Integrated bidirectional hydraulic pump station for in-tank car arrester

Abstract

The utility model discloses an integrated bidirectional hydraulic pump station for a car arrester in a tank, which comprises a valve block, a bidirectional hydraulic pump, a motor, an oil tank, a car arrester driving oil cylinder, overflow valves and one-way valves, a left oil way and a right oil way are arranged in the valve block, the left oil way is provided with a first overflow valve, a first one-way valve and a fifth one-way valve, and the fifth one-way valve is a hydraulic control one-way valve. A second overflow valve and a second one-way valve are installed on the right oil way, and the second one-way valve is a hydraulic control one-way valve and is controlled by the oil pressure of the left oil way; an oil port A1 of the two-way hydraulic pump is connected with a piston cavity oil port of the car arrester driving oil cylinder through a left oil way, and an oil port B1 of the two-way hydraulic pump is connected with a piston rod cavity oil port of the car arrester driving oil cylinder through a right oil way. The left oil way is connected with the oil tank through a fifth one-way valve, and the fifth one-way valve is used for releasing additional backpressure generated in a piston cavity in the process that the two-way hydraulic pump drives a piston rod of the car arrester driving oil cylinder to retract. According to the utility model, the power consumption is reduced, the energy is saved, and the reliability of the system is improved.

Description

Technical Field

[0001] This utility model relates to an integrated bidirectional hydraulic pump station for a tank-mounted vehicle stopper, belonging to the field of mining machinery. Background Technology

[0002] The working environment of the cage-mounted vehicle arrester is harsh, with frequent water spray and coal slag spillage. Furthermore, the cage's stopping position often deviates significantly, causing operational inconvenience. Currently, commonly used mining cage-mounted vehicle arresters mainly include hydraulic external-powered, manual, and electric types. Hydraulic external-powered cage-mounted vehicle arresters are subject to significant structural limitations; electric cage-mounted vehicle arresters have poor overload characteristics; and manual cage-mounted vehicle arresters require specialized manual operation, posing certain safety hazards. A bidirectional hydraulic pump-driven cage-mounted vehicle arrester system has a relatively simple structure and can be remotely operated, avoiding the risks of manual operation and improving operational safety. However, in typical bidirectional hydraulic pump-driven systems, there is an additional back pressure problem in the piston chamber of the cylinder during the control of the cylinder's retraction. This back pressure is usually counteracted by increasing the pressure in the piston rod chamber, thus forcing the piston rod to retract. This method leads to increased power consumption and energy waste. Summary of the Invention

[0003] To address the problems existing in the prior art, this utility model provides an integrated bidirectional hydraulic pump station for tank-mounted vehicle stoppers, which meets the working requirements of tank-mounted vehicle stoppers.

[0004] To achieve the above objectives, this utility model employs an integrated bidirectional hydraulic pump station for a tank-mounted vehicle stopper, comprising a valve block, a bidirectional hydraulic pump, a motor, an oil tank, a vehicle stopper drive cylinder, an overflow valve, and a check valve. The bidirectional hydraulic pump and the oil tank are respectively connected to the valve block. The oil tank is connected to the oil port A1 of the bidirectional hydraulic pump through check valve three, and the oil tank is connected to the oil port B1 of the bidirectional hydraulic pump through check valve four. The motor is connected to the bidirectional hydraulic pump.

[0005] The valve block is provided with a left oil passage and a right oil passage. The left oil passage is equipped with an overflow valve 1, a check valve 1, and a check valve 5. The check valve 5 is a hydraulically controlled check valve and is controlled by the oil pressure of the right oil passage. The right oil passage is equipped with an overflow valve 2 and a check valve 2. The check valve 2 is a hydraulically controlled check valve and is controlled by the oil pressure of the left oil passage. The oil port A1 of the bidirectional hydraulic pump is connected to the piston chamber oil port of the vehicle stopper drive cylinder via the left oil passage, and the oil port B1 of the bidirectional hydraulic pump is connected to the piston rod chamber oil port of the vehicle stopper drive cylinder via the right oil passage.

[0006] The left oil circuit is connected to the oil tank through one-way valve five. One-way valve five is the pressure relief structure of the left oil circuit, used to release the additional back pressure generated in the piston chamber during the retraction of the piston rod of the piston rod driven by the bidirectional hydraulic pump-driven brake cylinder.

[0007] As an improvement, the one-way valve is a hydraulically controlled one-way valve, which is controlled by the oil pressure in the right oil circuit.

[0008] As an improvement, the vehicle stopper driving cylinder includes a vehicle stopper driving cylinder one and a vehicle stopper driving cylinder two. The left oil circuit is connected to the piston chamber oil port of the two vehicle stopper driving cylinders respectively through a solenoid valve one, and the right oil circuit is connected to the piston rod chamber oil port of the two vehicle stopper driving cylinders respectively through a solenoid valve two.

[0009] As an improvement, both solenoid valve one and solenoid valve two are two-position three-way solenoid valves.

[0010] Compared with the prior art, the integrated bidirectional hydraulic pump station for the tank-mounted vehicle stopper of this utility model adopts a controlled pressure relief method, which effectively solves the problem of additional back pressure in the piston chamber oil circuit during the retraction process of the general bidirectional hydraulic pump drive system. This utility model does not need to use the method of increasing the pressure in the piston rod chamber of the oil cylinder to offset the back pressure, thereby reducing power consumption, saving energy, and improving the reliability of the system. Attached Figure Description

[0011] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0012] Figure 1 This is a schematic diagram of the structure of the present invention. Figure 1 (Applicable to single brake actuator drive cylinder);

[0013] Figure 2 This is a schematic diagram of the structure of the present invention. Figure 2 (Applicable to single brake actuator drive cylinder);

[0014] Figure 3 This is a schematic diagram of the structure of the present invention. Figure 3 (Applicable to hydraulic cylinders driven by two brake actuators);

[0015] In the diagram: 1. Valve block, 2. Two-way hydraulic pump, 3. Motor, 4. Oil tank, 5. Vehicle stopper drive cylinder one, 6. Vehicle stopper drive cylinder two, 7. Solenoid valve one, 8. Solenoid valve two; W1. Relief valve one, W2. Relief valve two; D1. Check valve one, D2. Check valve two, D3. Check valve three, D4. Check valve four, D5. Check valve five. Detailed Implementation

[0016] To make the objectives, technical solutions, and advantages of this utility model clearer, the technical solutions of this application will be described in detail below with reference to the accompanying drawings and specific embodiments. It should be understood that the embodiments and specific features in the embodiments are detailed descriptions of the technical solutions of this application, rather than limitations thereof. In the absence of conflict, the embodiments and technical features in the embodiments can be combined with each other.

[0017] In the description of this utility model, it should be understood that the terms "left" and "right" 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 this utility model and to simplify the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limiting the scope of protection of this utility model.

[0018] Example 1

[0019] like Figure 1 As shown, an integrated bidirectional hydraulic pump station for a tank-mounted vehicle stopper includes a valve block 1, a bidirectional hydraulic pump 2, a motor 3, an oil tank 4, a vehicle stopper drive cylinder 5, an overflow valve 1 W1, an overflow valve 2 W2, a check valve 1 D1, a check valve 2 D2, a check valve 3 D3, a check valve 4 D4, and a check valve 5 D5, etc.

[0020] The bidirectional hydraulic pump 2 is provided with oil port A1 and oil port B1, and the vehicle stopper drive cylinder 5 is provided with piston chamber oil port A2 and piston rod chamber oil port B2.

[0021] The bidirectional hydraulic pump 2 and the oil tank 4 are respectively connected to the valve block 1. The oil tank 4 is connected to the oil port A1 through the one-way valve D3 and the oil port B1 through the one-way valve D4. The motor 3 is connected to the bidirectional hydraulic pump 2.

[0022] The valve block 1 is integrated with the overflow valve W1, overflow valve W2, check valve D1, check valve D2, and check valve D5. The valve block 1 has a left oil passage and a right oil passage. Check valve D1, check valve D5, and overflow valve W1 are connected to the left oil passage, and check valve D2 and overflow valve W2 are connected to the right oil passage. Check valve D2 and check valve D5 are both hydraulically controlled check valves. Check valve D5 is controlled by the oil pressure of the right oil passage, and check valve D2 is controlled by the oil pressure of the left oil passage.

[0023] The left oil passage port A3 of the valve block 1 is connected to the piston chamber port A2 of the brake drive cylinder 5, and the right oil passage port B3 is connected to the piston rod chamber port B2 of the brake drive cylinder 5.

[0024] A one-way valve D5 is provided at oil port A3. The one-way valve D5 is a hydraulically controlled one-way valve. When the one-way valve D5 is opened, the piston chamber oil port A2 is connected to the oil tank 4, which plays a role in relieving pressure.

[0025] The motor 3 drives the bidirectional hydraulic pump 2 to operate in either the forward or reverse direction:

[0026] When motor 3 drives bidirectional hydraulic pump 2 to run in the forward direction, oil port A1 is the oil outlet and outputs high-pressure oil, and oil port B1 is the oil inlet. At this time, the high-pressure oil output from oil port A1 goes through check valve D1 to oil port A3, and continues to be output to piston chamber oil port A2. At the same time, the high-pressure oil in oil port A1 is limited by overflow valve W1. Under the control of the high-pressure oil in oil port A3, check valve D2 (hydraulic control check valve) is opened, the brake drive cylinder 5 is unlocked, the piston rod of brake drive cylinder 5 extends, and the hydraulic oil in the piston rod chamber is discharged through oil port B2, and then sequentially through oil port B3, the opened check valve D2, and oil port B1, and returns to bidirectional hydraulic pump 2. In addition, part of the oil entering bidirectional hydraulic pump 2 is replenished by oil tank 4 through check valve D4.

[0027] When motor 3 drives bidirectional hydraulic pump 2 to run in reverse, oil port B1 is the oil outlet and outputs high-pressure oil, and oil port A1 is the oil inlet. At this time, the high-pressure oil output from oil port B1 passes through check valve D2 to oil port B3, and is output to oil port B2 in the piston rod chamber. At the same time, the high-pressure oil in oil port B1 is limited by overflow valve W2. Under the control of the high-pressure oil in oil port B3, check valve D5 (hydraulic control check valve) opens, the brake drive cylinder 5 unlocks, and the piston rod of brake drive cylinder 5 retracts. All the return oil from oil port A2 in the piston chamber flows back to oil tank 4 through oil port A3 and the opened check valve D5, achieving the purpose of releasing back pressure. The oil required for oil port A1 of bidirectional hydraulic pump 2 is all replenished by oil tank 4 through check valve D3.

[0028] Example 2

[0029] Furthermore, the one-way valve D1 adopts a hydraulically controlled one-way valve type, which controls the return oil from the piston chamber oil port A2 to the bidirectional hydraulic pump 2, and the excess oil returns to the oil tank through the one-way valve D5 (hydraulically controlled one-way valve), which can also achieve the effect of releasing back pressure.

[0030] Specifically, such as Figure 2 As shown, an integrated bidirectional hydraulic pump station for a tank-mounted vehicle stopper includes a valve block 1, a bidirectional hydraulic pump 2, a motor 3, an oil tank 4, a vehicle stopper drive cylinder 5, an overflow valve 1 W1, an overflow valve 2 W2, a check valve 1 D1, a check valve 2 D2, a check valve 3 D3, a check valve 4 D4, and a check valve 5 D5, etc.

[0031] The bidirectional hydraulic pump 2 is provided with oil port A1 and oil port B1, and the brake drive cylinder 5 is provided with piston chamber oil port A2 and piston rod chamber oil port B2; the bidirectional hydraulic pump 2 and oil tank 4 are respectively connected to valve block 1, and oil tank 4 is connected to oil port A1 through one-way valve three D3, and oil tank 4 is connected to oil port B1 through one-way valve four D4.

[0032] The motor 3 is connected to the bidirectional hydraulic pump 2. The valve block 1 is integrated with the relief valve W1, relief valve W2, check valve D1, check valve D2, and check valve D5. The valve block 1 has a left oil circuit and a right oil circuit. Check valve D1, check valve D5, and relief valve W1 are connected to the left oil circuit, and check valve D2 and relief valve W2 are connected to the right oil circuit. Check valve D1, check valve D2, and check valve D5 are all hydraulically controlled check valves. Check valve D1 and check valve D5 are controlled by the oil pressure of the right oil circuit, and check valve D2 is controlled by the oil pressure of the left oil circuit.

[0033] The left oil passage port A3 of the valve block 1 is connected to the piston chamber port A2 of the brake drive cylinder 5, and the right oil passage port B3 is connected to the piston rod chamber port B2 of the brake drive cylinder 5.

[0034] The motor 3 drives the bidirectional hydraulic pump 2 to operate in the forward or reverse direction: when the oil port A1 of the bidirectional hydraulic pump 2 outputs high-pressure oil, the output path of the high-pressure oil is the same as in Example 1.

[0035] When the high-pressure oil is output from port B1 of the bidirectional hydraulic pump 2, port A1 is the inlet. The high-pressure oil output from port B1 is limited by the relief valve W2, passes through the check valve D2 (hydraulic control check valve) to port B3, and is output to port B2 of the piston rod chamber of the brake actuator drive cylinder 5. At the same time, the high-pressure oil from port B3 controls the opening of check valves D1 and D5 (both hydraulic control check valves), unlocking the brake actuator drive cylinder 5. The return oil from the piston chamber of the brake actuator drive cylinder 5 passes through port A3, the opened check valve D1, and port A1, returning to the bidirectional hydraulic pump 2. Part of the return oil returns to the oil tank 4 through check valve D5, and the back pressure of the piston chamber is released.

[0036] Example 3

[0037] Examples 1 and 2 describe the control of a single wheel stop drive cylinder. To be applicable to applications with double wheel stops and wheel stops for trackless rubber-tired vehicles, two two-position three-way solenoid valves can be installed on valve block 1. If one of the solenoid valves is energized, its corresponding wheel stop drive cylinder is turned on, allowing operation of the two wheel stop drive cylinders separately.

[0038] Specifically, such as Figure 3As shown, an integrated bidirectional hydraulic pump station for a tank-mounted vehicle stopper includes a valve block 1, a bidirectional hydraulic pump 2, a motor 3, an oil tank 4, a vehicle stopper drive cylinder 1 5, and a vehicle stopper drive cylinder 2 6.

[0039] The bidirectional hydraulic pump 2 is provided with bidirectional oil port A1 and bidirectional oil port B1. The bidirectional hydraulic pump 2 and the oil tank 4 are respectively connected to the valve block 1. The oil tank 4 is connected to oil port A1 through one-way valve D3 and oil port B1 through one-way valve D4. The motor 3 is connected to the bidirectional hydraulic pump 2.

[0040] The valve block 1 integrates solenoid valve 7, solenoid valve 8, overflow valve W1, overflow valve W2, check valve D1, check valve D2, and check valve D5. The valve block 1 has a left oil passage and a right oil passage. Check valve D1, check valve D5, and overflow valve W1 are connected to the left oil passage, and check valve D2 and overflow valve W2 are connected to the right oil passage. Check valve D2 and check valve D5 are both hydraulically controlled check valves. Check valve D5 is controlled by the oil pressure of the right oil passage, and check valve D2 is controlled by the oil pressure of the left oil passage. Solenoid valve 7 and solenoid valve 8 are both two-position three-way solenoid valves.

[0041] The valve block 1 is provided with bidirectional oil ports A4, B4, A5, and B5. The left oil passage in the valve block 1 is connected to oil ports A4 and B4 through solenoid valve 7, and the right oil passage in the valve block 1 is connected to oil ports A5 and B5 through solenoid valve 8. The piston chamber oil port A2 of the vehicle stopper driving cylinder 5 is connected to oil port A4, and the piston rod chamber oil port B2 is connected to oil port B5. The piston chamber oil port A6 of the vehicle stopper driving cylinder 6 is connected to oil port B4, and the piston rod chamber oil port B6 is connected to oil port A5.

[0042] The specific control process is as follows:

[0043] (1) When solenoid valve 7 is energized and solenoid valve 8 is not energized, the bidirectional hydraulic pump 2 can normally drive the brake drive cylinder 5.

[0044] For example, when the bidirectional hydraulic pump 2 rotates forward, oil is discharged from port A4, the piston rod of the brake drive cylinder 5 extends, and the first brake closes; when the bidirectional hydraulic pump 2 rotates in reverse, oil is discharged from port B5, and the piston rod of the brake drive cylinder 5 retracts.

[0045] (2) When solenoid valve 7 is not energized and solenoid valve 8 is energized, the bidirectional hydraulic pump 2 can normally drive the brake drive cylinder 6.

[0046] For example, when the bidirectional hydraulic pump 2 rotates forward, oil is discharged from port B4, the brake drives the piston rod of cylinder 6 to extend, and the second brake closes; when the bidirectional hydraulic pump 2 rotates in reverse, oil is discharged from port A5, and the brake drives the piston rod of cylinder 6 to retract.

[0047] (3) When neither solenoid valve 1 7 nor solenoid valve 2 8 is energized or both are energized, the bidirectional hydraulic pump 2 cannot output pressure oil, and the two drive cylinders are locked.

[0048] This utility model relates to an integrated bidirectional hydraulic pump station for a tank-mounted vehicle stopper. It employs a controlled pressure relief method, which effectively solves the problem of additional back pressure in the piston chamber oil circuit during the retraction process of a typical bidirectional hydraulic pump drive system. This utility model eliminates the need to increase the pressure in the piston rod chamber of the cylinder to counteract the back pressure, thereby reducing power consumption, saving energy, and improving the reliability of the system.

[0049] The above description is merely a preferred embodiment of the present utility model and is not intended to limit the present utility model in any way. Although the present utility model has been disclosed above with reference to a preferred embodiment, it is not intended to limit the present utility model. Any person skilled in the art can make some modifications or alterations to the above-described technical content to create equivalent embodiments without departing from the scope of the present utility model. Any simple modifications, equivalent changes, and alterations made to the above embodiments based on the technical essence of the present utility model without departing from the scope of the present utility model shall still fall within the scope of the present utility model.

Claims

1. An integrated bidirectional hydraulic pump station for a tank-mounted vehicle stopper, comprising a valve block (1), a bidirectional hydraulic pump (2), a motor (3), an oil tank (4), a vehicle stopper drive cylinder, an overflow valve, and a check valve. The bidirectional hydraulic pump (2) and the oil tank (4) are respectively connected to the valve block (1). The oil tank (4) is connected to the oil port A1 of the bidirectional hydraulic pump (2) through a check valve three (D3). The oil tank (4) is connected to the oil port B1 of the bidirectional hydraulic pump (2) through a check valve four (D4). The motor (3) is connected to the bidirectional hydraulic pump (2). Its features are, The valve block (1) is provided with a left oil circuit and a right oil circuit. The left oil circuit is equipped with an overflow valve (W1), a check valve (D1), and a check valve (D5). The check valve (D5) is a hydraulically controlled check valve and is controlled by the oil pressure of the right oil circuit. The right oil circuit is equipped with an overflow valve (W2) and a check valve (D2). The check valve (D2) is a hydraulically controlled check valve and is controlled by the oil pressure of the left oil circuit. The oil port A1 of the bidirectional hydraulic pump (2) is connected to the piston chamber oil port of the brake drive cylinder through the left oil circuit, and the oil port B1 of the bidirectional hydraulic pump (2) is connected to the piston rod chamber oil port of the brake drive cylinder through the right oil circuit. The left oil circuit is connected to the oil tank (4) through one-way valve five (D5). One-way valve five (D5) is the pressure relief structure of the left oil circuit, used to release the additional back pressure generated in the piston chamber during the retraction of the piston rod of the piston rod driven by the bidirectional hydraulic pump (2) driving the brake cylinder.

2. The integrated bidirectional hydraulic pump station for a tank-mounted vehicle stopper according to claim 1, characterized in that, The one-way valve (D1) is a hydraulically controlled one-way valve, which is controlled by the oil pressure in the right oil circuit.

3. The integrated bidirectional hydraulic pump station for an in-tank vehicle stopper according to claim 1, characterized in that, The vehicle stopper driving cylinder includes a vehicle stopper driving cylinder one (5) and a vehicle stopper driving cylinder two (6). The left oil circuit is connected to the piston chamber oil port of the two vehicle stopper driving cylinders respectively through a solenoid valve one (7). The right oil circuit is connected to the piston rod chamber oil port of the two vehicle stopper driving cylinders respectively through a solenoid valve two (8).

4. An integrated bidirectional hydraulic pump station for an in-tank vehicle stopper according to claim 3, characterized in that, Both solenoid valve one (7) and solenoid valve two (8) are two-position three-way solenoid valves.

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