Large buried direct pressure station hydraulic valve group

Abstract

The utility model discloses a large -scale buried direct pressure station hydraulic valve group, including first three position four -way electromagnetic valve, second three position four -way electromagnetic valve and third three position four -way electromagnetic valve, and the P oil port of first three position four -way electromagnetic valve, second three position four -way electromagnetic valve, third three position four -way electromagnetic valve has the main oil inlet road in parallel, and the T oil port of first three position four -way electromagnetic valve, second three position four -way electromagnetic valve, third three position four -way electromagnetic valve has the main oil return road in parallel, and the A, B oil port of first three position four -way electromagnetic valve intercommunication gate oil cylinder, and the A, B oil port of second three position four -way electromagnetic valve intercommunication slide cover oil cylinder, and the A oil port of third three position four -way electromagnetic valve intercommunication compression oil cylinder's rodless chamber, the P oil port of first two position four -way electromagnetic valve respectively, and the B oil port of third three position four -way electromagnetic valve intercommunication first two position four -way electromagnetic valve's T oil port, and the B oil port of first two position four -way electromagnetic valve intercommunication compression oil cylinder's rod chamber. This valve group has the ability of grading control, and has improved the operation efficiency of system.

Description

Technical Field

[0001] This utility model relates to the technical field of waste compression equipment, specifically to a hydraulic valve group for a large underground direct compression station. Background Technology

[0002] The hydraulic valve assembly is the core control unit of the electrohydraulic system in a large underground direct-pressure station. Its performance directly determines the pressure control accuracy, speed adaptability, and system operational stability during the waste compression process. Throughout the entire waste compression process in a large underground direct-pressure station, the resistance to waste changing from a loose to a compacted state dynamically increases, placing stringent demands on the staged control capabilities of the hydraulic valve assembly. However, existing hydraulic valve assemblies for large underground direct-pressure stations have significant design flaws:

[0003] Existing hydraulic valve assemblies mostly use a single valve path and fixed parameter control, lacking a graded regulation mechanism. They can only achieve uniform speed operation of the compression cylinder, which cannot match the differentiated needs of the initial stage (low resistance, high speed and high efficiency required) and the later stage (high resistance, high pressure and stable speed required) of garbage compression. This results in serious energy waste and a long processing cycle in the initial stage, while the later stage is prone to operation jams due to overload.

[0004] Therefore, it is necessary to provide a large-scale underground direct pressure station hydraulic valve group to solve the above-mentioned technical problems. Utility Model Content

[0005] The purpose of this invention is to address the shortcomings of existing technologies by providing a large-scale buried direct pressure station hydraulic valve group with graded regulation capabilities, precise and controllable pressure, and a high degree of integration.

[0006] To achieve the above objectives, the technical solution adopted by this utility model is as follows:

[0007] A hydraulic valve assembly for a large underground direct pressure station includes a first three-position four-way solenoid valve, a second three-position four-way solenoid valve, and a third three-position four-way solenoid valve. The P ports of the first three-position four-way solenoid valve, the second three-position four-way solenoid valve, and the third three-position four-way solenoid valve are connected in parallel to a main oil inlet circuit. The T ports of the first three-position four-way solenoid valve, the second three-position four-way solenoid valve, and the third three-position four-way solenoid valve are connected in parallel to a main oil return circuit. The main oil inlet circuit includes a main pump oil circuit connected to the main pump outlet, which is equipped with a first check valve, and a secondary pump oil circuit connected to the secondary pump outlet, which is equipped with a second check valve. A connection is provided between the main pump oil circuit and the main oil return circuit. There is a pilot-operated solenoid relief valve. A pressure regulating valve is installed between the secondary pump oil circuit and the main return oil circuit. The A port of the first three-position four-way solenoid valve is connected to the rodless chamber of the gate cylinder, and its B port is connected to the rod chamber of the gate cylinder. The A port of the second three-position four-way solenoid valve is connected to the rodless chamber of the sliding cover cylinder, and its B port is connected to the rod chamber of the sliding cover cylinder. The A port of the third three-position four-way solenoid valve is connected to the rodless chamber of the compression cylinder and the P port of the first two-position four-way solenoid valve. 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. The B port of the first two-position four-way solenoid valve is connected to the rod chamber of the compression cylinder.

[0008] Preferably, a one-way hydraulic lock is provided between the A port of the third-position four-way solenoid valve and the rodless chamber of the compression cylinder.

[0009] Preferably, a first bidirectional hydraulic lock and a first one-way throttle valve are sequentially provided between the first three-position four-way solenoid valve and the gate cylinder.

[0010] Preferably, a second bidirectional hydraulic lock and a second one-way throttle valve are sequentially provided between the second three-position four-way solenoid valve and the sliding cover cylinder.

[0011] 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.

[0012] 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.

[0013] Preferably, an unloading valve is provided between the main oil inlet circuit and the main oil return circuit.

[0014] Preferably, a temperature sensor is installed in the main oil inlet circuit.

[0015] Compared with the prior art, this utility model has the following advantages:

[0016] This hydraulic valve assembly employs a multi-solenoid valve collaborative control design, precisely coordinating the first, second, and third three-position four-way solenoid valves with the first and second-position four-way solenoid valves. Combined with the switching adaptation of the dual-pump oil circuit, it 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. This design can dynamically adjust the operating speed according to the resistance at each stage of waste compression, achieving high-speed and efficient compression in the initial stage of low resistance and maintaining stable compression speed in the later stage of high resistance, significantly shortening the waste processing cycle and improving processing efficiency. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of the hydraulic valve assembly of this utility model;

[0018] Figure 2 This is a system schematic diagram using the hydraulic valve assembly of this utility model;

[0019] Figure 3 This is a schematic diagram of the pilot-operated electromagnetic relief valve in this utility model.

[0020] Figure 4 This is a schematic diagram of the pressure regulating valve in this utility model;

[0021] Figure 5 This is the sequence of actions for the hydraulic system;

[0022] Among them, 1-first three-position four-way solenoid valve, 2-second three-position four-way solenoid valve, 3-third three-position four-way solenoid valve, 4-main oil inlet circuit, 5-main oil return circuit, 6-main pump, 7-first check valve, 8-secondary pump, 9-second check valve, 10-pilot-operated solenoid relief valve, 11-pressure regulating valve, 12-gate cylinder, 13-sliding cover cylinder, 14-compression cylinder, 15-first two-position four-way solenoid valve, 16-one-way hydraulic lock, 17-first two-way hydraulic lock, 18-first one-way throttle valve, 19-second two-way hydraulic lock, 20-second one-way throttle valve, 21-first pilot relief valve, 22-second two-position four-way solenoid valve, 23-second pilot relief valve, 24-first relief valve, 25-fourth three-position four-way solenoid valve, 26-unloading valve Detailed Implementation

[0023] 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.

[0024] 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.

[0025] 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.

[0026] like Figures 1 to 4 As shown, a hydraulic valve group for a large underground direct pressure station includes a first three-position four-way solenoid valve 1, a second three-position four-way solenoid valve 2, and a third three-position four-way solenoid valve 3. The P ports of the first three-position four-way solenoid valve, the second three-position four-way solenoid valve, and the third three-position four-way solenoid valve are connected in parallel to a main oil inlet circuit 4. The T ports of the first three-position four-way solenoid valve, the second three-position four-way solenoid valve, and the third three-position four-way solenoid valve are connected in parallel to a main oil return circuit 5.

[0027] The main oil inlet circuit includes a main pump oil circuit connected to the oil outlet of the main pump 6, which is equipped with a first check valve 7. It also includes a secondary pump oil circuit connected to the oil outlet of the secondary pump 8, which is equipped with a second check valve 9. A pilot-operated solenoid relief valve 10 is provided between the main pump oil circuit and the main return oil circuit. The pilot-operated solenoid relief valve includes a first pilot relief valve 21 and a second two-position four-way solenoid valve 22. The pressure setting value of the first pilot relief valve is 13 MPa.

[0028] A pressure regulating valve 11 is provided between the secondary pump oil circuit and the main return oil circuit. The pressure regulating valve includes a second pilot relief valve 23, a first relief valve 24, and a fourth three-position four-way solenoid valve 25. 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.

[0029] The A port of the first three-position four-way solenoid valve is connected to the rodless chamber of the gate cylinder, and its B port is connected to the rod chamber of the gate cylinder. A first bidirectional hydraulic lock and a first one-way throttle valve are sequentially provided between the first three-position four-way solenoid valve and the gate cylinder.

[0030] The A port of the second three-position four-way solenoid valve is connected to the rodless chamber of the sliding cover cylinder, and its B port is connected to the rod chamber of the sliding cover cylinder. A second bidirectional hydraulic lock and a second one-way throttle valve are sequentially provided between the second three-position four-way solenoid valve and the sliding cover cylinder.

[0031] The A port of the third and third position four-way solenoid valve is connected to the rodless chamber of the compression cylinder, the P port of the first and second position four-way solenoid valve, and the one-way hydraulic lock, respectively. The B port of the third and third position four-way solenoid valve is connected to the T port of the first and second position four-way solenoid valve, and the B port of the first and second position four-way solenoid valve is connected to the rod chamber of the compression cylinder.

[0032] An unloading valve 26 is installed between the main oil inlet circuit and the main oil return circuit;

[0033] A temperature sensor is installed in the main oil inlet circuit.

[0034] like Figure 5 The sequence of actions shown illustrates the principle and working process of this invention:

[0035] 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.

[0036] First, start the main pump and secondary pump under no-load. After starting,

[0037] 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.

[0038] 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.

[0039] When 5DT and 11DT are energized, the sliding cover cylinder extends, and the principle is the same as that of the gate cylinder.

[0040] When 6DT and 11DT are energized, the sliding cover cylinder returns, and the principle is the same as that of the gate cylinder.

[0041] 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.

[0042] 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.

[0043] 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.

[0044] 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.

[0045] 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.

[0046] 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.

[0047] 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 hydraulic valve assembly for a large underground direct pressure station, characterized in that: The system includes a first three-position four-way solenoid valve (1), a second three-position four-way solenoid valve (2), and a third three-position four-way solenoid valve (3). The P ports of the first three-position four-way solenoid valve, the second three-position four-way solenoid valve, and the third three-position four-way solenoid valve are connected in parallel to the main oil inlet circuit (4). The T ports of the first three-position four-way solenoid valve, the second three-position four-way solenoid valve, and the third three-position four-way solenoid valve are connected in parallel to the main return oil circuit (5). The main oil inlet circuit includes a main pump oil circuit connected to the outlet of the main pump (6), which is equipped with a first check valve (7). It also includes a secondary pump oil circuit connected to the outlet of the secondary pump (8), which is equipped with a second check valve (9). A pilot-operated solenoid valve is provided between the main pump oil circuit and the main return oil circuit. An overflow valve (10) is provided. A pressure regulating valve (11) is provided between the secondary pump oil circuit and the main return oil circuit. The A port of the first three-position four-way solenoid valve is connected to the rodless chamber of the gate cylinder (12), and its B port is connected to the rod chamber of the gate cylinder. The A port of the second three-position four-way solenoid valve is connected to the rodless chamber of the sliding cover cylinder (13), and its B port is connected to the rod chamber of the sliding cover cylinder. The A port of the third three-position four-way solenoid valve is connected to the rodless chamber of the compression cylinder (14) and the P port of the first two-position four-way solenoid valve (15). 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. The B port of the first two-position four-way solenoid valve is connected to the rod chamber of the compression cylinder.

2. The hydraulic valve assembly for a large underground direct pressure station according to claim 1, characterized in that: A one-way hydraulic lock (16) is provided between the A port of the third three-position four-way solenoid valve and the rodless chamber of the compression cylinder.

3. The hydraulic valve assembly for a large underground direct pressure station according to claim 1, characterized in that: The first three-position four-way solenoid valve and the gate cylinder are respectively provided with a first bidirectional hydraulic lock (17) and a first one-way throttle valve (18).

4. The hydraulic valve assembly for a large underground direct pressure station according to claim 1, characterized in that: A second bidirectional hydraulic lock (19) and a second one-way throttle valve (20) are sequentially provided between the second three-position four-way solenoid valve and the sliding cover cylinder.

5. A hydraulic valve group for a large underground direct pressure station according to claim 1, characterized in that: The pilot-operated solenoid relief valve (10) includes a first pilot relief valve (21) and a second two-position four-way solenoid valve (22), and the pressure setting value of the first pilot relief valve is 13 MPa.

6. The hydraulic valve assembly for a large underground direct pressure station according to claim 1, characterized in that: The pressure regulating valve (11) includes a second pilot relief valve (23), a first relief valve (24), and a fourth three-position four-way solenoid valve (25). 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.

7. A hydraulic valve assembly for a large underground direct pressure station according to claim 1, characterized in that: An unloading valve (26) is installed between the main oil inlet circuit and the main oil return circuit.

8. A hydraulic valve assembly for a large underground direct pressure station according to claim 1, characterized in that: A temperature sensor is installed in the main oil inlet circuit.

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