Integrated hydraulic mechanical control system

Abstract

The invention discloses an integrated hydraulic mechanical control system, and relates to the technical field of hydraulic mechanical control systems. An integrated hydraulic mechanical control system is composed of a reversing pressure regulating valve set, a prefill valve and an oil cylinder. The reversing pressure regulating valve group comprises an integrated valve block, a pressure regulating valve and the like, and all elements are integrated on the integrated valve block; all the valves are connected through oil ways, oil is controlled to flow to the plunger type cylinder and the return stroke oil cylinder, the prefill valve assists in action, the oil returns to the oil tank through the oil outlet of the main valve, and the whole body is of an integrated structure. By means of integrated design, the hydraulic control system achieves the comprehensive effects of being compact in structure, safe, reliable, accurate in control, capable of saving energy, efficient and convenient and fast to maintain, breaks through limitation of a traditional split type hydraulic control structure, and is suitable for various devices needing oil cylinder reciprocating motion control such as a press machine, an injection molding machine and a hydraulic machine tool. The method is especially suitable for scenes with high requirements for space, precision and energy saving performance.

Description

Technical Field

[0001] This invention relates to the field of hydraulic machinery control system technology, and specifically to an integrated hydraulic machinery control system. Background Technology

[0002] In the field of high-pressure, high-flow hydraulic components and hydraulic systems, the directional valve, as a core hydraulic component for precisely controlling the direction, flow, and pressure of high-pressure, high-flow hydraulic oil, directly determines the operating efficiency, stability, and load-bearing capacity of the high-pressure, high-flow hydraulic system, and plays a crucial role in the overall performance of the entire hydraulic machinery equipment.

[0003] Currently, in the practical application of high-pressure, high-flow hydraulic systems, the directional valves widely used in the industry mostly follow the split structure design concept of "pilot solenoid directional valve + main spool valve + independent valve block" to adapt to the demanding working conditions of high pressure and high flow. Specifically, in the workflow of a high-pressure, high-flow hydraulic system, the pilot solenoid directional valve first receives an external electrical signal, and then, with the help of a small flow of control oil within the system, overcomes the enormous resistance of the main spool valve core under high-pressure conditions, pushing the main spool valve core to move precisely. As the core control component of the high-pressure, high-flow hydraulic oil, the main spool valve can quickly change the direction of the high-pressure, high-flow main oil circuit after the valve core moves, thereby realizing key actions such as the extension and retraction of the cylinder and the start and stop of the actuator in the high-pressure, high-flow hydraulic system, ensuring that the equipment completes the operation according to the instructions.

[0004] Meanwhile, in order to meet the installation and connection requirements of high-pressure and high-flow hydraulic components, the matching independent valve block adopts a plate-type installation method, which not only provides a stable mounting carrier for core components such as pilot solenoid directional valves and main spool valves, but also undertakes the function of diverting and converging high-pressure and high-flow hydraulic oil, integrating the various scattered components into a complete functional unit that can adapt to high-pressure and high-flow working conditions, and ensuring the stable operation of the hydraulic system. However, this traditional split structure has significant technical shortcomings when adapting to high-pressure, high-flow hydraulic components and systems, making it difficult to fully meet the stringent performance requirements of the system under high-pressure, high-flow conditions. The specific technical shortcomings are as follows: (1) Installation and space issues: Each main spool valve body requires at least 4 screws for fixing. When combined with an independent valve block, the overall volume is huge, occupying a lot of space inside the equipment and increasing the difficulty of the hydraulic system layout. At the same time, the split structure design leads to an increase in the overall weight of the equipment, which is not conducive to lightweight design.

[0005] (2) High risk of leakage: Since there are multiple connection surfaces between the main slide valve body and the independent valve block, sealing is required through sealing components. After long-term use, the aging of the sealing components or uneven installation stress can easily lead to external oil leakage, affecting the safety of equipment operation and environmental cleanliness.

[0006] (3) High processing and maintenance costs: The main slide valve has high precision processing requirements, which leads to increased manufacturing costs; and the structure of the control part is dispersed, and troubleshooting requires disassembling multiple components, which increases the workload and maintenance difficulty of maintenance personnel.

[0007] (4) Poor system stability: It has strict requirements for oil cleanliness. Once impurities are mixed in the oil, the valve core of the main slide valve is easily stuck, resulting in an increased failure rate. At the same time, the pressure loss of the split structure is large and the energy waste is obvious.

[0008] Therefore, the inventors believe that developing an integrated hydraulic control solution that is compact, has low leakage risk, is easy to maintain, and is energy-efficient is the key to solving the above-mentioned defects of traditional directional valves and is also a technical problem that urgently needs to be solved in this field.

[0009] The information disclosed in this background section is intended only to enhance the understanding of the overall background of the invention and should not be construed as an admission or in any way implying that the information constitutes prior art known to those skilled in the art. Summary of the Invention

[0010] To address the aforementioned technical problems, embodiments of the present invention provide an integrated hydraulic machinery control system to solve the problems mentioned in the background section.

[0011] This invention provides the following technical solution: an integrated hydraulic mechanical control system, comprising: a reversing pressure regulating valve group, a filling valve, and a cylinder; the reversing pressure regulating valve group comprises an integrated valve block, a pressure regulating valve, a two-way cartridge reversing valve, a solenoid reversing valve, a main valve inlet, a main valve return port, a check valve, and a solenoid ball valve; The oil pump outlet is connected to the main valve inlet via a pipeline, and the main valve return port is connected to the oil tank via a pipeline. The main valve inlet is connected to the fourth directional valve, the first directional valve, the second directional valve, the second solenoid directional valve, and the second relief valve via an oil circuit. The second electromagnetic reversing valve is connected to the filling valve control interface and the main valve outlet, respectively. The filling valve control interface is connected to the first filling valve and the second filling valve. The second directional valve is connected to the third solenoid directional valve and the first check valve respectively. The third solenoid directional valve is connected to the main valve outlet. The first check valve is connected to the first plunger cylinder port and the second ball valve respectively. The second ball valve is connected to the main valve outlet. The first directional valve is connected to the fourth solenoid directional valve and the second check valve respectively. The fourth solenoid directional valve is connected to the main valve outlet. The second check valve is connected to the second plunger cylinder port and the third ball valve respectively. The third ball valve is connected to the main valve outlet. The first plunger cylinder interface is connected to the first plunger cylinder and the first filling valve respectively, and the second plunger cylinder interface is connected to the second plunger cylinder and the second filling valve respectively; The fourth directional valve is connected to the third check valve and the fifth solenoid directional valve respectively, and the fifth solenoid directional valve is connected to the oil outlet of the main valve. The third check valve is connected to the third directional valve. The third directional valve is connected to the fourth ball valve, the return cylinder interface, and the safety valve. The fourth ball valve and the safety valve are both connected to the main valve outlet. The return cylinder interface is connected to the return cylinder.

[0012] Preferably, the pressure regulating valve includes a return pressure regulating valve, a slow-down pressure regulating valve, a high-pressure pressure regulating valve, and a low-pressure pressure regulating valve; the solenoid directional valve includes a fast-down solenoid directional valve, a first solenoid directional valve, a third solenoid directional valve, a fourth solenoid directional valve, and a fifth solenoid directional valve; the solenoid ball valve includes a first solenoid ball valve, a second ball valve, a third ball valve, and a fourth ball valve.

[0013] Preferably, the two-way cartridge directional valve includes a first directional valve, a second directional valve, a third directional valve, and a fourth directional valve; the one-way valve includes a first one-way valve, a second one-way valve, and a third one-way valve.

[0014] Preferably, the reversing pressure regulating valve group further includes a first relief valve, which is connected in series in the oil circuit between the third reversing valve and the main valve outlet.

[0015] Preferably, the reversing pressure regulating valve assembly is an integral valve assembly, wherein the pressure regulating valve, two-way cartridge reversing valve, solenoid reversing valve, check valve and solenoid ball valve are all integrated into the integrated valve block.

[0016] The integrated hydraulic machinery control system provided in this embodiment of the invention has the following beneficial effects: (1) This invention integrates core components such as pressure regulating valve, two-way cartridge directional valve, and electromagnetic directional valve into one unit through an integrated valve block design, eliminating the connection space and screw fixing structure of traditional independent valve blocks, and greatly reducing the overall volume and weight; at the same time, the internal oil circuit replaces the external pipeline, reducing structural redundancy, significantly simplifying the hydraulic system layout, and better adapting to the design requirements of space-constrained and lightweight equipment, fundamentally solving the problems of complicated installation and large space occupation.

[0017] (2) Through integrated design, the present invention integrates all valve components into the same integrated valve block, which greatly reduces the external connection surface between the valve body and the valve block and the amount of seals used. This design reduces the risk of oil leakage caused by seal failure from the root, which not only improves the safety of equipment operation, but also avoids the pollution of the environment by oil leakage, and meets the requirements of clean production.

[0018] (3) By simplifying the structure of the core components, the present invention replaces the traditional main slide valve with a two-way cartridge reversing valve, eliminating the precision machining process of the main slide valve and reducing manufacturing costs. At the same time, the integrated structure makes the valve group layout clear and the fault points concentrated. Fault diagnosis does not require disassembling multiple scattered components, reducing the workload and maintenance difficulty of maintenance personnel, shortening equipment downtime, and reducing subsequent maintenance costs.

[0019] (4) By optimizing the structure and flow channel design, the two-way cartridge reversing valve and integrated oil circuit adopted in this invention are less sensitive to oil impurities, reducing valve core jamming and other faults, and improving system stability. At the same time, the integrated oil circuit shortens the oil flow path and reduces pressure loss. Combined with load-sensitive pressure control (pressure is increased only when the action is performed and low pressure is maintained when idle), energy waste is reduced and energy utilization efficiency is improved. In addition, the optimized design of the return cylinder combined with the auxiliary function of the filling valve further improves the stability and energy saving of the system operation. Attached Figure Description

[0020] Figure 1 This is a schematic diagram of the integrated hydraulic mechanical control system of the present invention. Detailed Implementation

[0021] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0022] See Figure 1 To address the problems mentioned in the background section, this invention provides an integrated hydraulic machinery control system to solve the aforementioned technical problems. The technical solution is as follows: An integrated hydraulic mechanical control system includes: a reversing pressure regulating valve group, a filling valve, and a cylinder; the reversing pressure regulating valve group includes an integrated valve block 33, a pressure regulating valve, a two-way cartridge reversing valve, a solenoid reversing valve, a main valve inlet 1, a main valve return port 2, a check valve, and a solenoid ball valve. The oil pump's outlet is connected to the main valve's inlet 1 via a pipeline, and the main valve's return port 2 is connected to the oil tank via a pipeline; wherein, the oil pump and the oil tank are in... Figure 1 Not shown separately in the text; The main valve inlet 1 is connected to the fourth directional valve 36, the first directional valve 27, the second directional valve 29, the second solenoid directional valve 13, and the second relief valve 11 via an oil circuit. The second electromagnetic reversing valve 13 is connected to the filling valve control interface 15 and the main valve oil outlet respectively. The filling valve control interface 15 is connected to the first filling valve 19 and the second filling valve 20. The second reversing valve 29 is connected to the third solenoid reversing valve 24 and the first check valve 14 respectively. The third solenoid reversing valve 24 is connected to the main valve outlet. The first check valve 14 is connected to the first plunger cylinder interface 16 and the second ball valve 12 respectively. The second ball valve 12 is connected to the main valve outlet. The first reversing valve 27 is connected to the fourth solenoid reversing valve 26 and the second check valve 25 respectively. The fourth solenoid reversing valve 26 is connected to the main valve outlet. The second check valve 25 is connected to the second plunger cylinder interface 17 and the third ball valve 28 respectively. The third ball valve 28 is connected to the main valve outlet. The first plunger cylinder interface 16 is connected to the first plunger cylinder 18 and the first filling valve 19 respectively, and the second plunger cylinder interface 17 is connected to the second plunger cylinder 21 and the second filling valve 20 respectively. The fourth directional valve 36 is connected to the third check valve 35 and the fifth solenoid directional valve 34 respectively, and the fifth solenoid directional valve 34 is connected to the oil outlet of the main valve. The third check valve 35 is connected to the third directional valve 31. The third directional valve 31 is connected to the fourth ball valve 30, the return cylinder interface 23 and the safety valve 32 respectively. The fourth ball valve 30 and the safety valve 32 are both connected to the main valve outlet. The return cylinder interface 23 is connected to the return cylinder 22.

[0023] It should be noted that in this integrated hydraulic mechanical control system, the main valve outlet is the key oil flow interface between the reversing pressure regulating valve group and external actuators (such as piston cylinders and return cylinders) and auxiliary components (such as filling valves). It is a bidirectional oil interaction channel. Through bidirectional oil flow, in conjunction with the coordinated action of various valves, the system achieves pressure control, direction switching and energy recovery. It is a key interface to ensure the efficient operation of the hydraulic cycle.

[0024] In this embodiment, the pressure regulating valve includes a return pressure regulating valve 3, a slow-down pressure regulating valve 6, a high-pressure pressure regulating valve 8, and a low-pressure pressure regulating valve 10; the electromagnetic directional valve includes a fast-down electromagnetic directional valve 4, a first electromagnetic directional valve 9, a third electromagnetic directional valve 24, a fourth electromagnetic directional valve 26, and a fifth electromagnetic directional valve 34; the electromagnetic ball valve includes a first electromagnetic ball valve 5, a second ball valve 12, a third ball valve 28, and a fourth ball valve 30.

[0025] In this embodiment, the two-way cartridge reversing valve includes a first reversing valve 27, a second reversing valve 29, a third reversing valve 31, and a fourth reversing valve 36; the one-way valve includes a first one-way valve 14, a second one-way valve 25, and a third one-way valve 35.

[0026] In this embodiment, the reversing pressure regulating valve group further includes a first relief valve 7, which is connected in series in the oil passage between the third reversing valve 31 and the main valve outlet.

[0027] In this embodiment, the reversing pressure regulating valve group is an integral valve group, and the pressure regulating valve, two-way cartridge reversing valve, solenoid reversing valve, check valve and solenoid ball valve are all integrated in the integrated valve block 33.

[0028] The operation method of an integrated hydraulic mechanical control system provided by this invention is as follows: (1) Initial state: The motor drives the oil pump to start, all solenoid directional valves have no electrical signal, the directional valves are in the closed state, and the system has no action.

[0029] (2) Rapid suppression phase: The first solenoid directional valve 9 is energized at the cross end with high pressure, and the system pressure increases; When the third solenoid directional valve 24 and the fourth solenoid directional valve 26 are energized, the oil enters the first plunger cylinder 18 through the first check valve 14 and enters the second plunger cylinder 21 through the second check valve 25. When the fourth ball valve 30 and the fast-down solenoid directional valve 4 are energized, the oil in the return cylinder 22 flows into the main valve outlet through the third directional valve 31 and the first overflow valve 7, and the plunger cylinder realizes the fast-down pressing action.

[0030] (3) Slow down suppression phase: When the plunger cylinder approaches the workpiece, the fast-down solenoid directional valve 4 is de-energized, the first solenoid ball valve 5 is energized, and the plunger cylinder switches to the slow-down mode to precisely press the workpiece. Once the set pressure is reached, the compression action is complete.

[0031] (4) Pre-depressurization and return phase: The second ball valve 12 and the third ball valve 28 are energized, and the pressure in the piston cylinder is pre-released. When the parallel ends of the second solenoid directional valve 13 and the first solenoid directional valve 9 are energized at low pressure, the filling valve opens. When the fifth solenoid directional valve 34 is energized, the oil flows through the fourth directional valve 36, the third check valve 35, and the third directional valve 31 into the return cylinder 22, driving the return cylinder to return.

[0032] (5) Reset phase: After the return cylinder 22 reaches the upper limit, all valves are de-energized and the system completes one working cycle.

[0033] Through the above process, the return speed is increased by utilizing the small-diameter design of the return cylinder 22, realizing pilot control of medium and large flow rates, and ensuring safe, energy-saving and efficient operation of the equipment.

[0034] The integrated hydraulic mechanical control system provided in this invention achieves a comprehensive effect of compact structure, safety and reliability, precise control, energy efficiency and convenient maintenance through integrated design. It breaks through the limitations of traditional split hydraulic control structure and is suitable for various equipment that require reciprocating motion control of hydraulic cylinders, such as presses, injection molding machines, and hydraulic machine tools. It is especially suitable for scenarios with high requirements for space, precision and energy saving.

[0035] The device embodiments described above are merely illustrative. The units described as separate components may or may not be physically separate, and the components shown as units may or may not be physical units; they may be located in one place or distributed across multiple network units. Some or all of the modules can be selected to achieve the purpose of this embodiment according to actual needs.

[0036] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "setting," "connection," "fixing," "screw connection," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; 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; they can refer to the internal communication of components or the interaction between components. Unless otherwise explicitly limited, those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0037] It is understood that those skilled in the art can make equivalent substitutions or modifications to the technical solutions and concepts of this invention, and all such substitutions or modifications should fall within the protection scope of the appended claims.

Claims

1. An integrated hydraulic mechanical control system, characterized in that, include: The reversing pressure regulating valve assembly includes a filling valve and a hydraulic cylinder; the reversing pressure regulating valve assembly includes an integrated valve block, a pressure regulating valve, a two-way cartridge reversing valve, a solenoid reversing valve, a main valve inlet, a main valve return port, a check valve, and a solenoid ball valve. The oil pump outlet is connected to the main valve inlet via a pipeline, and the main valve return port is connected to the oil tank via a pipeline; the main valve inlet is connected to the fourth directional valve, the first directional valve, the second directional valve, the second solenoid directional valve, and the second relief valve via an oil circuit. The second electromagnetic reversing valve is connected to the filling valve control interface and the main valve outlet, respectively. The filling valve control interface is connected to the first filling valve and the second filling valve. The second directional valve is connected to the third solenoid directional valve and the first check valve respectively. The third solenoid directional valve is connected to the main valve outlet. The first check valve is connected to the first plunger cylinder port and the second ball valve respectively. The second ball valve is connected to the main valve outlet. The first directional valve is connected to the fourth solenoid directional valve and the second check valve respectively. The fourth solenoid directional valve is connected to the main valve outlet. The second check valve is connected to the second plunger cylinder port and the third ball valve respectively. The third ball valve is connected to the main valve outlet. The first plunger cylinder interface is connected to the first plunger cylinder and the first filling valve respectively, and the second plunger cylinder interface is connected to the second plunger cylinder and the second filling valve respectively; The fourth directional valve is connected to the third check valve and the fifth solenoid directional valve respectively, and the fifth solenoid directional valve is connected to the oil outlet of the main valve. The third check valve is connected to the third directional valve. The third directional valve is connected to the fourth ball valve, the return cylinder interface, and the safety valve. The fourth ball valve and the safety valve are both connected to the main valve outlet. The return cylinder interface is connected to the return cylinder.

2. The integrated hydraulic mechanical control system according to claim 1, characterized in that, The pressure regulating valve includes a return pressure regulating valve, a slow-down pressure regulating valve, a high-pressure pressure regulating valve, and a low-pressure pressure regulating valve; the solenoid directional valve includes a fast-down solenoid directional valve, a first solenoid directional valve, a third solenoid directional valve, a fourth solenoid directional valve, and a fifth solenoid directional valve; the solenoid ball valve includes a first solenoid ball valve, a second ball valve, a third ball valve, and a fourth ball valve.

3. The integrated hydraulic mechanical control system according to claim 1, characterized in that, The two-way cartridge directional valve includes a first directional valve, a second directional valve, a third directional valve, and a fourth directional valve; the one-way valve includes a first one-way valve, a second one-way valve, and a third one-way valve.

4. The integrated hydraulic mechanical control system according to claim 1, characterized in that, The reversing pressure regulating valve group also includes a first relief valve, which is connected in series in the oil circuit between the third reversing valve and the main valve outlet.

5. The integrated hydraulic mechanical control system according to claim 1, characterized in that, The reversing pressure regulating valve group is an integral valve group, in which the pressure regulating valve, two-way cartridge reversing valve, solenoid reversing valve, check valve and solenoid ball valve are all integrated into the integrated valve block.

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