CA2143493A1 - Track-bound rotary crane - Google Patents
Track-bound rotary craneInfo
- Publication number
- CA2143493A1 CA2143493A1 CA002143493A CA2143493A CA2143493A1 CA 2143493 A1 CA2143493 A1 CA 2143493A1 CA 002143493 A CA002143493 A CA 002143493A CA 2143493 A CA2143493 A CA 2143493A CA 2143493 A1 CA2143493 A1 CA 2143493A1
- Authority
- CA
- Canada
- Prior art keywords
- crane
- machine frame
- signal transmitter
- drive
- boom
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B61—RAILWAYS
- B61D—BODY DETAILS OR KINDS OF RAILWAY VEHICLES
- B61D15/00—Other railway vehicles, e.g. scaffold cars; Adaptations of vehicles for use on railways
- B61D15/02—Breakdown cranes
-
- 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
- B66C23/50—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 mounted on railway vehicles, e.g. breakdown cranes
-
- 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
- B66C23/88—Safety gear
- B66C23/90—Devices for indicating or limiting lifting moment
- B66C23/905—Devices for indicating or limiting lifting moment electrical
-
- E—FIXED CONSTRUCTIONS
- E06—DOORS, WINDOWS, SHUTTERS, OR ROLLER BLINDS IN GENERAL; LADDERS
- E06C—LADDERS
- E06C5/00—Ladders characterised by being mounted on undercarriages or vehicles Securing ladders on vehicles
- E06C5/32—Accessories, e.g. brakes on ladders
- E06C5/36—Safety devices against slipping or falling of ladders; Safety devices against overloading ladders
Abstract
ABSTRACT OF THE DISCLOSURE
A rotary crane comprises a hydraulic cylinder drive for vertically adjusting an extensible crane boom, the hydraulic cylinder drive including a signal transmitter indicating the hydraulic pressure in the cylinder drive, a drive for changing the length of the extensible boom, a further drive for rotating the rotary crane on a machine frame about a substantially vertical axis whereby the crane boom may assume different angles of rotation with respect to a longitudinal direction of the machine frame, and a control for generating a reference value signal corresponding to a maximum permissible load for the crane in a given operating position, the control being associated with the hydraulic cylinder drive for vertically adjusting the extensible crane boom, the drive for changing the extensible boom length and the further drive for rotating the rotary crane, the control being connected to the signal transmitter indicating the hydraulic pressure in the cylinder drive and to at least one measuring device selected from the group consisting of a signal transmitter indicating the superelevation of the track, a signal transmitter indicating the angle of rotation of the rotary crane, a signal transmitter indicating changes in the extensible boom length, and a signal transmitter indicating the position of retractible support jacks for the machine frame. The control comprises a differential unit for comparing the reference value signal with an output signal of the signal transmitter indicating the hydraulic pressure in the cylinder drive, and a circuit breaker device is connected to the control for shutting down the drives when the differential unit indicates an overload. - 20 -
A rotary crane comprises a hydraulic cylinder drive for vertically adjusting an extensible crane boom, the hydraulic cylinder drive including a signal transmitter indicating the hydraulic pressure in the cylinder drive, a drive for changing the length of the extensible boom, a further drive for rotating the rotary crane on a machine frame about a substantially vertical axis whereby the crane boom may assume different angles of rotation with respect to a longitudinal direction of the machine frame, and a control for generating a reference value signal corresponding to a maximum permissible load for the crane in a given operating position, the control being associated with the hydraulic cylinder drive for vertically adjusting the extensible crane boom, the drive for changing the extensible boom length and the further drive for rotating the rotary crane, the control being connected to the signal transmitter indicating the hydraulic pressure in the cylinder drive and to at least one measuring device selected from the group consisting of a signal transmitter indicating the superelevation of the track, a signal transmitter indicating the angle of rotation of the rotary crane, a signal transmitter indicating changes in the extensible boom length, and a signal transmitter indicating the position of retractible support jacks for the machine frame. The control comprises a differential unit for comparing the reference value signal with an output signal of the signal transmitter indicating the hydraulic pressure in the cylinder drive, and a circuit breaker device is connected to the control for shutting down the drives when the differential unit indicates an overload. - 20 -
Description
- :
21~3~93 BACKGROUND OF THE INVENTION
1. Field of the Invention The present invention relates to a machine comprising a machine frame movable along a track on undercarriages supporting the machine frame on the track, the machine frame carrying a rotary crane comprising an extensible boom and ; ;~
drives for operating the crane.
~. ...., .-2. Description of the Prior Art U. S. patent No. 4,399,881 discloses such a track-bound rotary crane, which includes an arrangement for continuously monitoring and indicating the loads on the respective wheels -~-of the undercarriages. In addition, a hydraulic cylinder is ~ - -arranged between the machine frame and each undercarriage for ~ --equalizing the loads on the wheels. In this system, it is possible to take the additional load produced by a rotation of the crane into account in the calculation of the wheel loads, for which purpose an electrical pressure pickup is associated with each hydraulic cylinder. ` ;
U. S. patent No. 4,113,111 also discloses such a vehicle `
equipped with an arrangement for equalizing the wheel loads, - -`
which is comprised of shock-absorbing pressure cylinders mounted between the undercarriages and the machine frame. The upper and lower cylinder chambers of the shock absorbers at one side of the vehicle are interconnected by conduits which ~ ".
2 1 ~ 3 may be blocked. In this way, a desired torsion may be imparted to the machine frame so that the more heavily loaded -wheels may be relieved and the less heavily loaded wheels may be subjected to an additional load.
:
SUMMARY OF THE INVENTION
.. ....
, : . ::. ~:.
It is the primary object of this invention to provide a track-bound rotary crane of the first-indicated type, which attains the highest attainable safety in each operating - -position of the crane while at the same time achieving its ;
maximal operating capacity.
In a machine comprising a machine frame movable along a track on undercarriages supporting the machine frame on the track, the machine frame having vertically adjustable support jacks and drives for vertically adjusting the support jacks between a retracted position during movement of the machine frame along the track and an extended operating position for `
support of the machine frame on the track, and the machine frame carrying a rotary crane comprising an extensible boom, the above and other objects are accomplished according to the invention with a rotary crane comprising a hydraulic cylinder drive for vertically adjusting the extensible crane boom, the ~ b hydraulic cylinder drive including a signal transmitter indicating the hydraulic pressure in the cylinder drive, a drive for changing the length of the extensible boom, and a further drive for rotating the rotary crane on the machine frame about a substantially vertical axis whereby the crane boom may assume different angles of rotation with respect to a 2~ ~3493 longitudinal direction of the machine frame. The rotary crane further comprises a control associated with the nydraulic cylinder drive for vertically adjusting the extensible crane boom, the drive for changing the extensible boom length and the further drive for rotating the rotary crane. The control is connected to the signal transmitter indicating the : . ~ . - ::
hydraulic pressure in the cylinder drive and to at least one measuring device selected from the group consisting of a signal transmitter indicating the superelevation of the track, a signal transmitter indicating the angle of rotation of the rotary crane, a signal transmitter indicating changes in the extensible boom length, and a signal transmitter indicating the position of the support jacks, whereby a reference value signal corresponding to a maximum permissible load for the ;-~ -crane in a given operating position is generated, and the -control comprises a differential comparator unit for comparing the reference value signal with an output signal of the signal transmitter indicating the hydraulic pressure in the cylinder drive. An overload device is connected to the control for controlling the drives when the differential comparator unit indicates an overload. `~
Such a machine makes it possible to use without any problems the maximal load moment in every operating position . : . :: .: .
of the rotary crane without endangering the stability of the~ -machine. This enables the track-bound rotary crane to be used efficiently at its highest capacity. The differential ~
comparator unit in the control assures a continuous and -~ -constant comparison between a reference value signal which -depends on the operating position of the crane and corresponds - 3 - ~ -: ' to the maximum load which the crane may carry, and the actual value signal emitted by the signal transmitter indicating the hydraulic pressure in the vertical adjustment hydraulic cylinder drive. The different signal transmitters monitoring practically all operating positions of the crane make it possible to take into account just about every crane position By including such parameters as the track superelevation, for example, the load moment for the crane may be increased up to 15% at a maximum superelevation where the crane has been -: ~. ,, rotated toward the higher side of the superelevated track. On the other hand, when the rotary crane is turned to the opposite, lower track side, a corresponding reduction of the ~ ~`
maximal load and its corresponding reference value signal is automatically achieved so that the crane may be used in track `
curves with optimal efficiency and safety. The system excludes operating mistakes due to human error.
According to a preferred feature of the present - ;~
invention, the crane boom comprises a first arm pivotal about a horizontal axis extending transversely to the machine frame and a second arm slidably displaceable with respect to the -~
first arm for changing the length of the extensible crane boom, the drive for changing the length comprising a hydraulic cylinder for displacing the second arm with respect to the first arm, and the signal transmitter indicating changes in ~ -the extensible boom length being a cable potentiometer. This arrangement provides a very simple and dependable structure for monitoring the length of the crane boom for determining the maximum load moment for a given crane boom length.
21~3~93 BACKGROUND OF THE INVENTION
1. Field of the Invention The present invention relates to a machine comprising a machine frame movable along a track on undercarriages supporting the machine frame on the track, the machine frame carrying a rotary crane comprising an extensible boom and ; ;~
drives for operating the crane.
~. ...., .-2. Description of the Prior Art U. S. patent No. 4,399,881 discloses such a track-bound rotary crane, which includes an arrangement for continuously monitoring and indicating the loads on the respective wheels -~-of the undercarriages. In addition, a hydraulic cylinder is ~ - -arranged between the machine frame and each undercarriage for ~ --equalizing the loads on the wheels. In this system, it is possible to take the additional load produced by a rotation of the crane into account in the calculation of the wheel loads, for which purpose an electrical pressure pickup is associated with each hydraulic cylinder. ` ;
U. S. patent No. 4,113,111 also discloses such a vehicle `
equipped with an arrangement for equalizing the wheel loads, - -`
which is comprised of shock-absorbing pressure cylinders mounted between the undercarriages and the machine frame. The upper and lower cylinder chambers of the shock absorbers at one side of the vehicle are interconnected by conduits which ~ ".
2 1 ~ 3 may be blocked. In this way, a desired torsion may be imparted to the machine frame so that the more heavily loaded -wheels may be relieved and the less heavily loaded wheels may be subjected to an additional load.
:
SUMMARY OF THE INVENTION
.. ....
, : . ::. ~:.
It is the primary object of this invention to provide a track-bound rotary crane of the first-indicated type, which attains the highest attainable safety in each operating - -position of the crane while at the same time achieving its ;
maximal operating capacity.
In a machine comprising a machine frame movable along a track on undercarriages supporting the machine frame on the track, the machine frame having vertically adjustable support jacks and drives for vertically adjusting the support jacks between a retracted position during movement of the machine frame along the track and an extended operating position for `
support of the machine frame on the track, and the machine frame carrying a rotary crane comprising an extensible boom, the above and other objects are accomplished according to the invention with a rotary crane comprising a hydraulic cylinder drive for vertically adjusting the extensible crane boom, the ~ b hydraulic cylinder drive including a signal transmitter indicating the hydraulic pressure in the cylinder drive, a drive for changing the length of the extensible boom, and a further drive for rotating the rotary crane on the machine frame about a substantially vertical axis whereby the crane boom may assume different angles of rotation with respect to a 2~ ~3493 longitudinal direction of the machine frame. The rotary crane further comprises a control associated with the nydraulic cylinder drive for vertically adjusting the extensible crane boom, the drive for changing the extensible boom length and the further drive for rotating the rotary crane. The control is connected to the signal transmitter indicating the : . ~ . - ::
hydraulic pressure in the cylinder drive and to at least one measuring device selected from the group consisting of a signal transmitter indicating the superelevation of the track, a signal transmitter indicating the angle of rotation of the rotary crane, a signal transmitter indicating changes in the extensible boom length, and a signal transmitter indicating the position of the support jacks, whereby a reference value signal corresponding to a maximum permissible load for the ;-~ -crane in a given operating position is generated, and the -control comprises a differential comparator unit for comparing the reference value signal with an output signal of the signal transmitter indicating the hydraulic pressure in the cylinder drive. An overload device is connected to the control for controlling the drives when the differential comparator unit indicates an overload. `~
Such a machine makes it possible to use without any problems the maximal load moment in every operating position . : . :: .: .
of the rotary crane without endangering the stability of the~ -machine. This enables the track-bound rotary crane to be used efficiently at its highest capacity. The differential ~
comparator unit in the control assures a continuous and -~ -constant comparison between a reference value signal which -depends on the operating position of the crane and corresponds - 3 - ~ -: ' to the maximum load which the crane may carry, and the actual value signal emitted by the signal transmitter indicating the hydraulic pressure in the vertical adjustment hydraulic cylinder drive. The different signal transmitters monitoring practically all operating positions of the crane make it possible to take into account just about every crane position By including such parameters as the track superelevation, for example, the load moment for the crane may be increased up to 15% at a maximum superelevation where the crane has been -: ~. ,, rotated toward the higher side of the superelevated track. On the other hand, when the rotary crane is turned to the opposite, lower track side, a corresponding reduction of the ~ ~`
maximal load and its corresponding reference value signal is automatically achieved so that the crane may be used in track `
curves with optimal efficiency and safety. The system excludes operating mistakes due to human error.
According to a preferred feature of the present - ;~
invention, the crane boom comprises a first arm pivotal about a horizontal axis extending transversely to the machine frame and a second arm slidably displaceable with respect to the -~
first arm for changing the length of the extensible crane boom, the drive for changing the length comprising a hydraulic cylinder for displacing the second arm with respect to the first arm, and the signal transmitter indicating changes in ~ -the extensible boom length being a cable potentiometer. This arrangement provides a very simple and dependable structure for monitoring the length of the crane boom for determining the maximum load moment for a given crane boom length.
~ ~ ~ 3 ~ ~ 3 The pivoting angle of the crane boom arms may be monitored ready with an arrangement wherein the crane boom further comprises a support arm, the hydraulic cylinder drive for vertically adjusting the extensible crane boom being connected to the support arm and the first arm being linked to ~;
the support arm for pivoting about the horizontal axis, further comprising a hydraulic cylinder drive linking the first arm to the support arm for pivoting the first arm, and a ~ -measuring device for indicating the angle between the support and first arms. This enables an increase in the maximally permissible load moment due to a position of the crane boom arms closer to the vertical than the horizontal to be taken into account. The angle indicating measuring device may be a cable potentiometer arranged to indicate changes in the length of the hydraulic cylinder drive for pivoting the first arm or a rotary potentiometer whose axis of rotation is coaxial with the horizontal axis.
According to another preferred feature, the rotary crane further comprises a support column mounted on the machine frame for rotation about the vertical axis by the further ~ ~
drive, the support column carrying the support arm and the `~- `
hydraulic cylinder drive connected thereto, a counterweight mounted on the support column for displacement in a horizontal plane in a dir~ction extending perpendicularly to the horizontal axis, and a drive for displacing the counterweight.
Such a structure provides a very efficient crane operating `-~
within the loading gage of the track.
'- :, ~.
the support arm for pivoting about the horizontal axis, further comprising a hydraulic cylinder drive linking the first arm to the support arm for pivoting the first arm, and a ~ -measuring device for indicating the angle between the support and first arms. This enables an increase in the maximally permissible load moment due to a position of the crane boom arms closer to the vertical than the horizontal to be taken into account. The angle indicating measuring device may be a cable potentiometer arranged to indicate changes in the length of the hydraulic cylinder drive for pivoting the first arm or a rotary potentiometer whose axis of rotation is coaxial with the horizontal axis.
According to another preferred feature, the rotary crane further comprises a support column mounted on the machine frame for rotation about the vertical axis by the further ~ ~
drive, the support column carrying the support arm and the `~- `
hydraulic cylinder drive connected thereto, a counterweight mounted on the support column for displacement in a horizontal plane in a dir~ction extending perpendicularly to the horizontal axis, and a drive for displacing the counterweight.
Such a structure provides a very efficient crane operating `-~
within the loading gage of the track.
'- :, ~.
2,~ 3 The signal transmitter indicating the superelevation of the track may comprise a pendulum mounted on the machine frame for pivoting about a horizontal axis extending in the longitudinal direction, the pendulum carrying a damped :~-pendulum weight, which has the advantage that the track :: :~
superelevation may be dependably monitored even if the shut~
off device for the shock absorbers of the undercarriages does ~ ;~
not function properly.
Furthermore, the signal transmitter indicating the angle of rotation of the rotary crane preferably has a positive and a negative signal range respectively positioned at a left and -~
a right half of the machine frame on respective sides of a ~`
common zero position defined by a plane extending in the longitudinal direction through the vertical axis. This makes it possible accurately to determine the angular position of ~ -the crane boom not only relative to the longitudinal direction but also with respect to the left and right halves of the machine frame.
Finally, the machine may further comprise an auxiliary frame mounted on the machine frame for rotation about a vertical axis over an angle of rotation of 180~, the rotary crane being mounted on the auxiliary frame at one end thereof, as seen in the longitudinal direction. This makes it possible simply and rapidly to relocate the crane from one end of the machine frame to the other by turning the auxiliary frame, rather than having to turn around the entire machine, which would be time-consuming and creates problems with the stability of the machine.
superelevation may be dependably monitored even if the shut~
off device for the shock absorbers of the undercarriages does ~ ;~
not function properly.
Furthermore, the signal transmitter indicating the angle of rotation of the rotary crane preferably has a positive and a negative signal range respectively positioned at a left and -~
a right half of the machine frame on respective sides of a ~`
common zero position defined by a plane extending in the longitudinal direction through the vertical axis. This makes it possible accurately to determine the angular position of ~ -the crane boom not only relative to the longitudinal direction but also with respect to the left and right halves of the machine frame.
Finally, the machine may further comprise an auxiliary frame mounted on the machine frame for rotation about a vertical axis over an angle of rotation of 180~, the rotary crane being mounted on the auxiliary frame at one end thereof, as seen in the longitudinal direction. This makes it possible simply and rapidly to relocate the crane from one end of the machine frame to the other by turning the auxiliary frame, rather than having to turn around the entire machine, which would be time-consuming and creates problems with the stability of the machine.
2 1 il 3 ~
BRIEF DESCRIPTION OF THE DRAWING
The above and other objects, advantages and features of the present invention will become more apparent from the ~--following detailed description of a now preferred embodiment thereof, taken in conjunction with the accompanying, somewhat schematic drawing wherein :','",."~... ~, FIG. 1 is a side elevational view showing a machine according to this invention; and FIG. 2 is a simplified circuit diagram of the control circuit.
''~' ~ '~ ..' DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring now to the drawing and first to FIG. 1, there is shown machine 1 comprising machine frame 2 movable along track 40 on undercarriages 3 supporting the machine frame on the track. Machine 1 may be used as a railway crane, as a freight car for transporting materials and personnel, as well as an auxiliary vehicle in track maintenance or rehabilitation work. Undercarriages 3 are three-axle trucks. A rotary ~;~
support 6 mounts an auxiliary frame 5 on machine frame 2, and ;
drive 7 engages the rotary support for rotation of the auxiliary frame about vertical axis 8 over an angle of rotation of 180. A rotary crane 4 is mounted on auxiliary frame 5 at one end thereof, as seen in the longitudinal direction. A blocking device 9 is arranged at each end of 21~3~93 ~;
auxiliary frame 5 to retain the auxiliary frame in its respective end position in alignment with machine frame 2.
The machine frame has vertically adjustable support jacks 32 and hydraulic drives 33 for vertically adjusting the support jacks between a retracted position during movement of the machine frame along the track and an extended operating position for support of the machine frame on the track.
Rotary crane 4 carried by machine frame 2 comprises extensible boom 18 comprised of first arm 12 and second arm 13, the first arm being linked to support arm 11 for pivoting about horizontal axis 16 extending transversely to the machine frame and second arm 13 being slidably displaceable with respect to first arm 12 for changing the length of the extensible crane boom. A hydraulic cylinder drive 14 for vertically adjusting the extensible crane boom is connected to ~ ~:
support arm 11 and a hydraulic cylinder drive 15 links first arm 12 to support arm 11 for pivoting the first arm.
Hydraulic cylinder drive 14 includes signal transmitter 25 indicating the hydraulic pressure in the cylinder drive. -Hydraulic drive 17 connects second arm 13 to first arm 12 for slidably displacing the second arm to change the length of the extensible boom. Further drive 19 is arranged to rotate rotary crane 4 on machine frame 2 about substantially vertical axis 20 whereby the crane boom may assume different angles of rotation with respect to a longitudinal direction of machine frame 2. The illustrated rotary crane further comprises support column 10 mounted on machine frame 2 for rotation ~;
about vertical axis 20 by further drive 19, the support column ``
carrying support arm 11 and hydraulic cylinder drive 14 being - 8 - -~
': ` ~`-` ~' 2 1 ~ 3 ~ ~ 3 connected to support column 10. Support arm 11 is supported on support column 10 for pivoting about horizontal axis 16' extending parallel to axis 16 so that hydraulic cylinder drive 14 may lower and raise the crane boom. A counterweight 22 is -~
mounted on support column 10 for displacement in a horizontal plane in a direction extending perpendicularly to horizontal axis 16, and drive 21 is arranged to displace the counterweight.
At the end opposite the end supporting rotary crane 4, auxiliary frame 5 carries driver's cab 30, and the auxiliary frame defines loading platform 31 beneath boom 18 of the rotary crane. Spaced from each other in the longitudinal direction, three support jacks 32 are mounted on machine frame 2 at each side thereof. The vertically adjustable support jacks have shoes 34, and drives 33 are operable for vertical adjustment of support jacks 32 between a retracted position .
during movement of the machine frame along track 40 and an extended operating position for support of the machine frame on the track when jack shoes 34 engage the ends of the track ties and support machine frame 2 thereon. - -~
A motor 37 is connected to drives 38 for moving machine 1 along the track and to hydraulic system 39 connected to operating drives 14, 15, 17 and 19 for rotary crane 4.
Undercarriageg 3 have conventional blocking devices to block the springs arranged between the undercarriages and machine frame 2 so that the machine frame is held rigidly during operation of the crane.
g ~
2 ~ 3 ll l9 3 Control circuit 23 controls the operation of hydraulic cylinder drive 14 for vertically adjusting the extensible crane boom, drive 17 for changing the extensible boom length and further drive 19 for rotating rotary crane 4. The control is connected to signal transmitter 25 indicating the hydraulic ~ . . .
pressure in cylinder drive 14, and is further connected to at least one measuring device selected from the group consisting ~-of signal transmitter 26 indicating the superelevation of the `
track, signal transmitter 27 indicating the angle of rotation ~ of the rotary crane, signal transmitter 28 indicating changes in the extensible boom length, and signal transmitter 35 indicating the position of support jacks 32, whereby a reference value signal corresponding to a maximum permissible load for the crane in a given operating position is generated. `
Control circuit 23 comprises differential comparator unit 44 for comparing the reference value signal with an output signal ~ ;~
of signal transmitter 25 indicating the hydraulic pressure in cylinder drive 14. Overload control device 24 is connected to the differential comparator unit of control 23 for controlling the drives when the comparison of the signals in differential ~`
, : :
unit 44 indicates an overload.
The signal transmitter 28 indicating a change in the ~-extensible boom length is illustrated as cable potentiometer -~
29, one end of the cable being connected to the cylinder of drive 17 while its other end is connected to the piston rod of the drive so that the cable measures the length of the piston rod extending from the cylinder.
~;, "~ ", ~
2 ~ ~3'~3 : ~
A measuring device including signal transmitter 41 is ~ -provided to indicate the angle between the support arm 11 and first arm 12, and this measuring device may be a cable potentiometer arranged to indicate changes in the length of hydraulic cylinder drive 15 for pivoting the first arm, -~-similar to the cable potentiometer described hereinabove in -~--connection with measuring device 28, or a rotary potentiometer whose axis of rotation is coaxial with horizontal axis 16.
As shown in FIG. 2, signal transmitters 25, 26, 27, 28, 35 and 41 of the respective measuring devices are connected to differential comparator unit 44 through signal amplifiers 42 ;
and microprocessor 43 to transmit the output signals of the signal transmitters to the input of the differential -comparator unit 44 after the output signals have been amplified and processed in the microprocessor so that the sum of the output signals of signal transmitters 26, 27, 28, 35 and 41 forms a reference value signal corresponding to a maximum permissible load for the crane in a given operating position. This reference value signal is fed to differential unit comparator 44 in which it is compared with the actual value signal transmitted by signal transmitter 25 indicating the hydraulic pressure in cylinder drive 14. Overload control device 24 is connected to the differential comparator unit of control circuit 23 for controlling the drives when the differential comparator unit emits an output signal indicating an overload. The overload control device includes servo valves 45 in the lines of hydraulic system 39 leading to -~
respective drives. The hydraulic lines from servo valves 45 2 ~ 9 3 to vertical adjustment drive 14 and to drive 15 are shown in FIG. 2. -~
Signal transmitter 26 indicating the superelevation of track 40 comprises a pendulum mounted on machine frame 2 for pivoting about a horizontal axis extending in the longitudinal direction, the pendulum carrying a damped pendulum weight.
Signal transmitter 27 indicating the angle of rotation ~ of rotary crane 4 has a positive and a negative signal range respectively positioned at a left half 46 and a right half 47 of machine frame 2 on respective sides of a common zero position defined by plane 36 extending in the longitudinal direction through vertical axis 20. ; ~-.~
Signal transmitters 35 may emit signals indicating the hydraulic pressure in drives 33 for hydraulic jacks 32 to indicate when the support jacks on at least one side of machine frame 2 are in their extended operating position wherein their shoes 34 rest on the tie ends to support at ~ ;
least one half of the machine frame on the tie ends, thus . ...::. - ~
enhancing the stability of machine 1. In this operating position, hydraulic system 39 operates automatically to supply high hydraulic pressure to the operating drives of rotary crane 4 whereby the crane is enabled to make full use of its lifting capacity. When support jacks are retracted while machine 1 is moved between operating sites or when crane 4 is not used, as shown in FIG. 1, hydraulic system 39 operates automatically at low pressure, at which the loading moment of the crane is reduced. To assure a safe operation of rotary crane 4 independent of the operating positions, shut-off 21~3~93 device 24 in hydraulic system 39 is connected tomicroprocessor 43 and the signal transmitters 25, 26, 27, 28, 35 and 41 of the measuring devices. Signal transmitter 25 ~-~
transmits its output signal to microprocessor 43 and this output signal indicates the prevailing value of the loading moment to which crane 4 is subjected.
The reference value signal formed in microprocessor 43 is the sum of the output signals received from signal ~ -~
transmitters 26, 27, 28, 35 and 41, which monitor and measure ;
the superelevation of the track, the rotary angle of the crane, the length of the boom, position of the support jacks, and the relative angular position of the first and support -arms of the boom. In other words, this reference value signal corresponds to the maximum permissible load depending on the prevailing operating position of rotary crane 4.
The measuring device including signal transmitter 27 will accurately monitor angle ~, which is the angle the crane boom ~
encloses with plane 36 at the right half or left half of ;~ ;
machine frame 2. If this angle is less than 20, the crane can be subjected to its maximum load. If the angle exceeds 20-, microprocessor 43 will reduce the measuring signal by a ;~
predetermined amount, which depends on the structural details of the crane, so that this signal corresponds to the maximum load permissible at the monitored rotary angle of the crane.
'rhe measuring device including signal transmitter 26 will accurately monitor the superelevation of track 40 to determine - ~
its output signal in track curves. If crane boom 18 is positioned on the higher half of the machine frame in a curve, ~ -`
2143~9~
the measuring signal is correspondingly amplified. In other words, in this position of the boom, a higher load is permissible. On the other hand, if the crane boom is positioned on the lower machine frame half, the measuring signal, i.e. the reference value signal, is reduced.
.: .
Since the maximum load for the crane also depends on the length of boom 18, the signal received from signal transmitter 28 is also a component of the reference value signal. Another component is the signal from signal transmitter 41 because the angle which crane boom 18 encloses with the horizontal also influences the maximum load. -~
: . ~
The reference value signal derived from the sum of all `
these output signals in microprocessor 43 is compared in differential comparator unit 44 with the actual value signal emitted by signal transmitter 25 which monitors the prevailing ~;;
hydraulic pressure in hydraulic lifting cylinder 14, i.e. ;-~
indicates the actual value. If this actual value exceeds the reference value, the output signal from the differential `~
comparator unit immediately actuates overload control device ., ., ~, 24, i.e. servo valves 45 are selectively operated so that hydraulic drives 15, 17 and 19 may change the angle between support arm 11 and first arm 12, the length of crane boom 18, and the angle of rotation ~ of crane 4 so that the load moment .
is reduced. Furthermore, the load lifted by winch 48 on the crane can only be lowered in this condition. When the actual value is smaller than the reference value, overload control device 24 is not activated and drives 14, 15, 17 and 19 continue to operate undisturbed.
21~349~
If desired, the distance of counterweight 22 from support column 10 of rotary crane 4 may also be monitored by a further ~ -measuring device including signal transmitter 49. This, too, may be connected to control circuit 23 so that its output signal forms à further component of the reference value signal. It would also be possible to add another measuring ;
device monitoring a transverse displacement of support jacks ~ :~
32 which may be displaceable transversely to the longitudinal direction by transverse displacement drives.
Since the maximum load for the crane in any given -position of crane boom 18 is continuously monitored by the various measuring devices and the reference value derived therefrom is continuous compared with the actual value derived from the crane lifting drive, the crane may be used at its highest efficiency at all times. -~
: - ~ .
-~ . -, ~
'~: ' ~ . '.:. -~
:.
`:
BRIEF DESCRIPTION OF THE DRAWING
The above and other objects, advantages and features of the present invention will become more apparent from the ~--following detailed description of a now preferred embodiment thereof, taken in conjunction with the accompanying, somewhat schematic drawing wherein :','",."~... ~, FIG. 1 is a side elevational view showing a machine according to this invention; and FIG. 2 is a simplified circuit diagram of the control circuit.
''~' ~ '~ ..' DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring now to the drawing and first to FIG. 1, there is shown machine 1 comprising machine frame 2 movable along track 40 on undercarriages 3 supporting the machine frame on the track. Machine 1 may be used as a railway crane, as a freight car for transporting materials and personnel, as well as an auxiliary vehicle in track maintenance or rehabilitation work. Undercarriages 3 are three-axle trucks. A rotary ~;~
support 6 mounts an auxiliary frame 5 on machine frame 2, and ;
drive 7 engages the rotary support for rotation of the auxiliary frame about vertical axis 8 over an angle of rotation of 180. A rotary crane 4 is mounted on auxiliary frame 5 at one end thereof, as seen in the longitudinal direction. A blocking device 9 is arranged at each end of 21~3~93 ~;
auxiliary frame 5 to retain the auxiliary frame in its respective end position in alignment with machine frame 2.
The machine frame has vertically adjustable support jacks 32 and hydraulic drives 33 for vertically adjusting the support jacks between a retracted position during movement of the machine frame along the track and an extended operating position for support of the machine frame on the track.
Rotary crane 4 carried by machine frame 2 comprises extensible boom 18 comprised of first arm 12 and second arm 13, the first arm being linked to support arm 11 for pivoting about horizontal axis 16 extending transversely to the machine frame and second arm 13 being slidably displaceable with respect to first arm 12 for changing the length of the extensible crane boom. A hydraulic cylinder drive 14 for vertically adjusting the extensible crane boom is connected to ~ ~:
support arm 11 and a hydraulic cylinder drive 15 links first arm 12 to support arm 11 for pivoting the first arm.
Hydraulic cylinder drive 14 includes signal transmitter 25 indicating the hydraulic pressure in the cylinder drive. -Hydraulic drive 17 connects second arm 13 to first arm 12 for slidably displacing the second arm to change the length of the extensible boom. Further drive 19 is arranged to rotate rotary crane 4 on machine frame 2 about substantially vertical axis 20 whereby the crane boom may assume different angles of rotation with respect to a longitudinal direction of machine frame 2. The illustrated rotary crane further comprises support column 10 mounted on machine frame 2 for rotation ~;
about vertical axis 20 by further drive 19, the support column ``
carrying support arm 11 and hydraulic cylinder drive 14 being - 8 - -~
': ` ~`-` ~' 2 1 ~ 3 ~ ~ 3 connected to support column 10. Support arm 11 is supported on support column 10 for pivoting about horizontal axis 16' extending parallel to axis 16 so that hydraulic cylinder drive 14 may lower and raise the crane boom. A counterweight 22 is -~
mounted on support column 10 for displacement in a horizontal plane in a direction extending perpendicularly to horizontal axis 16, and drive 21 is arranged to displace the counterweight.
At the end opposite the end supporting rotary crane 4, auxiliary frame 5 carries driver's cab 30, and the auxiliary frame defines loading platform 31 beneath boom 18 of the rotary crane. Spaced from each other in the longitudinal direction, three support jacks 32 are mounted on machine frame 2 at each side thereof. The vertically adjustable support jacks have shoes 34, and drives 33 are operable for vertical adjustment of support jacks 32 between a retracted position .
during movement of the machine frame along track 40 and an extended operating position for support of the machine frame on the track when jack shoes 34 engage the ends of the track ties and support machine frame 2 thereon. - -~
A motor 37 is connected to drives 38 for moving machine 1 along the track and to hydraulic system 39 connected to operating drives 14, 15, 17 and 19 for rotary crane 4.
Undercarriageg 3 have conventional blocking devices to block the springs arranged between the undercarriages and machine frame 2 so that the machine frame is held rigidly during operation of the crane.
g ~
2 ~ 3 ll l9 3 Control circuit 23 controls the operation of hydraulic cylinder drive 14 for vertically adjusting the extensible crane boom, drive 17 for changing the extensible boom length and further drive 19 for rotating rotary crane 4. The control is connected to signal transmitter 25 indicating the hydraulic ~ . . .
pressure in cylinder drive 14, and is further connected to at least one measuring device selected from the group consisting ~-of signal transmitter 26 indicating the superelevation of the `
track, signal transmitter 27 indicating the angle of rotation ~ of the rotary crane, signal transmitter 28 indicating changes in the extensible boom length, and signal transmitter 35 indicating the position of support jacks 32, whereby a reference value signal corresponding to a maximum permissible load for the crane in a given operating position is generated. `
Control circuit 23 comprises differential comparator unit 44 for comparing the reference value signal with an output signal ~ ;~
of signal transmitter 25 indicating the hydraulic pressure in cylinder drive 14. Overload control device 24 is connected to the differential comparator unit of control 23 for controlling the drives when the comparison of the signals in differential ~`
, : :
unit 44 indicates an overload.
The signal transmitter 28 indicating a change in the ~-extensible boom length is illustrated as cable potentiometer -~
29, one end of the cable being connected to the cylinder of drive 17 while its other end is connected to the piston rod of the drive so that the cable measures the length of the piston rod extending from the cylinder.
~;, "~ ", ~
2 ~ ~3'~3 : ~
A measuring device including signal transmitter 41 is ~ -provided to indicate the angle between the support arm 11 and first arm 12, and this measuring device may be a cable potentiometer arranged to indicate changes in the length of hydraulic cylinder drive 15 for pivoting the first arm, -~-similar to the cable potentiometer described hereinabove in -~--connection with measuring device 28, or a rotary potentiometer whose axis of rotation is coaxial with horizontal axis 16.
As shown in FIG. 2, signal transmitters 25, 26, 27, 28, 35 and 41 of the respective measuring devices are connected to differential comparator unit 44 through signal amplifiers 42 ;
and microprocessor 43 to transmit the output signals of the signal transmitters to the input of the differential -comparator unit 44 after the output signals have been amplified and processed in the microprocessor so that the sum of the output signals of signal transmitters 26, 27, 28, 35 and 41 forms a reference value signal corresponding to a maximum permissible load for the crane in a given operating position. This reference value signal is fed to differential unit comparator 44 in which it is compared with the actual value signal transmitted by signal transmitter 25 indicating the hydraulic pressure in cylinder drive 14. Overload control device 24 is connected to the differential comparator unit of control circuit 23 for controlling the drives when the differential comparator unit emits an output signal indicating an overload. The overload control device includes servo valves 45 in the lines of hydraulic system 39 leading to -~
respective drives. The hydraulic lines from servo valves 45 2 ~ 9 3 to vertical adjustment drive 14 and to drive 15 are shown in FIG. 2. -~
Signal transmitter 26 indicating the superelevation of track 40 comprises a pendulum mounted on machine frame 2 for pivoting about a horizontal axis extending in the longitudinal direction, the pendulum carrying a damped pendulum weight.
Signal transmitter 27 indicating the angle of rotation ~ of rotary crane 4 has a positive and a negative signal range respectively positioned at a left half 46 and a right half 47 of machine frame 2 on respective sides of a common zero position defined by plane 36 extending in the longitudinal direction through vertical axis 20. ; ~-.~
Signal transmitters 35 may emit signals indicating the hydraulic pressure in drives 33 for hydraulic jacks 32 to indicate when the support jacks on at least one side of machine frame 2 are in their extended operating position wherein their shoes 34 rest on the tie ends to support at ~ ;
least one half of the machine frame on the tie ends, thus . ...::. - ~
enhancing the stability of machine 1. In this operating position, hydraulic system 39 operates automatically to supply high hydraulic pressure to the operating drives of rotary crane 4 whereby the crane is enabled to make full use of its lifting capacity. When support jacks are retracted while machine 1 is moved between operating sites or when crane 4 is not used, as shown in FIG. 1, hydraulic system 39 operates automatically at low pressure, at which the loading moment of the crane is reduced. To assure a safe operation of rotary crane 4 independent of the operating positions, shut-off 21~3~93 device 24 in hydraulic system 39 is connected tomicroprocessor 43 and the signal transmitters 25, 26, 27, 28, 35 and 41 of the measuring devices. Signal transmitter 25 ~-~
transmits its output signal to microprocessor 43 and this output signal indicates the prevailing value of the loading moment to which crane 4 is subjected.
The reference value signal formed in microprocessor 43 is the sum of the output signals received from signal ~ -~
transmitters 26, 27, 28, 35 and 41, which monitor and measure ;
the superelevation of the track, the rotary angle of the crane, the length of the boom, position of the support jacks, and the relative angular position of the first and support -arms of the boom. In other words, this reference value signal corresponds to the maximum permissible load depending on the prevailing operating position of rotary crane 4.
The measuring device including signal transmitter 27 will accurately monitor angle ~, which is the angle the crane boom ~
encloses with plane 36 at the right half or left half of ;~ ;
machine frame 2. If this angle is less than 20, the crane can be subjected to its maximum load. If the angle exceeds 20-, microprocessor 43 will reduce the measuring signal by a ;~
predetermined amount, which depends on the structural details of the crane, so that this signal corresponds to the maximum load permissible at the monitored rotary angle of the crane.
'rhe measuring device including signal transmitter 26 will accurately monitor the superelevation of track 40 to determine - ~
its output signal in track curves. If crane boom 18 is positioned on the higher half of the machine frame in a curve, ~ -`
2143~9~
the measuring signal is correspondingly amplified. In other words, in this position of the boom, a higher load is permissible. On the other hand, if the crane boom is positioned on the lower machine frame half, the measuring signal, i.e. the reference value signal, is reduced.
.: .
Since the maximum load for the crane also depends on the length of boom 18, the signal received from signal transmitter 28 is also a component of the reference value signal. Another component is the signal from signal transmitter 41 because the angle which crane boom 18 encloses with the horizontal also influences the maximum load. -~
: . ~
The reference value signal derived from the sum of all `
these output signals in microprocessor 43 is compared in differential comparator unit 44 with the actual value signal emitted by signal transmitter 25 which monitors the prevailing ~;;
hydraulic pressure in hydraulic lifting cylinder 14, i.e. ;-~
indicates the actual value. If this actual value exceeds the reference value, the output signal from the differential `~
comparator unit immediately actuates overload control device ., ., ~, 24, i.e. servo valves 45 are selectively operated so that hydraulic drives 15, 17 and 19 may change the angle between support arm 11 and first arm 12, the length of crane boom 18, and the angle of rotation ~ of crane 4 so that the load moment .
is reduced. Furthermore, the load lifted by winch 48 on the crane can only be lowered in this condition. When the actual value is smaller than the reference value, overload control device 24 is not activated and drives 14, 15, 17 and 19 continue to operate undisturbed.
21~349~
If desired, the distance of counterweight 22 from support column 10 of rotary crane 4 may also be monitored by a further ~ -measuring device including signal transmitter 49. This, too, may be connected to control circuit 23 so that its output signal forms à further component of the reference value signal. It would also be possible to add another measuring ;
device monitoring a transverse displacement of support jacks ~ :~
32 which may be displaceable transversely to the longitudinal direction by transverse displacement drives.
Since the maximum load for the crane in any given -position of crane boom 18 is continuously monitored by the various measuring devices and the reference value derived therefrom is continuous compared with the actual value derived from the crane lifting drive, the crane may be used at its highest efficiency at all times. -~
: - ~ .
-~ . -, ~
'~: ' ~ . '.:. -~
:.
`:
Claims (9)
1. A machine comprising a machine frame movable along a track on undercarriages supporting the machine frame on the track, the machine frame having vertically adjustable support jacks and drives for vertically adjusting the support jacks between a retracted position during movement of the machine frame along the track and an extended operating position for support of the machine frame on the track, and the machine frame carrying a rotary crane comprising an extensible boom, the rotary crane comprising (a) a hydraulic cylinder drive for vertically adjusting the extensible crane boom, the hydraulic cylinder drive including (1) a signal transmitter indicating the hydraulic pressure in the cylinder drive, (b) a drive for changing the length of the extensible boom, (c) a further drive for rotating the rotary crane on the machine frame about a substantially vertical axis whereby the crane boom may assume different angles of rotation with respect a longitudinal direction of the machine frame, and (d) a control associated with the hydraulic cylinder drive for vertically adjusting the extensible crane boom, the drive for changing the extensible boom length and the further drive for rotating the rotary crane, the control being connected to the signal transmitter indicating the hydraulic pressure in the cylinder drive and to at least one measuring device selected from the group consisting of (1) a signal transmitter indicating the superelevation of the track, (2) a signal transmitter indicating the angle of rotation of the rotary crane, (3) a signal transmitter indicating changes in the extensible boom length, and (4) a signal transmitter indicating the position of the support jacks, whereby a reference value signal corresponding to a maximum permissible load for the crane in a given operating position is generated, and the control comprising (5) a differential comparator unit for comparing the reference value signal with an output signal of the signal transmitter indicating the hydraulic pressure in the cylinder drive, and (e) an overload control device connected to the control for controlling the drives when the differential comparator unit indicates an overload.
2. The machine of claim 1, wherein the crane boom comprises a first arm pivotal about a horizontal axis extending transversely to the machine frame and a second arm slidably displaceable with respect to the first arm for changing the length of the extensible crane boom, the drive for changing the length comprising a hydraulic cylinder for displacing the second arm with respect to the first arm, and the signal transmitter indicating changes in the extensible boom length being a cable potentiometer.
3. The machine of claim 2, wherein the crane boom further comprises a support arm, the hydraulic cylinder drive for vertically adjusting the extensible crane boom being connected to the support arm and the first arm being linked to the support arm for pivoting about the horizontal axis, further comprising a hydraulic cylinder drive linking the first arm to the support arm for pivoting the first arm, and a measuring device for indicating the angle between the support and first arms.
4. The machine of claim 3, wherein the angle indicating measuring device is a cable potentiometer arranged to indicate changes in the length of the hydraulic cylinder drive for pivoting the first arm.
5. The machine of claim 3, wherein the angle indicating measuring device is a rotary potentiometer whose axis of rotation is coaxial with the horizontal axis.
6. The machine of claim 3, wherein the rotary crane further comprises a support column mounted on the machine frame for rotation about the vertical axis by the further drive, the support column carrying the support arm and the hydraulic cylinder drive connected thereto, a counterweight mounted on the support column for displacement in a horizontal plane in a direction extending perpendicularly to the horizontal axis, and a drive for displacing the counterweight.
7. The machine of claim 1, wherein the signal transmitter indicating the superelevation of the track comprises a pendulum mounted on the machine frame for pivoting about a horizontal axis extending in the longitudinal direction, the pendulum carrying a damped pendulum weight.
8. The machine of claim 1, wherein the signal transmitter indicating the angle of rotation of the rotary crane has a positive and a negative signal range respectively positioned at a left and a right half of the machine frame on respective sides of a common zero position defined by a plane extending in the longitudinal direction through the vertical axis.
9. The machine of claim 1, further comprising an auxiliary frame mounted on the machine frame for rotation about a vertical axis over an angle of rotation of 180°, the rotary crane being mounted on the auxiliary frame at one end thereof, as seen in the longitudinal direction.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| AT41194 | 1994-02-28 | ||
| ATA411/94 | 1994-02-28 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2143493A1 true CA2143493A1 (en) | 1995-08-29 |
Family
ID=3489916
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002143493A Abandoned CA2143493A1 (en) | 1994-02-28 | 1995-02-27 | Track-bound rotary crane |
Country Status (7)
| Country | Link |
|---|---|
| EP (1) | EP0675069B1 (en) |
| AT (1) | ATE184574T1 (en) |
| CA (1) | CA2143493A1 (en) |
| CZ (1) | CZ28995A3 (en) |
| DE (1) | DE59506820D1 (en) |
| ES (1) | ES2139174T3 (en) |
| SK (1) | SK17895A3 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3763664B1 (en) | 2019-07-04 | 2023-06-07 | HMF Group A/S | Method for operating a crane, crane operation system and crane comprising it |
Families Citing this family (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0801022A3 (en) * | 1996-04-09 | 1999-02-10 | Franz Plasser Bahnbaumaschinen-Industriegesellschaft m.b.H. | Railway-working machine with a slewing crane |
| FR2750971B1 (en) * | 1996-07-12 | 1998-10-02 | Fdi Sambron | HANDLING TROLLEY PROVIDED WITH A SECURITY SYSTEM TO AVOID ITS ACCIDENTAL TIP |
| GB9711317D0 (en) * | 1997-06-03 | 1997-07-30 | William Hook Limited | Safety monitoring device |
| EP1119514A1 (en) * | 1998-04-22 | 2001-08-01 | Hojbjerg Maskinfabrik A/S | Vehicle crane installation with limiter means |
| IT1319455B1 (en) * | 2000-06-29 | 2003-10-10 | Dana Italia Spa | DEVICE FOR THE DYNAMIC STABILITY CONTROL OF AN INDUSTRIAL VEHICLE. |
| IT1318066B1 (en) * | 2000-06-29 | 2003-07-21 | Dana Italia Spa | MEASUREMENT AND CONTROL DEVICE FOR THE STABILITY CONDITIONS OF A VEHICLE, IN PARTICULAR OF AN INDUSTRIAL VEHICLE. |
| CN102455177B (en) * | 2010-10-20 | 2013-12-11 | 徐州重型机械有限公司 | Wheeled crane and wheel turn angle measuring device thereof |
| US9446935B2 (en) * | 2012-06-13 | 2016-09-20 | Liebherr-Werk Ehingen Gmbh | Method for monitoring crane safety and crane |
| AT513283B1 (en) | 2012-11-12 | 2014-03-15 | Palfinger Ag | Method for reporting the risk of tipping a crane |
| CN103663176B (en) * | 2013-12-05 | 2015-11-18 | 长沙中联消防机械有限公司 | One ascend a height vehicle jib fixed point launch control method |
| DE102014009668B4 (en) * | 2013-12-16 | 2018-06-07 | Wuhan Bridge Heavy Industries Group Co., Ltd. | Cross-track scaffolding construction for a railway rescue crane |
| DE202016003051U1 (en) * | 2016-05-11 | 2016-07-12 | Robel Bahnbaumaschinen Gmbh | Rail crane for transporting rails |
| IT201600082789A1 (en) * | 2016-08-05 | 2018-02-05 | Tesmec Spa | AUTOMATIC RAILWAY POSITIONING SYSTEM |
| CN110104003B (en) * | 2019-04-15 | 2020-07-31 | 山东科技大学 | Railway roadbed slope dangerous rock falling comprehensive disposal track engineering vehicle |
| DE102022106074A1 (en) * | 2022-03-16 | 2023-09-21 | Windhoff Bahn- Und Anlagentechnik Gmbh | Modular system for producing a track construction machine |
| CN115230771B (en) * | 2022-08-16 | 2024-03-15 | 西南交通大学 | Motor shaft temperature monitoring and control system of rail transit train |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2488234A1 (en) * | 1980-08-07 | 1982-02-12 | Fernand Delpeyroux | Mobile railway maintenance vehicle - uses limit switches controlling rotation and vertical movement of arm to ensure it does not contact electrified zones |
| DE3103728A1 (en) * | 1981-02-04 | 1982-09-02 | Fried. Krupp Gmbh, 4300 Essen | Device for improving the operational behaviour of mobile slewing cranes |
| FR2504701A1 (en) * | 1981-04-22 | 1982-10-29 | Camiva | DEVICE FOR CONTROLLING AUTOMATIC CORRECTION OF DEVERS FOR DEPLOYABLE ORIENTABLE SCALE OR ARM-LIKE ARMOR ON VEHICLE |
| GB8406094D0 (en) * | 1984-03-08 | 1984-04-11 | Merryweather & Sons | Control system |
| JP2564060B2 (en) * | 1991-10-24 | 1996-12-18 | 株式会社神戸製鋼所 | Safety equipment for construction machinery |
| DE4237948C5 (en) * | 1992-11-06 | 2008-08-28 | Gottwald Port Technology Gmbh | Crane, in particular railway crane |
-
1995
- 1995-01-20 ES ES95890016T patent/ES2139174T3/en not_active Expired - Lifetime
- 1995-01-20 AT AT95890016T patent/ATE184574T1/en active
- 1995-01-20 DE DE59506820T patent/DE59506820D1/en not_active Expired - Lifetime
- 1995-01-20 EP EP95890016A patent/EP0675069B1/en not_active Expired - Lifetime
- 1995-02-06 CZ CZ95289A patent/CZ28995A3/en unknown
- 1995-02-09 SK SK178-95A patent/SK17895A3/en unknown
- 1995-02-27 CA CA002143493A patent/CA2143493A1/en not_active Abandoned
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3763664B1 (en) | 2019-07-04 | 2023-06-07 | HMF Group A/S | Method for operating a crane, crane operation system and crane comprising it |
Also Published As
| Publication number | Publication date |
|---|---|
| ES2139174T3 (en) | 2000-02-01 |
| EP0675069B1 (en) | 1999-09-15 |
| DE59506820D1 (en) | 1999-10-21 |
| EP0675069A1 (en) | 1995-10-04 |
| CZ28995A3 (en) | 1995-10-18 |
| ATE184574T1 (en) | 1999-10-15 |
| SK17895A3 (en) | 1995-09-13 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FZDE | Discontinued |