WO2002022489A1 - Materialumschlaggerät - Google Patents
Materialumschlaggerät Download PDFInfo
- Publication number
- WO2002022489A1 WO2002022489A1 PCT/EP2001/010787 EP0110787W WO0222489A1 WO 2002022489 A1 WO2002022489 A1 WO 2002022489A1 EP 0110787 W EP0110787 W EP 0110787W WO 0222489 A1 WO0222489 A1 WO 0222489A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- material handling
- handling device
- undercarriage
- superstructure
- articulated
- Prior art date
Links
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
- B66C23/54—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes with pneumatic or hydraulic motors, e.g. for actuating jib-cranes on tractors
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
- B66C23/62—Constructional features or details
Definitions
- the present invention relates to a material handling device with the features of the preamble of claim 1.
- Such material handling devices are mainly used in inland ports and their adjacent storage areas for handling different materials, such as wood, scrap, gravel, sand and the like.
- Material handling devices are powerful, flexible loading machines with a large range (at least 18 to 20 meters radius) and fast work cycles with large grippers, magnetic disks or the like.
- the requirements for these loading machines with regard to flexibility exist on the one hand with regard to the use of work on the quay wall for ship unloading in both high and low water and on the other hand in a quick relocation of the loading machine to another unloading point or to a storage location can also be further (10 to 50 km) away.
- Stationary loading machines or harbor cranes are known from the prior art, which are installed on a steel or concrete pillar at a height of approximately 4 to 7 meters. Furthermore, quasi-stationary harbor cranes are known, which are arranged to be movable on rails along the quay. In addition, mobile handling devices on caterpillar or wheel drives are known, which operate as self-propelled vehicles short distances (up to approx. 5 km distance) can be driven profitably. In the case of dislocation distances beyond the short distance mentioned, loading takes place on flatbed trucks. The dimensions of the last-mentioned material handling equipment are subject to the limits imposed by the passage heights of bridges, etc.
- a material handling device is also known from the prior art, which has a mobile undercarriage, in particular, on which the superstructure with driver's cab, engine compartment and boom is arranged at a height of 4 to 6 meters by means of a tubular pylon (steel column).
- the well-known material handling device is particularly suitable for use in ship unloading in port handling and space work, but has the disadvantage that it has to be set up on site and due to self-propulsion only in very limited distances of a maximum of 2 to 4 kilometers - provided no bridges, Power lines or the like are in the way - can be moved.
- Another disadvantage of the known material handling equipment is that the maintenance, lubrication, refueling etc.
- the engine compartment integrated in the superstructure has to be carried out over a height of 4 to 6 meters.
- the operating personnel of the well-known Material handling equipment must overcome the height difference between the undercarriage and the uppercarriage using a correspondingly high ladder.
- the superstructure must be secured by appropriate railings.
- the uppercarriage of the material handling device according to the invention is designed to be adjustable at a distance from the undercarriage between a sub-position (rest position) on the undercarriage and an upper position (working position).
- the measure according to the invention increases the flexibility of a material handling device, because by adjusting the position of the superstructure between a lower and an upper position, on the one hand a sufficiently high arrangement of the jib and thus all requirements regarding range, loading depth and overloading dimension of ship's side walls are met, on the other hand in the lowered position on the undercarriage improves mobility and enables transport on flatbed trucks.
- the uppercarriage is lowered, operating personnel can comfortably get into the driver's cab on the uppercarriage, and refueling, maintenance of the engine compartment, etc. is also facilitated in the lowered condition.
- a partially lowered position on the undercarriage is provided as the driving position for self-driving the material handling device according to the invention, while the actual rest position for transport on a flatbed trailer, for maintenance, refueling, and getting in / out of operating personnel represents a completely lowered position.
- the material handling device is designed such that a vertical axis of rotation of the superstructure in the upper position (working position) runs approximately through the center of the undercarriage with caterpillar drive or through the center of the supports of the undercarriage with wheel drive, in order to work, in particular when rotating the superstructure to achieve the same stability on all sides.
- the uppercarriage is adjusted relative to the undercarriage by means of a link arrangement with actuating cylinder located between the uppercarriage and the undercarriage.
- actuating cylinder located between the uppercarriage and the undercarriage.
- an adjustment device for height adjustment of the superstructure acts directly on the superstructure and is articulated at the lower end on an intermediate frame which is rotatably arranged relative to the undercarriage.
- the parallel links of the handlebar arrangement representing the adjusting device are preferably designed as 4-point links, whereby the combination is also possible that one of the links is a 3-point link, the other is a 4-point link.
- the uppercarriage is lowered into the sub-position by pivoting the parallel link to the rear of the material handling device.
- the superstructure is lowered into a position in which it comes to lie over the rear area of the material handling device, which makes it possible to fold in the boom extending in the direction of the front area of the material handling device above the front area of the material handling device and there with the lowest possible height expansion for the and to accommodate the loading position. It also proves advantageous that the engine compartment arranged on the superstructure comes to rest in a position located behind the undercarriage, in which it is directly accessible from several sides, which greatly simplifies maintenance, refueling and the like.
- the parallel link articulated in the rear area is articulated lower than the parallel link articulated in the front area
- the parallel articulation link articulated in the rear area is articulated on the superstructure on a section of the superstructure substructure that projects obliquely downwards.
- the obliquely downwardly projecting section of the superstructure substructure is oriented to the geometry of the undercarriage and is designed such that it rests in the lowered subposition of the superstructure when a front horizontal section of the substructure rests or is supported on the undercarriage behind the rear of the undercarriage to the ground (Lane level) is sufficient and thus provides maximum support and relief for the parallel link.
- steps can be formed or attached to the obliquely downwardly projecting section of the superstructure substructure, which provide easy entry from operating personnel to the uppercarriage or to the driver's cabin.
- the undercarriage has a caterpillar drive.
- a caterpillar drive is advantageously a telescopic crawler undercarriage whose track width is adjustable.
- a telescopic caterpillar drive is known from DE 93 19 382 UI.
- the angle of inclination of the parallel links in the upper position is between approximately 0 ° and approximately 20 ° to the vertical.
- An angle of inclination to the vertical of approximately 15 ° has proven to be particularly advantageous.
- a material handling device is proposed according to the invention with an undercarriage with a wheel drive with at least two wheel axles, with a superstructure with a driver's cab and engine compartment arranged rotatably relative to the undercarriage, and with a boom or boom system articulated on the superstructure, in which the Material handling device are provided in the operating state at least two lowerable support elements and the distance of the wheel axles from the superstructure rotation axis in the operating state corresponds at least to the distance of a tilt line given by the lowered support elements to the rotation axis.
- the distance between the wheel axles and the axis of rotation of the uppercarriage, which is perpendicular thereto, is therefore greater than or equal to the distance between a tilt line spanned by the lowered support elements and the axis of rotation.
- the ideal tilt line corresponds to a circle around the axis of rotation, the radius of which is the support length from the
- BESTATIGUNGSKOPIE Longitudinal axis (center line) of the undercarriage corresponds to the support edge.
- the requirement for the dimensioning of the material handling device according to the invention is therefore that the tilting lines must not undercut the described tilting circle in any position of the 360 ° pivoting of the superstructure.
- the material handling device has a wheel drive with an upper carriage which is adjustable between a sub-position on the undercarriage and an upper position at a distance from the undercarriage.
- the parallel link articulated in the rear area advantageously has a cranked shape, such that it bridges the wheel axle arranged in the rear area in the lowered sub-position.
- two lowerable support elements are provided, which are arranged between the two wheel axles of a material handling device with a wheel drive.
- four lowerable support elements are provided, of which a first pair is arranged on the end face of the undercarriage and a second pair between the two wheel axles.
- Figure 1 shows a material handling device according to the invention with a scale scale (meter grid) in the port handling position on a quay wall.
- Figure 2 shows the material handling device according to the invention of Figure 1 in a partial side view in the working position and lowered sub-position.
- FIG. 3 shows the material handling device according to the invention from FIG. 1 in the working position in a front view with a view of the front parallel handlebar designed as a 4-point handlebar.
- FIG. 4 shows the material handling device according to the invention from FIG. 1 in the working position in a rear view with a view of the rear parallel link designed as a 3-point link.
- Figure 5 shows the material handling device according to the invention in Figure 1 in a lateral overall view in the lowered rest or maintenance position.
- BESTATIGUNGSKOPIE Figure 6 shows the material handling device according to the invention of Figure 1 in a lateral overall view in the lowered rest or loading position.
- FIG. 7 shows a side view of a second exemplary embodiment of a material handling device according to the invention both in the working position and in the lowered rest position.
- FIG. 8 shows the material handling device according to the invention in a partially lowered self-propelled position.
- Figure 9 shows a third embodiment of a material handling device according to the invention with wheel drive and so-called 4-point claw support.
- FIG. 10 shows a material handling device similar to the material handling device of FIG. 9 with a wheel drive and a longer wheelbase and a 2-point claw support.
- FIG. 11 shows a top view of the undercarriage of the material handling device of FIG. 9.
- FIG. 12 shows a top view of the undercarriage of the material handling device of FIG. 10.
- FIG. 13 shows a view of the undercarriage of the material handling device of FIG. 1 from the front with the claws lowered.
- FIG. 14 shows, as a further exemplary embodiment, a material handling device according to the invention with a directly attached superstructure and 2-point claw support.
- Figure 15 shows the undercarriage of the material handling device of Figure 14 in plan view.
- Figure 16 shows a plan view of an undercarriage with two wheel axles, which has no additional lowerable support elements.
- FIG. 1 shows a first exemplary embodiment of a material handling device 1 according to the invention.
- the material handling device 1 according to the invention (hereinafter called the charger for the sake of simplicity) comprises an undercarriage 10 which can be moved on caterpillars and an uppercarriage 20 and a superstructure 20 comprising a rear weight 24 is attached to a substructure 30 by means of a pivot bearing 27 (cf. also FIG. 2, which shows the charger 1 according to the invention in a partial partial view).
- a boom 25 with a loading arm 28 and gripper 29 is articulated on a boom bearing axis 8 on the superstructure 20.
- the boom system shown for example with more or fewer articulated parts or telescopic boom combinations, can also be used.
- the superstructure 20 is arranged at a height of approximately 5 to 6 meters from the undercarriage 10.
- the spaced arrangement is achieved by a handlebar arrangement 9, by means of which the superstructure 20 can be lowered into a sub-position on the undercarriage 10.
- FIG. 1 illustrates the possible uses of a charger according to the invention using the example of use in port handling on a quay wall 2.
- the ship's hull 4 In front of the quay wall 2 is a cargo ship, the ship's hull 4 with cargo 5 of which is shown schematically in section.
- the side wall of the ship's hull 4 At low water level 3 and fully loaded, the side wall of the ship's hull 4 is approximately at the same height as the quay wall 2.
- maximum water level 6 on the other hand (and in particular when the unloading progresses), the ship's hull is raised to the position 7 shown in broken lines.
- the boom support 8 In order to still be able to work with the charger 1 in the raised position 7 of the ship's hull, the boom support 8 (see FIG. 2) must be arranged sufficiently high above the quay wall 2. For this purpose, a height of approx. 6 meters can be read from the meter grid stored in the drawing. The operator's eye level must also be at a similar
- both the lowered sub-position (resting or loading position) I and the raised upper position (working position) II are drawn in to illustrate the mode of operation and functioning of the invention.
- the uppercarriage 20 of the charger 1 according to the invention is raised and lowered by means of an adjusting device, which in the exemplary embodiment shown is a hydraulically driven handlebar arrangement 9.
- an adjusting device which in the exemplary embodiment shown is a hydraulically driven handlebar arrangement 9.
- FIG pointing caterpillar 13 of the crawler-driven undercarriage 10 cut away.
- the link arrangement 9 comprises a pair of parallel links 16, 18.
- the two parallel links 16, 18 forming the pair of parallel links are articulated at their lower ends to a chassis middle body 11 of the undercarriage 10 and with their upper ends to the substructure 30 of the superstructure 20.
- a first parallel link 16, which is a so-called 4-point link (see FIG. 3) is articulated in a front region of the undercarriage 10 on a front link axis 15 on the center body 11, while a second parallel link 18, at which is a so-called 3-point handlebar (see FIG. 4), is articulated in the rear area of the undercarriage 10 on a rear handlebar axle 17 on the center body 11.
- the two parallel links 16, 18 are of equal length, but are articulated to the center body 11 at different heights in order to improve the swivel geometry, in particular with regard to the position of the links and the uppercarriage in the lowered position.
- the superstructure is lowered by pivoting the parallel links 16, 18 towards the rear of the undercarriage 10. For this reason, the front parallel link 16 is higher and the rear parallel link 18 is articulated lower.
- the substructure 30 has two sections for this purpose, namely a first horizontally extending section 36, on which the pivot bearing is provided for the fully rotatable arrangement of the uppercarriage, and a second section 35, which runs obliquely downwards in the direction of the rear of the charger 1.
- the front parallel link 16 is articulated to a front substructure link axis 31 on the horizontal section 36 and the rear parallel link 18 to a rear sub link link axis 32 on the cantilevered section 35.
- the geometry of the sloping downward (cantilevered) section 35 of the superstructure substructure 30 is such that the different heights in the articulation of the two parallel links 16, 18 are compensated for.
- the handlebar arrangement 9 is designed such that - as can be seen from FIG. 2 - in the lowered position I of the superstructure 20, the parallel links 16, 18 rest on the undercarriage 19 or the ground (road level) 37, the end of the cantilever also Section 35 of the superstructure substructure 30 is supported in the region of the articulation axis 32 on the base 37.
- the front parallel link 16 which is driven via a pair of actuating cylinders 19, as a 4-point link with maximum width in order to rotate and Introduce tilting forces from the intermediate frame of the superstructure substructure 30 into the chassis center body 11.
- the second, non-driven link 18 articulated in the rear area is advantageously designed as a 3-point link in such a way that it engages the substructure 30 at one point (link axis 32) by around 3 for components of this size (the link length is approx 3.50 m) to compensate for length tolerances.
- FIGS. 3 and 4 show the charger 1 according to the invention in front view ( Figure 3) and in the rear view ( Figure 4).
- FIGS. 3 and 4 show the arrangement of the crawler drive of the undercarriage 10 with caterpillar ships 13, 14.
- the caterpillar drive is preferably a caterpillar drive which can be telescoped by means of telescopic guides 12, so that the track widths 13, 14 can be adjusted in the track width, as a result of which an adjustment between a space-saving transport state (transport width T) and an increased stability imparting working state (working width) A) is possible (see FIG. 4).
- the transport position of the caterpillars 13, 14 is shown in dashed lines in FIGS. 3 and 4.
- the representation of the telescopic guides 12 is purely schematic, and there is also no further detailed description of the telescopic adjustment of the caterpillar ships 13, 14, since it is known per se from the prior art.
- the front parallel link 16 preferably has a recess 33 (see FIGS. 3 and 4) which contributes to the weight saving and creates space for hose lines 34 running from the superstructure 20 to the undercarriage 10 (see FIG. 2).
- a stepladder 40 as shown in FIGS. 4 and 5 can be provided, which is arranged on the superstructure 20, more precisely on the substructure 30 of the superstructure 20 is that it comes to lie in the lowered state (sub-item I) with its lowest step a little above the subsurface 37. It proves to be particularly advantageous that To design the stepladder 40 so that it can be pushed out, so that it can be moved analogously to the telescopic caterpillar drive between the above working position and not laterally projecting transport position beyond the outer dimensions of the superstructure (cf. FIG. 4). However, operators can also board the caterpillar 13 if no step ladder is provided.
- FIG. 5 shows the charger 1 of Figure 1 according to the invention in a lateral overall view in sub-position I, which represents the exit and entry position for the operator and the maintenance position for refueling, lubrication, etc.
- FIG. 6 also shows an overall side view of sub-item I of the charger 1 according to the invention in the loading position with the boom folded in for a so-called low-bed truck.
- the boom 25 with the loading arm 28 is lowered and folded in so far that it does not, or only insignificantly, protrude from the roof of the driver's cab 21 with its highest point and does not exceed a height of approximately 3.70 m.
- the crawler track is also moved to transport width T.
- FIG. 7 finally shows a further embodiment of a charger according to the invention, in which, in contrast to the first embodiment shown in Figures 1 to 6, the parallel link 16, 18 in the upper position II of the superstructure 20 not vertically, but with a slight inclination towards the rear of the Charger stand. In the illustrated embodiment, this inclination is approximately 15 °.
- the axis of rotation 27 is located approximately above the center of the rear caterpillar drive wheel, while in the exemplary embodiment in FIG.
- control of the charger is preferably carried out in such a way that a (full) pivoting of the superstructure 20 about the vertical axis 27 is only released when the superstructure 20 has reached its working position and the two caterpillar ships 13, 14 are in their extended working width are located so that sufficient stability is ensured.
- the rotation of the uppercarriage would only be released if the corresponding legs were extended to improve stability.
- the longitudinal axis of the uppercarriage 20 with the boom 28 must be brought into alignment with the longitudinal axis of the undercarriage 10, the front side of the uppercarriage 20 (boom side) as shown in the figures in Front direction of the undercarriage 10, ie must point in the direction of the driven parallel link 16. Only then is the lowering from the upper position to the lower position on the actuating cylinders 19 released.
- a driving position III of the uppercarriage shown in FIG. 8 can also be provided as an intermediate position, in which the section 35 of the uppercarriage substructure 30 that projects obliquely downwards does not rest on the subsurface 37, but is located approximately at the level of the upper edge of the crawlers 13, 14.
- the charger can be driven with its own drive (whereby the uppercarriage is blocked from rotating) in order to keep the height and the center of gravity of the entire device low in difficult terrain or to drive under bridges.
- FIG. 9 shows a material handling device according to the invention with a wheel drive as a further exemplary embodiment.
- the wheel drive of the material handling device comprises two wheel axles 50, 51, namely a rigid axle 50 arranged in the rear area of the undercarriage 10 'and a pendulum axle 51 arranged in the front area of the undercarriage 10'.
- the material handling device comprises claw supports 60, 64 fastened to the undercarriage 10 ', a first pair 60 of which is arranged on the end face of the undercarriage 10' and a second pair 64 between the two wheel axles 50, 51. According to the distances and dimensions are chosen such that at least one of the wheel axles
- the rear rigid axle 50 a distance from the superstructure rotation axis in the operating state, i.e. in the upper position II, which is greater than or equal to the distance of a tilt line K from the superstructure axis of rotation 70 (cf. also FIG. 11).
- the ideal tilt line is a (imaginary) circle X around the axis of rotation 70 with a radius R that is the support length from the center line
- FIG. 10 shows, as a similar exemplary embodiment, a further material handling device with a wheel drive, which has a longer wheelbase between the two wheel axles 50, 51 and has only one pair of claws 64 for support, which is arranged between the two wheel axles 50, 51.
- the arrangement is such that the distance between the two wheel axles 50, 51 from the axis spanned by the two claws 61 corresponds to greater than or equal to the radius R as defined above (cf. also FIG. 12).
- the arrangements described achieve a stability of the material handling device which is adequate for adjusting the superstructure between a sub-position I and an upper position II.
- the undercarriage with wheel drive described are particularly necessary if the material handling equipment with tar covering, paving, asphalt or. fixed underground is used, which could be damaged by a caterpillar drive. Especially in inner-city demolition or demolition projects, caterpillar drives would cause too much damage on roads or paved areas.
- the material handling devices according to the invention have secure all-round support for such areas of use.
- the parallel link 18 '(so-called triangular link) articulated in the rear area of the undercarriage 10' is configured with a crank, such that the triangular link 18 'in the lowered sub-position bridges the wheel axle 50 located in the rear area and preferably rests with its end remote from the vehicle on the ground, as a result of which support is achieved.
- FIG. 13 shows a front view of a claw support device 60 with two lowerable claws 61 which rest on the base 62 by means of base plates 62 and thus enable the material handling device to be supported.
- the claws 61 are located within the transport width of the material handling device given by the wheels 66.
- the support force acting on the base plates 62 of the support claws 61 is preferably limited by means of the support cylinder 63 (see FIG. 13).
- This pressure limitation prevents the rigid axis 50 in the exemplary embodiment in FIG. 9 and the two axes 50, 51 in the exemplary embodiment in FIG. 10 from lifting off the ground and not being available as an (additional) support element in the operating state. This is particularly important because if the axis (s) were lifted, it would no longer act as a tilt line (s).
- the claw supports shown can also be replaced by so-called telescopic supports that extend vertical hydraulic rams to the dimension R (or larger).
- FIG. 14 shows a support according to the invention for a wheel-driven undercarriage also for a material handling device, in which the superstructure 20 bears directly on the undercarriage 10 ". is ordered.
- the arrangement ensures that both wheel axles 50, 51 act as support elements.
- FIG. 15 shows the top view of the undercarriage of the material handling device in FIG. 14.
- an inherently hydraulic swing axle lock 54 is shown, which is switched in such a way that the work functions only after the swing axle 51 has been supported and locked by the swing axle lock be released in the superstructure.
- the support and axle lock can be controlled using simple pressure sensors.
- a material handling device in which, using a known hydraulically or mechanically telescopic, hydraulically driven crawler undercarriage and a known superstructure, which can be fully rotated on a pivot bearing with a vertical axis, by the inventive adjustability of the superstructure relative to the undercarriage which results from the Disadvantages known in the art are eliminated.
- Equipped with wheel undercarriages is also provided, which can be realized with commercially available heavy-duty axles and in which the required all-round safety is achieved by arranging support devices according to the invention, including one or more wheel axles as support means.
- the function of the lowerable support elements can of course be replaced by the wheel axles and the wheels, provided that the wheel axles are widened to such an extent that the wheels form a square lying completely outside the tilt circle X. form.
- a wheel-driven material handling device can be designed without additional support elements. Such a configuration is shown in a top view of the undercarriage in FIG. 16.
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Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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EP01982312A EP1318965B1 (de) | 2000-09-18 | 2001-09-18 | Materialumschlaggerät |
DE50110065T DE50110065D1 (de) | 2000-09-18 | 2001-09-18 | Materialumschlaggerät |
US10/387,131 US7204378B2 (en) | 2000-09-18 | 2003-03-13 | Goods transshipment apparatus |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP00120389A EP1188707A1 (de) | 2000-09-18 | 2000-09-18 | Materialumschlaggerät |
EP00120389.2 | 2000-09-18 |
Publications (1)
Publication Number | Publication Date |
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WO2002022489A1 true WO2002022489A1 (de) | 2002-03-21 |
Family
ID=8169866
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/EP2001/010787 WO2002022489A1 (de) | 2000-09-18 | 2001-09-18 | Materialumschlaggerät |
Country Status (4)
Country | Link |
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US (1) | US7204378B2 (de) |
EP (2) | EP1188707A1 (de) |
DE (1) | DE50110065D1 (de) |
WO (1) | WO2002022489A1 (de) |
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US8066713B2 (en) * | 2003-03-31 | 2011-11-29 | Depuy Spine, Inc. | Remotely-activated vertebroplasty injection device |
WO2005030034A2 (en) | 2003-09-26 | 2005-04-07 | Depuy Spine, Inc. | Device for delivering viscous material |
ES2352807T3 (es) * | 2004-12-03 | 2011-02-23 | Manitowoc Crane Group Germany Gmbh | Grúa automotriz. |
US8395498B2 (en) | 2007-08-31 | 2013-03-12 | Cardiac Pacemakers, Inc. | Wireless patient communicator employing security information management |
US8812841B2 (en) | 2009-03-04 | 2014-08-19 | Cardiac Pacemakers, Inc. | Communications hub for use in life critical network |
US8319631B2 (en) | 2009-03-04 | 2012-11-27 | Cardiac Pacemakers, Inc. | Modular patient portable communicator for use in life critical network |
CN102642782B (zh) * | 2012-05-19 | 2014-01-08 | 南京工业大学 | 一种可运输装卸的塔机 |
JP6316769B2 (ja) * | 2015-03-30 | 2018-04-25 | 日立建機株式会社 | 建設機械 |
CN107628555A (zh) * | 2017-11-17 | 2018-01-26 | 长沙理工大学 | 一种卷扬机自动控制的两节折叠输送机 |
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AU640081B2 (en) * | 1991-12-26 | 1993-08-12 | Shinko Jyuki Co., Ltd | Working machine |
US5984618A (en) * | 1997-06-30 | 1999-11-16 | Caterpillar Inc. | Box boom loader mechanism |
JP3365737B2 (ja) * | 1998-01-19 | 2003-01-14 | 日立建機株式会社 | 運転室付き建設機械 |
US6173973B1 (en) * | 1998-07-09 | 2001-01-16 | Timberjack Inc. | Forestry machine swing-house leveling mechanism |
EP1008549A3 (de) * | 1998-12-09 | 2000-08-02 | Compact Truck AG | Kranfahrzeug |
US6135225A (en) * | 1999-06-30 | 2000-10-24 | Caterpillar Inc. | Tilt mechanism for supporting a cab assembly of a work machine and an associated method of operating a tilt mechanism of a work machine |
US6343799B1 (en) * | 2000-08-01 | 2002-02-05 | Caterpillar Inc. | Tilt mechanism for work machine |
JP3721123B2 (ja) * | 2001-11-29 | 2005-11-30 | 日信工業株式会社 | 車両用ディスクブレーキのキャリパボディ |
-
2000
- 2000-09-18 EP EP00120389A patent/EP1188707A1/de not_active Withdrawn
-
2001
- 2001-09-18 DE DE50110065T patent/DE50110065D1/de not_active Expired - Lifetime
- 2001-09-18 WO PCT/EP2001/010787 patent/WO2002022489A1/de active IP Right Grant
- 2001-09-18 EP EP01982312A patent/EP1318965B1/de not_active Expired - Lifetime
-
2003
- 2003-03-13 US US10/387,131 patent/US7204378B2/en not_active Expired - Fee Related
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
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GB1048722A (en) * | 1964-02-25 | 1966-11-16 | Priestman Brothers | Improvements in tower cranes |
GB1374253A (en) * | 1971-05-06 | 1974-11-20 | Gen Crane Industries | Mobile tower cranes |
DE2941813A1 (de) * | 1979-10-16 | 1981-05-14 | Hermann 8949 Mörgen Kaiser | Auf ein transportfahrzeug angeordneter kran |
US4365927A (en) * | 1980-05-02 | 1982-12-28 | Schenck Ray B | Slash recovery system |
DE4213077A1 (de) * | 1992-02-25 | 1993-08-26 | Liebherr Werk Nenzing | Kran |
DE4331832A1 (de) * | 1993-06-30 | 1995-01-12 | Schaeff Karl Gmbh & Co | Ladegerät |
EP0978472A2 (de) * | 1998-07-01 | 2000-02-09 | Grove U.S. LLC | Fahrbarer Kran |
DE19909356A1 (de) * | 1999-03-03 | 2000-09-14 | Erich Sennebogen | Materialumschlaggerät |
Also Published As
Publication number | Publication date |
---|---|
EP1318965B1 (de) | 2006-06-07 |
US7204378B2 (en) | 2007-04-17 |
DE50110065D1 (de) | 2006-07-20 |
EP1318965A1 (de) | 2003-06-18 |
EP1188707A1 (de) | 2002-03-20 |
US20040033124A1 (en) | 2004-02-19 |
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