Tensioning hydraulic system and inhaul cable tensioning system

Abstract

The invention discloses a tensioning hydraulic system and an inhaul cable tensioning system.The tensioning hydraulic system comprises a tensioning oil cylinder and a main valve, the tensioning oil cylinder comprises a cylinder barrel, a piston assembly and a piston rod locking assembly, and the piston assembly comprises a first piston rod end extending out of the first end of the cylinder barrel and a second piston rod end extending out of the second end of the cylinder barrel; the first piston rod end is an inhaul cable connecting end, the piston rod locking assembly is used for limiting the second piston rod end, the cylinder barrel comprises a first cylinder barrel oil port formed in the first end of the cylinder barrel and a second cylinder barrel oil port formed in the second end of the cylinder barrel, and the main valve comprises a main valve plate hydraulically connected with the first cylinder barrel oil port and the second cylinder barrel oil port; by means of the tensioning hydraulic system, hydraulic tensioning of the inhaul cable can be achieved, the hydraulic driving power density is high, the load capacity is high, and the tensioning hydraulic system is particularly suitable for scenes with large tensioning force.

Description

TECHNICAL FIELD

[0001] The application belongs to the technical field of tower crane equipment, and particularly relates to a tensioning hydraulic system and a cable tensioning system. BACKGROUND

[0002] For a tower building or equipment of steel structure, such as a power tower, a communication signal base station, a tower crane and the like, a pull rod or cable system is usually needed to be added to improve the stability and rigidity of the structure. In order to ensure that the pull rod or cable system reaches the required tension, a tensioning device needs to be used to tension the pull rod system. The existing tensioning device generally adopts a mechanical screw structure for tensioning, and the structure comprises an upper pull rod, a lower pull rod and a nut. The upper pull rod and the lower pull rod are both screw rods and are connected through the nut. By rotating the nut, the relative distance between the upper pull rod and the lower pull rod can be adjusted, so as to realize the relaxation or tensioning of the pull rod system. However, the tensioning force of this tensioning device is borne by the screw thread joint of the screw rod and the nut. With the tensioning process, the torque required for rotating the nut increases with the increase of the friction force on the screw thread contact surface. The manual tensioning becomes more and more laborious, and the tensioning force increases to a certain value, which cannot be completed by manpower.

[0003] CONTENT OF THE APPLICATION In view of the above defects or deficiencies, the application provides a tensioning hydraulic system and a cable tensioning system, aiming to solve the technical problem that the existing technology needs manual operation and is not suitable for a pull rod system with a large tensioning force.

[0004] To achieve the above-mentioned purpose, the first aspect of the application provides a tensioning hydraulic system, comprising a tensioning oil cylinder and a main valve. The tensioning oil cylinder comprises a cylinder barrel, a piston assembly and a piston rod locking assembly. The piston assembly comprises a first piston rod end extending from a first end of the cylinder barrel and a second piston rod end extending from a second end of the cylinder barrel. The first piston rod end is a cable connecting end. The piston rod locking assembly is used to limit the second piston rod end. The cylinder barrel comprises a first cylinder barrel oil port arranged at the first end of the cylinder barrel and a second cylinder barrel oil port arranged at the second end of the cylinder barrel. The main valve comprises a main valve piece hydraulically connecting the first cylinder barrel oil port and the second cylinder barrel oil port.

[0005] In the embodiment of the application, the main valve piece is an electromagnetic reversing valve.

[0006] In the embodiment of the application, the main valve piece is an electric proportional reversing valve with O-type neutral function.

[0007] In the embodiment of the application, the tensioning hydraulic system comprises: a first pressure sensor for detecting the oil pressure at the first cylinder barrel oil port; a second pressure sensor for detecting the oil pressure at the second cylinder barrel oil port; and a controller configured to: obtain the pressure detection values of the first pressure sensor and the second pressure sensor; determine the tensioning force of the tensioning oil cylinder according to the pressure detection values and the tensioning force calculation formula; The tensioning force calculation formula is F=(P1-P2)×S, F is the tensioning force of the tensioning oil cylinder, P1 is the pressure detection value of the first pressure sensor, P2 is the pressure detection value of the second pressure sensor, and S is the effective acting area of the piston rod of the tensioning oil cylinder.

[0008] In the embodiment of the application, the controller is further configured to: determine that the tensioning force of the tensioning oil cylinder reaches a preset tensioning value; issue a piston rod fixing signal.

[0009] In the embodiment of the application, the tensioning hydraulic system includes a plurality of tensioning oil cylinders, and the main valve is a multi-way valve and includes a plurality of main valve plates that control the plurality of tensioning oil cylinders one by one. Each tensioning oil cylinder is configured with a piston displacement sensor, and the tensioning hydraulic system further includes a controller in communication with each piston displacement sensor, and the controller is configured to: determine that each main valve plate is in a synchronous working state; real-time acquire displacement detection values of each piston displacement sensor, and real-time acquire a maximum displacement difference value according to a displacement difference value between any two displacement detection values; determine that the maximum displacement difference value reaches a preset displacement difference value; control the tensioning oil cylinder with the maximum piston rod stroke to stop oil supply.

[0010] In the embodiment of the application, the controller is further configured to: determine that the maximum displacement difference value is not greater than a safety displacement difference value; control the tensioning oil cylinder with the maximum piston rod stroke to resume oil supply; The safety displacement difference value is less than the preset displacement difference value.

[0011] In the embodiment of the application, the tensioning hydraulic system includes: An overflow valve is hydraulically connected to the oil inlet of the main valve.

[0012] In the embodiment of the application, the tensioning hydraulic system includes: A pressure gauge is arranged at the pumping oil port of the main pump.

[0013] In the embodiment of the application, the main valve is a hand-operated reversing valve.

[0014] To achieve the above-mentioned purpose, the second aspect of the application provides a cable tensioning system, which includes a fixed base, a cable, and the above-mentioned tensioning hydraulic system. The cylinder barrel is hinged to the base, one end of the cable is connected to the tower body, and the other end is connected to the first piston rod end.

[0015] By the technical solution, the tensioning hydraulic system has the following beneficial effects: When the tensioning hydraulic system is used, the cylinder barrel can be arranged on the corresponding fixed base, the first piston rod end is connected with the cable, before the cable is tensioned, the main valve plate controls the second cylinder barrel oil port to enter oil, the first cylinder barrel oil port returns oil, until the first piston rod end is completely extended, at this time, the cable is in a relaxed state; when the tensioning operation is performed, the main valve plate is switched to control the first cylinder barrel oil port to enter oil, the second cylinder barrel oil port returns oil, the first piston rod end is gradually retracted, and the cable is gradually tensioned; after the cable is in a tensioned state, the second piston rod end is limited by the piston rod locking assembly, at this time, the reaction force of the cable on the first piston rod end is transmitted to the cylinder barrel through the piston rod locking assembly, and the cylinder barrel transmits the force to the fixed base, so that the cable is fixed, and the tensioning hydraulic system can realize hydraulic tensioning of the cable, and has high hydraulic driving power density and strong load capacity, and is especially suitable for scenes with large tensioning force.

[0016] Other features and advantages of the present application will be described in detail in the following specific embodiments. BRIEF DESCRIPTION OF DRAWINGS

[0017] The accompanying drawings are included to provide a further understanding of the present application, and constitute a part of the specification, and are used together with the following specific embodiments to explain the present application, but do not constitute a limitation on the present application. In the drawings: Figure 1 is a hydraulic principle diagram of the tensioning hydraulic system according to an embodiment of the present application; Figure 2 is a hydraulic principle diagram of the tensioning hydraulic system according to another embodiment of the present application; Figure 3 is a sectional view of the tensioning cylinder according to an embodiment of the present application; Figure 4 is a top view of the tensioning cylinder according to an embodiment of the present application; Figure 5 is a schematic view of the rotary driving mechanism according to an embodiment of the present application; Figure 6 is a schematic view of the cable tensioning system according to an embodiment of the present application; Figure 7 is a control flowchart of the controller according to an embodiment of the present application.

[0018] BRIEF DESCRIPTION OF DRAWINGS DETAILED DESCRIPTION

[0019] The specific embodiments of the present application are described in detail below with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are only used to illustrate and explain the present application, and are not used to limit the present application.

[0020] The tensioning hydraulic system and the cable tensioning system of the present application are described below with reference to the accompanying drawings.

[0021] As shown in Figure 1 and Figure 3 The present application provides a tensioning hydraulic system, comprising: a tensioning oil cylinder, comprising a cylinder barrel 1, a piston assembly and a piston rod locking assembly 4, the piston assembly comprising a first piston rod end 2 extending from a first end of the cylinder barrel 1 and a second piston rod end 3 extending from a second end of the cylinder barrel 1, the first piston rod end 2 being a cable connecting end, the piston rod locking assembly 4 being used to limit the second piston rod end 3, the cylinder barrel 1 comprising a first cylinder barrel oil port 11 arranged at the first end of the cylinder barrel 1 and a second cylinder barrel oil port 12 arranged at the second end of the cylinder barrel 1; a main valve, comprising a main valve disc 81 hydraulically connected to the first cylinder barrel oil port 11 and the second cylinder barrel oil port 12.

[0022] The existing device relies on manual screwing of nuts to adjust the distance between the upper and lower pull rods. For scenes with large tensioning force, it is difficult to complete only by relying on human power. In view of this problem, the present application designs a tensioning hydraulic system, which replaces manual operation by using a tensioning oil cylinder. Correspondingly, the system also comprises a main pump 86 and a main valve for realizing hydraulic driving of the tensioning oil cylinder. The main valve disc 81 of the main valve can correspondingly control one of the first cylinder barrel oil port 11 and the second cylinder barrel oil port 12 to be an oil inlet port, and the other to be an oil return port, so as to realize control of the extension and retraction direction of the piston rod of the tensioning oil cylinder. Then, through the tensioning hydraulic system, hydraulic tensioning of the cable 7 can be realized, and the hydraulic driving power density is high and the load capacity is large, which is especially suitable for scenes with large tensioning force.

[0023] In addition, considering that the tensioning hydraulic system of the application needs to keep the cable 7 in the tensioned state for a long time after the cable 7 is tensioned, the tensioning oil cylinder of the application is provided with a double-piston rod hydraulic cylinder and a piston rod locking assembly 4. The first piston rod end 2 extends from the first end of the cylinder barrel 1 and is used to connect the cable 7. The second piston rod end 3 extends from the second end of the cylinder barrel 1. After the cable 7 is tensioned, the second piston rod end 3 is limited and locked by the piston rod locking assembly 4. At this time, even if the main pump 86 is turned off and the pressure on the piston rod is removed, the entire piston rod still remains in the position of tensioning the cable 7 due to the limiting action of the piston rod locking assembly 4. It can be understood that if a single-piston hydraulic cylinder is provided, the piston rod can only be maintained in the position of tensioning the cable 7 by hydraulic pressure. The cylinder barrel 1 must be kept in a high-pressure closed environment for a long time by a corresponding valve assembly. This has high requirements for the valve assembly and the corresponding oil port connection structure. Once the hydraulic oil leaks, the tensioning of the cable 7 is immediately invalid, which seriously affects the safety of the tower device or the building. In the application, the piston rod is mechanically locked by the piston rod locking assembly 4 after tensioning, and the tensioning oil cylinder does not need to continue to be supplied with hydraulic oil, which effectively reduces the use cost and improves the safety in the long-term tensioning state.

[0024] Specifically, the working process of the tensioning hydraulic system of the application is as follows: the cylinder barrel 1 is hinged to the fixed base 6, and the first piston rod end 2 is connected to the cable 7. Before tensioning the cable 7, the main valve plate 81 controls the second cylinder barrel oil port 12 to inlet oil and the first cylinder barrel oil port 11 to outlet oil until the first piston rod end 2 is fully extended. At this time, the cable 7 is in a relaxed state. When tensioning is performed, the main valve plate 81 is switched to control the first cylinder barrel oil port 11 to inlet oil and the second cylinder barrel oil port 12 to outlet oil. The first piston rod end 2 is gradually retracted, and the cable 7 is gradually tensioned. When the cable 7 is in a tensioned state, the second piston rod end 3 is limited by the piston rod locking assembly 4. At this time, the reaction force of the cable 7 on the first piston rod end 2 is transmitted to the cylinder barrel 1 through the piston rod locking assembly 4. The cylinder barrel 1 transmits the force to the fixed base 6 through the pin shaft between the cylinder barrel 1 and the fixed base 6, thereby fixing the cable 7.

[0025] The main valve plate 81 is used to select one of the first cylinder barrel oil port 11 and the second cylinder barrel oil port 12 as an inlet oil port and the other as an outlet oil port. In order to realize quick and accurate switching of the two functions, the main valve plate 81 is an electromagnetic reversing valve in the embodiment of the application. The electromagnetic reversing valve can cooperate with a corresponding controller and control program to realize automatic control of the tensioning oil cylinder, accurately control the inlet and outlet of the oil cylinder oil port according to the actual demand, and further improve the efficiency and stability of the tensioning operation.

[0026] As Figure 2As shown, in other embodiments of the present application, the main valve plate 81 can also be a manual reversing valve. The manual reversing valve has the characteristics of simple and intuitive operation, and the operator can flexibly control the flow direction of the hydraulic oil according to the actual work requirements, thereby realizing precise control of the action of the tensioning system. This manual operation mode can fully play its advantages in some occasions with high requirements for operation flexibility and immediacy. For example, during the installation and debugging of the equipment, the operator can quickly adjust the state of the tensioning system through the manual reversing valve, facilitating the positioning and calibration of the components of the equipment. It can be understood that after the tensioning hydraulic system completes the tensioning operation, if there is no need for maintenance and debugging, the tensioning oil cylinder will not act, and the cost of setting the manual reversing valve is lower. In addition, the manual reversing valve relies on mechanical structure action, and even in complex and harsh working environments, the probability of failure is relatively small.

[0027] Further, in order to improve the operation convenience and safety of the manual reversing valve, an anti-slip and anti-misoperation structure can also be designed on the operating handle of the valve to ensure that the operator can accurately control the valve during operation and avoid safety accidents caused by misoperation.

[0028] The hydraulic tensioning system of the present application is generally used for tensioning the cable 7 of large buildings or equipment such as tower cranes, power towers, and communication signal base stations. When performing the tensioning operation, it is necessary to not only ensure the operation efficiency, but also avoid the impact on the tower body caused by too fast tensioning speed. Since the general reversing valve can only realize the switching selection of the oil circuit, the hydraulic oil always enters the cylinder barrel 1 at a constant rate, i.e., the tensioning speed is constant, and it cannot be adjusted. Therefore, in the embodiments of the present application, the main valve plate 81 is an electric proportional reversing valve with O-type neutral function. The electric proportional reversing valve controls the opening size of the valve core by means of electric signal, thereby adjusting the oil inlet amount of the oil cylinder to control the extension and retraction speed of the first piston rod end 2, so as to control the tensioning speed of the tensioning oil cylinder. Specifically, the controller of the tensioning hydraulic system is configured to control the opening size of the valve core of the electric proportional reversing valve according to the size of the real-time tensioning force. The larger the tensioning force, the smaller the opening of the valve core, and the slower the extension and retraction speed of the first piston rod end 2.

[0029] Of course, the present application is not limited thereto, and in other embodiments, the main valve plate 81 can also be set as an electric proportional reversing valve with Y-type neutral function. The neutral function of the Y-type reversing valve is that when in neutral position, the oil inlet is closed, the working oil port is communicated with the oil return tank port, the tensioning oil cylinder piston is floating, and the pump is not unloaded, so the piston rod locking assembly 4 needs to be set to limit the piston rod before controlling the Y-type reversing valve to switch to the neutral position.

[0030] Alternatively, the main valve plate 81 can also be configured as an electro-proportional directional valve with an H-type neutral position function. When the valve core of the H-type directional valve is in the neutral position, all oil ports are in an unloaded state, allowing the main pump 86 to be directly unloaded, while the tension cylinder piston floats. Therefore, it is necessary to limit the piston rod by setting the piston rod locking assembly 4 and to control the Y-type directional valve to switch to the neutral position after shutting down the main pump 86.

[0031] For large structures or equipment such as tower cranes, power towers, and communication signal base stations, the tension of their cables 7 must meet design requirements. However, existing tensioning devices cannot measure the tension of the cables 7 and can only rely on the experience of operators to judge whether the tension is in place, which involves great uncertainty. Therefore, in this embodiment, the tensioning hydraulic system also includes a first pressure sensor 82, a second pressure sensor 83, and a controller; the first pressure sensor 82 is used to detect the oil pressure at the first cylinder port 11; the second pressure sensor 83 is used to detect the oil pressure at the second cylinder port 12; the controller is configured as follows: Acquire the pressure detection values ​​of the first pressure sensor 82 and the second pressure sensor 83; The tensioning force of the tensioning cylinder is determined based on the pressure detection value and the tensioning force calculation formula. The tension force is calculated as F = (P1 - P2) × S, where F is the tension force of the tensioning cylinder, P1 is the pressure detection value of the first pressure sensor 82, P2 is the pressure detection value of the second pressure sensor 83, and S is the effective working area of ​​the piston rod of the tensioning cylinder.

[0032] By setting up a first pressure sensor 82 and a second pressure sensor 83, the tensioning force of the tensioning cylinder can be calculated in real time, providing accurate data support for the stable operation of the system. Based on this real-time data, the controller can flexibly and accurately adjust the tensioning hydraulic system to adapt to changes in the tensioning force required for the cable 7 under different working conditions. Compared with the scheme of setting a tension sensor between the first piston rod end 2 and the cable 7, this scheme eliminates the need for an additional tension sensor in a confined space, greatly reducing installation difficulty and space occupation, and minimizing potential malfunctions caused by complex installation. Furthermore, using pressure sensors is more cost-effective and easier to maintain, effectively reducing the overall system cost and maintenance workload while ensuring detection accuracy.

[0033] Understandably, after tensioning is completed, the piston rod locking assembly 4 needs to be installed promptly. The conventional method is to manually monitor the tension force and take appropriate actions in a timely manner. However, this method requires operators to constantly monitor the tension force, which is time-consuming, labor-intensive, and lacks timely response. Therefore, in this embodiment, the controller is also configured to: Ensure that the tensioning force of the tensioning cylinder reaches the preset tension value; Send a signal to fix the piston rod.

[0034] After the controller sends a signal to fix the piston rod, the main valve plate 81 of the electromagnetic reversing valve can directly respond to the signal and act. This automated operation can effectively reduce the burden on operators, improve response speed, and ensure that the stability of the tower body is not affected by excessive tension. Furthermore, in the embodiments of this application, the piston rod locking assembly 4 can limit the piston rod by manual operation by an operator or by automatic limiting through a corresponding drive mechanism.

[0035] For the manually operated piston rod locking assembly 4, a corresponding indicator light or buzzer can also be set. After the controller sends a piston rod fixing signal, the indicator light or buzzer will emit a corresponding light or sound signal to prompt the operator to perform the piston rod fixing operation in a timely manner.

[0036] For the automatically operated piston rod locking assembly 4, after the controller sends a piston rod fixing signal, the system automatically executes the piston rod fixing action, locking the piston rod through a mechanical structure to ensure that the tensioning cylinder maintains a stable tension state.

[0037] For large buildings or equipment such as tower cranes, power towers, and communication signal base stations, the number of cables 7 configured is generally multiple, thereby stabilizing the tower body in multiple directions. Therefore, in this embodiment, the tensioning hydraulic system includes multiple tensioning cylinders, and the main valve is a multi-way valve including multiple main valve plates 81 that control the multiple tensioning cylinders one-to-one.

[0038] Considering that the load on the tensioning cylinder changes dynamically during the tensioning process, and the strokes of each first piston rod end 2 also differ, when the displacement difference is too large, the multiple cables 7 connecting the tower body will experience uneven stress, and the tower body will easily tilt to one side of one of the cables 7. To overcome this problem, in this embodiment, each tensioning cylinder is equipped with a piston displacement sensor 87, and the tensioning hydraulic system also includes a controller that communicates with each piston displacement sensor 87, such as... Figure 7 As shown, the controller is configured as follows: S100, confirm that each main valve plate 81 is in a synchronous working state; S200 acquires the displacement detection values ​​of each piston displacement sensor 87 in real time, and acquires the maximum displacement difference in real time based on the displacement difference between any two displacement detection values. S300, determine that the maximum displacement difference has reached the preset displacement difference; S400 controls the tensioning cylinder to stop supplying oil when the piston rod has reached its maximum stroke.

[0039] Through steps S100 to S400 of the piston rod displacement sensor and controller, multiple tensioning cylinders in the tensioning hydraulic system can be effectively and precisely controlled. In cases of excessive displacement difference, the oil supply to the tensioning cylinder at the end of the first piston rod with the largest stroke is promptly cut off to prevent the tower body from tilting. Specifically, during step S100, the main valve plate 81 is in the working state, switching to control the first cylinder oil port 11 as the oil inlet. At this time, the first piston rod end 2 retracts, and the cable 7 is gradually tensioned. When all the main valve plates 81 are in a synchronous working state, the multiple cables 7 connected to the tower body are simultaneously tensioned.

[0040] After step S400 is completed, the maximum displacement difference decreases, such as... Figure 7 As shown, to further improve the automation level of the tensioning hydraulic system, in this embodiment of the application, the controller is also configured to, after step S400: S500, determine that the maximum displacement difference is not greater than the safe displacement difference; S600, the tension cylinder that controls the piston rod stroke to the maximum resumes oil supply; Among them, the safe displacement difference is less than the preset displacement difference.

[0041] Specifically, after cutting off the oil supply in step S400, the displacement of each first piston rod end 2 is continuously monitored by displacement sensors to determine the change in the current maximum displacement difference. In step S500, the determined maximum displacement difference is compared with the safe displacement difference. If the maximum displacement difference is not greater than the safe displacement difference, it indicates that the uneven stress on each cable 7 has been effectively improved, and the risk of tower tilting has been reduced to an acceptable range. Therefore, in step S600, the controller controls the tensioning cylinder with the largest piston rod stroke to resume oil supply, allowing the entire tensioning hydraulic system to continue working, and each cable 7 to be continuously and synchronously tensioned, ensuring the stable construction of the tower.

[0042] Specifically, the safety displacement difference can be set as needed. In one embodiment, the safety displacement difference is set to 0, that is, when the maximum displacement difference exceeds the preset displacement difference, the controller will control each main valve plate 81 to move one by one until the stroke of the first piston rod end 2 of all tensioning cylinders is the same.

[0043] Specifically, the tensioning hydraulic system also includes an oil tank, a main pump 86, and connecting oil lines. The oil tank is used to supply hydraulic oil. The input port of the main pump 86 is hydraulically connected to the oil tank. The output port of the main pump 86 is hydraulically connected to the oil inlet of the main valve plate 81. The working oil port of the main valve plate 81 is hydraulically connected to the cylinder oil port of the cylinder 1. The return oil port of the main valve plate 81 is hydraulically connected to the oil tank.

[0044] Furthermore, as mentioned earlier, by setting corresponding pressure sensors and controllers, excessive tension can be avoided, and the pressure within the system can be kept within a safe range. However, if the actuators or pipelines become blocked, the system pressure will rise rapidly, making it difficult for the controller to respond quickly, posing a safety risk. Therefore, the tensioning hydraulic system also includes a relief valve 84, which is hydraulically connected to the inlet of the main valve. The relief valve 84 effectively prevents excessive system pressure. When the pressure at the main valve inlet exceeds the set pressure of the relief valve 84, the relief valve 84 opens, allowing some oil to flow back to the oil tank, thereby ensuring the safe and stable operation of the tensioning hydraulic system.

[0045] Furthermore, the relief valve 84 is configured as an electro-proportional relief valve. Compared to a conventional relief valve 84, the electro-proportional relief valve can precisely control the relief pressure based on an electrical signal, enabling more accurate regulation of the system pressure. This allows the tensioning hydraulic system to flexibly and stably maintain a suitable pressure level under different working scenarios and load conditions. Moreover, after the second piston rod end 3 is limited by the piston rod locking assembly 4, the system no longer needs to maintain a high-pressure hydraulic environment. The controller can adjust the relief pressure of the electro-proportional relief valve to 0, allowing the high-pressure oil in the system to flow back to the oil tank.

[0046] Furthermore, the tensioning hydraulic system also includes a pressure gauge 85, which is located at the pumping port of the main pump 86. The function of the pressure gauge 85 is to allow operators to visually understand the internal pressure of the tensioning hydraulic system, thereby promptly detecting any abnormal pressure conditions. When the pressure is too high, it may indicate a blockage or other malfunction within the system. Operators can quickly take appropriate measures based on the pressure gauge 85 reading, such as checking pipelines and troubleshooting valve malfunctions, to prevent damage to system components due to excessive pressure. When the pressure is too low, it may indicate a pump malfunction or oil leakage. Operators can promptly perform repairs or replenish oil based on the feedback from the pressure gauge 85. In addition, by observing the changes in the pressure gauge 85 over a long period, the overall operating status of the tensioning hydraulic system can be assessed and predicted, allowing for preventative maintenance and further ensuring the stable operation of the system. Furthermore, the tensioning hydraulic system is also equipped with a suction filter, which is installed on the connecting oil line between the main pump 86 and the oil tank. The suction filter is used to filter impurities in the oil, ensuring the normal operation of each component in the system, avoiding wear or blockage of the cylinder, valve and other components caused by impurities, and effectively extending the service life of each component.

[0047] Furthermore, the tensioning hydraulic system is also equipped with a temperature sensor located inside the oil tank, which can monitor the oil temperature in real time. When the oil temperature is too high, the temperature sensor transmits a signal to the controller, which then activates the cooling device to cool the oil, ensuring that the system operates stably within a suitable oil temperature range. This is because excessively high oil temperatures can affect the viscosity of the oil, thereby impacting the system's pressure and flow stability.

[0048] Furthermore, the tensioning hydraulic system is also equipped with a level sensor to monitor the oil level in the tank in real time. If the level is too low, the level sensor will issue an alarm signal to remind the staff to replenish the oil in time to prevent system failure due to insufficient oil. Furthermore, the oil tank of the tensioning hydraulic system is also equipped with an air filter. When the oil volume decreases or the temperature changes, causing the pressure inside the oil tank to change, air enters and exits the oil tank through the air filter. During this process, the air filter filters out pollutants such as dust and particles from the air.

[0049] Furthermore, the tensioning hydraulic system is also equipped with a return oil filter, which is located on the return oil main line connecting the oil circuit. The return oil main line is equipped with a return oil branch line for hydraulically connecting the relief valve 84 and the main valve plate 81.

[0050] In this embodiment, the second piston rod end 3 is a threaded connection end, and the piston rod locking assembly 4 includes a tension nut 41. The tension nut 41 is threadedly connected to the second piston rod end 3 and presses against the end face of the cylinder 1. The second piston rod end 3 has an external thread. By tightening the tension nut 41, its position on the second piston rod end 3 can be steplessly adjusted. After the cable 7 is tensioned, the tension nut 41 can be tightened until it abuts against the second end of the cylinder 1. The reaction force of the cable 7 on the first piston rod end 2 is transmitted to the tension nut 41 through the thread. The tension nut 41 acts on the second end of the cylinder 1, and then the cylinder 1 transmits the force to the fixed base 6, thus fixing the cable 7.

[0051] Of course, this application is not limited to this. The second piston rod section can also be set as a locking hole end, that is, the second piston rod end 3 is provided with multiple locking holes for the pin shaft to pass through. The piston rod locking assembly 4 can be set as a pin shaft. After the cable 7 is tensioned, the pin shaft can be passed into the corresponding locking hole so that the pin shaft abuts against the second end of the cylinder 1. The reaction force of the cable 7 on the first piston rod end 2 is applied to the cylinder 1 through the pin shaft. The cylinder 1 then transmits the force to the fixed base 6 to achieve the fixation of the cable 7.

[0052] like Figure 3As shown in this embodiment, the piston rod locking assembly 4 further includes a spacer 42, which is fitted between the cylinder 1 and the tension nut 41. The tension nut 41 is used to abut the spacer 42 against the end face of the cylinder 1. The spacer 42 reduces the length of the external thread section on the second piston rod end 3. It is understood that without the spacer 42, the external thread section needs to extend to the second end of the cylinder 1, while with the spacer 42, the external thread section only needs to extend to the position of the spacer 42. This reduces the processing difficulty and cost of the second piston rod end 3. Furthermore, the presence of the spacer 42 increases the contact area between the tension nut 41 and the cylinder 1, making the force transmission more uniform and effectively preventing deformation or damage to the end face of the cylinder 1 due to excessive local force. In addition, the spacer 42 also provides a certain buffering effect. When the cable 7 vibrates or is impacted during operation, the spacer 42 absorbs some energy, further protecting the cylinder 1 and the tension nut 41 and extending the service life of the entire tensioning device. Furthermore, to facilitate the installation and removal of the spacer 42, an anti-slip texture or a handle structure can be provided on the outer surface of the spacer 42 to improve the convenience and efficiency of operation. like Figure 4 As shown in this embodiment, the spacer 42 is sleeve-shaped and includes stop portions 422 at both ends and a central cylindrical section 421. The outer diameter of the stop portions 422 is larger than the outer diameter of the cylindrical section 421. The design of the stop portions 422 effectively restricts the axial movement of the spacer 42 within the cylinder 1, ensuring its stability during operation. The larger outer diameter of the stop portions 422 results in a larger contact area with the inner wall of the cylinder 1, further enhancing the uniformity of force transmission. When the tension nut 41 is tightened, the stop portions 422 can better distribute pressure, preventing wear or deformation of the inner wall of the cylinder 1 due to localized pressure concentration. In this embodiment, multiple spacers 42 are used. It is understood that in actual use, the length of the cable 7 and the installation position of the cylinder 1 will cause differences in the piston rod stroke. By setting multiple spacers 42, they can be flexibly combined according to specific needs to adapt to different piston rod stroke requirements. Using different numbers of spacers 42 allows for precise adjustment of the overall length of the tensioning device, thereby meeting the tensioning requirements of the cable 7 under different working conditions. For example, when the cable 7 is long and requires a larger tension stroke, the number of spacers 42 can be increased; conversely, when the cable 7 is short and requires a smaller tension stroke, the number of spacers 42 can be appropriately reduced. Furthermore, the multiple spacers 42 also facilitate maintenance and replacement. If one of the spacers 42 is worn or damaged, only that spacer 42 needs to be replaced individually, without requiring large-scale disassembly and replacement of the entire tensioning device, reducing maintenance and time costs. like Figure 3 and Figure 4As shown in this embodiment, the piston rod locking assembly 4 further includes an anti-loosening nut 43, which is threadedly connected to the second piston rod end 3 and located on the side of the tensioning nut 41 facing away from the cylinder 1. The anti-loosening nut 43 further enhances the stability of the tensioning device. It is understood that during equipment operation, the tensioning nut 41 may loosen due to factors such as vibration, leading to changes in tension force and affecting the normal operation of the tensioning cylinder. The anti-loosening nut 43 can effectively resist the loosening tendency caused by vibration, prevent the tensioning nut 41 from moving, keep the tensioning nut 41 in a tightened state, and maintain a stable tension force on the cable 7.

[0053] like Figure 5 As shown in this embodiment, the tensioning cylinder further includes a rotary drive mechanism 5 mounted on the cylinder barrel 1. The rotary drive mechanism 5 drives the tensioning nut 41 to move helically along the end 3 of the second piston rod. The rotary drive mechanism 5 further improves the ease of use of the tensioning cylinder. The rotary drive mechanism 5 can quickly and accurately adjust the position of the tensioning nut 41 through an automated driving method. Compared with manual adjustment, this not only improves work efficiency but also allows for precise adjustment of the preload of the tensioning nut 41.

[0054] Specifically, the rotary drive mechanism 5 has a preload detection module, which measures the preload of the tension nut 41 and sends a nut positioning signal when the preload reaches a preset value. The controller is communicatively connected to the rotary drive mechanism 5 and is configured as follows: Send a piston rod fixing signal to the rotary drive mechanism 5; Upon receiving the nut positioning signal, a stop signal is sent to the rotary drive mechanism 5, and the main valve plate 81 is switched to the neutral position, and the overflow valve 84 is adjusted to 0 overflow pressure.

[0055] Understandably, when the rotary drive mechanism 5 receives the piston rod fixing signal, it drives the tension nut 41 to move along the second piston rod end 3. When it receives the stop signal, it disconnects the drive, the main valve plate 81 switches to the neutral position, and the oil circuits connected to the first cylinder oil port 11 and the second cylinder oil port 12 are both in the cut-off state, and oil cannot enter or return. The main pump 86 also stops working simultaneously. After the overflow pressure is adjusted to 0 by the overflow valve 84, the excess hydraulic oil returns to the oil tank through the overflow oil circuit where the overflow valve 84 is located or the passage on the main valve plate 81.

[0056] Specifically, the rotary drive mechanism 5 includes a first motor 51 and a first drive gear 53 disposed on the output shaft of the first motor 51. A tension gear part 411 is correspondingly disposed on the outer peripheral wall of the tension nut 41. The first drive gear 53 meshes with the tension gear part 411. The first motor 51 drives the first drive gear 53 to rotate, thereby driving the tension gear part 411 meshing with it to rotate, so as to realize the spiral movement of the tension nut 41 along the end of the second piston rod 3.

[0057] Furthermore, the first motor 51 is mounted on the cylinder 1 and tilts and swings synchronously with the cylinder 1. Because the first motor 51 moves synchronously with the cylinder 1, the first drive gear 53 and the tension gear part 411 are always in a meshing state, ensuring the reliability of the gear transmission.

[0058] Furthermore, the preload detection module can be configured to detect the output torque or output power of the first motor 51, obtain the tightening torque of the tension nut 41 through the calculation formula of gear transmission, and then obtain the expected force of the tension nut 41 according to the calculation formula of bolt preload and bolt tightening torque.

[0059] Of course, this application is not limited to this. Alternatively, the second piston rod end 3 can be configured as a rotatable lead screw, and a slide rail parallel to the second piston rod end 3 can be provided on the cylinder. The inner wall of the tension nut 41 is threadedly connected to the second piston rod end 3, and the outer wall of the tension nut 41 is slidably connected to the slide rail. That is, the tension nut 41 and the second piston rod end 3 form a ball screw pair, and the rotary drive mechanism 5 is configured as a motor to drive the second piston rod end 3 to rotate. Specifically, the piston rod of the tensioning cylinder includes a rod body, and the second piston rod end 3 is rotatably connected to the rod body. The connection method can be that an annular groove is opened at the end of the rod body, and the second piston rod end 3 forms a sliding part embedded in the annular groove, thereby achieving a rotatable connection.

[0060] Furthermore, the rotary drive mechanism 5 also includes a second motor 52 and a second drive gear 54 disposed on the output shaft of the second motor 52. A corresponding anti-loosening gear portion 431 is disposed on the outer peripheral wall of the anti-loosening nut 43. The second drive gear 54 meshes with the anti-loosening gear portion 431. The second motor 52 drives the second drive gear 54 to rotate, thereby driving the meshing anti-loosening gear portion 431 to rotate, realizing the helical movement of the anti-loosening nut 43 along the end 3 of the second piston rod. Even further, the second motor 52 is mounted on the hydraulic cylinder and tilts and swings synchronously with the cylinder 1.

[0061] like Figure 4As shown in this embodiment, the first piston rod end 2 is provided with a plurality of parallel and spaced cable connection grooves 21 and cable connection pin holes 22 passing through the plurality of cable connection grooves 21. The cable 7 connection pin can pass through the cable connection pin hole 22 to firmly fix the cable 7 in the cable connection groove 21, ensuring the stability of the connection between the cable 7 and the tensioning cylinder and preventing the cable 7 from falling off or shifting during the tensioning process.

[0062] like Figure 6 As shown, to achieve the above objectives, a second aspect of this application provides a cable tensioning system, which includes a fixed base 6, a cable 7, and the aforementioned tensioning hydraulic system. A cylinder 1 is hinged to the base, one end of the cable 7 is connected to the tower body, and the other end is connected to the first piston rod end 2. Since the cable tensioning system employs all the technical solutions of the above embodiments, it possesses at least the aforementioned beneficial effects, which will not be elaborated upon here.

[0063] In the description of this application, it should be understood that the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this application, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0064] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection, an electrical connection, or a connection that allows communication between components; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise expressly limited. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0065] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of this application. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0066] Although embodiments of this application have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting this application. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of this application.

Claims

1. A tensioning hydraulic system, characterized in that, The tensioning hydraulic system includes: The tensioning cylinder includes a cylinder (1), a piston assembly and a piston rod locking assembly (4). The piston assembly includes a first piston rod end (2) extending from a first end of the cylinder (1) and a second piston rod end (3) extending from a second end of the cylinder (1). The first piston rod end (2) is a cable (7) connection end. The piston rod locking assembly (4) is used to limit the second piston rod end (3). The cylinder (1) includes a first cylinder oil port (11) disposed at a first end of the cylinder (1) and a second cylinder oil port (12) disposed at a second end of the cylinder (1). The main valve includes a main valve plate (81) that is hydraulically connected to the first cylinder port (11) and the second cylinder port (12).

2. The tensioning hydraulic system according to claim 1, characterized in that, The main valve plate (81) is an electromagnetic directional valve.

3. The tensioning hydraulic system according to claim 2, characterized in that, The main valve plate (81) is an electro-proportional directional valve with O-type neutral position function.

4. The tensioning hydraulic system according to claim 2 or 3, characterized in that, The tensioning hydraulic system includes: The first pressure sensor (82) is used to detect the oil pressure at the first cylinder oil port (11); The second pressure sensor (83) is used to detect the oil pressure at the second cylinder oil port (12); and The controller is configured as follows: Obtain the pressure detection values ​​of the first pressure sensor (82) and the second pressure sensor (83); The tension force of the tensioning cylinder is determined based on the pressure detection value and the tension force calculation formula. Wherein, the tension force is calculated as F = (P1 - P2) × S, where F is the tension force of the tensioning cylinder, P1 is the pressure detection value of the first pressure sensor (82), P2 is the pressure detection value of the second pressure sensor (83), and S is the effective working area of ​​the piston rod of the tensioning cylinder.

5. The tensioning hydraulic system according to claim 4, characterized in that, The controller is also configured to: Determine that the tensioning force of the tensioning cylinder reaches the preset tension value; Send a signal to fix the piston rod.

6. The tensioning hydraulic system according to claim 2 or 3, characterized in that, The tensioning hydraulic system includes multiple tensioning cylinders, and the main valve is a multi-way valve and includes multiple main valve plates (81) that control the multiple tensioning cylinders one by one. Each of the tensioning cylinders is equipped with a piston displacement sensor (87), and the tensioning hydraulic system further includes a controller that communicates with each of the piston displacement sensors (87) respectively. The controller is configured to: Ensure that each of the main valve plates (81) is in a synchronous working state; The displacement detection values ​​of each piston displacement sensor (87) are acquired in real time, and the maximum displacement difference is acquired in real time based on the displacement difference between any two displacement detection values. Determine that the maximum displacement difference reaches the preset displacement difference value; The tensioning cylinder, which controls the piston rod to its maximum stroke, stops supplying oil.

7. The tensioning hydraulic system according to claim 6, characterized in that, The controller is also configured to: It is determined that the maximum displacement difference is not greater than the safe displacement difference; The tensioning cylinder, which controls the piston rod to its maximum stroke, resumes oil supply. Wherein, the safe displacement difference is less than the preset displacement difference.

8. The tensioning hydraulic system according to claim 1, characterized in that, The tensioning hydraulic system includes: The relief valve (84) is hydraulically connected to the oil inlet of the main valve; And / or, the tensioning hydraulic system includes: A pressure gauge (85) is installed at the pumping port of the main pump (86).

9. The tensioning hydraulic system according to claim 1, characterized in that, The main valve is a manual directional valve.

10. A cable tensioning system, characterized in that, The cable tensioning system includes a fixed base (6), a cable (7), and a tensioning hydraulic system according to any one of claims 1-9. The cylinder (1) is hinged to the fixed base (6), and one end of the cable (7) is connected to the tower body and the other end is connected to the first piston rod end (2).

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