EP1911716A2 - Crane - Google Patents

Abstract

The crane has a traveling gear group (11) connected to an end carriage (10) by two connecting rods that are arranged on opposite sides of a central joint i.e. spherical joint. A pair of joints transmits compressive forces and tensile forces, where the joints have degrees of freedom for swiveling the connecting rods relative to the traveling gear group and relative to the end carriage. The rods are swiveled around a horizontal axis extending at right angles to a respective rail (1) and around a horizontal axis extending parallel to the rail.

Description

The invention relates to a crane comprising a chassis with a plurality of chassis groups for the movement along rails, each of which has at least two wheels rotatably mounted on a subframe and spaced apart in the longitudinal direction of the respective rail and connected to a head carrier of the crane via a central joint, which has at least degrees of freedom for rotating the chassis group relative to the head support about a vertical axis and for pivoting the chassis group relative to the head support about a horizontal axis perpendicular to the rails.

Landing gears of cranes movable on rails, in particular gantry cranes or overhead cranes, comprise at least two landing gear groups, each having at least one wheel for moving the crane and of which some or all are equipped with at least one drive motor for moving the crane. For example, a landing gear group is arranged on each of the four legs of a gantry crane.

Especially with heavy cranes whose suspension groups have two or more wheels, an exact alignment of the axles of the wheels relative to the rails for low wear is essential. Here, the trolleys themselves can be made both with respect to the axial positions and the position of the tracking means with very high accuracy. The chassis groups can be measured in the assembled state. Measurement results from practice show that the tolerances specified by the relevant standards and regulations are usually well undercut.

In a conventional embodiment of a crane whose chassis groups each have at least two or more spaced apart in the longitudinal direction of the respective rail wheels, the individual chassis groups with only one degree of freedom, namely a pivot about a horizontal axis transverse to the rails axis with a head support of the steel structure connected to the crane. Here, the pivot axis of the respective chassis group receiving holes in the head carrier must be very accurate, especially with regard to the axial position transverse to the road. These holes are interfaces between the mechanical engineering of the chassis group and the steel structure of the crane scaffolding, which have often proven to be problematic in practice. Among other things, an inclination of the axes can also occur due to solar radiation, which heats the head carrier unevenly, as a result of which the axial positions change. Also, horizontal forces resulting from skew, wind and inertial forces are taken over only by a certain number of wheels. In such multi-wheel chassis are thus the horizontal forces, which also must be absorbed by the rail construction, unfavorably large. The occurring axis deviations and the unfavorable distribution of horizontal forces lead to suspension restrictions and thus to increased wear of the tracking means, the wheel treads and the rails.

To reduce wear already constructions are known in which an additional degree of freedom is provided for the articulation of the chassis group on the head support, namely a rotation about a vertical axis. The trolleys are thus without any distortion compared to the stiff and inaccurate steel construction of the crane, for example gantry crane. External forces due to temperature differences and deformations no longer affect the driving geometry. Horizontal forces are transmitted to virtually all trackers on the rail. The skewing behavior is significantly improved or skew on cranes with synchronization devices can be excluded.

To form the connection between the chassis group and the head carrier with an additional twistability about a vertical axis different constructions have already become known:

A construction using a ball or roller slewing ring is technically perfect, but has a very large width and is very unfavorable in terms of cost. The use of a likewise already known sliding bearing with an additional counter-holder for receiving tilting forces has the disadvantage that very large rotational resistances must be overcome. The bearing forces can be, for example, 150 t or more. Due to the large tilting forces, especially in relieved cranial corners, in addition very elaborate countermounts are provided.

Furthermore, for this purpose, the installation of a Achsialkugellagers has become known with additional counter bearing. In this case, it is necessary to pretension the main bearing with very high pretensioning forces via the counterbearing so that a one-sided lifting of the main bearing is not possible. Should the main bearing only slightly lift, the entire vertical force shifts to one or a few rolling elements, which would lead to the destruction of the bearing. Disadvantages of this construction are u.a. the risk of a change in the preload forces, e.g. due to subsidence during crane operating time, the loads on the balls and the raceway and the costly construction which occur practically always at the same point due to the very slight movement of the bearing.

In another known construction, a central joint in the form of a spherical thrust bearing is provided for connecting the chassis group with the head carrier, which receives the support force. The tilting forces resulting from the horizontal forces transverse to the rail are absorbed by tie rods which are arranged on both sides of the central joint between the head support and the landing gear group. The disadvantage here is, inter alia, that resulting from the tilting moment high bearing forces, since the tie rods can only absorb tensile forces.

The object of the invention is to provide a connection of the chassis groups of the crane chassis to the head carrier, wherein in an advantageous power transmission, a cost-effective design is achieved. According to the invention, this is achieved by a crane having the features of claim 1.

The central joint is formed according to the invention in the vertical direction as a floating bearing, i. no vertical forces are transmitted by him. Vertical compressive and tensile forces are thus transmitted exclusively via the two handlebars, which are each connected on the one hand to the chassis group and on the other hand to the head carrier by superimposed joints. Preferably, these joints are in the form of spherical joints. Since the mobility with respect to the aligned parallel to the rail axis must be very small, it would for example also conceivable and possible to form the degree of freedom with respect to this lying parallel to the rail axis by a corresponding game of an axis perpendicular to the rail axis pivotable bearing or plain bearing ,

In a preferred embodiment of the invention, the central joint is in the form of a spherical joint. In principle conceivable and possible would be, for example, the training with a first part of the joint, which has only one degree of freedom for pivoting about an axis perpendicular to the rail, and a second partial joint, which has only one degree of freedom for pivoting about a vertical axis.

A crane according to the invention can be designed, for example, in the form of a gantry crane. A training in the form of a bridge crane is conceivable and possible, for example.

Fig. 1

und 2 eine Vorderansicht und Draufsicht eines Krans gemäß der Erfindung, stark schematisiert und vereinfacht;

Fig. 3

eine Seitenansicht (Blickrichtung A in Fig. 1) einer mit einem Kopfträger verbundenen Fahrwerksgruppe;

Fig. 4

eine Schrägsicht der mit dem Kopfträger verbundenen oberen Schwinge der Fahrwerksgruppe;

Fig. 5

eine Seitenansicht der Teile von Fig. 4;

Fig. 6

einen Schnitt entlang der Linie B-B von Fig. 5;

Fig. 7

eine schematische Darstellung einer weiteren Ausführungsform der Erfindung in Seitenansicht;

Fig. 8

eine schematische Vorderansicht der Ausführungsform von Fig. 7 (Teile des Fahrwerks sind hierbei der Übersichtlichkeit halber weggelassen).

Further advantages and details of the invention are explained below with reference to the accompanying drawings. In this show:

Fig. 1

and Figure 2 is a front and top view of a crane according to the invention, highly schematic and simplified;

Fig. 3

a side view (viewing direction A in Figure 1) connected to a head carrier chassis group.

Fig. 4

an oblique view of the connected to the head support upper rocker of the chassis group;

Fig. 5

a side view of the parts of Fig. 4;

Fig. 6

a section along the line BB of Fig. 5;

Fig. 7

a schematic representation of another embodiment of the invention in side view;

Fig. 8

a schematic front view of the embodiment of Fig. 7 (parts of the chassis are hereby omitted for clarity).

An embodiment of the invention is shown in the figures. The crane is designed in the form of a gantry crane, which is mounted on one of two spaced-apart rails 1 formed roadway is movable. Such a gantry crane usually has four legs 2, 3, 4, 5. Also constructions with three legs are known. Furthermore, two supports can be provided. The legs 2 - 5 or supports support the cross member 6 or 7, along which a trolley 8 is movable or which are provided with a different type of movable or fixed lifting device. In the case of training with two or more cross members 6, 7 run between these connection carrier. 9

At the lower ends of the arranged on a respective side of the portal legs 2, 3; 4, 5, a connecting this head carrier 10 is attached. Such a head carrier 10 is also referred to as a "chassis carrier" or "moving beam". The head carrier 10 serve to connect the steel structure of the crane with the individual chassis groups 11 of the crane chassis. Below each of the legs 2 - 5, such a chassis group 1 is arranged.

It would also be conceivable and possible, for example, to provide a separate head carrier 10 for each leg 2-5. Pro rail 1 are preferably at least two spaced apart in the longitudinal direction of the rail 1 chassis groups 11 are present. An arrangement below a respective leg 2 - 5 is preferred.

In the exemplary embodiment shown, a respective chassis group 11 has eight wheels 12 which are spaced apart from one another in the longitudinal direction of the rails 1. The axes 13 of the wheels 12 are aligned at right angles to the rails 1. A respective wheel 12 may have two spaced apart in the transverse direction of the rail 1 connected by an axis 13 flanges 14, 15, as indicated schematically in Fig. 1.

In each case two longitudinally of the rails one behind the other wheels 12 are rotatably mounted on a subframe 16. In the illustrated embodiment, four subordinate in the longitudinal direction of the rails subframe 16 per suspension group are thus available.

In each case two in the longitudinal direction of the rails one behind the other subframe 16 are connected to a common rocker 17. In the embodiment shown thus two spaced apart in the longitudinal direction of the rails 1 wings 17 are present. The subframe 16 are pivotally connected to the rockers 17 about horizontal, perpendicular to the rails axes 18.

The two rockers 17 are connected to a common rocker 19, wherein they are each pivotable relative to the rocker 19 about a horizontal, perpendicular to the rail 1 axis 20.

To move the crane along the rails 1 are drive motors 21, which drive the respective wheels 12. Depending on the application, more or fewer such drive motors 21 may be present.

The respective head carrier 10 is connected to the respective chassis group 11 in a manner such that the chassis group 11 is pivotable relative to the head carrier 10 about a horizontal, at right angles to the respective rail 1 axis and is rotatable about a vertical axis. For this purpose, a connecting device is provided, which has a central joint 22. This has at least the following degrees of freedom: a degree of freedom for rotating the chassis group 11 relative to the head carrier 10 about a vertical axis 23 and a degree of freedom for pivoting the chassis group 11 relative to the head carrier 10 about a horizontal, in particular perpendicular to the respective rail 1 lying horizontal axis 24th

These degrees of freedom are formed in the embodiment shown by the formation of the central joint 22 in the form of a spherical joint or ball joint. Here, the central joint 22 comprises a bearing pin 25 connected to the rocker 19, a bearing bush 26 connected to the head support 10, an inner ring 27 arranged on the bearing journal 25 with a spherical or spherical outer surface and an outer ring 28 arranged in the bearing bush 26 with a spherical or spherical segment-shaped inner surface which cooperates with the spherical outer surface of the inner ring 27. The joint could also be arranged "reversed", ie the bearing pin 25 with the head carrier 10 and the bearing bush 26 connected to the rocker 19.

The central joint 22 is formed in the vertical direction as a floating bearing, i. has a game in this direction in the assembled state. Thus, no vertical forces are transmitted from this central joint 22. By contrast, forces acting in the horizontal direction are transmitted, both in the direction of the respective rail 1 and at right angles thereto.

Furthermore, a respective connecting device between the respective head carrier 10 and the respective chassis group 11 comprises two arms 29, 30, which are arranged on both sides of the central joint 22 in the direction at right angles to the rail 1. Each of the two links 29, 30 is hinged to both the head carrier 10 and the rocker 19. These superimposed joints 31, 32 of the links 29, 30 are in this case designed such that both pressure and tensile forces between the respective head support 10 and the respective chassis group 11 can be transmitted via the links 29, 30. Here, these joints 31, 32 have at least the following degrees of freedom: a degree of freedom for pivoting the respective link 29, 30 both relative to the head support 10 and to the rocker 19 about an axis 33 perpendicular to the respective rail 1 and a degree of freedom for pivoting the respective Handlebar 29, 30 both with respect to the head support 10 and with respect to the chassis group 11 about a horizontal axis 34 lying parallel to the respective rail 1.

In the embodiment shown, the joints 31, 32 are in this case in the form of spherical joints or ball joints. At the head support 10 and on the rocker 19, a bearing pin 35 is held, on which an inner ring 36 is arranged with a spherical or ball-shaped outer surface. An outer ring 37 with a spherical or spherical section-shaped Inner surface which cooperates with the spherical outer surface of the inner ring 36 is disposed in a respective bore of the handlebar 29, 30.

Of the links 29, 30 thus all occurring vertical forces are transmitted. These result, on the one hand, from the weight of the crane construction and, on the other, from tilting moments, which in each case cause pairs of forces of tensile and compressive forces. However, horizontal forces are not transmitted by the links 29, 30, these are transmitted from the central joint 22, as already mentioned.

In a zero position shown in the figures of a respective chassis group 11 with respect to a rotation about the vertical axis 23 are the two joints 31, 32 of a respective arm 29, 30 exactly vertically above the other. Preferably, the links 29, 30 are straight and their longitudinal axes are aligned in the zero position in the vertical direction. By a rotation about the vertical axis 23 starting from this zero position, there is a certain inclination of the handlebars 29, 30. The joints 31, 32 of a respective arm 29, 30 are thus no longer exactly one above the other vertically. The required angles of rotation about the vertical axis 23 and thus the deviations from the vertical orientation of the joints 31, 32 are very small. In conventional applications, the connecting lines between the superimposed hinges 31, 32 in all angular positions of the occurring angular range of rotation about the vertical axis 23 are inclined less than 5 °, preferably less than 3 ° with respect to the vertical. In practice, this angle is usually less than 1 °.

In the event of a deviation from the zero position, furthermore, a force component acting around the vertical axis 23 occurs due to the weight of the crane, which increases with increasing deviation from the zero position and is transmitted to the rails 1 via the wheels 12.

Furthermore, a deviation from the zero position results in a reduction of the vertical play in the central joint 22, depending on the angle of rotation about the vertical axis 23. The vertical play in the central joint is dimensioned so that it reaches the maximum intended angle of rotation about the vertical axis 23 remains.

Upon pivoting of the landing gear group 11 about the horizontal axis 24 of the central joint 22, the links 29, 30 pivot about the horizontal axes 33 of the joints 31, 32. The horizontal axes 33 of the joints 31, 32 are parallel to the horizontal axis 24 of the central Joint 22.

For example, the respective chassis group 11 can be rotated relative to the respective head carrier 10 about the vertical axis 23 by at least 1 °.

For example, the respective chassis group 11 relative to the respective head support 10 about the right angle to the rail 1 horizontal axis 24 of the central joint 22 by at least 5 ° be pivoted.

For example, a respective link 29, 30 relative to the respective rocker 19 about the right angle to the rail 1 horizontal axis 33 of the joint 32 to be pivoted by at least 3 °.

For example, a respective link 29, 30 relative to the respective rocker 19 about the horizontal axis 34 of the joint 32 lying parallel to the rail 1 can be pivoted by at least 1 °.

For example, a respective link 29, 30 relative to the respective head support 10 about the right angle to the rail 1 horizontal axis 33 of the joint 31 to be pivoted by at least 3 °.

For example, a respective link 29, 30 relative to the respective head support 10 about the horizontal axis 34 of the joint 31 lying parallel to the rail 1 can be pivoted by at least 1 °.

A landing gear assembly according to the invention may also include more or fewer than eight spaced wheels 12 in the direction of travel, wherein at least two spaced apart in the longitudinal direction of the respective rail, on a common subframe 16 rotatably mounted wheels are present.

In the case of the formation of the chassis group with only one subframe, the central joint 22 may be arranged directly between this subframe and the head carrier and the lower joints 32 of the handlebars 29, 30 may also be arranged directly on the subframe.

For example, in a chassis with four consecutively arranged in the direction of travel wheels 12 two wheels can be rotatably mounted on a respective subframe and the subframe be connected in the manner described with a rocker 17. The central joint 22 could in this case be arranged directly between the head carrier 10 and this rocker and the lower joints 32 of the links 29, 30 directly between the links 29, 30 and this rocker.

Another embodiment of the invention is shown schematically in FIGS. 7 and 8. The differences from the previously described embodiment will be explained below. Incidentally, the training may be the same or analogous as previously described.

In contrast to the embodiment shown in FIGS. 1 to 6, which shows a "standing" mounting of the head carrier 10 on the chassis group 11, it is in the embodiment of FIGS. 7 and 8 is a "hanging" storage. That is, in the embodiment shown in FIGS. 1 to 6, the handlebars 29, 30, at least without acting on the crane external forces and in a central position of the lifting device of the crane only loaded on pressure, while the load is carried out in the embodiment of FIGS. 7 and 8 to train. Here, for a respective link 29, 30, the joint 31, via which the articulation on the head carrier 10 takes place below the joint 32, via which the articulation of the chassis group 11 takes place (in the embodiment according to FIGS. 1 to 6, however, are the joints 31st for connection to the head carrier 10 above the joints 32 for connection to the landing gear group 11).

For articulation of the links 29, 30 on the head carrier 10, this downwardly projecting connecting portions 38. On both sides of a part of the chassis group 11, here the rocker 17, such a connecting portion 38 extends downwards. The connecting portions 38 each carry a joint 31 for articulation of the respective link 29, 30th

The connecting sections 38 may, for example, be U-shaped as shown, having two vertical legs 38a, 38b spaced from each other in the longitudinal direction of the rail 1, extending from an overlying portion 39 of the head carrier 10 and at their lower ends by a horizontal web 38c connected to each other. At this web 38 c, the joint 31 is attached. Other embodiments of the connecting portions 38 may be provided. For example, these may also be continuous plate-shaped.

In Fig. 7 and 8, the chassis group 11 is shown with four spaced apart in the direction of travel wheels 12, wherein two wheels 12 are rotatably mounted on a common subframe 16 and the two subframe 16 are pivotally connected to a rocker 17 (in an analogous manner in the previously described embodiment). Also, for example, an education with eight wheels as shown in the embodiment of FIGS. 1 to 6, could be provided. Also, a different number of wheels 12 could be provided, in turn, at least two spaced apart in the direction of travel, on a common subframe 16 rotatably mounted wheels 12 are present.

What has been described in the description of the embodiment shown in FIGS. 1 to 6 for the joints 31, 32 and central joint 22, in particular with regard to the degrees of freedom and possible angles of rotation of these joints, also applies to this embodiment.

In accordance with the invention, for example, the chassis groups of a bridge crane could be connected to a head carrier of the steel structure of the crane.

Legend to the reference numbers:

1

rail

2

leg

3

leg

4

leg

5

leg

6

crossbeam

7

crossbeam

8th

trolley

9

connection support

10

endcarriages

11

LG group

12

wheel

13

axis

14

flange

15

flange

16

subframe

17

wing

18

axis

19

wing

20

axis

21

drive motor

22

central joint

23

vertical axis

24

horizontal axis

25

pivot

26

bearing bush

27

inner ring

28

outer ring

29

handlebars

30

handlebars

31

joint

32

joint

33

horizontal axis

34

horizontal axis

35

pivot

36

inner ring

37

outer ring

38

connecting portion

38a

leg

38b

leg

38c

web

39

section

Claims (7)

Crane, comprising for traveling along rails (1) a chassis with several chassis groups (11), each having at least two in the longitudinal direction of the respective rail (1) spaced apart on a subframe (16) rotatably mounted wheels (12) and with a head carrier (10) of the crane via a central joint (22) are connected, which at least degrees of freedom for rotation of the chassis group (11) relative to the head support (10) about a vertical axis (23) and for pivoting the chassis group (11) relative to the Head carrier (10) has a horizontal axis (24) lying at right angles to the rails (1), characterized in that the central joint (22) is designed as a floating bearing in the vertical direction, only horizontal forces being transferable from this central joint (22) are, and that a respective landing gear group (11) with a respective head carrier (10) further via two links (29, 30) is connected in the transverse direction de Seen on the respective rail (1) seen on opposite sides of the central joint (22) are arranged and on the one hand with the landing gear group (11) on the other hand to the head support (10) by superimposed joints (31, 32) are connected, of which both pressure - As well as tensile forces are transferable and the at least degrees of freedom for pivoting the links (29, 30) relative to the chassis group (11) or relative to the head support (10) about a right angle to the respective rail (1) lying horizontal axis (33) and have a horizontal axis (34) lying parallel to the respective rail (1). Crane according to claim 1, characterized in that the central joint (22) is in the form of a spherical joint. Crane according to claim 1 or 2, characterized in that the two joints (31, 32) of a respective link (29, 30) in a zero position of the pivoting of the central joint (22) about the vertical axis (23) lie vertically one above the other. Crane according to one of claims 1 to 3, characterized in that the two joints (31, 32) of a respective link (29, 30) in all positions of the pivoting of the central joint (22) about the vertical axis (23) relative to a vertical superimposed position have a deviation of less than 5 °, preferably less than 3 °. Crane according to one of claims 1 to 4, characterized in that the handlebars (29, 30) are straight. Crane according to one of claims 1 to 5, characterized in that the joints (31, 32), with which the links (29, 30) with the respective chassis group (11) and the respective head carrier (10) are connected, in the form of spherical joints are formed. Crane according to one of claims 1 to 6, characterized in that the handlebars (29, 30) via their lower joints (32) on a rocker (19, 17) are articulated directly or via at least one further rocker (17) of Passenger stools (16) is worn, or that the links (29, 30) via their lower joints (32) on the respective subframe (16) are articulated.

Images