Brake hydraulic system for mine monorail crane

Abstract

The application provides a brake hydraulic system for a mine single-track crane, which realizes rapid pressure relief through a separate pressure relief circuit, the pressure relief circuit comprises a two-way cartridge valve, a stroke valve, an electromagnetic ball valve and the like, the X port of the two-way cartridge valve is connected with the oil tank in a conductive or non-conductive manner through the reversing switching of the stroke valve and the electromagnetic ball valve, when the X port is connected with the oil tank in a conductive manner, the A port and the B port of the X port of the two-way cartridge valve are also connected, and since the flow of the two-way cartridge valve is large, the single-acting oil cylinder can be rapidly pressure relieved through the two-way cartridge valve. The X port of the two-way cartridge valve is connected with the oil tank in a conductive manner through the first ball valve, and manual rapid pressure relief can be realized.

Description

Technical Field

[0001] This invention belongs to the field of monorail control technology, specifically relating to a braking hydraulic system for a mining monorail. Background Technology

[0002] Explosion-proof battery monorails are widely used in auxiliary transportation in mines due to their clean energy and simple structure. The explosion-proof battery monorail controls the clamping of the clamping cylinder, the braking of the braking cylinder, and the lifting action of the lifting beam through a hydraulic system. When the monorail needs to brake urgently during operation, the oil in the braking cylinder needs to flow back to the oil tank quickly to achieve rapid pressure relief.

[0003] Existing braking circuits use a method of de-energizing the brake solenoid valve to release pressure in the hydraulic cylinder for braking. This typically involves two brake directional valves connected in parallel or series for oil supply or pressure release. This method prevents the valve core of one valve from becoming stuck when the solenoid valve is de-energized, thus avoiding the problem of insufficient pressure release for braking. However, both methods still share the same oil supply line, resulting in slow pressure release and a high failure rate. Alternatively, there are hydraulic cylinders with quick-release valves that can release pressure internally. However, these cylinders are expensive, have unstable performance, and require significant maintenance. Summary of the Invention

[0004] The purpose of this invention is to provide a braking hydraulic system for mine monorail cranes, which solves the problem of slow pressure relief speed in the braking circuit of existing hydraulic systems.

[0005] This invention provides a braking hydraulic system for a mining monorail crane, including a braking oil circuit that is connected to the oil ports of multiple single-acting cylinders. An electromagnetic directional valve is connected to the braking oil circuit, and the electromagnetic directional valve is used to control the oil supply or pressure relief of the single-acting cylinders.

[0006] The brake oil circuit is provided with a first branch oil circuit, which is connected to port A of the two-way cartridge valve, and port B of the two-way cartridge valve is connected to the oil tank.

[0007] The first bypass on the first branch oil line is connected to the X port of the two-way cartridge valve, and a solenoid ball valve and a stroke valve are connected on the first bypass.

[0008] The X port of the two-way cartridge valve is connected to the oil tank through a second bypass, and a first ball valve is provided on the second bypass.

[0009] When the solenoid directional valve is energized, the solenoid ball valve is energized, and the stroke valve is not activated, hydraulic oil passes through the solenoid ball valve and the stroke valve to fill the X port of the two-way cartridge valve so that the A port and B port of the two-way cartridge valve are not connected to maintain pressure.

[0010] During normal braking, the electromagnetic reversing valve is de-energized first, followed by the electromagnetic ball valve, and the single-acting cylinder is connected to the oil tank through the electromagnetic reversing valve to release pressure.

[0011] When the emergency stop button is pressed or the encoder speed exceeds the set value, the electromagnetic reversing valve is de-energized, the electromagnetic ball valve is de-energized, and the stroke valve does not operate. The X port of the two-way cartridge valve is connected to the oil tank through the stroke valve and the electromagnetic ball valve. After the connection is made, the A port and B port of the two-way cartridge valve are connected to quickly release pressure.

[0012] When the mechanical triggers the reversing of the stroke valve, the X port of the two-way cartridge valve is connected to the oil tank through the stroke valve. After the connection is made, the A port and B port of the two-way cartridge valve are connected to quickly release pressure.

[0013] When the first ball valve is opened, the X port of the two-way cartridge valve is directly connected to the oil tank. After the connection is established, the A and B ports of the two-way cartridge valve are connected to quickly release pressure.

[0014] In one possible embodiment, a second branch oil circuit is provided on the main oil circuit of the hydraulic system, and a pilot relief valve is connected to the second branch oil circuit. A third bypass is connected to the second bypass, and the third bypass is connected to the X port of the pilot relief valve. The first ball valve simultaneously controls the connection between the X port of the pilot relief valve and the oil tank.

[0015] In one possible embodiment, both the third bypass and the second bypass are provided with a one-way valve.

[0016] In one possible embodiment, a second ball valve is provided on the brake oil line at the oil port of the single-acting cylinder, and a third branch oil line is provided on the pipeline between the second ball valve and the oil port of the single-acting cylinder, the third branch oil line being connected to the outlet of the manual pump.

[0017] In one possible embodiment, the reversing valve is a two-position three-way reversing solenoid valve.

[0018] In one possible embodiment, the stroke valve is a two-position three-way mechanical directional valve.

[0019] In one possible embodiment, a throttle valve is connected to the line between the directional valve and the single-acting cylinder in the brake oil circuit.

[0020] In one possible embodiment, a damping valve is provided on the pipeline between port A of the first bypass two-way cartridge valve and the solenoid ball valve.

[0021] The brake hydraulic system provided by this invention achieves rapid pressure relief by setting up a separate pressure relief circuit. This pressure relief circuit includes a two-way cartridge valve, a stroke valve, and a solenoid ball valve. The X port of the two-way cartridge valve is connected to or disconnected from the oil tank by switching the stroke valve and the solenoid ball valve. When the X port is connected to the oil tank, ports A and B of the X port of the two-way cartridge valve are also connected. Due to the large flow rate of the two-way cartridge valve, a single-acting cylinder can be rapidly depressurized through the two-way cartridge valve. This invention also allows for manual rapid pressure relief by separately controlling the connection between the X port of the two-way cartridge valve and the oil tank using a first ball valve.

[0022] Furthermore, because the manual pressure relief valve is purely mechanically controlled, it is inconvenient to install explosion-proof sensors to detect its position. When manual braking is applied, the system detects a drop in braking pressure and controls the motor to start continuing to replenish pressure, which prolongs the braking time to some extent. A pilot relief valve is installed at the oil pump outlet, and the external control port of the relief valve is connected to the oil tank through this manual pressure relief ball valve to unload the oil pump. An oil circuit interlock prevents the oil pump from continuing to replenish pressure after manual pressure relief braking. Attached Figure Description

[0023] To more clearly illustrate the technical solutions in the embodiments of the present invention 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 some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0024] Figure 1 This is a rapid pressure relief hydraulic system for monorail cranes provided in one embodiment of the present invention.

[0025] In the diagram: 1. Oil pump; 2. Motor; 3. Manual pump; 4. Pilot relief valve; 5. Three-position four-way directional valve; 6. Third check valve; 7. Accumulator; 8.1. Solenoid directional valve; 8.2. Solenoid ball valve; 9. Stroke valve; 10. Throttle valve; 11. Two-way cartridge valve; 12.1. First check valve; 12.2. Second check valve; 13.1. Second ball valve; 13.2. First ball valve; 14. Single-acting cylinder; 15. Damping valve. Detailed Implementation

[0026] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are some embodiments of the present invention, but not all embodiments. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without creative effort are within the scope of protection of the present invention.

[0027] In the description of this specification, the terms "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with an embodiment or example that are included in at least one embodiment or example of the present invention. In this invention, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0028] refer to Figure 1 This embodiment provides a braking hydraulic system for a monorail crane, which includes an oil tank and an oil pump 1. The oil pump 1 is driven by a motor 2, and its outlet is connected to the main oil circuit. A three-position four-way directional valve 5 is installed on the main oil circuit. Optionally, the three-position four-way directional valve 5 is of type H. The main oil circuit switches between the lifting circuit and the braking circuit through the three-position four-way directional valve 5. In this embodiment, the lifting circuit is not modified, so it is not shown in this application.

[0029] Optionally, a third check valve 6 is provided on the brake oil line connected to the three-position four-way directional valve 5, and an accumulator 7 is also connected to the brake oil line via a branch.

[0030] In some embodiments, a solenoid directional valve 8.1 is connected to the brake fluid circuit. This solenoid directional valve 8.1 is used to control the oil supply or pressure relief of the single-acting hydraulic cylinder. Optionally, the solenoid directional valve 8.1 can be a two-position two-way solenoid directional valve or a two-position four-way solenoid directional valve. When the solenoid directional valve 8.1 is energized, it supplies oil to the single-acting cylinder 14. When the solenoid directional valve 8.1 is de-energized, the single-acting cylinder drains oil from the T port of the solenoid directional valve 8.1.

[0031] In some possible embodiments, a throttle valve 10 is provided in the brake oil circuit between the solenoid directional valve 8.1 and the single-acting cylinder 14. The throttle valve 10 regulates the oil pressure flow into the single-acting cylinder 14, thereby controlling the movement speed of the braking force of the single-acting cylinder.

[0032] In some possible implementations, a second ball valve 13.1 is provided on the brake oil line at the oil port of the single-acting cylinder 14, and a third branch oil line is provided on the pipeline between the second ball valve 13.1 and the oil port of the single-acting cylinder 14. The third branch oil line is connected to the outlet of the manual pump 3. The manual pump can be used to manually pressurize the single-acting cylinder 14 when the monorail malfunctions.

[0033] In some embodiments, a first oil passage is provided on the pipeline between the throttle valve 10 and the single-acting cylinder 14. This first oil passage is connected to port A of the two-way cartridge valve 11, and port B of the two-way cartridge valve 11 is connected to the oil tank. By controlling the inlet pressure of its X port, the valve core of the two-way cartridge valve 11 can achieve the opening and closing of ports A and B under the action of spring force.

[0034] In this embodiment, a first bypass is provided on the first branch oil line. The first bypass is connected to the X port of the two-way cartridge valve 11. A solenoid ball valve 8.2 and a stroke valve 9 are also connected to the first bypass. The conduction of the A port and the B port of the two-way cartridge valve 11 is realized by the switching of the solenoid ball valve 8.2 and the stroke valve 9.

[0035] When the hydraulic cylinder 14 is normally supplied with oil, the solenoid directional valve 8.1 is energized, the solenoid ball valve 8.2 is energized, and the stroke valve 9 is not activated. Hydraulic oil flows through the solenoid ball valve 8.2 and the stroke valve 9 to fill the X port of the two-way cartridge valve 11, thus preventing the A and B ports of the two-way cartridge valve from connecting and maintaining pressure. Specifically, the A and P ports of the solenoid directional valve 8.1, the stroke valve 9, and the solenoid ball valve 8.2 are all open. At this time, pressure is established at the X port of the two-way cartridge valve 11, blocking its A and B ports, and the oil in the brake circuit enters the single-acting cylinder 14.

[0036] During normal braking of the monorail crane, the solenoid directional valve 8.1 is de-energized first, allowing the hydraulic fluid in the single-acting cylinder 14 to be depressurized through the connection between port A and port T of the solenoid directional valve 8.1, and the fluid flows back to the oil tank. Since the solenoid ball valve 8.2 is initially energized, ports A and B of the two-way cartridge valve 11 are not connected, and no pressure is released in this circuit. When the monorail crane has stopped, the solenoid ball valve 8.2 is de-energized again to drain the fluid in the first bypass back to the oil tank, thereby reducing energy consumption.

[0037] When the emergency stop button is pressed or the encoder speed exceeds the set value, the solenoid directional valve 8.1 and solenoid ball valve 8.2 are de-energized, and the stroke valve 9 does not operate. The X port of the two-way cartridge valve 11 is connected to the oil tank via the stroke valve 9 and the solenoid ball valve 8.2. After connection, the A and B ports of the two-way cartridge valve 11 are connected for rapid pressure relief. Specifically, the A and T ports of the solenoid directional valve 8.1 and the solenoid ball valve 8.2 are connected, as are the A and P ports of the stroke valve 9. Because the throttle valve 10 and the solenoid directional valve 8.1 in the brake oil circuit have small diameters and slow oil discharge speeds, while the two-way cartridge valve 11 has a large flow rate and good sealing effect, rapid pressure relief can be achieved by controlling the rapid connection of its A and B ports.

[0038] A centrifugal speed limiter is installed on the monorail crane. When the speed exceeds the set value, the centrifugal speed limiter will trigger the switch of the stroke valve 9. That is, when the mechanically triggered stroke valve 9 switches, the X port of the two-way cartridge valve 11 is connected to the oil tank through the stroke valve 9. After the connection is made, the A and B ports of the two-way cartridge valve are connected to achieve rapid pressure relief. Specifically, after the stroke valve 9 switches, its A and T ports are connected, and the X port of the two-way cartridge valve 11 is connected to the oil tank through the A and T ports of the stroke valve 9 to achieve oil discharge.

[0039] In some possible embodiments, the X port of the two-way cartridge valve 11 is connected to the oil tank via a second bypass, and a first ball valve 13.2 is provided on the second bypass. When the first ball valve 13.2 is open, the X port of the two-way cartridge valve is directly connected to the oil tank. After connection, the A and B ports of the two-way cartridge valve are connected for rapid pressure relief. The first ball valve 13.2 is used for manual rapid pressure relief.

[0040] In this embodiment, a second branch oil circuit is provided on the main oil circuit of the hydraulic system. A pilot relief valve 4 is connected to the second branch oil circuit. A third bypass is connected to the second bypass, and the third bypass is connected to the X port of the pilot relief valve 4. The first ball valve 13.2 simultaneously controls the connection between the X port of the pilot relief valve and the oil tank. Because the manual pressure relief valve is purely mechanically controlled, it is inconvenient to install an explosion-proof sensor to detect its position. When the brake is manually applied, the system detects a drop in braking pressure and controls the motor to start and continue to replenish pressure, which prolongs the braking time to some extent. By configuring a pilot relief valve 4 at the outlet of the oil pump 1, the external control port of the relief valve is connected to the oil tank through the manual pressure relief ball valve to achieve oil pump unloading. Through oil circuit interlocking, it is prevented that the oil pump will continue to replenish pressure after manual pressure relief braking.

[0041] In some possible embodiments, both the second and third bypasses are equipped with check valves, with the check valve on the second bypass being a first check valve 12.1 and the check valve on the third bypass being a second check valve 12.2. Cross-flow is prevented by providing check valves separately.

[0042] In some possible embodiments, a damping valve 15 is provided on the pipeline between port A of the two-way cartridge valve 11 and the solenoid ball valve 8.2 on the first bypass, and the flow rate on the first bypass is adjusted by the damping valve 15.

[0043] In some implementations, the stroke valve is a two-position three-way mechanical directional valve, such as a two-position three-way roller directional valve.

[0044] For example, when the emergency stop button is pressed or the first ball valve is manually opened, the hydraulic system achieves rapid pressure relief. When the encoder speed exceeds the set value or the centrifugal speed limiter mechanically triggers the stroke valve to switch direction, the hydraulic system automatically achieves rapid pressure relief. By combining multiple rapid pressure relief methods, the monorail can achieve rapid pressure relief under various working conditions, thereby improving braking reliability and thus enhancing the safety performance of the monorail.

[0045] It should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and are not intended to limit them. Although the invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or modifications can be made to some or all of the technical solutions, or equivalent substitutions can be made to some or all of the technical features. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. A braking hydraulic system for a mining monorail hoist, comprising a braking oil circuit, characterized in that, The brake oil circuit is connected to the oil ports of multiple single-acting cylinders, and an electromagnetic reversing valve is connected to the brake oil circuit. The electromagnetic reversing valve is used to control the oil supply or pressure relief of the single-acting cylinders. The brake oil circuit is provided with a first branch oil circuit, which is connected to port A of the two-way cartridge valve, and port B of the two-way cartridge valve is connected to the oil tank. The first bypass on the first branch oil line is connected to the X port of the two-way cartridge valve, and a solenoid ball valve and a stroke valve are connected on the first bypass. The X port of the two-way cartridge valve is connected to the oil tank through a second bypass, and a first ball valve is provided on the second bypass. When the solenoid directional valve is energized, the solenoid ball valve is energized, and the stroke valve is not activated, hydraulic oil passes through the solenoid ball valve and the stroke valve to fill the X port of the two-way cartridge valve so that the A port and B port of the two-way cartridge valve are not connected to maintain pressure. During normal braking, the electromagnetic reversing valve is de-energized first, followed by the electromagnetic ball valve, and the single-acting cylinder is connected to the oil tank through the electromagnetic reversing valve to release pressure. When the emergency stop button is pressed or the encoder speed exceeds the set value, the electromagnetic reversing valve is de-energized, the electromagnetic ball valve is de-energized, and the stroke valve does not operate. The X port of the two-way cartridge valve is connected to the oil tank through the stroke valve and the electromagnetic ball valve. After the connection is made, the A port and B port of the two-way cartridge valve are connected to quickly release pressure. When the mechanical triggers the reversing of the stroke valve, the X port of the two-way cartridge valve is connected to the oil tank through the stroke valve. After the connection is made, the A port and B port of the two-way cartridge valve are connected to quickly release pressure. When the first ball valve is opened, the X port of the two-way cartridge valve is directly connected to the oil tank. After the connection is established, the A and B ports of the two-way cartridge valve are connected to quickly release pressure.

2. The braking hydraulic system for a mine monorail crane according to claim 1, characterized in that, A second branch oil circuit is provided on the main oil circuit of the hydraulic system. A pilot relief valve is connected to the second branch oil circuit. A third bypass is connected to the second bypass. The third bypass is connected to the X port of the pilot relief valve. The first ball valve simultaneously controls the connection between the X port of the pilot relief valve and the oil tank.

3. The braking hydraulic system for a mine monorail crane according to claim 2, characterized in that, Both the third bypass and the second bypass are equipped with one-way valves.

4. The braking hydraulic system for a mine monorail crane according to claim 1, characterized in that, A second ball valve is provided on the brake oil line at the oil port of the single-acting cylinder, and a third oil line is provided on the pipeline between the second ball valve and the oil port of the single-acting cylinder, and the third oil line is connected to the outlet of the manual pump.

5. The braking hydraulic system for a mine monorail crane according to claim 1, characterized in that, The reversing valve is a two-position three-way reversing solenoid valve.

6. The braking hydraulic system for a mine monorail crane according to claim 1, characterized in that, The stroke valve is a two-position three-way mechanical directional valve.

7. The braking hydraulic system for a mine monorail crane according to claim 1, characterized in that, A throttle valve is connected to the pipeline between the directional valve and the single-acting cylinder in the brake oil circuit.

8. The braking hydraulic system for a mine monorail crane according to claim 1, characterized in that, A damping valve is installed on the pipeline between port A of the two-way cartridge valve on the first bypass and the solenoid ball valve.

Images