic sectional view along line VI-VI according to FIG. 4 is shown in FIG. 6. The rotating device 22 has an incline 69 between the top or the connection level 65 and an end face 68 of the rotating device 22. This slope 69 can, for example, be inclined at an angle of 45° to the connection plane 65. Deviating from this, the slope 69 can also be provided at an angle to the connection plane 85. This slope 69 makes it possible in particular for the attachment bearing point 38 of the cheeks 36 to be moved closer to the rotating device 22 and/or downwards relative to the connection level 65 on the one hand. This Arrangement has the particular advantage that a reduced introduction of force from the handle 14 into the attachment device 21 is made possible, whereby shear forces acting on the coupling device 33 of the attachment device 21 during operation can be reduced.

The coupling device 33 is preferably connected to the rotating device 22 by a screw connection 83. In particular, one or more connection plates 34 rest on the top of the rotating device 22 and on the slope 69 of the rotating device 22 and are fixed in particular by the screw connection 83. This detachable arrangement of the coupling device 33 to the rotary device 22 also enables increased flexibility through a possible exchange of the coupling device 33 to the rotary drive 24 and the coupling 23.

By reducing the installation height of the attachment device 21, which can be done in particular by moving the attachment bearing point 38 into the connection level 65 or below in the direction of the rotation plane 39, the kinematics of the handle 14 and the attachment device 21 are improved to the extent that an overloading height and /or a breakaway force can be increased. This is particularly the case when the mounting bearing point 38 lies in the plane of rotation 39.

The attachment device 21 according to Figures 4 to 6 also has the advantage that a reduction in the number of hydraulic connections for controlling a working device 25 is made possible by integrating the rotary drive 24 and the clutch 23. For example, the number of connections in the coupling 23 can be reduced from five connections to three connections. Two of the connections serve a main function, namely an inlet and a return of the working fluid, in particular hydraulic oil. The third connection is intended for a so-called leakage oil. The connection or integration of the clutch 23 into the rotary drive 24 enables the hydraulic connections required for control of the rotary drive to be provided within the rotary drive 24 and/or the clutch 23 and to be permanently connected to one another. 7 shows a perspective view of the handle 14 according to FIG. 3 and the attachment device 21 according to FIG. 4 connected to it in an articulated manner. The fork-shaped connection 20 is provided between the swivel kinematics 27 and the attachment device 21. The pivoting kinematics 27 includes two deflectors 28, which are each positioned on an outside of the handle section 51 and are mounted in the deflector axis 29. Opposite, these deflectors 28 engage the pivot axis 35 of the pivot kinematics 27. The coupling 31 of the swivel kinematics 27 is fork-shaped. The paddock 31 has two coupling arms 64 pointing towards the attachment device 21. These coupling arms 64 preferably each engage on an outside of the cheek 36 of the coupling device 33. The respective ends of the coupling arms 64 are pivotally mounted on the coupling bearing point 37, preferably by a bolt. Opposite the coupling arms 64, the coupling 31 includes, for example, a coupling stem 65. This coupling stem 65 is narrower in width than the distance between the two coupling arms 64. The coupling stem 65 can include a recess so that a piston rod of the pressure cylinder 16 can be positioned in between and on the Pivot axis 35 attacks.

The height HK of the coupling bearing point 37 and the attachment bearing point 38 of the coupling device 33 advantageously corresponds to the height HS on the bent stem section 51, which is formed by the distance between the attachment axis 17 and the deflector axis 29. The cranked stem section 51 is positioned between the cheeks 36. The mounting axis 17 of the cranked handle section 51 is aligned with the mounting bearing point 38, so that they are pivotally connected to one another by a bearing pin.

The deflectors 28 are, for example, straight in this embodiment. This allows higher forces to be absorbed. This embodiment is preferably used in compact excavators or medium-sized or large excavators. The deflectors 28 are at the Embodiment according to FIGS. 8 and 9 c-shaped or arcuate. This embodiment is preferably used in mini excavators.

8 shows a schematic side view of the handle 14 with the attachment device 21 in a first pivoting or working position. In Figure 9, the handle 14 with the attachment device 21 is shown in a further pivoting or working position, different from the arrangement in Figure 7.

The handle 14 with the cranked handle section 51 makes it possible for the attachment device 21 to be pivotable relative to the fictitious straight line 53 at a pivot angle A of up to 60° towards the underside 43 of the handle 14. Due to the offset mounting bearing point 38 to the coupling bearing point 37 and the cranked stem section 51, the rotating device 22 can be positioned almost parallel or parallel to the fictitious straight line 52 with respect to its axis of rotation.

Figure 9 shows the further pivoting position of the attachment device 21 in the opposite direction to that in Figure 8. Compared to the fictitious straight line 53 through the deflector axis 29, a pivot angle B of up to 160 ° can be assumed. This pivoting position can be assumed by the cranked handle section 51. This results in a pivot angle of the attachment device 21 to the cranked handle section 51 of up to 220°.

An alternative embodiment of the handle 14 is shown in Figure 10. The handle section 51 is not aligned with the main handle section 50 in a cranked manner. Such a stem 14 is referred to as a straight stem. It is provided that an upper and/or lower side of the handle section 51 and the main handle section 50 lie in a common plane. Otherwise, the comments on the aforementioned Article 14 apply. 11 shows a perspective view of the handle 14 according to FIG. 10 and the attachment device 21 according to FIG. 4. The control of a pivoting movement of the attachment device 21 to the handle 14 takes place with a pivoting kinematics 27, which corresponds to the embodiment according to FIG. A fork-shaped paddock 31 is used. This embodiment therefore includes a fork-shaped connection 20 between the pivoting kinematics 27 and the attachment device 21.

12 shows an alternative embodiment of the handle 14 according to FIGS. 2 and 3. The handle 14 has a cranked handle section 51 to the main handle section 50. Deviating from the embodiment according to FIGS. 2 and 3, the cranked stem section 51 according to FIG. 12 is fork-shaped. The cranked stem section 51 includes two fork arms 61 which are spaced apart from one another. The deflector axle 29 and the mounting axle 17 are provided in each fork arm 61. The distance between the fork arms 61 in the area in which the deflection axis 29 is provided is preferably smaller than in the section facing the free end of the handle 48 and in which the mounting axis 17 lies. This has the advantage that the conditions for connecting the attachment device 21 to the handle 14 are analogous or the same as in the embodiment according to the handle in FIGS. 2 and 3 and in FIG. 9.

13 shows a perspective view of the handle 14 according to FIG. 12 with the attachment device 21 according to FIG. 4 in a pivoting position. The fork-shaped connection 20 is formed between the handle 14 and the attachment 21. In this embodiment, the pivoting kinematics 27 has a coupling 31, which is, for example, rod-shaped. Alternatively, it can also be provided that in this embodiment according to FIG. 12 the coupling 31 can also be designed as a fork-shaped coupling 31 with two coupling arms 64. The coupling 31 can preferably be designed as a welded construction in which two rod-shaped sheets are connected to a web, preferably also made of sheet metal, with the rod-shaped sheets both attack on the pivot axis 35 as well as on the coupling bearing point 37. Alternatively, the welded construction can also be designed as a cast construction.

An alternative embodiment of the handle 15 to FIG. 11 is shown in FIG. This embodiment differs from that in Figure 11 in that the handle section 51 is formed straight to the main handle section 50. An offset of the handle section 51 is not provided. Otherwise, the comments on Figure 12 apply.

15 shows a perspective view of the handle 14 according to FIG. 14 and the attachment device 21 according to FIG. 4 in a working position. In this embodiment, the pivoting kinematics 27 is designed analogously to that in Figure 12. Likewise, a fork-shaped coupling 31 can also be provided as an alternative in this regard.

Claims

Claims Stick for an excavator, with a stick section (51) provided on the stick end (48), which is provided on a main stick section (50), with a mounting axis (17) provided on a stick end (48) of the stick section (51), on which a mounting device (21) with a mounting bearing point (38) of a coupling device (33) is pivotally mounted about the mounting axis (17), with a deflector axis (29) provided adjacent to the mounting axis (17) at the end of the handle (48), with a pivoting kinematics (27 ), which comprises a pivot axis (35) on which a deflector (28) and a coupling (31) are mounted together, the deflector (28) being opposite the pivot axis (35) on the deflector axis (29) and the coupling (31 ) engages oppositely on a coupling bearing point (37) of the coupling device (33), characterized in that a fork-shaped connection ( 20) is provided. Handle according to claim 1, characterized in that a distance (HB) of the attachment bearing point (38) of the coupling device (33) to an end face or a slope (69) of the attachment device (21) and / or a distance (HA) of the coupling bearing point (37 ) of the coupling device (33) to a top surface (67) of the attachment device (21) a distance of equal to or smaller than a factor of 2.5 of a diameter of a bearing pin of the attachment bearing point (38) and/or the coupling bearing point (37) of the coupling device (33). Handle according to claim 1 or 2, characterized in that the fork-shaped connection (20) between the handle (14) and the attachment device (21) is formed by a fork-shaped handle section (51) pointing towards the handle end (48), which is two at a distance from one another arranged fork arms (61). Handle according to claim 3, characterized in that the mounting axle (17) and the deflector axle (29) are provided in the fork arms (61) of the fork-shaped handle section (51). Handle according to claim 3 or 4, characterized in that the fork-shaped handle section (51) is straight or cranked relative to the main handle section (50). Handle according to one of claims 3 to 5, characterized in that one deflector (28) is mounted on the inside of the fork arms (61) on the deflector axis (29), and that the coupling (31) is rod-shaped and preferably between two Cheeks (36) of the coupling device (33). Handle according to claim 1, characterized in that the fork-shaped arrangement (20) between the pivoting kinematics (27) and the attachment device (21) comprises a fork-shaped coupling (31) with two coupling arms (64, 65) which are articulated to the coupling device (33 ) are connected. Handle according to claim 7, characterized in that the fork-shaped coupling (31) engages with each coupling arm (64, 65) on an outside or inside of the cheek (36) of the coupling device (33). Handle according to claim 7 or 8, characterized in that the handle section (51) is designed as a fork-free handle section and a deflector (28) is mounted on the deflector axis (29) on each outside of the fork-free handle section (51) and the deflectors (28) are mounted on the pivot axis (35) on each outside of the paddock (31). Handle according to claim 9, characterized in that the fork-free handle section (51) is straight or offset relative to the main handle section (50). Handle according to one of the preceding claims, characterized in that the coupling device (33) is articulated with a mounting bearing point (38) on the mounting axis (17) of the handle section (51) and a coupling bearing point (37) is provided on the coupling device (33). , on which a coupling (31) of the swivel kinematics (27) engages and the attachment bearing point (38) is arranged offset relative to the coupling bearing point (37) in the direction of a rotation plane (39) of a rotating device (22) of the attachment device (21). Handle according to claim 11, characterized in that the attachment bearing point (38) is arranged offset from one another with a height (HK) relative to the coupling bearing point (37). Handle according to one of claims 11 or 12, characterized in that the attachment bearing point (38) and the coupling bearing point (37) are at an angle (ß) to a plane of rotation (39) of the rotating device (22) or parallel to the plane of rotation (39). Rotating device (22) are arranged, which results from two fictitious straight lines (56, 57), one fictitious straight line (56) extending through the coupling bearing point (37) and the add-on bearing point (38) and the other fictitious straight line (57) lies in the plane of rotation (39) or is aligned parallel to it and extends through the attachment bearing point (38). Handle according to claim 13, characterized in that the fictitious straight lines (56, 57) are arranged at an angle (ß) of 15° to 45°, preferably 25° to 35°. Handle according to one of the preceding claims, characterized in that the cranked handle section (51) is arranged at an angle (a) to an underside (43) of the main handle section (50), and the angle (a) is represented by two fictitious straight lines (52, 53), one fictitious straight line (52) extending through the mounting axis (17) and the deflection axis (29) and the other fictitious straight line (53) extending through the deflection axis (29) and parallel to the underside (43). of the main stem section (50) or extends through the deflector axis (29) and the bearing point (41). Handle according to claim 15, characterized in that the cranked handle section (51) is at an angle (a) of 15° to 45°, preferably 25° to 35°, relative to the underside (43) or the top (45) of the main handle section ( 50) is cranked upwards. Handle according to one of claims 15 or 16, characterized in that the mounting axis (17) is arranged in the cranked handle section (51) at a distance (HS) from the deflector axis (29), and preferably the mounting axis (17) above the top ( 45) of the main handle section (50). Handle according to one of claims 11 to 17, characterized in that the height (HK) between the coupling bearing point (37) and the attachment bearing point (38) is the height (HS) between the attachment axis (17) and the deflector axis (29) of the cranked handle section (51) corresponds. Handle according to one of claims 13 to 18, characterized in that the angular range of the fictitious straight line (56, 57) of the attachment device (21) and the angular range of the fictitious straight line (52, 53) on the cranked handle section (51) are the same. Handle according to one of the preceding claims, characterized in that the deflection axis (29) in the transition area between see the main handle section (50) and the cranked handle section (51), or that the deflector axis (29) is provided in the cranked handle section (51). Handle according to one of the preceding claims, characterized in that the cranked handle section (51) has a length of less than 20% of the total length of the handle (14).