阅读说明：本技术 一种臂架自重平衡的门座起重机单臂架变幅机构 (Luffing mechanism with balanced deadweight of jib for single jib of gantry crane ) 是由 裴看看 王全先 于 2021-09-07 设计创作，主要内容包括：本发明公开一种臂架自重平衡的门座起重机单臂架变幅机构,属于起重运输机械技术领域,用于起重量2-10吨,最大变幅距离12-20米范围的中型单臂架式门座起重机。该单臂架变幅机构包括回转台、臂架、变幅卷扬驱动装置、变幅钢绳组、人字架、臂架平衡装置及限位块,臂架及其变幅卷扬驱动装置与臂架平衡装置嵌套配置,臂架自重可通过臂架平衡装置得到基本平衡,利用限位块和平衡梁与人字架相互之间的结构限制,能够防止臂架的倾翻,保证变幅机构的安全,同时降低变幅过程中臂架自身摆动产生的能耗。(The invention discloses a single-boom luffing mechanism of a gantry crane with a balanced boom dead weight, belongs to the technical field of hoisting and transporting machinery, and is used for a medium-sized single-boom gantry crane with a hoisting capacity of 2-10 tons and a maximum luffing distance of 12-20 meters. The single-boom luffing mechanism comprises a rotary table, a boom, a luffing winch driving device, a luffing steel rope group, a propeller strut, a boom balancing device and a limiting block, wherein the boom and the luffing winch driving device are nested with the boom balancing device, the self weight of the boom can be basically balanced through the boom balancing device, and the boom can be prevented from tipping over by utilizing the structural limitation among the limiting block, a balance beam and the propeller strut, so that the safety of the luffing mechanism is ensured, and the energy consumption generated by the self-swinging of the boom in the luffing process is reduced.)

1. A single-boom luffing mechanism of a gantry crane with a balanced boom dead weight is characterized by comprising a rotary table (1), a luffing winch driving device (2), a propeller strut (3), a boom balancing device (4), a hinged support (5), a limiting block (6), a luffing steel rope group (7), a boom (8) and a boom support (9); the arm support (9) is rigidly fixed on the right side of the upper surface of the rotary table (1), and the lower end of the arm support (8) is hinged with the arm support (9); the propeller strut (3) is rigidly fixed on the upper surface of the rotary table (1), and the transverse neutral surface of the propeller strut (3) is superposed with the transverse neutral surface of the arm support (8); the variable-amplitude winch driving device (2) is arranged in the center of the upper surface of the rotary table (1); the two hinged supports (5) with the same structure are arranged on the upper surface of the propeller strut (3), and the two hinged supports (5) are symmetrical to the transverse neutral plane of the propeller strut (3); the limiting block (6) is welded on the upper surface of the propeller strut (3), and the limiting block (6) is positioned on the right side of the hinged support (5); one end of a steel wire rope (16) in the variable-amplitude steel wire rope group (7) is fixed on a winding drum (14) of the variable-amplitude winch driving device (2), and the other end of the steel wire rope (16) sequentially rounds a third pulley (20), a fifth pulley (22), a second pulley (19), a fourth pulley (21) and a first pulley (18), and is fixedly connected with the steel wire rope (16) which rounds into the first pulley (18) through a rope clamp after rounding the first pulley (18); the first pulley (18), the second pulley (19) and the third pulley (20) are arranged on a shaft (17), the shaft (17) is arranged in the hinged support (5), the fourth pulley (21), the fifth pulley (22) and the first rope ring (23) are coaxial, the second rope ring (25) is hinged with the upper end of the arm support (8), and the endless looped rope (24) is wound on the first rope ring (23) and the second rope ring (25); a hinge hole in the middle of a balance beam (27) in the arm support balancing device (4) is hinged to the hinged support (5), a balance weight (26) is filled in a box at the left end of the balance beam (27), the upper end of a pull rod (28) is hinged to the right end of the balance beam (27), a flange at the lower end of the pull rod (28) is connected with a flange of a connecting rod nut (29) through a bolt, a threaded hole at the lower end of the connecting rod nut (29) is connected with a bolt head of a rod end joint bearing (30) through a thread, and a lower hinge hole of the rod end joint bearing (30) is hinged to a waist-shaped seat hole of the arm support (8).

The technical field is as follows:

the invention belongs to the technical field of hoisting and transporting machinery, and particularly relates to a single-boom luffing mechanism of a portal crane with a balanced boom dead weight, which is used for luffing of a medium-sized portal crane.

Background art:

the luffing mechanism is the most important component in a portal crane, and has various structural forms according to different working condition requirements, wherein: the four-connecting-rod type luffing mechanism is mainly used for large portal cranes with the lifting capacity of more than 10 tons and the maximum luffing distance of more than 20 meters, has large size and heavy self weight, and is generally used by being nested with an arm support balancing device so as to ensure the safe operation of equipment and reduce the energy consumption of the luffing mechanism in the luffing process; the single-boom luffing mechanism is mainly used for small portal cranes with the lifting capacity of less than 2 tons and the maximum luffing distance of less than 12 meters, the single boom swings around the luffing of a lower fulcrum or is hoisted by a steel rope or is driven by a gear rack, the single boom is small in size and light in weight, and the balanced loading capacity of the boom is not required to be configured generally.

For a medium-sized portal crane with the lifting capacity of 2-10 tons and the maximum amplitude variation distance of 12-20 meters, if a luffing mechanism nested with a four-bar linkage and a boom balancing device is adopted, the luffing mechanism is complex in structure, heavy in self weight, high in manufacturing cost and high in operating cost, and if a simple single boom luffing mechanism without boom balancing loading is adopted, the luffing mechanism is simple in structure and low in manufacturing cost, but the boom is large in size, heavy in weight and poor in operating safety, and particularly when the windward pressure is large, the technical difficulty for preventing the boom from tipping is high.

The invention content is as follows:

aiming at the technical problems and the defects of the luffing mechanism of the existing portal crane, the invention provides the luffing mechanism of the single-boom frame of the portal crane with the balanced boom dead weight, so as to realize the balanced boom dead weight and safe luffing of the boom in the luffing process.

The invention provides a single-boom luffing mechanism of a gantry crane with a balanced boom dead weight, which comprises a rotary table 1, a luffing winch driving device 2, a propeller strut 3, a boom balancing device 4, a hinged support 5, a limiting block 6, a luffing steel rope group 7, a boom 8 and a boom support 9, and is shown in figures 1, 2 and 3; the arm support 9 is rigidly fixed on the right side of the upper surface of the rotary table 1, and the lower end of the arm support 8 is hinged with the arm support 9; the propeller strut 3 is rigidly fixed on the upper surface of the rotary table 1, and the transverse neutral surface of the propeller strut 3 is superposed with the transverse neutral surface of the arm support 8; the variable-amplitude winch driving device 2 is arranged in the center of the upper surface of the rotary table 1; two hinged supports 5 with the same structure are arranged on the upper surface of the propeller strut 3, and the two hinged supports 5 are symmetrical to the transverse neutral plane of the propeller strut 3; the limiting block 6 is welded on the upper surface of the propeller strut 3, and the limiting block 6 is positioned on the right side of the hinged support 5; one end of a steel wire rope 16 in the variable-amplitude steel wire rope group 7 is fixed on a winding drum 14 of the variable-amplitude winch driving device 2, and the other end of the steel wire rope 16 sequentially rounds a third pulley 20, a fifth pulley 22, a second pulley 19, a fourth pulley 21 and a first pulley 18, and is fixedly connected with the steel wire rope 16 which rounds the first pulley 18 by a rope clamp after rounding the first pulley 18; the first pulley 18, the second pulley 19 and the third pulley 20 are mounted on a shaft 17, the shaft 17 is mounted in the hinged support 5, the fourth pulley 21, the fifth pulley 22 and the first rope loop 23 are coaxial, the second rope loop 25 is hinged with the upper end of the arm support 8, and the endless looped rope 24 is wound on the first rope loop 23 and the second rope loop 25; a hinge hole in the middle of a balance beam 27 in the arm support balancing device 4 is hinged to the hinge support 5, a counterweight 26 is filled in a box at the left end of the balance beam 27, the upper end of a pull rod 28 is hinged to the right end of the balance beam 27, a flange at the lower end of the pull rod 28 is connected with a flange of a connecting rod nut 29 through a bolt, a threaded hole at the lower end of the connecting rod nut 29 is connected with a bolt head of a rod end joint bearing 30 through a thread, and a lower hinge hole of the rod end joint bearing 30 is hinged to a waist seat hole of the arm support 8.

As shown in fig. 4, the luffing winch drive device 2 includes a motor 10, a first brake 11, a speed reducer 12, a second brake 13, a winding drum 14, and a phase sensor 15. The right end of the winding drum 14 is rigidly connected with an output shaft of the speed reducer 12, the first brake 11 is connected with a left end input shaft of the speed reducer 12, the second brake 13 is connected with a right end input shaft of the speed reducer 12, and the motor 10 is connected with a brake disc of the first brake 11 through a coupler. The phase sensor 15 is connected to the spool 14. The first brake 11 and the second brake 13 are of the same type and are both normally closed brakes. The purpose of using two brakes on the high-speed shaft of the speed reducer 12 is to improve safety and reliability, and when one brake fails and cannot brake, the other brake can completely guarantee the stop brake of the winding drum 14.

The limiting block 6 has the effects that when the winding drum 14 in the variable amplitude winch driving device 2 rotates to make the steel wire rope 16 loose, the arm support 8 rotates around the lower hinge point to realize variable amplitude, when the arm support 8 rotates to reach the maximum variable amplitude, the steel wire rope continues to loose, and at the moment, the bottom of the balance beam 27 touches and presses the top of the limiting block 6, so that the arm support 8 does not continue to rotate. When the arm support 8 swings to the minimum amplitude variation position, the bottom of the balance weight 26 of the balance beam 27 abuts against the inclined upright column outside the propeller strut 3, the arm support 8 can be prevented from rotating and tipping to the left continuously, and meanwhile, the motor 10 in the amplitude variation winch driving device blocks the rotation and gives an alarm.

The steel wire rope 16 is long enough to reach the maximum amplitude position longer than the arm support. The aim is to fully lay the steel wire rope when the pulley block of the gantry crane hoisting mechanism and the steel wire rope of the cross-winding hoisting mechanism are arranged at the top of the arm support, to tilt the arm support as much as possible, to lower the top end of the arm support to the position of the rotary table working table, to facilitate the installation of the pulley block and the cross-winding hoisting of the steel wire rope.

The rod end joint bearing 30 is used for connecting the pull rod 28 and the arm support 8 after the arm support 8 and the arm support balancing device 4 are installed, and the transverse neutral plane of the pull rod 28 and the transverse neutral plane of the arm support 8 are not overlapped due to manufacturing or assembling errors, so that connection cannot be achieved, and the rod end joint bearing 30 can make up errors between the two and achieve good connection between the two.

The invention has the advantages that the invention is used for the medium-sized single-jib portal crane with the lifting capacity of 2-10 tons and the maximum amplitude variation distance of 12-20 meters, the self weight of the jib can be basically balanced through the jib balancing device, the tipping of the jib is prevented by utilizing the structural limitation among the limiting blocks, the balance beam and the propeller strut, the safety of the amplitude variation mechanism is ensured, and the energy consumed by the self swinging of the jib in the amplitude variation process is reduced.

Description of the drawings:

FIG. 1 is a schematic structural diagram of a luffing mechanism of a single jib of a gantry crane with a balanced jib dead weight according to the invention;

FIG. 2 is a schematic structural view of a luffing cable assembly according to the invention;

fig. 3 is a schematic structural diagram of the boom balancing device in the present invention;

fig. 4 is a schematic structural diagram of the variable amplitude winch driving device in the invention.

In the figure: 1: a turntable; 2: a variable amplitude winch driving device; 3: a herringbone frame; 4: a boom balancing device; 5: a hinged support; 6: a limiting block; 7: a variable-amplitude steel rope group; 8: a boom; 9: a cantilever crane support; 10: a motor; 11: a first brake; 12: a speed reducer; 13: a second brake; 14: a reel; 15: a phase sensor; 16: a wire rope; 17: a shaft; 18: a first pulley; 19: a second pulley; 20: a third pulley; 21: a fourth pulley; 22: a fifth pulley; 23: a first loop; 24: endless loop ropes; 25: a second loop; 26: balancing weight; 27: a balance beam; 28: a pull rod; 29: a connecting rod nut; 30: and a rod end joint bearing.

The specific implementation method comprises the following steps:

the invention provides a single-boom luffing mechanism of a portal crane with a balanced boom dead weight, which comprises a rotary table 1, a luffing winch driving device 2, a propeller strut 3, a boom balancing device 4, a hinged support 5, a limiting block 6, a luffing steel rope group 7, a boom 8 and a boom support 9, is used for 3t-15m portal cranes, and is shown in figures 1, 2 and 3, the crane has the maximum hoisting weight of 3 tons, the maximum amplitude variation distance of 15 meters and the minimum amplitude variation distance of 6.5 meters, according to the variable amplitude speed of 15 m/min, calculating the required motor power, determining that the model of a variable amplitude winch motor 10 is YZP160L-8, the rated power of the motor is 9kw, the rated rotating speed of 694rpm, the model of a speed reducer 12 is ZQD 500-90-VII-CA, the models of a first brake 11 and a second brake 13 are YWZB-300/25, and the model of a steel wire rope 16 is 26NAT6 multiplied by 19+ FC-1700. According to the maximum and minimum amplitude variation distance, the length of the arm support 8 is determined to be 16090mm, and the arm support inclination angles corresponding to the maximum amplitude variation and the minimum amplitude variation of the arm support are respectively 32.60 degrees and 71.70 degrees. And (3) obtaining a balance weight which is 760kg according to the moment balance of the arm support 8 and the balance weight 26 which are equivalent to the axis of the hinged support 5 during maximum amplitude variation, pouring concrete with corresponding weight into a box reserved on the balance beam 27, and adding a welding steel bar for fixing.

Sequentially installing and fixing the components of the variable-amplitude winch driving device 2, the arm support 9 and the propeller strut 3 on the rotary table 1 according to the designed position size; the lower hinge point of the arm support 8 is hinged with an arm support 9, the balance beam 27, the first pulley 18, the second pulley 19 and the third pulley 20 are hinged with the hinge support 5 through a shaft 17, the fourth pulley 21, the fifth pulley 22 and the first rope ring 23 are assembled into a coaxial assembly through bolt shafts, one end head of the steel wire rope 16 is fixed on the winding drum 14, the other end of the steel wire rope sequentially rounds the third pulley 20, the fifth pulley 22, the second pulley 19, the fourth pulley 21 and the first pulley 18, and the steel wire rope 16 which rounds the first pulley 18 is fixedly connected with the steel wire rope 16 which rounds the first pulley 18 through a rope clamp; the second rope loop 25 is hinged with the upper hinge point of the arm support 8, and the endless loop rope 24 is wound on the first rope loop 23 and the second rope loop 25. The inclination angle of the arm support 8 is adjusted by rotating the winding drum 14, and the pull rod 28 is sequentially connected with the connecting rod nut 29 and the rod end joint bearing 30 and then respectively hinged with the right end of the balance beam 27 and the waist seat hole of the arm support 8.

Finally, the arm support 8 is pulled to the minimum amplitude-changing position through the amplitude-changing winch driving device 2, namely the inclination angle is 71.70 degrees, the distance between the bottom edge of the box body of the counterweight 26 and the outer surface of the batter post of the propeller strut 3 is checked to be 160mm, in addition, the limiting block 6 is welded at the corresponding position of the upper plane of the propeller strut 3, the arm support 8 is placed to the maximum amplitude-changing position through the amplitude-changing winch driving device 2, namely the inclination angle is 32.60 degrees, the distance between the lower bottom edge of the box body of the balance beam 27 and the upper surface of the limiting block 6 is checked to be 160mm, the phase position of the phase sensor 15 corresponding to the two positions (corresponding to the minimum amplitude and the maximum amplitude) of the arm support 8 is determined in the control system, and the structure and the assembly are free of errors. All parts of the amplitude variation mechanism are assembled according to the steps, and the load amplitude variation of the portal crane can be carried out according to the production process requirements.