Rapid releasing hydraulic system of releasing machine
By designing a hydraulic system for fast-spreading of the release machine including a hydraulic oil supply module and an automatic oil switching circuit, the problems of inefficiency and high cost in the prior art are solved, and efficient, rapid and high load-slow extension of the release cylinder is achieved.
Patent Information
- Application Number
- CN202411988142.3
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2024-12-31
- Publication Date
- 2025-02-28
AI Technical Summary
The prior art cannot achieve light load and rapid operation of the discharge cylinder and slow operation of heavy load and ultra-high pressure through ordinary boosting systems, resulting in low efficiency and high cost.
A hydraulic system for fast discharge of the discharge machine including hydraulic oil supply module, discharge cylinder, low-pressure drive oil circuit and booster drive oil circuit is designed. The hydraulic oil driving pressure is sensed through the sequential valve, and the low-pressure driving oil circuit and the boosting driving oil circuit are automatically switched to achieve the rapid extension and slow extension of the release cylinder.
The efficient and fast extension of the release cylinder and the slow extension of the high load are achieved, reducing system costs and improving release efficiency.
Smart Images
Figure CN119532257A_ABST
Abstract
Description
Technical Field
[0001] The present application provides a rapid tensioning hydraulic system for a tensioning machine, and relates to the technical field of construction engineering. Background Art
[0002] The hydraulic system for deploying the cylinders not only requires high-frequency and rapid extension and retraction of the cylinders, but also requires the hydraulic system to provide very high hydraulic pressure during the heavy-load stage during the extension of the cylinders, with the maximum operating pressure reaching 70 MPa.
[0003] Since ordinary booster systems cannot meet the requirements of high-frequency and rapid extension and retraction of the oil cylinder, similar hydraulic systems of pipe pile release equipment in the prior art generally use ultra-high pressure pumps and valves to switch between high and low pressure oil pumps to achieve fast operation of the oil cylinder under light loads and slow operation under heavy loads at ultra-high pressure. Although this solution can also achieve the purpose of release, the technical and efficiency disadvantages are: 1) This solution requires more ultra-high pressure components, and the probability of external leakage and component failure is significantly increased. 2) Due to the limitations of existing ultra-high pressure pump and valve technology, it is no longer possible to continue to increase the speed of the oil cylinder under existing technical conditions, so there are widespread problems such as low efficiency that need to be solved urgently. Economically speaking, the cost of using ultra-high pressure pumps and valves to achieve release is much higher than that of ordinary hydraulic systems. Summary of the invention
[0004] The technical problem to be solved by the present application is how to realize the rapid operation of the hydraulic cylinder under light load and the slow operation under heavy load and ultra-high pressure by using a common booster system.
[0005] In order to solve the above-mentioned technical problems, the present application provides a rapid hydraulic system for a tensioning machine, including a hydraulic oil supply module, a tensioning cylinder, a low-pressure driving oil circuit connecting the hydraulic oil supply module and the tensioning cylinder, and a boost driving oil circuit connecting the hydraulic oil supply module and the tensioning cylinder; the boost driving oil circuit is provided with a sequence valve for sensing the hydraulic oil driving pressure, and when the hydraulic oil driving pressure is greater than a preset value of the sequence valve, the sequence valve is turned on to switch the low-pressure driving oil circuit to the boost driving oil circuit.
[0006] Preferably, the hydraulic oil supply module is provided with an oil supply end and an oil return end, and the oil supply end and the oil return end are provided with valves for controlling the oil supply end and the oil return end to be connected or disconnected to the outside.
[0007] Preferably, the low-pressure driving oil circuit includes a hydraulically controlled one-way valve, which includes an inlet A end, an outlet B end and an oil control interface X end; the inlet A end of the hydraulically controlled one-way valve is connected to the hydraulic oil supply module for oil inlet through an oil inlet branch, the outlet B end of the hydraulically controlled one-way valve is connected to the rodless chamber of the tensioning cylinder, and the rod chamber of the tensioning cylinder is connected to the hydraulic oil supply module for oil return through an oil return branch.
[0008] Preferably, the boost drive oil circuit includes a boost cylinder, a hydraulic control valve, a sequence valve, a first non-return valve and a second non-return valve; the boost cylinder is a double-chamber boost cylinder, including a fine chamber and a coarse chamber, a piston B is arranged in the fine chamber, a piston A is arranged in the coarse chamber, piston B is fixedly connected with piston A and moves synchronously, and piston B and piston A divide the double chamber into a small chamber, an intermediate chamber and a large chamber; the hydraulic control valve includes an interface P, a reversing control interface C, an interface A, an interface B and a hydraulic control interface D, the hydraulic control interface D is connected to the internal hydraulic control chamber, the reversing control interface C is connected to the internal reversing control chamber, the hydraulic control chamber is a large-area chamber, and the reversing control chamber is a small-area chamber; the sequence valve includes an inlet A end and an outlet B end, the sequence valve opens when the oil pressure at the inlet A end exceeds the preset pressure, and remains closed when it does not exceed the preset pressure; The inlet A end of the sequence valve, the interface P of the hydraulic control valve, and the reversing control interface C are all connected to the oil inlet branch through the first oil circuit branch; the interface A of the hydraulic control valve is connected to the large chamber of the booster cylinder, the interface B of the hydraulic control valve is connected to the middle chamber of the booster cylinder, and the hydraulic control interface D of the hydraulic control valve is connected between the small chamber and the middle chamber of the booster cylinder and is initially blocked by the piston B; the outlet B end of the sequence valve is connected to the inlet of the first one-way valve, the outlet of the first one-way valve is connected to the small chamber of the booster cylinder, the small chamber of the booster cylinder is connected to the inlet of the second one-way valve, and the outlet of the second one-way valve is connected to the oil circuit from the outlet B end of the hydraulic control one-way valve to the rodless chamber of the release cylinder; the middle chamber of the booster cylinder is connected to the oil return branch through the second oil circuit branch, and the oil control interface X end of the hydraulic control one-way valve is connected to the second oil circuit branch.
[0009] Preferably, the valve is configured as a three-position four-way solenoid reversing valve, which includes an inlet P end, an outlet T end, an interface A end and an interface B end. The three-position four-way solenoid reversing valve is provided with a first control electromagnet YV1a and a second control electromagnet YV1b. When the first control electromagnet YV1a is powered on, the inlet P end is connected to the interface A end, and the outlet T end is connected to the interface B end. When the second control electromagnet YV1b is powered on, the inlet P end is connected to the interface B end, and the outlet T end is connected to the interface A end. The first control electromagnet YV1a and the second control electromagnet YV1b are both powered off, the three-position four-way solenoid reversing valve is closed, the interface A end is disconnected, the interface B end is disconnected, and the inlet P end is connected to the outlet T end; the oil supply end of the hydraulic oil supply module is connected to the inlet P end of the three-position four-way solenoid reversing valve, and the outlet T end of the three-position four-way solenoid reversing valve is connected to the oil return end.
[0010] Preferably, the interface B end of the three-position four-way electromagnetic reversing valve is connected to the oil inlet branch, and the interface A end of the three-position four-way electromagnetic reversing valve is connected to the oil return branch.
[0011] Preferably, the low-pressure drive oil circuit also includes a first pressure switch and a second pressure switch. The first pressure switch is arranged on the oil circuit from the outlet B end of the hydraulically controlled one-way valve to the rodless chamber of the tensioning cylinder, and the second pressure switch is arranged on the oil circuit from the rod chamber of the tensioning cylinder to the interface A end of the three-position four-way electromagnetic reversing valve.
[0012] Furthermore, the rapid hydraulic system of the tensioning machine is provided with a low-load rapid extension condition of the tensioning cylinder driven by a low-pressure driving oil circuit and a high-load slow extension condition of the tensioning cylinder driven by a boost driving oil circuit. The hydraulic oil driving pressure is sensed by a sequential valve to switch between the low-load rapid extension condition of the tensioning cylinder and the high-load slow extension condition of the tensioning cylinder.
[0013] Furthermore, the rapid tensioning hydraulic system of the tensioning machine is provided with a rapid retraction condition of the tensioning cylinder. When the hydraulic oil flowing into the tensioning cylinder exceeds the set pressure of the first pressure switch, the first pressure switch transmits a signal to energize the first control solenoid YV1a of the three-position four-way solenoid reversing valve, executing the rapid retraction condition of the tensioning cylinder.
[0014] Preferably, the hydraulic oil supply module also includes an oil tank, an oil drain ball valve, an oil suction filter, an air filter, a liquid level thermometer, a three-phase asynchronous motor, a coupling, a metering pump, a third one-way valve, a seismic pressure gauge, a relief valve, a temperature switch and a forced air cooler; the oil drain ball valve is arranged at the bottom of the oil tank; an oil suction filter, an air filter and a liquid level thermometer are arranged in the oil tank; the oil suction filter is connected to the metering pump, and the metering pump is connected to the three-phase asynchronous motor through a coupling and driven by the three-phase asynchronous motor; the metering pump outlet is connected to the third one-way valve inlet, and the third one-way valve outlet is connected to the oil supply end; the seismic pressure gauge is connected to the oil circuit from the third one-way valve outlet to the oil supply end; the forced air cooler is arranged on the oil circuit from the return oil end to the oil tank, the temperature switch monitors the oil temperature, and the forced air cooler is started when the preset temperature is exceeded; an overflow branch is arranged between the oil supply end and the return oil end, and the overflow valve is arranged on the overflow branch, and when the oil pressure exceeds the preset pressure, the overflow valve is turned on to overflow.
[0015] The technical solution of this application adopts a common hydraulic system to drive the hydraulic booster to act sequentially, because the common hydraulic system is low in cost and the booster can achieve a large flow rate. Therefore, the new hydraulic system greatly improves the efficiency of the release and greatly reduces the price of the hydraulic system. BRIEF DESCRIPTION OF THE DRAWINGS
[0016] Figure 1 This is a schematic diagram of the structure of a rapid tensioning hydraulic system of a tensioning machine provided in an embodiment of the present application;
[0017] Description of reference numerals: hydraulic oil supply module 100, oil supply end 101, oil return end 102, oil tank 103, oil drain ball valve 104, oil suction filter 105, air filter 106, liquid level thermometer 107, three-phase asynchronous motor 108, coupling 109, metering pump 110, third one-way valve 111, earthquake-resistant pressure gauge 112, relief valve 113, temperature switch 114, forced air cooler 115,
[0018] Three-position four-way solenoid directional valve 201,
[0019] Low-pressure drive oil circuit 300, hydraulically controlled one-way valve 301, first pressure switch 302, second pressure switch 303,
[0020] Boost drive oil circuit 400, boost cylinder 401, small chamber 401-1, middle chamber 401-2, large chamber 401-3, hydraulic control valve 402, sequence valve 403, first check valve 404, second check valve 405,
[0021] Put the oil cylinder 500;
[0022] The first oil branch 601 and the second oil branch 602 . DETAILED DESCRIPTION
[0023] To make the application more obvious and easy to understand, various exemplary embodiments will be introduced below. These examples are non-limiting, and it should be understood that they are used for the more general application aspects of the illustrative device, system and method. Without departing from the substantive content and scope of the application, these embodiments can be subjected to multiple changes, and can be replaced by equivalents. In addition, multiple changes can be carried out to adapt to the purpose, content or scope of the application in order to adapt to special situations, materials, material components, treatment types, treatment actions or steps. All these changes will be within the protection scope of the application.
[0024] For any materials, dimensions, quantities introduced in the overview or detailed description, they will be examples only and are not intended to limit the subject matter of the present application. Moreover, the various implementations of the embodiments described herein will complement each other, rather than purely interchangeably, unless otherwise indicated. In other words, implementations from one embodiment can be freely combined with implementations of other embodiments, as those of ordinary skill in the art will readily appreciate, unless it is indicated that these implementations are only for replacement.
[0025] In the description of this application, it should be noted that the terms "inside", "outside", etc. indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, or the orientation or positional relationship in which the product of the application is usually placed when in use, which is only for the convenience of describing this application and simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on this application. In addition, the terms "first", "second", etc. are only used to distinguish the description, and cannot be understood as indicating or implying relative importance.
[0026] In the description of this application, it should also be noted that, unless otherwise clearly specified and limited, the terms "disposed" and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a direct connection, or an indirect connection through an intermediate medium, or it can be the internal communication of two elements. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to specific circumstances.
[0027] Example
[0028] The present application embodiment provides a hydraulic system for rapidly releasing a sheet of paper from a sheet-laying machine. Figure 1 , including a hydraulic oil supply module 100, a three-position four-way electromagnetic reversing valve 201, a low-pressure driving oil circuit 300, a boost driving oil circuit 400 and a tensioning cylinder 500 for driving a load.
[0029] The hydraulic oil supply module 100 is provided with an oil supply end 101 and an oil return end 102 .
[0030] The three-position four-way solenoid reversing valve 201 includes an inlet P end, an outlet T end, an interface A end and an interface B end. The three-position four-way solenoid reversing valve 201 is provided with a first control electromagnet YV1a and a second control electromagnet YV1b. When the first control electromagnet YV1a is powered on, the inlet P end is connected with the interface A end, and the outlet T end is connected with the interface B end. When the second control electromagnet YV1b is powered on, the inlet P end is connected with the interface B end, and the outlet T end is connected with the interface A end. The first control electromagnet YV1a and the second control electromagnet YV1b are both powered off. At this time, the three-position four-way solenoid reversing valve 201 is closed, the interface A end is disconnected, the interface B end is disconnected, and the inlet P end is connected with the outlet T end.
[0031] The oil supply end 101 of the hydraulic oil supply module 100 is connected to the inlet P end of the three-position four-way solenoid reversing valve 201, and the outlet T end of the three-position four-way solenoid reversing valve 201 is connected to the oil return end 102; the interface B end of the three-position four-way solenoid reversing valve 201 is connected to the low-pressure drive oil circuit 300; the low-pressure drive oil circuit 300 includes a hydraulically controlled one-way valve 301, a first pressure switch 302 (PT1), and a second pressure switch 303 (PT2), and the hydraulically controlled one-way valve 301 includes an inlet A end, an outlet B end and an oil control interface X end. The interface B end of the three-position four-way solenoid reversing valve 201 is connected to the inlet A end of the hydraulically controlled one-way valve 301, the outlet B end of the hydraulically controlled one-way valve 301 is connected to the rodless chamber of the tensioning cylinder 500, and the rod chamber of the tensioning cylinder 500 is connected to the interface A end of the three-position four-way solenoid reversing valve 201; the first pressure switch 302 is arranged on the oil path from the outlet B end of the hydraulically controlled one-way valve 301 to the rodless chamber of the tensioning cylinder 500, and the second pressure switch 303 is arranged on the oil path from the rod chamber of the tensioning cylinder 500 to the interface A end of the three-position four-way solenoid reversing valve 201.
[0032] The boost drive oil circuit 400 includes a boost cylinder 401, a hydraulic control valve 402, a sequence valve 403, a first check valve 404, and a second check valve 405. The boost cylinder 401 is a double-chamber boost cylinder, including a fine chamber and a coarse chamber, a piston B is arranged in the fine chamber, a piston A is arranged in the coarse chamber, the piston B is fixedly connected with the piston A and moves synchronously, and the piston B and the piston A divide the double chamber into a small chamber 40, an intermediate chamber 40, and a large chamber 40. The hydraulic control valve 402 includes an interface P, a reversing control interface C, an interface A, an interface B and a hydraulic control interface D. The hydraulic control interface D is connected to the internal hydraulic control cavity, and the reversing control interface C is connected to the internal reversing control cavity. The hydraulic control cavity is a large-area cavity, and the reversing control cavity is a small-area cavity. In the default state, the interface P is disconnected, and the interface A is connected to the interface B. When the hydraulic oil enters the hydraulic control interface D, since the force area of the hydraulic control cavity is larger than the force area of the reversing control cavity, the main valve core of the hydraulic control valve 402 is reversed downward, and the interface P is connected to the interface A, and the interface A is disconnected from the interface B. The sequence valve 403 includes an inlet A end and an outlet B end. The sequence valve 403 opens when the oil pressure at the inlet A end exceeds the preset pressure, and remains closed when it does not exceed the preset pressure. The inlet A end of the sequence valve 403, the interface P of the hydraulic control valve 402, and the reversing control interface C are all connected to the oil circuit from the interface B end of the three-position four-way electromagnetic reversing valve 201 to the inlet A end of the hydraulic control check valve 301 through the first oil circuit branch 601; the interface A of the hydraulic control valve 402 is connected to the large chamber 40 of the booster cylinder 401, the interface B of the hydraulic control valve 402 is connected to the middle chamber 40 of the booster cylinder 401, and the hydraulic control interface D of the hydraulic control valve 402 is connected between the small chamber 40 and the middle chamber 40 of the booster cylinder 401, and is initially blocked by the piston B; the outlet B end of the sequence valve 403 is connected to the first The inlet of the one-way valve 404 and the outlet of the first one-way valve 404 are connected to the small chamber 40 of the boosting cylinder 401, the small chamber 40 of the boosting cylinder 401 is connected to the inlet of the second one-way valve 405, and the outlet of the second one-way valve 405 is connected to the oil circuit from the outlet B end of the hydraulically controlled one-way valve 301 to the rodless chamber of the tensioning cylinder 500; the middle chamber 40 of the boosting cylinder 401 is connected to the oil circuit from the rod chamber of the tensioning cylinder 500 to the interface A end of the three-position four-way solenoid reversing valve 201 through the second oil circuit branch 602, and the oil control interface X end of the hydraulically controlled one-way valve 301 is connected to the second oil circuit branch 602.
[0033] In a further embodiment, the hydraulic oil supply module 100 includes an oil tank 103, an oil drain ball valve 104, an oil suction filter 105, an air filter 106, a liquid level thermometer 107, a three-phase asynchronous motor 108, a coupling 109, a metering pump 110, a third one-way valve 111, a shockproof pressure gauge 112, a relief valve 113, a temperature switch 114 and a forced air cooler 115. The oil drain ball valve 104 is arranged at the bottom of the oil tank 103; the oil suction filter 105, the air filter 106 and the liquid level thermometer 107 are arranged in the oil tank 103; the oil suction filter 105 is connected to the metering pump 110, and the metering pump 110 is connected to the three-phase asynchronous motor 108 through the coupling 109 and is driven by the three-phase asynchronous motor 108; the outlet of the metering pump 110 is connected to the inlet of the third one-way valve 111, and the outlet of the third one-way valve 111 is connected to the oil supply end 101; the shockproof pressure gauge 112 is connected to the third one-way valve 111, and the outlet of the third one-way valve 111 is connected to the oil supply end 101; The force meter 112 is connected to the oil circuit from the outlet of the third one-way valve 111 to the oil supply end 101; the forced air cooler 115 is arranged on the oil circuit from the return oil end 102 to the oil tank 103, the temperature switch 114 monitors the oil temperature, and the forced air cooler 115 is started when the preset temperature is exceeded; an overflow branch is arranged between the oil supply end 101 and the return oil end 102, the overflow valve 113 is arranged on the overflow branch, and when the oil pressure exceeds the preset pressure, the overflow valve 113 is turned on for overflow.
[0034] The hydraulic system for rapid tensioning of tensioning machines provided in this application includes the following operating states:
[0035] 1. Release the cylinder and extend it quickly with low load
[0036] When the second control electromagnet YV1b of the three-position four-way electromagnetic reversing valve 201 is energized, the three-phase asynchronous motor 108 drives the metering pump 110 through the coupling 109, and the metering pump 110 sucks the oil from the hydraulic oil tank 103 into the metering pump 110 through the oil suction filter 105. The metering pump 110 passes the pressurized hydraulic oil through the third check valve 111, the inlet P end and the interface B end of the three-position four-way electromagnetic reversing valve 201, and flows into the interface P of the hydraulic control valve 402 and the inlet A end of the hydraulic control check valve 301 in two ways. The hydraulic pressure flowing into the hydraulic control valve 402 is divided into two ways, one way flows into the reversing control interface C of the lower reversing control chamber (small area chamber) of the hydraulic control valve 402, and the other way flows into the interface P of the channel chamber of the hydraulic control valve 402. The position shown in the figure is in the cut-off state, and the oil is cut off. The hydraulic oil flowing into the hydraulically controlled one-way valve 301 flows into the rodless chamber of the stretching cylinder 500 through the inlet A end and the outlet B end of the hydraulically controlled one-way valve 301. At this time, the stretching cylinder 500 extends quickly, and the external load on the stretching cylinder 500 is relatively small.
[0037] 2. Extend the cylinder slowly with high load (using sequence valve 403 to sense high load)
[0038] When the tensioning cylinder 500 is subjected to a large external load, the hydraulic oil pressure at the pump outlet exceeds the set pressure of the sequence valve 403, and the pressure oil opens the sequence valve 403. The hydraulic oil flows into the upper chamber (small chamber 40, boosting chamber) of the boosting cylinder 401 through the inlet A end and the outlet B end of the sequence valve 403 and the one-way valve 404. The pressure oil causes the boosting piston A / B to move downward, and the pressure oil is injected into the boosting chamber. When the boosting piston A / B moves downward to the right position, the control oil port of the upper control chamber (large area chamber) of the hydraulic control valve 402 is also exposed. This pressure oil is injected into the upper control chamber (large area chamber) from the hydraulic control interface D of the hydraulic control valve 402. Because the force-bearing area of the upper control chamber of the hydraulic control valve 402 is larger than the force-bearing area of the lower control chamber, the main valve core of the hydraulic control valve 402 is reversed downward, so that the interfaces P and A of the hydraulic control valve 402 are connected. At this time, the pressure oil in the pipeline flows into the large chamber 401-3 of the booster cylinder 401 through the interfaces P and A of the hydraulic control valve 402, thereby pushing the booster piston A / B to move upward. Since the area of the booster piston A of the booster cylinder 401 is larger than the area of B, the oil in the small chamber 401-1 of the booster cylinder 401 flows into the rodless chamber of the tensioning oil cylinder 500 through the check valve 405 in a multiple relationship, so that the tensioning oil cylinder 500 is extended slowly with high load. At the same time, this pressure oil acts on the outlet B end of the hydraulic control check valve 301 to close the hydraulic control check valve 301.
[0039] It is understandable that the three-position four-way solenoid reversing valve 201 is not required to realize the low-load rapid extension of the tensioning cylinder and the high-load slow extension of the tensioning cylinder. Figure 1 By removing the three-position four-way electromagnetic reversing valve 201 and replacing it with a simple on-off valve, the start and close of the stretching cylinder 500 can be controlled. The hydraulic oil load pressure is automatically sensed through the sequence valve 403, without affecting the automatic switching between the two working conditions of low-load fast extension of the stretching cylinder and high-load slow extension of the stretching cylinder.
[0040] 3. Release the oil cylinder and retract it quickly
[0041] When the pressure oil flowing into the tensioning cylinder 500 exceeds the set pressure of the first pressure switch 302, the first pressure switch 302 transmits a signal to energize the electromagnet YV1a of the three-position four-way solenoid reversing valve 201. At this time, the pressure oil from the metering pump 110 flows into the rod chamber of the tensioning cylinder through the third one-way valve 111 and the P and A oil ports of the three-position four-way solenoid reversing valve 201. At the same time, this pressure oil flows into the X port of the hydraulic one-way valve 301 to open the hydraulic one-way valve 301, so that the A and B ports of the hydraulic one-way valve 301 are interconnected. At this time, the pressure oil flowing into the rod chamber of the tensioning cylinder 500 pushes the cylinder to retract quickly. When the piston of the tensioning cylinder 500 retreats to its position, the first pressure switch 302 transmits a signal to energize the electromagnet YV1a of the three-position four-way solenoid reversing valve 201, and the above cycle is repeated.
[0042] 4. Hydraulic system unloading
[0043] When the releasing task is paused, the electromagnets YV1a and YV1b of the three-position four-way solenoid reversing valve 201 are not energized. At this time, the valve core of the three-position four-way solenoid reversing valve 201 is in the middle position, and the pressure oil flowing out of the oil pump passes through the third one-way valve 111 and the middle position of the three-position four-way solenoid reversing valve 201 into the forced air cooler 115 and the hydraulic oil tank 103.
[0044] 5. Oil Cooling
[0045] When the temperature of the hydraulic oil in the hydraulic oil tank 103 reaches the set temperature upper limit of the temperature switch 114, the cooling fan of the forced air cooler 115 is turned on to cool the hydraulic oil passing through the forced air cooler 115. When the temperature of the hydraulic oil in the hydraulic oil tank 103 reaches the set temperature lower limit of the temperature switch 114, the cooling fan of the forced air cooler 115 is turned off.
[0046] The above is only a preferred embodiment of the present application, and is not any formal or substantial limitation to the present application. It should be pointed out that ordinary technicians in this technical field can make several improvements and supplements without departing from the present application, and these improvements and supplements should also be regarded as the protection scope of the present application. Any technician familiar with this profession, without departing from the content and scope of the present application, can make some changes, modifications and evolutions of the technical content disclosed above, which are equivalent embodiments of the present application; at the same time, any changes, modifications and evolutions of any equivalent changes made to the above-mentioned implementation methods based on the substantial technology of the present application are still within the scope of the technical solution of the present application.
Claims
1. A hydraulic system for rapid tensioning of tensioning machines, characterized in that: The invention comprises a hydraulic oil supply module (100), a tensioning oil cylinder 50, a low-pressure driving oil circuit (300) connecting the hydraulic oil supply module (100) and the tensioning oil cylinder (500), and a boost driving oil circuit (400) connecting the hydraulic oil supply module (100) and the tensioning oil cylinder (500); the boost driving oil circuit (400) is provided with a sequence valve (403) for sensing the hydraulic oil driving pressure; when the hydraulic oil driving pressure is greater than a preset value of the sequence valve (403), the sequence valve (403) is turned on to switch the low-pressure driving oil circuit (300) to the boost driving oil circuit (400).
2. A hydraulic system for rapid tensioning of a tensioning machine according to claim 1, characterized in that: The hydraulic oil supply module (100) is provided with an oil supply end (101) and an oil return end (102), and valves for controlling the oil supply end (101) and the oil return end (102) to be connected or disconnected to the outside are provided at the oil supply end (101) and the oil return end (102).
3. A hydraulic system for rapid tensioning of tensioning machines according to claim 2, characterized in that: The low-pressure drive oil circuit (300) includes a hydraulically controlled one-way valve (301), and the hydraulically controlled one-way valve (301) includes an inlet A end, an outlet B end, and an oil control interface X end; the inlet A end of the hydraulically controlled one-way valve (301) is connected to the hydraulic oil supply module (100) for oil inlet via an oil inlet branch, the outlet B end of the hydraulically controlled one-way valve (301) is connected to the rodless chamber of the tensioning oil cylinder (500), and the rod chamber of the tensioning oil cylinder (500) is connected to the hydraulic oil supply module (100) for oil return via an oil return branch.
4. A hydraulic system for rapid tensioning of tensioning machines according to claim 3, characterized in that: The boost drive oil circuit (400) comprises a boost cylinder (401), a hydraulic control valve (402), a sequence valve (403), a first non-return valve (404), and a second non-return valve (405); the boost cylinder (401) is a double-chamber boost cylinder, comprising a fine chamber and a coarse chamber, a piston B is arranged in the fine chamber, a piston A is arranged in the coarse chamber, the piston B is fixedly connected with the piston A for synchronous movement, and the piston B and the piston A divide the double chamber into a small chamber (401-1), an intermediate chamber (401-2), and a large chamber (401-3); the hydraulic control valve (402) comprises a connection The sequence valve (403) comprises an inlet A end and an outlet B end. When the oil pressure at the inlet A end exceeds a preset pressure, the sequence valve (403) opens. When the oil pressure at the inlet A end does not exceed the preset pressure, the sequence valve (403) remains closed. The inlet A end of the sequence valve (403), the interface P of the hydraulic control valve (402), and the reversing control interface C are all connected to the first oil circuit branch (60 1) is connected to the oil inlet branch; the interface A of the hydraulic control valve (402) is connected to the large chamber (401-3) of the boosting cylinder (401), the interface B of the hydraulic control valve (402) is connected to the middle chamber (401-2) of the boosting cylinder (401), the hydraulic control interface D of the hydraulic control valve (402) is connected between the small chamber (401-1) and the middle chamber (401-2) of the boosting cylinder (401), and is initially blocked by the piston B; the outlet B end of the sequence valve (403) is connected to the inlet of the first check valve (404), and the outlet of the first check valve (404) is connected to the inlet of the first check valve (404). The outlet is connected to the small chamber (401-1) of the boosting cylinder (401), the small chamber (401-1) of the boosting cylinder (401) is connected to the inlet of the second one-way valve (405), and the outlet of the second one-way valve (405) is connected to the oil circuit from the outlet B end of the hydraulically controlled one-way valve (301) to the rodless chamber of the tensioning cylinder (500); the middle chamber (401-2) of the boosting cylinder (401) is connected to the oil return branch through the second oil circuit branch (602), and the oil control interface X end of the hydraulically controlled one-way valve (301) is connected to the second oil circuit branch (602).
5. A hydraulic system for rapid tensioning of tensioning machines according to claim 4, characterized in that: The valve is configured as a three-position four-way electromagnetic reversing valve (201), the three-position four-way electromagnetic reversing valve (201) comprising an inlet P end, an outlet T end, an interface A end and an interface B end, the three-position four-way electromagnetic reversing valve (201) is provided with a first control electromagnet YV1a and a second control electromagnet YV1b, the inlet P end of the first control electromagnet YV1a being connected to the interface A end and the outlet T end being connected to the interface B end when the first control electromagnet YV1a is powered on, the inlet P end of the second control electromagnet YV1b being connected to the interface The B end is connected, the outlet T end is connected with the interface A end, the first control electromagnet YV1a and the second control electromagnet YV1b are both powered off, the three-position four-way electromagnetic reversing valve (201) is closed, the interface A end is disconnected, the interface B end is disconnected, and the inlet P end is connected with the outlet T end; the oil supply end (101) of the hydraulic oil supply module (100) is connected to the inlet P end of the three-position four-way electromagnetic reversing valve (201), and the outlet T end of the three-position four-way electromagnetic reversing valve (201) is connected to the oil return end (102).
6. A hydraulic system for rapid tensioning of tensioning machines according to claim 5, characterized in that: The interface B end of the three-position four-way electromagnetic reversing valve (201) is connected to the oil inlet branch, and the interface A end of the three-position four-way electromagnetic reversing valve (201) is connected to the oil return branch.
7. A hydraulic system for rapid tensioning of tensioning machines according to claim 6, characterized in that: The low-pressure drive oil circuit (300) further comprises a first pressure switch (302) and a second pressure switch (303), wherein the first pressure switch (302) is arranged on the oil circuit from the outlet B end of the hydraulically controlled one-way valve (301) to the rodless chamber of the tensioning cylinder (500), and the second pressure switch (303) is arranged on the oil circuit from the rod chamber of the tensioning cylinder (500) to the interface A end of the three-position four-way electromagnetic reversing valve (201).
8. A hydraulic system for rapid tensioning of tensioning machines according to any one of claims 4 to 7, characterized in that: The rapid tensioning hydraulic system of the tensioning machine is provided with a tensioning cylinder low-load rapid extension working condition driven by a low-pressure driving oil circuit (300) and a tensioning cylinder high-load slow extension working condition driven by a boost driving oil circuit (400). The hydraulic oil driving pressure is sensed by a sequence valve (403) to switch between the tensioning cylinder low-load rapid extension working condition and the tensioning cylinder high-load slow extension working condition.
9. A hydraulic system for rapid tensioning of tensioning machines according to claim 7, characterized in that: The rapid tensioning hydraulic system of the tensioning machine is provided with a rapid retraction working condition of the tensioning cylinder. When the hydraulic oil flowing into the tensioning cylinder (500) exceeds the set pressure of the first pressure switch (302), the first pressure switch (302) transmits a signal to energize the first control electromagnet YV1a of the three-position four-way electromagnetic reversing valve (201), thereby executing the rapid retraction working condition of the tensioning cylinder.
10. A hydraulic system for rapid tensioning of a tensioning machine according to claim 2, characterized in that: The hydraulic oil supply module (100) further comprises an oil tank (103), an oil drain ball valve (104), an oil suction filter (105), an air filter (106), a liquid level thermometer (107), a three-phase asynchronous motor (108), a coupling (109), a metering pump (110), a third one-way valve (111), a shockproof pressure gauge (112), a relief valve (113), a temperature switch (114) and a forced air cooler (115); the oil drain ball valve (104) is arranged at the bottom of the oil tank (103); the oil suction filter (105), the air filter (106) and the liquid level thermometer (107) are arranged in the oil tank (103); the oil suction filter (105) is connected to the metering pump (110), and the metering pump (110) is connected to the metering pump (110) through the coupling (109). The three-phase asynchronous motor (108) is connected to be driven by the three-phase asynchronous motor (108); the outlet of the quantitative pump (110) is connected to the inlet of the third one-way valve (111), and the outlet of the third one-way valve (111) is connected to the oil supply end (101); the shockproof pressure gauge (112) is connected to the oil line from the outlet of the third one-way valve (111) to the oil supply end (101); the forced air cooler (115) is arranged on the oil line from the return oil end (102) to the oil tank (103), and the temperature switch (114) monitors the oil temperature, and starts the forced air cooler (115) when the oil temperature exceeds a preset temperature; an overflow branch is arranged between the oil supply end (101) and the return oil end (102), and the overflow valve (113) is arranged on the overflow branch, and when the oil pressure exceeds the preset pressure, the overflow valve (113) is turned on to overflow.