Hydraulic control system and isothermal forging system

Abstract

This utility model discloses a hydraulic control system and an isothermal forging system, belonging to the field of isothermal forging technology. It includes an oil supply port, an oil return port, a first two-way cartridge directional valve, a first four-way directional valve, a high-pressure relief valve, a damper, a three-way cartridge pressure valve, and a low-pressure relief valve. The oil supply port is connected to the cylinder's plug cavity. The isothermal forging system includes an oil supply and return module, a cylinder with a replenishing oil circuit, and the aforementioned hydraulic control system. The oil supply end of the oil supply and return module is connected to the oil supply port of the hydraulic control system, and the oil return end of the oil supply and return module is connected to the oil return port of the hydraulic control system. The replenishing oil circuit is connected to the cylinder's plug cavity. By utilizing the combined use of the high-pressure relief valve and the damper, the opening and closing of the rapid oil release first two-way cartridge directional valve is controlled, effectively reducing pressure fluctuations during the transition from rapid to slow action at a relatively low cost.

Description

Technical Field

[0001] This utility model relates to the field of isothermal forging technology, and in particular to a hydraulic control system and an isothermal forging system. Background Technology

[0002] Isothermal forging is mainly used for precision forging of high-temperature alloys, titanium alloys, and other difficult-to-deform materials. However, during this forging process, the sudden change in speed from rapid to slow can cause significant pressure fluctuations in the hydraulic system, resulting in considerable noise and equipment vibration. Traditional buffer devices are either too costly or have unsatisfactory buffering effects. Utility Model Content

[0003] The purpose of this invention is to solve the above-mentioned technical problems and provide a hydraulic control system and an isothermal forging system. By using a high-pressure relief valve and a damper in combination, the opening and closing of the first two-way cartridge directional valve for rapid oil discharge is controlled, thereby reducing pressure fluctuations during the transition from rapid to slow action at a relatively low cost.

[0004] To achieve the above objectives, this utility model provides the following solution: This utility model discloses a hydraulic control system for controlling a hydraulic cylinder with a replenishing oil circuit. The replenishing oil circuit is connected to the cylinder's plug cavity and includes an oil supply port, an oil return port, a first two-way cartridge directional valve, a first four-way directional valve, a high-pressure relief valve, a damper, a three-way cartridge pressure valve, and a low-pressure relief valve. The oil supply port is connected to the cylinder's plug cavity. The A port of the first two-way cartridge directional valve, the A port of the three-way cartridge pressure valve, and the oil inlet of the damper are all connected to the cylinder's rod cavity. The B port of the first two-way cartridge directional valve is connected to the B1 port of the three-way cartridge pressure valve. The ports are connected as follows: the X port of the first two-way cartridge directional valve is connected to the A port of the first four-way directional valve; the P port of the first four-way directional valve is connected to the oil outlet of the damper; the oil inlet of the high-pressure relief valve is connected between the X port of the first two-way cartridge directional valve and the A port of the first four-way directional valve; the overflow end of the high-pressure relief valve is connected between the B port of the first two-way cartridge directional valve and the B1 port of the three-way cartridge pressure valve; the B2 port of the three-way cartridge pressure valve is connected to the oil return port; the X port of the three-way cartridge pressure valve is connected to the oil inlet of the low-pressure relief valve; and the oil outlet of the low-pressure relief valve is connected to the oil return port.

[0005] Preferably, it further includes a second two-way cartridge directional valve and a two-position three-way directional valve. The P port of the two-position three-way directional valve and the A port of the second two-way cartridge directional valve are both connected to the rod chamber of the cylinder. The A port of the two-position three-way directional valve is connected to the X port of the second two-way cartridge directional valve. The T port of the two-position three-way directional valve is connected to the return port. The A port of the first two-way cartridge directional valve, the A port of the three-way cartridge pressure valve, and the oil inlet of the damper are all connected to the B port of the second two-way cartridge directional valve.

[0006] Preferably, it also includes a safety relief valve, the oil inlet of which is connected between the rod chamber of the oil cylinder and the B port of the second two-way cartridge directional valve.

[0007] Preferably, the system further includes a second four-way directional valve, a third two-way cartridge directional valve, and a two-way valve. The A port of the third two-way cartridge directional valve is connected to the plug chamber of the cylinder. The B port of the third two-way cartridge directional valve is connected between the A ports of the first two-way cartridge directional valve and the A port of the second two-way cartridge directional valve. The X port of the third two-way cartridge directional valve is connected to the oil outlet of the two-way valve. The first oil inlet of the two-way valve is connected to the B port of the third two-way cartridge directional valve. The second oil inlet of the two-way valve is connected to the A port of the third two-way cartridge directional valve. The P port of the second four-way directional valve is connected to the plug chamber of the cylinder. The T port of the second four-way directional valve is connected to the oil return port.

[0008] Preferably, the first four-way directional valve, the second four-way directional valve, and the two-position three-way directional valve are all solenoid directional valves.

[0009] An isothermal forging system is also disclosed, including an oil supply and return module, a cylinder with a replenishing oil circuit, and the aforementioned hydraulic control system. The oil supply end of the oil supply and return module is connected to the oil supply port of the hydraulic control system, the oil return end of the oil supply and return module is connected to the oil return port of the hydraulic control system, and the replenishing oil circuit is connected to the plug cavity of the cylinder.

[0010] Preferably, the oil supply and return module includes an oil tank, a hydraulic pump unit, and a return pipeline. The oil inlet of the hydraulic pump unit is connected to the oil outlet of the oil tank. The oil supply port of the hydraulic control system and the oil return port of the oil tank are both connected to the oil outlet of the hydraulic pump unit. The oil return port of the hydraulic control system is connected to the oil return port of the oil tank.

[0011] Preferably, the oil supply and return module further includes a pump source pressure stabilizing module, which includes a one-way valve and a pump source relief valve. The oil inlet of the one-way valve is connected to the oil outlet of the hydraulic pump group. The oil supply port of the hydraulic control system and the oil return port of the oil tank are both connected to the oil outlet of the one-way valve. The oil inlet of the pump source relief valve is connected between the oil inlet of the one-way valve and the oil outlet of the hydraulic pump group. The oil outlet of the pump source relief valve is connected to the oil return port of the oil tank.

[0012] Preferably, it also includes a cylinder pressure stabilizing module, which includes a cylinder overflow valve. The oil inlet of the cylinder overflow valve is connected to the P port of the second four-way directional valve of the hydraulic control system.

[0013] Preferably, the oil replenishment line is equipped with a filling valve.

[0014] The present invention achieves the following technical advantages over the prior art:

[0015] In this invention, at the instant of transition from rapid to slow operation, when the system pressure exceeds the set value of the high-pressure relief valve, overflow occurs. Hydraulic oil flows through the damper, creating a pressure differential. Under the pressure differential, the valve core of the first two-way cartridge directional valve overcomes the spring force and opens to release pressure, effectively reducing pressure fluctuations at the moment of transition from rapid to slow operation. Furthermore, the throttle rod of the first two-way cartridge directional valve controls the opening size of the valve core, controlling the flow rate of the discharged oil, thereby controlling the speed of rapid oil discharge. By utilizing the combined use of the high-pressure relief valve and the damper to control the opening and closing of the first two-way cartridge directional valve for rapid oil discharge, pressure fluctuations at the moment of transition from rapid to slow operation can be effectively reduced. This method is low-cost, highly efficient, and reliable, reducing noise and equipment vibration, and extending equipment lifespan. Attached Figure Description

[0016] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained by analyzing these drawings without creative effort.

[0017] Figure 1 This is a schematic diagram of the isothermal forging system in an embodiment of this utility model;

[0018] Figure 2 This is a schematic diagram of the isothermal forging system during rapid operation in an embodiment of this utility model;

[0019] Figure 3 This is a schematic diagram of the isothermal forging system in the embodiment of this utility model during slow operation;

[0020] Figure 4 This is a schematic diagram of the isothermal forging system during rapid return in an embodiment of this utility model.

[0021] Explanation of reference numerals in the attached diagram: 1. Hydraulic cylinder; 2. Oil tank; 3. First two-way cartridge directional valve; 4. First four-way directional valve; 5. High-pressure relief valve; 6. Damping; 7. Three-way cartridge pressure valve; 8. Low-pressure relief valve; 9. Second two-way cartridge directional valve; 10. Two-position three-way directional valve; 11. Safety relief valve; 12. Third two-way cartridge directional valve; 13. Second four-way directional valve; 14. Two-way valve; 15. Hydraulic pump unit; 16. Filling valve. Detailed Implementation

[0022] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments analyzed and obtained by those skilled in the art without creative effort are within the protection scope of the present utility model.

[0023] The purpose of this invention is to provide a hydraulic control system and an isothermal forging system to solve the problems existing in the prior art. During the transition from rapid to slow speed, when the system pressure exceeds the set value of the high-pressure relief valve, overflow occurs. Hydraulic oil flows through the damper, generating a pressure difference. Under the action of this pressure difference, the valve core of the first two-way cartridge directional valve overcomes the spring force to open and release pressure, effectively reducing pressure fluctuations during the transition from rapid to slow speed. Furthermore, the throttle rod of the first two-way cartridge directional valve can control the opening size of the valve core, controlling the flow rate of the oil discharge, thereby controlling the speed of rapid oil discharge. By utilizing the combined use of the high-pressure relief valve and the damper to control the opening and closing of the first two-way cartridge directional valve for rapid oil discharge, pressure fluctuations during the transition from rapid to slow speed can be effectively reduced. This system is low-cost, highly efficient, and reliable, reducing noise and equipment vibration, and extending equipment lifespan. This system is low-cost, highly efficient, and reliable, and can be modularized, with a simple and compact structure and a reasonable design, meeting the functional requirements of each part.

[0024] To make the above-mentioned objectives, features and advantages of this utility model more apparent and understandable, the utility model will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0025] Example 1

[0026] like Figures 1 to 4As shown, this embodiment provides a hydraulic control system for controlling a cylinder 1 with a replenishing oil circuit, the replenishing oil circuit being connected to the plug cavity of the cylinder 1. This hydraulic control system includes an oil supply port, an oil return port, a first two-way cartridge directional valve 3, a first four-way directional valve 4, a high-pressure relief valve 5, a damper 6, a three-way cartridge pressure valve 7, and a low-pressure relief valve 8. The first four-way directional valve 4 can be a two-position four-way directional valve or a three-position four-way directional valve. The oil supply port is connected to the plug cavity of the cylinder 1. The A port of the first two-way cartridge directional valve 3, the A port of the three-way cartridge pressure valve 7, and the oil inlet of the damper 6 are all connected to the rod cavity of the cylinder 1. The B port of the first two-way cartridge directional valve 3 is connected to the B1 port of the three-way cartridge pressure valve 7, and the X port of the first two-way cartridge directional valve 3 is connected to the A port of the first four-way directional valve 4. The P port of the first four-way directional valve 4 is connected to the oil outlet of the damper 6. The inlet of the high-pressure relief valve 5 is connected between the X port of the first two-way cartridge directional valve 3 and the A port of the first four-way directional valve 4. The overflow end of the high-pressure relief valve 5 is connected between the B port of the first two-way cartridge directional valve 3 and the B1 port of the three-way cartridge pressure valve 7. The B2 port of the three-way cartridge pressure valve 7 is connected to the return port. The X port of the three-way cartridge pressure valve 7 is connected to the inlet of the low-pressure relief valve 8, and the outlet of the low-pressure relief valve 8 is connected to the return port.

[0027] Working principle:

[0028] Fast action phase:

[0029] Hydraulic oil enters through the supply port of the hydraulic control system, then enters the plug chamber of cylinder 1. The hydraulic oil in the rod chamber of cylinder 1 flows into port A of the first two-way cartridge directional valve 3. The first four-way directional valve 4 switches to the cross position, opening ports A and T. Oil drains from port X of the first two-way cartridge directional valve 3, opening ports A and B. The hydraulic oil then enters port B1 of the three-way cartridge pressure valve 7, opening port X. Oil drains from port B1 and B2 of the three-way cartridge pressure valve 7. The hydraulic oil flows out through the return port. Under negative pressure, the plug chamber of cylinder 1 is passively drawn in through the replenishment line 13, achieving rapid action. (Reference) Figure 2 As shown.

[0030] The instant when fast action transitions to slow action:

[0031] When the first four-way directional valve 4 switches to the parallel position, ports A and P of the first four-way directional valve 4 are open, but the direction of conduction of ports A and P is opposite to the direction of oil discharge from port X of the first two-way cartridge directional valve 3. Port X of the first two-way cartridge directional valve 3 no longer discharges oil. Since the system pressure is greater than the set value of the high-pressure relief valve 5 at this time, overflow will occur. The hydraulic oil flows through the damper 6 to generate a pressure difference. Under the action of the pressure difference, the valve core of the first two-way cartridge directional valve 3 overcomes the spring force and remains open. At this time, ports A and B of the first two-way cartridge directional valve 3 are still open, and pressure is discharged through ports B1 and B2 of the three-way cartridge pressure valve 7, effectively reducing the pressure fluctuation at the moment of rapid to slow speed transition. Moreover, the throttle rod at the first two-way cartridge directional valve 3 can control the opening size of the valve core, control the flow rate of oil discharge, thereby controlling the speed of rapid oil discharge and reducing noise. (Reference) Figure 3 As shown.

[0032] Slow motion moments:

[0033] During the transition from rapid to slow motion, after the system pressure stabilizes, the first two-way cartridge directional valve 3 closes, and ports A and B2 of the three-way cartridge pressure valve 7 open. Hydraulic oil from the rod chamber of cylinder 1 is released through ports A and B2 of the three-way cartridge pressure valve 7. The low-pressure relief valve 8 acts as a back pressure valve, supporting cylinder 1 and achieving slow motion. (Reference) Figure 3 As shown.

[0034] In one embodiment, the system further includes a second two-way cartridge directional valve 9 and a two-position three-way directional valve 10. The P port of the two-position three-way directional valve 10 and the A port of the second two-way cartridge directional valve 9 are both connected to the rod chamber of the cylinder 1. The A port of the two-position three-way directional valve 10 is connected to the X port of the second two-way cartridge directional valve 9. The T port of the two-position three-way directional valve 10 is connected to the return port. The A port of the first two-way cartridge directional valve 3, the A port of the three-way cartridge pressure valve 7, and the inlet end of the damper 6 are all connected to the B port of the second two-way cartridge directional valve 9. When ports A and T of the second two-way cartridge directional valve 9 are open, hydraulic oil from the rod chamber of cylinder 1 enters port B of the second two-way cartridge directional valve 9, opening the valve core and connecting ports B and A. Hydraulic oil flows out from port A of the second two-way cartridge directional valve 9 for subsequent rapid or slow actions. When ports A and P of the second two-way cartridge directional valve 9 are open, hydraulic oil from the rod chamber of cylinder 1 enters port X of the second two-way cartridge directional valve 9 through ports P and A. The valve core inside the second two-way cartridge directional valve 9 closes, preventing hydraulic oil from flowing out from ports B and A of the second two-way cartridge directional valve 9.

[0035] In one embodiment, a safety relief valve 11 is also included. The oil inlet of the safety relief valve 11 is connected between the rod chamber of the hydraulic cylinder 1 and the B port of the second two-way cartridge directional valve 9. The safety relief valve 11 serves as a safety protection function, preventing excessive pressure during workpiece pressing.

[0036] In one embodiment, the system further includes a third two-way cartridge directional valve 12, a second four-way directional valve 13, and a two-way valve 14. The A port of the third two-way cartridge directional valve 12 is connected to the plug cavity of the cylinder 1, and the B port of the third two-way cartridge directional valve 12 is connected between the A port of the first two-way cartridge directional valve 3 and the A port of the second two-way cartridge directional valve 9. The X port of the third two-way cartridge directional valve 12 is connected to the oil outlet of the two-way valve 14. The first oil inlet of the two-way valve 14 is connected to the B port of the third two-way cartridge directional valve 12, and the second oil inlet of the two-way valve 14 is connected to the A port of the third two-way cartridge directional valve 12. The P port of the second four-way directional valve 13 is connected to the plug cavity of the cylinder 1, and the T port of the second four-way directional valve 13 is connected to the return port.

[0037] Working principle:

[0038] Fast return phase:

[0039] When the second four-way directional valve 13 is switched to the cross position, the P port and A port of the second four-way directional valve 13 are open, which can control the opening of the third two-way cartridge directional valve 12. The hydraulic oil in the system enters the rod chamber of the cylinder 1 through the A port and B port of the third two-way cartridge directional valve 12 and the A port and B port of the second two-way cartridge directional valve 9. The hydraulic oil in the plug chamber of the cylinder 1 flows out through the replenishment oil circuit to achieve rapid return.

[0040] In one embodiment, the first four-way directional valve 4, the second four-way directional valve 13, and the two-position three-way directional valve 10 are all solenoid directional valves. When the first four-way directional valve 4 is energized, it switches to the cross position, with ports A and T connected, and ports B and P connected; when the first four-way directional valve 4 is de-energized, it switches to the parallel position, with ports A and P connected, and ports B and T connected. When the second four-way directional valve 13 is energized, it switches to the cross position, with ports A and T connected, and ports B and P connected; when the second four-way directional valve 13 is de-energized, it switches to the parallel position, with ports A and P connected, and ports B and T connected. When the two-position three-way directional valve 10 is energized, ports A and T are connected; when the two-position three-way directional valve 10 is de-energized, ports P and A are connected.

[0041] Example 2

[0042] like Figures 1 to 4As shown, this embodiment provides an isothermal forging system, including an oil supply and return module, a cylinder 1 with a replenishing oil circuit, and the hydraulic control system described in Embodiment 1. The oil supply end of the oil supply and return module is connected to the oil supply port of the hydraulic control system, and the oil return end of the oil supply and return module is connected to the oil return port of the hydraulic control system. The replenishing oil circuit is connected to the plug cavity of the cylinder 1. The working principle is the same as described in Embodiment 1, and will not be elaborated further here.

[0043] In one embodiment, the oil supply and return module includes an oil tank 2, a hydraulic pump assembly 15, and a return oil pipeline. The oil inlet of the hydraulic pump assembly 15 is connected to the oil outlet of the oil tank 2. The oil supply port of the hydraulic control system and the oil return port of the oil tank 2 are both connected to the oil outlet of the hydraulic pump assembly 15. The oil return port of the hydraulic control system is connected to the oil return port of the oil tank 2.

[0044] Working principle:

[0045] Initial stage:

[0046] When the hydraulic pump unit 15 starts, the first two-way cartridge directional valve 3, the second two-way cartridge directional valve 9, and the third two-way cartridge directional valve 12 are all closed (the solenoid valves are all de-energized). After the hydraulic pump unit 15 draws out the hydraulic oil from the oil tank 2, it sends it back to the oil tank 2 through the return oil line. The hydraulic oil undergoes an empty circulation, and the oil cylinder 1 is in a stationary state.

[0047] In one embodiment, the oil supply and return module further includes a pump source pressure stabilizing module, which includes a check valve and a pump source relief valve. The oil inlet of the check valve is connected to the oil outlet of the hydraulic pump group 15. The oil supply port of the hydraulic control system and the oil return port of the oil tank 2 are both connected to the oil outlet of the check valve. The oil inlet of the pump source relief valve is connected between the oil inlet of the check valve and the oil outlet of the hydraulic pump group 15. The oil outlet of the pump source relief valve is connected to the oil return port of the oil tank 2.

[0048] In one embodiment, a cylinder pressure stabilizing module is also included. The cylinder pressure stabilizing module includes a cylinder relief valve. The oil inlet of the cylinder relief valve is connected to the P port of the second four-way directional valve 13 of the hydraulic control system. The P port of the second four-way directional valve 13 is between the cylinder pressure stabilizing module and the A port of the third two-way cartridge directional valve 12.

[0049] In one embodiment, a filling valve 16 is provided on the oil replenishment line.

[0050] In one embodiment, the oil replenishment line is connected to the oil tank 2. Pressurized oil passes through the X port (control port) of the filling valve 16 to open the valve core of the filling valve 16, which can connect the plug cavity of the cylinder 1 to the oil tank 2, realizing oil replenishment (passive oil is drawn from the oil tank 2 during the rapid action phase) or oil return (the oil in the plug cavity of the cylinder 1 flows back to the oil tank 2 through the filling valve 16 during the rapid return phase).

[0051] This utility model uses specific examples to illustrate its principles and implementation methods. The above description of the embodiments is only for the purpose of helping to understand the method and core idea of ​​this utility model. At the same time, for those skilled in the art, there will be changes in the specific implementation methods and application scope based on the idea of ​​this utility model. In summary, the content of this specification should not be construed as a limitation of this utility model.

Claims

1. A hydraulic control system for controlling a hydraulic cylinder with a replenishing oil circuit, the replenishing oil circuit being connected to the cylinder's plug cavity, characterized in that, This includes an oil supply port, an oil return port, a first two-way cartridge directional valve, a first four-way directional valve, a high-pressure relief valve, a damper, a three-way cartridge pressure valve, and a low-pressure relief valve; the oil supply port is connected to the plug chamber of the cylinder; the A port of the first two-way cartridge directional valve, the A port of the three-way cartridge pressure valve, and the oil inlet of the damper are all connected to the rod chamber of the cylinder; the B port of the first two-way cartridge directional valve is connected to the B1 port of the three-way cartridge pressure valve; and the X port of the first two-way cartridge directional valve is connected to the A port of the first four-way directional valve. The P port of the first four-way directional valve is connected to the oil outlet of the damper; the oil inlet of the high-pressure relief valve is connected between the X port of the first two-way cartridge directional valve and the A port of the first four-way directional valve; the overflow end of the high-pressure relief valve is connected between the B port of the first two-way cartridge directional valve and the B1 port of the three-way cartridge pressure valve; the B2 port of the three-way cartridge pressure valve is connected to the oil return port; the X port of the three-way cartridge pressure valve is connected to the oil inlet of the low-pressure relief valve; and the oil outlet of the low-pressure relief valve is connected to the oil return port.

2. The hydraulic control system according to claim 1, characterized in that, It also includes a second two-way cartridge directional valve and a two-position three-way directional valve. The P port of the two-position three-way directional valve and the A port of the second two-way cartridge directional valve are both connected to the rod chamber of the cylinder. The A port of the two-position three-way directional valve is connected to the X port of the second two-way cartridge directional valve. The T port of the two-position three-way directional valve is connected to the return port. The A port of the first two-way cartridge directional valve, the A port of the three-way cartridge pressure valve, and the oil inlet of the damper are all connected to the B port of the second two-way cartridge directional valve.

3. The hydraulic control system according to claim 2, characterized in that, It also includes a safety relief valve, the oil inlet of which is connected between the rod chamber of the oil cylinder and the B port of the second two-way cartridge directional valve.

4. The hydraulic control system according to claim 2, characterized in that, It also includes a second four-way directional valve, a third two-way cartridge directional valve, and a two-way valve. The A port of the third two-way cartridge directional valve is connected to the plug chamber of the oil cylinder. The B port of the third two-way cartridge directional valve is connected between the A port of the first two-way cartridge directional valve and the A port of the second two-way cartridge directional valve. The X port of the third two-way cartridge directional valve is connected to the oil outlet of the two-way valve. The first oil inlet of the two-way valve is connected to the B port of the third two-way cartridge directional valve. The second oil inlet of the two-way valve is connected to the A port of the third two-way cartridge directional valve. The P port of the second four-way directional valve is connected to the plug chamber of the oil cylinder. The T port of the second four-way directional valve is connected to the oil return port.

5. The hydraulic control system according to claim 3, characterized in that, The first four-way directional valve, the second four-way directional valve, and the two-position three-way directional valve are all solenoid directional valves.

6. An isothermal forging system, characterized in that, The system includes an oil supply and return module, a cylinder with a replenishing oil circuit, and a hydraulic control system as described in any one of claims 1-5. The oil supply end of the oil supply and return module is connected to the oil supply port of the hydraulic control system, the oil return end of the oil supply and return module is connected to the oil return port of the hydraulic control system, and the replenishing oil circuit is connected to the plug cavity of the cylinder.

7. The isothermal forging system according to claim 6, characterized in that, The oil supply and return module includes an oil tank, a hydraulic pump unit, and a return pipeline. The oil inlet of the hydraulic pump unit is connected to the oil outlet of the oil tank. The oil supply port of the hydraulic control system and the oil return port of the oil tank are both connected to the oil outlet of the hydraulic pump unit. The oil return port of the hydraulic control system is connected to the oil return port of the oil tank.

8. The isothermal forging system according to claim 7, characterized in that, The oil supply and return module also includes a pump source pressure stabilizing module, which includes a check valve and a pump source relief valve. The oil inlet of the check valve is connected to the oil outlet of the hydraulic pump group. The oil supply port of the hydraulic control system and the oil return port of the oil tank are both connected to the oil outlet of the check valve. The oil inlet of the pump source relief valve is connected between the oil inlet of the check valve and the oil outlet of the hydraulic pump group. The oil outlet of the pump source relief valve is connected to the oil return port of the oil tank.

9. The isothermal forging system according to claim 6, characterized in that, It also includes a cylinder pressure stabilizing module, which includes a cylinder overflow valve. The oil inlet of the cylinder overflow valve is connected to the P port of the second four-way directional valve of the hydraulic control system.

10. The isothermal forging system according to claim 6, characterized in that, A filling valve is provided on the replenishment oil line.

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