CN218817297U

CN218817297U - Hydraulic system of high-power mobile emergency drainage equipment

Info

Publication number: CN218817297U
Application number: CN202223383810.9U
Authority: CN
Inventors: 张建朋; 胡景清; 陈时妹; 杨畅; 于百业
Original assignee: Xuzhou Handler Special Vehicle Co Ltd
Current assignee: Xuzhou Handler Special Vehicle Co Ltd
Priority date: 2022-12-16
Filing date: 2022-12-16
Publication date: 2023-04-07
Anticipated expiration: 2032-12-16

Abstract

The utility model provides a hydraulic system is equipped to high-power portable emergent drainage, including installing hydraulic tank, first variable pump, second variable pump, confluence valve, solenoid electric valves, first hydraulic motor, second hydraulic motor, first water pump, second water pump, radiator on the transport vechicle, hydraulic tank's exit end is respectively through the oil pipe intercommunication first variable pump the entrance point of second variable pump, the exit end of first variable pump, second variable pump passes through each entrance point that oil pipe corresponds intercommunication confluence valve, the confluence valve collects the confluence back, passes through oil pipe by the confluence valve exit end and carries extremely in the solenoid electric valves, distribute hydraulic oil by the solenoid electric valves in the first hydraulic motor with in the second hydraulic motor, realize independent drainage operation of first water pump and second water pump or drainage operation simultaneously through the solenoid electric valves, satisfy different drainage scene demands.

Description

Hydraulic system of high-power mobile emergency drainage equipment

Technical Field

The utility model relates to an emergent water drainage car technical field especially relates to a hydraulic system is equipped in emergent drainage of high-power portable.

Background

At present, the water pump of emergent drainage car uses motor drive and hydraulic drive as leading, does not have electric power resource to satisfy electric drainage car's demand in many drainage emergency occasions, and drainage car power is big more moreover, and the weight or the volume of motor also can be bigger, inconvenient removal, so high-power drainage car is mainly with hydraulic system drive more.

At present, most of hydraulic systems of high-power drainage vehicles adopt a constant delivery pump to take power from an engine, an electromagnetic valve controls starting and stopping, and a constant delivery motor drives a water pump to drain water, and output of different drainage flow rates of the water pump is realized through specific engine rotating speeds, the drainage flow rate adjusting range is small, the requirements of different scenes such as drought resistance, waterlogging drainage and the like and different drainage stages on the drainage flow rate are different, and the requirements of a flow rate adjusting interval cannot be fully met by the existing scheme; in addition, the water discharge flow is reduced by reducing the rotating speed of the engine, the output power and the torque of the engine are correspondingly reduced, and the engine cannot work in a high-efficiency interval, so that the water discharge vehicle cannot obtain enough power and reach enough water discharge lift.

SUMMERY OF THE UTILITY MODEL

To the problem that above-mentioned prior art exists, the utility model provides a hydraulic system is equipped to high-power portable emergent drainage for solve the technical problem that the prior art that explains in the background art has the defect.

In order to achieve the above object, the utility model discloses a following technical scheme realizes: the utility model provides a high-power portable emergent drainage equips hydraulic system, is including installing hydraulic tank, first variable pump, second variable pump, flow-combining valve, solenoid electric valve group, first hydraulic motor, second hydraulic motor, first water pump, second water pump, radiator on the transport vechicle, hydraulic tank's exit end communicates through oil pipe respectively first variable pump the entrance point of second variable pump, the exit end of first variable pump, second variable pump correspond each entrance point that communicates the flow-combining valve through oil pipe, the flow-combining valve converges after converging the confluence, carry to by the flow-combining valve exit end through oil pipe in the solenoid electric valve group, distribute hydraulic oil to by solenoid electric valve group in first hydraulic motor with in the second hydraulic motor, first hydraulic motor and second hydraulic motor drive first water pump, second water pump through the power that comes from hydraulic oil is corresponding, the exit ends of first hydraulic motor and second hydraulic motor communicate through oil pipe respectively the entrance point of radiator, the exit end of radiator passes through oil pipe with the entrance point of hydraulic tank and communicates.

Further, the water discharge flow rates of the first water pump and the second water pump are proportional to the displacement of the first variable pump and the second variable pump.

The variable displacement pump further comprises a first proportional valve and a second proportional valve, wherein the first proportional valve is installed on the first variable displacement pump and used for controlling the displacement of the first variable displacement pump, and the second proportional valve is installed on the second variable displacement pump and used for controlling the displacement of the second variable displacement pump.

Furthermore, the electromagnetic control valve group comprises a first electromagnetic valve, a second electromagnetic valve, a third electromagnetic valve, an overflow valve, a first cartridge valve, a second cartridge valve and a third cartridge valve, wherein the first electromagnetic valve and the first cartridge valve are used for controlling pressure relief and pressure build of a hydraulic system, the second electromagnetic valve and the second cartridge valve are used for controlling on-off of a first hydraulic motor oil way, and the third electromagnetic valve and the third cartridge valve are used for controlling on-off of a second hydraulic motor oil way.

The remote control device comprises a controller, a first proportional handle, a second proportional handle, a remote control receiver and a control panel, wherein a receiving end of the remote control receiver is connected with output ends of the first proportional handle and the second proportional handle respectively, output ends of the remote control receiver, the first proportional valve group, the second proportional valve group, the first electromagnetic valve, the second electromagnetic valve and the third electromagnetic valve are connected with the receiving end of the controller respectively, and an output end of the controller is connected with the control panel.

To sum up, the utility model provides a hydraulic system is equipped to high-power portable emergent drainage realizes that beneficial effect does: 1. independent drainage operation or simultaneous drainage operation of the first water pump and the second water pump is realized through the electromagnetic control valve bank, and the requirements of different drainage scenes are met;

2. the flow of the drainage pump can be adjusted from zero to the maximum flow in an electrodeless way through a power element consisting of the two variable pumps, so that the requirements of different application scenes and various drainage stages on a large-flow adjusting interval are fully met;

3. the water discharge flow of the water pump is changed by adjusting the discharge capacity of the variable displacement pump, so that the engine always works in a high-efficiency rotating speed and power interval, and the problem that the water pump cannot obtain enough power at a low rotating speed is solved.

Drawings

FIG. 1 is a top plan view of the power and auxiliary components of the particular embodiment;

FIG. 2 is a top plan view of the control and actuator mounting in the exemplary embodiment;

FIG. 3 is a schematic diagram of a hydraulic system in the exemplary embodiment;

FIG. 4 is a schematic electrical schematic of the embodiment;

in the figure: the system comprises a transport vehicle 1, a radiator 2, a hydraulic oil tank 3, a first variable pump 4, a second variable pump 5, a flow-combining valve 6, an electromagnetic control valve group 8, a first hydraulic motor 9, a first water pump 10, a second hydraulic motor 11, a second water pump 12, a first proportional handle 13, a remote control receiver 14, a second proportional handle 15, a control panel 16, a controller 17, a first proportional valve 41, a second proportional valve 51, a first electromagnetic valve 81, a first cartridge valve 82, an overflow valve 83, a second electromagnetic valve 84, a second cartridge valve 85, a third electromagnetic valve 86 and a third cartridge valve 87.

Detailed Description

The present invention will be further explained with reference to the accompanying drawings.

As shown in fig. 1-3, the system comprises a transport vehicle 1, a radiator 2, a hydraulic oil tank 3, a first variable pump 4, a second variable pump 5, a confluence valve block 6, an electromagnetic control valve group 8, a first hydraulic motor 9, a first water pump 10, a second hydraulic motor 11 and a second water pump 12; the first variable pump 4 and the second variable pump 5 are installed on a chassis of the transport vehicle 1, force is taken from an engine of the chassis, pressure oil at outlets of the first variable pump 4 and the second variable pump 5 is converged at a converging block 6, the converged pressure oil enters an inlet of an electromagnetic control valve group 8, the electromagnetic control valve group 8 distributes the converged pressure oil to a first hydraulic motor 9 and a second hydraulic motor 11, and drives the first hydraulic motor 9 and the second hydraulic motor 11 to rotate so as to drive a first water pump 10 and a second water pump 12 to suck and drain water; hydraulic oil at the outlets of the first hydraulic motor 9 and the second hydraulic motor 11 is converged and then enters the inlet of the radiator 2, and the hydraulic oil after radiation returns to the hydraulic oil tank 3; the first variable pump 4 is connected with the confluence valve block 6, the second variable pump 5 is connected with the confluence valve block 6, the confluence valve block 6 is connected with the electromagnetic control valve group 8, the electromagnetic control valve group 8 is connected with the first hydraulic motor 9, the electromagnetic control valve group 8 is connected with the second hydraulic motor 11, the first hydraulic motor 9 is connected with the radiator 2, the second hydraulic motor 11 is connected with the radiator 2, and the radiator 2 is connected with the oil tank 3 through oil pipes;

as shown in fig. 3, the solenoid control valve block 8 incorporates a first solenoid valve 81, a second solenoid valve 84, a third solenoid valve 86, a relief valve 83, a first cartridge valve 82, a second cartridge valve 85, and a third cartridge valve 87; inlets of the first cartridge valve 82, the second cartridge valve 85 and the third cartridge valve 87 are communicated with an inlet of the electromagnetic control valve group 8, a P port of the first electromagnetic valve 81 is communicated with inlets of the first cartridge valve 82 and the overflow valve 83, a port A of the first electromagnetic valve 81 is communicated with a hydraulic control port of the first cartridge valve 82, and a port B of the first electromagnetic valve 81 is plugged; a port P of the second solenoid valve 84 is communicated with an inlet and a hydraulic control port of the second cartridge valve 85, a port T and a port A of the second solenoid valve 84 are communicated with a port T of the solenoid valve group 8, and an outlet of the second cartridge valve 85 is connected with an inlet of the motor; a port P of the third electromagnetic valve 86 is communicated with an inlet and a hydraulic control port of the third cartridge valve 87, a port T and a port A of the third electromagnetic valve 86 are communicated with a port T of the electromagnetic valve group 8, and an outlet of the third cartridge valve 87 is connected with an inlet of the motor;

as shown in fig. 3, the port P of the first proportional valve 41 communicates with the outlet of the first variable pump 4, the port a of the first proportional valve 41 communicates with the variable cylinder of the first variable pump 4, and the port T of the first proportional valve 41 communicates with the drain oil of the first variable pump 4; a port P of the second proportional valve 51 is communicated with an outlet of the second variable pump 5, a port A of the second proportional valve 51 is communicated with a variable cylinder of the second variable pump 5, and a port T of the second proportional valve 51 is communicated with drainage of the second variable pump 5;

as shown in fig. 4, in order to facilitate the control of the variable displacement pump and the solenoid valve by the controller 17, the first proportional handle 13 and the second proportional handle 15 send signals to the receiver 14 through wireless transmission, the receiver 14 is connected with the controller 17 through a wire harness, the control panel 16 is connected with the controller 17 through a wire harness, and the controller 17 is connected with the first proportional valve group 41, the second proportional valve group 51, the first solenoid valve 81, the second solenoid valve 84 and the third solenoid valve 86 through a wire harness;

as shown in fig. 1-4, when the drain switch of the control panel 16 is in a closed state, the first solenoid valve 81, the second solenoid valve 84, the third solenoid valve 86, the first proportional valve group 41 and the second proportional valve group 51 are all in a power-off state, and the hydraulic system is unloaded; the control panel 16 operates to open the drainage switch, the first electromagnetic valve 81 is electrified, the port P of the first electromagnetic valve 81 is communicated with the port A, the engine is accelerated to a set rotating speed, pressure oil discharged by the pump passes through the electromagnetic valve 81 to close the first cartridge valve 82, and the hydraulic system builds pressure but does not exceed the pressure set by the overflow valve 83; the first proportional handle 13 or the second proportional handle 15 is independently adjusted, the first proportional handle 13 and the second proportional handle 15 can be simultaneously operated, the corresponding second electromagnetic valve 84 or the corresponding third electromagnetic valve 86 is electrified, the hydraulic control oil circuit of the corresponding second cartridge valve 85 and the corresponding third cartridge valve 87 is communicated with the T port of the electromagnetic valve group 8, the corresponding second cartridge valve 85 and the corresponding third cartridge valve 87 are opened, pressure oil enters the water pump 9 or the water pump 11 through the second electromagnetic valve 84 or the third electromagnetic valve 86, and the two water pumps can independently operate or simultaneously operate by operating the first proportional handle 13 or the second proportional handle 15; the current input to the first proportional valve group 41 and the second proportional valve group 51 is controlled according to the rotation angles of the first proportional handle 13 and the second proportional handle 15, the first proportional valve group 41 and the second proportional valve group 51 output different pressures to variable cylinders of the first variable pump 4 and the second variable pump 5 according to different currents, the first variable pump 4 and the second variable pump 5 are driven to continuously output different flows, the first hydraulic motor and the second hydraulic motor obtain different rotating speeds, further the stepless regulation of the first water pump 10 and the second water pump 12 from zero to the maximum drainage flow is realized, and the requirements of different application scenes and various drainage stages on a large flow regulation interval are fully met; compare and transfer low engine speed and change the drainage flow of water pump, adjust the displacement of variable pump through the proportion handle and change the drainage flow of water pump, make the engine work all the time under the high efficiency rotational speed, avoid the problem that the water pump can't obtain sufficient power under the low rotational speed of engine.

The foregoing detailed description of certain exemplary embodiments has been provided for the purpose of illustrating the principles of the invention and its practical application, so as to enable others skilled in the art to understand the invention for various embodiments and with various modifications as are suited to the particular use contemplated. This description is not necessarily intended to be exhaustive or to limit the invention to the precise embodiments disclosed. Any embodiments and/or elements disclosed herein may be combined with each other to form various additional embodiments not specifically disclosed. Accordingly, additional embodiments are possible and are intended to be included within the scope of the description and the present disclosure. The specification describes specific examples to achieve a more general objective that may be achieved in other ways.

The terms "front," "back," "upper," "lower," "upward," "downward," and other directional descriptors used in this application are intended to facilitate the description of exemplary embodiments of the invention, and are not intended to limit the structure of exemplary embodiments of the invention in any particular position or orientation. Terms of degree, such as "substantially" or "approximately" should be understood by those of ordinary skill to refer to a reasonable range outside of the given numerical value, e.g., the general tolerances associated with manufacturing, assembly, and use of the described embodiments.

Claims

1. The hydraulic system of the high-power mobile emergency drainage equipment is characterized by comprising a hydraulic oil tank (3), a first variable pump (4), a second variable pump (5), a flow combining valve (6), an electromagnetic control valve group (8), a first hydraulic motor (9), a second hydraulic motor (11), a first water pump (10), a second water pump (12) and a radiator (2) which are installed on a transport vehicle (1), wherein the outlet end of the hydraulic oil tank (3) is respectively communicated with the inlet ends of the first variable pump (4) and the second variable pump (5) through oil pipes, the outlet ends of the first variable pump (4) and the second variable pump (5) are correspondingly communicated with the inlet ends of the flow combining valve (6) through oil pipes, after the flow combining valve (6) is combined, the outlet ends of the flow combining valve (6) are conveyed into the electromagnetic control valve group (8) through the oil pipes, hydraulic oil is distributed to the first hydraulic motor (9) and the second hydraulic motor (11) through the electromagnetic control valve group (8), the first hydraulic motor (9) and the second hydraulic motor (11) are respectively driven by the inlet ends of the second hydraulic motor (10) and the second hydraulic motor (2), the outlet end of the radiator (2) is communicated with the inlet end of the hydraulic oil tank (3) through an oil pipe.

2. A high power mobile emergency drain rig hydraulic system according to claim 1, characterized in that the first and second water pumps (10, 12) discharge water flows proportional to the displacement of the first and second variable displacement pumps (4, 5).

3. A high power mobile emergency drain rig hydraulic system according to claim 1, further comprising a first proportional valve (41), a second proportional valve (51), said first proportional valve (41) being mounted on the first variable displacement pump (4) for controlling the displacement of the first variable displacement pump (4), said second proportional valve (51) being mounted on the second variable displacement pump (5) for controlling the displacement of the second variable displacement pump (5).

4. The high-power mobile emergency drainage equipment hydraulic system according to claim 3, wherein the solenoid control valve group (8) comprises a first solenoid valve (81), a second solenoid valve (84), a third solenoid valve (86), an overflow valve (83), a first cartridge valve (82), a second cartridge valve (85) and a third cartridge valve (87), the first solenoid valve (81) and the first cartridge valve (82) are used for controlling pressure relief and pressure build-up of the hydraulic system, the second solenoid valve (84) and the second cartridge valve (85) are used for controlling on-off of an oil path of the first hydraulic motor (9), and the third solenoid valve (86) and the third cartridge valve (87) are used for controlling on-off of an oil path of the second hydraulic motor (11).

5. The hydraulic system of a high-power mobile emergency drainage device according to claim 4, further comprising a controller (17), a first proportional handle (13), a second proportional handle (15), a remote control receiver (14) and a control panel (16), wherein a receiving end of the remote control receiver (14) is connected with output ends of the first proportional handle (13) and the second proportional handle (15), output ends of the remote control receiver (14), the first proportional valve (41), the second proportional valve (51), the first electromagnetic valve (81), the second electromagnetic valve (84) and the third electromagnetic valve (86) are connected with a receiving end of the controller (17), and an output end of the controller (17) is connected with the control panel (16).