Large buried direct compression station liquid electric system
Patent Information
- Application Number
- CN202522521228.1
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-11-27
- Publication Date
- 2026-10-16
- Estimated Expiration
- 2035-11-27
AI Technical Summary
然而，现有技术中的大型地埋直压站液电系统存在显著设计缺陷：压缩油缸普遍采用单一匀速低速的运行模式，未充分考虑垃圾压缩全流程中阻力动态变化的核心特征 —— 在压缩初始阶段，垃圾箱内垃圾存量少、分布松散，压缩油缸推进时所受阻力极小，液压系统处于低负荷运行状态，此时仍维持匀速低速运行，不仅导致垃圾压缩处理周期冗长、整体效率低下，还造成了能源的不必要浪费；而随着垃圾不断堆积、逐步密实，压缩阻力持续增大，单一的运行速度既无法适配高负荷下的压缩需求，也难以平衡处理效率与系统稳定性，甚至可能因负荷突变引发液压冲击
[0023] 1. Multi-stage speed control significantly improves waste treatment efficiency: This application, through the design of multi-stage valve group coordinated control, constructs a three-stage compression speed mode of "high-speed compression → rapid compression → compression" and a two-stage return speed mode of "return → rapid return" for the compression cylinder by combining different solenoid valves on and off; the speed is dynamically adjusted according to the resistance changes in the waste compression stage, the waste treatment cycle is significantly shortened compared with the existing technology, and the treatment efficiency is significantly improved.
Smart Images
Figure CN224859807U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to the technical field of waste compression equipment, specifically to a large-scale underground direct-pressure station hydraulic-electric system. Background Technology
[0002] Large-scale underground direct-compression stations, as key equipment for centralized urban waste treatment, primarily function to reduce and compress waste through the reciprocating motion of hydraulic cylinders, thereby improving waste transfer efficiency and storage space utilization. However, existing large-scale underground direct-compression station hydraulic-electric systems have significant design flaws: the hydraulic cylinders generally adopt a single, uniform, low-speed operation mode, failing to fully consider the core characteristic of dynamic resistance changes throughout the entire waste compression process. In the initial stage of compression, the waste in the bin is small and loosely distributed, resulting in minimal resistance to the hydraulic cylinder's movement and a low-load operation of the hydraulic system. Maintaining a uniform, low-speed operation at this time not only leads to a lengthy waste compression cycle and low overall efficiency but also causes unnecessary energy waste. As the waste accumulates and gradually compacts, the compression resistance continuously increases. A single operating speed cannot meet the compression demands under high loads, nor can it balance processing efficiency and system stability; it may even cause hydraulic shocks due to sudden load changes.
[0003] Therefore, it is necessary to provide a large-scale underground direct pressure station hydraulic-electric system to solve the above-mentioned technical problems. Utility Model Content
[0004] The purpose of this invention is to address the shortcomings of existing technologies by providing a large-scale buried direct-pressure station hydraulic-electric system that can adapt to different compression stage load requirements and achieve dynamic speed and pressure regulation.
[0005] To achieve the above objectives, the technical solution adopted by this utility model is as follows:
[0006] A large underground direct pressure station hydraulic-electric system includes an oil tank assembly for carrying hydraulic oil, a hydraulic valve assembly, a gate cylinder, a sliding cover cylinder, and a compression cylinder.
[0007] The oil tank assembly is equipped with a dual-pump oil pump, which is connected to the hydraulic valve assembly via two separate oil circuits.
[0008] The hydraulic valve assembly includes a main inlet circuit that is connected to the main pump circuit and the secondary pump circuit of the dual-pump oil pump, a first return circuit that is connected to the main pump circuit of the dual-pump oil pump, a second return circuit that is connected to the secondary pump circuit of the dual-pump oil pump, and a main return circuit that is connected to the oil tank assembly.
[0009] The main oil inlet circuit is connected to the P port of the first three-position four-way solenoid valve, the P port of the second three-position four-way solenoid valve, and the P port of the third three-position four-way solenoid valve.
[0010] The main return oil circuit is respectively connected to the T oil port of the first three-position four-way solenoid valve, the T oil port of the second three-position four-way solenoid valve and the T oil port of the third three-position four-way solenoid valve.
[0011] The first return oil circuit is connected to the main pump oil circuit and then sequentially connected to the first hydraulic gauge and the pilot-operated solenoid relief valve before leading to the main return oil circuit;
[0012] The second return oil circuit is connected to the secondary pump oil circuit and then sequentially connected to the second hydraulic gauge and pressure regulating valve before leading to the main return oil circuit;
[0013] The first three-position four-way solenoid valve has its A and B ports connected in parallel to the first bidirectional hydraulic lock and the first one-way throttle valve, and is connected to the gate cylinder.
[0014] The A and B ports of the second three-position four-way solenoid valve are connected in parallel to the second bidirectional hydraulic lock and the second one-way throttle valve, and are connected to the sliding cover cylinder.
[0015] The A port of the third three-position four-way solenoid valve is connected to the first one-way hydraulic lock and is respectively connected to the P port of the first two-position four-way solenoid valve and the inlet port of the compression cylinder. The B port of the third three-position four-way solenoid valve is connected to the T port of the first two-position four-way solenoid valve, and the B port of the first two-position four-way solenoid valve is connected to the outlet port of the compression cylinder.
[0016] An unloading valve is provided between the main oil inlet circuit and the main oil return circuit.
[0017] Preferably, the pilot-operated electromagnetic relief valve includes a first pilot relief valve and a second two-position four-way solenoid valve, wherein the pressure setting value of the first pilot relief valve is 13 MPa.
[0018] Preferably, the pressure regulating valve includes a second pilot relief valve, a first relief valve, and a fourth three-position four-way solenoid valve. The P port of the second pilot relief valve is connected to the P port of the fourth three-position four-way solenoid valve, the B port of the fourth three-position four-way solenoid valve is connected to the P port of the first relief valve, the T port of the fourth three-position four-way solenoid valve is connected to the T port of the first relief valve, and the T port of the first relief valve is connected to the T port of the second pilot relief valve. The pressure setting value of the second pilot relief valve is 21 MPa, and the pressure setting value of the first relief valve is 13 MPa.
[0019] Preferably, a temperature sensor is provided in the main oil inlet circuit.
[0020] Preferably, the oil tank assembly includes an inlet oil filter, a return oil filter, and a return oil cooler. The inlet oil filter is connected to a dual-pump oil pump, and the return oil cooler and return oil filter are connected to the main return oil circuit.
[0021] Preferably, both the main pump oil circuit and the secondary pump oil circuit are equipped with check valves.
[0022] Compared with the prior art, this utility model has the following advantages:
[0023] 1. Multi-stage speed control significantly improves waste treatment efficiency: This application, through the design of multi-stage valve group coordinated control, constructs a three-stage compression speed mode of "high-speed compression → rapid compression → compression" and a two-stage return speed mode of "return → rapid return" for the compression cylinder by combining different solenoid valves on and off; the speed is dynamically adjusted according to the resistance changes in the waste compression stage, the waste treatment cycle is significantly shortened compared with the existing technology, and the treatment efficiency is significantly improved.
[0024] 2. Precise and controllable staged pressure, safe and stable system operation: This application determines the staged pressure setting through a pilot-operated electromagnetic relief valve and a pressure regulating valve. At the same time, one-way valves are installed in both the main pump oil circuit and the secondary pump oil circuit. Each cylinder circuit is equipped with a two-way hydraulic lock or a one-way hydraulic lock. This not only achieves precise pressure control, but also effectively locks the load and prevents hydraulic shock, avoiding damage to the system caused by pressure overload or sudden load changes, and ensuring long-term safe operation of the system. Attached Figure Description
[0025] Figure 1 This is a hydraulic schematic diagram of this utility model;
[0026] Figure 2 This is a schematic diagram of the pilot-operated electromagnetic relief valve in this utility model.
[0027] Figure 3 This is a schematic diagram of the pressure regulating valve in this utility model;
[0028] Figure 4 This is the sequence of actions for this utility model;
[0029] Among them, 1-oil tank assembly, 2-hydraulic valve assembly, 3-gate cylinder, 4-sliding cover cylinder, 5-compression cylinder, 6-main pump oil circuit, 7-secondary pump oil circuit, 8-main inlet oil circuit, 9-main return oil circuit, 10-first three-position four-way solenoid valve, 11-second three-position four-way solenoid valve, 12-third three-position four-way solenoid valve, 13-first hydraulic gauge, 14-pilot-operated solenoid relief valve, 15-second hydraulic gauge, 16-pressure regulating valve, 17-first two-way hydraulic lock, 18-the... 19-Second double-acting hydraulic lock; 20-Second one-way throttle valve; 21-First one-way hydraulic lock; 22-First two-position four-way solenoid valve; 23-Unloading valve; 24-First pilot-operated relief valve; 25-Second two-position four-way solenoid valve; 26-Second pilot-operated relief valve; 27-First relief valve; 28-Fourth three-position four-way solenoid valve; 29-Temperature sensor; 30-Inlet oil filter; 31-Return oil filter; 32-Return oil cooler; 33-Check valve Detailed Implementation
[0030] The present invention will be further illustrated below with reference to the accompanying drawings and specific embodiments. It should be understood that these embodiments are only for illustrating the present invention and not for limiting the scope of the present invention. After reading the present invention, any modifications of the present invention in various equivalent forms by those skilled in the art will fall within the scope defined by the appended claims.
[0031] In this utility model, unless otherwise explicitly specified and limited, the terms "installation", "setting", "connection", "fixed connection", 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 or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal connection of two components or the interaction between two components. Unless otherwise explicitly limited, those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.
[0032] In this utility model, terms such as "upper", "lower", "bottom", and "top" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only used to facilitate the description of the structural relationship between the various components or elements of this utility model and do not specifically refer to any component or element in this utility model. They should not be construed as limiting this utility model.
[0033] like Figures 1 to 3 As shown, a large underground direct pressure station hydraulic-electric system includes an oil tank assembly 1 that carries hydraulic oil, a hydraulic valve assembly 2, a gate cylinder 3, a sliding cover cylinder 4, and a compression cylinder 5.
[0034] The oil tank assembly is equipped with a dual-pump oil pump, which is divided into a main pump oil circuit 6 and a secondary pump oil circuit 7. After merging, they form a main inlet oil circuit 8 and are connected to the hydraulic valve assembly. The oil tank assembly is also connected to a main return oil circuit 9. A first return oil circuit is provided between the main pump oil circuit and the main return oil circuit, and a second return oil circuit is provided between the secondary pump oil circuit and the main return oil circuit. Both the main pump oil circuit and the secondary pump oil circuit are equipped with check valves 33. The oil tank assembly also includes an inlet oil filter 30 connected to the dual-pump oil pump, and a return oil cooler 32 and a return oil filter 31 connected to the main return oil circuit. A temperature sensor 29 is also installed in the main inlet oil circuit, and an unloading valve 23 is provided between the main inlet oil circuit and the main return oil circuit.
[0035] The main oil inlet circuit 8 is connected to the P port of the first three-position four-way solenoid valve 10, the P port of the second three-position four-way solenoid valve 11, and the P port of the third three-position four-way solenoid valve 12, respectively; the main oil return circuit 9 is connected to the T port of the first three-position four-way solenoid valve, the T port of the second three-position four-way solenoid valve, and the T port of the third three-position four-way solenoid valve, respectively.
[0036] The A and B ports of the first three-position four-way solenoid valve 10 are connected in parallel to the first bidirectional hydraulic lock 17 and the first one-way throttle valve 18, and are connected to the gate cylinder 3.
[0037] The A and B ports of the second three-position four-way solenoid valve 11 are connected in parallel to the second bidirectional hydraulic lock 19 and the second one-way throttle valve 20, and are connected to the sliding cover cylinder 4.
[0038] The A port of the third three-position four-way solenoid valve 12 is connected to the first one-way hydraulic lock 21 and is connected to the P port of the first two-position four-way solenoid valve 22 and the inlet port of the compression cylinder respectively. The B port of the third three-position four-way solenoid valve is connected to the T port of the first two-position four-way solenoid valve, and the B port of the first two-position four-way solenoid valve is connected to the outlet port of the compression cylinder 5.
[0039] The first return oil circuit is connected to the main pump oil circuit and then sequentially connected to the first hydraulic gauge 13, the pilot-operated solenoid relief valve 14, and then to the main return oil circuit. The pilot-operated solenoid relief valve includes a first pilot relief valve 24 and a second two-position four-way solenoid valve 25. The pressure setting value of the first pilot relief valve is 13 MPa.
[0040] The second return oil circuit is connected to the secondary pump oil circuit and then sequentially connected to the second hydraulic gauge 15 and the pressure regulating valve 16 before leading to the main return oil circuit. The pressure regulating valve includes a second pilot relief valve 26, a first relief valve 27 and a fourth three-position four-way solenoid valve 28. The P port of the second pilot relief valve is connected to the P port of the fourth three-position four-way solenoid valve, the B port of the fourth three-position four-way solenoid valve is connected to the P port of the first relief valve, the T port of the fourth three-position four-way solenoid valve is connected to the T port of the first relief valve, and the T port of the first relief valve is connected to the T port of the second pilot relief valve. The pressure setting value of the second pilot relief valve is 21 MPa, and the pressure setting value of the first relief valve is 13 MPa.
[0041] like Figure 4 The sequence of actions shown illustrates the principle and working process of this invention:
[0042] When the pilot-operated solenoid relief valve and the pressure regulating valve are not energized, they are both in the normally open unloading state; when 11DT is energized, the unloading set pressure value of the pressure regulating valve is 13 MPa; when 1DT is energized, the unloading set pressure value of the pressure regulating valve is 21 MPa.
[0043] When 3DT and 11DT are energized, the gate cylinder is pushed out; the A and P ports of the first three-position four-way solenoid valve are connected, and the B and T ports of the first three-position four-way solenoid valve are connected. The hydraulic oil enters the rodless chamber of the gate cylinder from the main oil inlet circuit through the P and A ports of the first three-position four-way solenoid valve, the first bidirectional hydraulic lock, and the first one-way throttle valve. Then, it returns to the main return oil circuit through the rod chamber of the gate cylinder, the first one-way throttle valve, the first bidirectional hydraulic lock, and the B and T ports of the first three-position four-way solenoid valve. At this time, the main oil inlet circuit is supplied with hydraulic oil by the secondary pump.
[0044] When 4DT and 11DT are energized, the gate cylinder returns; the A and T ports of the first three-position four-way solenoid valve are connected, and the B and P ports of the first three-position four-way solenoid valve are connected. The hydraulic oil enters the rod chamber of the gate cylinder from the main oil inlet circuit through the P and B ports of the first three-position four-way solenoid valve, the first bidirectional hydraulic lock, and the first one-way throttle valve. Then, it returns to the main return oil circuit through the rodless chamber of the gate cylinder, the first one-way throttle valve, the first bidirectional hydraulic lock, and the A and T ports of the first three-position four-way solenoid valve. At this time, the main oil inlet circuit is supplied with hydraulic oil by the secondary pump.
[0045] When 5DT and 11DT are energized, the sliding cover cylinder extends, and the principle is the same as that of the gate cylinder.
[0046] When 6DT and 11DT are energized, the sliding cover cylinder returns, and the principle is the same as that of the gate cylinder.
[0047] When 2DT, 7DT, 9DT, and 11DT are energized, the compression cylinder compresses at high speed; the A and P ports of the third and third position four-way solenoid valves are connected, the B and T ports of the third and third position four-way solenoid valves are connected, and the B and P ports of the first and second position four-way solenoid valves are connected. The hydraulic oil enters the rodless chamber of the compression cylinder from the main oil inlet circuit through the P and A ports of the third and third position four-way solenoid valves, and then flows back to the rodless chamber of the compression cylinder through the rod chamber of the compression cylinder and the B and P ports of the first and second position four-way solenoid valves. At this time, the compression frequency of the compression cylinder is the fastest. The main oil inlet circuit provides hydraulic oil jointly supplied by the main pump and the secondary pump.
[0048] When 2DT, 7DT, and 11DT are energized, the compression cylinder compresses rapidly; the A and P ports of the third three-position four-way solenoid valve are connected, the B and T ports of the third three-position four-way solenoid valve are connected, and the B and T ports of the first two-position four-way solenoid valve are connected. The hydraulic oil enters the rodless chamber of the compression cylinder from the main oil inlet circuit through the P and A ports of the third three-position four-way solenoid valve, and then returns to the main return oil circuit through the rod chamber of the compression cylinder, the B and T ports of the first two-position four-way solenoid valve, and the B and T ports of the third three-position four-way solenoid valve. At this time, the compression frequency of the compression cylinder is lower than that of the high-speed compression stage. The main oil inlet circuit provides hydraulic oil jointly supplied by the main pump and the secondary pump.
[0049] When 1DT and 7DT are energized, the compression cylinder compresses; the A and P ports of the third three-position four-way solenoid valve are connected, the B and T ports of the third three-position four-way solenoid valve are connected, and the B and T ports of the first two-position four-way solenoid valve are connected. The hydraulic oil enters the rodless chamber of the compression cylinder from the main oil inlet circuit through the P and A ports of the third three-position four-way solenoid valve, and then returns to the main return oil circuit through the rod chamber of the compression cylinder, the B and T ports of the first two-position four-way solenoid valve, and the B and T ports of the third three-position four-way solenoid valve. At this time, the compression frequency of the compression cylinder is lower than that of the rapid compression stage, and the main oil inlet circuit is supplied with hydraulic oil by the secondary pump.
[0050] When the 10DT is energized, the compression cylinder is unloaded; the hydraulic oil returns from the main inlet circuit to the main return circuit via the unloading valves A and T.
[0051] When 8DT and 11DT are energized, the compression cylinder returns; the A and T ports of the third three-position four-way solenoid valve are connected, the B and P ports of the third three-position four-way solenoid valve are connected, and the B and T ports of the first two-position four-way solenoid valve are connected. The hydraulic oil enters the rod chamber of the compression cylinder from the main oil inlet circuit through the P and B ports of the third three-position four-way solenoid valve and the T and B ports of the first two-position four-way solenoid valve, and then returns to the main return oil circuit through the rodless chamber of the compression cylinder and the A and T ports of the third three-position four-way solenoid valve. The main oil inlet circuit is the hydraulic oil supplied by the secondary pump.
[0052] When 1DT, 2DT, and 8DT are energized, the compression cylinder returns rapidly; the A and T ports of the third three-position four-way solenoid valve are connected, the B and P ports of the third three-position four-way solenoid valve are connected, and the B and T ports of the first two-position four-way solenoid valve are connected. The hydraulic oil enters the rod chamber of the compression cylinder from the main inlet circuit through the P and B ports of the third three-position four-way solenoid valve and the T and B ports of the first two-position four-way solenoid valve, and then returns to the main return circuit through the rodless chamber of the compression cylinder and the A and T ports of the third three-position four-way solenoid valve. The main inlet circuit provides hydraulic oil for both the main pump and the secondary pump.
[0053] The foregoing description illustrates and describes preferred embodiments of the present invention. As previously stated, it should be understood that the present invention is not limited to the forms disclosed herein and should not be construed as excluding other embodiments. It can be used in various other combinations, modifications, and environments, and can be altered within the scope of the inventive concept described herein through the foregoing teachings or related technical or knowledge. Any modifications and variations made by those skilled in the art that do not depart from the spirit and scope of the present invention should be within the protection scope of the appended claims.
Claims
1. A large-scale buried direct-pressure station hydraulic-electric system, characterized in that: It includes an oil tank assembly (1) that carries hydraulic oil, a hydraulic valve assembly (2), a gate cylinder (3), a sliding cover cylinder (4), and a compression cylinder (5); The oil tank assembly is equipped with a dual-pump oil pump, which is connected to the hydraulic valve assembly via two separate oil circuits. The hydraulic valve assembly includes a main inlet circuit (8) that is connected to the main pump circuit (6) and the secondary pump circuit (7) of the dual-pump oil pump, a first return circuit that is connected to the main pump circuit of the dual-pump oil pump, a second return circuit that is connected to the secondary pump circuit of the dual-pump oil pump, and a main return circuit (9) that is connected to the oil tank assembly. The main oil inlet circuit is connected to the P port of the first three-position four-way solenoid valve (10), the P port of the second three-position four-way solenoid valve (11), and the P port of the third three-position four-way solenoid valve (12). The main return oil circuit is respectively connected to the T oil port of the first three-position four-way solenoid valve, the T oil port of the second three-position four-way solenoid valve and the T oil port of the third three-position four-way solenoid valve. The first return oil circuit is connected to the main pump oil circuit and then sequentially connected to the first hydraulic gauge (13), the pilot-operated solenoid relief valve (14) and then to the main return oil circuit; The second return oil circuit is connected to the secondary pump oil circuit and then connected to the second hydraulic gauge (15) and pressure regulating valve (16) in sequence before leading to the main return oil circuit; The first three-position four-way solenoid valve has its A and B ports connected in parallel to the first bidirectional hydraulic lock (17) and the first one-way throttle valve (18), and connected to the gate cylinder. The A and B ports of the second three-position four-way solenoid valve are connected in parallel to the second bidirectional hydraulic lock (19) and the second one-way throttle valve (20), and are connected to the sliding cover cylinder. The A port of the third three-position four-way solenoid valve is connected to the first one-way hydraulic lock (21) and is respectively connected to the P port of the first two-position four-way solenoid valve (22) and the inlet port of the compression cylinder. The B port of the third three-position four-way solenoid valve is connected to the T port of the first two-position four-way solenoid valve, and the B port of the first two-position four-way solenoid valve is connected to the outlet port of the compression cylinder. An unloading valve (23) is provided between the main oil inlet circuit and the main oil return circuit.
2. The large-scale buried direct-pressure station hydraulic-electric system according to claim 1, characterized in that: The pilot-operated electromagnetic relief valve includes a first pilot relief valve (24) and a second two-position four-way solenoid valve (25), with the pressure setting value of the first pilot relief valve being 13 MPa.
3. The large-scale buried direct-pressure station hydraulic-electric system according to claim 1, characterized in that: The pressure regulating valve includes a second pilot relief valve (26), a first relief valve (27), and a fourth three-position four-way solenoid valve (28). The P port of the second pilot relief valve is connected to the P port of the fourth three-position four-way solenoid valve. The B port of the fourth three-position four-way solenoid valve is connected to the P port of the first relief valve. The T port of the fourth three-position four-way solenoid valve is connected to the T port of the first relief valve. The T port of the first relief valve is connected to the T port of the second pilot relief valve. The pressure setting value of the second pilot relief valve is 21 MPa, and the pressure setting value of the first relief valve is 13 MPa.
4. The large-scale buried direct-pressure station hydraulic-electric system according to claim 1, characterized in that: A temperature sensor (29) is installed in the main oil inlet circuit.
5. The large-scale buried direct-pressure station hydraulic-electric system according to claim 1, characterized in that: The oil tank assembly includes an inlet filter (30), a return filter (31), and a return cooler (32). The inlet filter is connected to a dual-pump oil pump, and the return cooler and return filter are connected to the main return oil circuit.
6. The large-scale buried direct-pressure station hydraulic-electric system according to claim 1, characterized in that: Both the main pump oil circuit and the secondary pump oil circuit are equipped with check valves (33).