Landing leg control system of crawler scissor type overhead working truck

Abstract

The utility model provides a crawler scissor type overhead working truck landing leg control system and control method, which comprises a hydraulic oil tank, a gear pump, a speed reducer motor and a landing leg oil cylinder, a walking main oil inlet pipeline and a landing leg main oil inlet pipeline are respectively connected with the speed reducer motor and the landing leg oil cylinder through a walking control valve group and a landing leg control valve group; a priority valve is arranged on a pipeline of an oil outlet of the gear pump, and a valve element of the priority valve is connected with a walking main oil return pipeline arranged between the walking control valve set and the hydraulic oil tank through an electromagnetic switch control valve. A switch reversing valve is arranged on the supporting leg main oil inlet pipeline and is a three-position four-way electromagnetic valve. Hydraulic pressure is adopted as power to drive the speed reducer motor to drive the walking mechanism to act, the priority valve is arranged, oil liquid preferentially meets the working condition of retracting the supporting legs in the running process, a more economical scheme is used for achieving component type selection, energy consumption is reduced, endurance is prolonged, and the function of retracting the supporting legs can be achieved while the vehicle runs normally.

Description

Technical Field

[0001] The utility model relates to a crawler scissor type aerial work vehicle outrigger control system, belonging to the technical field of aerial work platforms. Background Art

[0002] The existing crawler scissor lifts on the market generally use travel motors to directly drive their travel systems. Considering that crawler models often involve some harsh working conditions, their reliability is not as good as hydraulic motors in muddy and muddy environments.

[0003] The crawler scissors on the domestic market are mainly electric-driven, and there are fewer hydraulic-driven products. The main reasons for this are as follows.

[0004] First, crawler scissor lifts with outriggers can retract their outriggers while traveling after completing their work and preparing to move to another location. This prevents the operator from forgetting to retract the outrigger cylinders to a safe position before traveling, which could result in damage to the outriggers. Electric-driven crawler scissor lifts on the market operate simultaneously without interfering with each other, as their travel systems are electrically controlled and their outriggers are hydraulically controlled. However, hydraulic-driven crawler scissor lifts utilize hydraulic control for both movements, posing challenges in component selection and flow distribution.

[0005] Secondly, because the travel system and outrigger system need to work simultaneously, the required flow rate will be very large, while the flow rate required during the work platform lifting process is relatively small. If a fixed-displacement gear pump is used for the entire machine, it will waste energy when performing the lifting operation under the working conditions of traveling and extending the outriggers. Moreover, the gear pump and motor are operating in an inefficient speed range, and the endurance of the entire machine is poor. If a variable displacement piston pump is used, it can solve the problem of large differences in flow rates required for different working conditions, but the size and cost of a variable displacement pump far exceed those of a gear pump, so it cannot be used. Summary of the Invention

[0006] Purpose of the invention: In view of the deficiencies in the prior art, the present invention provides a crawler scissors-type aerial work vehicle outrigger control system. By setting an electromagnetic switch valve, the vehicle can independently choose whether to control the combined walking mechanism and the outrigger mechanism. By setting a priority valve, the outriggers can be controlled to retract at the same time when the vehicle starts to move. Both walking and outrigger retraction are achieved through a hydraulic system, which has a low cost and better driving stability on muddy roads.

[0007] Technical solution: A crawler scissor lift outrigger control system includes a hydraulic oil tank, a gear pump, a reducer motor, and an outrigger oil cylinder. The gear pump oil outlet pipeline is divided into two branches, namely the main oil inlet pipeline for travel and the main oil inlet pipeline for outriggers. The main oil inlet pipeline for travel and the main oil inlet pipeline for outriggers are connected to the reducer motor and the outrigger oil cylinder through the travel control valve group and the outrigger control valve group respectively.

[0008] A priority valve is provided on the pipeline of the gear pump oil outlet, and the valve core of the priority valve is connected to the main oil return pipeline of the travel arranged between the travel control valve group and the hydraulic oil tank through the electromagnetic switch control valve. When the power is off, the electromagnetic switch control valve is in a two-way conduction state;

[0009] A switch reversing valve is provided on the main oil inlet pipeline of the support leg, and the switch reversing valve is a three-position four-way solenoid valve.

[0010] The utility model adopts hydraulics as the power to drive the reducer motor to drive the walking mechanism. Compared with the walking mechanism driven by an electric motor, it has a wider range of applications and can be stably used in wet and muddy working environments. By setting a priority valve, it can ensure that the oil will give priority to the working conditions of the retracting and outriggering legs during driving. A more economical solution is used to solve the component selection, which not only ensures the reduction of energy consumption and increase of endurance, but also realizes the function of retracting the outriggers while the vehicle is driving normally.

[0011] The outrigger control valve group includes two groups of front outrigger control valve groups and rear outrigger control valve groups with the same structure. Any front outrigger control valve group or rear outrigger control valve group includes an electromagnetic switch valve installed in the left outrigger oil cylinder and the right outrigger oil cylinder, and an outrigger switch valve arranged between the two electromagnetic switch valves and the switch reversing valve.

[0012] By setting two groups of corresponding outrigger control valve groups on the front and rear outrigger cylinders respectively, the control of the front and rear outrigger cylinders can be achieved, and the action of the outrigger cylinders on one side can be shielded by the outrigger switch valve, so that only the front or rear outrigger cylinders can be controlled to lift or lower separately. Under the condition of the same oil flow, the outrigger cylinder extension or retraction action can be completed faster.

[0013] The electromagnetic switch valve is arranged on the oil circuit corresponding to the large chamber of the outrigger oil cylinder, and also includes a hydraulically controlled one-way valve arranged between the electromagnetic switch valve and the outrigger switch valve. The hydraulically controlled one-way valve is arranged on the oil circuit corresponding to the large chamber of the outrigger oil cylinder and is connected to the oil circuit corresponding to the small chamber of the outrigger oil cylinder.

[0014] In order to ensure that the outrigger oil cylinder can provide stable support after being extended, an electromagnetic switch valve is set. When the oil cylinder needs to be moved, the electromagnetic switch valve is energized and the oil circuit is connected. When it is not energized, it is in a blocked state. After the outrigger oil cylinder is extended, the electromagnetic switch valve is not energized to achieve stable support. A hydraulically controlled one-way valve is set to ensure stable support even when the electromagnetic switch valve fails to block.

[0015] The travel control valve group includes an electromagnetic proportional reversing valve and a pressure compensation valve arranged on the oil circuit between the electromagnetic proportional reversing valve and the reducer motor.

[0016] In order to achieve hydraulically driven walking, an electromagnetic proportional reversing valve and a pressure compensation valve are set so that the hydraulic oil output to the reducer motor is only controlled by the opening size of the electromagnetic proportional reversing valve, which ensures stable operation and high reliability.

[0017] An overflow valve is provided between the main traveling oil inlet pipeline and the main traveling oil return pipeline, and a one-way valve is provided between the overflow valve and the main traveling oil inlet pipeline.

[0018] In order to protect the hydraulic system, an overflow valve is set up. When the system pressure value is too high, the excess hydraulic oil is returned to the oil tank through the overflow valve.

[0019] A three-way flow valve is provided between the main traveling oil inlet pipeline and the main traveling oil return pipeline.

[0020] The starting pressure value of the three-way flow valve is lower than that of the relief valve. When the system pressure value is too high, it will overflow from the three-way relief valve first, making the pressure value in the system smaller than the pressure value overflowing through the relief valve, resulting in less energy loss and achieving energy-saving effects.

[0021] Beneficial effects: The utility model adopts hydraulic power as the power to drive the reducer motor to drive the walking mechanism. Compared with the walking mechanism driven by the motor, it has a wider range of applications and can be stably used in wet and muddy working environments. By setting a priority valve, it can ensure that the oil will give priority to the working conditions of the retracting and outriggering legs during driving. A more economical solution is used to solve the component selection, which not only ensures the reduction of energy consumption and increase of endurance, but also realizes the function of retracting the outriggers while the vehicle is driving normally. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are merely embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on the provided drawings without paying any creative work.

[0023] Figure 1 This is the hydraulic principle diagram of the utility model. DETAILED DESCRIPTION

[0024] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the embodiments described are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0025] In the description of the present invention, it should be understood that the terms "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating directions or positional relationships, are based on the directions or positional relationships shown in the accompanying drawings. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific direction, be constructed and operated in a specific direction. Therefore, they should not be understood as limitations on the present invention.

[0026] In the present invention, unless otherwise expressly specified or limited, a first feature being "above" or "below" a second feature may include the first and second features being in direct contact, or may include the first and second features being in contact not directly but through another feature between them. Moreover, a first feature being "above," "above," and "above" a second feature may include the first feature being directly above or obliquely above the second feature, or may simply mean that the first feature is higher in level than the second feature. A first feature being "below," "below," and "below" a second feature may include the first feature being directly below or obliquely below the second feature, or may simply mean that the first feature is lower in level than the second feature.

[0027] like Figure 1 As shown, a crawler scissor lift outrigger control system includes a hydraulic oil tank 1, a gear pump 2, a reducer motor 3 and an outrigger oil cylinder. The oil outlet pipeline of the gear pump 2 is divided into two branches, namely the main oil inlet pipeline for walking and the main oil inlet pipeline for outriggers. The main oil inlet pipeline for walking and the main oil inlet pipeline for outriggers are connected to the reducer motor 3 and the outrigger oil cylinder through the walking control valve group 4 and the outrigger control valve group 5 respectively.

[0028] A priority valve 6 is provided on the pipeline of the oil outlet of the gear pump 2. The valve core of the priority valve 6 is connected to the main return oil pipeline of the travel arranged between the travel control valve group 4 and the hydraulic oil tank 1 through the electromagnetic switch control valve 7. When the power is off, the electromagnetic switch control valve 7 is in a two-way conduction state;

[0029] A switch reversing valve 8 is provided on the main oil inlet pipeline of the support leg, and the switch reversing valve 8 is a three-position four-way solenoid valve.

[0030] The utility model adopts hydraulic power as the driving force to drive the reducer motor 3 to drive the walking mechanism to move. Compared with the walking mechanism driven by the motor, it has a wider range of applications and can be stably used in wet and muddy working environments. By setting the priority valve 6, it is ensured that the oil will give priority to meeting the working conditions of the retracting and outrigger legs during driving. A more economical solution is used to solve the component selection, which not only ensures the reduction of energy consumption and the increase of endurance, but also realizes the function of retracting the outriggers while the vehicle is driving normally.

[0031] The outrigger control valve group 5 includes two groups of front outrigger control valve groups 51 and rear outrigger control valve groups 52 with the same structure. Any front outrigger control valve group 51 or rear outrigger control valve group 52 includes an electromagnetic switch valve 53 installed on the left outrigger oil cylinder and the right outrigger oil cylinder, and an outrigger switch valve 54 arranged between the two electromagnetic switch valves 53 and the switch reversing valve 8.

[0032] By setting two groups of correspondingly controlled outrigger control valve groups 5 on the front and rear outrigger cylinders respectively, the control of the front and rear outrigger cylinders is achieved, and the action of the outrigger cylinders on one side can be shielded by the outrigger switch valve 54, so that only the front or rear outrigger cylinder is controlled to lift or lower separately. Under the condition of the same oil flow rate, the outrigger cylinder extension or retraction action can be completed faster.

[0033] The electromagnetic switch valve 53 is arranged on the oil circuit corresponding to the large chamber of the outrigger oil cylinder, and also includes a hydraulically controlled one-way valve 55 arranged between the electromagnetic switch valve 53 and the outrigger switch valve 54. The hydraulically controlled one-way valve 55 is arranged on the oil circuit corresponding to the large chamber of the outrigger oil cylinder, and is connected to the oil circuit corresponding to the small chamber of the outrigger oil cylinder.

[0034] In order to ensure that the outrigger oil cylinder can provide stable support after being extended, an electromagnetic switch valve 53 is set. When the oil cylinder needs to be moved, the electromagnetic switch valve 53 is energized and the oil circuit is connected. When it is not energized, it is in a blocked state. After the outrigger oil cylinder is extended, the electromagnetic switch valve 53 is not energized, thereby achieving stable support. A hydraulically controlled one-way valve 55 is set, so that stable support can still be maintained when the electromagnetic switch valve 53 fails to be blocked.

[0035] The travel control valve group 4 includes an electromagnetic proportional reversing valve 41 and a pressure compensation valve 9 provided on the oil path between the electromagnetic proportional reversing valve 41 and the reducer motor 3 .

[0036] In order to achieve hydraulically driven travel, an electromagnetic proportional reversing valve 41 and a pressure compensation valve 9 are provided so that the hydraulic oil output to the reducer motor 3 is only controlled by the opening size of the electromagnetic proportional reversing valve 41, and the operation is stable and the reliability is high.

[0037] A relief valve 10 is provided between the main traveling oil inlet pipeline and the main traveling oil return pipeline, and a one-way valve 101 is provided between the relief valve 10 and the main traveling oil inlet pipeline.

[0038] In order to protect the hydraulic system, a relief valve 10 is provided. When the system pressure value is too high, the excess hydraulic oil is returned to the oil tank through the relief valve 10.

[0039] A three-way flow valve 102 is provided between the main traveling oil inlet pipeline and the main traveling oil return pipeline.

[0040] The starting pressure value of the three-way flow valve 102 is lower than that of the relief valve 10. When the system pressure value is too high, it will overflow from the three-way relief valve 10 first, so that the pressure value in the system is smaller than the pressure value overflowing through the relief valve 10, and the energy loss is smaller, thereby achieving energy saving effect.

[0041] A control method for a crawler scissor-type aerial work vehicle outrigger control system.

[0042] The electromagnetic switch control valve 7 is energized, and the working condition is divided into fully supported working condition and incompletely supported working condition according to the outrigger status;

[0043] The vehicle completes the support action, the outrigger oil cylinders are extended and in contact with the ground, entering the fully supported working condition, the operator issues a travel command, the electromagnetic proportional reversing valve 41 is de-energized, the traveling mechanism does not move, the operator issues a retraction command for the outrigger oil cylinders, and the switch reversing valve 8 is energized;

[0044] The outrigger oil cylinder retracts to leave the ground and enters the partially supported working condition. The operator issues a travel command, the electromagnetic proportional reversing valve 41 is energized, the whole system determines the direction of the travel command, and controls the outrigger switch valve 54 in the opposite direction to be energized, so that the outrigger oil cylinder in the travel direction is retracted first. 4 to 6 seconds after the operator issues the travel command, the outrigger switch valve 54 on the other side is de-energized and reset to the passage position, and the outrigger oil cylinders are all retracted.

[0045] The fully supported working condition is specifically as follows: a detection switch is installed at the connection between the frame and the outrigger cylinder, and the outrigger cylinder has an extending movement. When the outrigger cylinder is extended and supported on the ground, the cylinder barrel moves up and contacts the detection switch. When the cylinder barrels of the front and rear outrigger cylinders both move up and contact the detection switch, the system determines that the current condition is a fully supported working condition.

[0046] The incomplete support working condition is specifically: the outrigger oil cylinder has an extension action, and at least one outrigger oil cylinder is not in contact with the detection switch.

[0047] The various embodiments in this specification are described in a progressive manner, with each embodiment focusing on the differences from other embodiments. Reference can be made to the common and similar parts between the various embodiments. For the devices disclosed in the embodiments, since they correspond to the methods disclosed in the embodiments, the description is relatively simple, and the relevant parts can be referred to the method description.

[0048] The above description of the disclosed embodiments will enable one skilled in the art to implement or use the present invention. Various modifications to these embodiments will be readily apparent to one skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of the present invention. Therefore, the present invention is not limited to the embodiments shown herein but is intended to conform to the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A crawler scissor lift aerial work vehicle outrigger control system, comprising a hydraulic oil tank (1), a gear pump (2), a reducer motor (3) and an outrigger oil cylinder, wherein the oil outlet pipeline of the gear pump (2) is divided into two branches, namely a main oil inlet pipeline for traveling and a main oil inlet pipeline for outriggers, the main oil inlet pipeline for traveling and the main oil inlet pipeline for outriggers being connected to the reducer motor (3) and the outrigger oil cylinder via a traveling control valve group (4) and an outrigger control valve group (5), respectively, and characterized in that: A priority valve (6) is provided on the pipeline of the oil outlet of the gear pump (2); the valve core of the priority valve (6) is connected to the main oil return pipeline of the travel arranged between the travel control valve group (4) and the hydraulic oil tank (1) through the electromagnetic switch control valve (7); in the power-off state, the electromagnetic switch control valve (7) is in a two-way conduction state; A switch reversing valve (8) is provided on the main oil inlet pipeline of the support leg, and the switch reversing valve (8) is a three-position four-way solenoid valve.

2. The crawler scissor lift outrigger control system according to claim 1, characterized in that: The outrigger control valve group (5) comprises two groups of front outrigger control valve groups (51) and rear outrigger control valve groups (52) of identical structure. Any of the front outrigger control valve groups (51) and rear outrigger control valve groups (52) comprises electromagnetic switch valves (53) installed in the left outrigger oil cylinder and the right outrigger oil cylinder, and an outrigger switch valve (54) arranged between the two electromagnetic switch valves (53) and the switch reversing valve (8).

3. The crawler scissor lift outrigger control system according to claim 2, characterized in that: The electromagnetic switch valve (53) is arranged on the oil circuit corresponding to the large chamber of the outrigger oil cylinder, and further comprises a hydraulically controlled one-way valve (55) arranged between the electromagnetic switch valve (53) and the outrigger switch valve (54). The hydraulically controlled one-way valve (55) is arranged on the oil circuit corresponding to the large chamber of the outrigger oil cylinder and is in communication with the oil circuit corresponding to the small chamber of the outrigger oil cylinder.

4. The crawler scissor lift outrigger control system according to claim 1, characterized in that: The travel control valve group (4) comprises an electromagnetic proportional reversing valve (41) and a pressure compensation valve (9) arranged on the oil circuit between the electromagnetic proportional reversing valve (41) and the reducer motor (3).

5. The crawler scissor lift outrigger control system according to claim 1, characterized in that: A relief valve (10) is provided between the main traveling oil inlet pipeline and the main traveling oil return pipeline, and a one-way valve (101) is provided between the relief valve (10) and the main traveling oil inlet pipeline.

6. The crawler scissor lift outrigger control system according to claim 1, characterized in that: A three-way flow valve (102) is provided between the main traveling oil inlet pipeline and the main traveling oil return pipeline.

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