Abstract:
The invention relates to a crane having an undercarriage with a swivel connection and having a superstructure rotatably supported thereon via the swivel connection and comprising at least one boom system arranged at said superstructure and luffable about a luffing axis or a self-climbing tower slewing crane rotatably supported thereon via the swivel connection. In accordance with the invention, the undercarriage has a pot as a central component which, on the one hand, receives the swivel connection. Furthermore, however, the pivotable supports can also be pivotally connected to it. Side members are present at mutually oppositely disposed sides and at least one traveling gear can respectively connected to them with at least one degree of freedom.

Description:
CROSS REFERENCE TO RELATED APPLICATIONS 
     This application claims priority to German Patent Application No. 10 2013 021 916.7, entitled “Crane,” filed Dec. 20, 2013, which is hereby incorporated by reference in its entirety for all purposes. 
     TECHNICAL FIELD 
     The invention relates to a crane having an undercarriage with a swivel connection and having a superstructure rotatably supported thereon via the swivel connection and comprising at least one boom system arranged at said superstructure and luffable about a luffing axis or a self-climbing tower slewing crane rotatably supported thereon via the swivel connection. 
     BACKGROUND AND SUMMARY 
     There are various forms of cranes which can be divided as follows into three types, for example. The first type is that of mobile cranes which travel independently on the road. The traveling gears of the mobile cranes are raised from the ground with a large support at the construction site so that a large support base is produced with tilt edges which lie far apart. The bearing pressure under these supports is distributed almost homogeneously. 
     A further crane type is the crawler-mounted crane which has to be moved as a separate transport product on the road. The crawler-mounted crane can, however, move independently on the construction site. An inhomogeneous distribution of the ground pressure is produced beneath the base plate of the crawler. 
     Finally, as the third crane type, there is the so-called pedestal crane. This is also moved as transport product on the road. This pedestal crane is stationary at the construction site. It also has to be set up each time at every deployment location at the construction site. 
     Each of the aforesaid three types has advantages and disadvantages. 
     A mobile crane which has a modular design is already known from DE 10 2008 047 737, A1. It includes a platform module, an equipping module and a drive module as well as a support module. The modules can each be assembled and dismantled again. 
     A crane is known from DE 20 2010 002 947, U1, which positions a single-axle all-terrain dolly beneath the boom for travelling. The single-axle all-terrain dolly takes up the head weight of the boom. 
     It is the object of the invention to provide a mixed form of the initially named different crane types in which the advantages are utilized and the existing disadvantages are avoided as much as possible. 
     This object is solved in accordance with the invention by a crane in accordance with this disclosure. A crane is provided having an undercarriage with a swivel connection and having a superstructure rotatably supported thereon via the swivel connection and comprising at least one boom system arranged at said superstructure and luffable about a luffing axis or a self-climbing tower slewing crane rotatably supported thereon via the swivel connection. In accordance with the invention, the undercarriage has a pot as a central component which, on the one hand, receives the swivel connection. Furthermore, however, the pivotable supports can also be pivotally connected to it. Side members are present at mutually oppositely disposed sides and at least one traveling gear can respectively be connected to them with at least one degree of freedom. 
     A number of advantages of the initially named crane types can be realized with this conceptually newly designed crane. The new undercarriage concept can thus be set up on the construction site as a stationary base of a very stable design. After a corresponding setup, the traveling gear can be separated. After the separation of the traveling gear, it can, for example, take over another task at the construction site, for example in the form of a heavy load transporter. 
     On the other hand, the pot can selectively be connected to different traveling gears via the corresponding side members and the connections provided thereat to move the crane. On the one hand, it could be a track traveling gear which is advantageous for the movement of the crane on the construction site. On other hand, however, a wheel traveling gear can also be used. 
     Particular advantages of the invention result from other aspects of this disclosure. 
     Both the support and the side members can advantageously be releasably connected to the pot. This is in particular indicated with very large cranes in which the individual parts also have to be transported separately from one another. 
     In the same manner, it is advantageous that the side members are releasably connected to the traveling gears. This allows the replacement of the traveling gears or the decoupling of the traveling gears during stationary crane operation. 
     In accordance with another advantageous embodiment of the invention, the pot can be divided into two, with each part of the pot being releasably connected to a traveling gear via side members. 
     After their connection, the two parts of the divided pot form the swivel connection together with a revolving deck frame. 
     The releasable connection between the side members and the traveling gears advantageously takes place in that transverse struts having sliding shoes, rolls and/or rollers are arranged at the side members and cooperate with complementary ring elements at the traveling gear side such that the traveling gears can rotate beneath the side members. 
     The ring elements can advantageously be arranged on the traveling gear via a controlled three-point support or four-point support, with these advantageously comprising three hydraulic cylinders via which the ring element can be held in a horizontal position largely independently of the position of the traveling gear. A safe moving of the crane can hereby also be made possible off-road. This is in particular important when the crane is moved over a comparatively bumpy travel path off-road with comparatively widely spaced apart traveling gears. 
     It is of particular advantage if the traveling gears are configured in the form of modular heavy load transport vehicles. They can be driven or they can be not driven, with in particular the not-driven heavy load transport vehicles also being able to be adjustable in their widths in a manner known per se. It is very particularly advantageous, especially for transport on the construction site, that crawler travel gears are used as traveling gears. The advantage of a crawler traveling gear here is that it exerts a much more uniform bearing pressure on the ground than a comparable wheel traveling gear would. The crawler traveling gear is also of particular advantage with respect to the problem of the maximum axial load distribution on the travel path. The axial load of the wheel traveling gear namely has to be considered with corresponding wheel traveling gears. This very easily exceeds the permitted axial load (of, for example, 12, metric tons), in particular on the transport of large cranes. 
     The boom can particularly advantageously be supported via a separate additional traveling gear during movement. In this respect, the traveling gear can be coupled via correspondingly movable connection elements. 
     It is of advantage with respect to a particularly stable support if the supports are configured as lattice constructions which in this respect are also advantageously substantially designed with the same height as the pot itself. The supports configured as lattice designs have a particularly high stiffness. If they are designed exactly as high as the pot, the maximum transport height is also utilized so that in especially stable supports can in particular also be provided for the use of large cranes. 
     In accordance with a further advantageous embodiment of the invention, a control is provided for the common control of the traveling gears. Different traveling gear strategies can hereby be realized. All traveling gears can thus be orientated toward a common steering center, for example. Alternatively, two traveling gears can also be set to a common steering center beneath the ring elements, while the further traveling gear is steered separately beneath the boom. 
     Further features, details and advantages of the invention will be explained in more detail with reference to an embodiment shown in the drawing. 
    
    
     
       BRIEF DESCRIPTION OF THE FIGURES 
         FIG. 1  shows a side view of a crane in accordance with the invention in accordance with its first embodiment. 
         FIG. 2  shows a plan view of a part of the crane in accordance with  FIG. 1 . 
         FIG. 3  shows a side view of a crane in accordance with the invention in accordance with a second embodiment. 
         FIG. 4  shows a partial plan view of the crane in accordance with  FIG. 3 . 
         FIG. 5  shows a schematic representation of a part of the crane in accordance with  FIG. 1 . 
         FIG. 6A  shows a further schematic representation of a further detail of the crane in accordance with  FIG. 3 . 
         FIG. 6B  shows a sectional view through the ring element shown in  FIG. 6A . 
         FIGS. 7A, 7B, and 7C  show different representations of the traveling gear. 
         FIGS. 8A, 8B, and 8C  show a schematic representation for illustrating the movement of the crane on corresponding travel paths. 
         FIG. 9  shows a schematic representation for illustrating a specific travel state of the crane in accordance with the invention. 
         FIG. 10  shows a side view of a crane in accordance with the invention in accordance with a third embodiment. 
         FIG. 11  shows a plan view of a part of the crane in accordance with  FIG. 10 . 
         FIG. 12  shows a side view of a crane in accordance with the invention in accordance with a fourth embodiment. 
         FIG. 13  shows the undercarriage of the fourth embodiment variant, 
         FIG. 14  shows the undercarriage in accordance with  FIG. 13  during operation on a gradient. 
         FIG. 15  shows a plan view of an undercarriage in accordance with  FIG. 13  with traveled out supports. 
         FIG. 16  shows a perspective representation of an embodiment of a traveling gear. 
         FIG. 17  shows a detail of the traveling gear in accordance with  FIG. 16  for explaining the realized three-point support. 
     
    
    
     DETAILED DESCRIPTION 
     In the embodiment of the crane  100  in accordance with the invention shown in  FIG. 1 , the superstructure  1  of a large crane is shown which is connected to an undercarriage  5  via a swivel connection  2 . The superstructure  1  has a luffable boom  3 . A luffing cabling  4  is provided as a drive for luffing the boom  3 . The luffing cabling  4  in accordance with the example shown here has a guying frame  41 , a derrick boom  42 , a fixed guying  43 , which comprises different stay poles  43 ′, and an adjustment block  44 . The boom  3 , which is not shown in the illustration in accordance with  FIG. 1 , can be a lattice boom or a telescopic boom, such as is already known in the prior art. As a telescopic boom, it could comprise both a sheet metal construction and a lattice construction. 
     The superstructure  1  is connected to an undercarriage  5 . The structure of the undercarriage  5  is based on a completely novel concept. The interface between the superstructure  1  and the undercarriage  5  is a central pot  51 . The pot  51  is the central element which forwards the forces from the superstructure  1  into the remaining undercarriage  5  and finally into the ground on which the crane is set up. 
     Supports  52  (cf.  FIG. 2 ) are pivotably connected to the pot  51 . The supports  52  can be pivotably connected to the pot  51  as is known per se from the mobile crane field. Such a pivotable design of the supports  52  is shown in the embodiment of  FIGS. 1 and 2 . Pivot drives  53  in the form of hydraulic cylinders are provided here. The function of the support of the undercarriage corresponds to the known support such as is already sufficiently known from the mobile crane field. 
     To be able to move the crane  100  on the construction site, an external traveling gear  60  is provided. In general, the traveling gear  60  can be configured as a wheel traveling gear, as shown here in the embodiment in accordance with  FIGS. 1 and 2 , or also as a crawler traveling gear, such as shown in the embodiment in accordance with  FIGS. 3 and 4 . 
     It is of particular advantage if a standard traveling gear having its own drive units  61  is provided. If the supports  52  are pivoted outwardly, the traveling gear  60  can, as shown in the Figures, travel through the supports  52  and can be positioned in a connection position with the pot  51 . 
     Side members  54  which are disposed opposite one another with respect to the pot  51  are attached to the pot  51 . This can in particular be seen from  FIG. 2  or also from  FIG. 4 . The side members  54  provide a sufficient spacing so that at least two traveling gears  60  can move the crane  100  on the construction site. The side members  54  can in another respect each be connected in a boltable manner to the pot  51 . The connection of the side members to the traveling gears takes place over a plurality of degrees of freedom, where possible. This is necessary since a moving of the crane admittedly also frequently takes place over travel paths  70  on the construction site, but these travel paths are nevertheless also bumpy so that corresponding measures have to be taken to avoid a tilting of the crane during the transport. 
     For this purpose, transverse struts  55  are attached to the side members  54  and are connected to sliding shoes  56  (cf.  FIG. 5 ). A ring element  57  is attached to the traveling gear  60  as a mating connection element. The corresponding sliding shoes  56  of the transverse struts  55  slide in the ring element  57 . Each traveling gear  60  can thus rotate beneath the side member  54 . As shown with reference to  FIGS. 8A, 8B, and 8C , this is necessary during cornering. Compensation for the ground bumps furthermore has to be provided. For this purpose, the ring element  57  is arranged on the traveling gear  60  via a controlled three-point support  58 . This three-point support can comprise three main cylinders  58  which hold the ring element  57  in a horizontal plane which is anyway independent of the position of the traveling gear  60  in restricted regions (cf.  FIGS. 6A, 6B , and  FIG. 8B , in which the ring element is shown). A section through the ring element  57  can be seen from  FIG. 6B . 
     If modular heavy load transport vehicles are used as the traveling gear  60 , these driven heavy load transport vehicles  60 ″ and  60 ″″ and non-driven heavy load transport vehicles  60 ′ and  60 ′″ can be used. The non-driven heavy load transport vehicles do not have any structure for the drive units  61  and can thus pivot beneath the crane  100  on cornering. The non-driven heavy load transport vehicles can also be adjustable in their widths. This is shown by way of example in  FIGS. 7A, 7B, and 7C . In accordance with  FIG. 7A , the width of the non-driven heavy load transport vehicle can thus be increased from 4, meters to 4.5, meters. This is in turn advantageous since the tilt edges  62  can hereby be pushed apart. The tilt edges are formed by the pivot axles of the wheel sets. Each wheel set is tiltable seen on its own. 
     In  FIG. 7B , the non-driven heavy load transport vehicle  60  is shown in a pushed together position in which the width only amounts to 4, meters. In  FIG. 7C , in contrast, it is shown in a pushed apart position in which the width in the embodiment shown here amounts to 4.5, meters. The displacement device  63  for adjusting the width of the heavy load transport vehicle is generally already known from the prior art so that it will not be explained in detail again here. 
     To move the crane  100 , it is dismantled until it has reached a movable weight and a movable vertical center of gravity. The traveling gears  60  are positioned beneath the sliding shoes  56 . Support cylinders  521 , which are provided at the supports  52 , are traveled in and the sliding shoes are received in the ring elements  57 . If a small travel width is to be reached, the supports  62  can be pivoted inwardly. Alternatively, the supports  52  can, however, also be fully or partially pivoted outwardly, with the support plates  522  advantageously only being raised a little above the ground. If the crane should now reach its tilting range, the supports  52  can come into engagement and prevent a further tilting. This is particularly advantageous when the support  52  is fully inwardly pivoted and the support plates  522  are thus also located above the travel path  50  which likewise has a greater firmness than the ground located next to the travel path. If the support plates  522  are used due to a tilt movement, the support plates  522  are supported on the highly compacted travel path, that is a travel path which can carry more weight. A sinking of the support plates  522  is not to be expected here. 
     In the embodiment shown here, the supports  52  are configured as a lattice support structure. They are configured to be equally high as the pot  51  vertically. They hereby reach a very high stiffness and the supports can be optimally adapted to the transport window available on the road. 
     On moving the crane  100 , a further traveling gear  60  can be attached beneath the boom  3 , as is shown with reference to the embodiment in accordance with  FIGS. 10 and 11 . For this purpose, connection elements  31  can be provided at the boom  3 . They are connected to corresponding mating connection elements  63 . The connection allows the required degrees of freedom. The further traveling gear  60  can take up the head weight of the boom  3 . The support weight of the boom  3  is introduced into the superstructure via the boom pivot axle  32 . To achieve equilibrium here, a little more ballast  11  as to remain on the superstructure  1  in this case. This is advantageously coordinated such that the center of gravity  101  is arranged within the tilt edges  62 ; the center of gravity  101  is particularly advantageously located within the swivel connection  2 . The luffing cabling  4  should not be fully tautened on the moving of the crane. If the luffing cabling were tautened, this could already produce the problem with slight bumps on the travel path  70  that a traveling gear  60  undergoes load relief in an extreme case and is ultimately fully raised. On the other hand, the luffing cabling  4  may also not undergo too great a load relief to prevent a slack rope. Such a slack rope would later negatively influence the winding quality. 
     Very generally, a support of the boom would also be possible, instead of the traveling gear  60 , via a single-axle all-terrain dolly in accordance with German utility model DE 20 2010 002 947, U1. 
     A specific steering program can be set via a correspondingly provided control for the moving of the crane. Generally different steering programs are possible here. All traveling gears  60  can thus be orientated toward a common steering center  102 , for example. It is alternatively possible to set the two traveling gears  60 , such as are shown in  FIGS. 10 and 11 , beneath the ring elements  57  to a common steering center  102 , whereas the further traveling gear  60  which is arranged beneath the boom  3  is steered separately. In the latter case, it would have to be considered by the control that the spacing between the rotational axle of the superstructure  1  from the connection point is kept constant between the connection elements  31  and the mating connection elements  63 . 
       FIG. 12  shows a further embodiment of the crane in accordance with the invention. A mobile crane  200  having an undercarriage  5  and a superstructure  210  is provided here. It has a perpendicularly standing tower  220 . The tower comprises a plurality of tower elements  230 . Each tower element can be connected to at least one adjacent tower element. As shown in  FIG. 12 , such a mobile tower slewing crane can be used advantageously to erect high wind turbines. 
     Here, the superstructure  210  is therefore substantially configured as a tower  220  of a tower slewing crane  200 . The tower slewing crane is set up on the undercarriage  5  which is equipped with a corresponding support apparatus. 
     The setup of the undercarriage can be recognized better in the enlarged detailed representation in accordance with  FIG. 13 . The support apparatus comprises two times two supports  52  which are each connected to one another via half a pot  51  and which each alone represents a transport unit. The two pot halves are assembled and bolted to one another for assembly, as is shown in  FIG. 13 . The swivel connection for the bottom-slewing tower  220  of the mobile tower slewing crane  200  is formed together with a mounted and connected revolving deck frame  250 . 
     The supports  52  comprise a total of four hydraulic support cylinders  240  with automatic leveling. As shown in  FIG. 15 , a total support base of, for example, 16×16, meters is thereby achieved. Different sizes can naturally be achieved with a corresponding design of the support cylinders used. A support cylinder pair is shown in the lower part of the representation in  FIG. 15 , on the one hand, retracted in the transport position and, on the other hand, in the moved out support position. 
     A respective side member  54  adjoins each pot half  51  (cf.  FIG. 13 ); a mounting ring or ring element  57  is provided at it which can be moved below by suitable traveling gears, which are here configured as transport crawlers  60 . 
     The crane  60  can thus be supported with the aid of its support apparatus in stationary operation. For displacement, the crane  200  can then be taken up by the at least two traveling gears  60  configured as crawlers and can be moved from one deployment location to another. As can be seen from  FIG. 14 , gradients with a transverse slope can also be traveled by an automatic horizontal orientation of the support plates forming or receiving the receiving rings or ring elements  57 . 
       FIG. 16  shows a perspective representation of a traveling gear which is here configured as a transport crawler  60  with its own operator&#39;s cabin  260 . It has a pivotable support plate forming or receiving the receiving ring or the ring element  57 . The pivoting takes place via a three-point support which can be recognized in detail in the partly exposed representation in accordance with  FIG. 17 . The three-point support is here formed by three piston-in-cylinder units  280 . In addition, two connectors  290  are provided which take up the forces which are not directed into the longitudinal axes of the cylinders. 
     The crane  200  cannot only be transported by the traveling gears. It can rather also be received by the traveling gears  60  during the crane operation, with it then additionally be supported via the support apparatus. If the crane  200  should, however, only be supported by the support apparatus, the traveling gears can be used in another manner on the construction site. They can thus, for example, be used for transporting parts of the wind turbine. 
     A revolving deck is provided on the undercarriage, i.e. more exactly on the swivel connection of the undercarriage, and represents the connection piece between the undercarriage and the center piece with a rotary roll connection and slewing gears. The revolving deck additionally comprises a diesel engine with a generator and hydraulic pumps for the operation of the hydraulic support cylinders. A cable drum is furthermore provided on the revolving deck for the supply of the climbing frame. 
     The crane tower is secured using the connection piece so that the crane is configured as bottom-slewing. The individual lattice pieces are bolted to one another, with the respective bolts being spring loaded. 
     The further structure of the superstructure configured as a tower slewing crane results from the detailed description of the simultaneously filed German patent application of the applicant, the content of which is referenced here.