Amplitude control system and working machine

Abstract

The present application relates to the field of hydraulic systems, and provides a variable amplitude control system and a working machine. The variable amplitude control system comprises: a balance valve connected to an actuator, the balance valve comprising a first control port and a second control port, the oil return opening degree of the balance valve being proportional to the difference between the oil pressure of the second control port and the oil pressure of the first control port, and the oil port of the balance valve being connected to the second control port; a first adjustable damping and a second adjustable damping, which are connected in series and arranged in parallel with the balance valve, the oil passage between the first adjustable damping and the second adjustable damping being connected to the first control port, and the valve core of the first adjustable damping being arranged in linkage with the valve core of the balance valve, so that the opening degree of the first adjustable damping changes with the oil return opening degree of the balance valve. Through the cooperation of the first adjustable damping and the second adjustable damping, the opening degree of the balance valve is adjusted, and through the linkage arrangement of the first adjustable damping and the balance valve, the frequent changes in flow caused by pressure fluctuations to the balance valve are reduced, and the problem of jitter is reduced.

Description

Technical Field

[0001] This invention relates to the field of hydraulic system technology, and in particular to a variable amplitude control system and a working machine. Background Technology

[0002] In the field of aerial work, aerial work machinery often requires actuators such as hydraulic cylinders or hydraulic motors to complete lifting and lowering actions, and these actuators usually require balance valves to control the descent speed.

[0003] refer to Figure 2 As shown, in related technologies, the balance valve 1' is typically controlled by an externally controlled pilot oil. For example, in the descending state, the return port of the actuator is connected to the oil tank through the balance valve 1', and the pilot port of the balance valve 1' is connected to the inlet chamber 201' of the actuator 2'. When the pressurized oil supplied by the oil pump flows to the inlet chamber 201' of the actuator 2', some of the pressurized oil enters the pilot port of the balance valve 1', driving the balance valve 1' to open, allowing the pressurized oil at the return port of the actuator 2' to flow out through the balance valve 1', and the actuator 2' performs the descending action.

[0004] The inventors discovered that during the use of the above-mentioned balancing valve, when pressure fluctuations occur in the oil inlet chamber of the actuator, these pressure fluctuations are transmitted to the balancing valve, causing frequent changes in the opening of the balancing valve, which in turn causes the actuator to vibrate. Summary of the Invention

[0005] This invention provides a variable amplitude control system and working machinery to solve the defect in related technologies where the balance valve causes vibration of the actuator, thereby achieving the effect of stabilizing and regulating the balance valve.

[0006] This invention provides a variable amplitude control system, comprising:

[0007] A balancing valve is used to connect to an actuator and enable the actuator to return oil. The balancing valve includes a first control port and a second control port. The oil return opening degree of the balancing valve is 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 is connected to the oil port of the balancing valve that connects to the actuator.

[0008] A first adjustable damper and a second adjustable damper are connected in series and arranged in parallel with the balance valve. The first control port is connected to the oil passage between the first adjustable damper and the second adjustable damper. The valve core of the first adjustable damper is linked with the valve core of the balance valve so that the opening degree of the first adjustable damper changes with the oil return opening degree of the balance valve.

[0009] According to a variable amplitude control system provided by the present invention, the valve core of the balance valve is connected to the valve core of the first adjustable damping valve.

[0010] According to the present invention, a variable amplitude control system further includes a position detection device for detecting the position information of the valve core of the balance valve. The first adjustable damper is configured as an electro-proportional valve. Both the first adjustable damper and the position detection device are 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 damper based on the position information.

[0011] According to the present invention, a variable amplitude control system further includes an instruction acquisition component, wherein the second adjustable damper is configured as an electro-proportional valve, and both the instruction acquisition component and the second adjustable damper are connected to the control component of the variable amplitude control system. The instruction acquisition component is used to acquire an operation instruction, and the control component adjusts the opening degree of the second adjustable damper based on the operation instruction.

[0012] According to a variable amplitude control system provided by the present invention, the second adjustable damping is configured as a hydraulically controlled valve whose opening is adjusted by control oil.

[0013] According to a variable amplitude control system provided by the present invention, the second adjustable damping is configured as a manual valve for manually adjusting the opening degree.

[0014] According to the variable amplitude control system provided by the present invention, a first fixed damper is further included, wherein the first adjustable damper, the second adjustable damper and the first fixed damper are connected in series and in parallel with the balance valve.

[0015] According to the variable amplitude control system provided by the present invention, a second fixed damper is further included, and the control port corresponding to the second working position is connected to the oil port of the actuator through the second fixed damper and the balance valve.

[0016] According to the variable amplitude control system provided by the present invention, a third fixed damper is further included, and the oil passage 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.

[0017] The present invention also provides a working machine, including an actuator and a variable amplitude control system as described above.

[0018] The variable amplitude control system provided by the present invention is connected to the actuator through a balance 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 the descent action, or the oil discharge of the actuator can be restricted to stop the descent action.

[0019] The first and second adjustable dampers are connected in series and then in parallel with the balance valve. When descent is required, the second adjustable damper is opened, and part of the oil in the actuator is discharged through the first and second adjustable dampers. Due to the pressure loss after flowing through the first adjustable damper, the pressure at the second control port is greater than the pressure at the first control port. The opening of the balance valve increases so that the oil in the actuator can be discharged through the balance valve and return to the source, and the actuator performs the descent action.

[0020] By linking the valve core of the first adjustable damping valve with the valve core of the balancing valve, when the oil pressure fluctuation of the actuator increases, the pressure at the second control port increases, and the return oil opening of the balancing valve increases. At the same time, the opening of the first adjustable damping valve also increases, causing the pressure at the first control port to increase accordingly. This reduces the pressure difference between the first and second control ports, allowing the return oil opening of the balancing valve to return to its original state. Similarly, when the oil pressure fluctuation of the actuator decreases, the opening of the first adjustable damping valve decreases, which also reduces the pressure difference between the first and second control ports, allowing the return oil opening of the balancing valve to return to its original state and ensuring the stability of the return oil opening of the balancing valve.

[0021] With this configuration, the amplitude control system provided by the present invention achieves the effect of adjusting the opening of the balance valve through the cooperation of the first adjustable damper and the second adjustable damper. By linking the first adjustable damper with the balance valve, the frequent changes in flow caused by pressure fluctuations to the balance valve are reduced, ensuring the stable descent of the actuator and reducing the problem of jitter.

[0022] The working machinery provided by the present invention incorporates the luffing control system provided by the present invention, and therefore simultaneously incorporates all the above-mentioned advantages of the luffing control system. Attached Figure Description

[0023] To more clearly illustrate the technical solutions in this invention or related technologies, the accompanying drawings used in the description of the embodiments or related technologies will be briefly introduced below. Obviously, the accompanying drawings described below are some embodiments of this invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0024] Figure 1 This is a schematic diagram of the amplitude control system provided in some embodiments of the present invention.

[0025] Figure 1 Figure labels in the diagram:

[0026] 1. Balance valve; 101. First control port; 102. Second control port; 103. First oil port; 104. Second oil port; 105. First elastic element; 2. Actuating element; 3. First adjustable damper; 4. Second adjustable damper; 401. Third oil port; 402. Fourth oil port; 403. Second elastic element; 5. First fixed damper; 6. Second fixed damper; 7. Third fixed damper.

[0027] Figure 2 This is a schematic diagram of the structure of a balance valve in related technologies.

[0028] Figure 2 Figure labels in the diagram:

[0029] 1' Balance valve; 2' Actuator; 201' Oil inlet chamber. Detailed Implementation

[0030] To make the objectives, technical solutions, and advantages of this invention clearer, the technical solutions of this invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this invention. All other embodiments obtained by those skilled in the art based on the embodiments of this invention without creative effort are within the scope of protection of this invention.

[0031] The following is combined Figure 1 The amplitude control system provided in the embodiments of the present invention is described.

[0032] Specifically, the variable amplitude control system includes a balance valve 1, a first adjustable damper 3, and a second adjustable damper 4.

[0033] The balance valve 1 is used to connect to the actuator 2 and enables the actuator 2 to return oil. Optionally, the actuator 2 can be a hydraulic cylinder, and the balance valve 1 is connected to the rodless chamber of the hydraulic cylinder. During the descent, the oil in the rodless chamber of the hydraulic cylinder is discharged through the balance valve 1. Of course, the actuator 2 can also be a hydraulic motor, and during the descent, the oil discharged by the hydraulic motor is discharged through the balance valve 1.

[0034] The balancing valve 1 includes a first control port 101 and a second control port 102. Both the first control port 101 and the second control port 102 are connected to control oil so that the control oil can drive the valve core of the balancing valve 1 to move, thereby adjusting the return oil opening of the balancing valve 1. The return oil opening of the balancing valve 1 is proportional to the difference between the oil pressure at the second control port 102 and the oil pressure at the first control port 101. That is, the greater the difference between the oil pressure at the second control port 102 and the oil pressure at the first control port 101, the greater the return oil opening of the balancing valve 1, the faster the return oil speed of the actuator 2, and thus the faster the downward movement performed by the actuator 2. When the oil pressure at the first control port 101 is greater than or equal to the oil pressure at the second control port 102, the return oil opening of the balancing valve 1 is zero.

[0035] Optionally, the balance valve 1 further includes a first port 103, a second port 104, a first elastic element 105, and a valve core. The first port 103 is used to connect to the actuator 2, and the second port 104 can be selectively connected to the oil pump or oil tank of the working machinery via a reversing valve. The first elastic element 105 is used to drive the valve core of the balance valve 1 to move in the direction of reducing the return oil opening. When the oil pressure at the first control port 101 is greater than or equal to the oil pressure at the second control port 102, the valve core of the balance valve 1 moves to the first working position, and the second port 104 is unidirectionally connected to the first port 103, while the first port 103 is closed to the second port 104. The unidirectional connection between the second port 104 and the first port 103 allows the oil from the oil pump to enter the actuator 2 through the balance valve 1, driving the actuator 2 to perform an upward operation. The closure of the first port 103 to the second port 104 restricts the discharge of oil from the actuator 2 through the balance valve 1. When the sum of the oil pressure at the first control port 101 and the pressure generated by the first elastic element 105 is less than the oil pressure at the second control port 102, the valve core of the balance 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 balance valve 1 so that the actuator 2 can perform the descent operation.

[0036] The first adjustable damper 3 and the second adjustable damper 4 are connected in series and in parallel with the balance 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 linked to the valve core of the balance valve 1 so that the opening of the first adjustable damper 3 changes with the return oil opening of the balance valve 1. Optionally, in order to make the luffing control system operate more smoothly, the first adjustable damper 3 maintains a preset opening when the return oil opening of the balance valve 1 is zero.

[0037] The following is combined Figure 1The principle of the variable amplitude control system will be introduced. For ease of explanation, a hydraulic cylinder will be used as an example. The principle is the same for actuator 2, which is set as a hydraulic motor.

[0038] When the second adjustable damper 4 is fully closed, the pressure of the first control port 101 and the pressure of the second control port 102 are equal. The valve core of the balance valve 1 is in the first working position, the oil return opening of the balance valve 1 is zero, the oil in the rodless chamber of the oil cylinder cannot return, and the oil cylinder will not produce a descending action.

[0039] When the cylinder needs to descend, the second adjustable damper 4 is opened. At this time, part of the oil in the cylinder is discharged and returned through the first adjustable damper 3 and the second adjustable damper 4. Due to the pressure loss after the oil flows through the first adjustable damper 3, the pressure at the second control port 102 is greater than the pressure at the first control port 101. The valve core of the balance valve 1 moves to the second working position so that the oil in the actuator 2 can be discharged and returned through the balance valve 1, and the cylinder performs the descent action. When the opening of the second adjustable damper 4 decreases, the pressure difference across the second adjustable damper 4 increases, which increases the pressure at the first control port 101. This reduces the difference between the oil pressure at the second control port 102 and the oil pressure at the first control port 101, thereby reducing the return oil opening of the balance valve 1 and slowing down the descent speed of the cylinder. When the opening of the second adjustable damper 4 increases, the pressure difference between the two ends of the second adjustable damper 4 decreases, which reduces the pressure at the first control port 101. This increases the difference between the oil pressure at the second control port 102 and the oil pressure at the first control port 101, thereby increasing the return oil opening of the balance valve 1 and increasing the descent speed of the cylinder.

[0040] When the hydraulic pressure in the cylinder suddenly increases, the pressure at the second control port 102 also increases. The pressure difference between the second control port 102 and the first control port 101 increases, causing the return oil opening of the balance valve 1 to increase. Since the valve core of the first adjustable damper 3 is linked to the valve core of the balance valve 1, the opening of the first adjustable damper 3 also increases simultaneously, causing the pressure at the first control port 101 to increase accordingly. This reduces the pressure difference between the first control port 101 and the second control port 102, allowing the return oil opening of the balance valve 1 to return to its original state. Similarly, when the hydraulic pressure fluctuation in the cylinder decreases, the opening of the first adjustable damper 3 decreases, which also reduces the pressure difference between the first control port 101 and the second control port 102, allowing the return oil opening of the balance valve 1 to return to its original state and ensuring the stability of the return oil opening of the balance valve 1.

[0041] With this configuration, the amplitude control system provided in this embodiment of the invention achieves the effect of adjusting the opening of the balance valve 1 through the cooperation of the first adjustable damper 3 and the second adjustable damper 4. By linking the first adjustable damper 3 and the balance valve 1, the frequent changes in flow caused by pressure fluctuations to the balance valve 1 are reduced, ensuring the stable descent of the actuator 2 and reducing the problem of jitter.

[0042] According to the inventors, related technologies also include schemes that use an independent control oil source to control the valve opening of the balance valve 1. This method requires a separate oil supply from the control oil pump to the control port of the balance valve 1. However, for the balance valve 1, which is positioned high, the control oil pipe needs to be very long, which can easily cause response lag and vibration. In the variable amplitude control system provided in this embodiment of the invention, the control oil for both control ports of the balance valve 1 comes from the actuator 2, resulting in a shorter control oil path. This solves the problem of pressure distortion and fluctuation caused by temperature and pipe length when the control oil pipe is too long during high-altitude operations.

[0043] In some embodiments provided by the present invention, the valve core of the balance valve 1 is connected to the valve core of the first adjustable damper 3. This configuration simplifies the linkage between the valve core of the first adjustable damper 3 and the valve core of the balance valve 1, and improves stability.

[0044] Optionally, the valve core of the balance valve 1 and the valve core of the first adjustable damper 3 can be welded, threaded, or fastened together. For example, the first end of the valve core of the balance valve 1 extends out of the valve body of the balance valve 1, and the first end of the valve core of the first adjustable damper 3 extends out of the valve body of the first adjustable damper 3, with the first end of the valve core of the balance valve 1 connected to the first end of the valve core of the first adjustable damper 3. Alternatively, the valve core of the balance valve 1 and the valve core of the first adjustable damper 3 can be configured as an integral structure, and the valve body of the balance valve 1 and the valve body of the first adjustable damper 3 can be configured as an integral structure, wherein the valve core of the balance valve 1 slides in conjunction with the valve body of the balance valve 1, and the valve core of the first adjustable damper 3 slides in conjunction with the valve body of the first adjustable damper 3.

[0045] Of course, the linkage between the two is not limited to the form of connecting the valve core of the balance valve 1 with the valve core of the first adjustable damper 3. For example, in other embodiments provided by the present invention, the amplitude control system also includes a position detection device.

[0046] The position detection device is used to detect the position information of the valve core of the balance valve 1. For example, if a magnet is provided on the valve core of the balance valve 1, the position detection device can be configured as a magnetic sensor capable of detecting changes in the magnetic field. Magnetic sensors include, but are not limited to, Hall effect sensors. 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 the control component of the amplitude modulation control system. The control component can be, but is not limited to, a controller and a processor. Based on the position information, the control component adjusts the position of the valve core of the first adjustable damper 3.

[0047] With this configuration, when the pressure fluctuation of the actuator 2 causes a change in the return oil opening of the balance valve 1, it is easier to control the opening of the first adjustable damper 3 more accurately, 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 in the return oil opening of the balance valve 1 and ensuring the stability of the balance valve 1.

[0048] Specifically, when the hydraulic pressure in the cylinder suddenly increases, the pressure at the second control port 102 increases, and the pressure difference between the second control port 102 and the first control port 101 increases. This causes the return oil opening of the balance valve 1 to increase. When the control component determines, based on position information, that the valve core of the balance 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. This causes the pressure at 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, so that the return oil opening of the balance valve 1 returns to its original state. Similarly, when the hydraulic pressure in the cylinder suddenly decreases, the control component controls the opening of the first adjustable damper 3 to decrease, which also reduces the pressure difference between the first control port 101 and the second control port 102, so that the return oil opening of the balance valve 1 returns to its original state, ensuring the stability of the return oil opening of the balance valve 1.

[0049] In some embodiments provided by this invention, 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 the control component of the luffing control system. The command acquisition component is used to acquire operating commands; for example, the command acquisition component can be configured as an operating handle or an operating panel. The command acquisition component is used to acquire operating commands inserted by the operator. Based on the operating commands, the control component adjusts the opening degree of the second adjustable damper 4.

[0050] With this configuration, the opening of the second adjustable damper 4 can be steplessly adjusted, allowing for precise adjustment of the opening over a wide range, thus achieving precise adjustment and control of the descent motion of the actuator 2. Furthermore, it enables remote and program-controlled operation of the second adjustable damper 4, facilitating automation and enhancing the level of operational intelligence.

[0051] Optionally, the second adjustable damper 4 includes a third port 401, a fourth port 402, a second elastic element 403, and an electro-proportional assembly. The third port 401 is connected to the first adjustable damper 3, and the fourth port 402 is connected to the second port 104. The electro-proportional assembly is used to drive the valve core of the second adjustable damper 4 to move. When the valve core of the second adjustable damper 4 is in the first working position, the connection between the fourth port 402 and the third port 401 is open, and the connection between the third port 401 and the fourth port 402 is closed. When the valve core of the second adjustable damper 4 is in the second working position, the connection between the third port 401 and the fourth port 402 is open. The second elastic element 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 towards the first working position.

[0052] Of course, the second adjustable damper 4 is not limited to being an electro-proportional valve. For example, in other embodiments provided by the present invention, the second adjustable damper 4 is configured as a hydraulically controlled valve whose opening is adjusted by control oil. With this configuration, the second adjustable damper 4 is inexpensive, has a simple and reliable structure, and a fast response speed.

[0053] Of course, the second adjustable damper 4 is not limited to being hydraulically controlled. For example, in other embodiments provided by the present invention, the second adjustable damper 4 is configured as a manual valve with manually adjustable opening. This configuration allows the operator to directly and manually manipulate the second adjustable damper 4 to control the descent action of the actuator 2, resulting in a simple and cost-effective control structure for the amplitude-changing control system.

[0054] In some embodiments provided by the present invention, the amplitude-variable control system further includes a first fixed damper 5, a first adjustable damper 3, a second adjustable damper 4, and the first fixed damper 5 connected in series and in parallel with the balance valve 1. With this configuration, the first fixed damper 5 can stabilize the flow and reduce the impact of oil pressure fluctuations on the return oil opening of the balance valve 1.

[0055] In some embodiments provided by the present invention, the luffing control system further includes a second fixed damper 6, and the second control port 102 is connected to the oil port of the actuator 2 via the second fixed damper 6 and the balance valve 1. With this configuration, the second fixed damper 6 can stabilize the flow and reduce the impact of oil pressure fluctuations on the return oil opening of the balance valve 1.

[0056] In some embodiments of the present invention, 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 through the third fixed damper 7. With this configuration, the third fixed damper 7 can stabilize the flow and reduce the impact of oil pressure fluctuations on the return oil opening of the balance valve 1.

[0057] This invention also provides a working machine.

[0058] Specifically, the working machinery includes an actuator 2 and a luffing control system as described above. The balance valve 1 is connected to the actuator 2.

[0059] The operating machinery includes a luffing control system, and therefore also includes all the advantages of a luffing control system mentioned above.

[0060] Among them, the actuator 2 can be a hydraulic cylinder or a hydraulic motor.

[0061] Operating machinery includes, but is not limited to, cranes. For example, a crane could be a truck crane.

[0062] In the description of the embodiments of the present invention, it should be noted that the terms "center," "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "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 the embodiments of the present 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 the embodiments of the present invention. In addition, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0063] In the description of the embodiments of the present invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "connected" and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of the present invention based on the specific circumstances.

[0064] In the description of this specification, references to terms such as "an embodiment," "first aspect embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example that is included in at least one embodiment or example of the present invention.

[0065] In this specification, the illustrative expressions of the terms used do not necessarily refer to the same embodiments or examples. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of those different embodiments or examples, without contradiction.

[0066] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

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

2. The variable amplitude control system according to claim 1, characterized in that, The valve core of the balance valve (1) is connected to the valve core of the first adjustable damper (3).

3. The variable amplitude control system according to claim 1, characterized in that, It also includes a position detection device, which is used to detect the position information of the valve core of the balance valve (1). The first adjustable damper (3) is set as an electro-proportional valve. The first adjustable damper (3) and the position detection device are both connected to the control component of the amplitude control system. The control component adjusts the position of the valve core of the first adjustable damper (3) based on the position information.

4. The variable amplitude control system according to claim 1, characterized in that, It also includes an instruction acquisition component, the second adjustable damper (4) is configured as an electro-proportional valve, the instruction acquisition component and the second adjustable damper (4) are both connected to the control component of the amplitude control system, the instruction acquisition component is used to acquire operation instructions, and the control component adjusts the opening of the second adjustable damper (4) based on the operation instructions.

5. The variable amplitude control system according to claim 1, characterized in that, The second adjustable damper (4) is configured as a hydraulic control valve whose opening is adjusted by control oil.

6. The variable amplitude control system according to claim 1, characterized in that, The second adjustable damper (4) is set as a manual valve for manually adjusting the opening degree.

7. The variable amplitude control system according to any one of claims 1-6, characterized in that, It also includes a first fixed damper (5), the first adjustable damper (3), the second adjustable damper (4) and the first fixed damper (5) are connected in series and in parallel with the balance valve (1).

8. The variable amplitude control system according to any one of claims 1-6, characterized in that, It also includes a second fixed damper (6), and the second control port (102) is connected to the oil port of the actuator (2) through the second fixed damper (6) and the balance valve (1).

9. The variable amplitude control system according to any one of claims 1-6, characterized in that, It also 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) through the third fixed damper (7).

10. A type of operating machinery, characterized in that, It includes the actuator (2) and the variable amplitude control system as described in any one of claims 1-9.

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