A speed regulator with pressure regulating valve control
Patent Information
- Application Number
- CN202521850065.5
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-08-29
- Publication Date
- 2026-10-27
- Estimated Expiration
- 2035-08-29
AI Technical Summary
[0004]本实用新型的目的在于提供一种具有带调压阀控制的调速器，以解决上述背景技术中提出的在当前的液压传动系统及水轮机调速器液压系统中，调压阀的控制普遍依赖调速器液压进行直接驱动，由于直接驱动模式下，液压动力的传递路径单一且缺乏中间调节环节，当系统面临负载突变、压力波动等工况时，调压阀往往难以实现快速、精准的压力调节，特别是当水轮机运行过程中，若水流冲击力度突然变化，调速器液压直接驱动的调压阀无法及时作出反应以平衡系统压力，极易导致机组运行出现瞬时失稳，影响发电效率与设备安全的问题
通过液压放大组件对调压阀实现液压直接驱动控制，省去传统控制方式中的中间过渡环节，既简化了整体控制流程，又减少了能量损耗与响应延迟，让调压阀驱动更直接高效，大幅提升了调速器运行效率，同时，能对活塞行程进行毫米级精确控制，从根本上确保调压阀动作的可靠性，避免因控制不准导致的误动作或动作不到位等问题，为调速器稳定运行提供坚实保障，此外，通过控制组件采用模块化叠加安装设计，使各控制模块可灵活搭配、实现多元化组合，能根据不同使用场景和需求灵活调整扩展，极大增强了调速器的适用性与通用性，降低了针对不同工况的定制成本，且在结构上采用分级控制方式，通过合理分级进一步增大控制精度，让调速器在应对复杂工况时仍能保持稳定精确的控制效果，有效提升整体控制性能。
Smart Images
Figure CN224904222U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to the field of speed controller technology, specifically a speed controller with a pressure regulating valve. Background Technology
[0002] In hydropower projects with long water diversion pipelines and where the construction of surge tanks is not feasible due to objective limitations, the introduction of pressure regulating valves is undoubtedly a key measure to achieve economical operation. The application of this equipment can precisely and effectively resolve two major contradictions caused by sudden load changes during power plant operation: abnormal increase in unit speed and sudden surge in water pressure, providing an important guarantee for the stable operation of the power plant.
[0003] In current hydraulic transmission systems and turbine governor hydraulic systems, the control of pressure regulating valves generally relies on direct drive by the governor hydraulic system. Due to the single transmission path of hydraulic power and the lack of intermediate adjustment links in the direct drive mode, when the system faces sudden load changes, pressure fluctuations, and other operating conditions, the pressure regulating valve often struggles to achieve rapid and accurate pressure regulation. In particular, during turbine operation, if the impact force of the water flow changes suddenly, the pressure regulating valve directly driven by the governor hydraulic system cannot react in time to balance the system pressure, which can easily lead to momentary instability in the unit operation, affecting power generation efficiency and equipment safety. Therefore, we propose a governor with pressure regulating valve control. Utility Model Content
[0004] The purpose of this invention is to provide a speed governor with a pressure regulating valve to solve the problem mentioned in the background art. In current hydraulic transmission systems and turbine speed governor hydraulic systems, the control of the pressure regulating valve generally relies on the direct drive of the speed governor hydraulic system. Due to the single transmission path of hydraulic power and the lack of intermediate adjustment links in the direct drive mode, when the system faces sudden load changes, pressure fluctuations, and other operating conditions, the pressure regulating valve often cannot achieve rapid and accurate pressure regulation. In particular, when the turbine is running, if the impact force of the water flow changes suddenly, the pressure regulating valve directly driven by the speed governor hydraulic system cannot react in time to balance the system pressure, which can easily lead to momentary instability in the unit operation, affecting power generation efficiency and equipment safety.
[0005] To achieve the above objectives, the present invention provides the following technical solution: a speed regulator with a pressure regulating valve, comprising a second integrated block, a first integrated block fixedly mounted on the top of the second integrated block, multiple oil pipes fixedly mounted inside the first and second integrated blocks, the oil pipes having multiple segments, a control component disposed outside the first and second integrated blocks, and a hydraulic amplification component disposed at the bottom of the second integrated block, the hydraulic amplification component and the control component being connected in series.
[0006] The control components include a manual valve connected to an oil pipe and fixedly mounted on the top of the first integrated block. A proportional valve is fixedly mounted on the top of the first integrated block and connected to an oil pipe. A switching valve is fixedly mounted on one side of the first integrated block and connected to an oil pipe.
[0007] An emergency stop valve is fixedly installed on one side of the second integrated block. The emergency stop valve and the two input ends of the switching valve are respectively connected to the output oil pipes of the manual valve and the proportional valve. The output oil pipe of the emergency stop valve is connected to the input end of the switching valve. The return oil output oil pipes of the proportional valve, the manual valve and the switching valve are connected to the return oil input end of the emergency stop valve.
[0008] The hydraulic amplification component includes a valve body, which is fixedly installed at the bottom of the second integrated block. The oil pipe at the output end of the switching valve is connected to the valve body. An oil pipe is fixedly installed on the valve body. A bushing is fixedly installed inside the valve body. A piston is slidably connected inside the bushing.
[0009] The bushing divides the internal chamber of the valve body into upper and lower halves. A positioning feedback is fixedly installed at one end of the valve body, and a positioning rod is fixedly installed at one end of the piston. The positioning rod slides within the positioning feedback.
[0010] The valve body has a return spring fixedly installed inside, and a spring seat is fixedly installed at one end of the return spring. The bottom of the spring seat is fixedly installed to the outside of the piston, and the spring seat is in contact with the bushing.
[0011] This utility model has at least the following beneficial effects: By using a hydraulic amplification component to achieve direct hydraulic drive control of the pressure regulating valve, the intermediate transition links in traditional control methods are eliminated. This simplifies the overall control process, reduces energy loss and response delay, and makes the pressure regulating valve drive more direct and efficient, significantly improving the governor's operating efficiency. Simultaneously, it enables millimeter-level precise control of the piston stroke, fundamentally ensuring the reliability of the pressure regulating valve's operation and avoiding problems such as malfunctions or incomplete actions caused by inaccurate control. This provides a solid guarantee for the governor's stable operation. Furthermore, the modular stacking design of the control components allows for flexible combination and diverse configurations, enabling flexible adjustments and expansions according to different usage scenarios and needs. This greatly enhances the governor's applicability and versatility, reduces customization costs for different operating conditions, and employs a hierarchical control method. Reasonable hierarchical classification further increases control precision, allowing the governor to maintain stable and accurate control even under complex operating conditions, effectively improving overall control performance. Attached Figure Description
[0012] Figure 1 This is a schematic diagram of the planar structure of this utility model; Figure 2This is a side view of the structural plan of this utility model; Figure 3 This is a schematic diagram of the planar structure of the control component of this utility model; Figure 4 This is a side view of the control component of this utility model. Figure 5 This is an enlarged planar structural diagram of point A of this utility model; Figure 6 This is an enlarged planar structural diagram of point B in this utility model; Figure 7 This is a plan view of the hydraulic system of this utility model.
[0013] In the diagram: 1. First integrated block; 2. Second integrated block; 3. Hydraulic amplification assembly; 31. Valve body; 32. Positioning feedback; 33. Return spring; 34. Bushing; 35. Spring seat; 36. Piston; 37. Positioning rod; 4. Control assembly; 41. Manual valve; 42. Proportional valve; 43. Switching valve; 44. Emergency stop valve; 5. Oil pipe. Detailed Implementation
[0014] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.
[0015] Please see Figures 1 to 7 This utility model provides a technical solution: a speed regulator with pressure regulating valve control, including a second integrated block 2, a first integrated block 1 fixedly installed on the top of the second integrated block 2, multiple oil pipes 5 fixedly installed inside the first integrated block 1 and the second integrated block 2, the oil pipes 5 having multiple segments, a control component 4 arranged outside the first integrated block 1 and the second integrated block 2, and a hydraulic amplification component 3 arranged at the bottom of the second integrated block 2, the hydraulic amplification component 3 and the control component 4 being connected in series.
[0016] Control component 4 includes a manual valve 41, which is connected to oil pipe 5. The manual valve 41 is fixedly installed on the top of the first integrated block 1. A proportional valve 42 is fixedly installed on the top of the first integrated block 1 and is connected to oil pipe 5. A switching valve 43 is fixedly installed on one side of the first integrated block 1 and is connected to oil pipe 5. An emergency stop valve 44 is fixedly installed on one side of the second integrated block 2 and is connected to oil pipe 5. The two input ends of the switching valve 43 are respectively connected to the output ends of the manual valve 41 and the proportional valve 42 via oil pipe 5. The output oil pipe 5 of the emergency stop valve 44 is connected to the input end of the switching valve 43. The return oil output oil pipe 5 of the proportional valve 42, the manual valve 41 and the switching valve 43 is connected to the return oil input end of the emergency stop valve 44. The control component 4 receives the controller electrical signal through the proportional valve 42 and converts it into a hydraulic signal (adjusting flow and pressure). The switching valve 43 switches the oil circuit connection of the oil pipe 5 controlled automatically (proportional valve 42) and manually (manual valve 41). The emergency stop valve 44 normally ensures the supply of pressure oil, and cuts off the supply and relieves pressure in an emergency to ensure safety.
[0017] The hydraulic amplification assembly 3 includes a valve body 31, which is fixedly installed at the bottom of the second integrated block 2. The output oil pipe 5 of the switching valve 43 is connected to the valve body 31. The oil pipe 5 is fixedly installed on the valve body 31. A bushing 34 is fixedly installed inside the valve body 31, and a piston 36 is slidably connected inside the bushing 34. The bushing 34 divides the internal chamber of the valve body 31 into upper and lower halves. A positioning feedback 32 is fixedly installed at one end of the valve body 31, and a positioning rod 37 is fixedly installed at one end of the piston 36. The positioning rod 37 is slidably connected within the positioning feedback 32. A return spring 33 is fixedly installed on the piston 36. A spring seat 35 is fixedly installed on one end of the return spring 33. The bottom of the spring seat 35 is fixedly installed on the outside of the piston 36. The spring seat 35 is in contact with the bushing 34. In the hydraulic amplification assembly 3, the piston 36 in the valve body 31 moves relative to the bushing 34 under the push of the pressure oil, realizing the switching of the oil pipe 5 and hydraulic amplification, and controlling the guide vane relay and pressure regulating valve. The positioning feedback 32 provides real-time feedback on the displacement of the piston 36 to ensure millimeter-level accuracy. When the pressure is lost or the signal disappears, the return spring 33 returns the piston 36 to the neutral position to ensure system stability.
[0018] When the proportional valve 42 receives electrical signals such as opening and closing from the controller, as the core regulating element, it changes the valve core position (e.g., parallel or cross position) according to the signal magnitude and direction, thereby regulating parameters such as the flow rate and pressure of the hydraulic oil, realizing the conversion of electrical signals to hydraulic signals. The switching valve 43 switches the oil circuit of the oil pipe 5 between automatic control (proportional valve 42) and manual control (manual valve 41). In automatic mode, the switching valve 43 connects the proportional valve 42 to the main oil pipe 5, allowing the proportional valve 42 to... 2. The adjusted hydraulic oil can be transmitted smoothly. When manual operation is required, the switching valve 43 switches to the oil circuit connecting the manual valve 41 and the main oil pipe 5. The hydraulic oil parameters are controlled by the manual adjustment valve. The emergency stop valve 44 is connected in series in the oil circuit of the main oil inlet pipe 5. Under normal conditions, the oil circuit of the oil pipe 5 is kept unobstructed to ensure that the pressure oil can enter the subsequent valve group normally. When an emergency occurs, such as an emergency stop signal, the emergency stop valve 44 will quickly cut off the pressure oil supply and connect the oil circuit of the relevant oil pipe 5 to return oil, so as to realize the rapid depressurization of the system and ensure the safety of the equipment.
[0019] Since piston 36 and bushing 34 are installed inside valve body 31, when pressurized oil from the control components enters the upper or lower control chamber of valve body 31, it pushes the main piston 36 to make corresponding axial movements within bushing 34. The movement of piston 36 changes its relative position with bushing 34, thereby switching the oil circuit of oil pipe 5, guiding pressurized oil to the opening or closing chamber of the guide vane servo, or controlling the opening and closing of the pressure regulating valve, completing hydraulic amplification and oil circuit conversion of oil pipe 5. Positioning feedback 32 adopts a non-contact magnetic induction structure, installed at one end of valve body 31, and can provide real-time feedback. The displacement signals of the positioning rod 37 and piston 36 are accurately measured and fed back to the controller. The controller adjusts the output of the control section according to the feedback signal to ensure that the piston 36 moves with millimeter-level precision, thereby ensuring the accuracy and reliability of the pressure regulating valve and guide vane operation. The return spring 33 is an isobaric spring. When the control chamber loses pressure or the operation signal disappears, the preload of the return spring 33 will push the piston 36 to return to the neutral position quickly, so that the guide vane and pressure regulating valve are reset to a safe state. At the same time, the spring force ensures that the piston 36 and the bushing 34 fit tightly, restoring the initial sealing state and ensuring the stability of the system.
[0020] When the guide vane is normally open, pressurized oil enters the lower control chamber of valve body 31, pushing piston 36 to move. This causes pressurized oil to flow through the opening chamber of the guide vane servo and return oil to flow through the closing chamber, opening the guide vane. Because the stroke of piston 36 does not reach the opening threshold of the pressure regulating valve, the pressure regulating valve remains closed. When the guide vane is normally closed, pressurized oil enters the upper control chamber of valve body 31, pushing piston 36 to move in the opposite direction to the normal opening direction. Under the limitation of positioning feedback 32, the stroke of piston 36 does not exceed the opening threshold of the pressure regulating valve. Pressurized oil flows through the closing chamber of the guide vane servo and return oil flows through the opening chamber, closing the guide vane. The pressure regulating valve remains closed. However, when the system suddenly sheds load, piston 36 moves rapidly downwards, and its stroke exceeds the opening overlap of the pressure regulating valve, causing pressurized oil to flow through the opening chamber of the pressure regulating valve and opening it. At the same time, the closing chamber of the guide vane servo is slowly closed by limiting the flow through the throttle valve, achieving segmented closing of the guide vane.
[0021] It should be noted that, in this document, relational terms such as "first" and "second" are used only to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such process, method, article, or apparatus.
[0022] Although embodiments of the present invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the appended claims and their equivalents.
Claims
1. A speed controller with pressure regulating valve control, comprising a second integrated block, characterized in that: The first integrated block is fixedly installed on the top of the second integrated block. Multiple oil pipes are fixedly installed inside the first and second integrated blocks. The oil pipes are provided with multiple sections. A control component is provided on the outside of the first and second integrated blocks. The control component controls the output of oil by selecting manual or automatic control mode. A hydraulic amplification component is provided at the bottom of the second integrated block. The hydraulic amplification component maintains stable operation of the device by amplifying the hydraulic pressure and converting the oil circuit. The hydraulic amplification component and the control component are connected in series.
2. The speed controller with pressure regulating valve control according to claim 1, characterized in that: The control component includes a manual valve connected to an oil pipe and fixedly mounted on the top of a first integrated block. A proportional valve is fixedly mounted on the top of the first integrated block and connected to an oil pipe. A switching valve is fixedly mounted on one side of the first integrated block and connected to an oil pipe.
3. The speed controller with pressure regulating valve control according to claim 2, characterized in that: An emergency stop valve is fixedly installed on one side of the second integrated block. The emergency stop valve and the oil pipe, the two input ends of the switching valve are respectively connected to the output oil pipes of the manual valve and the proportional valve. The output oil pipe of the emergency stop valve is connected to the input end of the switching valve. The return oil output oil pipes of the proportional valve, the manual valve and the switching valve are connected to the return oil input end of the emergency stop valve.
4. The speed controller with pressure regulating valve control according to claim 3, characterized in that: The hydraulic amplification assembly includes a valve body, which is fixedly installed at the bottom of the second integrated block. The output oil pipe of the switching valve is connected to the valve body. An oil pipe is fixedly installed on the valve body. A bushing is fixedly installed inside the valve body. A piston is slidably connected inside the bushing.
5. The speed controller with pressure regulating valve control according to claim 4, characterized in that: The bushing divides the internal chamber of the valve body into upper and lower halves. A positioning feedback is fixedly installed at one end of the valve body, and a positioning rod is fixedly installed at one end of the piston. The positioning rod is slidably connected within the positioning feedback.
6. The speed controller with pressure regulating valve control according to claim 5, characterized in that: A return spring is fixedly installed inside the valve body. A spring seat is fixedly installed at one end of the return spring. The bottom of the spring seat is fixedly installed to the outside of the piston. The spring seat is in contact with the bushing.