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Analyzing Guillotine Shear Hydraulic System Failures

In the process of spiral welded pipe production, the next step involves cutting the end of the hot-rolled coil after it has gone through the uncoiler and straightener. The head and tail of the steel plate are often irregular in shape after hot rolling, as shown in Figure 1. It is necessary to align and weld the plate head and tail together after they are cut.

At present, the main cutting methods used are plate shearing and plasma cutting. Although plasma cutting has a slower cutting speed compared to plate shearing under the same plate width, most welded pipe units still prefer to use plate shearing.

There are two types of plate shearing: swing beam shearing and guillotine shearing. Guillotine shears have several advantages, including high cutting precision, high cutting force, and high cutting speed, which makes them widely used in spiral welded pipe production for large diameter pipes with thick walls.

Fig. 1 Schematic diagram of the head

Fig. 1 Schematic diagram of the head

1. Schematic diagram of braking-type plate shear system

Figure 3 shows the hydraulic schematic diagram of a guillotine shear. When the shear is not in use, the pump is idle and the electromagnet is not energized. To adjust the shearing angle, it is controlled by the reversing valve 5. Figure 2 illustrates the shearing process.

Fig. 2 Schematic diagram of presser foot cutting

Fig. 2 Schematic diagram of presser foot cutting

The directional valve 7 is powered on to activate the electromagnet Y4, which controls the presser foot hydraulic cylinders 13 and 14 to clamp the plate head or tail. The directional valve 4 controls the hydraulic cylinders 11 and 12 in series to perform the shearing action, and the directional valve 9 opens for oil return. The reversing valve 4 can also control the lifting of the cutting edge simultaneously. The specific sequence of electromagnet activation is shown in Table 1.

Table 1 The power on sequence of electromagnet

Shearing Y1 Y2 Y4 Y7 is powered on after 1 s delay
Lift Y1 Y3    
Shear angle+ Y1 Y5
Shear angle- Y1 Y6
  • 1 – Internal gear pump;
  • 2 – Motor;
  • 3 – Electromagnetic relief valve;
  • 4 – Electromagnetic directional valve;
  • 5 – Electromagnetic directional valve;
  • 6 – Hydraulic control check valve;
  • 7 – Electromagnetic directional valve;
  • 8 – Relief valve;
  • 9 – Electromagnetic ball valve;
  • 10 – Hydraulic control check valve;
  • 11 – Auxiliary shear cylinder;
  • 12 -Main shear cylinder;
  • 13 – Presser foot cylinder;
  • 14 – Presser foot cylinder
Fig. 3 Hydraulic schematic diagram of barking-type plate shear

Fig. 3 Hydraulic schematic diagram of guillotine shear

At present, the shear force estimation of plate shears usually uses the Nosari formula:


In the formula:

  • f – shear force;
  • σb – material strength limit;
  • ξx – elongation of the cut sheet;
  • h – sheet thickness;
  • α – blade angle;
  • z – bending force coefficient of the sheared part;
  • y – relative value of the lateral clearance of the front edge;
  • x – influence coefficient of the press.

According to the data, the values of ξx, z, y, and x are 0.25, 0.95, 0.083, and 7.7, respectively. Fig. 4 shows the quantitative analysis of σb, h, and α, which reveals that the strength limit and thickness of the plate are directly proportional to the shearing force F, while the angle of the blade’s incline is inversely proportional to the shearing force.

See also  Electric Shearing Machine

Based on this conclusion, the common faults in the main hydraulic system of this type of guillotine plate shear have been analyzed and summarized.

2. Problem analysis

2.1 No pressure in the system

To troubleshoot the issue, it is important to first determine if the motor is reversing and check for any damage to the coupling between the motor and the pump. If there is still no pressure after these two points have been ruled out, the fault of relief valve 3 can be suspected. The cause of the problem could be due to a blocked damping hole in the relief valve, or a stuck directional valve or severe leakage in the relief valve.

2.2 System pressure does not go up

Most faults are related to the valve. Internal leakage and a stuck valve core can prevent the system pressure from rising, and these issues can be resolved by controlling the corresponding solenoid valve one by one.

However, before troubleshooting the valve, it is important to check the system tank first. If there are a lot of bubbles in the oil tank, it indicates that the pump is not functioning properly. In this case, check the oil level in the tank first. If the hydraulic oil level is sufficient, inspect the plum blossom pad or nylon pin in the coupling for any damage. If these issues are ruled out, it can be concluded that the pump has been damaged. If there are iron and copper chips in the oil, it indicates that the pump and valve are severely worn and causing insufficient pressure.

This type of shear does not have a cooling system. If the operator fails to turn off the Y1 and Y3 electromagnets after work is completed, and if the motor is not turned off, a significant amount of heat will be generated in a short amount of time, causing the oil temperature to rise and degrade.

After troubleshooting the pump and valve, the sealing problem in the hydraulic cylinder can be directly identified, leading to a failure in system pressure.

Fig. 4 The relationship between the parameter and F

Fig. 4 The relationship between the parameter and F

2.3 Automatic falling of presser foot and scissors

Figure 5 depicts the structure of the presser foot in a plate shear. Due to its weight, the presser foot hydraulic cylinder has a tendency to fall. The schematic diagram helps to identify the reason for the falling of the presser foot hydraulic cylinder.

As shown in the diagram, the rod cavities of the hydraulic cylinders 13 and 14 are connected to the rod cavities of the hydraulic cylinder 12 and the solenoid valve 9. If the hydraulic cylinder 12 is functioning properly, the solenoid valve 9 should be the first point of consideration. If the solenoid valve 9 is removed, the oil in the rod cavities of the hydraulic cylinders 13 and 14 will be connected to the port B of the solenoid directional valve 4 and the control oil port of the hydraulic control check valve 10, which will result in leakage over time.

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To prevent leakage, the reversing valve 9 uses a seat valve structure. If the electromagnet Y7 is activated improperly or the seat valve sealing surface loses its sealing effect, the presser foot will fall again.

Another common cause of the presser foot falling is damage to the seals in the hydraulic cylinders 11 and 12.

Fig. 5 Presser foot mechanism of shearing machine

Fig. 5 Presser foot mechanism of shearing machine

Regarding the automatic falling of the cutting edge, as shown in Figure 3, the scissors are controlled by two hydraulic cylinders connected in series. The electromagnetic directional valves 4 and 5 control the different actions of the scissors. The rod diameter, cylinder diameter, and stroke of hydraulic cylinder 11 are 212 mm, 320 mm, and 185 mm, respectively. The rod diameter, cylinder diameter, and stroke of hydraulic cylinder 12 are 212 mm, 240 mm, and 185 mm, respectively. If the seals and joints of the two hydraulic cylinders leak, the cutting blade will fall automatically. Just like the presser foot, the electromagnetic ball valve 9 will also fall automatically.

Another possible cause of the automatic falling is the solenoid valve 5 and the hydraulic lock 6. If the O-ring on the hydraulic lock 6 is not installed correctly or the oil temperature becomes too high, the O-ring can get stuck in the hydraulic lock and block the oil circuit, preventing the hydraulic lock from closing properly. This will cause the oil in the two hydraulic cylinders to return to the oil tank through the electromagnetic directional valve 5 (“J-type function”), resulting in the falling of the cutter. The problem can be solved by replacing the “O” ring.

2.4 The cutting edge can not move the plate

It has been determined that the strength limit of the steel plate, the thickness of the steel plate, and the shear angle all play a role in the shearing process. For example, a 15.9mm thick X70 steel plate requires a pressure of approximately 12.5 MPa. However, in practice, it is common for the steel plate to fail to cut even when the pressure is adjusted to 15 MPa or 20 MPa and there is no oil leakage fault in the equipment. In these cases, it is necessary to identify the problem by examining the equipment structure.

Figure 4 shows that the shear force difference between a blade angle of 2.5° and 10° is nearly 5 times, so the failure of the shearing process is primarily due to the blade angle. During equipment operation, incorrect setting of the limit for the shearing hydraulic cylinder can result in the failure to reach the required angle for the shearing process, which can be resolved by adjusting the limit for the shearing hydraulic cylinder.

As shown in Figure 6, when cutting, the cutting edge often cuts first, but the presser foot cylinder does not press down, causing the steel plate to curl and fail to cut. The electromagnet Y2, which controls the shearing, and the electromagnet Y4, which controls the presser foot, are powered on at the same time, so the problem is not related to the power-on sequence.

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The speed of the shearing hydraulic cylinder 11 is v1=q/s11, and the speed of the presser foot hydraulic cylinder is v2=q/2/s13.

Among them, S11 is the piston area of hydraulic cylinder 11, with 0.08 m2.

S13 is the piston area of hydraulic cylinder 13, with 0.0095 m2, so v2 ≈ 4v1.

Therefore, in this system, the synchronization of shearing and presser foot can be adjusted by adjusting the direct acting relief valve 8.

Fig. 6 Schematic diagram of shear failure

Fig. 6 Schematic diagram of shear failure

The relief valve 8 serves two main purposes in the system. Firstly, it increases the oil return pressure to prevent the shearing cylinder from crawling. Secondly, it can be used to adjust the speed of the shearing and presser foot.

The flow characteristic equation is known as:


It can be determined that the flow g through relief valve 8 is proportional to the pressure difference △p between P and T.

When shearing, the pressure p12 at the joint of rod cavity of hydraulic cylinder 12 is greater than the sum of the pressure p1314 of rod cavity of two presser foot hydraulic cylinders 13 and 14.

Therefore, when the return oil flow g cannot be greater than or equal to p12 + p1314, p12 will exert a reaction force on the hydraulic cylinders 13 and 14 to slow down the pressing speed of the hydraulic cylinders 13 and 14, resulting in the failure shown in Figure 6.

At present, the pressure of relief valve 8 can be adjusted to alter the return oil flow (qT), resulting in the presser foot effect depicted in Figure 2.

As depicted in Figure 7, the shear hydraulic cylinder is secured to the rack through the steps on the cylinder.

When the step at point A becomes worn, similar to point B, the steel plate applies an upward force on the cutting edge, causing the hydraulic cylinder to move upwards due to the reaction of force.

Instantaneously, the angle of inclination of the blade increases and the shearing force decreases, which is a significant cause of the failure to shear the steel plate.

3. Conclusion

This article examines some flaws in the hydraulic system of a guillotine shear.

Based on recent years of operational experience, the faults of the equipment are frequently complex.

Mechanical faults often coincide with hydraulic faults, and hydraulic faults coincide with electrical faults.

However, by utilizing reference drawings, conducting on-site analysis, and establishing an equipment failure database, it is possible to quickly determine the source of equipment failure and ensure normal operation.

Fig. 7 Schematic diagram of shear hydraulic cylinder

Fig. 7 Schematic diagram of shear hydraulic cylinder

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