An implement synchronization hydraulic system based on dual synchronized diverter valves

Abstract

The application discloses a kind of based on double synchronous shunt valve's machine tool synchronous hydraulic system, including first synchronous shunt valve group and second synchronous shunt valve group;First synchronous shunt valve group and second synchronous shunt valve group are connected by reversing valve hydraulic power unit;The A oil port and B oil port of first synchronous shunt valve group are connected the rod cavity of two machine tool oil cylinders respectively;The A oil port and B oil port of second synchronous shunt valve group are connected the rodless cavity of two machine tool oil cylinders respectively;The first synchronous shunt valve group and second synchronous shunt valve group are under the action of internal compensation valve core, when the load pressure of two machine tool oil cylinders changes, maintain the flow ratio of A oil port and B oil port in the set range, when no pressure oil is introduced, two machine tool oil cylinders are locked;The application controls left and right machine tool oil cylinder big and small cavity by double valve parallel connection, realizes the synchronization of full stroke and solves the left and right machine tool oil cylinder string oil phenomenon in shutdown state.

Description

Technical Field

[0001] This invention belongs to the field of hydraulic control technology, specifically relating to a synchronous hydraulic system and control method for machinery based on dual synchronous flow dividers. Background Technology

[0002] In construction machinery, it is often necessary for the left and right hydraulic cylinders to operate synchronously to ensure the horizontal lifting and lowering of the implements. Existing hydraulic systems mostly use gear pumps in conjunction with ordinary multi-way valves for oil supply. However, due to the complexity of different working conditions, the forces on the left and right implements are often different (i.e., load asymmetry), resulting in inconsistent load pressures on the left and right hydraulic cylinders.

[0003] In existing technologies, if oil is supplied directly through a multi-way valve, according to fluid dynamics principles, the oil tends to flow towards the side with less load, causing asynchrony between the left and right implements. Furthermore, when the vehicle stops, because the hydraulic cylinder lines of the left and right implements are connected, applying a load to one side will cause the other side to move in the opposite direction, i.e., oil leakage. Adding an additional balance valve can solve the synchronization problem, but it cannot solve the oil leakage problem, and other valve structures are required, resulting in high system cost and large size. Summary of the Invention

[0004] This invention provides a machine tool synchronization hydraulic system based on a dual-synchronization diverter valve. By controlling the large and small chambers of the left and right machine tool cylinders in parallel with dual valves, the system achieves full-stroke synchronization and solves the problem of oil leakage between the left and right machine tool cylinders when the machine is stopped.

[0005] To achieve the above objectives, the technical solution adopted by the present invention is as follows:

[0006] The first aspect of the present invention provides a synchronous hydraulic system for machinery based on dual synchronous flow dividers, including a first synchronous flow divider valve group and a second synchronous flow divider valve group; the first synchronous flow divider valve group and the second synchronous flow divider valve group are connected to a hydraulic power unit through a reversing valve;

[0007] The A and B ports of the first synchronous flow divider valve group are connected to the rod chambers of the two tool cylinders, respectively; the A and B ports of the second synchronous flow divider valve group are connected to the rodless chambers of the two tool cylinders, respectively; under the action of the internal compensation valve core, the first and second synchronous flow divider valve groups maintain the flow ratio of the A and B ports within the set range when the load pressure of the two tool cylinders changes, and lock the two tool cylinders when no pressure oil is introduced.

[0008] Furthermore, the first and second synchronous flow divider valve groups can maintain a flow ratio of 1:1 between port A and port B.

[0009] Furthermore, the internal compensation valve cores of the first and second synchronous flow divider valve groups each include a first compensation valve and a second compensation valve connected in series.

[0010] The pressure before and after the first compensating valve acts on both sides of the valve core. When the pressure difference between the pressure before and after the valve is less than the threshold, the first compensating valve returns to the normally closed state under the action of the spring to lock the two machine cylinders; otherwise, the first compensating valve is in the open state.

[0011] The second compensation valve automatically adjusts the valve opening to balance the flow rates of port A and port B by sensing the load pressure difference between port A and port B.

[0012] Furthermore, the P port of the first and second synchronous flow divider valve groups is connected to the directional valve via an oil circuit; the P port, the first compensation valve, and the second compensation valve are connected sequentially via oil circuits; the second compensation valve is connected to the A port and the B port via an oil circuit.

[0013] Furthermore, the first compensation valve includes a first working position and a normal position; when the first compensation valve is in the normal position, the oil circuit is interrupted.

[0014] When the first compensating valve is in the first working position, the opening of the first compensating valve is changed by compressing the spring based on the pressure difference between the upstream and downstream pressures, and the flow rates of port A and port B are adjusted simultaneously. The calculation formula is as follows:

[0015]

[0016] In the formula, q is the flow rate after passing through the first compensation valve. For flow coefficient; The opening area of ​​the first compensation valve; This is the pressure difference between the pressure before and after the valve. This refers to the density of the hydraulic oil.

[0017] Furthermore, the P port is connected to the first control port of the first compensation valve through the first damping hole. The pressure oil in the first control port of the first compensation valve is used to drive the first compensation valve to switch to the first working position. The oil outlet of the first compensation valve is connected to the second control port of the first compensation valve through the second damping hole. The pressure oil in the second control port of the first compensation valve and the elastic force of the spring are used to drive the first compensation valve to switch to the normal position.

[0018] Furthermore, the second compensation valve includes a first working position, a normal position, and a second working position. When the load pressure of port A is equal to that of port B, the second compensation valve is in the normal position and directly connects the first compensation valve to ports A and B. When the load pressure of port A is greater than that of port B, the second compensation valve is in the first working position and automatically adjusts the valve opening connected to port B according to the load pressure difference between ports A and B. When the second compensation valve is in the second working position, it automatically adjusts the valve opening connected to port A according to the load pressure difference between ports A and B.

[0019] Furthermore, the first oil inlet of the second compensation valve is connected to the first control port of the second compensation valve through the fourth damping hole. The pressure oil in the first control port of the second compensation valve is used to drive the second compensation valve to switch to the first working position. The first oil inlet of the second compensation valve is connected to the A oil port accordingly.

[0020] The second oil inlet of the second compensation valve is connected to the second control port of the second compensation valve through the third damping hole. The pressure oil in the second control port of the second compensation valve is used to drive the second compensation valve to switch to the second working position. The second oil inlet of the second compensation valve is connected to the B oil port accordingly.

[0021] The second compensation valve is equipped with springs on both sides. When no pressure oil is introduced, the springs drive the second compensation valve to return to its normal position.

[0022] Furthermore, a first check valve and a second check valve are connected in parallel on both sides of the oil circuit connecting the first and second compensating valves; the input end of the first check valve is connected to port A through the oil circuit, and the input end of the second check valve is connected to port B through the oil circuit; the output ends of the first and second check valves are connected to port P through the oil circuit; the pressure oil provided by the hydraulic power unit enters the tool cylinder through the first and second compensating valves, and the return oil from the tool cylinder returns to the oil tank through the first and second check valves.

[0023] Furthermore, the reversing valve controls the switching of fluid flow direction and the opening and closing of oil circuits in the first and second synchronous flow divider valve groups.

[0024] Furthermore, the hydraulic power unit is connected in sequence to a pilot oil source valve and a pilot valve; the pilot valve is used to drive the directional valve to operate.

[0025] A second aspect of the present invention provides an engineering vehicle, including a tool and a tool synchronous hydraulic system, wherein the tool is equipped with two hydraulic cylinders that move synchronously; the tool synchronous hydraulic system drives the two hydraulic cylinders of the tool to move.

[0026] A second aspect of the present invention provides a working device, including a tool and a tool synchronous hydraulic system, wherein the tool is equipped with two hydraulic cylinders that move synchronously; the tool synchronous hydraulic system drives the two hydraulic cylinders of the tool to move.

[0027] Compared with the prior art, the beneficial effects of the present invention are as follows:

[0028] This invention uses two sets of synchronous flow-dividing valves to connect to the rod-side and rodless-side chambers of two machine tool cylinders respectively, achieving proportional flow distribution control in both the extension and retraction directions of the cylinders. Combined with the dynamic differential pressure compensation capability of the internal compensation valve core, when the load pressure on the two cylinders deviates (uneven load condition), the valve core can adjust the valve opening in real time to offset the effect of differential pressure, stably maintain the output flow ratio of ports A and B, and effectively suppress the synchronization error caused by uneven load.

[0029] When the hydraulic system stops supplying oil, the power source fails, or the pipeline loses pressure, this invention can simultaneously lock the rod-side and rodless-side chambers of two cylinders. The bidirectional locking can completely avoid the risks of cylinder movement, tool slippage, or load drop caused by single-chamber pressure loss. It is especially suitable for tools with vertical loads, high-altitude operations, or tools that need to be held stationary for a long time. At the same time, the locking function is integrated into the valve group, eliminating the need for additional bidirectional hydraulic locking components, thus improving safety without increasing system complexity. Attached Figure Description

[0030] Figure 1 This is a structural diagram of the synchronous hydraulic system for machinery provided in Embodiment 1 of the present invention;

[0031] Figure 2 This is a structural diagram of the first compensation valve and the second compensation valve provided in Embodiment 1 of the present invention;

[0032] In the diagram, 1 is a gear pump, 2 is a reversing valve, 3 is a pilot valve, 4 is a pilot oil source valve, 5 is a first synchronous flow divider valve, 6 is a second synchronous flow divider valve, 7 is a tool cylinder, 8 is a first compensation valve, 9 is a second compensation valve, 10 is a first check valve, 11 is a second check valve, 12 is a first damping orifice, 13 is a second damping orifice, 14 is a third damping orifice, and 15 is a fourth damping orifice. Detailed Implementation

[0033] The present invention will be further described below with reference to the accompanying drawings. The following embodiments are only used to more clearly illustrate the technical solution of the present invention, and should not be used to limit the scope of protection of the present invention.

[0034] Example 1

[0035] like Figure 1 As shown, this embodiment provides a machine tool synchronous hydraulic system based on dual synchronous flow divider valves, including a gear pump 1, a reversing valve 2, a pilot valve 3, a pilot oil source valve 4, a first synchronous flow divider valve 5, and a second synchronous flow divider valve 6; the gear pump 1 and the oil tank are combined to form a hydraulic power unit;

[0036] The hydraulic power unit is connected in sequence to the pilot oil source valve 4 and the pilot valve 3; the pilot valve 3 is used to drive the directional valve 2 to operate; the first synchronous flow divider valve group 5 and the second synchronous flow divider valve group 6 are connected to the hydraulic power unit through the directional valve; the directional valve controls the switching of fluid flow direction and the opening and closing of the oil circuit of the first synchronous flow divider valve group 5 and the second synchronous flow divider valve group 6.

[0037] The A and B ports of the first synchronous flow divider valve group 5 are respectively connected to the rod chambers of the two tool cylinders 7; the A and B ports of the second synchronous flow divider valve group 6 are respectively connected to the rodless chambers of the two tool cylinders 7; the P port of the first synchronous flow divider valve group 5 and the second synchronous flow divider valve group 6 are connected to the reversing valve 2 through an oil circuit.

[0038] The first synchronous flow divider valve group 5 and the second synchronous flow divider valve group 6 can maintain the flow ratio of port A and port B within a set range when the load pressure of the two tool cylinders changes, and lock the two tool cylinders when no pressure oil is introduced; it can be further optimized to: the first synchronous flow divider valve group 5 and the second synchronous flow divider valve group 6 can maintain the flow ratio of port A and port B at 1:1.

[0039] like Figure 2 As shown, the first synchronous flow divider valve group 5 and the second synchronous flow divider valve group 6 have the same structure, both including a first compensating valve 8, a second compensating valve 9, a first check valve 10, a second check valve 11, a first damping orifice 12, a second damping orifice 13, a third damping orifice 14, and a fourth damping orifice 15. Among them, the first damping orifice 12, the second damping orifice 13, the third damping orifice 14, and the fourth damping orifice 15 all serve a voltage stabilizing function.

[0040] The left side of the first compensation valve 8 is the pressure at port P before the valve core, and the right side of the first compensation valve 8 is the pressure compensation structure after the valve core. Since the internal openings of oil passages A and B are set to be the same, the flow rates at ports A and B output by the compensation valve core 8 are the same. When the pressure difference between the pressure before and after the valve is less than the threshold, the first compensation valve 8 returns to the normally closed state under the action of the spring to lock the two tool cylinders. Otherwise, the first compensation valve 8 is in the open state.

[0041] In this embodiment, the adjustment process of the first compensation valve is as follows: the first compensation valve 8 includes a first working position and a normal position; when the first compensation valve is in the normal position, the oil circuit is interrupted;

[0042] When the first compensating valve 8 is in the first working position, the opening of the first compensating valve is changed by compressing the spring based on the pressure difference between the upstream and downstream pressures, and the flow rates of port A and port B are adjusted simultaneously. The calculation formula is as follows:

[0043]

[0044] In the formula, q is the flow rate after passing through the first compensation valve. For flow coefficient; The opening area of ​​the first compensation valve; This is the pressure difference between the pressure before and after the valve. This refers to the density of the hydraulic oil.

[0045] The second compensation valve 9 automatically adjusts its opening to balance the flow rates at ports A and B by sensing the load pressure difference between ports A and B; specifically including:

[0046] The second compensation valve 9 includes a first working position, a normal position, and a second working position. When the load pressure of port A is equal to that of port B, the second compensation valve 9 is in the normal position and directly connects the first compensation valve to ports A and B. When the load pressure of port A is greater than that of port B, the second compensation valve 9 is in the first working position and automatically adjusts the opening of the valve connected to port B according to the load pressure difference between ports A and B. When the second compensation valve 9 is in the second working position, it automatically adjusts the opening of the valve connected to port A according to the load pressure difference between ports A and B.

[0047] The internal structural connection relationship between the first synchronous flow divider valve group 5 and the second synchronous flow divider valve group 6 is as follows:

[0048] Port P, the first compensating valve 8, and the second compensating valve 9 are connected sequentially via an oil circuit; the second compensating valve 9 is connected to port A and port B via an oil circuit; a first check valve 10 and a second check valve 11 are connected in parallel on both sides of the oil circuit connecting the first compensating valve 8 and the second compensating valve 9; the input end of the first check valve 10 is connected to port A via an oil circuit, and the input end of the second check valve 11 is connected to port B via an oil circuit; the output ends of the first check valve 10 and the second check valve 11 are connected to port P via an oil circuit; the pressure oil provided by the hydraulic power unit enters the tool cylinder 7 through the first compensating valve 8 and the second compensating valve 9, and the return oil from the tool cylinder 7 returns to the oil tank via the first check valve 10 and the second check valve 11.

[0049] The P port is connected to the first control port of the first compensation valve 8 (the left side position of the first compensation valve in this embodiment) through the first damping hole 12. The pressure oil in the first control port of the first compensation valve 8 is used to drive the first compensation valve to switch to the first working position. The oil outlet of the first compensation valve 8 is connected to the second control port of the first compensation valve 8 (the right side position of the first compensation valve in this embodiment) through the second damping hole 13. The pressure oil in the second control port of the first compensation valve 8 and the elastic force of the spring are used to drive the first compensation valve 8 to switch to the normal position.

[0050] The first oil inlet of the second compensation valve 9 is connected to the first control port of the second compensation valve (the left side position of the second compensation valve in this embodiment) through the fourth damping hole 15. The pressure oil in the first control port of the second compensation valve 9 is used to drive the second compensation valve 9 to switch to the first working position. The first oil inlet of the second compensation valve 9 is connected to the A oil port.

[0051] The second oil inlet of the second compensation valve 9 is connected to the second control port of the second compensation valve (the right side position of the second compensation valve in this embodiment) through the third damping hole 14. The pressure oil in the second control port of the second compensation valve 9 is used to drive the second compensation valve 9 to switch to the second working position. The second oil inlet of the second compensation valve 9 is connected to the B oil port.

[0052] The second compensation valve 9 is equipped with springs on both sides. When no pressure oil is introduced, the springs drive the second compensation valve 9 to return to its normal position.

[0053] In the cylinder extension mode (tool lifting): the reversing valve 2 controls the fluid flow direction switching of the first synchronous flow divider valve group 5 and the second synchronous flow divider valve group 6. The pressurized oil passes through the A port and B port of the second synchronous flow divider valve group 6 to the rodless chambers of the two tool cylinders 7 respectively, ensuring that the flow rate entering the rodless chambers of the left and right tool cylinders is equal, and ensuring that the tool is lifted horizontally; the oil in the rod chambers of the two tool cylinders 7 returns to the oil tank through the first check valve 10 and the second check valve 11 of the first synchronous flow divider valve group 5.

[0054] In the cylinder retraction mode (tool descent): the reversing valve 2 controls the fluid flow direction switching of the first synchronous flow divider valve group 5 and the second synchronous flow divider valve group 6. The pressurized oil passes through the A and B ports of the first synchronous flow divider valve group 5 to the rod chambers of the two tool cylinders 7 respectively, ensuring that the flow rate entering the rod chambers of the left and right tool cylinders is equal, and ensuring that the tool descends horizontally; the oil in the rodless chambers of the two tool cylinders 7 returns to the oil tank through the first check valve 10 and the second check valve 11 of the second synchronous flow divider valve group 6.

[0055] When no pressure oil is introduced into the synchronous diverter valve, the first synchronous diverter valve group 5 and the second synchronous diverter valve group 6 switch to the non-working position. The first compensation valve 8 inside is in the normal position and interrupts the oil circuit. The oil circuit between ports A and B is cut off, and the oil in the left and right tool cylinders 7 cannot be interconnected, thus preventing the occurrence of oil leakage between the left and right tool cylinders.

[0056] The flow regulation process of port A and port B of the first synchronous flow divider valve group 5 and the second synchronous flow divider valve group 6 is as follows:

[0057] Pressure oil enters the first control port of the first compensation valve 8 and drives the first compensation valve to switch to the first working position. After the first compensation valve 8 is in the conducting state, pressure oil enters the second compensation valve 9. The second compensation valve 9 maintains the flow ratio of port A and port B at 1:1.

[0058] When the external loads at ports A and B are different, if port A has a high load and port B has a low load, the pressure on the left side of the second compensating valve 9 will be greater than the pressure on the right side. The valve core will move to the right, and the second compensating valve 9 will enter its first working position. At this time, the oil passage on the low-pressure side, i.e., the port B passage, will be throttled inside the valve core, increasing the hydraulic resistance. The oil passage on the high-pressure side, i.e., the port A passage, will remain unchanged in size. This ensures that the output flow rates at ports A and B are consistent, meaning that the flow rates obtained on both sides of the machine are the same, rather than the flow rate on the side with a lower load being greater than the flow rate on the side with a higher load. This ensures that the actions on both sides of the machine are synchronized. Similarly, if the load at port B is high and the load at port A is low, the pressure on the right side of the second compensating valve 9 will be greater than the pressure on the left side. The valve core will move to the left, and the second compensating valve 9 will enter its second working position. The low-pressure side port A will be throttled inside the valve core, increasing the hydraulic resistance. The port B passage on the high-pressure side will remain unchanged in size, and the output flow rates at ports A and B will be the same.

[0059] Example 2

[0060] This embodiment provides an engineering vehicle, including a tool and the tool synchronous hydraulic system described in Embodiment 1. The tool is equipped with two hydraulic cylinders that move synchronously; the tool synchronous hydraulic system drives the two hydraulic cylinders of the tool to move.

[0061] Example 3

[0062] This embodiment provides a working device, including a tool and the tool synchronous hydraulic system described in Embodiment 1. The tool is equipped with two hydraulic cylinders that move synchronously; the tool synchronous hydraulic system drives the two hydraulic cylinders of the tool to move.

[0063] The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. A synchronous hydraulic system for machinery based on dual synchronous flow dividers, characterized in that, It includes a first synchronous flow divider valve group and a second synchronous flow divider valve group; the first synchronous flow divider valve group and the second synchronous flow divider valve group are connected to the hydraulic power unit through a reversing valve; The A and B ports of the first synchronous flow divider valve group are connected to the rod chambers of the two tool cylinders, respectively; the A and B ports of the second synchronous flow divider valve group are connected to the rodless chambers of the two tool cylinders, respectively; under the action of the internal compensation valve core, the first and second synchronous flow divider valve groups maintain the flow ratio of the A and B ports within the set range when the load pressure of the two tool cylinders changes, and lock the two tool cylinders when no pressure oil is introduced.

2. The synchronous hydraulic system for machinery according to claim 1, characterized in that, The first and second synchronous flow divider valve groups can maintain a flow ratio of 1:1 between port A and port B.

3. The synchronous hydraulic system for machinery according to claim 1, characterized in that, The first and second synchronous flow divider valve groups each have a first compensation valve and a second compensation valve connected in series. The pressure before and after the first compensating valve acts on both sides of the valve core. When the pressure difference between the pressure before and after the valve is less than the threshold, the first compensating valve returns to the normally closed state under the action of the spring to lock the two machine cylinders; otherwise, the first compensating valve is in the open state. The second compensation valve automatically adjusts the valve opening to balance the flow rates of port A and port B by sensing the load pressure difference between port A and port B.

4. The synchronized hydraulic system for machinery according to claim 3, characterized in that, The P port of the first and second synchronous flow divider valve groups is connected to the directional valve via an oil circuit; the P port, the first compensation valve, and the second compensation valve are connected sequentially via an oil circuit; the second compensation valve is connected to the A port and the B port via an oil circuit.

5. The synchronized hydraulic system for machinery according to claim 4, characterized in that, The first compensation valve includes a first working position and a normal position; when the first compensation valve is in the normal position, the oil circuit is interrupted. When the first compensating valve is in the first working position, the opening of the first compensating valve is changed by compressing the spring based on the pressure difference between the upstream and downstream pressures, and the flow rates of port A and port B are adjusted simultaneously. The calculation formula is as follows: ； In the formula, q is the flow rate after passing through the first compensation valve. For flow coefficient; The opening area of ​​the first compensation valve; This is the pressure difference between the pressure before and after the valve. This refers to the density of the hydraulic oil.

6. The synchronized hydraulic system for machinery according to claim 5, characterized in that, The P port is connected to the first control port of the first compensation valve through the first damping hole. The pressure oil in the first control port of the first compensation valve is used to drive the first compensation valve to switch to the first working position. The oil outlet of the first compensation valve is connected to the second control port of the first compensation valve through the second damping hole. The pressure oil in the second control port of the first compensation valve and the elastic force of the spring are used to drive the first compensation valve to switch to the normal position.

7. The synchronized hydraulic system for machinery according to claim 4, characterized in that, The second compensation valve includes a first working position, a normal position, and a second working position. When the load pressure of port A is equal to that of port B, the second compensation valve is in the normal position and directly connects the first compensation valve to ports A and B. When the load pressure of port A is greater than that of port B, the second compensation valve is in the first working position and automatically adjusts the opening of the valve connected to port B according to the load pressure difference between ports A and B. When the second compensation valve is in the second working position, it automatically adjusts the opening of the valve connected to port A according to the load pressure difference between ports A and B.

8. The synchronized hydraulic system for machinery according to claim 7, characterized in that, The first oil inlet of the second compensation valve is connected to the first control port of the second compensation valve through the fourth damping hole. The pressure oil in the first control port of the second compensation valve is used to drive the second compensation valve to switch to the first working position. The first oil inlet of the second compensation valve is connected to the A oil port. The second oil inlet of the second compensation valve is connected to the second control port of the second compensation valve through the third damping hole. The pressure oil in the second control port of the second compensation valve is used to drive the second compensation valve to switch to the second working position. The second oil inlet of the second compensation valve is connected to the B oil port accordingly. The second compensation valve is equipped with springs on both sides. When no pressure oil is introduced, the springs drive the second compensation valve to return to its normal position.

9. The synchronous hydraulic system for machinery according to claim 4, characterized in that, The first and second compensating valves are connected in parallel on both sides of the oil circuit with a first check valve and a second check valve; the input end of the first check valve is connected to port A through the oil circuit, and the input end of the second check valve is connected to port B through the oil circuit; the output ends of the first and second check valves are connected to port P through the oil circuit; the pressure oil provided by the hydraulic power unit enters the tool cylinder through the first and second compensating valves, and the return oil from the tool cylinder returns to the oil tank through the first and second check valves.

10. The synchronous hydraulic system for machinery according to claim 1, characterized in that, The reversing valve controls the switching of fluid flow direction and the opening and closing of oil circuits in the first and second synchronous flow divider valve groups.

11. The synchronized hydraulic system for machinery according to claim 1 or 12, characterized in that, The hydraulic power unit is connected in sequence to the pilot oil source valve and the pilot valve; the pilot valve is used to drive the directional valve to operate.

12. An engineering vehicle, characterized in that, The invention includes a tool and a tool synchronous hydraulic system as described in any one of claims 1 to 11, wherein the tool is equipped with two hydraulic cylinders that move synchronously; the tool synchronous hydraulic system drives the two hydraulic cylinders of the tool to move.

13. A working device, comprising a tool and a tool synchronous hydraulic system as described in any one of claims 1 to 11, wherein the tool is equipped with two hydraulic cylinders that move synchronously; the tool synchronous hydraulic system drives the two hydraulic cylinders of the tool to move.

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