A continuous flow amplifier and a hydraulic press

Abstract

The present invention discloses a continuous flow amplifier, which includes a first reversing valve, a first shuttle valve, a flow amplification cylinder and an oil supply circuit; a hydraulic cylinder is also disclosed, which includes a hydraulic cylinder, a pressure oil supply device and the continuous flow amplifier in the above. The beneficial effects achieved by the present invention: It has the advantages of good sealing performance, reduces the leakage of hydraulic oil, has small overall energy loss, effectively reduces energy consumption, improves the sealing performance, can select hydraulic system components with a lower sealing grade and lower price, thereby can further reduce the manufacturing cost, reduces the probability of failure, and further improves the reliability. It realizes a variety of different working states, can adapt to different working states, meets different usage requirements, and plays a role in improving the applicability and production efficiency. It realizes the effect of increasing the output flow, and achieves the advantages of high efficiency, good sealing performance, stable reliability and low cost.

Description

Technical Field

[0001] The present invention relates to the technical field of flow amplifiers, and particularly relates to a continuous flow amplifier and a hydraulic press. Background Art

[0002] In the field of hydraulic transmission, in order to improve work efficiency, the actuator usually needs to move quickly under no-load or low-load conditions, such as the common fast return action and large-stroke low-pressure pressurization action of large hydraulic presses. In order to meet the large flow demand of the system for a relatively long period of time, the common solutions usually adopted are to configure hydraulic pumps with larger displacement or more pumps, configure a large number of accumulators, and use a supercharger for reverse pressurization, etc., which will result in a high cost of the hydraulic system. It takes a certain amount of time for the accumulator to be filled with pressurized oil, and the time for the accumulator to release pressurized oil is short and the process is uncontrollable. Additional throttling measures are required to control the flow, and throttling causes energy loss in the system. Due to stroke limitations, the reverse pressurization of the supercharger can only meet the supply of a small section of low-pressure large-flow hydraulic oil. Therefore, how to meet the low-pressure large-flow working conditions of the system at low cost, continuously and efficiently is of great significance for reducing costs, increasing efficiency and saving energy.

[0003] The Chinese invention patent with the publication number CN102588578B discloses a hydraulic control system for a transmission with increased flow, which includes a main pump driven by an engine and an auxiliary pump driven by an electric motor. The pump driven by the engine is used to provide a first supply of hydraulic fluid; the pump driven by the electric motor is used to provide a second supply of hydraulic fluid. A first check valve, the first check valve is arranged to be in fluid communication with the pump driven by the engine downstream and is configured to allow the first supply of the hydraulic fluid to flow through the first check valve from the pump driven by the engine; a second check valve, the second check valve is arranged to be in fluid communication with the pump driven by the electric motor downstream and is configured to allow the second supply of the hydraulic fluid to flow through the second check valve from the pump driven by the electric motor. By controlling the main pump driven by the engine and the auxiliary pump driven by the electric motor to work respectively, the function of adjusting the flow of the hydraulic system is realized, and the effect of increasing the flow is achieved. Although the effect of increasing the flow is achieved by increasing the pump and the motor, additional sealing parts need to be added after adding the pump and the motor, resulting in an increase in manufacturing cost and the sealing performance will also be affected. Therefore, the prior art requires a flow amplification device with high efficiency, good sealing performance, stable reliability and low cost. Summary of the Invention

[0004] To solve the above technical problems, the object of the present invention is to provide a continuous flow amplifier, which includes a first reversing valve, a first shuttle valve, a flow amplification cylinder and an oil supply circuit, and also provides a hydraulic cylinder, which includes a hydraulic cylinder, a pressure oil supply device and the continuous flow amplifier described above. This continuous flow amplifier has the advantages of high efficiency, good sealing performance, stability and reliability, and low cost.

[0005] To achieve the above object of the invention, the technical solutions adopted by the present invention are as follows:

[0006] A continuous flow amplifier includes a first reversing valve and a first shuttle valve, and also includes a flow amplification cylinder and an oil supply circuit. The flow amplification cylinder includes a housing, a first driving rod, a second driving rod and a driven piston. A first oil chamber, a second oil chamber, a third oil chamber and a fourth oil chamber are provided in the housing. The driven piston is fixedly connected to the first driving rod and the second driving rod respectively. The first driving rod, the second driving rod and the driven piston are slidably installed in the housing. The second oil chamber and the third oil chamber are respectively located on both sides of the sliding direction of the driven piston. The first driving rod extends into the first oil chamber, and the second driving rod extends into the fourth oil chamber. The first oil chamber and the fourth oil chamber are respectively communicated with the first reversing valve. The oil supply circuit is respectively communicated with the second oil chamber and the third oil chamber. The second oil chamber and the third oil chamber are respectively communicated with two oil inlets of the first shuttle valve. The first reversing valve is provided with a pressure oil connection end, and the first shuttle valve is provided with an oil outlet end. Through such a setting: hydraulic oil flows into the first oil chamber through the pressure oil connection end and the reversing valve. The hydraulic oil in the first oil chamber pushes the first driving rod to move. The first driving rod drives the driven piston and the second driving rod to move away from the first oil chamber. During the movement of the driven piston, the hydraulic oil in the third oil chamber is pushed out through the first shuttle valve and the oil outlet end. The effect of increasing the output flow is achieved, and the advantages of high efficiency, good sealing performance, stability and reliability, and low cost are achieved.

[0007] Preferably, the first oil chamber and the second oil chamber are respectively communicated with the first shuttle valve. A first valve is provided between the first oil chamber and the first shuttle valve, and a second valve is provided between the fourth oil chamber and the first shuttle valve. A first one-way valve is provided between the first oil chamber and the first reversing valve, and a second one-way valve is provided between the fourth oil chamber and the first reversing valve. Through such a setting: the hydraulic oil in the first oil chamber and the fourth oil chamber can flow to the first shuttle valve, improving the flow rate at the oil outlet end and achieving the effect of amplifying the flow rate of the hydraulic oil.

[0008] Preferably, both the first valve and the second valve are liquid-controlled valves. The control end of the first valve is communicated with the fourth oil chamber, and the control end of the second valve is communicated with the first oil chamber. Through such a setting: the function of automatically controlling the opening and closing of the first valve and the second valve according to the pressure oil in the first oil chamber and the second oil chamber is realized.

[0009] Preferably, a first pressing element and a second pressing element are fixedly installed on the housing. The first pressing element is located in the first oil chamber and abuts against the first driving rod, and the second pressing element is located in the fourth oil chamber and abuts against the second driving rod. The first pressing element and the second pressing element are respectively connected to the first reversing valve. With such a setting, the function that the continuous flow amplifier can automatically and continuously amplify the flow rate is realized, achieving the effects of convenient use and improved efficiency.

[0010] Preferably, a third check valve and a fourth check valve are provided in the oil supply circuit. The two ends of the third check valve are respectively communicated with the oil supply circuit and the second oil chamber, and the two ends of the fourth check valve are respectively communicated with the oil supply circuit and the third oil chamber. With such a setting, the stability of the hydraulic oil flow rate at the oil outlet end is ensured.

[0011] Preferably, a first overflow valve is communicated with the first oil chamber, and a second overflow valve is communicated with the fourth oil chamber. Both the first overflow valve and the second overflow valve are communicated with the oil supply circuit. With such a setting, the hydraulic oil pressure in the first oil chamber and the second oil chamber is prevented from being too high, playing a role in improving safety and the reliability of the hydraulic system.

[0012] Preferably, the first reversing valve is provided with an oil return end, and the oil return end is communicated with the oil supply circuit. With such a setting, it is prevented that the oil pressures in the first oil chamber and the fourth oil chamber are equal, resulting in the inability of the hydraulic oil to push the first driving rod, the second driving rod, and the driven piston to move, and it can also prevent the oil pressures at the two oil inlets of the first shuttle valve from being equal, playing a role in improving the reliability of the equipment operation.

[0013] A hydraulic press includes a hydraulic cylinder and a pressure oil supply device, and also includes the continuous flow amplifier described above. The pressure oil connection end of the continuous flow amplifier is communicated with the pressure oil supply device, and the oil outlet end of the continuous flow amplifier is communicated with the hydraulic cylinder. With such a setting, the hydraulic cylinder is driven to move quickly, achieving the effect of improving the working efficiency of the hydraulic press.

[0014] Preferably, a second reversing valve and a second shuttle valve are further included. The second reversing valve is arranged on the pipeline between the continuous flow amplifier and the pressure oil supply device, and the second shuttle valve is arranged on the pipeline between the continuous flow amplifier and the hydraulic cylinder. The two oil inlets of the second shuttle valve are respectively communicated with the oil outlet end of the continuous flow amplifier and the second reversing valve. The pressure oil supply device is communicated with a hydraulic oil tank, and the second reversing valve is communicated with the hydraulic oil tank. With such a setting, the working efficiency is improved, having the advantage of high applicability.

[0015] Preferably, it further includes a third reversing valve, which is arranged on the pipeline between the continuous flow amplifier and the hydraulic cylinder. Through such a setting, multiple different working states are achieved, which can adapt to different working states, meet different usage requirements, and play a role in improving applicability and production efficiency.

[0016] Compared with the prior art, the present invention has achieved beneficial technical effects:

[0017] 1. When the continuous flow amplifier is working normally, there is no throttling loss and overflow loss. Moreover, the check valve and the first shuttle valve can adopt conical valve cores, which have the advantage of good sealing performance, reducing the leakage of hydraulic oil. Therefore, the overall energy loss is small, achieving the advantage of high energy efficiency and effectively reducing energy consumption.

[0018] 2. It realizes automatic continuous flow amplification, enabling the hydraulic system not to require additional accumulators, pumps, motors, and equipment for increasing flow through differential connection. This makes the layout structure of the hydraulic system simpler, effectively reducing the manufacturing cost while meeting the usage requirements, and can also reduce the probability of hydraulic oil leakage, achieving the effect of improving sealing performance.

[0019] 3. Since there is no need to equip additional devices such as accumulators, pumps, and motors, it helps to control the pressure of hydraulic oil. Therefore, the internal pressure of the hydraulic system is also small. As a result, in the design and manufacturing, the hydraulic system does not need to be designed with a too high sealing level. While facilitating the design and manufacturing, it is also possible to select hydraulic system components with a lower sealing level and a lower price, thereby further reducing the manufacturing cost.

[0020] 4. Due to the small internal pressure of the hydraulic system, the continuous flow amplifier has very high reliability during the working process. The switching of the connection state of the first reversing valve is directly controlled by the first pressing element and the second pressing element, effectively reducing the complexity of the system and further reducing the probability of failure, thereby further improving the reliability.

[0021] 5. Combining the continuous flow amplifier, the second reversing valve, and the third reversing valve enables the hydraulic press to switch between 5 different working states. Thus, multiple different working states are achieved, which can adapt to different working states, meet different usage requirements, and play a role in improving applicability and production efficiency. Description of the Drawings

[0022] Figure 1 is a schematic structural diagram of a continuous flow amplifier in Embodiment 1 of the present invention when the first reversing valve supplies pressure oil to the first oil chamber;

[0023] Figure 2 is a schematic structural diagram of a continuous flow amplifier in Embodiment 1 of the present invention when the first reversing valve supplies pressure oil to the fourth oil chamber;

[0024] Figure 3 It is a schematic structural diagram of a hydraulic press in Embodiment 2 of the present invention;

[0025] Figure 4 It is a schematic structural diagram of a hydraulic press in Embodiment 3 of the present invention;

[0026] Figure 5 It is a schematic structural diagram of a hydraulic press in Embodiment 4 of the present invention.

[0027] Among them, the technical features represented by each reference numeral are as follows:

[0028] 10. Continuous flow amplifier; 11. First reversing valve; 12. Pressure oil connection end; 13. First pressing element; 14. Second pressing element; 15. Oil return end; 16. First shuttle valve; 17. Oil outlet end; 21. Flow amplification cylinder; 22. Housing; 23. First driving rod; 24. Second driving rod; 25. Driven piston; 26. First oil chamber; 27. Second oil chamber; 28. Third oil chamber; 29. Fourth oil chamber; 31. First valve; 32. Second valve; 33. First check valve; 34. Second check valve; 35. First relief valve; 36. Second relief valve; 41. Oil supply line; 42. Third check valve; 43. Fourth check valve; 44. Tank connection end; 51. Hydraulic cylinder; 52. Second reversing valve; 53. Second shuttle valve; 54. Third reversing valve; 55. Slide block; 56. Fixed block; 57. Hydraulic pump; 58. Safety valve; 59. Hydraulic oil tank. Specific embodiments

[0029] In order to make the objectives, technical solutions and advantages of the present invention clearer and more understandable, the present invention will be further described in detail below with reference to embodiments. However, the scope of protection required by the present invention is not limited to the specific embodiments described below.

[0030] Embodiment 1:

[0031] Refer to Figure 1 and Figure 2 , a continuous flow amplifier 10, comprising a first reversing valve 11, a first shuttle valve 16, a flow amplification cylinder 21 and an oil supply line 41.

[0032] The flow amplification cylinder 21 includes a housing 22, a first driving rod 23, a second driving rod 24 and a driven piston 25. A first oil chamber 26, a second oil chamber 27, a third oil chamber 28 and a fourth oil chamber 29 are provided inside the housing 22. The driven piston 25 is fixedly connected to the first driving rod 23 and the second driving rod 24 respectively. The first driving rod 23, the second driving rod 24 and the driven piston 25 are slidably installed inside the housing 22. The second oil chamber 27 and the third oil chamber 28 are respectively located on both sides of the sliding direction of the driven piston 25. The diameters of the first driving rod 23 and the second driving rod 24 are the same. The first driving rod 23 extends into the first oil chamber 26, and the second driving rod 24 extends into the fourth oil chamber 29. The first driving rod 23 blocks the gap between the first oil chamber 26 and the second oil chamber 27, the second driving rod 24 blocks the gap between the third oil chamber 28 and the fourth oil chamber 29, and the driven piston 25 blocks the gap between the second oil chamber 27 and the third oil chamber 28, so that the first oil chamber 26, the second oil chamber 27, the third oil chamber 28 and the fourth oil chamber 29 are sealed from each other. The cross-sectional area of the first driving rod 23 is smaller than the difference between the cross-sectional area of the driven piston 25 and the cross-sectional area of the second driving rod 24. The cross-sectional area of the second driving rod 24 is smaller than the difference between the cross-sectional area of the driven piston 25 and the cross-sectional area of the first driving rod 23.

[0033] The first oil chamber 26 and the fourth oil chamber 29 are respectively connected to the first reversing valve 11. The first reversing valve 11 is provided with a pressure oil connection end 12 and an oil return end 15. The first reversing valve 11 can adopt an electromagnetic reversing valve or a hydraulic control reversing valve. In this embodiment, the first reversing valve 11 is a two-position four-way electromagnetic reversing valve. The first reversing valve 11 is provided with 4 interfaces, namely port a, port b, port p and port t. Port a is connected to the first oil chamber 26, port b is connected to the fourth oil chamber 29, port p is connected to the pressure oil connection end 12, and port t is connected to the oil return end 15. The housing 22 is fixedly installed with a first pressing element 13 and a second pressing element 14. The first pressing element 13 is located inside the first oil chamber 26 and abuts against the first driving rod 23. The second pressing element 14 is located inside the fourth oil chamber 29 and abuts against the second driving rod 24. The first pressing element 13 and the second pressing element 14 are respectively connected to the first reversing valve 11. Both the first pressing element 13 and the second pressing element 14 adopt travel switches, and the first pressing element 13 and the second pressing element 14 are respectively electrically connected to the first reversing valve 11.

[0034] The second oil chamber 27 and the third oil chamber 28 are respectively connected to two oil inlets of the first shuttle valve 16. The oil supply circuit 41 is provided with a third check valve 42 and a fourth check valve 43. Both ends of the third check valve 42 are respectively connected to the oil supply circuit 41 and the second oil chamber 27. Both ends of the fourth check valve 43 are respectively connected to the oil supply circuit 41 and the third oil chamber 28. The first shuttle valve 16 is provided with an oil outlet end 17.

[0035] The oil supply circuit 41 is respectively connected to the second oil chamber 27 and the third oil chamber 28. The first oil chamber 26 and the second oil chamber 27 are respectively connected to the first shuttle valve 16. A first valve 31 is provided between the first oil chamber 26 and the first shuttle valve 16, and a second valve 32 is provided between the fourth oil chamber 29 and the first shuttle valve 16. A first check valve 33 is provided between the first oil chamber 26 and the first reversing valve 11, and a second check valve 34 is provided between the fourth oil chamber 29 and the first reversing valve 11. Both the first valve 31 and the second valve 32 are hydraulically controlled valves. The control end of the first valve 31 is connected to the fourth oil chamber 29, and the control end of the second valve 32 is connected to the first oil chamber 26. A first relief valve 35 is connected to the first oil chamber 26, and a second relief valve 36 is connected to the fourth oil chamber 29. Both the first relief valve 35 and the second relief valve 36 are connected to the oil supply circuit 41. The oil supply circuit 41 is provided with a fuel tank connection end 44, and the oil return end 15 is connected to the oil supply circuit 41.

[0036] Specific working process:

[0037] In the initial state, the p port is connected to the a port, and the t port is connected to the b port. The first valve 31 and the second valve 32 are closed. The hydraulic oil with a relatively large pressure flows into the first oil chamber 26 through the pressure oil connection end 12, the p port, the a port, and the first check valve 33. The pressure of the hydraulic oil in the first oil chamber 26 pushes the first driving rod 23 to drive the driven piston 25 and the second driving rod 24 to move away from the first oil chamber 26. During the movement of the driven piston 25 and the second driving rod 24, they respectively push the hydraulic oil in the third oil chamber 28 and the fourth oil chamber 29, so that the hydraulic oil in the third oil chamber 28 can flow to the first shuttle valve 16. When the hydraulic oil with a relatively large pressure is introduced into the first oil chamber 26, the hydraulic oil is introduced into the control end of the second valve 32 to open the second valve 32. And through the setting of the second check valve 34, the hydraulic oil in the fourth oil chamber 29 is pushed out by the second driving rod 24 and flows into the first shuttle valve 16 through the second valve 32. Thus, the hydraulic oil is discharged through the first shuttle valve 16 and the oil outlet end 17, realizing the function of increasing the output flow rate of the hydraulic oil. While the driven piston 25 is moving, it sucks in hydraulic oil through the oil supply circuit 41 and the fuel tank connection end 44.

[0038] When the first driving rod 23 drives the second driving rod 24 to move and the second driving rod 24 presses the second pressing element 14, the first reversing valve 11 is triggered to switch to the state where the p port is communicated with the b port, and the t port is communicated with the b port. The second valve 32 is closed because the control end loses the pressure oil. The hydraulic oil with a relatively large pressure flows into the fourth oil chamber 29 through the pressure oil connection end 12, the p port, the b port and the second one-way valve 34. The pressure of the hydraulic oil in the fourth oil chamber 29 pushes the second driving rod 24 to drive the driven piston 25 and the first driving rod 23 to move away from the fourth oil chamber 29. During the movement of the driven piston 25 and the first driving rod 23, they respectively push the hydraulic oil in the second oil chamber 27 and the first oil chamber 26, so that the hydraulic oil in the third oil chamber 28 can flow to the first shuttle valve 16. When the hydraulic oil with a relatively large pressure is introduced into the fourth oil chamber 29, the hydraulic oil is introduced into the control end of the first valve 31, causing the first valve 31 to open. And through the setting of the first one-way valve 33, the hydraulic oil in the fourth oil chamber 29 is pushed out by the first driving rod 23 and flows into the first shuttle valve 16 through the first valve 31, so that the hydraulic oil is discharged through the first shuttle valve 16 and the oil outlet end 17, realizing the function of increasing the output flow rate of the hydraulic oil. While the driven piston 25 is moving, it sucks the hydraulic oil through the oil supply oil path 41 and the fuel tank connection end 44.

[0039] When the second driving rod 24 drives the first driving rod 23 to move and the first driving rod 23 presses the first pressing element 13, the first reversing valve 11 is triggered to switch to the state where the p port is communicated with the a port, and the t port is communicated with the b port. The first valve 31 is closed because the control end loses the pressure oil. When the hydraulic oil with a relatively large pressure is introduced into the fourth oil chamber 29, the hydraulic oil is introduced into the control end of the first valve 31, causing the first valve 31 to open. Thus, the continuous cyclic operation of the flow amplifier is realized.

[0040] The flow amplification factor k of the continuous flow amplifier 10 is k = Q 2 / Q 1 = D 2 / d 2 . Where Q 2 is the flow rate of the oil outlet end 17, Q 1 is the flow rate of the pressure oil connection end 12, D is the diameter of the driven piston 25, and d is the diameter of the first driving rod 23 and the second driving rod 24.

[0041] This embodiment has the following advantages:

[0042] The hydraulic oil flows into the first oil chamber 26 through the pressure oil connection end 12 and the first reversing valve 11. The hydraulic oil in the first oil chamber 26 pushes the first driving rod 23 to move. The first driving rod 23 drives the driven piston 25 and the second driving rod 24 to move away from the first oil chamber 26. During the movement of the driven piston 25, it pushes the hydraulic oil in the third oil chamber 28 to be discharged through the first shuttle valve 16 and the oil outlet end 17. Since the cross-sectional area of the first driving rod 23 is smaller than the difference between the cross-sectional area of the driven piston 25 and the cross-sectional area of the second driving rod 24, the flow rate of the hydraulic oil discharged from the third oil chamber 28 is greater than the flow rate of the hydraulic oil entering the first oil chamber 26, realizing the function of increasing the flow rate.

[0043] Then, switch the connection state of the first reversing valve 11 to make the hydraulic oil flow into the second oil chamber 27 through the pressure oil connection end 12 and the first reversing valve 11. The hydraulic oil in the second oil chamber 27 pushes the second driving rod 24 to move. The second driving rod 24 drives the driven piston 25 and the first driving rod 23 to move away from the second oil chamber 27. During the movement of the driven piston 25, it pushes the hydraulic oil in the second oil chamber 27 to be discharged through the first shuttle valve 16 and the oil outlet end 17. Since the cross-sectional area of the second driving rod 24 is smaller than the difference between the cross-sectional area of the driven piston 25 and the cross-sectional area of the first driving rod 23, the flow rate of the hydraulic oil discharged from the second oil chamber 27 is greater than the flow rate of the hydraulic oil entering the second oil chamber 27, realizing the function of increasing the flow rate.

[0044] During the process that the driven piston 25 pushes the hydraulic oil in the third oil chamber 28 to flow to the first shuttle valve 16, the volume of the second oil chamber 27 increases and sucks in hydraulic oil through the oil supply line 41. Then, switch the connection state of the first reversing valve 11 to make the driven piston 25 move in the reverse direction and push the hydraulic oil in the second oil chamber 27 to flow to the first shuttle valve 16. At the same time, the volume of the third oil chamber 28 increases and sucks in hydraulic oil through the oil supply line 41. Thus, by repeatedly switching the connection state of the first reversing valve 11, pressure oil can be injected into the first oil chamber 26 and the fourth oil chamber 29 respectively, pushing the first driving rod 23, the second driving rod 24 and the driven piston 25 to move reciprocally, and further realizing the function of continuously discharging the hydraulic oil, achieving the effect of continuously amplifying the flow rate.

[0045] When the continuous flow amplifier 10 is working normally, there is no throttling loss and overflow loss. And the one-way valve and the first shuttle valve 16 can adopt conical valve cores, which have the advantage of good sealing performance, reducing the leakage of the hydraulic oil. Therefore, the overall energy loss is small, achieving the advantage of high energy efficiency and being able to effectively reduce the energy consumption.

[0046] It realizes automatic and continuous amplification of the flow rate, enabling the hydraulic system not to be equipped with additional accumulators, pumps, motors, and devices for increasing the flow rate through differential connection. This makes the layout structure of the hydraulic system simpler, effectively reduces the manufacturing cost while meeting the usage requirements, and can reduce the probability of hydraulic oil leakage and improve the sealing performance.

[0047] Since there is no need to be equipped with additional devices such as accumulators, pumps, and motors, it helps to control the pressure of the hydraulic oil. Therefore, the internal pressure of the hydraulic system is also relatively small. As a result, in the design and manufacturing, the hydraulic system does not need to be designed with a too high sealing level. While facilitating the design and manufacturing, it is also possible to select hydraulic system components with a lower sealing level and a lower price, thereby further reducing the manufacturing cost.

[0048] Since the internal pressure of the hydraulic system is relatively small, the continuous flow amplifier 10 has very high reliability during the working process. The connection state of the first reversing valve 11 is directly controlled by the first pressing element 13 and the second pressing element 14, effectively reducing the complexity of the system and further reducing the probability of failures, thereby further improving the reliability. It achieves the advantages of high efficiency, good sealing performance, stability, reliability, and low cost.

[0049] By switching the opening and closing of the first valve 31 and the second valve 32, the hydraulic oil in the first oil chamber 26 and the fourth oil chamber 29 can flow to the first shuttle valve 16, increasing the flow rate at the oil outlet end 17 and achieving the effect of amplifying the flow rate of the hydraulic oil. The first check valve 33 and the second check valve 34 are provided to prevent the hydraulic oil in the first oil chamber 26 and the fourth oil chamber 29 from flowing to the first reversing valve 11.

[0050] When the pressure oil enters the first oil chamber 26, the pressure oil enters the control end of the second valve 32, causing the second valve 32 to open. The pressure oil in the first oil chamber 26 pushes the first driving rod 23 to drive the second driving rod 24 to push out the hydraulic oil in the fourth oil chamber 29, so that the hydraulic oil in the fourth oil chamber 29 enters the first shuttle valve 16 through the second valve 32. When the pressure oil enters the second oil chamber 27, the pressure oil enters the control end of the first valve 31, causing the first valve 31 to open. The pressure oil in the second oil chamber 27 pushes the second driving rod 24 to drive the first driving rod 23 to push out the hydraulic oil in the first oil chamber 26, so that the hydraulic oil in the first oil chamber 26 enters the first shuttle valve 16 through the first valve 31. It realizes the function of automatically controlling the opening and closing of the first valve 31 and the second valve 32 according to the pressure oil in the first oil chamber 26 and the second oil chamber 27.

[0051] When the first driving rod 23 and the second driving rod 24 respectively press the first pressing element 13 and the second pressing element 14, the first pressing element 13 and the second pressing element 14 can respectively trigger the first reversing valve 11 to switch the communication state, so as to realize the automatic switching of the communication state of the first reversing valve 11 according to the movements of the first driving rod 23 and the second driving rod 24, and realize the function that the continuous flow amplifier 10 can automatically and continuously amplify the flow rate, achieving the effects of convenient use and improved efficiency.

[0052] Through the settings of the third one-way valve 42 and the fourth one-way valve 43, it is possible to prevent the driven piston 25 from flowing into the oil supply pipeline 41 during the processes of respectively pushing the hydraulic oil out of the second oil chamber 27 and the third oil chamber 28, ensuring the stability of the hydraulic oil flow rate at the oil outlet end 17.

[0053] Through the settings of the first overflow valve 35 and the second overflow valve 36, when the hydraulic oil pressures in the first oil chamber 26 and the second oil chamber 27 are too high, it can prevent the hydraulic oil pressures in the first oil chamber 26 and the second oil chamber 27 from being too high, playing a role in improving safety and the reliability of the hydraulic system.

[0054] When the first reversing valve 11 switches the communication state, the pipeline connected to the pressure oil connection end 12 is disconnected to discharge the pressure oil into the return oil pipeline, preventing the oil pressures in the first oil chamber 26 and the fourth oil chamber 29 from being equal, which may cause the hydraulic oil to be unable to push the first driving rod 23, the second driving rod 24 and the driven piston 25 to move, and can also prevent the oil pressures at the two oil inlets of the first shuttle valve 16 from being equal, playing a role in improving the reliability of the equipment operation.

[0055] The fuel tank connection end 44 is communicated with the hydraulic fuel tank 59, so that the hydraulic fuel tank 59 can supply oil to the oil supply pipeline 41, ensuring that there is enough hydraulic oil in the oil supply pipeline 41 to be sucked into the second oil chamber 27 and the third oil chamber 28. When the overflow oil of the first overflow valve 35 and the second overflow valve 36 flows into the oil supply pipeline 41, the excess hydraulic oil can flow back into the hydraulic fuel tank 59 through the fuel tank connection end 44, preventing the hydraulic oil pressure in the oil supply pipeline 41 from being too high, playing a role in improving safety and reliability.

[0056] Embodiment 2:

[0057] Reference Figure 3, A hydraulic press, comprising a hydraulic cylinder 51, a slider 55, a fixed block 56, a pressure oil supply device, and the continuous flow amplifier 10 in Embodiment 1. The slider 55 is fixedly installed on the hydraulic cylinder 51. The pressure oil connection end 12 of the continuous flow amplifier 10 communicates with the pressure oil supply device, and the oil outlet end 17 of the continuous flow amplifier 10 communicates with the hydraulic cylinder 51. The pressure oil supply device communicates with a hydraulic oil tank 59. The pressure oil supply device includes a hydraulic pump 57 and a safety valve 58. The hydraulic pump 57 communicates with the continuous flow amplifier 10, the second shuttle valve 53, and the hydraulic oil tank 59 respectively, and the safety valve 58 communicates with the hydraulic pump 57. Place the workpiece between the slider 55 and the fixed block 56, and the hydraulic cylinder 51 drives the slider 55 to move towards the fixed block 56 and press the workpiece to achieve the function of machining the workpiece.

[0058] This embodiment has the following advantages:

[0059] The hydraulic pump 57 inputs the hydraulic oil in the hydraulic oil tank 59 into the continuous flow amplifier 10, amplifies the output flow of the hydraulic oil through the continuous flow amplifier 10, and inputs the hydraulic oil with a larger flow into the hydraulic cylinder 51 to drive the hydraulic cylinder 51 to move quickly, achieving the effect of improving the working efficiency of the hydraulic press.

[0060] Embodiment 3:

[0061] Reference Figure 4 , A hydraulic press, comprising a hydraulic cylinder 51, a slider 55, a fixed block 56, a pressure oil supply device, a second reversing valve 52, a second shuttle valve 53, and the continuous flow amplifier 10 in Embodiment 1. The slider 55 is fixedly installed on the hydraulic cylinder 51. The second reversing valve 52 adopts a three-position four-way electromagnetic reversing valve, and the second reversing valve 52 includes a left position, a middle position, and a right position. The second reversing valve 52 is arranged on the pipeline between the continuous flow amplifier 10 and the pressure oil supply device, and the second shuttle valve 53 is arranged on the pipeline between the continuous flow amplifier 10 and the hydraulic cylinder 51. The pressure oil supply device communicates with the second reversing valve 52. The pressure oil connection end 12 of the continuous flow amplifier 10 communicates with the second reversing valve 52. The two oil inlet ports of the second shuttle valve 53 communicate with the oil outlet end 17 of the continuous flow amplifier 10 and the second reversing valve 52 respectively. The pressure oil supply device communicates with a hydraulic oil tank 59. The pressure oil supply device includes a hydraulic pump 57 and a safety valve 58. The hydraulic pump 57 communicates with the continuous flow amplifier 10, the second shuttle valve 53, and the hydraulic oil tank 59 respectively, and the safety valve 58 communicates with the hydraulic pump 57. The second reversing valve 52 communicates with the hydraulic oil tank 59. Place the workpiece between the slider 55 and the fixed block 56, and the hydraulic cylinder 51 drives the slider 55 to move towards the fixed block 56 and press the workpiece to achieve the function of machining the workpiece.

[0062] This embodiment has the following advantages:

[0063] When the second reversing valve 52 is switched to the middle position, the hydraulic pump 57 is not connected to the second shuttle valve 53 and the continuous flow amplifier 10, thereby stopping the movement of the hydraulic cylinder 51. When the second reversing valve 52 is switched to the left position, the pressure oil supply device delivers hydraulic oil into the second shuttle valve 53 through the second reversing valve 52, causing the hydraulic cylinder 51 to feed at a slower speed. When the second reversing valve 52 is switched to the right position, the output flow rate of the hydraulic oil is amplified by the continuous flow amplifier 10, causing the hydraulic cylinder 51 to fast forward at a faster speed. When stopping work, the second reversing valve 52 is switched to the middle position to stop the movement of the hydraulic cylinder 51; when the hydraulic cylinder 51 is feeding, the hydraulic oil pressure is relatively high, resulting in a relatively large thrust of the hydraulic cylinder 51, so that it can be applicable to the working condition of providing thrust to clamp the workpiece; when it is necessary to drive the hydraulic cylinder 51 to move quickly, it can be switched to the fast forward state to improve work efficiency, having the advantage of high applicability.

[0064] Embodiment 4:

[0065] Reference Figure 5 A hydraulic press, comprising a hydraulic cylinder 51, a slider 55, a fixed block 56, a pressure oil supply device, a second reversing valve 52, a third reversing valve 54, a second shuttle valve 53, and the continuous flow amplifier 10 in Embodiment 1. The slider 55 is fixedly installed on the hydraulic cylinder 51. The pressure oil supply device is connected to the second reversing valve 52. The pressure oil connection end 12 of the continuous flow amplifier 10 is connected to the second reversing valve 52. The two oil inlets of the second shuttle valve 53 are respectively connected to the oil outlet end 17 of the continuous flow amplifier 10 and the second reversing valve 52. The pressure oil supply device is connected to a hydraulic oil tank 59. The pressure oil supply device includes a hydraulic pump 57 and a safety valve 58. The hydraulic pump 57 is respectively connected to the continuous flow amplifier 10, the second shuttle valve 53, and the hydraulic oil tank 59. The safety valve 58 is connected to the hydraulic pump 57. The third reversing valve 54 is arranged on the pipeline between the second shuttle valve 53 and the hydraulic cylinder 51. The output end of the second shuttle valve 53 is connected to the third reversing valve 54. Both the second reversing valve 52 and the third reversing valve 54 are connected to the hydraulic oil tank 59. Place the workpiece between the slider 55 and the fixed block 56, and the hydraulic cylinder 51 drives the slider 55 to move towards the fixed block 56 and press the workpiece, realizing the function of machining the workpiece.

[0066] The third reversing valve 54 is a two-position four-way electromagnetic reversing valve, and the third reversing valve 54 includes an upper position and a lower position.

[0067] When the third reversing valve 54 is switched to the upper position, the hydraulic pump 57 can supply hydraulic oil to the rodless cavity of the hydraulic cylinder 51, causing the hydraulic cylinder 51 to move forward. When the second reversing valve 52 is switched to the lower position, the hydraulic pump 57 can supply hydraulic oil to the rod chamber of the hydraulic cylinder 51, causing the hydraulic cylinder 51 to move in the reverse direction.

[0068] Combined with the continuous flow amplifier 10, the second reversing valve 52 and the third reversing valve 54, this hydraulic press can switch between five different working states:

[0069] 1. When it is necessary to stop the movement of the hydraulic cylinder 51, the second reversing valve 52 is switched to the neutral position, and the hydraulic pump 57 is unloaded;

[0070] 2. When it is necessary for the hydraulic cylinder 51 to move forward rapidly (fast forward state), the second reversing valve 52 is switched to the right position, the third reversing valve 54 is switched to the upper position, and the hydraulic pump 57 supplies oil to the hydraulic cylinder 51 after the flow rate is amplified by the continuous flow amplifier 10. The hydraulic cylinder 51 drives the slider 55 to move forward rapidly;

[0071] 3. When it is necessary for the hydraulic cylinder 51 to move forward slowly (working feed state), the second reversing valve 52 is switched to the left position, the third reversing valve 54 is switched to the upper position, and the hydraulic pump 57 directly supplies oil to the hydraulic cylinder 51. The hydraulic cylinder 51 drives the slider 55 to move forward slowly;

[0072] 4. When it is necessary for the hydraulic cylinder 51 to move backward slowly (slow return state), the second reversing valve 52 is switched to the left position, the third reversing valve 54 is switched to the lower position, and the hydraulic pump 57 directly supplies oil to the hydraulic cylinder 51. The hydraulic cylinder 51 drives the slider 55 to move backward slowly;

[0073] 5. When it is necessary for the hydraulic cylinder 51 to move backward rapidly (fast return state), the second reversing valve 52 is switched to the right position, the third reversing valve 54 is switched to the lower position, and the hydraulic pump 57 supplies oil to the hydraulic cylinder 51 after the flow rate is amplified by the continuous flow amplifier 10. The hydraulic cylinder 51 drives the slider 55 to move backward rapidly.

[0074] This embodiment has the following advantages:

[0075] Thus, multiple different working states are realized, which can adapt to different working states, meet different usage requirements, and play a role in improving applicability and production efficiency.

[0076] According to the disclosure and teaching of the above specification, those skilled in the art to which the present invention pertains can also make changes and modifications to the above embodiments. Therefore, the present invention is not limited to the specific embodiments disclosed and described above, and some modifications and changes to the invention should also fall within the protection scope of the claims of the present invention. In addition, although some specific terms are used in this specification, these terms are only for convenience of description and do not constitute any limitation to the invention.

Claims

1. A hydraulic press, comprising a hydraulic cylinder (51) and a pressure oil supply device, Characterized in that: It further comprises a continuous flow amplifier (10), a pressure oil connection end (12) of the continuous flow amplifier (10) is communicated with the pressure oil supply device, and an oil outlet end (17) of the continuous flow amplifier (10) is communicated with the hydraulic cylinder (51); The hydraulic press further comprises a second reversing valve (52) and a second shuttle valve (53), the second reversing valve (52) is arranged on a pipeline between the continuous flow amplifier (10) and the pressure oil supply device, the second shuttle valve (53) is arranged on a pipeline between the continuous flow amplifier (10) and the hydraulic cylinder (51), two oil inlet ports of the second shuttle valve (53) are respectively communicated with the oil outlet end (17) of the continuous flow amplifier (10) and the second reversing valve (52), the pressure oil supply device is communicated with a hydraulic oil tank (59), and the second reversing valve (52) is communicated with the hydraulic oil tank (59); The hydraulic press further comprises a third reversing valve (54), the third reversing valve (54) is arranged on a pipeline between the continuous flow amplifier (10) and the hydraulic cylinder (51); The continuous flow amplifier (10) comprises a first reversing valve (11) and a first shuttle valve (16), a flow amplification cylinder (21) and an oil supply pipeline (41), the flow amplification cylinder (21) comprises a housing (22), a first driving rod (23), a second driving rod (24) and a driven piston (25), a first oil chamber (26), a second oil chamber (27), a third oil chamber (28) and a fourth oil chamber (29) are arranged in the housing (22), the driven piston (25) is fixedly connected with the first driving rod (23) and the second driving rod (24) respectively, the first driving rod (23), the second driving rod (24) and the driven piston (25) are slidably installed in the housing (22), the second oil chamber (27) and the third oil chamber (28) are respectively located on two sides of the sliding direction of the driven piston (25), the first driving rod (23) extends into the first oil chamber (26), the second driving rod (24) extends into the fourth oil chamber (29), the first oil chamber (26) and the fourth oil chamber (29) are respectively communicated with the first reversing valve (11), the oil supply pipeline (41) is respectively communicated with the second oil chamber (27) and the third oil chamber (28), the second oil chamber (27) and the third oil chamber (28) are respectively communicated with two oil inlet ports of the first shuttle valve (16), the first reversing valve (11) is provided with a pressure oil connection end (12), and the first shuttle valve (16) is provided with an oil outlet end (17).

2. The hydraulic press according to claim 1, Characterized in that: The first oil chamber (26) and the second oil chamber (27) are respectively communicated with a first shuttle valve (16). A first valve (31) is provided between the first oil chamber (26) and the first shuttle valve (16). A second valve (32) is provided between the fourth oil chamber (29) and the first shuttle valve (16). A first one-way valve (33) is provided between the first oil chamber (26) and the first reversing valve (11). A second one-way valve (34) is provided between the fourth oil chamber (29) and the first reversing valve (11).

3. The hydraulic press according to claim 2, characterized in that: The first valve (31) and the second valve (32) are both liquid-controlled valves. The control end of the first valve (31) is communicated with the fourth oil chamber (29). The control end of the second valve (32) is communicated with the first oil chamber (26).

4. The hydraulic press according to claim 1, characterized in that: The housing (22) is fixedly installed with a first pressing element (13) and a second pressing element (14). The first pressing element (13) is located in the first oil chamber (26) and abuts against the first driving rod (23). The second pressing element (14) is located in the fourth oil chamber (29) and abuts against the second driving rod (24). The first pressing element (13) and the second pressing element (14) are respectively connected to the first reversing valve (11).

5. The hydraulic press according to claim 1, characterized in that: The oil supply circuit (41) is provided with a third one-way valve (42) and a fourth one-way valve (43). The two ends of the third one-way valve (42) are respectively communicated with the oil supply circuit (41) and the second oil chamber (27). The two ends of the fourth one-way valve (43) are respectively communicated with the oil supply circuit (41) and the third oil chamber (28).

6. The hydraulic press according to claim 1, characterized in that: The first oil chamber (26) is communicated with a first overflow valve (35). The fourth oil chamber (29) is communicated with a second overflow valve (36). The first overflow valve (35) and the second overflow valve (36) are both communicated with the oil supply circuit (41).

7. The hydraulic press according to claim 6, characterized in that: The first reversing valve (11) is provided with an oil return end (15). The oil return end (15) is communicated with the oil supply circuit (41).

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