Luffing control system and operation machine

Abstract

Disclosed are a luffing control system and an operation machine. The luffing control system comprises: a balance valve (1) configured for connection to an actuator (2), the balance valve comprising a first control port (101) and a second control port (102), the oil return opening degree of the balance valve being proportional to the pressure difference between the oil pressure at the second control port and the oil pressure at the first control port, and the second control port being connected to an oil port of the balance valve; and a first adjustable damper (3) and a second adjustable damper (4) which are arranged in series and connected in parallel to the balance valve, an oil passage between the first adjustable damper and the second adjustable damper being connected to the first control port, and a valve element of the first adjustable damper being linked with a valve element of the balance valve so as to allow the opening degree of the first adjustable damper change along with the oil return opening degree of the balance valve. By means of the cooperation of the first adjustable damper with the second adjustable damper, the effect of adjusting the opening degree of the balance valve is achieved, and by means of the linkage of the first adjustable damper and the balance valve, frequent changes in flow of the balance valve caused by pressure fluctuation are reduced, thereby reducing the problem of jitter.

Description

Luffing control system and operating machinery

[0001] CROSS-REFERENCE TO RELATED APPLICATIONS

[0002] This application claims priority to Chinese patent application No. 202410218447.X, filed on February 28, 2024, entitled “Amplitude Control System and Operating Machinery,” which is incorporated herein by reference in its entirety. Technical Field

[0003] The present application relates to the technical field of hydraulic systems, and in particular to a variable amplitude control system and an operating machine. Background Art

[0004] In the field of aerial work, aerial work machinery often requires actuators such as hydraulic cylinders or hydraulic motors to complete lifting actions, and the actuators usually require a balancing valve to control the descent speed.

[0005] Referring to Figure 2, a balancing valve 1' in related art is typically controlled by an external pilot oil control. For example, in the descending state, the actuator's oil return port is connected to the oil tank through the balancing valve 1', and the pilot oil port of the balancing valve 1' is connected to the oil inlet chamber 201' of the actuator 2'. When the pressurized oil provided by the oil pump flows into the oil inlet chamber 201' of the actuator 2', some of the pressurized oil enters the pilot oil port of the balancing valve 1', driving the balancing valve 1' to open, allowing the pressurized oil at the actuator 2's oil return port to flow out through the balancing valve 1', causing the actuator 2' to descend.

[0006] The inventors have discovered that when the above-mentioned balancing valve is in use, when pressure fluctuations occur in the oil inlet chamber of the actuator, such pressure fluctuations will be transmitted to the balancing valve, causing the opening of the balancing valve to change frequently, thereby causing the actuator to vibrate.

[0007] Summary of the Invention

[0008] The present application provides a variable amplitude control system and an operating machine to solve the defect in the related art that the balancing valve may cause the actuator to vibrate, thereby achieving the effect of stabilizing and adjusting the balancing valve.

[0009] The present application provides a variable amplitude control system, comprising:

[0010] a balancing valve for connecting to an actuator and enabling oil return from the actuator, the balancing valve comprising a first control port and a second control port, the oil return opening of the balancing valve being proportional to the difference between the oil pressure at the second control port and the oil pressure at the first control port, the second control port being connected to an oil port of the balancing valve connected to the actuator;

[0011] The first adjustable damping and the second adjustable damping are connected in series and arranged in parallel with the balancing valve. The first control port is connected to the oil channel between the first adjustable damping and the second adjustable damping. The valve core of the first adjustable damping is linked to the valve core of the balancing valve so that the opening of the first adjustable damping changes with the return oil opening of the balancing valve.

[0012] According to the amplitude control system provided by the present application, the valve core of the balancing valve is connected to the valve core of the first adjustable damping.

[0013] According to a variable amplitude control system provided in the present application, it also includes a position detection device, which is used to detect the position information of the valve core of the balancing valve. The first adjustable damping is set as an electric proportional valve. The first adjustable damping and the position detection device are both connected to the control component of the variable amplitude control system. The control component adjusts the position of the valve core of the first adjustable damping based on the position information.

[0014] According to a variable amplitude control system provided in the present application, it also includes an instruction acquisition component, the second adjustable damping is set as an electric proportional valve, the instruction acquisition component and the second adjustable damping are both connected to the control component of the variable amplitude control system, the instruction acquisition component is used to obtain operating instructions, and the control component adjusts the opening of the second adjustable damping based on the operating instructions.

[0015] According to a variable amplitude control system provided by the present application, the second adjustable damper is provided as a hydraulically controlled valve whose opening is adjusted by control oil.

[0016] According to a variable amplitude control system provided by the present application, the second adjustable damper is configured as a manual valve whose opening is manually adjusted.

[0017] According to the amplitude control system provided by the present application, it also includes a first fixed damper, and the first adjustable damper, the second adjustable damper and the first fixed damper are sequentially connected in series and in parallel with the balancing valve.

[0018] According to a variable amplitude control system provided by the present application, it further includes a second fixed damper, and the control port corresponding to the second working position is connected to the oil port of the balancing valve connected to the actuator through the second fixed damper.

[0019] According to a variable amplitude control system provided by the present application, it also includes a third fixed damper, and the oil channel between the first adjustable damper and the second adjustable damper is connected to the control port corresponding to the first working position through the third fixed damper.

[0020] The present application also provides a working machine, comprising an actuator and the amplitude control system as described above.

[0021] The variable amplitude control system provided in the present application is connected to the actuator through a balancing valve, and by controlling the pressure difference between the first control port and the second control port, the oil of the actuator can be discharged and returned to perform a descending action, or the oil discharge of the actuator can be restricted to stop the descending action.

[0022] By connecting the first adjustable damper and the second adjustable damper in series and then setting them in parallel with the balancing valve, when it is necessary to descend, the second adjustable damper is controlled to open, and part of the oil of the actuator is discharged through the first adjustable damper and the second adjustable damper. Due to the pressure loss after flowing through the first adjustable damper, the pressure of the second control port is greater than the pressure of the first control port, and the opening of the balancing valve is increased, so that the oil of the actuator can be discharged through the balancing valve and returned, and the actuator performs the descending action.

[0023] By interlocking the valve core of the first adjustable damper with the valve core of the balancing valve, when the oil pressure fluctuation of the actuator increases, the pressure of the second control port increases, and the return oil opening of the balancing valve increases. At this time, the opening of the first adjustable damper also increases, causing the pressure of the first control port to increase accordingly, thereby reducing the pressure difference between the first and second control ports, and restoring the return oil opening of the balancing valve to its original state. Similarly, when the oil pressure fluctuation of the actuator decreases, the opening of the first adjustable damper decreases, which can also reduce the pressure difference between the first and second control ports, restoring the return oil opening of the balancing valve to its original state, and ensuring the stability of the return oil opening of the balancing valve.

[0024] With such a setting, the variable amplitude control system provided in the present application achieves the effect of adjusting the opening of the balancing valve through the cooperation of the first adjustable damping and the second adjustable damping. Through the linkage setting of the first adjustable damping and the balancing valve, the frequent changes in the flow of the balancing valve caused by pressure fluctuations are reduced, the stable descent of the actuator is ensured, and the problem of jitter is reduced.

[0025] The operating machine provided in the present application includes the luffing control system provided in the present application, and therefore also includes all the above-mentioned advantages of the luffing control system. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] In order to more clearly illustrate the technical solutions in this application or related technologies, the following briefly introduces the drawings required for use in the embodiments or related technical descriptions. Obviously, the drawings described below are some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0027] FIG1 is a schematic structural diagram of an amplitude control system provided in some embodiments of the present application.

[0028] FIG2 is a schematic structural diagram of a balancing valve in the related art.

[0029] Reference numerals:

[0030] 1. Balancing valve; 101. First control port; 102. Second control port; 103. First oil port; 104. Second oil port; 105. First elastic member; 2. Actuator; 3. First adjustable damper; 4. Second adjustable damper; 401. Third oil port; 402. Fourth oil port; 403. Second elastic member; 5. First fixed damper; 6. Second fixed damper; 7. Third fixed damper

[0031] 1', balancing valve; 2', actuator; 201', oil inlet chamber. DETAILED DESCRIPTION

[0032] To make the objectives, technical solutions, and advantages of this application more clear, the technical solutions of this application will be clearly and completely described below in conjunction with the accompanying drawings. Obviously, the embodiments described are only part of the embodiments of this application, not all of them. Based on the embodiments of this application, all other embodiments obtained by ordinary technicians in this field without making any creative efforts are within the scope of protection of this application.

[0033] The following describes the amplitude control system provided in the embodiment of the present application with reference to FIG1 .

[0034] Specifically, the luffing control system includes a balancing valve 1 , a first adjustable damper 3 and a second adjustable damper 4 .

[0035] The balancing valve 1 is connected to the actuator 2 and enables oil return from the actuator 2. Alternatively, the actuator 2 may be a cylinder, with the balancing valve 1 connected to the rodless chamber of the cylinder. During the descent, the oil in the rodless chamber of the cylinder is discharged through the balancing valve 1. Alternatively, the actuator 2 may be a hydraulic motor. During the descent, the oil discharged from the hydraulic motor is discharged through the balancing valve 1.

[0036] The balancing valve 1 includes a first control port 101 and a second control port 102, both of which are used to connect to control oil, enabling the control oil to drive the valve core of the balancing valve 1 to move, thereby adjusting the oil return opening of the balancing valve 1. The oil return opening of the balancing valve 1 is proportional to the difference between the oil pressure in the second control port 102 and the oil pressure in the first control port 101. That is, the greater the difference between the oil pressures in the second control port 102 and the first control port 101, the larger the oil return opening of the balancing valve 1, the faster the oil return speed of the actuator 2, and thus the faster the actuator 2 descends. When the oil pressure in the first control port 101 is greater than or equal to the oil pressure in the second control port 102, the oil return opening of the balancing valve 1 is zero.

[0037] Optionally, the balancing valve 1 further includes a first oil port 103, a second oil port 104, a first elastic member 105, and a valve core. The first oil port 103 is connected to the actuator 2, while the second oil port 104 can be selectively connected to the oil pump or oil tank of the working machine via a reversing valve. The first elastic member 105 is used to drive the valve core of the balancing valve 1 in a direction that reduces the oil return opening. When the oil pressure in the first control port 101 is greater than or equal to the oil pressure in the second control port 102, the valve core of the balancing valve 1 moves to the first operating position, establishing a one-way connection from the second oil port 104 to the first oil port 103, and blocking the connection from the first oil port 103 to the second oil port 104. The one-way connection from the second oil port 104 to the first oil port 103 allows oil from the oil pump to enter the actuator 2 through the balancing valve 1, driving the actuator 2 to ascend. The blocking of the connection from the first oil port 103 to the second oil port 104 restricts the discharge of oil from the actuator 2 through the balancing valve 1. When the sum of the oil pressure of the first control port 101 and the pressure generated by the first elastic member 105 is less than the oil pressure of the second control port 102, the valve core of the balancing valve 1 moves to the second working position, the first oil port 103 and the second oil port 104 are connected, and the actuator 2 can return oil through the balancing valve 1, so that the actuator 2 can perform the descending operation.

[0038] The first adjustable damper 3 and the second adjustable damper 4 are arranged in series and in parallel with the balancing valve 1. Specifically, the end of the first adjustable damper 3 away from the second adjustable damper 4 is connected to the first oil port 103, and the end of the second adjustable damper 4 away from the first adjustable damper 3 is connected to the second oil port 104. The first control port 101 is connected to the oil passage between the first adjustable damper 3 and the second adjustable damper 4. The valve core of the first adjustable damper 3 is arranged in linkage with the valve core of the balancing valve 1 so that the opening of the first adjustable damper 3 changes with the return oil opening of the balancing valve 1. Optionally, in order to make the amplitude control system run more smoothly, when the return oil opening of the balancing valve 1 is zero, the first adjustable damper 3 maintains a preset opening.

[0039] The principle of the luffing control system is described below with reference to Figure 1. For ease of explanation, an oil cylinder is used as an example, and the principle is the same for the actuator 2 configured as a hydraulic motor.

[0040] When the second adjustable damper 4 is fully closed, the pressure of the first control port 101 is equal to the pressure of the second control port 102, the valve core of the balancing valve 1 is in the first working position, the return oil opening of the balancing valve 1 is zero, the oil in the rodless chamber of the cylinder cannot return, and the cylinder will not produce a descending action.

[0041] When the cylinder needs to descend, the second adjustable damper 4 is controlled to open. At this time, part of the oil in the cylinder is discharged through the first adjustable damper 3 and the second adjustable damper 4 and returned to the oil. Because the oil generates pressure loss after flowing through the first adjustable damper 3, the pressure of the second control port 102 is greater than the pressure of the first control port 101. The valve core of the balancing valve 1 moves to the second working position, allowing the oil in the actuator 2 to be discharged through the balancing valve 1 and returned to the oil, and the cylinder performs the descending action. When the opening of the second adjustable damper 4 decreases, the pressure difference across the second adjustable damper 4 increases, causing the pressure of the first control port 101 to increase, thereby reducing the difference between the oil pressure of the second control port 102 and the oil pressure of the first control port 101, and then reducing the return oil opening of the balancing valve 1, slowing the descent speed of the cylinder. When the opening of the second adjustable damper 4 increases, the pressure difference at both ends of the second adjustable damper 4 decreases, so that the pressure of the first control port 101 decreases, thereby increasing the difference between the oil pressure of the second control port 102 and the oil pressure of the first control port 101, and then increasing the return oil opening of the balancing valve 1 and the descending speed of the cylinder.

[0042] When the oil pressure in the cylinder suddenly increases, the pressure in the second control port 102 increases, and the difference between the pressure in the second control port 102 and the pressure in the first control port 101 increases, causing the oil return opening of the balancing valve 1 to increase. Since the valve core of the first adjustable damper 3 is linked to the valve core of the balancing valve 1, the opening of the first adjustable damper 3 increases simultaneously, causing the pressure in the first control port 101 to increase accordingly, thereby reducing the pressure difference between the first control port 101 and the second control port 102, allowing the oil return opening of the balancing valve 1 to return to its original state. Similarly, when the oil pressure fluctuation in the cylinder decreases, the opening of the first adjustable damper 3 decreases, which can also reduce the pressure difference between the first control port 101 and the second control port 102, allowing the oil return opening of the balancing valve 1 to return to its original state, ensuring the stability of the oil return opening of the balancing valve 1.

[0043] With such a configuration, the variable amplitude control system provided in the embodiment of the present application achieves the effect of adjusting the opening of the balancing valve 1 through the cooperation of the first adjustable damping 3 and the second adjustable damping 4. By the linkage setting of the first adjustable damping 3 and the balancing valve 1, the frequent changes in the flow of the balancing valve 1 caused by pressure fluctuations are reduced, the stable descent of the actuator 2 is ensured, and the problem of jitter is reduced.

[0044] According to the inventors' understanding, related art also provides a solution for controlling the valve opening of the balancing valve 1 using an independent control oil source. This method requires separately drawing oil from a control oil pump to the control port of the balancing valve 1. However, for balancing valves 1 located at a higher position, the control oil pipe needs to be very long, which can easily cause faults such as response lag and jitter. In the variable amplitude control system provided in the embodiment of the present application, the control oil for the two control ports of the balancing valve 1 is both derived from the actuator 2, and the control oil travels a shorter path. This can solve the problem of pressure distortion and fluctuation caused by the influence of temperature and pipe length on the control oil pipe when the control oil pipe is too long during high-altitude operations.

[0045] In some embodiments provided herein, the valve core of the balancing valve 1 is connected to the valve core of the first adjustable damper 3. In this way, the linkage between the valve core of the first adjustable damper 3 and the valve core of the balancing valve 1 is simple and has better stability.

[0046] Optionally, the valve core of the balancing valve 1 and the valve core of the first adjustable damper 3 can be welded, threaded, or connected with fasteners. For example, the first end of the valve core of the balancing valve 1 extends through the valve body of the balancing valve 1, the first end of the valve core of the first adjustable damper 3 extends through the valve body of the first adjustable damper 3, and the first end of the valve core of the balancing valve 1 is connected to the first end of the valve core of the first adjustable damper 3. Alternatively, the valve core of the balancing valve 1 and the valve core of the first adjustable damper 3 are configured as an integral structure, and the valve body of the balancing valve 1 and the valve body of the first adjustable damper 3 are configured as an integral structure, wherein the valve core of the balancing valve 1 and the valve body of the balancing valve 1 are in sliding engagement with each other, and the valve core of the first adjustable damper 3 and the valve body of the first adjustable damper 3 are in sliding engagement with each other.

[0047] Of course, the linkage between the two is not limited to being achieved by connecting the valve core of the balancing valve 1 to the valve core of the first adjustable damper 3. For example, in other embodiments provided in the present application, the amplitude control system further includes a position detection device.

[0048] The position detection device is used to detect the position of the spool of the balancing valve 1 . For example, the spool of the balancing valve 1 is provided with a magnet. The position detection device can be configured as a magnetic sensor capable of detecting changes in a magnetic field. The magnetic sensor includes, but is not limited to, a Hall-effect sensor. The first adjustable damper 3 is configured as an electro-proportional valve. Both the first adjustable damper 3 and the position detection device are connected to a control component of the amplitude control system, which can be, but is not limited to, a controller and a processor. The control component adjusts the position of the spool of the first adjustable damper 3 based on the position information.

[0049] With such an arrangement, when the pressure of the actuator 2 fluctuates and causes the return oil opening of the balancing valve 1 to change, it is convenient to more accurately control the opening of the first adjustable damper 3, so that the pressure change amplitude of the first control port 101 is closer to the pressure change amplitude of the second control port 102, thereby reducing the change of the return oil opening of the balancing valve 1 and ensuring the stability of the balancing valve 1.

[0050] Specifically, when the oil pressure in the cylinder suddenly increases, the pressure in the second control port 102 increases, the difference between the pressure in the second control port 102 and the pressure in the first control port 101 increases, and the return oil opening of the balancing valve 1 increases. When the control component determines based on the position information that the valve core of the balancing valve 1 is moving in the direction of increasing the return oil opening, it controls the opening of the first adjustable damper 3 to increase, so that the pressure in the first control port 101 also increases accordingly, thereby reducing the difference between the pressures in the first control port 101 and the second control port 102, so that the return oil opening of the balancing valve 1 returns to its original state. Similarly, when the oil pressure in the cylinder suddenly decreases, the control component controls the opening of the first adjustable damper 3 to decrease, which can also reduce the pressure difference between the first control port 101 and the second control port 102, so that the return oil opening of the balancing valve 1 returns to its original state, ensuring the stability of the return oil opening of the balancing valve 1.

[0051] In some embodiments provided herein, the luffing control system further includes a command acquisition component. The second adjustable damper 4 is configured as an electro-proportional valve, and both the command acquisition component and the second adjustable damper 4 are connected to a control component of the luffing control system. The command acquisition component is used to acquire operating instructions. For example, the command acquisition component can be configured as an operating handle or an operating panel, and is used to acquire operating instructions input by an operator. Based on the operating instructions, the control component adjusts the opening of the second adjustable damper 4.

[0052] With this arrangement, the opening of the second adjustable damper 4 can be infinitely adjusted, thereby enabling precise adjustment of the opening over a wide range, thereby achieving precise adjustment and control of the descending movement of the actuator 2. In addition, the second adjustable damper 4 can be remotely controlled and program-controlled, providing convenience for automation and making the operation more intelligent.

[0053] Optionally, the second adjustable damper 4 includes a third oil port 401, a fourth oil port 402, a second elastic member 403, and an electric proportional assembly. The third oil port 401 is connected to the first adjustable damper 3, and the fourth oil port 402 is connected to the second oil port 104. The electric proportional assembly is used to drive the valve core of the second adjustable damper 4. When the valve core of the second adjustable damper 4 is in the first working position, the fourth oil port 402 is connected to the third oil port 401, and the third oil port 401 is blocked from connecting to the fourth oil port 402. When the valve core of the second adjustable damper 4 is in the second working position, the third oil port 401 and the fourth oil port 402 are connected. The second elastic member 403 is connected to the valve core of the second adjustable damper 4 and is used to drive the second adjustable damper 4 to move toward the first working position.

[0054] Of course, the second adjustable damper 4 is not limited to being an electric proportional valve. For example, in other embodiments provided herein, the second adjustable damper 4 is configured as a hydraulically controlled valve whose opening is adjusted by control oil. This configuration allows the second adjustable damper 4 to be low-cost, simple and reliable in structure, and fast in response.

[0055] Of course, the second adjustable damper 4 is not limited to being hydraulically controlled. For example, in other embodiments provided herein, the second adjustable damper 4 is configured as a manual valve with a manually adjustable opening. This configuration allows the operator to directly manually manipulate the second adjustable damper 4 to control the lowering movement of the actuator 2, thereby simplifying the control structure of the luffing control system and reducing costs.

[0056] In some embodiments provided herein, the luffing control system further includes a first fixed damper 5. The first adjustable damper 3, the second adjustable damper 4, and the first fixed damper 5 are sequentially connected in series and in parallel with the balancing valve 1. This arrangement allows the first fixed damper 5 to stabilize the flow and reduce the impact of oil pressure fluctuations on the return oil opening of the balancing valve 1.

[0057] In some embodiments provided herein, the luffing control system further includes a second fixed damper 6, through which the second control port 102 is connected to the oil port of the balancing valve 1 connected to the actuator 2. This configuration allows the second fixed damper 6 to stabilize the flow and reduce the impact of oil pressure fluctuations on the return oil opening of the balancing valve 1.

[0058] In some embodiments provided herein, the luffing control system further includes a third fixed damper 7, and the oil passage between the first adjustable damper 3 and the second adjustable damper 4 is connected to the first control port 101 via the third fixed damper 7. This configuration allows the third fixed damper 7 to stabilize the flow and reduce the impact of oil pressure fluctuations on the return oil opening of the balancing valve 1.

[0059] An operating machine is also provided in an embodiment of the present application.

[0060] Specifically, the working machine includes an actuator 2 and the above-mentioned luffing control system. The balancing valve 1 is connected to the actuator 2.

[0061] The operating machine includes a luffing control system and also includes all the above advantages of the luffing control system.

[0062] The actuator 2 may be a cylinder or a hydraulic motor.

[0063] The working machine includes but is not limited to a crane. For example, the crane can be a truck crane.

[0064] In the description of the embodiments of the present application, it should be noted that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating the orientation or positional relationship, are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing the embodiments of the present application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operate in a specific orientation, and therefore cannot be understood as limiting the embodiments of the present application. In addition, the terms "first", "second", and "third" are used for descriptive purposes only and cannot be understood as indicating or implying relative importance.

[0065] In the description of the embodiments of this application, it should be noted that, unless otherwise specified or limited, the terms "connected" and "connection" should be understood in a broad sense. For example, they can refer to fixed connections, detachable connections, or integral connections; they can refer to mechanical connections or electrical connections; they can refer to direct connections or indirect connections through an intermediate medium. Those skilled in the art will understand the specific meanings of the above terms in the embodiments of this application based on the specific circumstances.

[0066] In the description of this specification, the reference terms "one embodiment", "first aspect embodiment", "some embodiments", "example", "specific example", or "some examples" mean that the specific features, structures, materials or characteristics described in combination with the embodiment or example are included in at least one embodiment or example of the embodiments of the present application.

[0067] In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described can be combined in any suitable manner in any one or more embodiments or examples. In addition, those skilled in the art can combine and combine different embodiments or examples described in this specification, as well as features of different embodiments or examples, unless they are mutually inconsistent.

[0068] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present application, rather than to limit them. Although the present application has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or make equivalent replacements for some of the technical features therein. However, these modifications or replacements do not deviate the essence of the corresponding technical solutions from the spirit and scope of the technical solutions of the embodiments of the present application.

Claims

1. A variable amplitude control system comprising: A balancing valve (1) is used to connect an actuator (2) and enable the actuator (2) to return oil. The balancing valve (1) comprises a first control port (101) and a second control port (102). The oil return opening of the balancing valve (1) is proportional to the difference between the oil pressure of the second control port (102) and the oil pressure of the first control port (101). The second control port (102) is connected to the oil port of the balancing valve (1) connected to the actuator (2). The first adjustable damper (3) and the second adjustable damper (4) are connected in series and arranged in parallel with the balancing valve (1); the first control port (101) is connected to the oil passage between the first adjustable damper (3) and the second adjustable damper (4); the valve core of the first adjustable damper (3) is arranged in linkage with the valve core of the balancing valve (1), so that the opening of the first adjustable damper (3) changes with the return oil opening of the balancing valve (1).

2. The luffing control system according to claim 1, wherein: The valve core of the balancing valve (1) is connected to the valve core of the first adjustable damper (3).

3. The amplitude variation control system according to claim 1 further includes a position detection device, which is used to detect the position information of the valve core of the balancing valve (1). The first adjustable damping (3) is set as an electric proportional valve. The first adjustable damping (3) and the position detection device are both connected to the control component of the amplitude variation control system. The control component adjusts the position of the valve core of the first adjustable damping (3) based on the position information.

4. The amplitude control system according to claim 1 further includes an instruction acquisition component, the second adjustable damping (4) is set as an electric proportional valve, the instruction acquisition component and the second adjustable damping (4) are both connected to the control component of the amplitude control system, the instruction acquisition component is used to obtain operating instructions, and the control component adjusts the opening of the second adjustable damping (4) based on the operating instructions.

5. The luffing control system according to claim 1, wherein: The second adjustable damper (4) is configured as a hydraulically controlled valve whose opening is adjusted by control oil.

6. The luffing control system according to claim 1, wherein: The second adjustable damper (4) is configured as a manual valve with a manually adjustable opening.

7. The amplitude control system according to any one of claims 1 to 6, further comprising a first fixed damper (5), wherein the first adjustable damper (3), the second adjustable damper (4) and the first fixed damper (5) are sequentially connected in series and in parallel with the balancing valve (1).

8. The amplitude control system according to any one of claims 1 to 6, further comprising a second fixed damper (6), wherein the second control port (102) is connected to the oil port of the balancing valve (1) connected to the actuator (2) via the second fixed damper (6).

9. The luffing control system according to any one of claims 1 to 6, further comprising a third fixed damper (7), wherein the oil passage between the first adjustable damper (3) and the second adjustable damper (4) is connected to the first control port (101) via the third fixed damper (7).

10. A working machine, characterized in that: The invention comprises an actuator (2) and a variable amplitude control system according to any one of claims 1 to 9.

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