High-speed hydraulic machine with multi-stage tonnage and slider weight balance

Abstract

Main cylinders are symmetrically fixed in an upper cross beam, the lower end of a piston rod of each main cylinder is connected with the corresponding sliding block, an upper cavity of each main cylinder is connected with an upper oil tank through a prefill valve, each main cylinder comprises a composite cylinder located in the middle and piston cylinders located on the two sides, and each composite cylinder is connected with the corresponding sliding block through a prefill valve. A rapid cylinder is arranged in a piston rod of the composite cylinder, upper cavity oil ports of the piston cylinders on the two sides are both connected with a port C of the main cylinder control block, an upper cavity oil port of the composite cylinder is connected with a port D of the main cylinder control block, and a rapid cylinder oil inlet hole of the composite cylinder is connected with a port E of the main cylinder control block; lower cavity oil ports of the two piston cylinders and an F port of the main cylinder control block are connected with an inlet of a proportional flow valve YAB, and an outlet of the proportional flow valve YAB is connected with an oil tank; and a lower cavity oil port of the composite cylinder is connected with the energy accumulator through the energy accumulator control block. The hydraulic machine can conduct multi-tonnage switching, the return stroke force of the sliding block is reduced, and the idle stroke fast descending speed and the return stroke speed of the sliding block are improved.

Description

Technical Field

[0001] The utility model relates to a hydraulic press, in particular to a high-speed hydraulic press with multiple tonnages and balanced slider weight, belonging to the technical field of hydraulic machine tools. Background Art

[0002] Large tie-rod frame hydraulic presses are widely used in industries such as automobile sheet metal stamping. With the increasing automation level, traditional low-speed and low-power hydraulic presses can no longer meet the needs of modern industrial production. Especially in the field of hot stamping forming of high-strength steel plates, the fast-down and return speeds of hydraulic presses are required to reach 700 - 1000 mm / s. The hot stamping technology of high-strength steel plates is a new manufacturing process technology that combines traditional hot forging technology and cold stamping technology. Generally, high-strength boron alloy steel is used because trace amounts of boron elements in boron alloy steel can improve the hardenability of the steel plate.

[0003] The main process of processing boron steel using the hot forming process can be divided into two steps: putting the boron alloy steel into a heating furnace to fully transform the original microstructure of ferrite and pearlite into austenite, transferring the sheet metal into a mold with a cooling system, and fully transforming the matrix structure of austenite into lath martensite. Heating the high-strength steel plate (thin plate) to 900°C and deforming it at 700°C can obtain lath martensite, improving the strength and hardness of the steel plate. The temperature of the thin plate drops relatively quickly during the process from being taken out of the furnace to being sent into the mold of the hydraulic press, which requires the hydraulic press to have a high working speed.

[0004] To increase the return speed of the hydraulic press, the traditional method is to increase the number of oil pump motor sets and increase the return flow rate to increase the return speed. This will inevitably increase the installed power, increase energy consumption, increase the diameter of the cartridge valves for controlling the movement of the slider, and increase the manufacturing and use costs of the hydraulic press.

[0005] On the other hand, simply increasing the fast-down speed of the hydraulic press during the idle stroke will inevitably bring a series of problems, especially the problem of hydraulic shock. During the process of the slider moving downward at high speed and then stopping, the weight of the slider and the mold of the large-frame hydraulic press is relatively large, up to 30 - 50 T, and the high-speed inertia is very large. Suddenly stopping will cause a huge hydraulic shock, making the hydraulic press vibrate significantly. Long-term operation will cause the screws to loosen, the pipeline to burst, and even the displacement of the machine body. Summary of the Utility Model

[0006] The purpose of the utility model is to overcome the problems existing in the prior art and provide a high-speed hydraulic press with multiple tonnages and balanced slider weight, which can perform multi-tonnage switching, reduce the return force of the slider, and can greatly increase the fast-down speed and return speed of the hydraulic press slider without increasing the installed power.

[0007] To solve the above technical problems, a high-speed hydraulic press with multiple tonnages and balanced slider weights according to the utility model includes a machine body. An upper crossbeam is provided at the top of the machine body. Main cylinders are symmetrically fixed in the upper crossbeam. The lower ends of the piston rods of each main cylinder are respectively connected to a slider. The upper chambers of each main cylinder are respectively connected to an upper oil tank through a filling valve. The main cylinder includes a composite cylinder in the middle and piston cylinders on both sides. A quick cylinder is built in the piston rod of the composite cylinder. The upper chamber oil ports of the piston cylinders on both sides are connected to port C of the main cylinder control block. The upper chamber oil port of the composite cylinder is connected to port D of the main cylinder control block. The oil inlet hole of the quick cylinder of the composite cylinder is connected to port E of the main cylinder control block;

[0008] The lower chamber oil ports of the two piston cylinders and port F of the main cylinder control block are all connected to the inlet of a proportional flow valve YAB. The outlet of the proportional flow valve YAB is connected to the oil tank; The lower chamber oil port of the composite cylinder is connected to an accumulator through an accumulator control block.

[0009] Further, port D of the main cylinder control block is also connected to the inlet of a proportional flow valve YAA. The outlet of the proportional flow valve YAA is connected to the oil tank.

[0010] Further, a piston rod is provided in the inner cavity of the cylinder body of the composite cylinder. Main cylinder upper chamber oil ports communicating with the upper chamber of the cylinder body are provided on the upper circumference of the cylinder body. Main cylinder lower chamber oil ports communicating with the lower chamber of the cylinder body are provided on the lower circumference of the cylinder body. A filling valve installation port is provided at the upper end of the cylinder body. A filling chamber is provided below the filling valve installation port. A cylinder body diaphragm is provided between the filling chamber and the top of the piston rod. A plurality of axially penetrating diaphragm through holes are evenly provided on the cylinder body diaphragm;

[0011] A downwardly extending quick cylinder is provided at the center of the upper end face of the piston rod to the middle and lower part of the piston rod. A quick rod is provided in the quick cylinder. The upper part of the quick rod passes through and is sealed with a quick rod guide sleeve. The quick rod guide sleeve is installed in the step hole at the upper port of the quick cylinder. The upper end of the quick rod passes through the central hole of the cylinder body diaphragm;

[0012] A radially penetrating quick cylinder oil inlet hole is provided along the radius of the cylinder body diaphragm. The inner port of the quick cylinder oil inlet hole communicates with an annular oil groove on the outer circumference of the upper part of the quick rod. The annular oil groove is connected to the upper end of the central oil hole of the quick rod through a quick rod radial hole. The central oil hole of the quick rod extends downward to the outlet at the lower end face of the quick rod.

[0013] Compared with the prior art, the utility model has achieved the following beneficial effects: 1. It can meet the rapid pressing requirements of high-temperature metal thin plates. Without increasing the oil pump motor set, it can improve the quick downward speed and return speed of the slider and reduce energy consumption;

[0014] 2. Through the combination of the compound cylinder and the piston cylinder, various pressing pressures and pressing speeds can be achieved as needed;

[0015] 3. The compound cylinder can meet the installation requirements of the large-diameter filling valve. By setting the cylinder body diaphragm, the diaphragm through-hole on it, and the quick cylinder oil inlet hole, it can not only meet the oil injection of the quick cylinder but also meet the requirement of a large amount of liquid filling into the upper cavity of the main cylinder; when the tonnage and table of the hydraulic press are very small, the weight of the moving parts is very small, and the proportion of friction is relatively high, injecting a small flow of oil into the quick rod can push the piston rod to move quickly, which can overcome the defect that the empty-stroke fast-down speed of the slider is slow and has a large fluctuation range relying on the self-weight of the slider and the mold, and at the same time can overcome the adverse effect of the uncontrollable empty-stroke speed of the slider caused by other external factors;

[0016] 4. It can achieve the flexible acceleration and deceleration movement of the slider, so as to achieve the purpose of smooth acceleration at the beginning of the high-speed movement of the slider and smooth deceleration at the end, eliminating hydraulic shock; it can also overcome the rebound force of the nitrogen cylinder. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] The present invention will be further described in detail below in conjunction with the drawings and specific embodiments. The drawings are only provided for reference and illustration, and are not intended to limit the present invention.

[0018] Figure 1 It is the front view of the high-speed hydraulic press with multiple tonnages and balanced slider weight of the present invention;

[0019] Figure 2 It is the hydraulic schematic diagram of the present invention;

[0020] Figure 3 It is the front view of the first embodiment of the compound cylinder in the present invention;

[0021] Figure 4 It is Figure 3 the top view;

[0022] Figure 5 It is the front view of the second embodiment of the compound cylinder in the present invention;

[0023] In the figure: 1. Cylinder block; 1a. Oil port of the upper chamber of the main cylinder; 1b. Mounting port of the filling valve; 1c. Filling chamber; 1d. Transverse diaphragm of the cylinder block; 1e. Through hole of the diaphragm; 1f. Oil inlet hole of the quick cylinder; 1g. Oil port of the lower chamber of the main cylinder; 2. Piston rod; 2a. Oil port of the upper chamber of the center cylinder; 2b. Radial oil hole of the center cylinder; 2c. Oil port of the lower chamber of the center cylinder; 3. Piston rod seal sleeve; 4. Large lock nut; 5. Quick rod; 5a. Central oil hole of the quick rod; 6. Small lock nut; 7. Guide sleeve of the quick rod; 8. Compression nut; 9. Guide sleeve of the cylinder port; 10. Cylinder port flange; 11. Piston rod flange; 12. Center rod; 13. Guide sleeve of the center rod; 14. Cylinder block lock nut; 15. Upper crossbeam; 16. Piston cylinder; 17. Slide block; AC1. Accumulator. Detailed implementation manners

[0024] In the following description of the present invention, the orientation or positional relationship indicated by the terms "upper", "lower", "front", "rear", "left", "right", "inner", "outer", etc. is based on the orientation or positional relationship shown in the drawings, and is only for the convenience of describing the present invention and simplifying the description, rather than indicating that the device must have a specific orientation.

[0025] In order to make the technical means, creative features, achieved purposes and effects realized by the present invention easy to understand, the present invention will be further described below with reference to specific drawings.

[0026] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by those skilled in the technical field to which the present invention belongs. The terms used in the description of the present invention herein are only for the purpose of describing specific embodiments, and are not intended to limit the present invention.

[0027] As Figure 1 、 Figure 2 shown, the high-speed hydraulic press with multi-stage tonnage and balanced slide block weight of the present invention includes a machine body. An upper crossbeam 15 is provided at the top of the machine body. The main cylinder installed in the upper crossbeam 15 includes a composite cylinder in the middle and piston cylinders 16 symmetrically located on both sides. A quick cylinder is built in the piston rod of the composite cylinder. The lower ends of the piston rods of the composite cylinder and the two piston cylinders 16 are respectively connected to the slide block 17. The oil port of the upper chamber of the composite cylinder is connected to the upper oil tank through a filling valve DZ1, and the oil ports of the upper chambers of the two piston cylinders 16 are respectively connected to the upper oil tank through filling valves DZ2. The hydraulic control port of the filling valve DZ2 is connected to port A of the filling valve control block, and the hydraulic control port of the filling valve DZ1 is connected to port B of the filling valve control block. The pump source control block supplies pressure oil to the main cylinder control block and the filling valve control block.

[0028] The upper chamber oil ports of the two side piston cylinders 16 are both connected to port C of the main cylinder control block. The upper chamber oil port of the compound cylinder is connected to port D of the main cylinder control block. The oil inlet hole of the fast cylinder of the compound cylinder is connected to port E of the main cylinder control block. The lower chamber oil ports of the two piston cylinders and port F of the main cylinder control block are all connected to the inlet of the proportional flow valve YAB. The outlet of the proportional flow valve YAB is connected to the oil tank. The lower chamber oil port of the compound cylinder is connected to the accumulator AC1 through the accumulator control block.

[0029] The main oil cylinder driving the slider 17 to move adopts a three-cylinder combined structure, and a five-cylinder combined structure can also be adopted. The three-cylinder combination is: one compound cylinder with an internal fast cylinder in the middle, and two identical piston cylinders on both sides. The five-cylinder combination is: on the basis of the three-cylinder combination, two more identical piston cylinders are added. The working principle is described below with the three-cylinder combination as an example. The five-cylinder combination is similar and will not be elaborated.

[0030] The compound cylinder with an internal fast rod is installed in the middle of the upper crossbeam 15. During operation, the hydraulic oil first outputs from port E of the main cylinder control block and enters the fast cylinder. Since the diameter of the fast rod is relatively small, generally with a tonnage of 30 - 60T, the slider can obtain a relatively high empty stroke fast-down speed. For example, when the diameter of the fast rod d = φ120, two 125 + 125 double pumps can reach a working speed of 730 mm / s when pumping oil at 2000 r / min. Thus, the empty stroke fast-down speed of the slider can be accurately calculated according to the flow rate and the cross-sectional area of the fast rod, and the rotational speed of the servo motor can also be controlled during the start-up acceleration and deceleration stages of the slider for flexible control. Driving the slider to quickly descend during the empty stroke with a power oil source can overcome problems such as unstable empty stroke fast speed of the slider or failure to meet the design requirements caused by other influencing factors. When the slider quickly descends during the empty stroke, the upper chambers of the compound cylinder and the two piston cylinders are replenished with oil through the flushing valve.

[0031] An accumulator AC1 is connected to the lower chamber of the compound cylinder. The function of the accumulator AC1 is to provide a certain range of lifting force for the slider. The magnitude of the lifting force is generally appropriate to overcome the weight of the slider, acting as a balance cylinder for the weight of the slider. In this way, the return force of moving parts such as the slider can be reduced, the rod diameters of the two side piston cylinders can be increased, and the cross-sectional area of the annular surface of the return piston rod can be reduced, so as to increase the return speed without increasing the pump flow rate. When the slider quickly descends, the oil in the lower chamber of the middle cylinder is pressed into the accumulator AC1, and the pressure of the accumulator AC1 rises to a certain extent, playing a certain decelerating role. When the slider returns, the pressure oil enters the lower chambers of the two piston cylinders to push the slider to return. At the same time, the accumulator AC1 provides a certain lifting force for the compound cylinder. During the return process, the pressure oil in the accumulator AC1 is released, the pressure of the accumulator AC1 decreases, and the lifting force decreases, which can also play a certain role in decelerating the return when stopping at the upper dead center. The separate balance cylinder setting in the lower chamber of the middle cylinder can be omitted, saving manufacturing costs.

[0032] The accumulator control block is used to control the oil inlet and outlet of the accumulator, and at the same time set functions such as an oil safety overflow valve, an oil drain ball valve, a pressure sensor, etc., as well as an oil replenishing function.

[0033] To solve the problem of the slider quickly descending during the idle stroke and smoothly decelerating during the working stroke, a large-diameter proportional flow valve YAB is connected to the lower chambers of the two piston cylinders. During the fast descent, the oil discharge channel in the lower chamber can be infinitely reduced, enabling the slider to decelerate smoothly and eliminating hydraulic shock.

[0034] This hydraulic press also has the function of multi-stage tonnage conversion. As long as the different oil inlet sequences of the three main cylinders are controlled, different tonnages and working speeds can be obtained, further improving the working efficiency. For example:

[0035] Hydraulic oil enters the upper chamber of the compound cylinder from port D of the main cylinder control block, enabling a smaller tonnage and a larger speed. The upper chambers of the two side piston cylinders suck oil through the filling valves respectively.

[0036] Hydraulic oil enters the upper chambers of the two side piston cylinders from port C of the main cylinder control block, enabling an intermediate tonnage and an intermediate working speed. The upper chamber of the compound cylinder sucks oil through the filling valve.

[0037] Hydraulic oil enters the upper chambers of the two side piston cylinders from port C of the main cylinder control block, and at the same time enters the upper chamber of the compound cylinder from port D of the main cylinder control block. When all the filling valves are closed, the full tonnage and the third working speed, i.e., low speed, can be obtained.

[0038] The five-cylinder combination can obtain more tonnage and speed combinations, which will not be elaborated here.

[0039] Currently, nitrogen cylinders are usually used in automotive stamping dies. At the moment when the slider relieves pressure, the nitrogen cylinder rebounds upward and ejects at high speed, causing relatively large vibrations, rebounds, and knocking sounds of the slider. Therefore, to overcome the adverse effects of the rebound force of the nitrogen cylinder die, port D of the main cylinder control block is also connected to the inlet of the proportional flow valve YAA. The outlet of the proportional flow valve YAA is connected to the oil tank. The proportional flow valve YAA can control the slow release of the pressure in the intermediate cylinder to overcome the rebound force of the nitrogen cylinder. The nitrogen cylinder in a typical automotive stamping die is about 300 tons. Therefore, the tonnage of the intermediate cylinder can be set slightly larger than the total force of the nitrogen cylinder, and the proportional flow of the intermediate cylinder is set to offset this rebound force. The two side cylinders can relieve pressure quickly normally to eliminate these adverse effects.

[0040] In summary, the intermediate compound cylinder has four functions: a fast cylinder, a balance cylinder, a pressurizing cylinder, and an infinitely variable pressure relief cylinder for overcoming the rebound force of the nitrogen cylinder die.

[0041] Such as Figure 3 、 Figure 4As shown in the figure, the composite cylinder installed in the middle of the upper crossbeam includes a cylinder block 1. A cylinder block lock nut 14 is screwed onto the external thread on the upper part of the cylinder block 1 to fix the cylinder block 1 on the upper crossbeam. A piston rod 2 is arranged in the inner cavity of the cylinder block 1. A main cylinder lower cavity oil port 1g communicating with the lower cavity of the cylinder block is arranged on the lower circumference of the cylinder block 1. A filling valve installation port 1b is arranged at the upper end of the cylinder block. A filling cavity 1c is arranged below the filling valve installation port 1b. A main cylinder upper cavity oil port 1a communicating with the upper cavity of the cylinder block is arranged on the side wall of the filling cavity 1c. A cylinder block transverse partition 1d is arranged between the filling cavity 1c and the top of the piston rod 2. A plurality of axially penetrating partition through holes 1e are uniformly arranged on the cylinder block transverse partition 1d.

[0042] At the center of the upper end face of the piston rod 2, a quick cylinder extending downward to the middle and lower part of the piston rod 2 is arranged. A quick rod 5 is arranged in the quick cylinder. The upper part of the quick rod 5 passes through a quick rod guide sleeve 7 and is sealed with each other. The quick rod guide sleeve 7 is embedded in the step hole at the upper port of the quick cylinder. The upper external step of the quick rod guide sleeve 7 abuts against the lower part of a compression nut 8. The outer circumference of the compression nut 8 is screwed into the upper end screw hole of the piston rod 2.

[0043] A quick rod convex ring is arranged on the outer circumference of the upper part of the quick rod 5. The quick rod convex ring abuts against the lower part of the cylinder block transverse partition 1d. The upper end of the quick rod 5 passes through the central hole of the cylinder block transverse partition 1d, and a small lock nut 6 is screwed onto the upper end outer circumference. The bottom of the small lock nut 6 presses on the upper surface of the cylinder block transverse partition 1d to realize the axial fixation of the quick rod 5.

[0044] A radially penetrating quick cylinder oil inlet hole 1f is arranged along the radius of the cylinder block transverse partition 1d. The inner port of the quick cylinder oil inlet hole 1f communicates with the annular oil groove on the outer circumference of the upper part of the quick rod 5. The annular oil groove is connected to the upper end of a quick rod central oil hole 5a through a quick rod radial hole. The quick rod central oil hole 5a extends downward to the outlet at the lower end face of the quick rod 5.

[0045] A piston rod sealing section is arranged on the upper part of the piston rod 2 to cooperate with the inner wall of the cylinder block and be sealed with each other. An upper reduced diameter section of the piston rod is arranged above the piston rod sealing section. The outer peripheral space of the upper reduced diameter section of the piston rod forms the upper cavity of the main cylinder, and the lower part of the piston rod sealing section forms the lower cavity of the main cylinder. The lower part of the piston rod 2 passes through a cylinder mouth guide sleeve 9, and the cylinder mouth guide sleeve 9 is fixed in the lower port of the cylinder block.

[0046] A cylinder mouth flange 10 is fixed to the lower end face of the cylinder block by screws. The inner edge of the cylinder mouth flange 10 is sealed with the lower circumference of the piston rod 2. The upper inner stop of the cylinder mouth flange 10 presses on the lower external step of the cylinder mouth guide sleeve 9. A piston rod flange 11 is screwed onto the lower outer circumference of the piston rod 2. The piston rod flange 11 is connected to the slider through flange screws.

[0047] When the slider moves downward quickly in the idle stroke, oil is injected into the central oil hole 5a of the quick rod through the oil inlet hole 1f of the quick cylinder. The oil flows out from the lower end of the central oil hole 5a of the quick rod and enters the quick cylinder, and the quick cylinder pushes the piston rod 2 to move at high speed. Since the diameter of the quick rod is much smaller than the bore of the main cylinder, the hydraulic oil of the same flow rate first enters the quick rod 5 to push the piston rod 2 to move, which can obtain a higher movement speed, and the movement speed of the piston rod 2 can be accurately calculated based on the flow rate and the cross-sectional area of ​​the quick rod 5. With the servo pump, flexible acceleration and deceleration movement can also be achieved, so as to achieve the purpose of smooth acceleration of the slider at the beginning of high-speed movement and smooth deceleration at the end.

[0048] In this way, the slider is driven by power to achieve high-speed free travel and fast descent, which can overcome the adverse effects of other external factors. For example, when the guiding accuracy requirements are high, the guide rail gap is small and the friction resistance increases significantly, this fast cylinder can still achieve stable high-speed movement.

[0049] A cylinder body transverse partition 1d is provided in the cylinder body for installing the quick rod 5 and the quick cylinder oil inlet hole 1f. A large-diameter filling valve installation port 1b is provided at the upper end of the cylinder body for installing a large-diameter filling valve to solve the requirements of large-volume filling of the slider through the filling valve when the slider is in a high-speed idle stroke and large-flow oil replenishment through the filling valve when the slider is in a high-speed return stroke.

[0050] Four larger-diameter partition through holes 1e are processed on the upper part of the cylinder body transverse partition 1d to communicate with the upper cavity of the cylinder body to meet the demand for large flow.

[0051] The annular oil groove of the quick rod 5 is connected with the quick cylinder oil inlet hole 1f in the cylinder body diaphragm 1d, so that the quick rod 5 can be reliably connected with the quick cylinder oil inlet hole 1f when it rotates arbitrarily.

[0052] like Figure 5 As shown, in another embodiment of the composite cylinder, a piston rod upper diameter reduction section is provided on the upper part of the piston rod 2, and a piston rod sealing sleeve 3 is sleeved on the outer periphery of the piston rod upper diameter reduction section, and the inner wall of the piston rod sealing sleeve 3 is sealed with the outer periphery of the piston rod upper diameter reduction section through an O-ring, and the outer periphery of the piston rod sealing sleeve 3 matches and seals with the inner wall of the cylinder body; the bottom of the piston rod sealing sleeve 3 abuts against the outer step of the piston rod upper diameter reduction section, and a large lock nut 4 is pressed on the upper end of the piston rod sealing sleeve 3, and the large lock nut 4 is screwed on the outer periphery of the upper end external thread of the piston rod 2. The upper chamber oil port 1a of the master cylinder is located on the side wall of the cylinder body below the cylinder body diaphragm 1d.

[0053] At the center of the lower end face of the piston rod 2, there is a central cylinder extending upward. A central rod 12 is arranged in the central cylinder. A central rod sealing section is provided on the upper circumference of the central rod 12 to seal with the inner wall of the central cylinder. The lower end of the central rod 12 extends out of the central rod guide sleeve 13 and is sealed with each other. The outer circumference of the central rod guide sleeve 13 is screwed to the lower port of the central cylinder. An annular groove is provided on the outer circumference of the lower part of the piston rod 2. A split piston rod flange 11 is embedded in the annular groove. The piston rod flange 11 is fixed on the slider by screws.

[0054] On the lower circumference of the piston rod 2, there are respectively an upper cavity oil port 2a of the central cylinder and a lower cavity oil port 2c of the central cylinder. The lower cavity oil port 2c of the central cylinder is directly communicated with the lower cavity of the central cylinder along the radial direction. The upper cavity oil port 2a of the central cylinder is communicated with the axial oil hole of the central cylinder. The upper part of the axial oil hole of the central cylinder is directly communicated with the upper cavity of the central cylinder through the radial oil hole 2b of the central cylinder.

[0055] A small central cylinder is arranged at the end of the piston rod 2. The central rod 12 in the central cylinder can extend or retract relative to the piston rod 2, and can realize feeding or perform other process requirements.

[0056] When the slider moves down quickly: When moving down quickly, oil is first injected into the quick rod 5, the filling valve opens, the upper cavity of the main cylinder is refilled through the filling valve, the quick rod 5 does not move, and the oil entering the inner cavity of the quick cylinder of the piston rod 2 pushes the piston rod 2 to move quickly, realizing the high-speed idle stroke quick down movement of the slider.

[0057] When working and pressurizing: The filling valve is closed, there is back pressure in the lower cavity, the oil from the pump enters the upper cavity of the main cylinder, realizing the working and pressurizing of the slider. The quick rod 5 can be pressurized or not. When pressurizing, oil is injected into the upper cavity of the main cylinder and the quick rod 5 at the same time; when not pressurizing, the quick rod 5 does not receive oil, and a vacuum is formed in the inner cavity of the quick cylinder along with the movement of the piston rod 2 and the slider, and oil is supplemented by self-priming through the one-way valve.

[0058] The above is only the preferred and feasible embodiment of the present invention, which shows and describes the basic principles, main features and advantages of the present invention. It does not limit the patent protection scope of the present invention. Those skilled in the art should understand that the present invention is not limited by the above embodiments. Except for the above embodiments, without departing from the spirit and scope of the present invention, the present invention can also have other implementation manners. The present invention will also have various changes and improvements. All technical solutions formed by equivalent replacement or equivalent transformation fall within the protection scope required by the present invention. The protection scope required by the present invention is defined by the appended claims and their equivalents. The technical features not described in the present invention can be realized by or adopted the existing technology, and will not be elaborated here.

Claims

1. A high-speed hydraulic press with multi-level tonnage and balanced slider weight, comprising a body, an upper crossbeam is provided on the top of the body, master cylinders are symmetrically fixed in the upper crossbeam, the lower end of the piston rod of each master cylinder is respectively connected to the slider, and the upper chamber of each master cylinder is respectively connected to the upper oil tank through a filling valve, characterized in that: The master cylinder includes a composite cylinder located in the middle and piston cylinders located on both sides. A quick cylinder is built in the piston rod of the composite cylinder. The upper chamber oil ports of the piston cylinders on both sides are connected to the C port of the master cylinder control block. The upper chamber oil port of the composite cylinder is connected to the D port of the master cylinder control block. The quick cylinder oil inlet hole of the composite cylinder is connected to the E port of the master cylinder control block. The lower chamber oil ports of the two piston cylinders and the F port of the master cylinder control block are connected to the inlet of the proportional flow valve YAB, and the outlet of the proportional flow valve YAB is connected to the oil tank; the lower chamber oil port of the composite cylinder is connected to the accumulator through the accumulator control block.

2. The high-speed hydraulic press with multi-level tonnage and balanced slider weight according to claim 1, characterized in that: The D port of the master cylinder control block is also connected to the inlet of the proportional flow valve YAA, and the outlet of the proportional flow valve YAA is connected to the oil tank.

3. The high-speed hydraulic press with multi-level tonnage and balanced slider weight according to claim 1, characterized in that: The inner cavity of the composite cylinder is provided with a piston rod, the upper circumference of the cylinder is provided with a master cylinder upper cavity oil port communicating with the upper cavity of the cylinder, the lower circumference of the cylinder is provided with a master cylinder lower cavity oil port communicating with the lower cavity of the cylinder, the upper end of the cylinder is provided with a filling valve installation port, a filling cavity is provided below the filling valve installation port, a cylinder body diaphragm is provided between the filling cavity and the top of the piston rod, and a plurality of axially penetrating diaphragm through holes are evenly provided on the cylinder body diaphragm; The center of the upper end surface of the piston rod is provided with the quick cylinder extending downward to the middle and lower part of the piston rod, and the quick cylinder is provided with a quick rod, the upper part of the quick rod passes through the quick rod guide sleeve and is sealed with each other, the quick rod guide sleeve is embedded in the step hole of the upper port of the quick cylinder, and the upper end of the quick rod passes through the center hole of the cylinder body diaphragm; A radially penetrating quick cylinder oil inlet hole is provided along the radius of the cylinder body cross partition, the inner port of the quick cylinder oil inlet hole is communicated with the annular oil groove on the outer periphery of the upper part of the quick rod, the annular oil groove is connected with the upper end of the quick rod center oil hole through the quick rod radial hole, and the quick rod center oil hole extends downward to the lower end surface outlet of the quick rod.

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