Specialized lifting equipment for a modular resilient cured track bed

Abstract

The utility model relates to a special hoisting equipment for assembled elastic solidified ballast bed, including main beam, branch leg, running mechanism, hoist system, horizontal regulation mechanism, guide mechanism and electric control system. Main beam adopts aviation aluminium alloy welded box type structure, and the inboard side is equipped with I -beam type horizontal -moving guide groove, and is connected through high -strength bolt flange with branch leg, and the lower part of branch leg is equipped with modular height adjustment section, and is adapted track super -high through bolt hole group, and running mechanism is driven chain transmission tread wheel by motor speed reducer, and realizes track deviation correction in cooperation with V type polyurethane guide wheel group, and the hollowness seat of hoist system slides along horizontal -moving guide groove, and controls positioning accuracy through trapezoidal thread rod horizontal regulation mechanism, and the bottom of lifting appliance is equipped with pressure -equalizing rubber pad, and electric control system integrates frequency conversion speed regulation and wireless remote control, and improves operation efficiency.

Description

Technical Field

[0001] This utility model relates to the field of rail transit construction equipment technology, and in particular to a special hoisting equipment for prefabricated elastic curing track bed for track maintenance during track openings. It is applicable to the construction and maintenance of track bed and sleepers for urban rail transit and railway ballasted tracks. Background Technology

[0002] Existing hoisting equipment generally suffers from problems such as excessive weight, inconvenient assembly and disassembly, and lack of positioning accuracy, making it difficult to adapt to narrow construction environments and high-altitude requirements on curved sections. Traditional cranes mostly adopt fixed structures or manual adjustments, resulting in large overall dimensions and weight, low efficiency, and high labor intensity. In addition, conventional winch or hoist solutions have shortcomings such as uneven load distribution and lack of lateral fine-tuning capabilities. Therefore, there is an urgent need for a lightweight, modular hoisting device suitable for skylight operations. Utility Model Content

[0003] To address the shortcomings of existing technologies, this utility model discloses a specialized hoisting equipment for prefabricated elastic curing track beds, the technical solution of which is as follows:

[0004] A specialized hoisting equipment for prefabricated elastic curing track beds, characterized in that it comprises a main beam, outriggers, a traveling mechanism, a hoisting system, a lateral adjustment mechanism, a guiding mechanism, and an electrical control system; wherein:

[0005] The main beam is a segmented rectangular box structure, with I-shaped transverse guide grooves symmetrically arranged on the inner side of the web on both sides. Each segment of the main beam is connected by a pin shaft, and the two ends of the beam are fixed to the top of the support leg by flange connecting plates and bolts.

[0006] The outrigger has an H-shaped frame structure with a traveling mechanism installed at the bottom. The lower part of the outrigger has a multi-segment height adjustment section, and height compensation is achieved through bolt groups.

[0007] The traveling mechanism includes a drive wheel set and an articulated driven wheel set symmetrically arranged at the bottom of the outriggers. The drive wheel set drives the chain transmission mechanism through a motor reducer in the wheel box.

[0008] The lifting system includes a hoist seat that is slidably assembled in the transverse guide groove, a hand chain hoist fixed to the hoist seat, a lifting chain connected to the hand chain hoist, a balance beam at the end of the lifting chain, and a lifting device with a rubber pad that is hinged by a pin.

[0009] The horizontal adjustment mechanism consists of an adjusting handwheel in the middle of the main beam, a trapezoidal threaded rod coaxially connected to the handwheel, and a positioning seat fixed on the hoist seat, forming a screw pair transmission.

[0010] The guiding mechanism includes V-shaped guide wheel sets symmetrically arranged on both sides of the drive wheel set, which maintain a gap with the side wall of the channel steel guide rail through a spring preload device;

[0011] The electrical control system includes an explosion-proof electrical cabinet, a frequency converter for controlling the motor reducer, and a wireless remote controller. The electrical cabinet integrates an overload protection module and an emergency stop switch.

[0012] Preferably, the segmented connection of the main beam is provided with a tenon and mortise structure, and the transverse guide groove achieves a continuous sliding surface through a stepped overlap.

[0013] Preferably, the height adjustment segment of the outrigger includes a basic segment and a replaceable height-adjustable segment, and the height adjustment is achieved through a flange connection.

[0014] Preferably, the chain drive mechanism consists of a drive sprocket, a roller chain, and a tread wheel, and the motor reducer is keyed to the drive sprocket.

[0015] Preferably, the thread fit clearance between the positioning seat and the trapezoidal threaded rod is adjustable, forming a precision helical pair.

[0016] Preferably, the V-shaped guide wheel assembly consists of two sets of polyurethane guide wheels, and the gap between the guide wheel and the guide rail is adaptively adjusted by a spring preload device.

[0017] Preferably, the rubber pads of the lifting device are evenly distributed on the bottom surface of the lifting device and are hinged to the balance beam.

[0018] Preferably, the wireless remote controller controls the travel speed via a frequency converter and supports micro-motion mode positioning.

[0019] Preferably, the flange connection surfaces of the main beam and the support leg are pre-tightened and fixed with high-strength bolts.

[0020] Preferably, the overload protection module is connected in series with the power supply circuit of the motor reducer, and after being triggered, the linkage braking device locks the chain.

[0021] Beneficial effects

[0022] Lightweight design: The main beam and legs are made of aerospace aluminum alloy, which is easy to disassemble and assemble manually.

[0023] Modular structure: The main beam is connected by pins in sections, and the support legs and heightening sections are replaceable, adapting to the needs of multiple scenarios.

[0024] The combination of box girder main beam and adjustable legs enhances load-bearing capacity. Attached Figure Description

[0025] Figure 1 This is a schematic diagram of the overall structure of this utility model. Detailed Implementation

[0026] This utility model provides a special hoisting equipment for prefabricated elastic curing track beds used in skylight operations, achieved through the following technical solution:

[0027] A special hoisting equipment for prefabricated elastic curing track bed used in skylight operations includes a main beam (1), outriggers (2), traveling mechanism (3), hoisting system (4), lateral adjustment mechanism (5), guiding mechanism (6), and electrical control system (7); wherein:

[0028] The main beam (1) is a rectangular box-shaped welded structure with a cross-sectional dimension of 400mm (height) × 200mm (width). The thickness of the web and flange is 8mm. Horizontal guide grooves (11) are symmetrically arranged on the inner side of the web on both sides. The cross-section of the horizontal guide groove (11) is I-shaped, with a distance of 30-50mm between the upper and lower flanges. The beam body is provided with main beam flange connecting plates (12) at both ends. The main beam is made of 7075-T6 aluminum alloy, conforming to GB / T 3880-2012 standard, with a yield strength ≥450MPa. The I-shaped cross-section design of its horizontal guide groove (11) (flange width 60mm, web height 40mm) reduces the friction contact area while ensuring rigidity. The main beam (1) is divided into two sections, each 1800mm long. The two sections of the main beam are connected by a tongue and groove tenon structure and a 40Cr alloy steel pin with a diameter of 50mm. This facilitates installation, disassembly and transportation. The tenon height is 10mm and the fit clearance is 0.1mm to ensure that the straightness error of the main beam after splicing is ≤1mm / m. The transverse guide groove (11) at the section interface adopts a stepped lap structure with an lap length ≥50mm. Nylon guide strips are installed in the guide groove to ensure that the sliding surface is continuous and smooth. After the sectioned main beam is assembled, the straightness error of the transverse guide groove (11) is ≤0.5mm / m, which is verified by coordinate measuring machine.

[0029] The outrigger (2) is provided with a base segment and a height adjustment segment. The upper and lower ends of the base segment are welded with outrigger flange connection plates. The outrigger flange connection plates are the same as the main beam flange connection plates. The middle of the base segment is provided with a main beam adjustable diagonal tie rod connection plate and an outrigger diagonal tie rod connection plate. The outrigger (2) is made of 6061-T6 aluminum alloy, which conforms to GB / T 3191-2010 standard. It is welded to form an H-shaped frame. The top of the outrigger is connected to the main beam flange connection plate (12) of the main beam (1) with 8.8 grade M20 bolts through the outrigger flange connection plate. The preload of a single bolt reaches 170kN, which ensures the connection strength while realizing quick manual disassembly and assembly. The outrigger and the main beam are also reinforced with 6061 aluminum alloy main beam adjustable diagonal tie rods (8). The outrigger also includes a height adjustment segment. The upper and lower ends of the height adjustment segment are provided with flange connection plates of the same specifications as the outrigger flange connection plates. Multiple height adjustment segments can be assembled. The height adjustment section is installed between the outrigger and the main beam. The lower end of the height adjustment section is fixedly connected to the outrigger flange connection plate at the top of the outrigger by 8.8 grade M20 bolts, and the upper end of the height adjustment section is fixedly connected to the main beam flange connection plate by 8.8 grade M20 bolts. The height can be adjusted by adding or removing height adjustment sections (each section is 100mm high). The length of the adjustable diagonal tie rod of the main beam can be adjusted according to the number of height adjustment sections. The H-shaped frame is welded with 6-series aluminum alloy (6061-T6), and cross-shaped stiffening plates are added inside the frame. According to the material mechanics test, the yield strength of the main beam (1) is ≥450MPa, and the bending stiffness of the outrigger (2) reaches 1.8×10^4 N·m², which meets the GB / T 6892-2015 standard, achieving the unity of lightweight and high strength. Replaceable extension sections for outriggers: The height-adjustable sections adopt a standard section design (each section is 100mm high), connected by 8.8 grade M20 bolts. The bolt hole spacing error is ≤0.1mm, ensuring interchangeability between different sections. The extension sections achieve height compensation in 100mm multiples via flange connections. The outrigger flange connection plate at the bottom of the outrigger is connected to the distribution beam via 8.8 grade M20 bolts.

[0030] The distribution beam is welded from 7075 aviation aluminum alloy sheet, with a flange connection plate of the same specification as the support leg flange connection plate at the top, and wheel box mounting positions at both ends at the bottom.

[0031] The traveling mechanism (3) includes a drive wheel set (31) and a driven wheel set (32) symmetrically arranged at both ends of the distribution beam. The drive wheel set (31) is fixed to the wheel box mounting position at the lower front end of the distribution beam via a wheel box (33). The wheel box (33) is provided with a motor reducer (34), a transmission sprocket (35) keyed to the output shaft of the motor reducer (34), and a tread wheel (36) driven by the transmission sprocket (35) via a roller chain. The driven wheel set (32) is hinged to the wheel box mounting position at the lower rear end of the distribution beam via a rotating shaft.

[0032] The lifting system (4) includes a hoist seat (41) slidably disposed in the transverse guide groove (11), a hand chain hoist (42) fixed to the hoist seat (41) by bolts, a lifting chain (43) connected to the hook of the hand chain hoist (42), and a balance beam (44) connected to the end of the lifting chain (43). The bottom of the balance beam (44) is hinged with a lifting device (46) with a rubber pad by a pin. The rubber pad (45) is 15-20mm thick. The I-shaped cross-sectional dimension tolerance of the transverse guide groove (11) is controlled at IT7 grade, and the sliding fit clearance with the hoist seat (41) is 0.5±0.1mm to ensure the positioning accuracy after the module is assembled.

[0033] The horizontal adjustment mechanism (5) consists of an adjustment handwheel set on the main beam (1), a trapezoidal threaded rod coaxially connected to the handwheel, and a positioning seat fixed on the hoist seat (41). The lead of the trapezoidal threaded rod is 50mm, and the trapezoidal threaded rod and the threaded hole of the positioning seat form a helical pair. The maximum stroke of the horizontal adjustment mechanism (5) is ±50mm, and the positioning accuracy in micro-motion mode is ±0.5mm.

[0034] The guiding mechanism (6) includes guide wheel sets symmetrically installed on both sides of the wheel box (33) of the drive wheel set (31). The guide wheel set consists of two sets of polyurethane guide wheels arranged in a V-shape. The guide wheels maintain a 1-3mm gap with the side wall of the channel steel guide rail through a spring preload device.

[0035] The electrical control system (7) includes an explosion-proof electrical cabinet installed on the distribution beam, a frequency converter connected to the motor reducer (34) via a cable, and a wireless remote controller that communicates via the 2.4GHz frequency band. The electrical cabinet is equipped with an overload protector connected in series in the power supply circuit of the motor reducer (34), and the electrical cabinet panel is equipped with an emergency stop switch that is directly connected to the main power circuit breaker.

[0036] Detailed explanation of working principle and process:

[0037] 1. Overall structural coordination

[0038] Mechanical transmission path: The main beam (1) serves as the core load-bearing component, forming a rigid frame with the outriggers (2) through the flange connecting plate (12). The traveling mechanism (3) at the bottom of the outriggers (2) transmits the load to the track. The hoist seat (41) of the lifting system (4) forms a sliding pair with the transverse guide groove (11), so that the lifting load is distributed laterally along the main beam (1).

[0039] Motion coupling mechanism:

[0040] The motor reducer (34) adopts an integrated design of permanent magnet synchronous motor (rated power 3kW) and planetary reducer (speed ratio 1:30), and with the control of frequency converter, the walking speed is continuously adjustable from 0.1 to 1.5m / s.

[0041] The tread wheel (36) has a diameter of 300mm, a rim hardness of HRC55, a contact width with the track of 80mm, and a wheel pressure of ≤12kN, meeting the low ground pressure requirements of lightweight design. The motor reducer (34) drives the tread wheel (36) to achieve longitudinal movement through chain drive. The trapezoidal threaded rod of the lateral adjustment mechanism (5) and the helical pair of the hoist seat (41) control the lateral positioning, forming an XY two-dimensional precision positioning system.

[0042] The machine's energy consumption during travel is ≤0.8kWh / km, which is 60% lower than that of traditional steel equipment, and the weight of a single piece is ≤150kg, which meets the needs of manual handling.

[0043] 2. Phased Workflow

[0044] Phase 1: Walking and Positioning

[0045] The equipment travels along the track via the traveling mechanism (3). When approaching the construction area, the operator sends a low-speed forward command via a wireless remote control. The frequency converter of the electrical control system (7) outputs a 15Hz frequency power supply, causing the motor reducer (34) to drive the transmission sprocket (35) at a speed of 20r / min. The sprocket drives the tread wheel (36) to rotate via the roller chain, and the equipment moves along the track at a speed of 0.5m / s. The wireless remote control communicates with the frequency converter using the Modbus-RTU protocol and has a built-in PID algorithm to achieve closed-loop speed control.

[0046] The V-shaped polyurethane guide wheels of the guide wheel assembly, under the action of the spring preload device, always maintain a 2mm gap with one side of the channel steel guide rail. When track deviation is detected, the V-shaped included angle (60°) design generates differential resistance on both sides of the guide wheels, automatically correcting the travel deviation. The spring preload device includes an adjusting screw, a disc spring with a stiffness coefficient of 50N / mm, and a locking nut. Rotating the screw can adjust the lateral gap between the guide wheel and the channel steel guide rail to 1-3mm, and the preload force ranges from 500-800N.

[0047] Phase Two: Adjusting the outriggers

[0048] To address the superelevation of the curved track section, the operator selected the second set of bolt holes in the height adjustment segment, loosened the original connecting bolts, and lowered the outrigger (2). The height difference was compensated by adding a new adjustment segment. After adjustment, the pressure at the flange contact surface between the outrigger (2) and the main beam (1) reached 35 MPa according to finite element analysis, ensuring structural stability.

[0049] The bolt hole group of the height adjustment segment is formed in one step by CNC machining center, with a hole spacing error of ≤±0.05mm, ensuring coaxiality when splicing different segments. The flatness of the flange surface connecting the outrigger (2) and the main beam (1) is ≤0.1mm / m. With the high-strength bolt preload control (torque value set at 450N·m), the overall structural rigidity reaches 18kN / mm. The measured height adjustment accuracy of the outrigger is ±1mm, and the compression deformation of the outrigger is ≤0.5mm when bearing 5 tons, meeting the millimeter-level flatness requirements for high-speed rail track slab installation.

[0050] Phase Three: Lifting Operation

[0051] The operator turns the handwheel to drive the trapezoidal threaded rod to rotate. Due to the side effect of the 50mm lead thread, the hoist seat (41) moves laterally along the transverse guide groove (11) with each turn of the handwheel. When transverse movement is required, the handwheel rotates, and the coefficient of friction between the copper-based alloy thread of the positioning seat and the trapezoidal threaded rod is ≤0.1, ensuring a transmission efficiency >92%.

[0052] The rubber pads (45) of the lifting device (46) undergo compression deformation upon contact with the track bed slab. The 15mm thick rubber pads generate a 3mm compression under a 5-ton load, reducing the contact pressure from 12MPa to 4MPa and preventing damage to the concrete surface. Twelve evenly distributed rubber pads (45) are installed at the bottom of the lifting device (46), each measuring 200×200×15mm, with a Shore hardness of 60±5 and a pressure ≤2MPa at a compression deformation rate of 20%. The effective stroke of the transverse guide groove (11) is 50mm.

[0053] Phase Four: Precise Positioning

[0054] When the track bed is close to the installation position, the electrical control system (7) switches to micro-motion mode, the frequency converter outputs 1Hz low-frequency power, and the motor reducer (34) runs at a speed of 0.5r / min. With the adjustment accuracy of 0.05mm / revolution of the horizontal adjustment mechanism (5), ±1mm positioning is achieved. Dynamic compensation of the guide wheel group: the V-shaped guide wheel (62) has an included angle of 60° and the spring preload is adjustable from 500 to 800N. When the track deviation is >3mm, the lateral resistance of the guide wheel automatically increases to 1.5kN, forcibly correcting the deviation.

[0055] 3. Security Protection Logic

[0056] Overload protection: When the load exceeds 5.5 tons, the overload protector detects that the motor current rises to 120% of the rated value and cuts off the power supply within 0.2 seconds. The overload protector uses a Hall current sensor to output a signal to the solenoid valve, which drives the friction plate brake to clamp the lifting chain (43) within 0.2 seconds. The overload protector is set to a threshold of 120% of the motor's rated current (32A), i.e., 38.4A, at which point the power-off protection is triggered.

[0057] Emergency stop response: After the emergency stop switch is triggered, the contactor in the electrical cabinet disconnects the main circuit within 0.1 seconds, and the electromagnetic brake of the motor reducer (34) immediately engages. The emergency stop switch adopts a dual-circuit redundant design, the main power supply cut-off time is ≤80ms, and the braking torque of the electromagnetic brake of the motor reducer (34) is ≥200N·m, ensuring that the sliding distance of a 5-ton load is <30mm.

[0058] The foregoing has shown and described the basic principles, main features, and advantages of the present invention. Those skilled in the art should understand that the present invention is not limited to the above embodiments. The embodiments and descriptions in the specification are merely principles of the invention. Various changes and modifications can be made to the invention without departing from its spirit and scope, and all such changes and modifications fall within the scope of the claimed invention. The scope of protection claimed by the appended claims and their equivalents is defined.

Claims

1. Specialized hoisting equipment for the assembly of a modular resilient solidified road bed, characterized in that, This includes the main beam, outriggers, traveling mechanism, lifting system, lateral adjustment mechanism, guiding mechanism, and electrical control system; among which: The main beam is a segmented rectangular box structure, with I-shaped transverse guide grooves symmetrically arranged on the inner side of the web on both sides. Each segment of the main beam is connected by a pin shaft, and the two ends of the beam are fixed to the top of the support leg by flange connecting plates and bolts. The outrigger has an H-shaped frame structure with a traveling mechanism installed at the bottom. The lower part of the outrigger has a multi-segment height adjustment section, and height compensation is achieved through bolt groups. The traveling mechanism includes a drive wheel set and an articulated driven wheel set symmetrically arranged at the bottom of the outriggers. The drive wheel set drives the chain transmission mechanism through a motor reducer in the wheel box. The lifting system includes a hoist seat that is slidably assembled in the transverse guide groove, a hand chain hoist fixed to the hoist seat, a lifting chain connected to the hand chain hoist, a balance beam at the end of the lifting chain, and a lifting device with a rubber pad that is hinged by a pin. The horizontal adjustment mechanism consists of an adjusting handwheel in the middle of the main beam, a trapezoidal threaded rod coaxially connected to the handwheel, and a positioning seat fixed on the hoist seat, forming a screw pair transmission. The guiding mechanism includes V-shaped guide wheel sets symmetrically arranged on both sides of the drive wheel set, which maintain a gap with the side wall of the channel steel guide rail through a spring preload device; The electrical control system includes an explosion-proof electrical cabinet, a frequency converter for controlling the motor reducer, and a wireless remote controller. The electrical cabinet integrates an overload protection module and an emergency stop switch.

2. Hoisting arrangement according to claim 1, characterized in that: The main beam is provided with a tenon and mortise structure at the segmented connection, and the transverse guide groove achieves a continuous sliding surface through stepped overlap.

3. The hoisting arrangement of claim 1, wherein: The height adjustment segment of the outrigger includes a basic segment and a replaceable height-adjustable segment, and the height is adjusted through a flange connection.

4. The hoisting rig of claim 1, wherein: The chain drive mechanism consists of a drive sprocket, a roller chain, and a tread wheel, with the motor reducer keyed to the drive sprocket.

5. The hoisting rig of claim 1, wherein: The threaded fit clearance between the positioning seat and the trapezoidal threaded rod is adjustable, forming a precision helical pair.

6. The hoisting rig of claim 1, wherein: The V-shaped guide wheel assembly consists of two sets of polyurethane guide wheels, and the gap between the guide wheel and the guide rail is adaptively adjusted by a spring preload device.

7. The hoisting rig of claim 1, wherein: The rubber pads of the lifting device are evenly distributed on the bottom surface of the lifting device and are hinged to the balance beam.

8. The hoisting rig of claim 1, wherein: The wireless remote control controls the travel speed via a frequency converter and supports micro-motion mode positioning.

9. The hoisting rig of claim 1, wherein: The flange connection surfaces of the main beam and the support leg are pre-tightened and fixed with high-strength bolts.

10. The hoisting rig of claim 1, wherein: The overload protection module is connected in series with the power supply circuit of the motor reducer, and after being triggered, it is linked to the braking device to lock the chain.

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