DE2007197A1 - Display device or control for cranes - Google Patents

Description

Herne, 8000 Munich 23,

Freiligrathstrasse 19 _ Eisenacher Strasse 17

P.O. Box 140 Dipl.-Ing. RH Bahr _Pa , .. _Anw . _Bef2ler

P «t.-Anw. Herrmann-Trentepohl Dinl -Ph VQ Bdliarri R _p l ₇ | _pr Telephone: 39 S011

Telephone: 510 13 UI ρ I. - t * Π y S. CQUaru ΒΘΙΖΙβΓ 398012

r ;; W. Herrmann-Trerrtepohl

Bahrpatente Herne PATENTANWÄLTE Babetzpat Munich

Telex 08 229 853 Telex 05245 62

^Γ "1 bank accounts:

Bayrische Vereinsbank Munich 952 287 Dresdner Bank AG Herne 202 436 Postal check account Dortmund 558 68

Ref .: M 02 108 Lw / Pa

please indicate in the answer

Please send a letter to:

Munich

BALDWIN-LIMA-HAMILTON CORPORATION 2007 197

Chicago, Illinois, USA

Display device or control for cranes

The invention relates to cranes, crane vehicles or crane devices, in particular to display devices or Regulations for such cranes.

So far, load capacity indicators and control devices are for Known cranes mounted on vehicles, which signal an overload condition, which leads to a tilting or to a Failure of the crane parts could result. Such devices may include a strain gauge for measuring rope loading, whereby a signal emitted by this can be modified according to the boom angle and the boom length, to provide a reading of the load torque or a warning signal. Such devices were generally not satisfactory, since they are not able to simply and precisely determine all the parameters that make up the entire or effective Determine, generate and compensate for the load torque. These parameters include the rope or hook loading, the

009836 / U66 - 2 -

Vertical angle and the length of the boom, the vehicle and load orientation and ancillary loads as well as those induced in various ways by boom deflection, rope arrangement and environmental conditions. In order to compensate for parameters that have not been taken into account or that have not been precisely set up, it has hitherto been the practice to include an essential safety factor when setting maximum loads or loads that are permissible in terms of safety, whereby a consistent use of the crane's full capacity under many working conditions has been forbidden. In other known devices, the accuracy should be increased by despising to provide an indication of the actual or total load torque exerted on the vehicle by the boom and to modify the display according to the boom vertical angle. Such devices may include a fluid pressure measuring device which measures fluid pressure on the pressure side of the boom lift or extension cylinder. However, these latter devices have not consistently resulted in accuracies in practice due to errors induced by uncontrollable variations in fluid pressure on the low pressure side of the boom lift cylinder. In addition, these devices have failed when exactly the maximum permissible load moment should be displayed through all working areas of the boom, since they were not able to take into account the influence of secondary loads, which vary with regard to the boom length. Furthermore, such devices were not able to differentiate in the operation between the operating area of the boom, in which the maximum load moment is limited by loads that lead to tilting of the vehicle in contrast to other work areas where the crane stability is not critical, however, where other limitations such as B ₄ the length dtr

■ - 3 009836 / U66

Crane components are critical. For example, if a loaded crane boom is in a relatively low position, then so Overturning of the crane, rather than structural strength, may be critical. However, if the Boom pivoted into a relatively high position, the actual boom working radius or the load lever or the moment arm is reduced. i a load from the stability point of view would not be critical, so can from a constructive point of view due to the pressure loads generated critical, which can lead to failure of the boom components.

According to the invention, a display or control device for cranes is to be proposed in which the previously discussed Problems are bypassed »

In order to achieve this general goal, a device responsive to a cantilever orientation is provided in accordance with the invention for a material handling device with a boom mounted on a vehicle for pivoting movement about a horizontal axis suggested. The vehicle is set up so that it is supported on a support surface and the boom is designed so that it carries a load at the free end carries at a variety of points with a variety of moment arms about the horizontal axis. The facility includes a cantilever orienter for providing a signal in response to a change in the moment arm around the horizontal axis and moving devices operatively connected to the boom orientation means around them to operate. The movable device is in a first direction corresponding to the change in the length of the moment arm movable about the horizontal axis during movement of the boom in a first direction. To make a change in

- 4 009836 / U66

maximum permissible load torque that was induced as a result of movement through a work area, whereby a load-limiting influencing variable is not critical to return to another work area where another load-limiting Factor becomes critical, the movement-modifying devices are provided to control the movement of these Moving devices during the further movement of the boom in the first direction and to modify the operating characteristics of the cantilever orientation to change appealing facilities.

fe According to one embodiment of the invention, strain gauges, ζ. B. strain gauges, provided in order to read the total torque from the boom the horizontal pivot axis is exerted and the device may further comprise the boom extension means, the respond to longitudinal extension and retraction of the boom to the movement means to move a.

For example, embodiments of the invention will now be explained in more detail with reference to the accompanying drawings, in which

r Fig. 1 is a schematic view of a movable crane

which can be provided with a capacity display or control according to the invention;

Fig. 2 shows the typical crane load moment diagram, where the maximum permissible load moment on a crane due to different work areas and conditions and the effective Aueleger working area in English feet (also meters) against the moment

- 5 -009836 / H66

- 3 -

plotted around the pivot axis in inch-pounds (cm-kg) is;

Pig, 3 is a schematic, partially exploded view Representation of a load capacity display according to the invention, which is used in the mobile crane according to Fig. 1 is constructed;

Pig. 4 is a schematic representation of the parallel link arrangement However, the load capacity display according to FIG. 3 »shows the boom position corresponding to an increased Position of the boom;

Fig. 5 is a schematic illustration of the linkage movement modifying mechanism according to Fig. 4 »shows the mechanism in the position accordingly a retracted length of the telescopic boom; and

Fig. 6 is a schematic illustration of the linkage movement modifying mechanism of Fig. 5; however, shows a position of the mechanism corresponding to an extended length of the telescopic boom.

A capacity indicator according to the invention is designed for use on a conventional, movable crane 10 with its own propulsion. The crane comprises a driven multi-wheel vehicle 12 on which a boom which can be extended in the longitudinal direction is mounted and which is mounted for pivoting movement about the vertical and horizontal axes. The boom assembly includes a boom base portion 16 that is pivotable with a boom bracket or loader 18 for pivotal movement

- 6 -009836 / UeS

is connected to a horizontally arranged shipper pivot pin 20. An extensible fluid motor or hydraulic cylinder 22 is pivotable between the boom base sections 16 and boom support 18 connected by upper and lower cylinder pivot pins 21 and 23 to pivot the To move boom assembly 14 in a vertical plane or to lift. The boom support 18 is pivotably connected to the vehicle 12 for pivoting movement about a vertical axis, which is effected by a not shown BluiddreJ (piston) motor can be brought about. The boom assembly 14 further includes first and second extendable sections 24 and 26, which are received telescopically in the base section 16 and are designed so that they can be extended or retracted in the longitudinal direction by extendable fluid motors (not shown). It should be noted that that although two extendable sections are shown, any number of extendable sections can be provided can. A customary hand-operated fluid control (not shown) can be provided to lift and extend the To regulate the boom. On the outer end of the second extendable section 26 is a boom tip or a Permanently connected guide pulley block 28 is provided, over which a rope 30 is pulled in order to suspend a movable guide pulley block 32 which carries a load hook 34. Common Laterally and downwardly extendable spreader bars 36 can be adjusted on the sides of the vehicle for selective contact be stored with the ground for an additional stabilizing effect during certain lifting operations.

When moving cranes of this type are operated, the influencing factor is how the maximum rope load is limited when the boom assembly 14 is in a relatively low lift position or a work area near the

- 7 -009836 / U66

In full lines 1 is located, usually the crane stability against tilting. A typical diagram for maximum allowable crane load moment is shown in Fig. 2, where the effective boom working radius in English feet is plotted against the moment about the boom pivot axis in (English) pounds - (English) inches. While the boom assembly 14 is raised or retracted, the effective working radius or the load lever or the moment arm decreases or the maximum permissible load torque increases without this leading to tilting, as indicated by segment A of curve B of the load diagram shown in FIG is shown. The disturbance or secondary load torque decreases as the working radius decreases, as indicated by curve C. If stability were the only limiting factor, the maximum permissible load torque would continue to increase with an increasing working radius, as shown in segment D of curve B. If, however, the boom arrangement 14 is positioned so that it reaches a relatively short working radius, increased compared to that shown in dashed lines in FIG. 1, then the factor limiting the maximum permissible load moment is to be seen in the structural strength of the crane components. It is important that the structural strength of the components can be substantially less than the maximum allowable load from the point of view of stability. Furthermore, in some cases the maximum structural load element can remain constant in this shortened working radius range, while the working radius decreases, as indicated in segment E of curve F. In other cases, the maximum structural load moment can decrease while the working radius decreases, as shown in segment G of curve B. Eb has been found that the reverse point where the maximum permissible load moment ceases to increase when decreasing while the working radius and starts

009836/1466

decrease, varies in terms of boom length. For this reason there are a number of such turning points for an extendable or telescopic boom. In addition, it was found that in some cases the speed at which the maximum permissible load torque decreases, while the working radius in the working area decreases - where the Structural strength is critical (segment G of curve B) approaches the reversible of the value at which the maximum allowable Load torque increases while the working radius in the working area decreases, whereby stability can be critical fc (upper part of segment A). Based on this concept, a load capacity indicator is created according to the invention, which not only compensates for all of the parameters that determine the actual crane load, but also one Means creates to exactly the maximum permissible load moment both in the work area, where the stability is critical as well as in the work area, where structural strength becomes critical.

According to FIG. 3 of the drawings, a unique load capacity indicator is proposed according to the invention, the basic components of which can be summarized as follows. In order to read the total w or effective load moment W applied to the vehicle 12 by a load, as well as that induced by the parasitic loads, a strain gauge assembly 40 is operatively connected to the lower boom lift cylinder pivot pin 23 for reading the strain induced therein. The signal output of the strain measuring arrangement is given to an amplifier arrangement 41 and to a display arrangement 44. A positio meter arrangement 42 is connected to a linkage arrangement 46 which is dependent on the boom orientation and which adjusts the potentiometer arrangement according to the working radius, which is

- 9 009836 / U6G

angle and length is fixed. A signal from the potentiometer assembly 42 is thus given to the display arrangement 44, which the last-mentioned signal with that of the strain gauge arrangement 40 compares and indicates a percentage of the maximum permissible load torque. The linkage assembly 46 includes a linkage movement modifying mechanism 48 which is operable with a boom extension responsive device 50 is connected to adjust the point at which boom movement is modified according to the boom length. These arrangements can be accommodated in a housing 51 which is stuck on the boom base portion 16.

In particular, the derivation gauge strip assembly 40, which is of a type similar to the SR-4 strain gauges of US Pat BLH Electronics is to deliver an electrical signal, the size of which is proportional to the total load torque the boom assembly 14 is. The strain gauge assembly is with amplifier assembly 41, display assembly 44 and a suitable electrical power source, for example the vehicle ignition switch 52 through electrical leads 54, 55 and 56 connected. The display assembly 44 may include an electrically calibrated meter 58 which shows a percentage Indicates proportion of the permissible load torque about the pivot axis and can also be an electric light 60 for warning include in an overload condition.

The boom orientation responsive linkage assembly 46 includes a support arm 62 pivotally supported on the boom base portion 16 by a pivot pin 70. The support arm 62 includes a horizontal leg that is attached to first and second vertical legs 64 and 66 , respectively. The lower end of the second leg 66 is pivotable with a loading or release link 67

009836 / U66

the boom support or shipper 18 below the pivot pin 20 connected.

The upper ends of the first and second vertical legs 64 and 66 are pivotably attached by pivot pins 68 and 70 the lower ends of the substantially vertical first and second parallel link arms 72 and 74 are connected. the upper ends of the parallel rod arms 72 and 74 are spring-loaded by a spring 75 for pivoting clockwise, as shown in Fig. 3, and are by pivot pins 76 and 78 at opposite ends of a horizontal Leg 80 of a "!" -Shaped cam follower rail arrangement 82. The cam follower rail arrangement 82 further includes a vertical leg 84 having a vertically extending slot 86 therein. The slot 86 becomes clear a cam roller 87 which forms part of the boom extension assembly 50. It should be noted that while the boom assembly 14 is pivoted about the boom pivot pin 20, the horizontal leg 63 of the support arm 62 in an absolutely horizontal position due to a parallelogram effect caused by the arrangement of its connection to the boom base portion 16 and the shipper handlebar 67, both of which are pivotally connected to the shipper 18.

Pivotable on pivot pin 68 on the first vertical Leg 64 of the support arm 62 is supported by the lower end of a direct drive arm 89 »whose upper end has notches and is designed to bear against a direct drive stop pin 88 which is attached to an intermediate member the length of the first parallel link arm 72 is attached.

The linkage movement modifying mechanism 48 includes

- 11 -009836 / U68

a drive link 90, the lower end of which is pivotally mounted on the pivot pin 70, the pivotable the second vertical leg 66 of the support arm 62 carries. Mounted between the length of the drive link 90 by a pivot pin 92 is a motion-modifying link 94, the lower end is pivotally connected to the lower end of a movement modifying arm 96 which is pivotable is mounted on the pivot pin 68. The upper end of the arm 96 is notched and designed so that it rests against a stop pin for the reverse movement, which is mounted on an intermediate point over the length of the direct drive arm. (

The responsive to the extension of the boom assembly 50 includes a spring motor 104 which is drivingly with a Cable drum 106 is connected to cause a cable 108 to be rolled up. The free end of the cable 108 is to one fixed guide roller block 28 of the boom assembly 14 connected. The cable drum 106 is provided with a drive shaft 110, on which a bevel gear 112 is positioned which drivingly meshes with a pinion 114 which is on one end a threaded barrel block support shaft 116 is. The shaft 116 is rotatable on the boom base portion 16 by first and second pillow blocks or pillow blocks 118 and 119 worn. A second threaded abutment 120 is movably mounted on the threaded part of the shaft 116 and carries a first cam roller 87 while rotating, the side of it protrudes and a second cam roller 121, rotatably mounted on the related upper end. The second corner roll 121 carries a cam rail 122, one inward end of which is pivotable on the upper end of the first pedestal bearing 118 is stored. One end of a flexible push-pull cable 124 is connected to the cam rail 122, the other end

- 12 009836 / U66

of the cable 124 is carried on the second parallel link arm and connected to the upper end of the drive linkage 90. The second cam rail 122 is designed so that the position of the drive linkage 90 relative to the second parallel linkage arm 74 according to the boom length, such as. shown in _s g | 5 Figures 5 and 6, can be adjusted. It should be noted that while boom extension responsive device 50 is shown laterally displaced from linkage assembly 46 in FIG Fig. 3 shown, indicated.

The potentiometer arrangement 42 should have an electrical resistance, which is directly variable with the working radius, as determined by the boom angle and length. These Arrangement includes first and second resistance potentiometers 142 and 144 with movable first and second wipers or 148 to adjust their resistance. The wipers 146 and 148 operate through the movement of the first and second cam follower 150 and 152 adjusted. A spreader bar switch 154, which can be brought into a working position by moving the spreader bars 36, is provided to send a signal from either the first or second potentiometer 142 or 144 to the display assembly 44.

The potentiometer 142 is adjusted by the movement of the direct drive arm 89, which is connected to a first drive linkage 132 is connected to a first crank arm 134. The first crank arm 134 is spring loaded by a spring 135 set and rotates clockwise according to Fig. 3 and is arranged horizontally on a first

- 13 009836 / U66

Neten shaft 136 attached which is rotatable on the boom base portion 16 is stored. A first cam plate 138 is supported on shaft 136 so that lateral movement of the first drive linkage 132 to rotate the first cam plate 138 and move the first cam follower 150 will lead.

The second potentiometer 144 is adjusted by the movement of a second drive linkage 158, which is pivotable is connected between the second parallel arm 74 and a second crank arm 160. The second crank arm 160 is attached to a second horizontally disposed shaft 162 which is rotatably supported on the boom base section 16. A second cam plate 164 'which can have a shape different from that of the first cam plate 138 is mounted on the shaft 162 so that a lateral movement of the second drive linkage 158 to a rotation of the second Cam plate 164 and will result in movement of the second cam follower 152.

It should be noted that although the cams 138, 164 are used together with simple variable resistance potentiometers 142 and 144 can be used, but in some cases it may be desirable to use potentiometers with a variable tap or variable designed potentiometer for this arrangement, which eliminates the need to providing the cam disks is eliminated.

The mode of operation of the entire device with the spreader bars adjusted to carry the crane is as follows:

After the boom assembly 14 is loaded, the strain gauge assembly reads 40 the expansion of the lower cylinder pivot pin 23 and sends an electrical signal through the

009836 / U66 -H-

Amplifier arrangement 41 to the indicator arrangement 44. The magnitude of the signal from the extensometer arrangement 40 is proportional to the magnitude of the total load torque which is caused by the Boom pivot pin 20 is exercised. This signal is compared with a signal from the first potentiometer 142, which is given by the switch 154 and varies according to the working radius. Is the boom assembly 14 positioned in an interst and fully extended position, the boom orientation responsive linkage assembly 46 is positioned as shown in FIG. The maximum

Ψ permissible load torque, which is indicated by segment A of curve B in Fig. 2, reaches a minimum. After the boom assembly 14 has been pivoted upwards or after it has been lifted, the bearing arm 62 pivots about the pivot pin 70, but is held in an absolutely horizontal position due to the parallelogram effect that is induced by this connection of the boom assembly 14, the loader linkage 17 and the loader 18 . Such pivotal movement between linkage assembly 46 and boom assembly 14 causes cam roller 87, which is stationary at that location, to pivot parallel link arms 72 and 74 in a clockwise direction, as shown in FIG. 3, counter to that in FIG

position shown in k. Such arm movement allows for lateral movement of the spring-loaded drive linkage 132, reducing the resistance of the potentiometer 142 is changed by an amount proportional to the additional load torque, which can be safely withstood due to a reduction in the torque arm.

Retraction of the first or second extensible extension arm section β 24 and 26 enables the spring motor 104, the Rotate the cable drum 106, whereby the cable IO8 is rolled up. One rotation of the Troemel 106 creates a Rotation of the barrel block support shaft 166, causing the block 120

009836/1466

runs laterally along the shaft 116. A sideways movement of the barrel block 120 provides a further pivoting movement of the parallel rod arms 72 and 74 due to the contact of the cam roller 87 under stop within the Noeken ram rail slot 83 and thus the change in potentiometer resistance. This type of movement continues during the boom assembly lift or retraction, until the motion modifying stop pin 98 on the direct drive linkage 89 clockwise until has been pivoted to a point just before that shown in Fig. 4, where it is towards the end of the movement-modifying Arm 96 is applied, which has been moved by the drive link 90. The motion modifying arm 96 turns counterclockwise corresponding to the retraction of the boom due to its connection to the push-pull cable 124 and the Cam rail 122 moves. Another upward swivel movement or retraction of the boom ensures that that the motion modifying arm 96 moves clockwise and similarly the direct drive link 89 carries, whereby opposite potentiometer 142 is adjusted to change the resistance and to prevent the setting of the maximum permissible load torque.

If the crane 10 without stabilizing effect due to the Spreading bars actuated, this leads to significantly different maximum permissible load torque characteristics. A typical course of the maximum permissible load torque when a crane is "operated on rubber" is through the Have H shown in Fig. 2. It turns out that maximum load moments are essential for corresponding work areas are smaller than that of a crane, which is

- 16 009836/1466

Holme was stabilized. To compensate for this reduction, the spreader bar switch 154 is moved to a To send the signal from the second potentiometer 144 to the display arrangement 44. The second cam plate 164 is like that designed that a lifting or retraction of the Auilegeranordnung 14 and thus a pivoting of the parallel arms 72 and 74 lead to a suitable movement of the second drive link 158 and the second grinder 148 the maximum Allow the permissible load torque to be specified, which is indicated by the curve H in FIG. 2.

It should be noted that the drive link 90 can be designed so that it either the movement of the direct Drive link to any desired extent during further upward movement or retraction the boom assembly interrupts or reverses. In any case, the accommodation or turning point, which varies according to the boom length, can be precisely determined in order to distinguish between the working area in where stability is critical compared to the work area where structural strength is critical and where that maximum permissible load element is significantly reduced. Similarly, the potentiometer drive cams can be used 138 and 140 can be designed to provide any desired degree of change in characteristics.

Although the invention has been described as a load capacity indicator, it is clear to a person skilled in the art that it is based on the Principle is also applicable to control devices for the crane boom movement, with warning signals through control features can be supplemented and replaced.

Furthermore, various novel aspects of the invention can advantageously be used in a device for the crane boom position

009836 / U66 - 17 -

be installed, in which the usual devices are provided to indicate regulation or orientation of the boom.

Finally, although only one embodiment of the invention has been disclosed, it should be pointed out that the A wide variety of mechanical modifications or substitutions can be made, especially for the drive and Linkage arrangements without departing from the scope of the invention.

Patent claims:

009836/1466

Claims (19)

- 18 -patent claims: A device for a device for handling a material which responds to the cantilever orientation a boom mounted on a vehicle for pivoting movement about a horizontal axis, the vehicle being designed so that it is on a load-bearing Surface is supported, the boom being adapted to carry a load on the free end at a plurality of locations with a plurality of moment arms carries the horizontal axis, the device comprising boom orientation means which supply a signal dependent on a change in this moment arm and Movement devices are effectively connected to the boom orientation device for actuation thereof and these movement devices in a first direction corresponding to a change in the length of the moment arm the horizontal axis are movable in a first direction during movement of the boom, characterized by movement modifying means for modifying the movement of these moving means during further movement of the boom (14) in the first direction such that the operating characteristics of the boom orientation responsive Facility can be changed. 2. Boom orientation device according to claim 1, characterized characterized in that the movement modifying device is movement reversing device to reverse the direction of movement of this movement device has during this further movement of the boom. - 19 -009836/1466 3. Facility responding to cantilever orientation. Claim 1, characterized in that this movement-modifying device has interrupting means to interrupt the movement of the moving devices during this further movement of the boom. 4. response device according to claim 2, characterized in that that the movement reversing device the movement of the movement devices after the movement of the The boom is steered through a zone in which tilting of the vehicle is critical, namely before the movement through a zone where cantilever structure strength is critical. 5. response device according to claim 1, characterized g e k e η η ze i c h η e t that this boom orientation device has a signal dependent on the movement of the boom supplies around the horizontal axis, the boom still being extendable in the longitudinal direction and this device continue to respond to the boom extension depending on the extension or the retraction of the boom in the longitudinal direction to these movement devices and this movement modifying facilities to move. 6. response device according to claim 5, characterized in that it is on the boom extension appealing device is associated with the movement-modifying devices to change the position, on which the movement modifying device controls the movement of the moving devices in accordance with the boom length modified. - 20 - 009836 / U66 BATH ORIGINAL 7. response device according to claim 6, marked e t by a strain measuring device for measuring the magnitude of the load absorbed by the boom, the load measuring device cooperates with this boom orientation device and one for boom orientation and load "supplies indicative signal. 8. response device according to claim 7, characterized by one with the boom orientation device and connected to this load measuring device ψ warning device, the warning device being an indicator the overload on the device provides. 9. response device according to claim 8, characterized in that this load measuring device Having strain gauges for measuring total movement about the horizontal axis to which the boom is pivotable, wherein the boom orientation device has a potentiometer, which with the extensometer device and the moving device cooperate. * 10. response device according to claim 9, characterized that the movement device first eccentric means for varying the adjustment size of the Potentiometer training per unit boom movement as well as second eccentric means to the movement size of this to vary the motion-modifying devices. 11. response device according to claim 9 »characterized in that the potentiometer training a has shaped potentiometer with multiple tap. - 21 -009836/1466 12. Response.einrich.turg according to claim 10, characterized characterized in that the vehicle is a self-propelled truck fitted with rubber tires with movable spreader bars to stabilize them, the device furthermore having second movement devices which is operatively connected to the cantilever orientation device and in a first Direction corresponding to a change in the length of the movement arm around this horizontal axis during movement of the boom is movable in a first direction, wherein the second movement device is third eccentric means to vary the adjustment size of the potentiometer training per unit of boom movement after movement of the Has spreader bar device in a rest position. 13. Load capacity device for a material handling device with a boom that can be extended in the longitudinal direction, carrier devices mounted on a vehicle for supporting the boom for pivoting movement about a horizontal axis, with the vehicle on a Can store support surface, characterized by load devices for reading the marked by the boom total moment exerted about the horizontal axis; Boom orientation devices that interact with the loading devices and a signal accordingly provide the overload of the boom at a plurality of locations around the horizontal axis; Movement devices, operatively connected to the boom orientation device for activation thereof, the movement devices are movable according to the movement of the boom around the horizontal Achsxe; and through boom extension devices, the extension or retraction of the boom in the longitudinal direction to move it Address movement devices. 009836 / U66 -22- 14. Responding to the boom orientation device according to claim 13, characterized in et, that the loading device has strain gauge formations between the boom and the carrier device are interposed. 15. Response device according to claim 14, characterized by the movement reversing devices for reversing the direction of movement of these movement devices during the movement of the boom in a first direction. 16. Carrying facility for a material handling device with a boom, support devices mounted on a vehicle for carrying the boom for a pivoting movement about a horizontal axis, wherein the vehicle is adapted to be on a Can store support surface and the device cantilever orientation means for delivering a signal accordingly the moment arm length around the horizontal axis, characterized by extensometer devices between boom and boom support devices for measuring the around the horizontal axis total moment exerted, the extensometer device cooperates with the boom orientation device. 17. Load capacity device according to claim 16, characterized in that the strain gauge device measures the total load moment on the horizontal axis around which the boom can be pivoted. - 23 -009836 / U66 18. Load capacity device according to claim 17, characterized characterized in that the boom is extendable in the longitudinal direction and the support devices continue extendable fluid motor formations for moving the Have boom and the fluid motor formation pivotable with the boom and the rest of the support means is connected by pivot pins and the strain gauge means with the pivot pin means for reading is connected by their elongation. 19. Load capacity device for a material handling device with a boom, supported on a vehicle provided with Gurami wheels for the Bearing the boom for pivoting movement about a horizontal axis, the vehicle being made with movable spreader bar formations for stabilizing the vehicle on a supporting surface, wherein the spreader bar devices are movable from a working position to a rest position and load measuring devices are provided, to provide a signal proportional to the moment exerted by the boom around the horizontal axis, wherein the boom orientation means with the loading means for modifying this signal cooperate corresponding boom orientation and the boom orientation device has first movement means to first signal modification characteristics to deliver after moving the Spreizholmausbildung in a working position, gekennzeichn et cLffch second movement devices to deliver second ones Signal modification characteristics after moving the spreader bar formations to a rest position. 009836 / U66 Blank page