A hydraulic system of a large displacement hydraulic reciprocating slurry delivery pump

Abstract

The application discloses a hydraulic system of a large-displacement hydraulic reciprocating slurry conveying pump, which comprises a first oil cylinder, a second oil cylinder, a reversing valve group, a total oil inlet pipe and a total oil return pipe; a rodless cavity of the first oil cylinder is provided with a first oil port, a rodless cavity of the second oil cylinder is provided with a second oil port, and a rod cavity of the first oil cylinder is connected with a rod cavity of the second oil cylinder through a connecting pipe; the reversing valve group comprises a first cartridge valve, a second cartridge valve, a third cartridge valve, a fourth cartridge valve and a hydraulic control module, and C ports of the first cartridge valve, the second cartridge valve, the third cartridge valve and the fourth cartridge valve are controlled by the hydraulic control module; four cartridge valves are used to replace the reversing valve to realize large-flow transmission of hydraulic oil, and the opening and closing of the four cartridge valves are controlled by cooperation of a first control valve and a second control valve, so that the reversing transmission of the hydraulic oil is realized, and the second control valve controls the reversing through a first reversing cartridge valve and a second reversing cartridge valve according to the working conditions of the two oil cylinders, and the application is more intelligent.

Description

Technical Field

[0001] This invention relates to the field of hydraulic system technology, specifically to a hydraulic system for an ultra-large displacement hydraulic reciprocating slurry conveying pump. Background Technology

[0002] In fields such as construction engineering, mining filling, and fluid transportation, hydraulically driven reciprocating pumps are core equipment. Hydraulic cylinders, as actuators that convert hydraulic energy into mechanical energy, are widely used in reciprocating transfer pumps. Currently, reciprocating transfer pumps use dual cylinders that automatically switch directions via a reversing valve assembly to achieve alternating operation of the two cylinders. However, the currently used reversing valve assembly suffers from flow limitations due to pipeline constraints, resulting in slow reversing speeds. Summary of the Invention

[0003] The purpose of this invention is to address the shortcomings of existing technologies by providing a hydraulic system for an ultra-large displacement hydraulic reciprocating slurry conveying pump.

[0004] The technical solution of the present invention to solve the above problems is: a hydraulic system for a large displacement hydraulic reciprocating slurry conveying pump, including a first oil cylinder, a second oil cylinder, a reversing valve group, a main oil inlet pipe, and a main oil return pipe;

[0005] The rodless chamber of the first hydraulic cylinder is provided with a first oil port, the rodless chamber of the second hydraulic cylinder is provided with a second oil port, and the rod chamber of the first hydraulic cylinder and the rod chamber of the second hydraulic cylinder are connected by a connecting pipe. The directional valve assembly includes a first cartridge valve, a second cartridge valve, a third cartridge valve, a fourth cartridge valve, and a hydraulic control module. Port A of the first cartridge valve is connected to Port A of the second cartridge valve via a first pipe. Port B of the first cartridge valve is connected to the main return oil pipe. Port B of the second cartridge valve is connected to Port B of the third cartridge valve via a second pipe. Port A of the third cartridge valve is connected to Port A of the fourth cartridge valve via a third pipe. Port B of the fourth cartridge valve is connected to the main return oil pipe. The main inlet oil pipe is connected to the second pipe. The first pipe is connected to the first oil port via a first large displacement pipe. The third pipe is connected to the second oil port via a second large displacement pipe. The C ports of the first, second, third, and fourth cartridge valves are controlled by a hydraulic control module.

[0006] Furthermore, the first and second largest displacement pipelines are composed of multiple branch pipelines, which are connected in parallel.

[0007] Furthermore, the hydraulic control module includes a first control valve, a second control valve, a first reversing cartridge valve, and a second reversing cartridge valve. The first control valve is a pilot-operated manual reversing valve, and the second control valve is a three-position four-way reversing valve. The second control valve is controlled by the first reversing cartridge valve and the second reversing cartridge valve for reversing.

[0008] The P port of the first control valve is connected to the main oil inlet pipe through the first hydraulic control pipeline. The A port of the first control valve, the A port of the second control valve, the C port of the first cartridge valve, and the C port of the third cartridge valve are connected via a second hydraulic control pipeline. The B port of the first control valve, the B port of the second control valve, the C port of the second cartridge valve, and the C port of the fourth cartridge valve are connected via a third hydraulic control pipeline. The T-ports of the first control valve and the second control valve are respectively connected to the main return oil pipe through the fourth hydraulic control pipe; The first hydraulic cylinder has a first hydraulic control port in front of the reversing point and a second hydraulic control port behind it. The first reversing cartridge valve has port C connected to the first hydraulic control port through a pipe, port A connected to the second hydraulic control port through a pipe, port B1 connected to the first hydraulic control port of the second control valve through a fifth hydraulic control pipe, and port B2 connected to the first large displacement pipe through a pipe and a check valve. The second hydraulic cylinder has a third hydraulic control port in front of the reversing point and a fourth hydraulic control port behind it. The second reversing cartridge valve has port C connected to the third hydraulic control port through a pipe, port A connected to the fourth hydraulic control port through a pipe, port B1 connected to the second hydraulic control port of the second control valve through a sixth hydraulic control pipe, and port B2 connected to the second large displacement pipe through a pipe and a check valve.

[0009] Furthermore, one end of the main oil inlet pipe is connected to an oil inlet assembly, which includes at least one oil pump. One end of the oil pump is connected to the oil tank through a pipe, and the other end is connected to the main oil inlet pipe through an oil inlet pipe. A one-way valve is provided on the oil inlet pipe, and the oil inlet pipe is connected to the main return oil pipe through an overflow pipe. An overflow valve is provided on the overflow pipe.

[0010] Furthermore, oil enters through the main inlet pipe, then through the first hydraulic control pipeline, and through the P port of the second control valve. It then enters the third hydraulic control pipeline through port B. The second and fourth cartridge valves are closed. Therefore, the hydraulic oil in the main inlet pipe enters the second port through the second, third, and second large-displacement pipelines. When the second cylinder moves forward until the piston reaches the front reversing point, the hydraulic pressure at port A of the second reversing cartridge valve is greater than at port C. Oil is discharged from port B1 into the second hydraulic control port of the second control valve, and the second control valve reverses. After the second control valve reverses, oil enters through the main inlet pipe, then through the first hydraulic control pipeline, and through the P port of the second control valve. It then enters the second hydraulic control pipeline through port A. The first and third cartridge valves are closed. Therefore, the hydraulic oil in the main inlet pipe enters the first port through the second, first, and first large-displacement pipelines. When the first cylinder moves forward until the piston reaches the front reversing point, the hydraulic pressure at port A of the first reversing cartridge valve is greater than at port C. Oil is discharged from port B1 into the first hydraulic control port of the second control valve, and the second control valve reverses again.

[0011] The present invention has the following beneficial effects: This invention provides a hydraulic system for an ultra-large displacement hydraulic reciprocating slurry conveying pump. It achieves high-flow transmission of hydraulic oil by replacing directional valves with four cartridge valves. The opening and closing of the four cartridge valves are controlled by the cooperation of a first control valve and a second control valve to achieve the reversing transmission of hydraulic oil. The second control valve controls the reversing according to the working conditions of the two cylinders through the first and second reversing cartridge valves, making it more intelligent. Attached Figure Description

[0012] Figure 1 This is a schematic diagram of the structure of the present invention; In the diagram: 1-First oil cylinder, 2-Second oil cylinder, 3-Main oil inlet pipe, 4-Main oil return pipe, 5-First oil port, 6-Second oil port, 7-Connecting pipe, 8-Oil pump; 201-First cartridge valve, 202-Second cartridge valve, 203-Third cartridge valve, 204-Fourth cartridge valve, 205-First control valve, 206-Second control valve, 207-First reversing cartridge valve, 208-Second reversing cartridge valve, 209-First pipeline, 210-Second pipeline, 211-Third pipeline, 212-First large displacement pipeline, 213-Second large displacement pipeline; 301 - First hydraulic control pipeline, 302 - Second hydraulic control pipeline, 303 - Third hydraulic control pipeline, 304 - Fourth hydraulic control pipeline, 305 - Fifth hydraulic control pipeline, 306 - Sixth hydraulic control pipeline. Detailed Implementation

[0013] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; 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; and they can refer to the internal connection of two components. Those skilled in the art will understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0014] As shown in the figure, a hydraulic system for an ultra-large displacement hydraulic reciprocating slurry conveying pump includes a first cylinder 1, a second cylinder 2, a reversing valve group, a main oil inlet pipe 3, an oil inlet assembly, and a main oil return pipe 4. The rodless chamber of the first cylinder 1 is provided with a first oil port 5, the rodless chamber of the second cylinder 2 is provided with a second oil port 6, and the rod chamber of the first cylinder 1 and the rod chamber of the second cylinder 2 are connected by a connecting pipe 7. The directional valve assembly includes a first cartridge valve 201, a second cartridge valve 202, a third cartridge valve 203, a fourth cartridge valve 204, and a hydraulic control module. Port A of the first cartridge valve 201 and port A of the second cartridge valve 202 are connected through a first pipe 209. Port B of the first cartridge valve 201 is connected to the main return oil pipe 4. Port B of the second cartridge valve 202 and port B of the third cartridge valve 203 are connected through a second pipe 210. Port A of the third cartridge valve 203 and port A of the fourth cartridge valve 204 are connected through a third pipe 211. Port B of the fourth cartridge valve 204 is connected to the main return oil pipe 4. One end of the main inlet pipe 3 is connected to the inlet assembly, and the other end is connected to the second pipe 210. The first pipe 209 is connected to the first oil port 5 through a first large displacement pipe 212, and the third pipe 211 is connected to the second oil port 6 through a second large displacement pipe 213. The first large displacement pipeline 212 and the second large displacement pipeline 213 are composed of multiple branch pipelines, which are connected in parallel.

[0015] The C ports of the first cartridge valve 201, the second cartridge valve 202, the third cartridge valve 203, and the fourth cartridge valve 204 are connected to a hydraulic control module. The hydraulic control module includes a first control valve 205, a second control valve 206, a first directional cartridge valve 207, and a second directional cartridge valve 208. The first control valve 205 is a pilot-operated manual directional valve, and the second control valve 206 is a three-position four-way directional valve. The second control valve 206 is controlled to switch direction by the first directional cartridge valve 207 and the second directional cartridge valve 208.

[0016] The P port of the first control valve 205 is connected to the main oil inlet pipe 3 through the first hydraulic control pipeline 301. The A port of the first control valve 205, the A port of the second control valve 206, the C port of the first cartridge valve 201, and the C port of the third cartridge valve 203 are connected through the second hydraulic control pipeline 302. The B port of the first control valve 205, the B port of the second control valve 206, the C port of the second cartridge valve 202, and the C port of the fourth cartridge valve 204 are connected via the third hydraulic control pipeline 303. The T-port of the first control valve 205 and the T-port of the second control valve 206 are respectively connected to the main return oil pipe 4 through the fourth hydraulic control pipe 304; The first hydraulic cylinder 1 has a first hydraulic control port in front of the reversing point and a second hydraulic control port behind it. The first reversing cartridge valve 207C port is connected to the first hydraulic control port through a pipe, port A is connected to the second hydraulic control port through a pipe, port B1 is connected to the first hydraulic control port of the second control valve 206 through the fifth hydraulic control pipe 305, and port B2 is connected to the first large displacement pipe 212 through a pipe and a check valve. The second hydraulic cylinder 2 has a third hydraulic control port in front of the reversing point and a fourth hydraulic control port behind it. The second reversing cartridge valve 208C port is connected to the third hydraulic control port through a pipe, port A is connected to the fourth hydraulic control port through a pipe, port B1 is connected to the second hydraulic control port of the second control valve 206 through the sixth hydraulic control pipe 306, and port B2 is connected to the second large displacement pipe 213 through a pipe and a check valve.

[0017] Oil enters through the main inlet pipe 3, then through the first hydraulic control pipe 301, and the P port of the second control valve 206. It then enters the third hydraulic control pipe 303 through the B port. The second cartridge valve 202 and the fourth cartridge valve 204 are closed. Therefore, the hydraulic oil in the main inlet pipe 3 enters the second port 6 through the second pipe 210, the third pipe 211, and the second large displacement pipe 213. When the second cylinder 2 moves forward until the piston reaches the front reversing point, the hydraulic pressure at port A of the second reversing cartridge valve 208 is greater than that at port C. Oil is discharged from port B1 into the second hydraulic control port of the second control valve 206, causing the second control valve 206 to reverse. The second control valve 20... After the reversal, oil enters through the main inlet pipe 3, then through the first hydraulic control pipe 301, and the P port of the second control valve 206. It then enters the second hydraulic control pipe 302 through the A port. The first cartridge valve 201 and the third cartridge valve 203 are closed. Therefore, the hydraulic oil in the main inlet pipe 3 enters the first oil port 5 through the second pipe 210, the first pipe 209, and the first large displacement pipe 212. When the first cylinder 1 moves forward until the piston reaches the front reversal point, the hydraulic pressure at the A port of the first reversal cartridge valve 207 is greater than that at the C port. Oil is discharged from the B1 port into the first hydraulic control port of the second control valve 206, and the second control valve 206 reverses again.

[0018] The oil inlet assembly includes at least one oil pump 8. One end of the oil pump 8 is connected to the oil tank through a pipeline, and the other end is connected to the main oil inlet pipe 3 through an oil inlet pipeline. A one-way valve is provided on the oil inlet pipeline. The oil inlet pipeline is connected to the main return oil pipe 4 through an overflow pipe. An overflow valve is provided on the overflow pipe.

[0019] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention in any other way. Any person skilled in the art may make changes or modifications to the above-disclosed technical content to create equivalent embodiments for application in other fields. However, any simple modifications, equivalent changes, and modifications made to the above embodiments based on the technical essence of the present invention without departing from the scope of the present invention shall still fall within the protection scope of the present invention.

Claims

1. A hydraulic system for an ultra-large displacement hydraulic reciprocating slurry conveying pump, characterized in that: Includes a first oil cylinder (1), a second oil cylinder (2), a reversing valve group, a main oil inlet pipe (3), and a main oil return pipe (4); The rodless chamber of the first cylinder (1) is provided with a first oil port (5), the rodless chamber of the second cylinder (2) is provided with a second oil port (6), and the rod chamber of the first cylinder (1) and the rod chamber of the second cylinder (2) are connected by a connecting pipe (7). The directional valve assembly includes a first cartridge valve (201), a second cartridge valve (202), a third cartridge valve (203), a fourth cartridge valve (204), and a hydraulic control module. Port A of the first cartridge valve (201) is connected to Port A of the second cartridge valve (202) through a first pipe (209). Port B of the first cartridge valve (201) is connected to the main return oil pipe (4). Port B of the second cartridge valve (202) is connected to Port B of the third cartridge valve (203) through a second pipe (210). The A port of the third cartridge valve (203) is connected to the A port of the fourth cartridge valve (204) through the third pipe (211), and the B port of the fourth cartridge valve (204) is connected to the main return oil pipe (4); the main inlet oil pipe (3) is connected to the second pipe (210), the first pipe (209) is connected to the first oil port (5) through the first large displacement pipe (212), and the third pipe (211) is connected to the second oil port (6) through the second large displacement pipe (213); The C ports of the first cartridge valve (201), the second cartridge valve (202), the third cartridge valve (203), and the fourth cartridge valve (204) are controlled by the hydraulic control module.

2. The hydraulic system of a high-displacement hydraulic reciprocating slurry conveying pump as described in claim 1, characterized in that: The first large displacement pipeline (212) and the second large displacement pipeline (213) are composed of multiple branch pipelines, which are connected in parallel.

3. The hydraulic system of a high-displacement hydraulic reciprocating slurry conveying pump as described in claim 1, characterized in that: The hydraulic control module includes a first control valve (205), a second control valve (206), a first reversing cartridge valve (207), and a second reversing cartridge valve (208). The first control valve (205) is a pilot-operated manual reversing valve, and the second control valve (206) is a three-position four-way reversing valve. The second control valve (206) is controlled by the first reversing cartridge valve (207) and the second reversing cartridge valve (208) for reversing. The P port of the first control valve (205) is connected to the main oil inlet pipe (3) of the first hydraulic control pipeline (301). The A port of the first control valve (205), the A port of the second control valve (206), the C port of the first cartridge valve (201), and the C port of the third cartridge valve (203) are connected through the second hydraulic control pipeline (302). The B port of the first control valve (205), the B port of the second control valve (206), the C port of the second cartridge valve (202), and the C port of the fourth cartridge valve (204) are connected through the third hydraulic control pipe (303). The T port of the first control valve (205) and the T port of the second control valve (206) are respectively connected to the main return oil pipe (4) through the fourth hydraulic control pipe (304); The first cylinder (1) has a first hydraulic control port in front of the reversing point and a second hydraulic control port behind it. The first reversing cartridge valve (207) has port C connected to the first hydraulic control port through a pipe, port A connected to the second hydraulic control port through a pipe, port B1 connected to the first hydraulic control port of the second control valve (206) through the fifth hydraulic control pipe (305), and port B2 connected to the first large displacement pipe (212) through a pipe and a check valve. The second cylinder (2) has a third hydraulic control port in front of the reversing point and a fourth hydraulic control port behind it. The second reversing cartridge valve (208) has port C connected to the third hydraulic control port through a pipe, port A connected to the fourth hydraulic control port through a pipe, port B1 connected to the second hydraulic control port of the second control valve (206) through the sixth hydraulic control pipe (306), and port B2 connected to the second large displacement pipe (213) through a pipe and a check valve.

4. The hydraulic system of a high-displacement hydraulic reciprocating slurry conveying pump as described in claim 1, characterized in that: One end of the main oil inlet pipe (3) is connected to the oil inlet assembly, which includes at least one oil pump (8). One end of the oil pump (8) is connected to the oil tank through a pipe, and the other end is connected to the main oil inlet pipe (3) through an oil inlet pipe. A one-way valve is provided on the oil inlet pipe, and the oil inlet pipe is connected to the main return oil pipe (4) through an overflow pipe. An overflow valve is provided on the overflow pipe.

5. The hydraulic system of a high-displacement hydraulic reciprocating slurry conveying pump as described in claim 1, characterized in that: Oil enters through the main inlet pipe (3), then through the first hydraulic control pipe (301), and the P port of the second control valve (206). It then enters the third hydraulic control pipe (303) through the B port. The second cartridge valve (202) and the fourth cartridge valve (204) are closed. Therefore, the hydraulic oil in the main inlet pipe (3) enters the second port (6) through the second pipe (210), the third pipe (211), and the second large displacement pipe (213). The second cylinder (2) moves forward until the piston reaches the front reversing point. At this point, the hydraulic pressure at port A of the second reversing cartridge valve (208) is greater than that at port C. Oil is discharged from port B1 into the second hydraulic control port of the second control valve (206), and the second control valve (206) reverses direction. The second control valve (206) (202)... 6) After the reversal, oil enters through the main oil inlet pipe (3), through the first hydraulic control pipe (301), through the P port of the second control valve (206), and enters the second hydraulic control pipe (302) through the A port. The first cartridge valve (201) and the third cartridge valve (203) are closed. Therefore, the hydraulic oil in the main oil inlet pipe (3) enters the first oil port (5) through the second pipe (210), the first pipe (209), and the first large displacement pipe (212). When the first cylinder (1) moves forward until the piston moves to the front reversal point, the hydraulic pressure at the A port of the first reversal cartridge valve (207) is greater than that at the C port. Oil is discharged from the B1 port into the first hydraulic control port of the second control valve (206). The second control valve (206) reverses again.

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