Classifications

• • 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
  • B66C23/64—Jibs
  • B66C23/68—Jibs foldable or otherwise adjustable in configuration
• • 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
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B66—HOISTING; LIFTING; HAULING
  • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
  • B66C13/00—Other constructional features or details
  • B66C13/18—Control systems or devices
  • B66C13/20—Control systems or devices for non-electric drives
• • 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
  • B66C23/18—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 specially adapted for use in particular purposes
  • B66C23/36—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 specially adapted for use in particular purposes mounted on road or rail vehicles; Manually-movable jib-cranes for use in workshops; Floating cranes
  • B66C23/42—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 specially adapted for use in particular purposes mounted on road or rail vehicles; Manually-movable jib-cranes for use in workshops; Floating cranes with jibs of adjustable configuration, e.g. foldable
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B66—HOISTING; LIFTING; HAULING
  • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
  • B66C2700/00—Cranes
  • B66C2700/03—Cranes with arms or jibs; Multiple cranes
  • B66C2700/0321—Travelling cranes
  • B66C2700/0357—Cranes on road or off-road vehicles, on trailers or towed vehicles; Cranes on wheels or crane-trucks

Definitions

• This invention relates to an outer-boom crane of the type having a first boom section connected to a post by a main articulation, and an outer boom connected to the first boom section and pivotable relative thereto by means of a double-acting hydraulic cylinder which is arranged on the upper side of the first boom section and whose one end, e.g. the cylinder end, is connected to the first boom section by a first articulation and whose opposite end, e.g.
• the piston-rod end is connected to the outer boom by a second articulation which is offset a certain distance transversely of an imaginary longitudinal axis through the pivotal articulation of the outer boom to permit pivoting the outer boom between different positions, not only with ⁇ in a working range below an imaginary extension line drawn approximately straight out from or at a small angle to the first boom section, but also in a range of motion situated above this extension line adjacent a parking position.
• the first boom section In connection with parking of at least vehicle-mounted outer-boom cranes, the first boom section is thus lowered to a position in which it is hanging obliquely downwards-outwards from the main articulation of the post while at the same time the outer boom is pivoted upwards to a position near and approximately parallel to the first boom section.
• the space then available is in practice limited and unconditionally decisive of the maxi ⁇ mum length of the first boom section. For this reason, the first boom section and the outer boom are given approx- imately equal length to provide maximum crane reach within the working range.
• the present invention aims at providing a crane con ⁇ struction which meets both of the above-indicated demands, in themselves contradictory, that are placed on a forest crane.
• a basic object of the invention thus is to provide a crane construction in which the effective length of the first boom section, i.e the distance between the main articulation and the outer boom articulation, is consider ⁇ ably greater than the length of the outer boom when this is moving within the working range while at the same time giving the crane, within the scope of a given parking space, a considerable maximum reach.
• Another object is, while meeting these demands, to maintain the location of the outer boom cylinder on the upper side of the first boom section.
• Yet another object of the invention is to provide the aimed-at crane construction without necessi ⁇ tating the use of additional hydraulic cylinders other than the above-mentioned outer boom cylinder.
• FIG 1 is a schematic side view showing a crane accord ⁇ ing to the invention with the first boom section in an appoximately horizontal position and with the outer boom being in a substantially straight extension of the first boom section
• FIG. 2 is a similar side view showing the two booms in a parking position
• FIGS 3-10 are side views on a smaller scale showing dif ⁇ ferent positions of the outer boom when pivot ⁇ ing from a parking position shown in Fig. 3 on the upper side of the first boom section to an extreme swung-back position, shown in Fig. 10, within the lower working range of the outer boom
• FIG. 11 is a cut-away side view on an enlarged scale showing the link device that connects the outer boom to the first boom section
• FIG. 12 is a top plan view of the crane portion in Fig. 11
• FIGS 13-18 are schematic side views showing the function of a locking latch for locking the link relative to the outer boom and the first boom section, respectively, in the different crane positions shown in Figs 3-8, and FIG.
• FIG. 19 is a plan view showing two hydraulic cylinders for rotating a post being part of the crane.
• the crane shown in Figs 1 and 2 comprises a first boom section 1 and an outer boom 2.
• the first boom section 1 is connected at an inner end to a post 4 by a main arti ⁇ culation 3 and can be pivoted relative to the post by means of a hydraulic cylinder 5, in practice termed lift cylinder.
• the post 4 is mounted on a base 6, more speci ⁇ fically via a live ring device 7 including two hydraulic cylinder units 8, 8' (see also Fig. 19) serving to bring about rotation of the post to different rotational posi ⁇ tions relative to the base.
• the base 6 may consist or be part of a supporting beam, standing on legs, which is included in a vehicle frame.
• the main part of the first boom section 1 suitably is a box girder with an upper side 9 and a lower side 9' .
• the main part of the outer boom 2 also consists of a box girder with an upper side 10 and a lower side 10' .
• a tool carrier 11 which can be mounted either directly on the outer boom or on an extendible telescopic boom incorporated therein.
• the tool carrier 11 may carry e.g. a rotator, from which is suspended a timber grapple. Naturally, the tool carrier 11 may carry any optional tool.
• the outer boom 2 is pivotable relative to the first boom section 1 with the aid of a second hydraulic cylinder 12, in practice termed outer boom cylinder.
• the hydraulic cylinder 12 is mounted on the upper side of the first boom section and has its one end, in this case the cylinder end 12' , connected to the first boom section by a first arti ⁇ culation 13 and its opposite end, in this case the piston rod end 12", connected to the outer boom 2 by a second articulation 14.
• the centre of the articulation 13 is spaced a certain distance from the upper side 9 of the first boom section, such that the cylinder end 12' can occupy a position immediately adjacent and parallel to this upper side (see Fig. 3).
• a link device in practice comprising two separate links or link plates 15', 15" (see Fig. 12).
• This link device is connnected to the first boom section 1 by a third articulation 16 and to the outer boom by a fourth articulation 17 which is spaced from the second articulation 14 and the third articulation 16. More speci ⁇ fically, the third articulation 16 is located at a greater distance from the fourth articulation 17 than the second articulation 14.
• the articulation 14 is made up of a transverse shaft or pin which extends between two wedge-shaped, tapering side flanges 18, 18' which project at an angle from the inner end of the outer boom 2.
• the pivot pin 14 is disposed at the free ends of the flanges 18, 18', which means that this articulation is offset a certain distance transversely of an imaginary longitudinal axis which is parallel to the outer boom and intersects the articulation 17 thereof.
• the articulation 17 also consists of a through shaft or pin, although merely illustrated by a dash-dot line in Fig. 12.
• the articulation 16 consists of two spaced-apart pivot pins 16', 16" which are mounted in flanges 19, 19' fixed on the free, outer end of the first boom section and projecting obliquely upwards from the upper side of the first boom section.
• the piston rod 12" of the outer boom cylinder 12 can be accommodated in the space between the pivot pins 16, 16" and the flanges 19, 19', respectively.
• the piston rod 12" has a connecting ring 20 surrounding the pivot pin 14.
• the width of the ring 20 is considerably smaller than the distance between the wedge flanges 18, 18', which means that the pivot pin 14 is exposed over a certain distance on both sides of the ring 20.
• Each of the two link plates 15', 15" is generally angular and has, on one side, two edges 21, 22 extending at an angle to each other and joining in a point 23 located at a distance from the fourth articulation 17 which is substantially equal to the distance between the articulations 14 and 17.
• the angle between the edges 21 and 22 may be in the range of 150-160°.
• the point 23 forms an abutment for the second articulation 14.
• a part-circular recess corresponding to the cylindrical shape of the pivot pin 14 may be provided in the area of this point.
• each link plate 15', 15" has a terminal edge 24 extending transversely, e.g.
• the pivot pins 16', 16" forming the third articulation being arranged in the vicinity of one end of the terminal edge 24 of the two link plates.
• a suitably semicircular recess or seat 25 adapted to cooperate with a shaft or pin 26 fixedly mounted on the tip of the first boom section and serving as a stop for the link device.
• the outer boom 2 can move in two basically distinct ranges of motion, name ⁇ ly one working range and one inactive range or parking range. These two ranges are separated by an intermediate position illustrated in Fig. 6, in which the outer boom projects in the extension of the first boom section, optionally at a certain, small angle in relation thereto.
• the crane comprises means for locking the link device relative to the outer boom 2 when this is moving in the range between the parking position according to Fig. 3 and the intermediate position according to Fig. 6, i.e. within the parking range.
• the crane also comprises means for locking the link relative to the first boom section 1 when the outer boom 2 is moving with ⁇ in the above-mentioned working range.
• one and the same locking means is adapted, on the one hand, to lock the link relative to the outer boom when this is moving within the parking range and, on the other hand, to lock it relative to the first boom section when the outer boom is moving within the work ⁇ ing range.
• Figs 11 and 12 show, in combination with Figs 13-18, such a particularly preferred locking means which is able to lock the link device with respect to both the outer boom and the first boom section.
• This locking means comprises two latches 27, 27' which, via an articu ⁇ lation 28, are pivotally connected to the associated link plates 15, 15".
• the indivi ⁇ dual latch 27 has a first, suitably fork-shaped female member 29 serving, in locking, to receive the pivot pin 14.
• the latch also comprises a second female member in the form of a semicircular recess 30 which can receive or at least partially embrace the pin 26 serving as a stop.
• Each locking latch cooperates with a guide member 31, 31' which is fixed to the upper side of the first boom section in the immediate vicinity of the boom tip.
• the guide member is essentially hook-shaped and has an outer, arcuately rounded hook portion 32.
• FIG. 3 shows how the outer boom 2 in its parking position is located adjacent and substantially parallel to the first boom section 1. In this position, the outer boom cylinder 12 has been shortened to minimal length, i.e. the piston rod 12" is maximally retracted into the cylin ⁇ der 12'.
• the link device 13 is locked relative to the outer boom, such that the link device and the outer boom together form a rigid unit.
• the outer boom cylinder is lengthened or extended, the outer boom, together with the link device, will be pivoted outwards and upwards from the first boom section beyond the posi ⁇ tions shown in Figs 4 and 5, up to the intermediate posi ⁇ tion illustrated in Fig. 6. In this position, further pivotal movement of the link device 15 is prevented by the recess 25 engaging the associated stop pin 26.
• a continued extension of the outer boom cylinder 12 will therefore entail switching of the articulation point of the outer boom from the previous articulation point 16 to the arti- culation point 17, such that the outer boom, upon further extension of the cylinder 12 to the different positions shown in Figs 7-10, will operate within its working range with the pivot pin 17 as articulation point.
• the crane will operate in the reverse manner.
• the pivot pin 17 will still serve ⁇ s articulation point.
• the articulation point is however switched, so that a continued pivotal movement of the outer boom upwards towards the parking position according to Fig. 3 will take place about the articulation 16.
• Figs 13-18 which illu- strate the function of the locking latches 27, 27' (only the function of the latch 27 will be described herein ⁇ after, since it is obvious that the latch 27' acts in a similar way).
• the fork- shaped female member 29 engages the pivot pin 14, more precisely by engaging the exposed portion of the pin 14 located between the connecting ring 20 and the flange 18.
• the outer edge portion of the latch 27, or here its lower edge portion engages the upper side of the guide member 31.
• the fork-shaped or female member 29 of the latch will be maintained in continuous engagement with the pivot pin 14 by the latch continuously engaging and riding on the guide member 31, which means that the link and the outer boom are locked relative to each other so as to form a rigid unit. Also in the position according to Fig. 15, the locking engagement of the latch with respect to the pivot pin 14 is maintain ⁇ ed by the guide member 31 still preventing the latch from pivoting anticlockwise about the articulation 28. In Fig. 16, on the other hand, the latch has been disengaged from the guide member 31, whereby it becomes free to pivot anticlockwise about the articulation 28, whereupon the latch becomes free, with its female recess 30, to engage the stop pin 26 which has then already engaged the recess 25 in the terminal edge 24 of the link.
• the overall length of the outer boom (calculated as the distance between the articu ⁇ lation 17 and the tool carrier 11) and the link (calculat ⁇ ed as the distance between the articulations 16 and 17) may be substantially equal to or optionally only slightly smaller than the length of the first boom section 1 (cal- culated as the distance between the main articulation 3 and the link articulation 16).
• the length of the outer boom 2 in relation to the length of the link device 15 may vary quite considerably. In the Example shown in the draw ⁇ ings, the outer boom is about 3.5 times longer than the link device. It is however also possible to design the crane with, relatively speaking, considerably longer link devices. However, the outer boom should always be at least equally long as the link device. Suitably, the length of the outer boom should be in the range of 1-5 or preferably 2-4 times the length of the link device.
• the crane will, when the outer boom passes the intermediate position described above, automa- tically switch articulation points in order, when operat ⁇ ing within the working range, to pivot about an articu ⁇ lation point comparatively remote from the main articula ⁇ tion of the first boom section, while when moving within the parking range it will pivot about an articulation point situated closer to the main articulation of the first boom section.
• the effective length of the first boom section is considerably greater than the length of the first boom section proper, which means that the inventive crane can be parked using a relatively small space while at the same time it becomes much easier to operate the crane in the operative state since the outer boom can be pivoted about an articulation point located at a great distance from the main articula ⁇ tion of the first boom section.
• each unit consists of two cooperating, single-acting hydraulic cylinders, to which is connected a reciprocating straight rack which meshes with a gear rim integrated in the rotary device 7.
• Using two cylinder units confers the advantage that an even torque can be imparted to the post, which is twice the size of the torque achievable with only one cylinder.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Automation & Control Theory (AREA)
• Jib Cranes (AREA)
• Mechanically-Actuated Valves (AREA)
• Mechanical Control Devices (AREA)
• Suspension Of Electric Lines Or Cables (AREA)

Applications Claiming Priority (3)

Publications (2)

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ID=20386871

Family Applications (1)

Country Status (10)

Families Citing this family (7)

Family Cites Families (3)

• 1992
  • 1992-08-04 SE SE9202279A patent/SE470437B/sv not_active IP Right Cessation
• 1993
  • 1993-07-08 DE DE69327807T patent/DE69327807T2/de not_active Expired - Fee Related
  • 1993-07-08 ES ES93916360T patent/ES2142875T3/es not_active Expired - Lifetime
  • 1993-07-08 KR KR1019950700412A patent/KR0181569B1/ko not_active IP Right Cessation
  • 1993-07-08 JP JP06505221A patent/JP3074022B2/ja not_active Expired - Fee Related
  • 1993-07-08 EP EP93916360A patent/EP0726872B1/de not_active Expired - Lifetime
  • 1993-07-08 AU AU45942/93A patent/AU4594293A/en not_active Abandoned
  • 1993-07-08 WO PCT/SE1993/000622 patent/WO1994003389A1/en active IP Right Grant
  • 1993-07-08 AT AT93916360T patent/ATE189445T1/de not_active IP Right Cessation
• 1995
  • 1995-02-03 FI FI950494A patent/FI108026B/fi not_active IP Right Cessation

Non-Patent Citations (1)

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