Hydraulic pipe bending control system

Abstract

The utility model discloses a hydraulic elbow control system, which relates to the technical field of hydraulic control systems and comprises a pilot proportional pressure reducing valve, an electromagnetic directional valve and a throttle valve which are sequentially connected and communicated with an oil cavity. Each auxiliary pushing oil cylinder is provided with a rod cavity and a plug cavity, each rod cavity is connected and communicated with the corresponding electromagnetic reversing valve, each plug cavity can be connected and communicated with the corresponding throttling valve through an oil way, and each oil way is provided with an electromagnetic ball valve. According to the hydraulic pipe bending control system, pressure adjustment is convenient, and cost can be reduced.

Description

Technical Field

[0001] The utility model relates to the technical field of hydraulic control systems, in particular to a hydraulic pipe bending control system. Background Art

[0002] The pipe bending machine is mainly based on the principle of vector pipe bending and is mainly divided into three parts: mechanical part, hydraulic part, and control system. It uses microcomputer control to complete any spatial three-dimensional pipe shape required by the user. It is an important processing equipment for modern bending and shaping. With the development of modern manufacturing industry, the requirements for the performance of pipe bending machines are becoming higher and higher, requiring greater breakthroughs in adaptability, efficiency and precision. As a result, the number of molds in the mechanical part continues to increase, and the volume accounts for an increasingly larger proportion. In order to keep the overall volume of the hydraulic pipe bender unchanged, how to reduce costs has become an urgent problem that needs to be solved. Utility Model Content

[0003] The purpose of the utility model is to provide a hydraulic pipe bending control system to solve the problems existing in the above-mentioned prior art, facilitate pressure regulation, and reduce costs.

[0004] To achieve the above purpose, the present invention provides the following solutions:

[0005] The utility model provides a hydraulic pipe bending control system, comprising a pilot proportional pressure reducing valve, an electromagnetic reversing valve and a throttle valve which are sequentially connected and communicated with an oil chamber; and a plurality of auxiliary thrust cylinders, wherein the auxiliary thrust cylinders have a rod chamber and a plug chamber, each of the rod chambers is connected and communicated with the electromagnetic reversing valve, each of the plug chambers can be connected and communicated with the throttle valve through an oil circuit, and each of the oil circuits is provided with an electromagnetic ball valve.

[0006] Preferably, the electromagnetic ball valve is a cartridge ball valve.

[0007] Preferably, four auxiliary thrust cylinders are provided.

[0008] Preferably, the pilot proportional pressure reducing valve and the electromagnetic reversing valve are connected and communicated with each other through a pipeline, a branch pipe is connected and communicated with the pipeline, and a one-way valve is provided on the branch pipe.

[0009] Compared with the prior art, the utility model has achieved the following technical effects:

[0010] (1) The hydraulic pipe bending control system provided by the utility model adopts a parallel structure of electromagnetic ball valves, which can control multiple groups of auxiliary push cylinder molds by one group of electromagnetic reversing valves, and realizes precise switching control by connecting the cylinders with a single line, and facilitates pressure adjustment, thus solving the shortcomings of the original electromagnetic valves that are more complicated to operate;

[0011] (2) The plug-in ball valve has a fast response, small footprint, and is easy to replace. It reduces the product structure, solves the problem of narrow internal space of the integrated pipe bending machine, and reduces product costs.

[0012] (3) The functional circuit that originally required multiple components to realize can be reduced by using fewer components, which is conducive to shortening the length of the oil channel, reducing the energy consumption in the oil chamber, reducing the heat generated during operation, and preventing overload;

[0013] (4) To prevent the impact of excessive pressure on external actuators caused by excessive pressure at the oil chamber port, a pilot proportional pressure reducing valve and a one-way valve are used for protection to prevent high and low pressure differences during starting and stopping. BRIEF DESCRIPTION OF THE DRAWINGS

[0014] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0015] Figure 1 This is a schematic diagram of the structure of the hydraulic pipe bending control system provided by the utility model;

[0016] In the figure: 1- auxiliary thrust cylinder; 2- pilot proportional pressure reducing valve; 3- electromagnetic reversing valve; 4- throttle valve; 5- electromagnetic ball valve. DETAILED DESCRIPTION

[0017] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the embodiments described are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0018] The purpose of the utility model is to provide a hydraulic pipe bending control system to solve the problems existing in the prior art, facilitate pressure regulation, and reduce costs.

[0019] In order to make the above-mentioned objects, features and advantages of the present invention more obvious and easy to understand, the present invention is further described in detail below with reference to the accompanying drawings and specific implementation methods.

[0020] The utility model provides a hydraulic pipe bending control system, such as Figure 1As shown, in this embodiment, it includes a pilot proportional pressure reducing valve 2, an electromagnetic reversing valve 3 and a throttle valve 4 which are connected and communicated with the oil chamber in sequence; and a plurality of auxiliary thrust cylinders 1, the auxiliary thrust cylinders 1 having a rod chamber and a plug chamber, each rod chamber is connected and communicated with the electromagnetic reversing valve 3, each plug chamber can be connected and communicated with the throttle valve 4 through an oil circuit, and each oil circuit is provided with an electromagnetic ball valve 5.

[0021] Furthermore, the electromagnetic ball valve 5 is a cartridge-type ball valve.

[0022] Furthermore, four auxiliary thrust cylinders 1 are provided.

[0023] Furthermore, the pilot proportional pressure reducing valve 2 and the electromagnetic reversing valve 3 are connected and communicated via a pipeline, a branch pipe is connected and communicated on the pipeline, and a one-way valve is provided on the branch pipe.

[0024] The hydraulic pipe bending control system provided by this utility model adopts the following control scheme to achieve its goal. It consists of two parts: an overload protection part and a control part. The control part mainly consists of a solenoid reversing valve, a superimposed one-way solenoid throttle valve, and five cartridge-type ball valves. The protection part consists of a pilot proportional pressure reducing valve. There is a total of one unit and four actions: normal operation extension, normal operation retraction, accident pressure maintenance, and stop. The specific working principle is as follows:

[0025] When the auxiliary thrust unit is extended normally, the electromagnets YA17 and YA22 are energized, and YAD is connected (both are in the positive position); the pilot proportional reducing valve 2 is in the open state, and the hydraulic oil flows from the oil chamber P port into the B port of the pilot proportional reducing valve 2, and then flows out from the A port of the pilot proportional reducing valve 2, and then flows into the P port of the electromagnetic reversing valve 3, and flows out from the A port of the electromagnetic reversing valve 3. The hydraulic oil then starts to flow from the A port oil channel through the throttle valve 4, to the 1 port of the electromagnetic ball valve 5, and flows out from the 2 port of the electromagnetic ball valve 5. It finally flows into the plug chamber of the auxiliary thrust cylinder 1 through the oil circuit, and the oil in the rod chamber of the auxiliary thrust cylinder 1 flows into the B port of the electromagnetic reversing valve 3, and flows out from the T port of the electromagnetic reversing valve 3. The rod chamber of the auxiliary thrust cylinder 1 extends to realize the extension action. Other cylinders can also realize linkage extension according to the connection of the electromagnetic ball valve 5.

[0026] During normal retraction, electromagnets YA16 and YA22 are energized, and YAD is connected (both are in the positive position); the pilot proportional reducing valve 2 is in the open state, and the hydraulic oil flows from the oil chamber P port into the B port of the pilot proportional reducing valve 2, and then flows out from the A port of the pilot proportional reducing valve 2, and then flows through the P port and B port of the electromagnetic reversing valve 3. The hydraulic oil then begins to flow into the rod chamber of the auxiliary push cylinder 1 from the B port oil channel of the electromagnetic reversing valve 3, and the oil in the plug chamber of the auxiliary push cylinder 1 flows into the 2 port of the electromagnetic ball valve 5, and then flows out from the 1 port of the electromagnetic ball valve 5 to the throttle valve 4, and finally flows out from the T port of the electromagnetic reversing valve 3. The auxiliary push cylinder 11 retracts to realize the retraction action. The other cylinders can also realize the linkage retraction according to the connection of the electromagnetic ball valve 5. If one of the cylinders needs to remain extended, the pressure can be maintained by de-energizing the electromagnetic ball valve 5 of the corresponding auxiliary push cylinder 1;

[0027] When an accident occurs and pressure maintenance is required, the solenoid valves YA16, YA17, YA22, YA23, YA24, and YA25 lose power, and the pilot proportional pressure reducing valve 2YAD loses power. The oil in the plug chamber of the auxiliary push cylinder 1 flows into the 2 port of the electromagnetic ball valve 5 and cannot flow out. The oil in the rod chamber of the auxiliary push cylinder 1 flows into the B port of the electromagnetic reversing valve 3. Since both sides of the electromagnetic reversing valve 3 lose power, it remains in the middle position and the oil cannot flow out. Finally, the auxiliary push cylinder 1 stops working and keeps the action state stationary, thus achieving accident pressure maintenance.

[0028] When stopping, electromagnets YA16, YA22, YA23, YA24, and YA25 are energized, and YAD is connected (all in the positive position). The hydraulic oil flows from the oil chamber P port to the B port of the pilot proportional reducing valve 2 to the A port, and then flows through the P port of the electromagnetic reversing valve 3 to the B port. The hydraulic oil then begins to flow into the rod chamber of the auxiliary push cylinder 1 from the B port oil channel, and the oil in the plug chamber of the auxiliary push cylinder 1 flows into the 2 port of the electromagnetic ball valve 5, and then flows out from the 1 port to the throttle valve 4, and finally flows out from the T port of the electromagnetic reversing valve 3. The auxiliary push cylinder 1 is completely reset, and then all the solenoid valves are de-energized, and the auxiliary push unit is stopped.

[0029] The hydraulic pipe bending control system provided by the utility model adopts a parallel structure of electromagnetic ball valves, allowing a group of electromagnetic reversing valves to control multiple groups of auxiliary push cylinder molds. A single-line connection between the oil cylinders achieves precise on-off control and convenient pressure adjustment, which solves the shortcomings of the original electromagnetic valves, such as the cumbersome operation. The cartridge ball valve has a fast response, occupies a small volume, and is easy to replace, which reduces the product structure, solves the shortcomings of the narrow internal space of the integrated pipe bending machine, and reduces product costs. The functional circuit that originally required multiple components is reduced in the number of components, which helps to shorten the length of the oil channel, reduce energy consumption in the oil chamber, reduce heat generated during operation, and prevent overload. The problem of excessive pressure at the oil chamber port impacting the external actuator is protected by a pilot proportional pressure reducing valve and a check valve to prevent high and low pressure differentials during startup and shutdown. The hydraulic pipe bending control system provided by the utility model can meet various production and debugging requirements. The functional components and ancillary facilities are rationally arranged, and the flow and pressure of the equipment are adjustable, making the equipment more intelligent, ensuring reliable control of system flow, and high energy utilization. The system is more stable and reliable, and can meet the usage requirements of different loads. And with the help of the integrated function of the electromagnetic ball valve, the system is made more compact and reasonable, which provides convenience for the subsequent inspection and maintenance of the equipment.

[0030] The hydraulic pipe bending control system provided by the utility model utilizes the low leakage characteristics of the plug-in electromagnetic ball valve, which greatly reduces the capacity loss of the control system valve block in the hydraulic pipe bending control system valve block, can provide high-frequency pressure, and has ideal control force for the main valve core with a long stroke, so that it can still achieve precise control in harsh environments;

[0031] The electromagnetic ball valve parallel structure design makes the valve body simple and compact, but it can pass a larger flow and high pressure. The pressure oil channel is distributed in the center of the valve block, strictly complying with the valve block design sealing standard (Hooke's law);

[0032] Different from the commonly used ball valve, the cartridge ball valve is different not only in terms of larger diameter and more sensitive response, but also has the advantages of B-type valve, two-way passage, and greatly reduces the impact on flow rate when hanging upside down or sideways. The use environment of the valve block is greatly improved.

[0033] The external interface selection is convenient and diverse, whether it is a pipe joint or a flange, etc., it can be connected to the valve block and different machine combinations to meet its use conditions;

[0034] The components are updated and used. When these components are damaged or updated, they can be directly replaced. The hydraulic components of the future will be further intelligent, and the models and functions of the components will be more powerful. The replacement of components of this equipment is extremely convenient, making the equipment more intelligent, and making the system flow reliably controlled and energy utilization high.

[0035] The present invention uses specific examples to illustrate the principles and implementation methods of the present invention. The above examples are only intended to help understand the method and core concept of the present invention. At the same time, those skilled in the art will find that the specific implementation methods and application scopes may vary based on the concept of the present invention. In summary, the contents of this specification should not be construed as limiting the present invention.

Claims

1. A hydraulic pipe bending control system, characterized by: include: A pilot proportional pressure reducing valve, a solenoid reversing valve and a throttle valve are sequentially connected and communicated with the oil chamber; And multiple auxiliary thrust cylinders, each of which has a rod cavity and a plug cavity, each of the rod cavities is connected and communicated with the electromagnetic reversing valve, each of the plug cavities can be connected and communicated with the throttle valve through an oil circuit, and each of the oil circuits is provided with an electromagnetic ball valve.

2. A hydraulic pipe bending control system according to claim 1, characterized in that: The electromagnetic ball valve is a cartridge ball valve.

3. The hydraulic pipe bending control system according to claim 1, characterized in that: There are four auxiliary thrust cylinders.

4. The hydraulic pipe bending control system according to claim 1, characterized in that: The pilot proportional pressure reducing valve and the electromagnetic reversing valve are connected and communicated through a pipeline, a branch pipe is connected and communicated with the pipeline, and a one-way valve is provided on the branch pipe.

Images