Electrically controlled boom holding valve

Abstract

This application relates to the technical field of electrically controlled valve assemblies, and in particular to an electrically controlled boom holding valve, including a proportional relief valve, a main valve core, a valve seat, a plunger, a valve cover, a valve block, and a sensor. The valve block has a first flow channel; one end of the first flow channel is closed by a sealing nut, and the other end is sealed to the valve cover. The main valve core, valve seat, and plunger are housed within the first flow channel. One end of the main valve core passes through the valve seat and abuts against one end of the plunger, while the other end extends into the valve cover. The valve seat and main valve core are sealed together. The chamber between the plunger and the sealing nut forms a pilot chamber, which is connected to the output end of the proportional relief valve through a pilot flow channel located within the valve block. An oil inlet is provided in the wall of the first flow channel between the valve cover and the valve seat. A sensor is mounted on the valve block for monitoring pressure signals. This application allows for adjustment of the oil inlet opening size according to actual conditions to regulate the oil flow rate, resulting in a more intelligent and automated effect.

Description

Technical Field

[0001] This application relates to the technical field of electrically controlled valve assemblies, and in particular to an electrically controlled boom holding valve. Background Technology

[0002] In the construction machinery industry, boom holding valves play a crucial role in the stable operation of equipment. With the continuous development of the construction machinery industry, the application of booms in various engineering operations is becoming increasingly widespread. Equipment such as excavators and cranes experience frequent boom operations with extremely high requirements for precision and stability. Boom holding valves ensure the boom maintains its position and moves smoothly under different working conditions, which is of great significance for improving engineering operation efficiency and ensuring construction safety. The quality of their performance directly affects the overall performance and reliability of construction machinery; therefore, the development of related technologies has always been a focus of attention.

[0003] In the past, boom holding valves typically used hydraulic control to achieve their function. Hydraulic control relies primarily on the coordinated action of the mechanical structure and hydraulic system, controlling the flow of hydraulic oil through the movement of mechanical components to achieve boom position holding and movement control. When the internal pressure of the boom holding valve exceeds the required value, the excess oil pressure is released through the relief valve to balance the oil pressure. This control method can, to a certain extent, meet the basic control requirements of the boom.

[0004] Based on the above-mentioned solutions, the existing hydraulic control method can only relieve excess oil pressure through the overflow valve, but cannot adjust the flow rate of oil entering the inlet according to the actual situation. Summary of the Invention

[0005] In order to adjust the size of the oil inlet opening and control the flow rate of the oil, the purpose of this application is to provide an electrically controlled boom holding valve, which adopts the following technical solution: Includes a proportional relief valve, main valve core, valve seat, plunger, valve cover, valve block, and sensor; The valve block is provided with a first flow channel; one end of the first flow channel is closed by a sealing nut, and the other end is sealed to the valve cover. The main valve core, valve seat, and plunger are housed within the first flow channel; one end of the main valve core passes through the valve seat and abuts against one end of the plunger, while the other end extends into the valve cover; the valve seat and the main valve core are sealed together. The chamber between the plunger and the sealing nut forms a pilot chamber, and the pilot chamber is connected to the output end of the proportional relief valve through a pilot flow channel provided in the valve block; An oil inlet is provided on the side wall of the first flow channel between the valve cover and the valve seat; The sensor is mounted on the valve block and is used to monitor pressure signals.

[0006] By adopting the above technical solution, the pilot channel is connected to an external oil pump. The oil pump outputs oil, which flows into the pilot chamber through the pilot channel. Subsequently, the oil fills the pilot chamber, applying pressure to the plunger, causing the plunger to push the main valve core to move to the left. The seal between the main valve core and the valve seat separates, and the oil inlet enters the first flow channel, finally reaching the required working position. The sensor monitors the oil pressure and transmits it to the proportional relief valve via an electrical signal, controlling the current of the proportional relief valve, thereby controlling the flow rate in the pilot channel, further controlling the pressure on the plunger, and finally controlling the opening between the main valve core and the valve seat, thereby regulating the flow rate of oil entering through the inlet.

[0007] Optionally, a first spring is provided in the first flow channel on the side of the valve seat facing away from the oil inlet; one end of the first spring is connected to the valve seat, and the other end is connected to the inner wall of the first flow channel.

[0008] By adopting the above technical solution, a continuous restoring force can be provided to the valve seat, enhancing the sealing stability between the valve seat and the main valve core. This design helps maintain the pre-tightened position of the valve seat during system pressure fluctuations, preventing seal failure or internal leakage caused by sudden pressure changes, thereby improving the overall sealing performance and operational reliability of the retaining valve and extending its service life.

[0009] Optionally, the valve cover has a cavity, and a second spring is provided in the cavity. The end of the main valve core extends into the cavity and is fixedly connected to the second spring.

[0010] By adopting the above technical solution, the main valve core obtains elastic support and buffering during its movement. This structure can smooth the opening and closing action of the main valve core, reduce hydraulic shock and vibration, improve the controllability and response smoothness of the valve core movement, and also help reduce wear and noise, thereby improving the durability of the valve under frequent operating conditions.

[0011] Optionally, the valve seat is a conical valve seat, and the main valve core is a slide valve and forms a sealing fit with the conical valve seat.

[0012] By adopting the above technical solution, the conical valve seat and the spool valve-type main valve core cooperate to form a line contact or surface contact sealing form, which has good sealing performance and centering characteristics. The conical valve seat can achieve self-reinforcing sealing under certain pressure, while the spool valve has a simple structure and good guiding properties. The combination of the two not only improves the sealing reliability of the valve under high pressure, but also facilitates processing and assembly, which helps to reduce manufacturing costs and ensure consistency.

[0013] Optionally, the valve body is further provided with a second flow channel, the first flow channel and the second flow channel are connected to each other, and the end of the second flow channel is provided with a working oil port.

[0014] By adopting the above technical solution, a clear flow path guide is provided for the inflow and outflow of hydraulic oil. This design enhances the integration and smoothness of the internal oil circuit, reduces the need for external pipe connections, lowers the risk of leakage, and allows the working oil port to be flexibly arranged according to actual installation needs, improving the adaptability and space utilization efficiency of the entire valve assembly.

[0015] Optionally, the sensor is a pressure sensor, with its monitoring end located near the initial end of the second flow channel, and the pressure sensor is used to monitor pressure changes in the second flow channel.

[0016] By adopting the above technical solution, the sensor is specifically defined as a pressure sensor, and its monitoring end is placed close to the initial end of the second flow channel, enabling it to directly and promptly detect pressure changes in the working oil circuit. This arrangement improves the accuracy and response speed of pressure signal acquisition, providing a reliable data source for the system to achieve real-time pressure closed-loop control. It also helps to accurately adjust the boom load and prevent equipment malfunctions caused by overload or insufficient pressure.

[0017] Optionally, the pressure sensor has a monitoring range of 0-40 MPa, and the output signal of the pressure sensor is used to control the current input value of the proportional relief valve.

[0018] By adopting the above technical solution, the monitoring range and signal application of the pressure sensor are clearly defined, and its output signal is limited to controlling the current input of the proportional relief valve, forming a closed-loop link from pressure sensing to electronic control regulation. This design enables the system to automatically adjust the control current of the proportional relief valve according to the actual working pressure, achieving precise and dynamic pressure regulation, enhancing the system's adaptive capability, and ensuring the system's wide applicability and safety by covering commonly used high-pressure operating conditions.

[0019] Optionally, the proportional relief valve adjusts the pilot pressure via an electrical signal, and the pilot pressure setpoint of the proportional relief valve decreases as the pressure signal monitored by the pressure sensor increases.

[0020] By adopting the above technical solution, a negative feedback regulation mechanism is achieved in the system. When the working pressure increases, the pilot pressure decreases accordingly, causing the balancing valve to tend to close to limit further pressure increases, thereby automatically suppressing pressure fluctuations and overload risks. This intelligent pressure-following regulation not only improves the stability and safety of the system but also reduces reliance on operator experience, demonstrating the automation advantages of the electronic control system.

[0021] Optionally, a damping orifice may also be included, which is disposed between the sensor and the second flow channel to reduce the pressure impact of the oil on the sensor output end.

[0022] By adopting the above technical solution, the damping orifice acts as a filter and buffer, effectively attenuating high-frequency pressure pulsations and instantaneous impacts that may exist in the main oil circuit, preventing these severe pressure fluctuations from being directly transmitted to the precision pressure sensor. This protects the sensor from damage, extends its service life, and makes the pressure signal monitored by the sensor smoother and more stable, reducing control signal noise and improving the stability and reliability of the entire closed-loop control system.

[0023] In summary, this application includes at least one of the following beneficial technical effects: 1. The pilot channel is connected to an external oil pump. The oil pump outputs oil, which flows into the pilot chamber through the pilot channel. The oil then fills the pilot chamber, applying pressure to the plunger, causing the plunger to push the main valve core to move to the left. The seal between the main valve core and the valve seat separates, and the oil inlet enters the first flow channel, finally reaching the required working position. The sensor monitors the oil pressure and transmits it to the proportional relief valve via an electrical signal, controlling the current of the proportional relief valve, thereby controlling the flow rate in the pilot channel, further controlling the pressure on the plunger, and finally controlling the opening between the main valve core and the valve seat, thereby regulating the flow rate of oil entering through the inlet. 2. The balancing valve employs a sealing fit between a conical valve seat and a spool valve core, combined with first and second springs providing elastic support and reset for the valve seat and main valve core, respectively. This design significantly improves the valve's sealing reliability, smooth operation, and shock resistance under high pressure and frequent operation conditions, effectively reducing internal leakage and wear, thereby enhancing the overall system's operational stability and service life. 3. The system monitors the working oil circuit pressure in real time via a pressure sensor and feeds the signal back to the proportional relief valve, dynamically adjusting the pilot pressure using an electrical signal. In particular, it employs negative feedback control logic where the pilot pressure decreases accordingly when the overall pressure increases. This allows the system to automatically suppress pressure fluctuations and overload risks, significantly improving the automation, safety, and precision of boom operation. Attached Figure Description

[0024] Figure 1 This is a schematic diagram of the overall structure of the electrically controlled boom holding valve; Figure 2 This is a cross-sectional view of the electrically controlled boom holding valve; Figure 3 This is a schematic diagram of the back structure of the electrically controlled boom holding valve; Figure 4 yes Figure 3 A schematic diagram of the cross-sectional structure of section AA in the middle; Figure 5 yes Figure 4 Schematic diagram of the cross-sectional structure of the middle BB section; In the picture, 1. Proportional relief valve; 2. Main valve core; 3. Valve seat; 4. Piston; 5. Valve cover; 6. Valve block; 61. First flow channel; 611. Oil inlet; 62. Second flow channel; 621. Working oil port; 7. Sensor; 8. Sealing nut; 9. First spring; 10. Second spring; 11. Pilot cavity; 12. Pilot flow channel. Detailed Implementation

[0025] The following is in conjunction with the appendix Figure 1 - Appendix Figure 5 This application will be described in further detail below.

[0026] An electrically controlled boom holding valve, as described in the following figure Figure 1 and Figure 2 The system includes a proportional relief valve 1, a main valve core 2, a valve seat 3, a plunger 4, a valve cover 5, a valve block 6, and a sensor 7. The valve block 6 provides the mounting base and flow channel for the entire unit. The proportional relief valve 1, main valve core 2, valve seat 3, plunger 4, valve cover 5, and sensor 7 work together to precisely control the flow and pressure of the hydraulic fluid, thereby achieving stable boom operation and high efficiency. This coordination makes the boom operation smoother, avoiding swaying and instability, while reducing energy consumption and automatically adjusting operating parameters according to actual working conditions.

[0027] Specifically, refer to Figure 2 The valve block 6 contains a first flow channel 61. The first flow channel 61 serves as a passage for oil flow and is crucial for the normal operation of the entire hydraulic system. The first flow channel 61 is generally made of a metal material, such as stainless steel or carbon steel, possessing high strength and good corrosion resistance. In some special operating environments, lightweight materials such as aluminum alloy can also be used. One end of the first flow channel 61 is sealed by a sealing nut 8, which prevents oil leakage and ensures the sealing performance of the hydraulic system. The sealing nut 8 is usually threaded and tightly fitted to the valve block 6, and sealant can be added to the threads to further enhance the sealing effect. The sealing nut 8 is generally made of copper alloy or stainless steel, offering good sealing performance and corrosion resistance. The other end of the first flow channel 61 is sealed to the valve cover 5. This connection ensures that oil can smoothly enter the first flow channel 61 from the valve cover 5. The connection between the valve cover 5 and the first flow channel 61 can be sealed using a sealing gasket or sealing ring to prevent oil leakage at the connection point. Valve cover 5 is typically manufactured using a casting process and has a suitable shape and size to fit with valve block 6 and other components.

[0028] Furthermore, refer to Figure 2The main valve core 2, valve seat 3, and plunger 4 are housed within the first flow channel 61. The main valve core 2 is a key component controlling oil flow. Within the first flow channel 61, it moves according to different operating conditions, thereby altering the oil flow path and flow rate. The main valve core 2 is generally made of alloy steel, with a finely machined and treated surface to ensure wear resistance and sealing performance. The valve seat 3 is sealed to the main valve core 2. The valve seat 3 is a conical valve seat 3; this design ensures a good seal between the main valve core 2 and the valve seat 3, reducing oil leakage. The valve seat 3 is typically made of hard alloy material, possessing high hardness and wear resistance, and capable of withstanding significant pressure. One end of the main valve core 2 passes through the valve seat 3 and abuts against one end of the plunger 4, while the other end extends into the valve cover 5. The plunger 4 transmits pressure and force within the first flow channel 61. Its cooperation with the main valve core 2 allows the main valve core 2 to move accordingly based on different pressure conditions. The plunger 4 is generally made of carbon steel and plated with a layer of chromium to improve its wear resistance and corrosion resistance.

[0029] Reference Figure 2 and Figure 3 An oil inlet 611 is provided on the side wall of the first flow channel 61 between the valve cover 5 and the valve seat 3. The oil inlet 611 is the entrance for oil to enter the first flow channel 61, and its size and shape will affect the oil entry speed and flow rate. The oil inlet 611 is generally designed to be round or square, and a filter screen can be installed at the inlet to prevent impurities from entering the hydraulic system.

[0030] Furthermore, refer to Figure 4 The chamber between the plunger 4 and the sealing nut 8 forms the pilot chamber 11, which is connected to the output end of the proportional relief valve 1 via a pilot flow channel 12 located within the valve block 6. The proportional relief valve 1 can adjust the output oil pressure according to different control signals, thereby changing the pressure within the pilot chamber 11. The function of the pilot chamber 11 is to provide pilot pressure for the movement of the main valve core 2, enabling the main valve core 2 to move accordingly based on different operating states. The pilot flow channel 12 is the passage connecting the proportional relief valve 1 and the pilot chamber 11; its size and shape affect the oil flow resistance and response speed.

[0031] Furthermore, refer to Figure 1 Sensor 7 is mounted on valve block 6 to monitor pressure signals. Sensor 7 is typically a pressure sensor, which monitors pressure changes in the hydraulic system in real time and converts the pressure signal into an electrical signal output. The monitoring end of pressure sensor 7 is close to the initial end of the second flow channel 62, allowing for more accurate monitoring of pressure changes in the second flow channel 62. Pressure sensor 7 usually employs piezoelectric or piezoresistive principles, featuring high precision and high reliability.

[0032] Furthermore, refer to Figure 2Within the first flow channel 61, a first spring 9 is provided on the side of the valve seat 3 facing away from the oil inlet 611. One end of the first spring 9 is connected to the valve seat 3, and the other end is connected to the inner wall of the first flow channel 61. The first spring 9 serves as a buffer and reset mechanism. When the main valve core 2 moves, the first spring 9 can absorb some of the impact force and provide a certain elastic force when the main valve core 2 resets. The first spring 9 is generally a helical spring made of spring steel with a suitable elastic coefficient.

[0033] Furthermore, refer to Figure 2 The valve cover 5 has a cavity, within which a second spring 10 is installed. The end of the main valve core 2 extends into the cavity and is fixedly connected to the second spring 10. The second spring 10 also serves as a buffer and reset mechanism, ensuring the smoothness of the main valve core 2 during movement and providing auxiliary elastic force when the main valve core 2 resets. The structure and material of the second spring 10 are similar to those of the first spring 9; it is also a helical spring made of spring steel.

[0034] Furthermore, refer to Figure 2 The valve body also includes a second flow channel 62, which is interconnected with the first flow channel 61. A working port 621 is located at the end of the second flow channel 62. The function of the second flow channel 62 is to transport the oil flowing from the first flow channel 61 to the working element, and the working port 621 is the interface connecting the oil to the external working element. The size and shape of the second flow channel 62 are designed according to specific working requirements to ensure that the oil can be smoothly delivered to the working element.

[0035] The pressure sensor 7 has a monitoring range of 0-40 MPa, and its output signal is used to control the current input value of the proportional relief valve 1. The proportional relief valve 1 adjusts the pilot pressure via an electrical signal. The pilot pressure setpoint of the proportional relief valve 1 decreases as the pressure signal detected by the pressure sensor 7 increases. When the pressure sensor 7 detects an increase in the pressure signal, it indicates that the pressure in the hydraulic system is too high. In this case, the proportional relief valve 1 will decrease the current input value according to the output signal of the pressure sensor 7, thereby reducing the pilot pressure, causing the main valve core 2 to move, reducing the oil flow rate, and lowering the system pressure. Conversely, when the pressure sensor 7 detects a decrease in the pressure signal, the proportional relief valve 1 will increase the current input value, increasing the pilot pressure, increasing the oil flow rate, and increasing the system pressure.

[0036] This embodiment also includes a damping orifice, which is disposed between the sensor 7 and the second flow channel 62 to reduce the pressure impact of the oil on the output end of the sensor 7. The damping orifice is generally designed with a small diameter, and its function is to impede the flow of oil, thereby reducing the impact of oil pressure fluctuations on the sensor 7. The damping orifice can be circular or square, and its diameter and length will be designed according to specific application requirements.

[0037] The valve block 6 has a hole on its back that communicates with the hydraulic oil pump. The hole is connected to the pilot flow channel 12. The hydraulic oil pump continuously supplies oil into the pilot flow channel 12. The oil enters the pilot cavity 11 between the plunger 4 and the sealing nut 8 along the pilot flow channel 12 and fills the space. The continuously entering oil generates oil pressure, which applies a leftward pressure to the plunger 4. Subsequently, the plunger 4 pushes the main valve core 2 to move to the left. The main valve core 2 and the valve seat 3, which are sealed together, separate at this time. The oil inlet 611 opened in the wall of the first flow channel 61 between the valve cover 5 and the valve seat 3 is filled with working oil. The working oil enters the first flow channel 61 from the opening between the main valve core 2 and the valve seat 3, and then enters the second flow channel 62. Finally, it reaches the working position from the working oil port 621 at the end of the second flow channel 62, completing the oil supply work.

[0038] The output end of the proportional relief valve 1 is connected to the pilot channel 12. The proportional relief valve 1 can control the flow rate in the pilot channel 12. That is, the valve core in the proportional relief valve 1 will move up and down at the output end to control the opening of the pilot channel 12. The valve core moves up and down through the electromagnetic effect generated by the electromagnet above being energized. The sensor 7 monitors the pressure of the oil in the second channel 62. When the hydraulic pressure is high, the sensor 7 converts the pressure signal into an electrical signal and transmits it to the control terminal, such as a computer. Then, it controls the current of the proportional relief valve 1 to adjust the flow rate in the pilot channel 12, thereby adjusting the pressure on the plunger 4. Finally, it controls the opening size between the main valve core 2 and the valve seat 3, so as to adjust the flow rate of the oil inlet 611.

[0039] Meanwhile, there may be gaps between the plunger 4 and the side wall of the first flow channel 61. The hydraulic oil in the pilot chamber 11 may be under pressure and enter the chamber on the left side of the plunger 4 through the gap, which will hinder the movement of the plunger 4. Therefore, a pressure relief hole is opened in the chamber to connect with the outside and remove the oil that has accidentally entered, so as to prevent it from hindering the movement of the plunger 4.

[0040] The implementation principle of this application embodiment is as follows: The electrically controlled boom holding valve of this solution achieves precise control of boom operation through the reasonable arrangement of various components. The combined use of the proportional relief valve 1 and the pressure sensor 7 can automatically adjust the oil pressure according to the actual pressure in the hydraulic system, thereby ensuring the smooth operation of the boom. Compared with the traditional hydraulic control method, this automatic adjustment method greatly improves efficiency and reduces energy consumption. At the same time, the pressure sensor 7 can monitor pressure changes in real time. When abnormal situations such as pipeline rupture occur, it can promptly feed back a signal, enabling the proportional relief valve 1 to respond quickly and cut off the oil circuit between the cylinder and the main valve, thus playing a protective role. In addition, the use of a conical valve seat 3 and a spool valve type main valve core 2 effectively reduces leakage at the joint surface, improves throttling characteristics, and further enhances the performance of the entire system. Moreover, the standardized design of each component reduces the processing difficulty and cost of parts, providing strong support for the upgrading and development of engineering machinery.

[0041] The embodiments described in this specific implementation are preferred embodiments of this application and are not intended to limit the scope of protection of this application. Identical components are represented by the same reference numerals. Therefore, all equivalent changes made to the structure, shape, and principle of this application should be covered within the scope of protection of this application.

Claims

1. An electrically controlled boom holding valve, characterized in that, It includes a proportional relief valve (1), a main valve core (2), a valve seat (3), a plunger (4), a valve cover (5), a valve block (6), and a pressure sensor (7); The valve block (6) is provided with a first flow channel (61) and a second flow channel (62), which are interconnected. The end of the second flow channel (62) is provided with a working oil port (621). One end of the first flow channel (61) is closed by a sealing nut (8), and the other end is sealed to the valve cover (5). The main valve core (2), valve seat (3) and plunger (4) are housed in the first flow channel (61); one end of the main valve core (2) passes through the valve seat (3) and abuts against one end of the plunger (4), and the other end extends into the valve cover (5); the valve seat (3) is sealed to the main valve core (2); The chamber between the plunger (4) and the sealing nut (8) forms a pilot chamber (11), and the pilot chamber (11) is connected to the output end of the proportional relief valve (1) through a pilot flow channel (12) provided in the valve block (6); An oil inlet (611) is provided in the wall of the first flow channel (61) between the valve cover (5) and the valve seat (3). The pressure sensor (7) is disposed on the valve block (6) and is used to monitor the pressure signal. The monitoring end of the pressure sensor (7) is close to the initial end of the second flow channel (62). The pressure sensor (7) is used to monitor the pressure change of the second flow channel (62). The monitoring range of the pressure sensor (7) is 0-40MPa. The output signal of the pressure sensor (7) is used to control the current input value of the proportional relief valve (1). The proportional relief valve (1) adjusts the pilot pressure through an electrical signal. The pilot pressure setting value of the proportional relief valve (1) decreases as the pressure signal monitored by the pressure sensor (7) increases. It also includes a damping orifice, which is disposed between the pressure sensor (7) and the second flow channel (62) to reduce the pressure impact of the oil on the output end of the pressure sensor (7).

2. The electrically controlled boom holding valve according to claim 1, characterized in that, Inside the first flow channel (61), a first spring (9) is provided on the side of the valve seat (3) facing away from the oil inlet (611); one end of the first spring (9) is connected to the valve seat (3), and the other end is connected to the inner wall of the first flow channel (61).

3. The electrically controlled boom holding valve according to claim 1, characterized in that, The valve cover (5) has a cavity, and a second spring (10) is provided in the cavity. The end of the main valve core (2) extends into the cavity and is fixedly connected to the second spring (10).

4. The electrically controlled boom holding valve according to claim 1, characterized in that, The valve seat (3) is a conical valve seat (3), and the main valve core (2) adopts the form of a slide valve and forms a sealing fit with the conical valve seat (3).

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