CN211715441U

CN211715441U - Hydraulic integrated valve set for realizing double-pump confluence and large-flow multi-action

Info

Publication number: CN211715441U
Application number: CN202020280411.1U
Authority: CN
Inventors: 许利君; 翟磊; 上官林建
Original assignee: Zhengzhou Hensco Electromechanical Equipment Co ltd
Current assignee: Zhengzhou Hensco Electromechanical Equipment Co ltd
Priority date: 2020-03-10
Filing date: 2020-03-10
Publication date: 2020-10-20
Anticipated expiration: 2030-03-10

Abstract

The utility model relates to a hydraulic integrated valve group for realizing double-pump confluence and large flow and multiple actions, which comprises an electro-hydraulic reversing valve, a plate-type pilot overflow valve, a cartridge-type electromagnetic valve, a direct-acting sequence valve, a cartridge-type one-way valve and a cartridge-type pressure reducing valve which are arranged inside a valve block, the utility model can realize the double-pump confluence composite function of a group of hydraulic systems which can meet the requirements of multiple actions and different pressures, and meet the use requirements of larger flow; the utility model adopts a process of completing all pore processing by one-time clamping, which can greatly improve the quality of the valve group, reduce the rejection rate and save materials; the utility model can greatly reduce the liquid resistance increased by too much and overlong pipelines and joints; the utility model discloses can realize that automatic formula lubrication refuels can not only realize constantly self-service lubrication refuels, also can optimize structural arrangement, lifting means's stability and reliability.

Description

Hydraulic integrated valve set for realizing double-pump confluence and large-flow multi-action

Technical Field

The utility model relates to a realize double pump confluence and hydraulic pressure integrated valves of large-traffic many actions.

Technical Field

With the gradual development of the trailer pump machinery, a single machine type realizes multiple action functions and more composite working conditions, and higher configuration requirements are provided for a hydraulic valve set.

The traditional trailer pump machinery conventionally only has single function and single action, can only meet the construction under single working condition, generally requires two or even a plurality of mechanical equipment to enter the field for construction simultaneously when multiple working conditions are involved, not only occupies field resources, but also greatly increases the labor and equipment occupancy rate, and greatly increases the coordination strength among various working modes. When the structure was arranged, the tradition dragged pump machinery mostly adopted single pump single valves to realize a certain action function, for solving the problem that the engine only has a power take off end, the drive train adopted the belt pulley drive structure, not only transmission efficiency is low, and the fault rate is high and the belt easily wears out moreover, and the maintenance is changed and is wasted time and energy.

The design of valves also adopts the mode that independent sub-module arranged alone mostly, the conventional way is to adopt the mode of sequential tiling connection in proper order between each control valve, pass through hydraulic line connection with pressure component, switching-over component etc. in proper order, it is comparatively dispersed to arrange between each component, it is long to bring the pipeline that is showing the problem, the pipeline is dense numb, the coupling is in large quantity, not only increase hydraulic system's liquid resistance, reduce the use efficiency of equipment, the pipeline leakage point is turned over in step and is promoted, the safety fault point also shows to be increased, technical requirement to after-sale and maintenance personal also improves, after-sale cost aggravation.

The trailer pump equipment has high use frequency, and the pin shaft, the bearing of a transmission system and the like need to be lubricated and maintained regularly, otherwise the trailer pump equipment is easy to damage. The conventional trailer pump mechanical lubricating system adopts a mode of manually filling butter, and is totally dependent on the literacy and regulatory constraints of workers, even if operators forget to fill the grease, the bearings are sintered and damaged. Even if workers fill the oil regularly, the problems of adding missing, adding less and the like are also solved.

Along with the development of trailer pump mechanical equipment, it requires that it possesses the characteristics that the model increases, work efficiency is higher, and its required hydraulic system's flow also promotes several times, and the most flow of traditional hydraulic valve group is on the low side, and the energy consumption is high, and the function is on the single side, and intelligent degree is lower.

Disclosure of Invention

The utility model aims at realizing double-pump confluence and large-flow multi-action hydraulic integrated valve set aiming at the defects existing in the prior art.

The purpose of the utility model is realized like this: the utility model provides a realize double pump confluence and large-traffic many hydraulic pressure integrated valve group of action, it includes the valve block, install left and right switching-over valve, overflow mechanism, sequence valve, check valve, relief pressure valve and manometer on the valve block, be provided with oil inlet P1, P2 and the main oil return T of pressure oil on the valve block lateral wall, wait to press oil mouth G and pressure measurement mouth K1, K2, the pipeline that oil inlet P1, P2 are connected is confluent in valve block H department, and through overflow mechanism and main oil return T intercommunication all the way, another way communicates with the oil inlet of left switching-over valve, manometer, the oil inlet of sequence valve respectively, left side switching-over valve communicates with hydraulic fluid port A1, B1 respectively, hydraulic fluid port A1, B1 and executive component's hydraulic fluid port intercommunication, the oil-out of sequence valve communicates with the oil inlet of right switching-over valve and the oil inlet of relief pressure valve respectively through the check valve, right side switching-over valve communicates with hydraulic fluid port A2, A3 and parallelly connected hydraulic fluid ports B2, B3 communicate, hydraulic fluid ports A2, B2 and hydraulic fluid ports A3, B3 communicate with the hydraulic fluid port of executive component and lubricating oil pump respectively, the oil-out and the pressure oil port G that waits on the valve block of relief valve communicate, the oil leakage mouth and the oil return port of left and right switching-over valve, sequence valve, relief valve all communicate through pipeline and the main oil return port T on the valve block lateral wall.

And the side wall of the valve block is provided with an auxiliary oil return port T1 and an auxiliary pressure measuring port K2.

The overflow mechanism comprises an overflow valve and an electromagnetic valve, the overflow valve is a plate-type pilot-controlled overflow valve, the electromagnetic valve is a plug-in type electromagnetic valve, an oil inlet of the overflow valve is communicated with oil inlets P1 and P2 at a position H inside a valve block, an oil outlet of the overflow valve is communicated with a main oil return port T on the valve block, a working oil port of the electromagnetic valve is communicated with an oil way of the overflow valve, and the pressure switching state of a flow valve controlled by the plate-type pilot overflow is controlled through the power-on and power-off of the electromagnetic valve.

The left reversing valve and the right reversing valve are electro-hydraulic reversing valves, the sequence valves are direct-acting sequence valves, the one-way valves are cartridge type one-way valves, and the pressure reducing valves are cartridge type pressure reducing valves.

The electro-hydraulic directional control valve adopts an electromagnetic pilot control structure and consists of a small-flow electromagnetic pilot valve and a large-flow hydraulic control directional control valve, pilot oil adopts an internal control and internal discharge mode, namely, the internal discharge of the oil is controlled, and the internal discharge of leaked oil is realized, so that the directional control of hydraulic large flow is realized with the minimum electric power consumption.

The direct-acting sequence valve arranged on the oil circuit is set with a fixed pressure value, and oil can only pass through the sequence valve after the system pressure reaches the set pressure value, so that the composite action of the same hydraulic system when different pressure values are required can be met, and the adaptability of the hydraulic system is greatly improved.

The utility model can realize the large-flow confluence of the double hydraulic pumps, and solve the problem of insufficient flow caused by the increase of the tractor type; an electro-hydraulic reversing valve is selected, and the reversing action of a small-flow pilot electromagnetic valve is controlled to realize the reversing of a hydraulic control valve so as to realize the oil passing working capacity of large flow and high pressure; the multi-action linkage function which has composite action requirements and needs different set pressure values can be realized; the integrated valve group design concept can reduce the use number of pipelines and joints in a hydraulic system as much as possible through the communication of internal pore channels, reduce the hydraulic resistance and reduce the leakage points at the pipeline connection position; two groups of electro-hydraulic reversing valves which are independently arranged on the left and the right realize the requirements of high flow and multi-function compound actions; the direct-acting type pressure reducing valve arranged on the valve bank can meet the composite action of the same hydraulic system when different pressure values are required, and the adaptability of the hydraulic system is greatly improved; the cartridge type pressure reducing valve designed on the valve bank can provide a pilot oil source for the hydraulic system, so that the use number of hydraulic pumps is saved, and the cost is reduced; the whole valve group adopts a combined structure of a cartridge valve type and a plate valve type, so that the oil passing capacity is ensured, the service performance is met, meanwhile, the installation space is saved as much as possible, the practicability of the valve group can be greatly improved, the structure is more compact, and the maintenance is more convenient; two oil outlets A3 and B3 are additionally arranged at an oil passage outlet of the right electro-hydraulic reversing valve 4 and used for driving a lubricating oil pump, so that automatic lubrication of the trailer pump machinery can be realized, various defects of adding less grease and adding less grease are thoroughly overcome, and long-term high-efficiency operation of the trailer pump machinery is guaranteed.

Compared with the prior art, the utility model, following beneficial effect has:

1. the utility model can realize the composite function that the configuration of the same hydraulic system meets the requirements of multiple actions and different pressures, easily realize the confluence function of the double hydraulic pumps and meet the use requirement of larger flow;

2. the utility model adopts the design concept of cartridge valve type and plate valve type, the valve block adopts a No. 45 steel forging, and the process of processing all pore channels can be completed by one-time clamping in the processing, thereby greatly improving the quality of the valve group, reducing the rejection rate and saving materials; and the communicating pore channels are mostly designed in the valve block, so that the hydraulic pipeline is saved, the use number of joints is reduced, the hydraulic resistance increased by excessive and overlong pipelines and joints can be greatly reduced, and the pipeline installation difficulty can also be reduced;

3. the utility model discloses an automatic lubricated refuelling of formula can not only improve work efficiency, realizes constantly self-service lubrication refuelling, and can reduce operating personnel's intensity of labour, also can optimize structural arrangement, lifting means's stability and reliability.

Drawings

FIG. 1 is a hydraulic schematic diagram of the present invention

FIG. 2 is a front view of the appearance structure of the utility model

FIG. 3 is a top view of FIG. 2

Fig. 4 is a left side view of fig. 3.

Detailed Description

The invention will be further described with reference to the accompanying drawings:

as shown in fig. 1, the hydraulic integrated valve set capable of realizing double-pump confluence and large flow multi-action of the present invention comprises a left electro-hydraulic directional valve 3, a right electro-hydraulic directional valve 4, a plate-type pilot overflow valve 1, a cartridge-type solenoid valve 2, a direct-acting sequence valve 5, a cartridge-type check valve 6 and a cartridge-type pressure reducing valve 7, which are installed at corresponding positions of a valve block 8 by a plate-type and cartridge-type combination assembly method; two groups of pressure oil inlets P1 and P2 are arranged and processed on the valve block 8, and pore passages of the pressure oil inlets are drilled through the inside of the valve block 8 to realize confluence of high-flow high-pressure oil passages of oil outlets of the double hydraulic pumps, namely two paths of pressure oil are synthesized into one path inside the valve block 8 to realize high pressure and high flow; the plate-type pilot overflow valve 1 is used for setting the working pressure of the whole hydraulic system and ensuring the safe operation of the system, and has the characteristics of sensitive response, large oil passing capacity and strong pollution resistance, a pressure oil inlet of the plate-type pilot overflow valve 1 is communicated with the insides of two groups of pressure oil inlets P1 and P2 arranged on the valve block 8, and an oil outlet of the overflow valve 1 is communicated with a main oil return port T on the valve block 8; the working pressure of the overflow valve 1 is controlled by a plug-in type electromagnetic valve 2, a working oil port of the electromagnetic valve 2 is communicated with a pilot oil path of a plate type pilot overflow valve 1, the pressure switching state of the plate type pilot overflow valve 1 is controlled by the power loss and the gain of 1DT of the electromagnetic valve 2, if the electromagnetic valve 2 is powered off (namely is not powered on), the pilot oil of the plate type pilot overflow valve 1 is communicated with a main oil return port T through an oil path of the electromagnetic valve 2, at the moment, P1, P2 and T are communicated only by overcoming the set value (about 3 bar) of a spring of the plate type pilot overflow valve 1, the system is in a large-flow unloading state, if the 1DT of the electromagnetic valve 2 is powered on, the pilot oil of the plate type pilot overflow valve 1 is separated by the oil path of the electromagnetic valve 2, at the moment, P1, P2 and T are not communicated, the hydraulic system is in a, the energy consumption is reduced, the cost is saved, and the 1DT needs to be powered when the system works normally; the two paths of converged pressure oil are respectively communicated with a P port of the left electro-hydraulic reversing valve 3 and a 5-1 high-pressure working oil port of the right direct-acting sequence valve 5 through an internal pipeline of the valve block 8, and the oil can pass through the sequence valve 5 only when the system pressure reaches a set value of the fixed pressure value due to the fact that the direct-acting sequence valve 5 is set with the fixed pressure value, so that the oil is preferentially supplied to the electro-hydraulic reversing valve 3 in a large flow rate, and the working state of the electro-hydraulic reversing valve is guaranteed; the electro-hydraulic directional control valve 3 adopts an electromagnetic pilot control structure and consists of a small-flow electromagnetic pilot valve 3.1 and a large-flow hydraulic control directional control valve 3.2, pilot oil adopts an internal control and internal discharge mode, namely, the internal control oil is internally discharged, leaked oil is internally discharged, hydraulic large-flow control is realized by consuming the minimum electric power, when the system normally works, if a left electromagnet 2DT of the electromagnetic pilot valve 3.1 is electrified, a valve core of the electromagnetic pilot valve 3.1 moves towards the right side, a port I and a pilot valve port of the electromagnetic pilot valve 3.1 are communicated, a port III and a port IV are communicated, high-pressure oil acts on the right side of the hydraulic control directional control valve 3.2 from a port P through an port X and the port IV, so that the valve core of the hydraulic control directional control valve 3.2 is pushed to move towards the left side, at the moment, the hydraulic control directional control valve 3.2 is communicated with a main oil return port T through a port III and a leakage port IV of the electromagnetic pilot valve 3.1, and the hydraulic control directional control valve 3.2 is communicated with a main oil return port 1B on a valve block, the port A1 on the valve block 8 is communicated with the port II and the port IV, the pressure oil passes through the port I and the port III to the port B1 from the port P, the port A1 is communicated with the main oil return port T, and the reverse is also true; when the system normally works and reaches a rated pressure set value of the direct-acting sequence valve 5, high-flow high-pressure oil is communicated with an oil inlet 6-1 of the plug-in type one-way valve 6 through an oil inlet 5-1 and an oil outlet 5-2 of the sequence valve 5, and if the pressure does not reach the set value of the sequence valve 5, the sequence valve 5 is in a closed state and no oil passes through; the plug-in type one-way valve 6 adopts a threaded screwing type structure, so that the weight of the valve group is reduced while the oil passing capacity is increased and the volume of the valve block is reduced; after high-pressure oil passes through an oil outlet 6-2 of the cartridge type one-way valve 6, high-flow pressure oil reaching a rated value is divided into two paths, one path is communicated with an oil inlet P port of the right electro-hydraulic directional valve 4, and the other path is communicated with an oil inlet 7-1 of the cartridge type pressure reducing valve 7; the electro-hydraulic directional valve 4 adopts an electromagnetic pilot control structure and consists of a small-flow electromagnetic pilot valve 4.1 and a large-flow hydraulic control directional valve 4.2, pilot oil adopts an internal control and internal discharge mode, namely, the internal control of oil is adopted, the internal discharge of leaked oil is realized, the hydraulic large flow is controlled by consuming the minimum electric power, the control principle and the idea are similar to those of the electro-hydraulic directional valve 3, oil ports A2, A3, B2 and B3 which are internally communicated are respectively arranged at the outlet of the electro-hydraulic directional valve 4, the oil ports A2 and B2 are connected with an actuating mechanism to realize the action of equipment, and the oil ports A3 and B3 are used for driving a lubricating oil pump which linearly reciprocates to automatically work, so that the independent oil filling function of a bearing is realized; pressure oil enters from an oil inlet 7-1 of the cartridge type reducing valve 7, is reduced to pilot pressure required by a hydraulic system after passing through the reducing valve 7, is communicated with a to-be-pressed port G on the valve block 8 through an oil outlet 7-2, and provides required standby pressure for the system; the pilot oil leakage ports of the element electro-hydraulic reversing valve 3, the electro-hydraulic reversing valve 4, the direct-acting sequence valve 5 and the cartridge type reducing valve 7 are communicated with the main oil return port T of the valve block.

The working principle of the utility model is as follows:

after the towing pump is mechanically started, a hydraulic system is in a standby state, the plug-in type electromagnetic valve 2, the electro-hydraulic reversing valve 3 and the electro-hydraulic reversing valve 4 are not electrified, large-flow high-pressure oil at the oil outlet of the double hydraulic pump is converged at the position H inside the valve block 8, namely two paths of pressure oil are combined into one path at the position H inside the valve block 8, pilot oil of the plate-type pilot overflow valve 1 is communicated with a main return oil T through ports 1-3 through ports 2-1 and 2-2 of the electromagnetic valve 2, at the moment, the communication of P1, P2 and T only needs to overcome a set value (about 3 bar) of a spring of the plate-type pilot overflow valve 1, the converged oil is communicated with the main return oil T of the valve block 8 through ports 1-1 and 1-2 of the pilot overflow valve 1, the hydraulic system is in a large-flow unloading state, the power consumption.

When the hydraulic system normally works, 1DT of the electromagnetic valve 2 needs to be electrified firstly, pilot oil of the plate type pilot overflow valve 1 is isolated by the inside of an oil duct of the electromagnetic valve 2, and P, T is not communicated at the moment, so that the hydraulic system is at a working pressure value; if the system works normally, the 1DT needs to be powered; after the hydraulic system normally works, two paths of converged pressure oil are respectively communicated with a P port of a left electro-hydraulic directional control valve 3 and a 5-1 high-pressure working oil port of a right direct-acting sequence valve 5 through an internal pipeline of a valve block 8, the converged pressure oil acts on the P port of the electro-hydraulic directional control valve 3, at the moment, if a left electromagnet 2DT of the electromagnetic directional control valve 3.1 is electrified, a valve core of the electromagnetic directional control valve 3.1 moves towards the right side, a port I and a port II of the electromagnetic directional control valve 3.1 are communicated, a port III and a port III are communicated, at the moment, the high-pressure oil flows from the port P to the port I and the port II through an internal pore channel and acts on the right side of the electro-hydraulic directional control valve 3.2 to push the valve core of the electro-hydraulic directional control valve 3.2 to move towards the left side, meanwhile, leakage oil of the electro-hydraulic directional control valve 3.2 is communicated with main return oil through the port III and the port IV of the electromagnetic directional control valve 3.1, the port III and the port III, the port III, the port A1 on the valve block 8 is communicated with the port II and the port IV, at the moment, high-flow high-pressure oil is communicated from the port P of the electro-hydraulic reversing valve 3 to the port B1 through the port I and the port III of the hydraulic control reversing valve 3.2 to drive an executing element to act, and the port A1 is communicated with a main oil return port T through the port II and the port IV of the hydraulic control reversing valve 3.2 to return oil; and vice versa; when the system pressure reaches the set value of the direct-acting sequence valve 5, oil can pass through, so that the oil is preferentially supplied to the electro-hydraulic reversing valve 3 in a large flow rate, the working state of the electro-hydraulic reversing valve is guaranteed, and the multi-action sequence working function of the system is realized; when the system normally works, when a rated pressure set value of the direct-acting sequence valve 5 is reached, high-flow high-pressure oil is communicated with an oil inlet 6-1 of the plug-in type one-way valve 6 through an oil inlet 5-1 and an oil outlet 5-2 of the sequence valve 5, the high-flow high-pressure oil reaching the rated value is divided into two paths after passing through an oil outlet 6-2 of the plug-in type one-way valve 6, one path of high-flow pressure oil is communicated with an oil inlet P port of the right-side electro-hydraulic reversing valve 4, and the other path of high-flow pressure oil is communicated with an oil; the high flow rate pressure oil of the rated value acts on the P port of the electro-hydraulic reversing valve 4, if the left electromagnet 4DT of the electromagnetic pilot valve 4.1 is electrified, the valve core of the electromagnetic pilot valve 4.1 moves to the right side, the port I of the electromagnetic pilot valve 4.1 is communicated with the port II, the port III is communicated with the port I, the high flow rate high pressure oil of the rated value moves to the port I and the port II from the X port through the inner pore passage at the moment, the pressure is acted on the right side of the electro-hydraulic reversing valve 4.2, thereby pushing the valve core of the electro-hydraulic reversing valve 4.2 to move to the left side, meanwhile, the leakage oil of the electro-hydraulic reversing valve 4.2 is communicated with the main oil return port T through the port III and the port II of the electromagnetic pilot valve 4.1, after the electro-hydraulic reversing valve 4.2 is pushed to the left side, the port I and the port III are communicated with the ports B2 and B3 on the valve block 8, the ports A2 and A3 on the valve block 8 are communicated with the port III and the port 3, b2 and B3 are communicated in the valve block 8, the oil drives the executive component to act through the port B2, the port B3 is used for driving the grease pump of the linear reciprocating motion to automatically work, the function of self-service grease filling of the bearing and the pin shaft is realized, and A2 and A3 are communicated with the main T port for oil return through the port II and the port III of the hydraulic control reversing valve 4.2; and vice versa; pressure oil with a rated value enters through an oil inlet 7-1 of the cartridge type reducing valve 7, is reduced to pilot pressure required by a hydraulic system after passing through the reducing valve 7, and is communicated with a pressure-waiting opening G on the valve block 8 through an oil outlet 7-2 to provide required standby pressure for the system; the pilot oil leakage ports of the element electro-hydraulic reversing valve 3, the electro-hydraulic reversing valve 4, the direct-acting sequence valve 5 and the cartridge type pressure reducing valve 7 are communicated with the main oil return port T of the valve block; and system pressure measuring ports K2 and MP are arranged on the valve group, and an oil return port T1 is reserved.

Claims

1. The utility model provides a realize double pump confluence and large-traffic many hydraulic pressure integrated valve group of moving which includes the valve block, its characterized in that: the valve block is provided with a left reversing valve, a right reversing valve, an overflow mechanism, a sequence valve, a one-way valve, a pressure reducing valve and a pressure gauge, the side wall of the valve block is provided with oil inlets P1 and P2 and a main oil return port T of pressure oil, an oil inlet G to be pressed and a pressure measuring port K1, pipelines connected with the oil inlets P1 and P2 are converged at a position H in the valve block, one path of the pipeline is communicated with the main oil return port T through the overflow mechanism, the other path of the pipeline is respectively communicated with an oil inlet of the left reversing valve, the pressure gauge and an oil inlet of the sequence valve, the left reversing valve is respectively communicated with oil ports A1 and B1, the oil ports A1 and B1 are communicated with oil ports of an actuating element, an oil outlet of the sequence valve is respectively communicated with an oil inlet of the right reversing valve and an oil inlet of the pressure reducing valve through the one-way valve, the right reversing valve is respectively communicated with oil ports A2 and A3 which are connected in parallel and an oil port B2 and B3 which are connected in parallel, the oil outlet of the pressure reducing valve is communicated with an oil opening G to be pressed on the valve block, and the oil leakage opening and the oil return opening of the left reversing valve, the right reversing valve, the sequence valve and the pressure reducing valve are communicated with a main oil return opening T on the side wall of the valve block through pipelines.

2. The hydraulic integrated valve group for realizing double-pump confluence and large-flow multi-action according to claim 1, which is characterized in that: the overflow mechanism comprises an overflow valve and an electromagnetic valve, wherein an oil inlet of the overflow valve is communicated with oil inlets P1 and P2 at a position H inside the valve block, an oil outlet of the overflow valve is communicated with a main oil return port T on the valve block, and a working oil port of the electromagnetic valve is communicated with an oil way of the overflow valve.

3. The hydraulic integrated valve group for realizing double-pump confluence and large-flow multi-action according to claim 2, which is characterized in that: the overflow valve is a plate-type pilot-controlled overflow valve, and the electromagnetic valve is a plug-in electromagnetic valve.

4. The hydraulic integrated valve group for realizing double-pump confluence and large-flow multi-action according to claim 1, which is characterized in that: the left reversing valve and the right reversing valve are electro-hydraulic reversing valves, the sequence valves are direct-acting sequence valves, the one-way valves are cartridge type one-way valves, and the pressure reducing valves are cartridge type pressure reducing valves.

5. The hydraulic integrated valve group for realizing double-pump confluence and large-flow multi-action according to claim 4, which is characterized in that: the electro-hydraulic directional control valve adopts electromagnetic pilot control and comprises a small-flow electromagnetic pilot valve and a large-flow hydraulic directional control valve.

6. The hydraulic integrated valve group for realizing double-pump confluence and large-flow multi-action according to claim 4, which is characterized in that: and the side wall of the valve block is provided with an auxiliary oil return port T1 and an auxiliary pressure measuring port K2.