Anti-overturning interlocking structure for external exploration suspension operation platform

Abstract

The present application relates to the technical field of building construction auxiliary equipment, and discloses a kind of anti-overturning interlocking structure for external exploration suspension operation platform, including hydraulic telescopic leg assembly, movable counterweight assembly and hydraulic feedback oil circuit.Hydraulic feedback oil circuit passes through first branch pipe, second branch pipe, check valve and differential pressure valve, so that leg oil cylinder can be driven to drive counterweight block to move out after lifting platform base and making roller off the ground;When the load of hanging plate increases and reaches the compensation condition, the counterweight block moves in the direction away from the hanging plate in one-way progression, and the load is reduced to maintain the achieved compensation position.The structure can convert leg load, roller off the ground, load compensation and overload risk into counterweight position determination, and improve the anti-overturning safety of platform.

Description

Technical Field

[0001] This invention relates to the field of auxiliary equipment technology for building construction, and in particular to an anti-tipping interlocking structure for an external suspended operation platform. Background Technology

[0002] In the installation, maintenance, and cleaning of building curtain walls, as well as in the construction of special areas such as eaves, connecting corridors, stairwells, and the outer sides of trestle bridges between floors, external suspended work platforms are often required. These platforms typically include a platform base, an external truss mounted on the platform base, a suspended work platform at the outer end of the external truss, and a counterweight on the counterweight side of the platform base. During operation, the suspended work platform extends beyond the platform base, and the workers, tools, or materials on the suspended work platform create an external load. The counterweight on the counterweight side of the platform base counteracts the overturning moment generated by the external load, thus reducing the risk of platform tipping over.

[0003] Existing external exploration suspended work platforms, for ease of movement, typically have rollers at the bottom of the platform base, and are supported at the work position by outriggers, adjustable supports, or jacks. During use, operators must first move the platform to the work position, then adjust the outriggers to press them firmly against the ground, relying on counterweights to provide anti-overturning moment. However, in actual construction sites, the ground may be uneven, with localized settlement, or the support pads may have sunk under pressure. Even though the outriggers are extended, they may not necessarily provide reliable load-bearing. Furthermore, if the rollers are still in contact with the ground and sharing the platform's weight, it indicates that the platform is not fully and stably supported by the outriggers. Directly performing external exploration suspended work under these conditions still carries the risk of tipping over.

[0004] Furthermore, existing platforms typically employ fixed or manually added / removed counterweight structures. These counterweight methods are usually configured based on a preset maximum load and cannot automatically adjust the anti-overturning moment according to changes in the actual load on the suspended work platform. Initially configuring too much counterweight increases the difficulty of platform handling, erection, and relocation, and may also cause the platform's center of gravity to shift excessively towards the counterweight side under light load conditions. Conversely, configuring too little counterweight may result in insufficient anti-overturning moment when the load on the suspended platform increases. Existing structures cannot visually reflect the current load compensation margin through the counterweight position, nor can they provide clear warnings to operators when approaching overload conditions.

[0005] Meanwhile, existing outrigger support structures and counterweight structures are usually independent of each other. Whether the outriggers are truly bearing load, whether the rollers are off the ground, whether the load on the suspended platform has increased, and whether the counterweight meets the anti-overturning requirements mainly rely on manual observation and experience. Especially before formal construction, even if the platform has been loaded with personnel, tools, or equivalent test loads, operators find it difficult to determine, through simple and intuitive means, whether a particular outrigger has any hidden dangers such as false support, loss of pressure, local ground subsidence, or oil leaks. Once a particular outrigger becomes unstable during operation, the platform may experience local subsidence, swaying, or tilting, thereby increasing the risk of overturning during external suspended operations.

[0006] However, in existing external suspended work platforms, the outrigger load-bearing status, roller ground clearance, suspended platform load status, counterweight compensation status, and outrigger pressure loss risk typically require separate assessments. For example, determining if the outriggers are firmly supported requires observing the condition of the outriggers or pads; checking if the rollers are off the ground requires examining their contact with the ground; assessing if the suspended platform load is nearing its limit relies on manual estimation; determining if the counterweight is sufficient requires experience-based judgment; and detecting outrigger pressure loss or ground subsidence is difficult in a timely manner. These assessment criteria are fragmented and heavily reliant on manual experience, making them prone to omissions, misjudgments, or inconsistencies.

[0007] Therefore, it is necessary to provide an anti-tipping interlocking structure for an external exploration suspended operation platform, which unifies multiple safety states such as effective outrigger load-bearing, roller off the ground, load compensation, overload warning, and outrigger depressurization pre-detection into the position change of the counterweight block. This allows operators to judge whether the platform has safe operating conditions mainly by observing the position of the counterweight block, thereby reducing the difficulty of on-site judgment and improving the anti-tipping safety of the external exploration suspended operation platform. Summary of the Invention

[0008] The purpose of this invention is to provide an anti-tipping interlocking structure for an external exploration suspended operation platform, in order to solve the problem that the outrigger bearing status, roller off-ground status, suspended platform load status, and counterweight compensation status of existing external exploration suspended operation platforms need to be judged separately, which is prone to overturning risk due to manual omission or misjudgment.

[0009] To achieve the above objectives, the present invention adopts the following technical solution: an anti-tipping interlocking structure for an external suspended working platform, wherein the external suspended working platform includes a platform base, rollers disposed at the bottom of the platform base, an external truss disposed on the platform base, and a suspended working platform disposed at the external end of the external truss; the anti-tipping interlocking structure includes: A hydraulic telescopic outrigger assembly includes multiple outrigger cylinders mounted on a platform base and pads mounted on the telescopic ends of each outrigger cylinder. A movable counterweight assembly includes a support platform slidably mounted on a platform base, a counterweight block mounted on the support platform, and a counterweight cylinder. The counterweight cylinder is used to drive the support platform to move the counterweight block in a direction away from or towards the suspended work platform. The hydraulic feedback circuit includes an input pipe connected to a hydraulic source, an output pipe connected to the rodless chamber of the counterweight cylinder, multiple first branch pipes connecting the input pipe to the rodless chambers of each outrigger cylinder, multiple second branch pipes connecting the rodless chambers of each outrigger cylinder to the output pipe, a first check valve installed on the first branch pipe, a second check valve installed on the second branch pipe, and a differential pressure valve installed on the output pipe. Wherein, the first check valve allows hydraulic medium to enter the rodless chamber of the corresponding outrigger cylinder from the input pipe, the second check valve allows hydraulic medium to enter the output pipe from the rodless chamber of the corresponding outrigger cylinder, and the opening pressure of the differential pressure valve corresponds to the pressure in the rodless chamber of the outrigger cylinder when multiple outrigger cylinders lift the platform base and make the rollers leave the ground; When the roller is not lifted off the ground, the differential pressure valve blocks the connection between the output pipe and the counterweight cylinder; when the roller is lifted off the ground, the differential pressure valve opens, allowing the hydraulic medium to enter the rodless chamber of the counterweight cylinder through the compensation oil circuit consisting of the second branch pipe, the second check valve, the output pipe and the differential pressure valve, so as to drive the counterweight block to move away from the suspended work platform. Furthermore, when the load on the suspended work platform increases and the pressure in the rodless chamber of the outrigger cylinder reaches the corresponding compensation condition, the hydraulic medium enters the rodless chamber of the counterweight cylinder through the compensation oil circuit, driving the counterweight block to move unidirectionally away from the suspended work platform; when the load on the suspended work platform decreases, the second check valve and the differential pressure valve restrict the unexpected backflow of the hydraulic medium in the rodless chamber of the counterweight cylinder, keeping the counterweight block at the reached compensation position.

[0010] Preferably, the effective pressure-bearing cross-sectional area of ​​the rodless chamber of the outrigger cylinder is greater than that of the rodless chamber of the counterweight cylinder, or the combined effective pressure-bearing cross-sectional area of ​​the rodless chambers of multiple outrigger cylinders is greater than that of the rodless chamber of the counterweight cylinder, so that the pressure feedback fluid flow or micro-displacement output in the rodless chamber of the outrigger cylinder can drive the counterweight cylinder to produce an amplified extension stroke.

[0011] Preferably, the platform base is provided with an initial position mark, a support position mark, a dynamic compensation interval mark, and a maximum compensation position mark; when the counterweight is located at the support position mark, it indicates that the multiple outrigger cylinders have lifted the rollers off the ground; when the counterweight is located within the dynamic compensation interval mark, it indicates that the counterweight is in the anti-overturning compensation position that has been reached; when the counterweight is located at the maximum compensation position mark, it indicates that the counterweight compensation capacity is close to or has reached its limit.

[0012] Preferably, the movable counterweight assembly further includes a limit triggering element disposed on the platform base. The limit triggering element includes a contact sensor, a limit switch, or a mechanical triggering element. When the load-bearing platform moves to the maximum compensation position and triggers the limit triggering element, the limit triggering element issues an overload indication signal or triggers an overload warning action to remind that there is a risk of tipping over during operation, reduce the load on the suspended operation platform, or add counterweights to the load-bearing platform.

[0013] Preferably, the hydraulic feedback circuit further includes a pressure loss compensation branch, one end of which is connected to the rodless chamber of the counterweight cylinder, and the other end is connected to the input pipe. The pressure loss compensation branch is equipped with a manual compensation valve and a pressure replenishing check valve. The pressure replenishing check valve allows the hydraulic medium to flow from the rodless chamber of the counterweight cylinder to the input pipe.

[0014] Preferably, when the manual compensation valve is closed, the pressure loss compensation branch is disconnected; when the manual compensation valve is open, the hydraulic medium in the rodless chamber of the counterweight cylinder can be replenished into the rodless chamber of the outrigger cylinder via the pressure loss compensation branch, the pressure replenishment check valve, the input pipe, the first branch pipe, and the first check valve; the manual compensation valve is used to open during the load pre-inspection process before formal construction, so as to determine whether there is false support, ground settlement, oil leakage, support pressure loss, incorrect initial position of counterweight, uneven load, or unexpected individual compression of a single outrigger cylinder based on the displacement direction, displacement amount, or stabilization time of the counterweight block.

[0015] Preferably, the retraction side of the counterweight cylinder is connected to an accumulator. The accumulator is used to provide stored back pressure to the retraction side of the counterweight cylinder when liquid is introduced into the rodless chamber of the counterweight cylinder and the counterweight block is moved away from the suspended working platform, so as to buffer and constrain the extension action of the counterweight cylinder. Furthermore, the accumulator is also used to release the stored back pressure when the rodless chamber of the counterweight cylinder is actively depressurized, so as to push the counterweight cylinder to retract. A return spring is provided in the rod chamber of the outrigger cylinder, and the return spring is used to push the outrigger cylinder to retract in the depressurized and retracted state.

[0016] Preferably, the multiple outrigger cylinders include a near-side outrigger cylinder group closer to the suspended working platform and a far-side outrigger cylinder group farther from the suspended working platform. When the counterweight moves away from the suspended working platform, the center of gravity of the outrigger platform shifts towards the far-side outrigger cylinder group, making the bearing pressure of the far-side outrigger cylinder group greater than that of the near-side outrigger cylinder group. This causes the platform base to form a controlled anti-tilting posture where the side farther from the suspended working platform is lower than the side closer to the suspended working platform. The controlled anti-tilting posture is used to reduce the equivalent horizontal lever arm of the suspended working platform load relative to the platform overturning edge.

[0017] Preferably, the hydraulic source includes a manual hydraulic pump or an electric hydraulic pump and an oil tank. The oil inlet of the manual hydraulic pump or the electric hydraulic pump is connected to the oil tank, and the oil outlet of the manual hydraulic pump or the electric hydraulic pump is connected to the input pipe through a connecting valve. The rodless chamber of the counterweight cylinder is connected to the oil tank through a return branch pipe, and a manual pressure relief valve is provided on the return branch pipe.

[0018] The present invention has the following beneficial effects: 1. This invention establishes a hydraulic feedback circuit connected to the rodless chamber of the outrigger cylinders and installs a differential pressure valve on the output pipe. This ensures that the counterweight cylinders can only operate after multiple outrigger cylinders have lifted the platform base and lifted the rollers off the ground. Thus, the movement of the counterweight is interlocked with the effective load-bearing state of the outriggers, preventing the platform from entering the external exploration operation state while the rollers are still sharing the platform weight and the outriggers are not reliably bearing weight. This improves the support reliability and anti-tipping safety of the external exploration suspended operation platform.

[0019] 2. This invention employs a unidirectional progressive compensation method for the counterweight. When the load on the suspended platform increases and reaches the corresponding compensation condition, the counterweight cylinder drives the support platform and counterweight to move away from the suspended platform, thereby increasing the horizontal lever arm of the counterweight relative to the platform's overturning edge. When the load on the suspended platform decreases, the counterweight does not automatically retract but remains at the achieved compensation position. Thus, the counterweight's position can record the largest load conditions or risk states that have occurred during the current construction cycle. Through the initial position, support positioning, dynamic compensation range, and maximum compensation position, the outrigger load, roller ground clearance, compensation margin, and overload risk are uniformly converted into changes in the counterweight's position, facilitating operators' intuitive assessment of the platform's safety status.

[0020] 3. In this invention, after the counterweight moves outward along the direction away from the suspended working platform, the overall center of gravity of the platform shifts to the side away from the suspended working platform. This causes a relative increase in the pressure on the outrigger cylinders on the side away from the suspended working platform, resulting in controlled micro-compression, while the compression of the outrigger cylinders on the side closer to the suspended working platform is relatively small. This results in a controlled anti-tilting posture for the platform base, where the side away from the suspended working platform is slightly lower and the side closer to the suspended working platform is slightly higher. This controlled anti-tilting posture increases the horizontal lever arm of the counterweight while reducing the equivalent horizontal lever arm of the suspended working platform load relative to the platform's overturning edge, thereby further reducing the overturning moment generated by the external load and improving the platform's anti-tilting stability.

[0021] 4. This invention enables load pre-inspection before formal construction. After the suspended platform is loaded with personnel, tools, materials, or an equivalent test load, the counterweight moves to the corresponding pre-compression reference position, and the counterweight cylinder and accumulator maintain a pressure state corresponding to the pre-compression condition. This creates safety redundancy during formal construction, reducing the risk of unexpected individual compression of a single leg cylinder due to fluctuations in ordinary loads. Simultaneously, operators can observe the displacement direction, displacement amount, and stabilization time of the counterweight during load pre-inspection to determine if there are risks such as false support of the outriggers, ground settlement, oil leakage, incorrect initial counterweight position, uneven loading, or abnormal compression of a single leg, thus eliminating potential platform instability hazards before formal construction. Attached Figure Description

[0022] Figure 1 This is a schematic diagram of the overall three-dimensional structure of the external exploration suspension operation platform in an embodiment of the present invention.

[0023] Figure 2 This is a three-dimensional schematic diagram of the bottom structure of the platform base in an embodiment of the present invention.

[0024] Figure 3 This is a three-dimensional schematic diagram of the upper structure of the platform base in an embodiment of the present invention.

[0025] Figure 4 This is a schematic diagram illustrating how the outrigger cylinder lifts the platform base and causes the rollers to detach from the ground in an embodiment of the present invention.

[0026] Figure 5 This is a schematic diagram showing the positional relationship between the platform base and the movable counterweight component in an embodiment of the present invention.

[0027] Figure 6 This is a schematic diagram of the hydraulic flow when the hydraulic source pressurizes the hydraulic telescopic outrigger assembly, the outrigger cylinder lifts the platform base, and the rollers are lifted off the ground, according to an embodiment of the present invention.

[0028] Figure 7 This is a schematic diagram of the hydraulic flow direction during load pre-inspection before formal construction in an embodiment of the present invention. In the diagram, the arrows indicate the flow direction of the hydraulic medium in the rodless chamber of the counterweight cylinder after the manual compensation valve is opened, which is then replenished into the rodless chamber of the outrigger cylinder through the pressure loss compensation branch.

[0029] Figure 8 This is a schematic diagram of hydraulic feedback compensation when the load on the suspended platform increases in an embodiment of the present invention. In the diagram, the arrows indicate the flow direction of the hydraulic medium in the rodless chamber of the outrigger cylinder through the second branch pipe, the output pipe and the differential pressure valve into the rodless chamber of the counterweight cylinder.

[0030] Figure 9This is a schematic diagram of the hydraulic flow direction when the pressure is released and the cylinder returns to its original position after the operation is completed in an embodiment of the present invention. In the diagram, the arrows indicate the flow direction of the hydraulic medium in the rodless chamber of the counterweight cylinder back to the oil tank through the return branch pipe after the manual pressure relief valve is opened.

[0031] In the picture: 100. Platform base; 101. Rollers; 102. External truss; 103. Suspended work platform; 200. Outrigger cylinder; 201. Pad plate; 301. Loading platform; 302. Counterweight block; 303. Counterweight cylinder; 304. Contact sensor; 305. Accumulator; 306. Return spring; 401. Input pipe; 402. Output pipe; 403. First branch pipe; 404. Second branch pipe; 405. First check valve; 406. Second check valve; 407. Differential pressure valve; 408. Pressure loss compensation branch; 409. Manual compensation valve; 410. Pressure replenishment check valve; 500, Hydraulic power source; 501, Connecting valve; 600, Return branch pipe; 601, Manual pressure relief valve; Wherein, A: initial position marker; B: support in place position marker; BC: dynamic compensation interval marker; D: maximum compensation position marker. Detailed Implementation

[0032] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments.

[0033] In the description of this invention, it should be understood that the terms "upper", "lower", "front", "rear", "left", "right", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0034] Example 1: Overall Structure; like Figures 1 to 5 As shown, this embodiment provides an anti-tipping interlocking structure for an external suspended work platform. The external suspended work platform includes a platform base 100, rollers 101 disposed at the bottom of the platform base 100, an external truss 102 disposed on the platform base 100, and a suspended work platform 103 disposed at the external end of the external truss 102.

[0035] The platform base 100 supports the outer truss 102, the hydraulic telescopic outrigger assembly, the movable counterweight assembly, and the hydraulic feedback circuit. Rollers 101 enable platform movement when not in operation. The suspended work platform 103 supports construction personnel, tools, or materials. One end of the outer truss 102 is connected to the platform base 100, and the other end extends outward from the platform base 100 and connects to the suspended work platform 103, allowing the suspended work platform 103 to be positioned outside the platform base 100 for external suspended operations.

[0036] The hydraulic telescopic outrigger assembly includes multiple outrigger cylinders 200 and pads 201 disposed at the telescopic ends of each outrigger cylinder 200. The multiple outrigger cylinders 200 are distributed at different support positions on the platform base 100. When the outrigger cylinders 200 extend, the pads 201 abut against the ground and lift the platform base 100, causing the rollers 101 to detach from the ground, thereby changing the platform from a roller-supported state to an outrigger-loaded state. Since there may be differences in ground level at the construction site, the outrigger cylinders 200 are allowed to have different extension lengths during initial support. This invention does not require the multiple outrigger cylinders 200 to extend to the same length, but rather requires that the multiple outrigger cylinders 200 collectively form a stable load-bearing state at their respective extension lengths.

[0037] The movable counterweight assembly includes a support platform 301 slidably mounted on the platform base 100, a counterweight block 302 mounted on the support platform 301, and a counterweight cylinder 303. The counterweight cylinder 303 drives the support platform 301 to move the counterweight block 302 in a direction away from or towards the suspended working platform 103. When the counterweight block 302 moves away from the suspended working platform 103, the horizontal lever arm of the counterweight block 302 relative to the overturning edge of the platform increases, thereby improving the platform's anti-overturning capability.

[0038] In one embodiment, an accumulator 305 is connected to the retraction side of the counterweight cylinder 303. The accumulator 305 is preferably a pneumatic accumulator, a diaphragm accumulator, or a piston accumulator. The accumulator 305 is used to provide stored back pressure to the retraction side of the counterweight cylinder 303 when liquid is introduced into the rodless chamber of the counterweight cylinder 303 and the counterweight block 302 is moved away from the suspended working platform 103, so as to buffer and constrain the extension action of the counterweight cylinder 303. Furthermore, when the rodless chamber of the counterweight cylinder 303 is actively depressurized, the accumulator 305 releases the stored back pressure and pushes the counterweight cylinder 303 to retract, so that the support platform 301 drives the counterweight block 302 to return to its original position closer to the suspended working platform 103.

[0039] In one embodiment, the effective pressure-bearing cross-sectional area of ​​the outrigger cylinder 200 is greater than that of the counterweight cylinder 303; or, the combined effective pressure-bearing cross-sectional area of ​​the multiple outrigger cylinders 200 is greater than that of the counterweight cylinder 303. Therefore, the pressure feedback fluid flow or minute displacement output within the rodless chamber of the outrigger cylinder 200 can drive the counterweight cylinder 303 to produce a larger extension stroke, resulting in a more significant positional change in the counterweight block 302. This design improves the sensitivity of the counterweight block 302 to load changes and makes the positional change of the counterweight block 302 easier for the operator to observe, thus better translating the platform's safety status into the positional state of the counterweight block 302.

[0040] like Figure 3 As shown, the platform base 100 is marked with an initial position mark A, a support position mark B, dynamic compensation interval marks BC, and a maximum compensation position mark D. The position of the counterweight 302 reflects the safety status of the platform: when the counterweight 302 is at the initial position mark A, it indicates that the platform is in the initial state before entering support compensation; when the counterweight 302 moves to the support position mark B, it indicates that the outrigger cylinder 200 has lifted the roller 101 off the ground and reached the support position; when the counterweight 302 is within the dynamic compensation interval mark BC, it indicates that the counterweight 302 is in the reached anti-overturning compensation position; when the counterweight 302 moves to the maximum compensation position mark D, it indicates that the current counterweight compensation capacity is close to or has reached its limit.

[0041] In one implementation, such as Figure 2 As shown, the movable counterweight assembly also includes a limit trigger mounted on the platform base 100. The limit trigger includes a contact sensor 304, a limit switch, or a mechanical trigger. The contact sensor 304 is located at a position that can be triggered when the load-bearing platform 301 moves to the maximum compensation position. When the load-bearing platform 301 moves to the maximum compensation position and triggers the contact sensor 304, the contact sensor 304 issues an overload indication signal to remind the operator that there is a risk of tipping over during the current operation, and that the load on the suspended work platform 103 should be reduced or a counterweight 302 should be added to the load-bearing platform 301.

[0042] Therefore, this embodiment does not only provide a fixed anti-overturning moment through the counterweight 302, but also unifies the outrigger bearing state, roller off-ground state, load compensation state and compensation limit state into the position change of the counterweight 302, so that the operator can judge whether the platform has safe operating conditions by observing the position of the counterweight 302.

[0043] Example 2: Interlocking process of outrigger lifting and support positioning; like Figure 6As shown, the hydraulic feedback circuit includes an input pipe 401 connected to the hydraulic source 500, an output pipe 402 connected to the rodless chamber of the counterweight cylinder 303, multiple first branch pipes 403 connecting the input pipe 401 to the rodless chambers of each outrigger cylinder 200, multiple second branch pipes 404 connecting the rodless chambers of each outrigger cylinder 200 to the output pipe 402, a first check valve 405 installed on the first branch pipe 403, a second check valve 406 installed on the second branch pipe 404, and a differential pressure valve 407 installed on the output pipe 402.

[0044] The first check valve 405 allows hydraulic medium to enter the rodless chamber of the corresponding outrigger cylinder 200 from the input pipe 401, preventing the hydraulic medium in the rodless chamber of the outrigger cylinder 200 from flowing back through the first branch pipe 403. The second check valve 406 allows hydraulic medium to enter the output pipe 402 from the rodless chamber of the corresponding outrigger cylinder 200, preventing the hydraulic medium in the output pipe 402 from flowing back into the rodless chamber of the corresponding outrigger cylinder 200. The differential pressure valve 407 is located between the output pipe 402 and the counterweight cylinder 303, and its opening pressure corresponds to the pressure in the rodless chamber of the outrigger cylinder 200 when the multiple outrigger cylinders 200 lift the platform base 100 and lift the rollers 101 off the ground.

[0045] In one embodiment, the differential pressure valve 407 is an adjustable differential pressure opening valve or a pressure control valve with differential pressure opening function. The opening pressure of the differential pressure valve 407 is set according to the pressure in the rodless chamber of the outrigger cylinder 200 when the roller 101 is off the ground. By setting this pressure, the counterweight cylinder 303 will not act prematurely before the outrigger cylinder 200 has effectively lifted the platform base 100, but will only allow hydraulic medium to enter the rodless chamber of the counterweight cylinder 303 after the outrigger cylinder 200 reaches the preset bearing pressure. Therefore, whether the counterweight block 302 moves can be used as a basis for judging whether the roller 101 is off the ground and whether the outrigger cylinder 200 has entered the effective bearing state.

[0046] In one embodiment, the hydraulic source 500 includes a manual hydraulic pump or an electric hydraulic pump and an oil tank. The suction port of the manual hydraulic pump or the electric hydraulic pump is connected to the oil tank, and the outlet port of the manual hydraulic pump or the electric hydraulic pump is connected to the input pipe 401 through a connecting valve 501. During operation preparation, the connecting valve 501 is opened, and the hydraulic source 500 supplies pressure to the input pipe 401.

[0047] When the hydraulic power source 500 supplies pressure to the input pipe 401, the hydraulic medium enters the rodless chamber of the corresponding outrigger cylinder 200 through each first branch pipe 403 and the first check valve 405, pushing the outrigger cylinder 200 to extend. After the outrigger cylinder 200 extends, the pad 201 first contacts the ground, and then continues to lift the platform base 100, causing the roller 101 to gradually detach from the ground.

[0048] Before the roller 101 leaves the ground, the pressure in the rodless chamber of the outrigger cylinder 200 is lower than the opening pressure of the differential pressure valve 407. The differential pressure valve 407 remains closed, and the connection between the output pipe 402 and the rodless chamber of the counterweight cylinder 303 is blocked. The counterweight cylinder 303 does not drive the counterweight block 302 to move outward. At this time, even if the outrigger cylinder 200 has extended, the platform cannot be judged to be stably supported solely by the outrigger extension length. This avoids the mistaken belief that the platform is ready for external exploration operations while the roller 101 may still be sharing the weight.

[0049] As the multiple outrigger cylinders 200 continue to lift the platform base 100 and cause the rollers 101 to leave the ground, the pressure in the rodless chamber of the outrigger cylinders 200 reaches or exceeds the opening pressure of the differential pressure valve 407, causing the differential pressure valve 407 to open. At this time, the hydraulic medium in the rodless chamber of the outrigger cylinders 200 can enter the rodless chamber of the counterweight cylinder 303 through the compensation oil circuit consisting of the second branch pipe 404, the second check valve 406, the output pipe 402, and the differential pressure valve 407, pushing the counterweight cylinder 303 to extend, causing the support platform 301 to drive the counterweight block 302 to move away from the suspended working platform 103.

[0050] When the counterweight 302 moves to the support position mark B, it indicates that the differential pressure valve 407 has opened and the pressure in the rodless chamber of the outrigger cylinder 200 has reached the pressure condition to lift the roller 101 off the ground. Operators do not need to check whether each roller 101 is completely off the ground, nor do they need to individually determine whether each outrigger cylinder 200 is effectively bearing load. Instead, they can determine whether the platform has entered the effective outrigger bearing state by observing whether the counterweight 302 has reached the support position mark B.

[0051] Example 3: Unidirectional progressive compensation and controlled anti-tilting posture during formal construction; like Figure 8 As shown, after the platform enters the formal construction state, the suspended work platform 103 is used to support construction personnel, tools, or materials. When the load on the suspended work platform 103 increases and the pressure in the rodless chamber of the outrigger cylinder 200 reaches the corresponding compensation condition, the hydraulic medium enters the rodless chamber of the counterweight cylinder 303 through the second branch pipe 404, the second check valve 406, the output pipe 402, and the differential pressure valve 407, pushing the counterweight cylinder 303 to extend, causing the support platform 301 to drive the counterweight block 302 to move away from the suspended work platform 103.

[0052] After the counterweight 302 moves further outward, the horizontal lever arm of the counterweight 302 relative to the overturning edge of the platform increases, thereby increasing the anti-overturning moment generated by the counterweight 302 and improving the platform's anti-overturning capacity under larger load conditions. This compensation process is a unidirectional progressive compensation, meaning that the counterweight 302 can gradually move away from the suspended working platform 103 under larger load conditions, but it will not automatically retract as the load on the suspended working platform 103 decreases.

[0053] When the load on the suspended working platform 103 decreases, the second check valve 406 prevents the hydraulic medium in the output pipe 402 from flowing back into the rodless chamber of the outrigger cylinder 200. The differential pressure valve 407, when not meeting the opening conditions, restricts the unexpected backflow of hydraulic medium from the rodless chamber of the counterweight cylinder 303 through the output pipe 402. Simultaneously, both the manual compensation valve 409 and the manual pressure relief valve 601 are closed, preventing the hydraulic medium in the rodless chamber of the counterweight cylinder 303 from being discharged through the pressure loss compensation branch 408 or the return branch pipe 600. Therefore, the counterweight 302 will not automatically retract due to the decrease in load on the suspended working platform 103, but will remain at the already achieved compensation position. Thus, the position of the counterweight 302 can record the largest load or risk state experienced by the platform during the current construction cycle, forming a counterweight position memory function.

[0054] During this process, the counterweight 302 is located within the dynamic compensation range marked BC. By observing the position of the counterweight 302 within the dynamic compensation range marked BC, the operator can determine whether the platform is currently within the normal compensation range. The closer the counterweight 302 is to the maximum compensation position marked D, the closer the platform is to the counterweight compensation limit within the current construction cycle. When the load-bearing platform 301 moves to the maximum compensation position and triggers the contact sensor 304, the contact sensor 304 issues an overload indication signal, reminding the operator to reduce the load on the suspended work platform 103 or add the counterweight 302 to the load-bearing platform 301.

[0055] It should be noted that the reference Figure 4 As the counterweight 302 moves outward away from the suspended working platform 103, the overall center of gravity of the extended suspended working platform shifts towards the direction of the far-side outrigger cylinder group, thus relatively increasing the pressure on the far-side outrigger cylinder group. Simultaneously, the accumulator 305 connected to the retraction side of the counterweight cylinder 303 provides stored energy back pressure to the counterweight cylinder 303, buffering and constraining the outward movement of the counterweight 302. Therefore, under the combined action of the hydraulic feedback circuit and the stored energy back pressure of the accumulator 305, the far-side outrigger cylinder group can generate a controlled, slightly larger compression than the near-side outrigger cylinder group, causing the platform base 100 to form a controlled anti-tilt posture, slightly lower on the side away from the suspended working platform 103 and slightly higher on the side closer to the suspended working platform 103.

[0056] This controlled tilting posture is not a sign of support instability, but rather a favorable posture change formed under the constraints of the outward movement of the counterweight 302, the differential pressure of the outrigger cylinders 200, and the energy storage back pressure of the accumulator 305. In this posture, on the one hand, the outward movement of the counterweight 302 increases the horizontal lever arm of the counterweight 302 relative to the overturning edge of the platform; on the other hand, the platform base 100 forms a controlled tilting posture, which can reduce the equivalent horizontal lever arm of the load of the suspended work platform 103 relative to the overturning edge of the platform, thereby further reducing the overturning moment generated by the load of the suspended work platform 103.

[0057] Example 4: Load pre-inspection and safety redundancy assessment before formal construction Before formal construction, apply personnel, tools, materials, or equivalent test loads to the suspended platform 103 to place the platform under pre-stressing conditions close to those of formal construction. During the pre-stressing process, if... Figure 8 As shown, the load on the suspended working platform 103 increases the force exerted by the platform base 100 on the outrigger cylinder 200, causing the pressure in the rodless chamber of the outrigger cylinder 200 to rise. When this pressure reaches the opening condition of the differential pressure valve 407, the hydraulic medium enters the rodless chamber of the counterweight cylinder 303 through the second branch pipe 404, the second check valve 406, the output pipe 402, and the differential pressure valve 407, pushing the counterweight cylinder 303 to extend, causing the support platform 301 to move the counterweight block 302 away from the suspended working platform 103.

[0058] As the counterweight 302 moves outward, its horizontal lever arm relative to the platform's overturning edge increases, enhancing the platform's anti-overturning capability. Simultaneously, the hydraulic medium on the retracting side of the counterweight cylinder 303 enters the accumulator 305, compressing the gas inside the accumulator 305 via the air bladder, diaphragm, or piston, creating a stored back pressure in the accumulator 305 corresponding to the pre-compression condition. After pre-compression, the counterweight 302 stabilizes at the pre-compression reference position, and the rodless chamber of the counterweight cylinder 303, the retracting side of the counterweight cylinder 303, and the accumulator 305 together form a pressure holding state corresponding to the pre-compression condition. This pre-compression reference position is located within the dynamic compensation interval marked BC. If, during pre-compression, the counterweight 302 directly reaches the maximum compensation position marked D and triggers the contact sensor 304, it indicates that the current pre-compression load has approached or reached the counterweight compensation limit, and the pre-compression load should be reduced, the counterweight 302 added, or the support status rechecked.

[0059] After preloading is completed, the rodless chamber of the counterweight cylinder 303, the retraction side of the counterweight cylinder 303, and the accumulator 305 form a pressure holding state corresponding to the preloading condition. This pressure holding state creates a safety redundancy between the pressure holding state and normal construction load changes. During formal construction, when the actual load on the suspended working platform 103 does not exceed the preloading condition, the pressure in the rodless chamber of the outrigger cylinder 200 is usually insufficient to open the differential pressure valve 407 to push the counterweight cylinder 303 to move again, thereby avoiding unexpected individual compression of one or more outrigger cylinders 200 due to ordinary load fluctuations.

[0060] During pre-pressure testing, such as Figure 7 As shown, the operator opens the manual compensation valve 409 to connect the pressure loss compensation branch 408, and uses the position of the counterweight 302 before opening the manual compensation valve 409 as the pre-inspection reference position. If, within the preset observation time, the counterweight 302 only produces a small displacement within the allowable range relative to the pre-inspection reference position, or can quickly stabilize at the corresponding compensation position, it indicates that the multiple outrigger cylinders 200 can stably support the platform base 100 under the current extension length.

[0061] If the counterweight 302 moves back towards the suspended working platform 103 by more than the allowable amount, it indicates that at least one outrigger cylinder 200 may have insufficient support, ground subsidence, oil leakage, or loss of support pressure. At this time, the hydraulic medium in the rodless chamber of the counterweight cylinder 303 is replenished into the rodless chamber of the outrigger cylinder 200 through the pressure loss compensation branch 408, the pressure replenishment check valve 410, the input pipe 401, the first branch pipe 403, and the first check valve 405 to compensate for the pressure loss of the outrigger cylinder 200; at the same time, the counterweight cylinder 303 retracts under the action of the accumulator 305, and the support platform 301 drives the counterweight 302 to move back towards the suspended working platform 103.

[0062] Through the above-mentioned load pre-inspection, this embodiment does not require multiple outrigger cylinders 200 to extend synchronously and at the same length. Instead, it uses the displacement direction, displacement amount and stabilization time of the counterweight block 302 under pre-compression state to determine whether the outrigger system is in a stable load-bearing state. This eliminates the risk of platform instability caused by false support of outriggers, loss of support pressure, incorrect counterweight position and abnormal compression of a single outrigger cylinder 200 before formal construction.

[0063] It should be noted that after the load pre-inspection is completed, if the position of the counterweight 302 is not suitable as the initial compensation position in the formal construction, the operator can briefly open the manual compensation valve 409, allowing some of the hydraulic medium in the rodless chamber of the counterweight cylinder 303 to flow to the input pipe 401 through the pressure loss compensation branch 408 and the pressure replenishment check valve 410, thereby partially depressurizing the rodless chamber of the counterweight cylinder 303. As the pressure in the rodless chamber of the counterweight cylinder 303 decreases, the accumulator 305 pushes the counterweight cylinder 303 to retract slightly, causing the support platform 301 to drive the counterweight 302 back to the predetermined compensation starting position. After the adjustment is completed, the manual compensation valve 409 is closed, allowing the counterweight 302 to continue to perform unidirectional progressive compensation in the direction away from the suspended working platform 103 during the formal construction process.

[0064] Example 5: Depressurization and return process; like Figure 9 As shown, the retraction side of the counterweight cylinder 303 is connected to an accumulator 305, and the rodless chamber of the counterweight cylinder 303 is connected to the oil tank through a return branch pipe 600. A manual pressure relief valve 601 is installed on the return branch pipe 600. A return spring 306 is installed in the rod chamber of the outrigger cylinder 200. The return spring 306 is used to push the outrigger cylinder 200 to retract in the depressurized retraction state.

[0065] When the work is completed or the platform needs to be moved, the operator opens the manual pressure relief valve 601. The hydraulic medium in the rodless chamber of the counterweight cylinder 303 flows back to the oil tank through the return branch pipe 600, reducing the pressure in the rodless chamber of the counterweight cylinder 303. Since the retraction side of the counterweight cylinder 303 is connected to the accumulator 305, the accumulator 305 pushes the counterweight cylinder 303 to retract when the pressure in the rodless chamber of the counterweight cylinder 303 decreases. This causes the support platform 301 to drive the counterweight block 302 back to its original position near the suspended working platform 103, until the counterweight block 302 returns to the vicinity of the initial position mark A.

[0066] Simultaneously, after the pressure in the rodless chamber of the outrigger cylinder 200 decreases, the return spring 306, located in the rod chamber of the outrigger cylinder 200, pushes the outrigger cylinder 200 to retract, causing the pad 201 to lift off the ground and the roller 101 to re-contact the ground. At this point, the platform returns from the outrigger-supported state to the roller-supported state, enabling it to be moved or stored.

[0067] During this process, the return spring 306 primarily pushes the outrigger cylinder 200 to retract in the depressurized and retracted state, rather than actively changing the supporting pressure of the outrigger cylinder 200 in the working state. This ensures stable support of the outrigger cylinder 200 to the platform base 100 during operation, while also enabling automatic retraction of the outrigger cylinder 200 after depressurization, thus improving the convenience of retraction.

[0068] In other embodiments, to prevent sudden displacement of the counterweight 302 when the load on the suspended work platform 103 changes, a throttling damping element can be installed on the second branch pipe 404 or the output pipe 402. The throttling damping element does not block the pressure transmission between the rodless chamber of the outrigger cylinder 200 and the rodless chamber of the counterweight cylinder 303, but rather limits the flow rate of hydraulic medium from the rodless chamber of the outrigger cylinder 200 to the rodless chamber of the counterweight cylinder 303, allowing the counterweight 302 to move smoothly with changes in the load on the suspended work platform 103, preventing rapid outward movement of the counterweight 302 that could cause platform swaying.

[0069] In summary, this embodiment uses a hydraulic feedback circuit to link the pressure state of the outrigger cylinder 200 with the action of the counterweight cylinder 303. This allows the position of the counterweight 302 to reflect the outrigger's load-bearing state, roller off-ground state, load compensation state, overload state, and outrigger instability risk during load pre-inspection. This unifies multiple dispersed safety judgments into an observation and judgment of the counterweight 302's position, improving the anti-tipping safety of the external suspended work platform.

[0070] The above description is only a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any equivalent substitutions or modifications made by those skilled in the art within the scope of the technology disclosed in the present invention, based on the technical solution and inventive concept of the present invention, should be covered within the scope of protection of the present invention.

Claims

1. An anti-tipping interlocking structure for an external suspended working platform, the external suspended working platform comprising a platform base (100), rollers (101) disposed at the bottom of the platform base (100), an external truss (102) disposed on the platform base (100), and a suspended working platform (103) disposed at the external end of the external truss (102), characterized in that, include: The hydraulic telescopic outrigger assembly includes a plurality of outrigger cylinders (200) disposed on the platform base (100) and a pad (201) disposed at the telescopic end of each outrigger cylinder (200). The movable counterweight assembly includes a support platform (301) slidably mounted on a platform base (100), a counterweight block (302) mounted on the support platform (301), and a counterweight cylinder (303). The counterweight cylinder (303) is used to drive the support platform (301) to move the counterweight block (302) in a direction away from or towards the suspended work platform (103). The hydraulic feedback circuit includes an input pipe (401) connected to a hydraulic source (500), an output pipe (402) connected to the rodless chamber of a counterweight cylinder (303), multiple first branch pipes (403) connecting the input pipe (401) to the rodless chambers of each outrigger cylinder (200), multiple second branch pipes (404) connecting the rodless chambers of each outrigger cylinder (200) to the output pipe (402), a first check valve (405) installed on the first branch pipe (403), a second check valve (406) installed on the second branch pipe (404), and a differential pressure valve (407) installed on the output pipe (402). Wherein, the first check valve (405) allows hydraulic medium to enter the rodless chamber of the corresponding outrigger cylinder (200) through the input pipe (401), and the second check valve (406) allows hydraulic medium to enter the output pipe (402) through the rodless chamber of the corresponding outrigger cylinder (200). The opening pressure of the differential pressure valve (407) corresponds to the pressure in the rodless chamber of the outrigger cylinder (200) when the multiple outrigger cylinders (200) lift the platform base (100) and make the rollers (101) leave the ground; When the roller (101) is not lifted off the ground, the differential pressure valve (407) blocks the connection between the output pipe (402) and the counterweight cylinder (303); when the roller (101) is lifted off the ground, the differential pressure valve (407) opens, allowing the hydraulic medium to enter the rodless chamber of the counterweight cylinder (303) through the compensation oil circuit consisting of the second branch pipe (404), the second check valve (406), the output pipe (402) and the differential pressure valve (407), so as to drive the counterweight block (302) to move away from the suspended working platform (103); Furthermore, when the load on the suspended working platform (103) increases and the pressure in the rodless chamber of the outrigger cylinder (200) reaches the corresponding compensation condition, the hydraulic medium enters the rodless chamber of the counterweight cylinder (303) through the compensation oil circuit, driving the counterweight block (302) to move unidirectionally away from the suspended working platform (103); when the load on the suspended working platform (103) decreases, the second check valve (406) and the differential pressure valve (407) restrict the unexpected backflow of the hydraulic medium in the rodless chamber of the counterweight cylinder (303), keeping the counterweight block (302) in the reached compensation position.

2. The anti-tipping interlocking structure for an external suspended work platform according to claim 1, characterized in that: The effective pressure-bearing cross-sectional area of ​​the rodless chamber of the outrigger cylinder (200) is greater than that of the effective pressure-bearing cross-sectional area of ​​the rodless chamber of the counterweight cylinder (303), or the combined effective pressure-bearing cross-sectional area of ​​the rodless chambers of multiple outrigger cylinders (200) is greater than that of the effective pressure-bearing cross-sectional area of ​​the rodless chamber of the counterweight cylinder (303), so that the pressure feedback fluid flow or micro-displacement output in the rodless chamber of the outrigger cylinder (200) can drive the counterweight cylinder (303) to generate an amplified extension stroke.

3. The anti-tipping interlocking structure for an external suspended work platform according to claim 1, characterized in that: The platform base (100) is marked with an initial position mark, a support position mark, a dynamic compensation interval mark, and a maximum compensation position mark. When the counterweight (302) is located at the support position mark, it indicates that multiple outrigger cylinders (200) have lifted the roller (101) off the ground. When the counterweight (302) is located within the dynamic compensation interval mark, it indicates that the counterweight (302) is in the anti-overturning compensation position that has been reached. When the counterweight (302) is located at the maximum compensation position mark, it indicates that the counterweight compensation capacity is close to or has reached its limit.

4. The anti-tipping interlocking structure for an external suspended work platform according to claim 1, characterized in that: The movable counterweight assembly also includes a limit trigger on the platform base (100). The limit trigger includes a contact sensor (304), a limit switch, or a mechanical trigger. When the load-bearing platform (301) moves to the maximum compensation position and triggers the limit trigger, the limit trigger sends an overload indication signal or triggers an overload warning action to remind that there is a risk of tipping over, reduce the load on the suspended work platform (103), or add a counterweight (302) to the load-bearing platform (301).

5. The anti-tipping interlocking structure for an external suspended work platform according to claim 1, characterized in that: The hydraulic feedback circuit also includes a pressure loss compensation branch (408), one end of which is connected to the rodless chamber of the counterweight cylinder (303), and the other end is connected to the input pipe (401). The pressure loss compensation branch (408) is equipped with a manual compensation valve (409) and a pressure replenishing check valve (410). The pressure replenishing check valve (410) allows the hydraulic medium to flow from the rodless chamber of the counterweight cylinder (303) to the input pipe (401).

6. The anti-tipping interlocking structure for an external suspended work platform according to claim 5, characterized in that: When the manual compensation valve (409) is closed, the pressure loss compensation branch (408) is disconnected; when the manual compensation valve (409) is open, the hydraulic medium in the rodless chamber of the counterweight cylinder (303) can be replenished into the rodless chamber of the outrigger cylinder (200) through the pressure loss compensation branch (408), the pressure replenishment check valve (410), the input pipe (401), the first branch pipe (403) and the first check valve (405); The manual compensation valve (409) is used to open during the load pre-inspection process before formal construction to determine whether the outrigger cylinder (200) has false support, ground settlement, oil leakage, support pressure loss, incorrect initial position of counterweight, uneven load, or unintended compression of a single outrigger cylinder (200) based on the displacement direction, displacement amount, or stabilization time of the counterweight block (302).

7. The anti-tipping interlocking structure for an external suspended work platform according to claim 1, characterized in that: An accumulator (305) is connected to the retraction side of the counterweight cylinder (303). The accumulator (305) is used to provide energy storage back pressure to the retraction side of the counterweight cylinder (303) when liquid is introduced into the rodless chamber of the counterweight cylinder (303) and the counterweight block (302) is pushed to move away from the suspended working plate (103), so as to buffer and constrain the extension action of the counterweight cylinder (303). In addition, the accumulator (305) is also used to release the energy storage back pressure when the rodless chamber of the counterweight cylinder (303) is actively depressurized, so as to push the counterweight cylinder (303) to retract. A return spring (306) is provided in the rod chamber of the outrigger cylinder (200). The return spring (306) is used to push the outrigger cylinder (200) to retract in the depressurized retraction state.

8. The anti-tipping interlocking structure for an external suspended work platform according to claim 7, characterized in that: Multiple outrigger cylinders (200) include a near-side outrigger cylinder group close to the side of the suspended working platform (103) and a far-side outrigger cylinder group away from the side of the suspended working platform (103); when the counterweight (302) moves away from the suspended working platform (103), the center of gravity of the outrigger platform shifts towards the direction of the far-side outrigger cylinder group, so that the pressure of the far-side outrigger cylinder group is greater than that of the near-side outrigger cylinder group, and the platform base (100) forms a controlled anti-tilt posture where the side away from the suspended working platform (103) is lower than the side close to the suspended working platform (103). The controlled anti-tilt posture is used to reduce the equivalent horizontal lever arm of the load of the suspended working platform (103) relative to the overturning edge of the platform.

9. The anti-tipping interlocking structure for an external suspended work platform according to claim 1, characterized in that: The hydraulic source (500) includes a manual hydraulic pump or an electric hydraulic pump and an oil tank. The oil inlet of the manual hydraulic pump or the electric hydraulic pump is connected to the oil tank, and the oil outlet of the manual hydraulic pump or the electric hydraulic pump is connected to the input pipe (401) through a connecting valve (501). The rodless chamber of the counterweight cylinder (303) is connected to the oil tank through a return branch pipe (600), and a manual pressure relief valve (601) is provided on the return branch pipe (600).

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