阅读说明：本技术 一种液压滚动式宽厚板剪切机液压增力储能系统 (Hydraulic force-increasing energy storage system of hydraulic rolling type wide and thick plate shearing machine ) 是由 和东平 王涛 徐慧东 任忠凯 马晓宝 王君 郝平菊 于 2019-10-11 设计创作，主要内容包括：本发明属于金属板剪切机技术领域,具体涉及一种液压滚动式宽厚板剪切机液压增力储能系统。包括活塞杆端部分别通过推杆和连杆与机架和上刀架上方相铰接的第一伺服液压缸和第二伺服液压缸,还包括第一滚动剪切回路、第二滚动剪切回路、第一储能单元、第二储能单元、第一液压增力回路以及第二液压增力回路；所述第一伺服液压缸和第二伺服液压缸的活塞杆内部分别安装有第一内置位移传感器和第二内置位移传感器。通过液压增力回路的使用提高了液压滚动式宽厚板剪切机的剪切力,增大了剪切厚度范围。储能单元的使用起到了能量回收的作用,同时加快了回程速度,提高了生产效率。双压力闭环协同控制回路保证了液压滚动式宽厚板剪切机剪切力的控制与调整。(The invention belongs to the technical field of metal plate shearing machines, and particularly relates to a hydraulic force-increasing and energy-storing system of a hydraulic rolling type wide and thick plate shearing machine. The hydraulic servo system comprises a first servo hydraulic cylinder and a second servo hydraulic cylinder, wherein the end parts of piston rods are respectively hinged with the upper parts of a rack and an upper tool rest through a push rod and a connecting rod; and a first built-in displacement sensor and a second built-in displacement sensor are respectively arranged in piston rods of the first servo hydraulic cylinder and the second servo hydraulic cylinder. The hydraulic boosting loop is used to improve the shearing force of the hydraulic rolling type wide and thick plate shearing machine and increase the shearing thickness range. The energy storage unit plays a role in energy recovery, and meanwhile, the return speed is increased, and the production efficiency is improved. The double-pressure closed-loop cooperative control loop ensures the control and adjustment of the shearing force of the hydraulic rolling type wide and thick plate shearing machine.)

1. A hydraulic force-increasing energy-storing system of a hydraulic rolling type wide and thick plate shearing machine comprises a first servo hydraulic cylinder (13.1) and a second servo hydraulic cylinder (13.2) which are hinged with the upper parts of a rack and an upper tool rest (21) through a push rod (19) and a connecting rod (20) at the end parts of piston rods, and is characterized by further comprising a first rolling shearing loop, a second rolling shearing loop, a first energy-storing unit, a second energy-storing unit, a first hydraulic force-increasing loop and a second hydraulic force-increasing loop;

a first built-in displacement sensor (12.1) and a second built-in displacement sensor (12.2) are respectively arranged in piston rods of the first servo hydraulic cylinder (13.1) and the second servo hydraulic cylinder (13.2);

the first rolling shearing loop comprises a first plug-in directional valve (8.1), an oil port A of the first plug-in directional valve (8.1) is connected to a high-pressure oil pipe (P), an oil port B of the first plug-in directional valve (8.1) is connected to the oil port P of a first high-frequency response proportional servo valve (10.1), the oil port A of the first high-frequency response proportional servo valve (10.1) is connected to the oil port A of a second plug-in directional valve (8.2), and the oil port B of the second plug-in directional valve (8.2) is connected to a rodless cavity of a first servo hydraulic cylinder (13.1); a rod cavity of the first servo hydraulic cylinder (13.1) is connected with an oil port B of a third plug-in directional valve (8.3), an oil port A of the third plug-in directional valve (8.3) is connected with an oil port B of a first high-frequency response proportional servo valve (10.1), and an oil port T of the first high-frequency response proportional servo valve (10.1) is connected to an oil return pipe (T);

the first energy storage unit comprises a first electromagnetic ball valve (16.1) coupled to the rod cavity of the first servo hydraulic cylinder (13.1), a first relief ball valve (18.1) with a first energy accumulator (17.1) coupled to the first electromagnetic ball valve (16.1);

the first hydraulic boosting loop comprises a first three-position four-way electromagnetic reversing valve (5.1), an oil port P of the first three-position four-way electromagnetic reversing valve (5.1) is connected to a high-pressure oil pipe (P), and an oil port A of the first three-position four-way electromagnetic reversing valve (5.1) and an oil port A of a first supercharger (7.1) are connected with each other ₁And A ₃The working oil chambers are communicated, and A of the first supercharger (7.1) ₂And A ₄The working oil cavity is respectively connected with an oil port B of a first three-position four-way electromagnetic reversing valve (5.1), an oil port T of the first three-position four-way electromagnetic reversing valve (5.1) is connected to an oil return pipe (T), and an oil port A of a first supercharger (7.1) ₁And A ₂The working oil cavity is communicated through a pipeline and then is connected to a rodless cavity of the first servo hydraulic cylinder (13.1);

the second rolling shearing loop has the same structure as the first rolling shearing loop, the second energy storage unit has the same structure as the first energy storage unit, the second hydraulic boosting loop has the same structure as the first hydraulic boosting loop, and the second rolling shearing loop, the second energy storage unit and the second hydraulic boosting loop are used for controlling a second servo hydraulic cylinder (13.2); each plug-in mounting directional valve is provided with an electromagnetic directional valve.

2. The hydraulic pressure reinforcement energy storage system of the hydraulic rolling type wide and thick plate shearing machine according to claim 1, characterized in that the first three-position four-way electromagnetic directional valve (5.1) is connected to a high-pressure oil pipe (P) through a first proportional pressure reducing valve (3.1), and A of the first supercharger (7.1) ₁And A ₂And a third pressure sensor (14.3) is arranged on a pipeline between the working oil cavity and the rodless cavity of the first servo hydraulic cylinder (13.1).

3. The hydraulic rolling type wide and thick plate shearing machine hydraulic force-increasing energy storage system according to claim 1, characterized in that a first pressure sensor (14.1) is installed on the rodless cavity of the first servo hydraulic cylinder (13.1), and the rodless cavity of the first servo hydraulic cylinder (13.1) is connected to an oil tank through a first proportional overflow valve (11.1).

4. The hydraulic rolling type wide and thick plate shearing machine hydraulic pressure reinforcement energy storage system according to claim 1, characterized in that the rod cavity of the first servo hydraulic cylinder (13.1) is connected to an oil tank through a first cartridge overflow valve (15.1).

5. Hydraulic pressure reinforcement energy storage system of a hydraulic rolling type wide and thick plate shearing machine according to claim 1, characterized in that A of the first supercharger (7.1) ₁A first one-way valve (6.1) and a first supercharger (7.1) are arranged between the working oil cavity and an oil port A of a first three-position four-way electromagnetic directional valve (5.1) ₂A fourth one-way valve (6.4) and a first booster (7.1) are arranged between the working oil cavity and an oil port B of the first three-position four-way electromagnetic directional valve (5.1) ₁And A ₂A second one-way valve (6.2) and a third one-way valve (6.3) are respectively arranged between the working oil cavity and the rodless cavity of the first servo hydraulic cylinder (13.1).

6. The hydraulic rolling type wide and thick plate shearing machine hydraulic pressure reinforcement energy storage system according to claim 1, characterized in that a first non-return one-way valve (4.1) is installed between the oil port T and the oil return pipe (T) of the first three-position four-way electromagnetic directional valve (5.1).

7. The hydraulic rolling type wide and thick plate shearing machine hydraulic pressure reinforcement energy storage system according to claim 1, characterized in that a second non-return one-way valve (4.2) is installed between the oil port T and the oil return pipe (T) of the first high frequency response proportional servo valve (10.1).

Technical Field

The invention belongs to the technical field of metal plate shearing machines, and particularly relates to a hydraulic force-increasing and energy-storing system of a hydraulic rolling type wide and thick plate shearing machine.

Background

The hydraulic rolling type wide and thick plate shearing machine is a major technical device urgently needed for producing high-strength, wear-resistant, corrosion-resistant and high-added-value wide and thick plates, and mainly completes the work of head cutting, tail cutting, sizing cutting, sampling and the like of steel plates. The hydraulic rolling type wide and thick plate shearing machine directly drives the composite connecting rod shearing mechanism by adopting the servo hydraulic cylinder according to the rolling shearing principle, so that the circular arc-shaped upper tool rest can transversely roll and shear wide and thick steel plates. At present, the maximum shearing thickness of the hydraulic rolling type wide and thick plate shearing machine in the prior art can reach 60mm, the shearing force is 1300T-1600T, and the maximum shearing width is 4300 mm. In the rolling shearing movement process of the wide and thick plate, the hydraulic system in the prior art adopts a method of adding a plunger pump and opening an energy accumulator at regular time, when a piston rod of a hydraulic cylinder extends to a specified position, the energy accumulator releases high-pressure oil and flows into a rodless cavity of the hydraulic cylinder together with the high-pressure oil provided by a pump source so as to complete the rolling shearing process of the steel plate, but the high-pressure oil released by the energy accumulator is an instantaneous flow; in the shearing process of the steel plate, if the liquid fed into the energy accumulator is not timely, the steel plate is likely to be continuously sheared due to insufficient shearing force, and the like. With the progress of science and technology, the industries such as national defense, shipbuilding, nuclear power and the like put forward higher requirements on the service thickness of the high-strength, wear-resistant, corrosion-resistant and other wide and thick plates, and the shear capacity of the hydraulic rolling type wide and thick plate shearing machine is put forward higher standards.

Disclosure of Invention

The invention provides a hydraulic boosting and energy storage system of a hydraulic rolling type wide and thick plate shearing machine on the basis of a hydraulic system (ZL 200810080225.7) of the hydraulic rolling type metal plate shearing machine, overcomes the defects of the prior art, and has the characteristics of simple structure, strong practicability and easy implementation.

The invention is realized by the following technical scheme: a hydraulic reinforcement energy storage system of a hydraulic rolling type wide and thick plate shearing machine comprises a first servo hydraulic cylinder and a second servo hydraulic cylinder, wherein the end parts of piston rods are respectively hinged with a rack and the upper part of an upper tool rest through push rods and connecting rods;

a first built-in displacement sensor and a second built-in displacement sensor are respectively arranged in piston rods of the first servo hydraulic cylinder and the second servo hydraulic cylinder;

the first rolling shearing loop comprises a first plug-in directional valve, an oil port A of the first plug-in directional valve is connected to a high-pressure oil pipe, an oil port B of the first plug-in directional valve is connected to an oil port P of a first high-frequency response proportional servo valve, an oil port A of the first high-frequency response proportional servo valve is connected to an oil port A of a second plug-in directional valve, and an oil port B of the second plug-in directional valve is connected to a rodless cavity of a first servo hydraulic cylinder; a rod cavity of the first servo hydraulic cylinder is connected with an oil port B of a third plug-in directional valve, an oil port A of the third plug-in directional valve is connected with an oil port B of a first high-frequency response proportional servo valve, and an oil port T of the first high-frequency response proportional servo valve is connected to an oil return pipe;

the first energy storage unit comprises a first electromagnetic ball valve and a first safety ball valve, wherein the first electromagnetic ball valve is connected to a rod cavity of the first servo hydraulic cylinder;

the first hydraulic pressure-increasing circuitThe hydraulic booster comprises a first three-position four-way electromagnetic reversing valve, wherein an oil port P of the first three-position four-way electromagnetic reversing valve is connected to a high-pressure oil pipe, and an oil port A of the first three-position four-way electromagnetic reversing valve is respectively connected with an oil port A of a first booster ₁And A ₃The working oil cavities are communicated, and A of the first supercharger ₂And A ₄The working oil cavity is respectively connected with an oil port B of a first three-position four-way electromagnetic reversing valve, an oil port T of the first three-position four-way electromagnetic reversing valve is connected to an oil return pipe, and an oil port A of a first supercharger ₁And A ₂The working oil cavity is communicated through a pipeline and then is connected to a rodless cavity of the first servo hydraulic cylinder;

the second rolling shearing loop has the same structure as the first rolling shearing loop, the second energy storage unit has the same structure as the first energy storage unit, the second hydraulic boosting loop has the same structure as the first hydraulic boosting loop, and the second rolling shearing loop, the second energy storage unit and the second hydraulic boosting loop are used for controlling a second servo hydraulic cylinder; each plug-in mounting directional valve is provided with an electromagnetic directional valve.

As a further improvement of the technical scheme of the invention, the first three-position four-way electromagnetic directional valve is connected to a high-pressure oil pipe through a first proportional pressure reducing valve, and A of the first supercharger ₁And A ₂And a third pressure sensor is arranged on a pipeline between the working oil cavity and the rodless cavity of the first servo hydraulic cylinder.

As a further improvement of the technical scheme of the invention, a first pressure sensor is arranged on the rodless cavity of the first servo hydraulic cylinder, and the rodless cavity of the first servo hydraulic cylinder is connected to the oil tank through a first proportional overflow valve.

As a further improvement of the technical scheme of the invention, the rod cavity of the first servo hydraulic cylinder is connected to the oil tank through a first cartridge overflow valve.

As a further improvement of the technical scheme of the invention, A of the first supercharger ₁A first check valve is arranged between the working oil cavity and an oil port A of the first three-position four-way electromagnetic directional valve, and A of the first supercharger ₂A fourth one-way valve is arranged between the working oil cavity and an oil port B of the first three-position four-way electromagnetic reversing valve, and a first supercharger A ₁And A ₂And a second check valve and a third check valve are respectively arranged between the working oil cavity and the rodless cavity of the first servo hydraulic cylinder.

As a further improvement of the technical scheme of the invention, a first non-return one-way valve is arranged between an oil port T and an oil return pipe of the first three-position four-way electromagnetic directional valve.

As a further improvement of the technical scheme of the invention, a second non-return one-way valve is arranged between the oil port T of the first high-frequency response proportional servo valve and the oil return pipe.

The invention has the advantages and positive effects that:

1. the hydraulic boosting loop is used to improve the shearing force of the hydraulic rolling type wide and thick plate shearing machine and increase the shearing thickness range. The energy storage unit plays a role in energy recovery, and meanwhile, the return speed is increased, and the production efficiency is improved.

2. The double-pressure closed-loop cooperative control loop ensures the accurate control and timely adjustment of the shearing force of the hydraulic rolling type wide and thick plate shearing machine, so that the rolling shearing process is extremely stable, and the position precision of the upper tool rest in the rolling shearing process is ensured by using the position closed loop.

3. The invention has the characteristics of simple structure, strong practicability and easy implementation.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.

Fig. 1 is a schematic diagram of a hydraulic force-increasing energy-storing system of the hydraulic rolling type wide and thick plate shearing machine of the invention.

In the figure: 1-a low-pressure ball valve, 2-a high-pressure ball valve, 3.1-a first proportional pressure reducing valve, 3.2-a second proportional pressure reducing valve, 4.1-a first check valve, 4.2-a second check valve, 4.3-a third check valve, 4.4-a fourth check valve, 5.1-a first three-position four-way electromagnetic directional valve, 5.2-a second three-position four-way electromagnetic directional valve, 6.1-a first check valve, 6.2-a second check valve, 6.3-a third check valve, 6.4-a fourth check valve, 6.5-a fifth check valve, 6.6-a sixth check valve, 6.7-a seventh check valve, 6.8-an eighth check valve, 7.1-a first booster, 7.2-a second booster, 8.1-a first cartridge direction valve, 8.2-a second cartridge direction valve, 8.3-a third cartridge valve, 8.4-a fourth cartridge direction valve, 8.5-a fifth cartridge direction valve, 8.6-a sixth cartridge direction valve, 9.1-a first electromagnetic directional valve, 9.2-a second electromagnetic directional valve, 9.3-a third electromagnetic directional valve, 9.4-a fourth electromagnetic directional valve, 9.5-a fifth electromagnetic directional valve, 9.6-a sixth electromagnetic directional valve, 10.1-a first high frequency response proportional servo valve, 10.2-a second high frequency response proportional servo valve, 11.1-a first proportional relief valve, 11.2-a second proportional relief valve, 12.1-a first built-in displacement sensor, 12.2-a second built-in displacement sensor, 13.1-a first servo hydraulic cylinder, 13.2-a second servo hydraulic cylinder, 14.1-a first pressure sensor, 14.2-a second pressure sensor, 14.3-a third pressure sensor, 14.4-a fourth pressure sensor, 15.1-a first plug-in overflow valve, 15.2-a second plug-in overflow valve, 16.1-a first electromagnetic ball valve, 16.2-a second electromagnetic ball valve, 17.1-a first accumulator, 17.2-a second accumulator, 18.1-a first safety ball valve, 18.2-a second safety ball valve, 19-a push rod, 20-a connecting rod, 21-a top knife rest, P-a high-pressure oil pipe, T-an oil return pipe, YVH 1.1.1, YVH 1.2.2, YVH1.3, YVH 1.4.4, YVH2.1, YVH2.2, YVH 2.3.3, YVH 2.4.4, YVH 2.5.5, YVH 2.6.6, YVH 3.1.1, YVH 3.2.2-electromagnets, YB1.1, YB1.2, YB2.1, YB2.2, YB2.3, YB2.4, YB3.1 and YB 3.2-proportion.

Detailed Description

In order to make the objects, technical solutions and advantages of the present invention more apparent, the technical solutions of the present invention will be described in detail below. It is to be understood that the described embodiments are merely exemplary of the invention, and not restrictive of the full scope of the invention. All other embodiments, which can be derived by a person skilled in the art from the examples given herein without any inventive step, are within the scope of the present invention.

Referring to fig. 1, the embodiment provides a hydraulic force-increasing energy-storing system of a hydraulic rolling type wide and thick plate shearing machine, which includes a first servo hydraulic cylinder 13.1 and a second servo hydraulic cylinder 13.2, the ends of which are hinged to the upper sides of a frame and an upper tool rest 21 through a push rod 19 and a connecting rod 20, and further includes a first rolling shearing circuit, a second rolling shearing circuit, a first energy-storing unit, a second energy-storing unit, a first hydraulic force-increasing circuit and a second hydraulic force-increasing circuit.

And a first built-in displacement sensor 12.1 and a second built-in displacement sensor 12.2 are respectively arranged in the piston rods of the first servo hydraulic cylinder 13.1 and the second servo hydraulic cylinder 13.2. Wherein one end of the upper tool carrier 21 close to the second servo hydraulic cylinder 13.2 is hinged with the frame.

The first rolling shearing loop comprises a first plug-in directional valve 8.1, an oil port A of the first plug-in directional valve 8.1 is connected to a high-pressure oil pipe P, an oil port B of the first plug-in directional valve 8.1 is connected to the oil port P of a first high-frequency response proportional servo valve 10.1, an oil port A of the first high-frequency response proportional servo valve 10.1 is connected to an oil port A of a second plug-in directional valve 8.2, and an oil port B of the second plug-in directional valve 8.2 is connected to a rodless cavity of a first servo hydraulic cylinder 13.1; the rod cavity of the first servo hydraulic cylinder 13.1 is connected with the oil port B of the third plug-in directional valve 8.3, the oil port A of the third plug-in directional valve 8.3 is connected with the oil port B of the first high-frequency response proportional servo valve 10.1, and the oil port T of the first high-frequency response proportional servo valve 10.1 is connected to the oil return pipe T.

Similarly, the second rolling shearing loop comprises a fourth plug-in directional valve 8.4, an oil port a of the fourth plug-in directional valve 8.4 is connected to a high-pressure oil pipe P, an oil port B of the fourth plug-in directional valve 8.4 is connected to an oil port P of a second high-frequency response proportional servo valve 10.2, an oil port a of the second high-frequency response proportional servo valve 10.2 is connected to an oil port a of a sixth plug-in directional valve 8.6, and an oil port B of the sixth plug-in directional valve 8.6 is connected to a rod cavity of a second servo hydraulic cylinder 13.2; the rodless cavity of the second servo hydraulic cylinder 13.2 is connected with an oil port B of a fifth plug-in directional valve 8.5, an oil port A of the fifth plug-in directional valve 8.5 is connected with an oil port B of a second high-frequency response proportional servo valve 10.2, and an oil port T of the second high-frequency response proportional servo valve 10.2 is connected to an oil return pipe T.

The first energy storage unit comprises a first electromagnetic ball valve 16.1 coupled to the rod chamber of the first servo hydraulic cylinder 13.1, and a first relief ball valve 18.1 with a first accumulator 17.1 coupled to the first electromagnetic ball valve 16.1.

Similarly, the second energy storage unit comprises a second electromagnetic ball valve 16.2 coupled to the rod chamber of the second servo hydraulic cylinder 13.2, and a second relief ball valve 18.2 with a second accumulator 17.2 coupled to the second electromagnetic ball valve 16.2.

The first hydraulic boosting loop comprises a first three-position four-way electromagnetic reversing valve 5.1, an oil port P of the first three-position four-way electromagnetic reversing valve 5.1 is connected to a high-pressure oil pipe P, and an oil port A of the first three-position four-way electromagnetic reversing valve 5.1 is respectively connected with an oil port A of a first supercharger 7.1 ₁And A ₃The working oil cavities are communicated, and A of a first supercharger 7.1 ₂And A ₄The working oil cavity is respectively connected with an oil port B of a first three-position four-way electromagnetic reversing valve 5.1, an oil port T of the first three-position four-way electromagnetic reversing valve 5.1 is connected to an oil return pipe T, and an oil port A of a first supercharger 7.1 ₁And A ₂The working oil chamber is connected to the rodless chamber of the first servo hydraulic cylinder 13.1 after being communicated through a pipeline.

Similarly, the second hydraulic pressure boosting loop comprises a second three-position four-way electromagnetic reversing valve 5.2, an oil port P of the second three-position four-way electromagnetic reversing valve 5.2 is connected to a high-pressure oil pipe P, and an oil port A of the second three-position four-way electromagnetic reversing valve 5.2 is respectively connected with an oil port A of a second supercharger 7.2 ₁And A ₃The working oil chambers are communicated, and A of a second supercharger 7.2 ₂And A ₄The working oil cavity is respectively connected with an oil port B of a second three-position four-way electromagnetic reversing valve 5.2, an oil port T of the second three-position four-way electromagnetic reversing valve 5.2 is connected to an oil return pipe T, and an oil port A of a second supercharger 7.2 ₁And A ₂The working oil chamber is connected to the rodless chamber of the second servo hydraulic cylinder 13.2 after being communicated through a pipeline.

In this embodiment, each direction valve is installed with an electromagnetic directional valve. The connection mode between the cartridge directional valve and the electromagnetic directional valve can be realized by those skilled in the art. The first plug-in directional valve 8.1 is provided with a first electromagnetic directional valve 9.1, the second plug-in directional valve 8.2 is provided with a second electromagnetic directional valve 9.2, the third plug-in directional valve 8.3 is provided with a third electromagnetic directional valve 9.3, the fourth plug-in directional valve 8.4 is provided with a fourth electromagnetic directional valve 9.4, the fifth plug-in directional valve 8.5 is provided with a fifth electromagnetic directional valve 9.5, and the sixth plug-in directional valve 8.6 is provided with a sixth electromagnetic directional valve 9.6.

When the high-pressure oil pipe hydraulic servo valve is used specifically, the electromagnet YVH 2.1.1, the electromagnet YVH 2.2.2, the electromagnet YVH 3.1.1, the proportional electromagnet YB2.2 and the proportional electromagnet YB3.1 are electrified simultaneously, the first electromagnetic directional valve 9.1, the second electromagnetic directional valve 9.2, the first electromagnetic ball valve 16.1 and the first high-frequency-response proportional servo valve 10.1 are reversed simultaneously, oil of the high-pressure oil pipe P sequentially flows into ｃA rodless cavity of the first servo hydraulic cylinder 13.1 through an A-B channel of the first plug-in directional valve 8.1, ｃA P-A channel of the first high-frequency-response proportional servo valve 10.1 and an A-B channel of the second plug-in directional valve 8.2, and ｃA piston rod is driven to extend out. Meanwhile, the hydraulic oil in the rod cavity of the first servo hydraulic cylinder 13.1 flows into the first energy accumulator 17.1 of the first energy storage unit through the P-A channel of the first electromagnetic ball valve 16.1 for energy recovery. When the piston rod of the first servo hydraulic cylinder 13.1 moves to the position target set value of the first built-in displacement sensor 12.1, the electromagnet YVH 3.1.1 is powered off, the electromagnet YVH 2.3.3 is powered on, and hydraulic oil in the rod cavity of the first servo hydraulic cylinder 13.1 flows into the oil return pipe T through the B-A channel of the third plug-in directional valve 8.3, the B-T channel of the first high-frequency response proportional servo valve 10.1 and the A-B channel of the second check one-way valve.

Meanwhile, the electromagnet YVH 2.4.4, the electromagnet YVH 2.5.5, the electromagnet YVH 3.2.2, the proportional electromagnet YB2.3 and the proportional electromagnet YB3.2 are simultaneously electrified, the fourth electromagnetic directional valve 9.4, the fifth electromagnetic directional valve 9.5, the second electromagnetic ball valve 16.2 and the second high-frequency-response proportional servo valve 10.2 are simultaneously reversed, oil liquid of the high-pressure oil pipe P sequentially flows into a rodless cavity of the second servo hydraulic cylinder 13.2 through an A-B channel of the fourth cartridge directional valve 8.4, a P-B channel of the second high-frequency-response proportional servo valve 10.2 and an A-B channel of the fifth cartridge directional valve 8.5 to drive a piston rod to extend out. Meanwhile, the hydraulic oil in the rod cavity of the second servo hydraulic cylinder 13.2 flows into ｃA second energy accumulator 17.2 of the second energy storage unit through ｃA P-A channel of the second electromagnetic ball valve 16.2 for energy recovery; when the piston rod of the second servo hydraulic cylinder 13.2 moves to the position target set value of the second built-in displacement sensor 12.2, the electromagnet YVH 3.2.2 is powered off, the electromagnet YVH 2.6.6 is powered on, and hydraulic oil in the rod cavity of the second servo hydraulic cylinder 13.2 flows into the oil return pipe T through the B-A channel of the sixth cartridge directional valve 8.6, the A-T channel of the second high-frequency response proportional servo valve 10.2 and the A-B channel of the third check one-way valve.

The purpose of rolling and shearing the upper tool post 21 is realized through the mutual cooperative control of the first servo hydraulic cylinder 13.1 and the second servo hydraulic cylinder 13.2.

Further, the first servo hydraulic cylinder 13.1 and the second servo hydraulic cylinder 13.2 are respectively provided with a first built-in displacement sensor 12.1 and a second built-in displacement sensor 12.2. In the process of rolling shearing, the position accuracy of the upper tool rest 21 is ensured mainly by forming a position closed loop by the first built-in displacement sensor 12.1 and the second built-in displacement sensor 12.2 in the first high-frequency response proportional servo valve 10.1 and the second high-frequency response proportional servo valve 10.2 respectively to control the displacement of the first servo hydraulic cylinder 13.1 and the second servo hydraulic cylinder 13.2 in real time. The pressure of the rodless cavity of the first servo hydraulic cylinder 13.1 is accurately controlled and timely adjusted through a pressure closed loop formed by the first proportional overflow valve 11.1 and the first pressure sensor 14.1. Similarly, the pressure of the rodless cavity of the second servo hydraulic cylinder 13.2 is accurately controlled and timely adjusted by a pressure closed loop formed by the second proportional overflow valve 11.2 and the second pressure sensor 14.2. The use of the pressure closed loop avoids serious accidents such as frame breaking caused by untimely overload protection response. When the upper tool rest 21 moves to the displacement target value of the built-in displacement sensor, the hydraulic boosting loop continuously outputs high-pressure oil through the non-reversal of the valve core of the three-position four-way electromagnetic directional valve, so that the shearing force of the hydraulic rolling type wide and thick plate shearing machine is improved, and the shearing thickness range is enlarged.

Further, when the upper tool post 21 moves to the displacement target values of the first built-in displacement sensor 12.1 and the second built-in displacement sensor 12.2 to prepare for shearing the steel plate, the first three-position four-way electromagnetic directional valve 5.1 and the second three-position four-way electromagnetic directional valve 5.2 respectively start to operate:

when electromagnet YVH 1.1.1 is obtainedWhen the electric booster is powered on, oil of ｃA high-pressure oil pipe P sequentially passes through ｃA channel B-A of the first proportional pressure reducing valve 3.1 and ｃA channel P-A of the first three-position four-way electromagnetic directional valve 5.1 to enter ｃA channel A of the first booster 7.1 ₁And A ₃A working oil cavity; a. the ₄Oil in the working oil cavity flows into an oil return pipe T through a B-T channel of a first three-position four-way electromagnetic directional valve 5.1 and an A-B channel of a first check one-way valve 4.1; a. the ₂High-pressure oil in the working oil cavity flows into the rodless cavity of the first servo hydraulic cylinder 13.1 through an A-B channel of the third one-way valve 6.3 to push the piston to do work, so that the shearing force is increased. When the electromagnet YVH 1.2.2 is electrified, oil in the high-pressure oil pipe P sequentially passes through the B-A channel of the first proportional pressure reducing valve 3.1 and the P-B channel of the first three-position four-way electromagnetic reversing valve 5.1 to enter the A channel of the first supercharger 7.1 ₂And A ₄A working oil cavity; a. the ₃Oil in the working oil cavity flows into an oil return pipe T through an A-T channel of a first three-position four-way electromagnetic directional valve 5.1 and an A-B channel of a first check one-way valve 4.1; a. the ₁High-pressure oil in the working oil cavity flows into the rodless cavity of the first servo hydraulic cylinder 13.1 through an A-B channel of the second one-way valve 6.2 to push the piston to do work, so that the shearing force is increased. The continuous pressurization of the first rolling shearing loop is realized by the uninterrupted alternate work of the electromagnet YVH 1.1.1 and the electromagnet YVH 1.2.2 of the first three-position four-way electromagnetic directional valve 5.1, so that the shearing force of the hydraulic rolling type wide and thick plate shearing machine is improved, and the shearing thickness range is enlarged.

Similarly, when the electromagnet YVH 1.3.3 is powered on, oil in the high-pressure oil pipe P sequentially passes through the B-A channel of the second proportional pressure reducing valve 3.2 and the P-A channel of the second three-position four-way electromagnetic reversing valve 5.2 to enter the A channel of the second supercharger 7.2 ₁And A ₃A working oil cavity; a. the ₄Oil in the working oil cavity flows into an oil return pipe T through a B-T channel of a second three-position four-way electromagnetic directional valve 5.2 and an A-B channel of a fourth check one-way valve 4.4; a. the ₂High-pressure oil in the working oil cavity flows into a rodless cavity of the second servo hydraulic cylinder 13.2 through an A-B channel of the seventh one-way valve 6.7 to push a piston to do work, so that the shearing force is increased. When the electromagnet YVH 1.4.4 is electrified, oil in the high-pressure oil pipe P sequentially passes through the B-A channel of the second proportional pressure reducing valve 3.2 and the P-B channel of the second three-position four-way electromagnetic reversing valve 5.2 to enter the secondA of supercharger 7.2 ₂And A ₄A working oil cavity; a. the ₃Oil in the working oil cavity flows into an oil return pipe T through an A-T channel of a second three-position four-way electromagnetic reversing valve 5.2 and an A-B channel of a fourth check one-way valve 4.4; a. the ₁High-pressure oil in the working oil cavity flows into a rodless cavity of the second servo hydraulic cylinder 13.2 through an A-B channel of the sixth one-way valve 6.6 to push a piston to do work, so that the shearing force is increased. The continuous pressurization of the second rolling shearing loop is realized through the uninterrupted alternate work of the electromagnet YVH 1.3.3 and the electromagnet YVH 1.4.4 of the second three-position four-way electromagnetic directional valve 5.2, so that the shearing force of the hydraulic rolling type wide and thick plate shearing machine is improved, and the shearing thickness range is enlarged.

Further, the first three-position four-way electromagnetic directional valve 5.1 is connected to a high-pressure oil pipe P through a first proportional pressure reducing valve 3.1, and A of the first supercharger 7.1 ₁And A ₂A third pressure sensor 14.3 is arranged on a pipeline between the working oil cavity and the rodless cavity of the first servo hydraulic cylinder 13.1. The second three-position four-way electromagnetic directional valve 5.2 is connected to a high-pressure oil pipe P through a second proportional pressure reducing valve 3.2, and A of the second supercharger 7.2 ₁And A ₂A fourth pressure sensor 14.4 is arranged on a pipeline between the working oil chamber and the rodless chamber of the second servo hydraulic cylinder 13.2. The pressure of the first hydraulic pressure increasing circuit can be accurately controlled and timely adjusted through a pressure closed loop formed by the first proportional pressure reducing valve 3.1 and the third pressure sensor 14.3. Similarly, the pressure of the second hydraulic pressure increasing circuit can be accurately controlled and timely adjusted by forming a pressure closed loop by the second proportional pressure reducing valve 3.2 and the fourth pressure sensor 14.4.

Further, a first pressure sensor 14.1 is mounted on a rodless cavity of the first servo hydraulic cylinder 13.1, and the rodless cavity of the first servo hydraulic cylinder 13.1 is connected to the oil tank through a first proportional overflow valve 11.1. A second pressure sensor 14.2 is mounted on a rodless cavity of the second servo hydraulic cylinder 13.2, and the rodless cavity of the second servo hydraulic cylinder 13.2 is connected to an oil tank through a second proportional overflow valve 11.2. The first servo hydraulic cylinder 13.1 forms a first servo hydraulic cylinder pressure closed loop by a first pressure sensor 14.1 and a first proportional overflow valve 11.1; the first proportional pressure reducing valve 3.1 and the third pressure sensor 14.3 form a first hydraulic pressure booster circuit pressure closed loop; the double-pressure closed loop cooperative control circuit ensures the accurate control and timely adjustment of the shearing force of the first rolling shearing circuit of the hydraulic rolling type wide and thick plate shearing machine. Similarly, the second servo hydraulic cylinder 13.2 forms a second servo hydraulic cylinder pressure closed loop by a second pressure sensor 14.2 and a second proportional overflow valve 11.2; the second proportional pressure reducing valve 3.2 and the fourth pressure sensor 14.4 form a second hydraulic pressure booster circuit pressure closed loop; the double-pressure closed loop cooperative control circuit ensures the accurate control and timely adjustment of the shearing force of the second rolling shearing circuit of the hydraulic rolling type wide and thick plate shearing machine.

Further, when the first servo hydraulic cylinder 13.1 and the second servo hydraulic cylinder 13.2 return, the first three-position four-way electromagnetic directional valve 5.1 and the second three-position four-way electromagnetic directional valve 5.2 stop working.

The electromagnet YVH 2.1.1, the electromagnet YVH 2.2.2, the electromagnet YVH 2.3.3, the electromagnet YVH 3.1.1, the proportional electromagnet YB2.1 and the proportional electromagnet YB3.1 are simultaneously electrified, the first electromagnetic directional valve 9.1, the second electromagnetic directional valve 9.2, the third electromagnetic directional valve 9.3, the first electromagnetic ball valve 16.1 and the first high-frequency-response proportional servo valve 10.1 are simultaneously reversed, oil of the high-pressure oil pipe P sequentially flows into a rod cavity of the first servo hydraulic cylinder 13.1 through an A-B channel of the first plug-in directional valve 8.1, a P-B channel of the first high-frequency-response proportional servo valve 10.1 and an A-B channel of the third plug-in directional valve 8.3, and simultaneously, the first energy accumulator 17.1 of the first energy storage unit releases stored high-pressure oil to flow into the rod cavity of the first servo hydraulic cylinder 13.1 through the A-P channel of the first electromagnetic ball valve 16.1, so as to drive a piston rod of the first servo hydraulic cylinder 13.1 to return quickly. Meanwhile, the hydraulic oil in the rodless cavity of the first servo hydraulic cylinder 13.1 flows back to the main oil return pipe T through a channel B-A of the second plug-in directional valve 8.2, a channel A-T of the first high-frequency response proportional servo valve 10.1 and a channel A-B of the second check one-way valve 4.2.

When ｃA piston rod of the first servo hydraulic cylinder 13.1 moves back to ｃA position target set value of the first built-in displacement sensor 12.1, the electromagnet YVH 2.4.4, the electromagnet YVH 2.5.5, the electromagnet YVH 2.6.6, the electromagnet YVH 3.1.1, the proportional electromagnet YB2.4 and the proportional electromagnet YB3.2 are simultaneously electrified, the fourth electromagnetic directional valve 9.4, the fifth electromagnetic directional valve 9.5, the sixth electromagnetic directional valve 9.6, the second electromagnetic ball valve 16.2 and the second high-frequency-response proportional servo valve 10.2 are simultaneously reversed, oil of the high-pressure oil pipe P sequentially passes through an A-B channel of the fourth plug-in directional valve 8.4, ｃA P-A channel of the second high-frequency-response proportional servo valve 10.2 and an A-B channel of the sixth directional valve 8.6 to flow into ｃA rod cavity of the second servo hydraulic cylinder 13.2, and simultaneously, the second energy accumulator 17.2 of the second energy storage unit releases stored high-pressure oil to flow into the second servo hydraulic cylinder 13.2 rod cavity through an A-P channel of the second plug-in the second electromagnetic ball valve 16.2, thereby driving the second servo hydraulic cylinder 13.2 to return quickly. Meanwhile, the hydraulic oil in the rodless cavity of the second servo hydraulic cylinder 13.2 flows back to the main oil return pipe T through a B-A channel of the fifth cartridge directional valve 8.5, a B-T channel of the second high-frequency response proportional servo valve 10.2 and an A-B channel of the third check one-way valve 4.3.

Furthermore, the first energy storage unit and the second energy storage unit are used for accelerating the return speed of the first servo hydraulic cylinder 13.1 and the second servo hydraulic cylinder 13.2, and the shearing efficiency is improved.

In the process of rolling shearing, when a piston rod of the servo hydraulic cylinder extends and moves and does not reach a target position, oil in a rodless cavity of the servo hydraulic cylinder recovers and stores energy through the energy storage unit; when a piston rod of the servo hydraulic cylinder extends and moves to a target position, the energy storage unit stops working; when a piston rod of the servo hydraulic cylinder returns, the energy storage unit releases the stored high-pressure oil to join with oil of the pump source together to enter a rodless cavity of the servo hydraulic cylinder to complete quick return, so that the shearing efficiency is improved.

Preferably, the rod chamber of the first servo hydraulic cylinder 13.1 is coupled to the tank via a first relief valve cartridge 15.1. Similarly, the rod cavity of the second servo hydraulic cylinder 13.2 is connected to the oil tank through a second cartridge overflow valve 15.2. This makes it possible to protect the first hydraulic actuator 13.1 and the second hydraulic actuator 13.2 from overload.

Furthermore, in order to make the operation of the supercharger more stable, a of the first supercharger 7.1 ₁Working oil cavity and first three-position four-way electromagnetic reversing valveA first check valve 6.1 is arranged between the oil ports A of the first three-position four-way electromagnetic directional valve 5.1, and the first check valve 6.1 allows oil to be conveyed to the oil port A of the first supercharger 7.1 from the oil port A of the first three-position four-way electromagnetic directional valve 5.1 ₁A working oil chamber; a of the first supercharger 7.1 ₂A fourth one-way valve 6.4 is arranged between the working oil cavity and an oil port B of the first three-position four-way electromagnetic reversing valve 5.1, and the fourth one-way valve 6.4 can prevent oil from flowing from A of the first supercharger 7.1 ₂The working oil cavity flows back to an oil port B of the first three-position four-way electromagnetic reversing valve 5.1; a of the first supercharger 7.1 ₁And A ₂A second check valve 6.2 and a third check valve 6.3 are respectively arranged between the working oil chamber and the rodless chamber of the first servo hydraulic cylinder 13.1, and the second check valve 6.2 and the third check valve 6.3 can prevent oil in the rodless chamber of the first servo hydraulic cylinder 13.1 from flowing back to the A of the first supercharger 7.1 ₁And A ₂And the working oil chamber. The same applies to the second hydraulic pressure booster circuit.

Preferably, a first check one-way valve 4.1 is installed between the oil port T of the first three-position four-way electromagnetic directional valve 5.1 and the oil return pipe T, and a second check one-way valve 4.2 is installed between the oil port T of the first high-frequency response proportional servo valve 10.1 and the oil return pipe T. Similarly, a fourth check one-way valve 4.4 is installed between the oil port T of the second three-position four-way electromagnetic directional valve 5.2 and the oil return pipe T, and a third check one-way valve 4.3 is installed between the oil port T of the second high-frequency response proportional servo valve 10.2 and the oil return pipe T.

Specifically, the first booster is composed of a large piston and two small pistons and is divided into A ₁、A ₂、A ₃And A ₄The effective acting area ratio of the large piston to the small piston is 10: 1. The second booster is composed of a large piston and two small pistons and is divided into A ₁、A ₂、A ₃And A ₄The effective acting area ratio of the large piston to the small piston is 10: 1.