Multi-functional counterweight action control valve and hydraulic system
Patent Information
- Application Number
- CN202521534654.2
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-07-22
- Publication Date
- 2026-10-20
- Estimated Expiration
- 2035-07-22
AI Technical Summary
[0004]实用新型目的：本实用新型的目的在于提供一种多功能平衡重动作控制阀及液压系统，该控制阀能够实现平衡重提升功能、平衡重变位功能、液压油缸拔轴功能，解决了现有液压系统复杂，管路杂乱的问题
[0013]有益效果：与现有技术相比，本实用新型的显著技术效果如下：(1)通过液压阀集成设计，仅通过一个控制阀就能实现平衡重提升功能、平衡重变位功能、液压油缸拔轴功能等多个功能的控制，控制阀具有集成度高、成本低、体积小、安装简便等特点，能有效简化液压系统管路，减少液压元件使用，提高液压系统可靠性；(2)第五电磁换向阀得电时，通过控制第二电磁开关阀和第三电磁开关阀中只有一个电磁开关阀得电来实现单个平衡重提升油缸的单独提升或下落；第六电磁换向阀得电时，通过控制第四电磁开关阀和第五电磁开关阀中只有一个电磁开关阀得电来实现单个平衡重变位油缸的单独提升或下落；解决了解决两个平衡重提升油缸和两个平衡重变位油缸运动过程不同步的问题。
Smart Images
Figure CN224871575U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to engineering machinery technology, specifically to a multi-functional counterweight motion control valve and hydraulic system. Background Technology
[0002] Heavy machinery is increasingly used in construction in cities and factories, and customers have higher and higher requirements for the performance and space adaptability of cranes. To improve the lifting capacity of cranes, it is necessary to continuously increase the weight of the counterweight to increase the crane's anti-tipping moment, thus greatly limiting the crane's operation in many confined spaces. To solve the technical challenge of maximizing lifting performance with minimal counterweight weight and adapting to more confined spaces, counterweight devices are trending towards variable displacement designs. Modern variable displacement counterweight devices need to have both counterweight lifting and displacement functions, both typically driven by hydraulic cylinders. Since the counterweight base and mounting bracket of the variable displacement counterweight device need to be assembled together via pins, a hydraulic cylinder pin-pulling function is also required to facilitate the pin installation process.
[0003] Existing technical solutions mainly implement the counterweight lifting function, counterweight displacement function, and hydraulic cylinder shaft pulling function separately through control valves. For example, the counterweight lifting function and displacement function both require separate control valves. Figure 1 As shown, Figure 1 Figure (a) is a schematic diagram of the hydraulic cylinder's shaft-pulling function. Figure 1 Figure (b) in the figure is a schematic diagram of the counterweight lifting function and the counterweight displacement function. The existing technology has the following defects: (1) Each function needs to be implemented by a separate control valve, resulting in a large number of control valves used in the hydraulic system, complicated pipeline connections, large space required for placement, high cost, and difficulty in installation; since each control valve controls each function separately, many hydraulic components such as relief valves, check valves and damping valves inside the control valve need to be designed, the integration is low, and the failure rate of the hydraulic system is also increased, resulting in poor reliability. Therefore, the existing displacement counterweight device does not have a dedicated integrated control valve to complete the above functions, and the existing hydraulic system is complex and the pipeline is messy. (2) For the most important counterweight lifting and displacement functions of the displacement counterweight device, both are driven by two hydraulic cylinders. The existing control valve controls the two hydraulic cylinders to move together, but when the cylinder load is unbalanced or the control accuracy of the diverter valve does not meet the requirements, the cylinder movement will be asynchronous. The existing control valve cannot effectively solve the problem of asynchronous movement of the counterweight lifting and displacement cylinders. Utility Model Content
[0004] Purpose of the utility model: The purpose of this utility model is to provide a multifunctional counterweight action control valve and hydraulic system. This control valve can realize the functions of counterweight lifting, counterweight displacement, and hydraulic cylinder shaft pulling, thus solving the problems of complex and messy pipelines in existing hydraulic systems.
[0005] Technical Solution: This utility model discloses a multifunctional counterweight action control valve, comprising: a first electromagnetic directional valve, a second electromagnetic directional valve, a third electromagnetic directional valve, a fourth electromagnetic directional valve, a first electromagnetic switch valve, an oil outlet P, and an oil return port T; the oil inlet of the first electromagnetic switch valve is connected to the oil outlet P, and the oil outlet of the first electromagnetic switch valve is connected to the oil inlets of the first, second, third, and fourth electromagnetic directional valves respectively; the oil return ports of the first, second, third, and fourth electromagnetic directional valves are each connected to the oil return port T via a check valve; the first, second, third, and fourth electromagnetic directional valves are used to control the extension and retraction of four shaft-pulling cylinders, at which time the first electromagnetic switch valve is energized; it also includes an oil port A7, a fifth electromagnetic directional valve, a second electromagnetic switch valve, and a third electromagnetic switch valve; the oil inlet of the fifth electromagnetic directional valve is connected to the oil outlet P, and the oil return port of the fifth electromagnetic directional valve is connected to... The system includes a sixth check valve connected to the return port T, and a fifth solenoid directional valve whose working port is connected to the inlet ports of the second and third solenoid valves. The other working port of the fifth solenoid directional valve is connected to port A7. Port A7 connects to the small chambers of the two counterweight lifting cylinders, and the outlet ports of the second and third solenoid valves connect to the large chambers of the two counterweight lifting cylinders. The system also includes port A10, a sixth solenoid directional valve, a fourth solenoid valve, and a fifth solenoid valve. The inlet port of the sixth solenoid directional valve connects to the outlet port P, and the return port of the sixth solenoid directional valve is connected to the return port T via a seventh check valve. A working port of the sixth solenoid directional valve connects to the inlet ports of the fourth and fifth solenoid valves, and the other working port of the sixth solenoid directional valve connects to port A10. Port A10 connects to the small chambers of the two counterweight displacement cylinders, and the outlet ports of the fourth and fifth solenoid valves connect to the large chambers of the two counterweight displacement cylinders.
[0006] Furthermore, the oil outlet of the first electromagnetic switch valve is equipped with damping, which can reduce the extension and retraction speed of the shaft-pulling cylinder; the return oil port T is equipped with a first check valve, which can prevent the back pressure flow generated at the return oil port T from flowing back into the counterweight action control valve.
[0007] Furthermore, a first relief valve is connected between the oil outlet P and the oil return port T, and a second relief valve is provided between the oil outlet and the oil return port T of the first electromagnetic switch valve. The first relief valve limits the pressure of the entire control valve, and the second relief valve limits the pressure of the shaft-pulling cylinder.
[0008] Furthermore, when the fifth solenoid directional valve Ya5 is energized, and both the second and third solenoid valves are energized, the two counterweight lifting cylinders lift synchronously; when the fifth solenoid directional valve Ya6 is energized, and both the second and third solenoid valves are energized, the two counterweight lifting cylinders fall synchronously.
[0009] Furthermore, when the fifth solenoid directional valve Ya5 is energized, and only one of the second and third solenoid valves is energized, the counterweight lifting cylinder corresponding to the energized solenoid valve lifts independently; when the fifth solenoid directional valve Ya6 is energized, and only one of the second and third solenoid valves is energized, the counterweight lifting cylinder corresponding to the energized solenoid valve falls independently.
[0010] Furthermore, when the sixth electromagnetic directional valve Ya7 is energized, and both the fourth and fifth electromagnetic switch valves are energized, the two counterweight displacement cylinders rise synchronously; when the sixth electromagnetic directional valve Ya8 is energized, and both the fourth and fifth electromagnetic switch valves are energized, the two counterweight displacement cylinders fall synchronously.
[0011] Furthermore, when the sixth electromagnetic directional valve Ya7 is energized, and only one of the fourth and fifth electromagnetic switching valves is energized, the counterweight displacement cylinder corresponding to the energized electromagnetic switching valve is raised individually; when the sixth electromagnetic directional valve Ya8 is energized, and only one of the fourth and fifth electromagnetic switching valves is energized, the counterweight displacement cylinder corresponding to the energized electromagnetic switching valve is lowered individually.
[0012] Based on the same inventive concept, the present invention provides a hydraulic system including the aforementioned multifunctional counterweight motion control valve.
[0013] Beneficial effects: Compared with the prior art, the significant technical effects of this utility model are as follows: (1) Through the integrated design of hydraulic valves, multiple functions such as counterweight lifting, counterweight displacement, and hydraulic cylinder shaft pulling can be controlled by only one control valve. The control valve has the characteristics of high integration, low cost, small size, and easy installation, which can effectively simplify the hydraulic system pipeline, reduce the use of hydraulic components, and improve the reliability of the hydraulic system; (2) When the fifth electromagnetic directional valve is energized, it controls the... second electromagnetic switching valve and third Only one solenoid valve in the solenoid switching valve is energized to achieve the individual lifting or lowering of a single counterweight lifting cylinder; when the sixth solenoid directional valve is energized, it controls... fourth electromagnetic switching valve and fifthOnly one solenoid switch valve in the solenoid switch valve is energized to achieve the individual lifting or lowering of a single counterweight displacement cylinder; this solves the problem of asynchronous movement between two counterweight lifting cylinders and two counterweight displacement cylinders. Attached Figure Description
[0014] Figure 1 This is a schematic diagram of the existing technology;
[0015] Figure 2 This is a hydraulic schematic diagram of a multifunctional counterweight action control valve according to the present invention.
[0016] Figure 3 This is a hydraulic schematic diagram of a hydraulic system according to the present invention. Detailed Implementation
[0017] The technical solution of this utility model will now be described in detail with reference to specific embodiments and accompanying drawings.
[0018] Example 1
[0019] like Figure 2 As shown, this utility model discloses a multifunctional counterweight action control valve, including oil ports A1-A10, oil ports B1-B4, oil outlet P, oil return port T, a first solenoid directional valve 101, a second solenoid directional valve 102, a third solenoid directional valve 103, a fourth solenoid directional valve 104, a fifth solenoid directional valve 105, a sixth solenoid directional valve 106, a first solenoid switch valve 107, a second solenoid switch valve 108, a third solenoid switch valve 109, a fourth solenoid switch valve 110, a fifth solenoid switch valve 111, a first relief valve 112, a second relief valve 113, a third relief valve 114, a fourth relief valve 115, a first check valve 116, a second check valve 117, a third check valve 118, a fourth check valve 119, a fifth check valve 120, a sixth check valve 121, and a seventh check valve 122.
[0020] The first working port of the first solenoid directional valve 101 is connected to port A1, and its second working port is connected to port B1. The first working port of the second solenoid directional valve 102 is connected to port A2, and its second working port is connected to port B2. The first working port of the third solenoid directional valve 103 is connected to port A3, and its second working port is connected to port B3. The first working port of the fourth solenoid directional valve 104 is connected to port A4, and its second working port is connected to port B4. The inlet of the first solenoid switch valve 107 is connected to the outlet P, and the outlet of the first solenoid switch valve 107 is connected to the inlet of the first solenoid directional valve 101, the second solenoid directional valve 102, the third solenoid directional valve 103, and the fourth solenoid directional valve 104, respectively. The return ports of the first solenoid directional valve 101, the second solenoid directional valve 102, the third solenoid directional valve 103, and the fourth solenoid directional valve 104 are each connected to the return port T via a check valve. Specifically, the return port of the first solenoid directional valve 101 is connected to the return port T via the second check valve 117, the return port of the second solenoid directional valve 102 is connected to the return port T via the third check valve 118, the return port of the third solenoid directional valve 103 is connected to the return port T via the fourth check valve 119, and the return port of the fourth solenoid directional valve 104 is connected to the return port T via the fifth check valve 120. The first solenoid directional valve 101, the second solenoid directional valve 102, the third solenoid directional valve 103, and the fourth solenoid directional valve 104 are used to control the extension and retraction of the four shaft-pulling cylinders. At this time, the first solenoid switching valve 107 is energized.
[0021] Generally, the return oil line of the counterweight displacement device is merged with the return oil lines of other hydraulic systems before flowing back to the oil tank. When the return oil flow rate of other hydraulic systems is high, a certain back pressure will be generated at the return port T of the counterweight action control valve, causing hydraulic oil to flow back from the return port T into the counterweight action control valve, thereby causing control disorder of the entire hydraulic system. To avoid this problem, a first check valve 116 is installed at the return port T. A damper 123 is installed at the outlet of the first solenoid valve 107 to reduce the extension and retraction speed of the shaft cylinder. A first relief valve 112 is connected between the outlet P and the return port T, and a second relief valve 113 is installed between the outlet of the first solenoid valve 107 and the return port T.
[0022] The inlet of the fifth solenoid directional valve 105 is connected to the outlet port P. The return port of the fifth solenoid directional valve 105 is connected to the return port T through the sixth check valve 121. One working port of the fifth solenoid directional valve 105 is connected to the inlet ports of the second solenoid valve 108 and the third solenoid valve 109 respectively. The other working port of the fifth solenoid directional valve 105 is connected to port A7. A third relief valve 114 is installed between one working port of the fifth solenoid directional valve 105 and the return port T. The outlet of the second solenoid valve 108 is connected to port A5, and the outlet of the third solenoid valve 109 is connected to port A6. Port A7 is used to connect the small chambers of the two counterweight lifting cylinders. The outlets of the second solenoid valve 108 and the third solenoid valve 109 are connected to the large chambers of the two counterweight lifting cylinders through ports A5 and A6.
[0023] When the fifth solenoid directional valve 105 (Ya5) is energized, and both the second and third solenoid valves 108 and 109 are energized, the two counterweight lifting cylinders lift synchronously. When the fifth solenoid directional valve 105 (Ya6) is energized, and both the second and third solenoid valves 108 and 109 are energized, the two counterweight lifting cylinders fall synchronously. When the fifth solenoid directional valve 105 (Ya5) is energized, and only one of the second or third solenoid valves (108 and 109) is energized, the counterweight lifting cylinder corresponding to the energized solenoid valve lifts alone. When the fifth solenoid directional valve 105 (Ya6) is energized, and only one of the second or third solenoid valves (108 and 109) is energized, the counterweight lifting cylinder corresponding to the energized solenoid valve falls alone.
[0024] The inlet of the sixth solenoid directional valve 106 is connected to the outlet port P. The return port of the sixth solenoid directional valve 106 is connected to the return port T via the seventh check valve 122. One working port of the sixth solenoid directional valve 106 is connected to the inlet ports of the fourth solenoid switch valve 110 and the fifth solenoid switch valve 111, respectively. The other working port of the sixth solenoid directional valve 106 is connected to port A10. A fourth relief valve 115 is installed between one working port of the sixth solenoid directional valve 106 and the return port T. The outlet of the fourth solenoid switch valve 110 is connected to port A8, and the outlet of the fifth solenoid switch valve 111 is connected to port A9. Port A10 is used to connect the small chambers of the two counterweight displacement cylinders. The outlets of the fourth solenoid switch valve 110 and the fifth solenoid switch valve 111 are connected to the large chambers of the two counterweight displacement cylinders via ports A8 and A9.
[0025] When the sixth solenoid directional valve 106 (Ya7) is energized, and both the fourth and fifth solenoid valves (110 and 111) are energized, the two counterweight positioning cylinders rise synchronously. When the sixth solenoid directional valve 106 (Ya8) is energized, and both the fourth and fifth solenoid valves (110 and 111) are energized, the two counterweight positioning cylinders fall synchronously. When the sixth solenoid directional valve 106 (Ya7) is energized, and only one of the four solenoid valves (110 and 111) is energized, the counterweight positioning cylinder corresponding to the energized solenoid valve rises individually. When the sixth solenoid directional valve 106 (Ya8) is energized, and only one of the four solenoid valves (110 and 111) is energized, the counterweight positioning cylinder corresponding to the energized solenoid valve falls individually.
[0026] Example 2
[0027] like Figure 3 As shown, the hydraulic system of this utility model includes the multi-functional counterweight action control valve 1 described in Embodiment 1, as well as the first diversion and combination valve 2, the second diversion and combination valve 3, the first balance valve 4, the second balance valve 5, the third balance valve 6, the fourth balance valve 7, the first counterweight lifting cylinder 8, the second counterweight lifting cylinder 9, the first counterweight displacement cylinder 10, the second counterweight displacement cylinder 11, the first shaft pulling cylinder 12, the second shaft pulling cylinder 13, the third shaft pulling cylinder 14, and the fourth shaft pulling cylinder 15.
[0028] The first solenoid valve 107 is a solenoid valve that controls the hydraulic cylinder's shaft-pulling function in the displacement counterweight device. The first solenoid valve 107 must be energized whenever the hydraulic cylinder's shaft-pulling function is used; otherwise, it must be de-energized. For example, when the first shaft-pulling cylinder 12 needs to retract to pull out the pin, the first solenoid valve 107 is energized, and simultaneously, Yb1 of the first solenoid directional valve 101 is energized. At this time, hydraulic oil flows to the small chamber of the first shaft-pulling cylinder 12, and the first shaft-pulling cylinder 12 retracts to pull out the pin. Similarly, when the first solenoid valve 107 is energized, and simultaneously, Ya1 of the first solenoid directional valve 101 is energized, hydraulic oil flows to the large chamber of the first shaft-pulling cylinder 12, and the first shaft-pulling cylinder 12 extends to insert the pin.
[0029] Similarly, the second electromagnetic reversing valve 102, the third electromagnetic reversing valve 103, and the fourth electromagnetic reversing valve 104 control the extension and retraction of the second shaft pulling cylinder 13, the third shaft pulling cylinder 14, and the fourth shaft pulling cylinder 15, respectively. Of course, the first electromagnetic switching valve 107 needs to be energized at this time.
[0030] The first relief valve 112 is the main relief valve, which limits the pressure of the hydraulic system of the entire counterweight action control valve and also plays a safety protection role. The second relief valve 113 is a secondary relief valve, which limits the pressure of the shaft pulling cylinder. Since the thrust or pull required for hydraulic shaft pulling is relatively low, the second relief valve 113 is added to further reduce the pressure of the shaft pulling system and play a safety protection role for the hydraulic cylinder shaft pulling system. In addition, when the hydraulic cylinder performs the shaft pulling action, it needs to pull the shaft slowly. Therefore, in order to prevent the shaft pulling cylinder from failing to insert or pull the pin due to the high speed during the insertion and removal of the pin, a damper 123 is designed after the first solenoid switch valve 107 to reduce the extension and retraction speed of the hydraulic cylinder in the shaft pulling system.
[0031] The small chambers of the first counterweight lifting cylinder 8, the second counterweight lifting cylinder 9, the first counterweight displacement cylinder 10, and the second counterweight displacement cylinder 11 are all equipped with balancing valves. Specifically: the V2 port of the first balancing valve 4 is connected to the C2 port of the first diverting and combining valve 2; the V1 port of the first balancing valve 4 is connected to the oil port A5 of the multi-functional counterweight action control valve 1; the C1 port of the first balancing valve 4 is connected to the large chamber of the first counterweight lifting cylinder 8; and the C2 port of the first balancing valve 4 is connected to the small chamber of the first counterweight lifting cylinder 8. The V2 port of the second balancing valve 5 is connected to the C1 port of the first diverting and combining valve 2; the V1 port of the second balancing valve 5 is connected to the oil port A6 of the multi-functional counterweight action control valve 1; the C1 port of the second balancing valve 5 is connected to the large chamber of the second counterweight lifting cylinder 9; and the C2 port of the second balancing valve 5 is connected to the small chamber of the second counterweight lifting cylinder 9. The third balancing valve 6 has its V2 port connected to the C2 port of the second diverting and combining valve 3, its V1 port connected to the A9 port of the multi-functional counterweight action control valve 1, its C1 port connected to the large chamber of the first counterweight displacement cylinder 10, and its C2 port connected to the small chamber of the first counterweight displacement cylinder 10. The fourth balancing valve 7 has its V2 port connected to the C1 port of the second diverting and combining valve 3, its V1 port connected to the A8 port of the multi-functional counterweight action control valve 1, its C1 port connected to the large chamber of the second counterweight displacement cylinder 11, and its C2 port connected to the small chamber of the second counterweight displacement cylinder 11. The first diverting and combining valve 2 has its V port connected to the A7 port of the counterweight action control valve 1, and the second diverting and combining valve 3 has its V port connected to the A10 port of the counterweight action control valve 1.
[0032] The hydraulic principles of the counterweight lifting function and the counterweight displacement function are the same. The fifth solenoid directional valve 105, the second solenoid switch valve 108, the third solenoid switch valve 109, and the third relief valve 114 of the multi-functional counterweight action control valve 1 control the counterweight lifting function, while the sixth solenoid directional valve 106, the fourth solenoid switch valve 110, the fifth solenoid switch valve 111, and the fourth relief valve 115 control the counterweight displacement function. The following explanation uses the counterweight lifting function as an example.
[0033] When the fifth solenoid directional valve 105 is energized (Ya5), hydraulic oil flows out from port A7 of the multi-functional counterweight action control valve 1, passes through the first diverter valve 2, and then flows in from the V2 ports of the first balance valve 4 and the second balance valve 5. It then flows through the C2 ports of the first balance valve 4 and the second balance valve 5 to the small chambers of the first counterweight lifting cylinder 8 and the second counterweight lifting cylinder 9. At this time, the second solenoid switch valve 108 and the third solenoid switch valve 109 are both energized. The hydraulic oil in the large chambers of the first counterweight lifting cylinder 8 and the second counterweight lifting cylinder 9 will then flow through the first balance valve 4 and the second balance valve 5 to ports A5 and A6 of the multi-functional counterweight action control valve 1, and then through the second solenoid switch valve 108 and the third solenoid switch valve 109, flowing back to the oil tank from the T port of the multi-functional counterweight action control valve 1. This achieves synchronous lifting of the first counterweight lifting cylinder 8 and the second counterweight lifting cylinder 9.
[0034] However, when the cylinder load is unbalanced or the control accuracy of the flow divider / combiner valve is insufficient, the cylinder movements will be asynchronous. In this case, the individual action of the lifting cylinder can be achieved by controlling the energization of the second solenoid valve 108 and the third solenoid valve 109. For example, when the fifth solenoid directional valve 105 is energized (Ya5), the second solenoid valve 108 is energized, while the third solenoid valve 109 is not energized. At this time, only the first counterweight lifting cylinder 8 performs the lifting action, while the second counterweight lifting cylinder 9 does not move, thus achieving the individual action of the lifting cylinder.
[0035] Similarly, when the fifth solenoid directional valve 105 is energized (Ya6), the second solenoid valve 108 and the third solenoid valve 109 are simultaneously energized, enabling the synchronous descent of the first counterweight lifting cylinder 8 and the second counterweight lifting cylinder 9. When the fifth solenoid directional valve 105 is energized (Ya6), and one of the second solenoid valve 108 and the third solenoid valve 109 is energized while the other is not, the first counterweight lifting cylinder 8 or the second counterweight lifting cylinder 9 can be descented individually.
[0036] The first relief valve 112 is the main relief valve and also a safety valve that limits the lifting pressure of the counterweight lifting and displacement cylinders. The third relief valve 114 is a secondary relief valve and is used to limit the falling pressure of the counterweight lifting and displacement cylinders.
[0037] Since the first electromagnetic directional valve 101, the second electromagnetic directional valve 102, the third electromagnetic directional valve 103, the fourth electromagnetic directional valve 104, the fifth electromagnetic directional valve 105, and the sixth electromagnetic directional valve 106 are three-position four-way Y-type electromagnetic directional valves, and the A and B ports of the directional valves are connected to the T port, when one of them is activated, for example, when the Ya1 of the first electromagnetic directional valve 101 is energized, the hydraulic oil flows to the large chamber of the first shaft-pulling cylinder 12, and the hydraulic oil in the small chamber of the first shaft-pulling cylinder 12 flows out from the T port. Some of the outflowing hydraulic oil will flow into the large and small chambers of the second shaft-pulling cylinder 13 through the T port of the second electromagnetic directional valve 102. Due to the area difference between the large and small chambers, the cylinder will extend, causing control disorder of the entire hydraulic system. In order to prevent oil leakage between the various actions of the system, a check valve is designed at the T port of each electromagnetic directional valve.
[0038] The technical solution of this utility model can be circumvented by replacing the damper 123 in the multi-functional counterweight action control valve 1 with a variable throttle valve or a flow valve to achieve controllable speed of the hydraulic cylinder shaft pulling function. The technical solution of this utility model can also be circumvented by replacing the three-position four-way Y-type solenoid directional valve in the multi-functional counterweight action control valve 1 with other types of directional valves. Finally, the technical solution of this invention can be circumvented by replacing the two-position two-way solenoid valve in the multi-functional counterweight action control valve 1 with other types of solenoid valves.
[0039] This solution enables control of multiple functions, including counterweight lifting, counterweight displacement, and hydraulic cylinder shaft pulling. It features high integration, low cost, small size, and easy installation. It effectively simplifies hydraulic system piping, reduces the number of hydraulic components, and improves the reliability of the hydraulic system. It can achieve both synchronous and independent movement of the counterweight lifting and displacement cylinders.
Claims
1. A multifunctional counterweight actuation control valve, characterized in that: It includes a first solenoid directional valve (101), a second solenoid directional valve (102), a third solenoid directional valve (103), a fourth solenoid directional valve (104), a first solenoid switching valve (107), an oil outlet P, and an oil return port T; The oil inlet of the first electromagnetic switch valve (107) is connected to the oil outlet P. The oil outlet of the first electromagnetic switch valve (107) is connected to the oil inlet of the first electromagnetic directional valve (101), the second electromagnetic directional valve (102), the third electromagnetic directional valve (103), and the fourth electromagnetic directional valve (104). The oil return ports of the first electromagnetic directional valve (101), the second electromagnetic directional valve (102), the third electromagnetic directional valve (103), and the fourth electromagnetic directional valve (104) are connected to the oil return port T through a check valve. The first electromagnetic reversing valve (101), the second electromagnetic reversing valve (102), the third electromagnetic reversing valve (103), and the fourth electromagnetic reversing valve (104) are used to control the extension and retraction of the four shaft-pulling cylinders. At this time, the first electromagnetic switching valve (107) is energized. It also includes oil port A7, fifth solenoid directional valve (105), second solenoid switch valve (108), and third solenoid switch valve (109); the oil inlet of the fifth solenoid directional valve (105) is connected to the oil outlet P, the oil return port of the fifth solenoid directional valve (105) is connected to the oil return port T through the sixth check valve (121), one working oil port of the fifth solenoid directional valve (105) is connected to the oil inlet of the second solenoid switch valve (108) and the third solenoid switch valve (109) respectively, and the other working oil port of the fifth solenoid directional valve (105) is connected to oil port A7; The oil port A7 is used to connect the small chambers of the two counterweight lifting cylinders, and the oil outlets of the second electromagnetic switch valve (108) and the third electromagnetic switch valve (109) are used to connect the large chambers of the two counterweight lifting cylinders. It also includes oil port A10, a sixth solenoid directional valve (106), a fourth solenoid switch valve (110), and a fifth solenoid switch valve (111); the oil inlet of the sixth solenoid directional valve (106) is connected to the oil outlet P, the oil return port of the sixth solenoid directional valve (106) is connected to the oil return port T through the seventh check valve (122), one working oil port of the sixth solenoid directional valve (106) is connected to the oil inlet of the fourth solenoid switch valve (110) and the fifth solenoid switch valve (111) respectively, and the other working oil port of the sixth solenoid directional valve (106) is connected to oil port A10; The oil port A10 is used to connect the small chambers of the two counterweight displacement cylinders, and the oil outlets of the fourth electromagnetic switch valve (110) and the fifth electromagnetic switch valve (111) are used to connect the large chambers of the two counterweight displacement cylinders.
2. The multifunctional counterweight action control valve according to claim 1, characterized in that: The oil outlet of the first electromagnetic switch valve (107) is equipped with a damper (123), and the oil return port T is equipped with a first check valve (116).
3. The multifunctional counterweight action control valve according to claim 1, characterized in that: A first overflow valve (112) is connected between the oil outlet P and the oil return port T, and a second overflow valve (113) is provided between the oil outlet and the oil return port T of the first electromagnetic switch valve (107).
4. The multifunctional counterweight action control valve according to claim 1, characterized in that: When the fifth electromagnetic reversing valve (105) is energized at Ya5, and the second electromagnetic switch valve (108) and the third electromagnetic switch valve (109) are also energized, the two counterweight lifting cylinders lift synchronously. When the fifth electromagnetic reversing valve (105) is energized at Ya6, and the second electromagnetic switch valve (108) and the third electromagnetic switch valve (109) are also energized, the two counterweight lifting cylinders fall synchronously.
5. The multifunctional counterweight action control valve according to claim 1, characterized in that: When the fifth electromagnetic reversing valve (105) is energized, and only one of the second electromagnetic switching valve (108) and the third electromagnetic switching valve (109) is energized, the counterweight lifting cylinder corresponding to the energized electromagnetic switching valve is lifted separately. When the fifth electromagnetic reversing valve (105) is energized, and only one of the second electromagnetic switch valve (108) and the third electromagnetic switch valve (109) is energized, the counterweight lifting cylinder corresponding to the energized electromagnetic switch valve falls separately.
6. The multifunctional counterweight action control valve according to claim 1, characterized in that: When the sixth electromagnetic reversing valve (106) is energized at Ya7, and the fourth electromagnetic switch valve (110) and the fifth electromagnetic switch valve (111) are both energized, the two counterweight displacement cylinders are lifted synchronously. When the sixth electromagnetic reversing valve (106) is energized at Ya8, and the fourth electromagnetic switch valve (110) and the fifth electromagnetic switch valve (111) are also energized, the two counterweight displacement cylinders fall synchronously.
7. The multifunctional counterweight action control valve according to claim 1, characterized in that: When the sixth electromagnetic reversing valve (106) is energized, and only one of the fourth electromagnetic switch valve (110) and the fifth electromagnetic switch valve (111) is energized, the counterweight displacement cylinder corresponding to the energized electromagnetic switch valve is lifted separately. When the sixth electromagnetic reversing valve (106) is energized, and only one of the fourth electromagnetic switch valve (110) and the fifth electromagnetic switch valve (111) is energized, the counterweight displacement cylinder corresponding to the energized electromagnetic switch valve falls separately.
8. A hydraulic system, characterized in that: Includes the multi-functional counterweight action control valve as described in any one of claims 1 to 7.