CN220415859U - High-pressure high-flow synchronous diverter valve hydraulic system - Google Patents
High-pressure high-flow synchronous diverter valve hydraulic system Download PDFInfo
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- CN220415859U CN220415859U CN202322121614.2U CN202322121614U CN220415859U CN 220415859 U CN220415859 U CN 220415859U CN 202322121614 U CN202322121614 U CN 202322121614U CN 220415859 U CN220415859 U CN 220415859U
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Abstract
The utility model provides a high-pressure high-flow synchronous flow-dividing valve hydraulic system, which comprises a synchronous flow-dividing valve, a valve core regulating valve, a hydraulic pump and a hydraulic cylinder, wherein the synchronous flow-dividing valve comprises an outer valve sleeve, a spring assembly, a rotary valve, a supporting plate and an end cover, the rotary valve divides an inner cavity of the outer valve sleeve into a spring cavity and a closed cavity, the supporting plate is arranged on two sides of the rotary valve, and the end cover is arranged on two sides of the supporting plate; the first ends of the first regulating valve and the second regulating valve are connected with the rotary valve, the second end of the first regulating valve is connected with the low-pressure oil tank, and the second end of the second regulating valve is connected with high-pressure oil; the first hydraulic pump and the second hydraulic pump are connected with the input end of the rotary valve through one-way valves; the oil supply pipeline of the first hydraulic pump is communicated with a compensation oil supply pipeline and is respectively communicated with a plurality of hydraulic cylinders through a second one-way valve and a reversing valve; the hydraulic cylinders are respectively and correspondingly connected with the output ends of the rotary valves through the reversing valves. The utility model improves the flow of the flow dividing valve, increases the accuracy of synchronous control and realizes the oil supply of high pressure and large flow.
Description
Technical Field
The utility model relates to the field of fluid transmission and control, in particular to a high-pressure high-flow synchronous flow dividing valve hydraulic system.
Background
Under the demand that drive power gradually increases, the application occasions of high-pressure high-flow hydraulic systems are more and more, especially, for mining hydraulic engineering machinery, for example, a scraper conveyor is an important component mechanism of coal mining engineering machinery, mainly by more hydraulic supports, the working range of the coal mining machine is enlarged through adjusting the expansion and contraction amount of a support hydraulic cylinder, the working efficiency of the coal mining machine is improved, the process needs to supply oil to a plurality of hydraulic supports simultaneously, synchronous working and quick action of the hydraulic cylinders are guaranteed, namely, a control valve and a control hydraulic system with larger flow and pressure are needed, if the traditional flow dividing valve is adopted for carrying out hydraulic synchronous control on each group of supports, the hydraulic synchronous control is limited to the valve core structure of the traditional flow dividing valve, the high-pressure high-flow demand cannot be realized, and the synchronous precision is not high. In order to improve the synchronization precision and efficiency in the bracket adjustment process, a high-pressure high-flow synchronous flow dividing valve and a hydraulic system are needed to be designed.
Disclosure of Invention
Aiming at the problems existing in the prior art, the utility model aims to provide a high-pressure high-flow synchronous flow dividing valve hydraulic system, which is characterized in that the synchronous flow dividing valve is arranged, oil supply and two oil ways are designed, the opening size of the synchronous flow dividing valve is controlled through a valve core regulating valve in the operation process, and the structure is optimized, so that the flow of the flow dividing valve is improved, the synchronous control precision is increased, and the high-pressure high-flow oil supply is realized.
The utility model is realized by the following technical scheme:
the high-pressure high-flow synchronous flow-dividing valve hydraulic system comprises a synchronous flow-dividing valve, a valve core regulating valve and a hydraulic pump, wherein the synchronous flow-dividing valve comprises an outer valve sleeve, a spring assembly, a rotary valve, a supporting plate and an end cover, the end part of the rotary valve stretches into a cavity at the inner circumference of the outer valve sleeve, a spring cavity is formed between the first side of the rotary valve and the outer valve sleeve, and the spring assembly is arranged in the spring cavity, and two ends of the spring assembly are respectively abutted against the rotary valve and the outer valve sleeve; a closed cavity is formed between the second side of the rotary valve and the outer valve sleeve; the support plates are respectively arranged at two sides of the rotary valve, and the end covers are respectively arranged at two sides of the support plates and are connected with the outer valve sleeve;
the valve core regulating valve comprises a first regulating valve and a second regulating valve, wherein the first ends of the first regulating valve and the second regulating valve are connected with the control end of the rotating valve, the second end of the first regulating valve is connected with a low-pressure oil tank, and the second end of the second regulating valve is connected with high-pressure oil;
the hydraulic pump comprises a first hydraulic pump and a second hydraulic pump, and the first hydraulic pump and the second hydraulic pump are connected with the input end of the rotary valve through one-way valves; the one-way valve comprises a first one-way valve, a second one-way valve and a third one-way valve, the first one-way valve is arranged on a high-pressure pipeline for unidirectional oil supply of the second hydraulic pump to the rotary valve, and the second one-way valve and the third one-way valve are both arranged on the high-pressure pipeline for unidirectional oil supply of the first hydraulic pump to the rotary valve; a high-pressure oil supply pipeline between the second check valve and the third check valve is communicated with a compensation oil supply pipeline, and the first hydraulic pump is respectively communicated with a plurality of hydraulic cylinders through the second check valve and the reversing valve; the oil delivery port of the output end of the rotary valve is respectively connected with the corresponding hydraulic cylinder through a plurality of groups of reversing valves.
Preferably, the end cover comprises a first end cover and a second end cover, the first end cover and the second end cover are fixedly connected with the outer valve sleeve through fastening bolts, and the rotary valve and the support plates positioned on two sides of the rotary valve are mutually pressed and jointed;
the closed cavity comprises a first closed cavity, a second closed cavity, a third closed cavity and a fourth closed cavity;
the spring chambers include a first spring chamber, a second spring chamber, a third spring chamber, and a fourth spring chamber.
Preferably, the support plates include a first support plate and a second support plate;
the first support plate is provided with a first sinking table for leading out pressure oil, the first sinking table is communicated with the first spring cavity, the second spring cavity, the third spring cavity and the fourth spring cavity, and the first sinking table is connected with the first regulating valve and the second regulating valve through a sixth oil hole arranged at the control end of the rotary valve;
the second supporting plate is provided with a first pressure hole, a second pressure hole, a third pressure hole and a fourth pressure hole, and the first pressure hole, the second pressure hole, the third pressure hole and the fourth pressure hole are respectively communicated with the first closed cavity, the second closed cavity, the third closed cavity and the fourth closed cavity.
Preferably, the first pressure hole, the second pressure hole, the third pressure hole and the fourth pressure hole have the same structure, each pressure hole comprises a fourth sinking table and a fifth oil hole, the fourth sinking table and the fifth oil hole are coaxially arranged, and the four fifth oil holes are respectively connected with an output port of the output end of the rotary valve.
Preferably, a first oil hole, a second oil hole and a third oil hole are formed in the rotary valve, the first oil hole is formed in the center of the rotary valve, and the second oil hole is communicated with the third closed cavity and the first closed cavity through the first oil hole; the third oil hole is communicated with the second closed cavity and the fourth closed cavity through the first oil hole; the four closed cavities are communicated with each other, and the output port of the first oil hole is communicated with the first hydraulic pump and the second hydraulic pump respectively through a fourth oil hole penetrating through the second end cover and the second supporting plate.
Preferably, the reversing valve comprises a two-position three-way electromagnetic reversing valve, a three-position four-way electromagnetic reversing valve and a two-position two-way electromagnetic reversing valve;
the two-position three-way electromagnetic directional valve comprises a first two-position three-way electromagnetic directional valve, a second two-position three-way electromagnetic directional valve, a third two-position three-way electromagnetic directional valve, a fourth two-position three-way electromagnetic directional valve and a fifth two-position three-way electromagnetic directional valve;
the three-position four-way electromagnetic reversing valve comprises a first three-position four-way electromagnetic reversing valve, a second three-position four-way electromagnetic reversing valve, a third three-position four-way electromagnetic reversing valve and a fourth three-position four-way electromagnetic reversing valve.
Preferably, the first inlet ends of the first two-position three-way electromagnetic directional valve, the second two-position three-way electromagnetic directional valve, the third two-position three-way electromagnetic directional valve and the fourth two-position three-way electromagnetic directional valve are respectively communicated with the first output port, the second output port, the third output port and the fourth output port of the rotary valve;
the first outlet ends of the first two-position three-way electromagnetic directional valve, the second two-position three-way electromagnetic directional valve, the third two-position three-way electromagnetic directional valve and the fourth two-position three-way electromagnetic directional valve are respectively communicated with the first inlet ends of the first three-position four-way electromagnetic directional valve, the second three-position four-way electromagnetic directional valve, the third three-position four-way electromagnetic directional valve and the fourth three-position four-way electromagnetic directional valve;
the second inlet ends of the first two-position three-way electromagnetic directional valve, the second two-position three-way electromagnetic directional valve, the third two-position three-way electromagnetic directional valve and the fourth two-position three-way electromagnetic directional valve are all communicated with the first outlet end of the fifth two-position three-way electromagnetic directional valve, and the second outlet end of the fifth two-position three-way electromagnetic directional valve is communicated with the two-position two-way electromagnetic directional valve through a cooler; the inlet end of the fifth two-position three-way electromagnetic reversing valve is communicated with the first hydraulic pump through a second one-way valve.
Preferably, the hydraulic cylinder comprises a first hydraulic cylinder, a second hydraulic cylinder, a third hydraulic cylinder and a fourth hydraulic cylinder, and a first inlet end and a second inlet end of the first hydraulic cylinder, the second hydraulic cylinder, the third hydraulic cylinder and the fourth hydraulic cylinder are respectively communicated with a first outlet end and a second outlet end of a first three-position four-way electromagnetic reversing valve, a second three-position four-way electromagnetic reversing valve, a third three-position four-way electromagnetic reversing valve and a fourth three-position four-way electromagnetic reversing valve.
Preferably, when the first hydraulic cylinder, the second hydraulic cylinder, the third hydraulic cylinder or the fourth hydraulic cylinder needs to be supplemented with oil, the first hydraulic pump is communicated with the hydraulic cylinders through the fifth two-position three-way electromagnetic directional valve.
Preferably, a sealing ring for sealing is arranged between the end cover and the outer valve sleeve.
Compared with the prior art, the utility model has the following beneficial effects:
1. the synchronous flow dividing valve adopts the two valve core regulating valves to regulate and control the internal pressure of the flow dividing valve, so as to regulate the rotation angle of the valve block in the high-pressure high-flow synchronous flow dividing valve, achieve the effect of regulating the size of the inlet of the flow dividing cavity, realize the high flow of oil supply and accurately control the flow dividing valve.
2. The synchronous flow dividing valve has the advantages that the two sides of the rotary valve are respectively provided with the static pressure supporting structures consisting of the supporting plates, and the supporting plates are in compression connection with the rotary valve through the end covers, so that the synchronous flow dividing valve can adapt to different pressure working conditions and realize high-pressure oil supply.
3. According to the utility model, the compensation oil supply adjustment of the single hydraulic cylinder in the hydraulic cylinder group is realized through the hydraulic system loop, the synchronization error is compensated, and the stability of the hydraulic system is improved.
4. The valves in the oil supply main loop are all controlled by the slide valve, so that the flow of the flow dividing valve is improved, and the synchronous control precision is improved.
Drawings
FIG. 1 is a hydraulic schematic diagram of a high pressure, high flow synchronous diverter valve hydraulic system of the present utility model;
FIG. 2 is a radial cross-sectional view of the synchronous diverter valve of the present utility model;
fig. 3 is an axial cross-sectional view of the synchronous diverter valve of the present utility model.
The figure indicates:
1-a motor; 2-a first hydraulic pump; 3-a second hydraulic pump; 401-a first pilot-operated overflow valve; 402-a second pilot-operated overflow valve; 403-a third pilot relief valve; 5-an air cleaner; 6-a stop valve; 7-a synchronous diverter valve; 801-a first two-position three-way electromagnetic reversing valve; 802-a second two-position three-way electromagnetic reversing valve; 803-a third two-position three-way electromagnetic reversing valve; 804-fourth two-position three-way electromagnetic reversing valve; 901-a first three-position four-way electromagnetic reversing valve; 902-a second three-position four-way electromagnetic reversing valve; 903-third three-position four-way electromagnetic directional valve; 904-a fourth three-position four-way electromagnetic reversing valve; 1001-a first hydraulic cylinder; 1002-a second hydraulic cylinder; 1003-third hydraulic cylinder; 1004-fourth hydraulic cylinder; 11-a fifth two-position three-way electromagnetic reversing valve; 12-two-position two-way electromagnetic directional valve; 13-a temperature control element; 14-a cooler; 15-a filter; 16-a heater; 17-liquid level thermometer; 1801-a first one-way valve; 1802-second check valve; 1803-a third one-way valve;
7011-a first regulator valve; 7012-a second regulating valve; 7021-an outer valve sleeve, 7022-a rotary valve, 7023-a first end cover, 7024-a second end cover, 7025-a first support plate, 7026-a second support plate, 7027-a sealing ring and 7029-a fastening bolt;
730-fourth oil hole, 731-fourth sink table, 732-fifth oil hole, 733-third sink table, 740-sixth oil hole, 741-first sink table, 742-first damping hole, 743-second sink table, 751-first pressure hole, 752-second pressure hole, 753-third pressure hole, 754-fourth pressure hole, 761-first oil hole, 762-second oil hole, 763-third oil hole, 771-first closed cavity, 772-first spring cavity, 773-second closed cavity, 774-second spring cavity, 775-third closed cavity, 776-third spring cavity, 777-fourth closed cavity, 778-fourth spring cavity, 7030-spring assembly.
Detailed Description
The present utility model will be described in detail with reference to the accompanying drawings.
The high-pressure high-flow synchronous flow dividing valve hydraulic system comprises a synchronous flow dividing valve, a valve core regulating valve, a hydraulic pump and a hydraulic cylinder, and can realize synchronous control of the sizes of a plurality of openings of the valve core, so that the synchronous flow dividing valve hydraulic system is applied to synchronous control of a plurality of execution elements. The synchronous flow dividing valve adopts the valve core of the rotary valve, and the larger flow area and the effective axial sealing of the valve core are more suitable for mining machinery under the working condition of synchronous control of a plurality of hydraulic cylinders which need high pressure and large flow. The high pressure in the utility model means that the support plate and the rotary valve form a static support structure, and the support plate and the rotary valve are in compression connection through the end cover, so that the high pressure oil supply can be realized by self-adapting to different pressure working conditions. The high flow rate refers to that high-pressure oil introduced through an input end respectively enters four closed cavities, the pressure of the pressure oil is regulated through the control of a valve core regulating valve, the rotation of a rotary valve is further realized, the size of an inlet of the closed cavity is regulated, and therefore the high-flow oil supply is realized.
As shown in fig. 2 and 3, the synchronous diverter valve includes an outer valve housing 7021, a swivel valve 7022, a first end cap 7023, a second end cap 7024, a first support plate 7025, a second support plate 7026, a rubber seal 7027, four fastening bolts 7029, and a spring assembly 7030.
The outer valve sleeve 7021 is of a rectangular structure, the inside of the outer valve sleeve 7021 is of a circular structure and is matched with the outer circle of the rotary valve 7022, four cavities are formed in the inner circumference of the outer valve sleeve 7021, four end portions arranged on the outer circumference of the rotary valve 7022 extend into the four cavities in the inner circumference of the outer valve sleeve 7021 respectively, a spring cavity is formed between the first side of the rotary valve 7022 and the outer valve sleeve 7021, and a spring assembly 7030 is arranged in the spring cavity, and two ends of the spring assembly 7030 are respectively abutted against the rotary valve 7022 and the outer valve sleeve 7021. A closed chamber is formed between the second side of the rotary valve 7022 and the outer valve sleeve 7021. The support plates are respectively arranged at two sides of the rotary valve 7022, and the end covers are respectively arranged at two sides of the support plates and fixedly connected with the outer valve sleeve 7021.
The end cover comprises a first end cover 7023 and a second end cover 7024, the first end cover 7023 and the second end cover 7024 are fixedly installed with the outer valve sleeve 7021 through four fastening bolts 7029, a first support plate 7025, a rotary valve 7022 and a second support plate 7026 are sequentially attached to each other and are in compression connection, and a cavity in the outer valve sleeve 7021 is separated through the end part of the rotary valve 7022 to form a closed cavity and a spring cavity. The rotary valve 7022 is sandwiched between two support plates 7025 and 7026, and a pressing force is applied to the rotary valve 7022 by the two support plates, so that the rotary valve 7022 works normally under the action of pressure. The closed lumens are provided in four and identical structures, including a first closed lumen 771, a second closed lumen 773, a third closed lumen 775, and a fourth closed lumen 777. The spring chambers are four and are identical in construction, including a first spring chamber 772, a second spring chamber 774, a third spring chamber 776, and a fourth spring chamber 778.
Each closed cavity and each spring cavity are formed by mutually bonding, pressing and connecting an outer valve sleeve 7021, a rotary valve 7022, a first supporting plate 7025 and a second supporting plate 7026, and a sealing ring 7027 made of rubber is arranged between an end cover and the outer valve sleeve 7021, so that the sealing effectiveness of the first closed cavity 771, the second closed cavity 773, the third closed cavity 775 and the fourth closed cavity 777 can be ensured by the tight connection during fixing. Wherein the spring assembly 7030 is mounted within each of the first, second, third, and fourth spring lumens 772, 774, 776, 778.
The second oil hole 762 and the third oil hole 763 in the rotary valve 7022 are through holes and are arranged at 90 degrees to be converged with the first oil hole 761 in the center, the fourth oil hole 730 formed by the center holes of the second support plate 7026 and the second end cover 7024 is concentrically arranged with the first oil hole 761 in equal diameter, and pressure oil connected to the fourth oil hole 730 can be guaranteed to continuously circulate to the second oil hole 762 and the third oil hole 763, and then is in oil communication with each closed cavity of the rotary valve 7022. The sixth oil hole 740 formed by the first end cover 7023 and the central hole of the first support plate 7025 is communicated with the first sinking platform 741, so that pressure oil accessed by the sixth oil hole 740 can continuously flow to one side of the spring cavity of the rotary valve, the fourth sinking platform 731 is uniformly distributed on the first mounting surface of the second support plate 7026 in a radial direction at 90 degrees, the fourth sinking platform 731 is communicated with the closed cavity of the rotary valve 7022, the fifth oil hole 732 and the fourth sinking platform 731 are concentrically arranged, and oil liquid at the side of the spring cavity of the rotary valve is respectively led out to P1, P2, P3 and P4 output ports. Wherein the first damping hole 742 penetrates the second sinking table 743 and the first sinking table 741, and introduces pressure oil on one side of the spring chamber of the rotary valve 7022 into the second sinking table 743. The annular gap between the second support plate 7026 and the second end cap 7024 directs pressurized oil from the fourth oil aperture 730 into the third sink 733.
The spool regulating valve comprises a first regulating valve 7011 and a second regulating valve 7012, wherein first ends of the first regulating valve 7011 and the second regulating valve 7012 are connected with a control end of a rotary valve 7022, a second end of the first regulating valve 7011 is connected with a low-pressure oil tank, a second end of the second regulating valve 7012 is connected with high-pressure oil, and the high-pressure oil is oil input by a first hydraulic pump and a second hydraulic pump through one-way valves.
The hydraulic pump comprises a first hydraulic pump 2 and a second hydraulic pump 3, and the first hydraulic pump 2 and the second hydraulic pump 3 are connected with the input end of the rotary valve 7022 through one-way valves. The check valves include a first check valve 1801, a second check valve 1802, and a third check valve 1803, the first check valve 1801 is disposed on a high-pressure oil line through which the second hydraulic pump 3 supplies oil to the rotary valve 7022 in a unidirectional manner, and the second check valve 1802 and the third check valve 1803 are disposed on a high-pressure oil line through which the first hydraulic pump 2 supplies oil to the rotary valve 7022 in a unidirectional manner. The high-pressure oil pipeline of the first hydraulic pump 2 is communicated with a compensation oil supply pipeline between a second check valve 1802 and a third check valve 1803, and the first hydraulic pump 2 is respectively communicated with a first two-position three-way electromagnetic directional valve 801, a second two-position three-way electromagnetic directional valve 804, a third two-position three-way electromagnetic directional valve 803 and a fourth two-position three-way electromagnetic directional valve 804 which are connected with four hydraulic cylinders through the second check valve 1802 and the fifth two-position three-way electromagnetic directional valve 11.
The hydraulic cylinders are connected with oil delivery ports of the output end of the rotary valve in a one-to-one correspondence manner through the reversing valve.
The synchronous shunt function of the synchronous shunt valve 7 is as follows: the first, second, third, and fourth closed chambers 771, 773, 775, 777 communicate with the first, second, and third oil ports 761, 762, 763 provided in the rotary valve 7022. In a preferred embodiment of the present utility model, the first oil hole 761 is disposed at the center of the rotary valve 7022, the second oil hole 762 and the third oil hole 763 are both provided as through holes, and the second oil hole 762 communicates with the third closed cavity 775 and the first closed cavity 771 through the first oil hole 731. The third oil hole 763 communicates the second closed chamber 773 and the fourth closed chamber 777 through the first oil hole 761. The utility model realizes the mutual communication of the four closed cavities.
The output port P0 of the first oil hole 761 is respectively communicated with the first hydraulic pump 2 and the second hydraulic pump 3 through a fourth oil hole 730 penetrating the second support plate 7026 and the second end cover 7024, and pressure oil is connected thereto. The first, second, third and fourth closed chambers 771, 773, 775 and 777 are respectively communicated with the first, second, third and fourth pressure holes 751, 752, 753 and 754, which are formed in the second support plate 7026, so that pressure oil is conveniently inputted into the hydraulic cylinder through the four pressure holes, respectively.
The rotation of the rotary valve 7022 causes the pressure oil to flow from the first oil passage 761 to the first, second, third, and fourth pressure passages 751, 752, 753, and 754, respectively, with the same flow area. In this embodiment, the four pressure holes are all structures of concentric matching of the sinking platform and the oil holes, that is, the first pressure hole 751, the second pressure hole 752, the third pressure hole 753 and the fourth pressure hole 754 each include a fourth sinking platform 731 and a fifth oil hole 732, the fourth sinking platform 731 and the fifth oil hole 732 are arranged as concentric holes, and the four fifth oil holes 732 are respectively connected with the output ports P1, P2, P3 and P4 of the output end of the rotary valve one by one.
The third settling stage 733 is the same as the fourth oil hole 730, and the pressure oil at the output port P0 of the input end of the rotary valve is introduced into the third settling stage 733, so that the second support plate 7026 is pressed onto the rotary valve 7022; the first damping hole 742 introduces the pressure oil in the rotary valve 7022 into the second settling platform 743, so that the first support plate 7025 is pressed onto the rotary valve 7022, thereby realizing the volume chamber effectiveness of the rotary valve 7022.
According to the utility model, by comparing the oil pressure of the closed cavity with the oil pressure of the spring cavity, when the oil pressure of the closed cavity is smaller than the oil pressure of the spring cavity, the rotary valve is reset under the pressure of the spring cavity, so that the rotary valve rotates anticlockwise, and after the rotary valve is reset, the four pressure holes are synchronously closed; when the oil pressure of the closed cavity is larger than the sum of the oil pressure of the spring cavity and the pressing force of the spring assembly, the closed cavity is opened by clockwise rotation of the rotary valve through compressing the spring cavity, and four pressure holes are opened synchronously. The pressure in the closed chamber is derived from the oil pressure created by the pressurized oil introduced into the closed chamber by the first oil port 761, and the pressure in the spring chamber is derived from the sum of the oil pressure introduced into the spring chamber by the sixth oil port 740 and the compression force of the spring assembly 7030 itself.
The spool control function of the synchronous diverter valve 7 is as follows, the first spool spring chamber 772, the second spool spring chamber 774, the third spool spring chamber 776, the fourth spool spring chamber 778 are respectively communicated with the first sinking platform 741 processed on the first support plate 7025, and the first sinking platform 741 is connected with the first regulating valve 7011 and the second regulating valve 7012 through the third oil hole 740 arranged at the control end of the rotary valve, namely, a control oil path is connected here. In the present embodiment, the first sinking platform 741 has a groove structure, and the first sinking platform 741 is communicated with the four spring chambers and is connected to the control oil through the sixth oil hole 740. The first sinking platform 741 can uniformly lead out the pressure oil in the four spring cavities to the side of the sixth oil hole 740, so that the pressure of the spring cavities can be well controlled under the condition that the closed volume cannot be compressed and stretched, and the working capacity of the synchronous diverter valve is improved. The rotary valve 7022 rotates in the cavity of the outer valve sleeve 7021, and the rotary valve 7022 is opened and closed by controlling the size of an oil opening through the combined action of the pressure of pressure oil on the working surface (pressure of a closed cavity) of the rotary valve, the pressing force of the spring assembly 7030 and the pressure of the spring cavity driven by the control oil.
The flow control function of the synchronous diverter valve 7 is as follows, the control end of the synchronous diverter valve 7 is connected with a first regulating valve 7011 and a second regulating valve 7012 respectively, and the first ends of the first regulating valve 7011 and the second regulating valve 7012 are connected with a control oil path through a sixth oil hole 740 arranged at the control end of the synchronous diverter valve 7. The second end of the first regulating valve 7011 is connected to a low-pressure oil tank for pressure relief of the oil tank, and the second end of the second regulating valve 7012 is connected to high-pressure oil and is pressurized by inputting high-pressure oil into the spring cavity. The larger the opening of the first regulator valve 7011, the smaller the pressure of the spring chamber; the larger the opening of second regulator valve 7012, the greater the spring chamber pressure. The spring cavity pressure is a power source for the action of the rotary valve, and the opening size of the closed cavity of the synchronous diverter valve 7 is realized by adjusting the opening sizes of the first regulating valve 7011 and the second regulating valve 7012, so that the synchronous adjustable control of multiple execution elements is realized. In this embodiment, rotation of the rotary valve 7022 controls the synchronous increase or decrease of the flow areas of the first pressure hole 751, the second pressure hole 752, the third pressure hole 753, and the fourth pressure hole 754, thereby controlling the oil flow rates of the first output port P1, the second output port P2, the third output port P3, and the fourth output port P4.
The following detailed description of specific embodiments of the utility model follows:
as shown in fig. 1, the high-pressure high-flow synchronous diverter valve hydraulic system of the present utility model integrally includes a motor 1, a first hydraulic pump 2, a second hydraulic pump 3, a first pilot-type relief valve 401, a second pilot-type relief valve 402, a third pilot-type relief valve 403, a synchronous diverter valve 7, a first regulator valve 7011, a second regulator valve 7012, a first two-position three-way electromagnetic directional valve 801, a second two-position three-way electromagnetic directional valve 802, a third two-position three-way electromagnetic directional valve 803, a fourth two-position three-way electromagnetic directional valve 804, a first three-position four-way electromagnetic directional valve 901, a second three-position four-way electromagnetic directional valve 902, a third three-position four-way electromagnetic directional valve 903, a fourth three-position four-way electromagnetic directional valve 904, a fifth two-position three-way electromagnetic directional valve 11, a two-position two-way electromagnetic directional valve 12, a first hydraulic cylinder 1001, a second hydraulic cylinder 1002, a third hydraulic cylinder 1003, a fourth hydraulic cylinder 1004, a first check valve 1801, a second check valve 1802, and a third check valve 1803.
The stop valve 6 in the hydraulic system ensures regular replacement and maintenance of hydraulic oil in the hydraulic oil tank, the air filter 5 ensures air pressure and air cleanliness in the oil tank, the hydraulic oil tank adopts a water-cooling radiator to perform water-cooling in a rated temperature interval, the thermometer 13 and the two-position two-way electromagnetic directional valve 12 are temperature control loops of the water-cooling radiator, the two-position two-way electromagnetic directional valve 12 is opened for water circulation heat dissipation after the temperature reaches the set temperature of the thermometer 13, the heater 16 ensures effective minimum temperature of the oil tank, the liquid level meter 17 detects the oil level of the oil tank, and the filter 15 filters the hydraulic oil tank to effectively ensure the cleanliness of the oil tank.
The second hydraulic pump 3 supplies the pressure oil to the synchronous shunt valve 7 through the first check valve 1801 while the first hydraulic pump 2 supplies the pressure oil to the synchronous shunt valve 7 through the second check valve 1802 and the third check valve 1803 under the driving of the motor 1. The control end of the synchronous diverter valve 7 is connected with a first regulating valve 7011 and a second regulating valve 7012, respectively.
The output end of the synchronous diverter valve 7 is provided with four output ports, namely a first output port P1, a second output port P2, a third output port P3 and a fourth output port P4, and the four output ports are respectively connected with the first inlet ends of the first two-position three-way electromagnetic directional valve 801, the second two-position three-way electromagnetic directional valve 802, the third two-position three-way electromagnetic directional valve 803 and the fourth two-position three-way electromagnetic directional valve 804.
First outlet ends of the first two-position three-way electromagnetic directional valve 801, the second two-position three-way electromagnetic directional valve 802, the third two-position three-way electromagnetic directional valve 803 and the fourth two-position three-way electromagnetic directional valve 804 are connected to first inlet ends of the first three-position four-way electromagnetic directional valve 901, the second three-position four-way electromagnetic directional valve 902, the third three-position four-way electromagnetic directional valve 903 and the fourth three-position four-way electromagnetic directional valve 904, respectively.
The first outlet end and the second outlet end of the first three-position four-way electromagnetic directional valve 901, the second three-position four-way electromagnetic directional valve 902, the third three-position four-way electromagnetic directional valve 903 and the fourth three-position four-way electromagnetic directional valve 904 are connected to the first inlet end and the second inlet end of the first hydraulic cylinder 1001, the second hydraulic cylinder 1002, the third hydraulic cylinder 1003 and the fourth hydraulic cylinder 1004, respectively.
The first hydraulic pump 2 is communicated with the fifth two-position three-way electromagnetic directional valve 11 through a second check valve 1802, and is respectively connected to the second inlet ends of the first two-position three-way electromagnetic directional valve 801, the second two-position three-way electromagnetic directional valve 802, the third two-position three-way electromagnetic directional valve 803 and the fourth two-position three-way electromagnetic directional valve 804 through the first outlet end of the fifth two-position three-way electromagnetic directional valve 11. The second outlet end of the fifth two-position three-way electromagnetic directional valve 11 is communicated with the two-position two-way electromagnetic directional valve 12 through a cooler 14. The two-position two-way electromagnetic directional valve 12 controls the flow state of the coolant of the cooler 14.
The synchronous shunt control function of the multiple hydraulic cylinders is as follows: under the driving of the motor 1, the first hydraulic pump 2 and the second hydraulic pump 3 supply oil, wherein when the executing element needs to work, the first hydraulic pump 2 and the second hydraulic pump 3 supply oil in a combined way, and the pressure oil is split by the synchronous splitter valve 7 and outputs the same flow to the first inlet ends of the first two-position three-way electromagnetic directional valve 801, the second two-position three-way electromagnetic directional valve 802, the third two-position three-way electromagnetic directional valve 803 and the fourth two-position three-way electromagnetic directional valve 804 respectively. Under the condition that electromagnets of the first two-position three-way electromagnetic directional valve 801, the second two-position three-way electromagnetic directional valve 802, the third two-position three-way electromagnetic directional valve 803 and the fourth two-position three-way electromagnetic directional valve 804 are not in electric operation, oil is output to first inlet ends of the first three-position four-way electromagnetic directional valve 901, the second three-position four-way electromagnetic directional valve 902, the third three-position four-way electromagnetic directional valve 903 and the fourth three-position four-way electromagnetic directional valve 904, and then output to first inlet ends of the first hydraulic cylinder 1001, the second hydraulic cylinder 1002, the third hydraulic cylinder 1003 and the fourth hydraulic cylinder 1004 through first output ends of the first three-position four-way electromagnetic directional valve 901, the second three-position four-way electromagnetic directional valve 902, the third three-position four-way electromagnetic directional valve 903 and the fourth three-position four-way electromagnetic directional valve 904 respectively, so that synchronous split control of multiple hydraulic cylinders is realized.
The independent flow compensation function of the multiple hydraulic cylinders is as follows: when the first hydraulic cylinder 1001, the second hydraulic cylinder 1002, the third hydraulic cylinder 1003 and the fourth hydraulic cylinder 1004 leak or are damaged and oil is needed to be replenished, the electromagnets of the first two-position three-way electromagnetic directional valve 801, the second two-position three-way electromagnetic directional valve 802, the third two-position three-way electromagnetic directional valve 803 and the fourth two-position three-way electromagnetic directional valve 804 are powered on, the oil supply state of the current hydraulic cylinder is cut off by the synchronous shunt valve 7, and the first hydraulic pump 2 supplies oil to the second inlet end of the first two-position three-way electromagnetic directional valve 801, the second two-position three-way electromagnetic directional valve 802, the third two-position three-way electromagnetic directional valve 803 or the fourth two-position three-way electromagnetic directional valve 804 through the first outlet end of the fifth two-position three-way electromagnetic directional valve 11, and the hydraulic cylinders which need to be replenished are independently regulated and controlled.
The first pilot relief valve 401, the second pilot relief valve 402, and the third pilot relief valve 403 automatically release pressure and stabilize the system pressure when the oil pressure in the line in which they are located exceeds a predetermined value.
In the preferred embodiment of the present utility model, the oil shortage refers to a state in which it is assumed that synchronous operation with other hydraulic cylinders cannot be achieved after a certain hydraulic cylinder among the four externally connected hydraulic cylinders leaks itself. Wherein the oil supplement is correspondingly opened, such as: the first hydraulic cylinder 1001 corresponds to the first two-position three-way electromagnetic directional valve 801, and the first two-position three-way electromagnetic directional valve 801 connected with the first hydraulic cylinder 1001 which is short of oil is independently electrified. The leakage compensation means that after the synchronous operation of all the hydraulic cylinders is finished, the hydraulic cylinders which are not in place are replenished, the oil supply state of the first hydraulic pump 2 to the synchronous flow dividing valve 7 is cut off, and the first hydraulic pump 2 singly supplements the first hydraulic cylinder 1001 which lacks oil through the fifth two-position three-way electromagnetic directional valve 11.
The above examples are only illustrative of the preferred embodiments of the present utility model and are not intended to limit the scope of the present utility model, and various modifications and improvements made by those skilled in the art to the technical solution of the present utility model should fall within the scope of protection defined by the claims of the present utility model without departing from the spirit of the present utility model.
Claims (10)
1. A high-pressure high-flow synchronous flow dividing valve hydraulic system is characterized by comprising a synchronous flow dividing valve, a valve core regulating valve and a hydraulic pump,
the synchronous flow dividing valve comprises an outer valve sleeve, a spring assembly, a rotary valve, a supporting plate and an end cover, wherein the end part of the rotary valve stretches into a cavity in the inner circumference of the outer valve sleeve, a spring cavity is formed between the first side of the rotary valve and the outer valve sleeve, and the spring assembly is arranged in the spring cavity, and two ends of the spring assembly are respectively abutted against the rotary valve and the outer valve sleeve; a closed cavity is formed between the second side of the rotary valve and the outer valve sleeve; the support plates are respectively arranged at two sides of the rotary valve, and the end covers are respectively arranged at two sides of the support plates and are connected with the outer valve sleeve;
the valve core regulating valve comprises a first regulating valve and a second regulating valve, wherein the first ends of the first regulating valve and the second regulating valve are connected with the control end of the rotating valve, the second end of the first regulating valve is connected with a low-pressure oil tank, and the second end of the second regulating valve is connected with high-pressure oil;
the hydraulic pump comprises a first hydraulic pump and a second hydraulic pump, and the first hydraulic pump and the second hydraulic pump are connected with the input end of the rotary valve through one-way valves; the one-way valve comprises a first one-way valve, a second one-way valve and a third one-way valve, the first one-way valve is arranged on a high-pressure pipeline for unidirectional oil supply of the second hydraulic pump to the rotary valve, and the second one-way valve and the third one-way valve are both arranged on the high-pressure pipeline for unidirectional oil supply of the first hydraulic pump to the rotary valve; a high-pressure oil supply pipeline between the second check valve and the third check valve is communicated with a compensation oil supply pipeline, and the first hydraulic pump is respectively communicated with a plurality of hydraulic cylinders through the second check valve and the reversing valve; the oil delivery port of the output end of the rotary valve is respectively connected with the corresponding hydraulic cylinder through a plurality of groups of reversing valves.
2. The high pressure, high flow synchronous diverter valve hydraulic system of claim 1,
the end cover comprises a first end cover and a second end cover, the first end cover and the second end cover are fixedly connected with the outer valve sleeve through fastening bolts, and the rotary valve and the support plates positioned on two sides of the rotary valve are mutually pressed and jointed;
the closed cavity comprises a first closed cavity, a second closed cavity, a third closed cavity and a fourth closed cavity;
the spring chambers include a first spring chamber, a second spring chamber, a third spring chamber, and a fourth spring chamber.
3. The high pressure, high flow synchronous diverter valve hydraulic system of claim 2,
the support plates include a first support plate and a second support plate;
the first support plate is provided with a first sinking table for leading out pressure oil, the first sinking table is communicated with the first spring cavity, the second spring cavity, the third spring cavity and the fourth spring cavity, and the first sinking table is connected with the first regulating valve and the second regulating valve through a sixth oil hole arranged at the control end of the rotary valve;
the second supporting plate is provided with a first pressure hole, a second pressure hole, a third pressure hole and a fourth pressure hole, and the first pressure hole, the second pressure hole, the third pressure hole and the fourth pressure hole are respectively communicated with the first closed cavity, the second closed cavity, the third closed cavity and the fourth closed cavity.
4. The high-pressure, high-flow synchronous diverter valve hydraulic system of claim 3,
the first pressure hole, the second pressure hole, the third pressure hole and the fourth pressure hole are identical in structure, each pressure hole comprises a fourth sinking table and a fifth oil hole, the fourth sinking table and the fifth oil hole are arranged in a coaxial mode, and the four fifth oil holes are connected with an output port of the output end of the rotary valve respectively.
5. The high-pressure high-flow synchronous flow dividing valve hydraulic system according to claim 2, wherein a first oil hole, a second oil hole and a third oil hole are arranged in the rotary valve, the first oil hole is arranged at the center of the rotary valve, and the second oil hole is communicated with the third closed cavity and the first closed cavity through the first oil hole; the third oil hole is communicated with the second closed cavity and the fourth closed cavity through the first oil hole; the four closed cavities are communicated with each other, and the output port of the first oil hole is communicated with the first hydraulic pump and the second hydraulic pump respectively through a fourth oil hole penetrating through the second end cover and the second supporting plate.
6. The high pressure, high flow synchronous diverter valve hydraulic system of claim 1,
the reversing valve comprises a two-position three-way electromagnetic reversing valve, a three-position four-way electromagnetic reversing valve and a two-position two-way electromagnetic reversing valve;
the two-position three-way electromagnetic directional valve comprises a first two-position three-way electromagnetic directional valve, a second two-position three-way electromagnetic directional valve, a third two-position three-way electromagnetic directional valve, a fourth two-position three-way electromagnetic directional valve and a fifth two-position three-way electromagnetic directional valve;
the three-position four-way electromagnetic reversing valve comprises a first three-position four-way electromagnetic reversing valve, a second three-position four-way electromagnetic reversing valve, a third three-position four-way electromagnetic reversing valve and a fourth three-position four-way electromagnetic reversing valve.
7. The high pressure, high flow synchronous diverter valve hydraulic system of claim 6,
the first inlet ends of the first two-position three-way electromagnetic directional valve, the second two-position three-way electromagnetic directional valve, the third two-position three-way electromagnetic directional valve and the fourth two-position three-way electromagnetic directional valve are respectively communicated with a first output port, a second output port, a third output port and a fourth output port of the rotary valve;
the first outlet ends of the first two-position three-way electromagnetic directional valve, the second two-position three-way electromagnetic directional valve, the third two-position three-way electromagnetic directional valve and the fourth two-position three-way electromagnetic directional valve are respectively communicated with the first inlet ends of the first three-position four-way electromagnetic directional valve, the second three-position four-way electromagnetic directional valve, the third three-position four-way electromagnetic directional valve and the fourth three-position four-way electromagnetic directional valve;
the second inlet ends of the first two-position three-way electromagnetic directional valve, the second two-position three-way electromagnetic directional valve, the third two-position three-way electromagnetic directional valve and the fourth two-position three-way electromagnetic directional valve are all communicated with the first outlet end of the fifth two-position three-way electromagnetic directional valve, and the second outlet end of the fifth two-position three-way electromagnetic directional valve is communicated with the two-position two-way electromagnetic directional valve through a cooler; the inlet end of the fifth two-position three-way electromagnetic reversing valve is communicated with the first hydraulic pump through a second one-way valve.
8. The high pressure, high flow synchronous diverter valve hydraulic system of claim 7,
the hydraulic cylinders comprise a first hydraulic cylinder, a second hydraulic cylinder, a third hydraulic cylinder and a fourth hydraulic cylinder, and a first inlet end and a second inlet end of the first hydraulic cylinder, the second hydraulic cylinder, the third hydraulic cylinder and the fourth hydraulic cylinder are respectively communicated with a first outlet end and a second outlet end of a first three-position four-way electromagnetic reversing valve, a second three-position four-way electromagnetic reversing valve, a third three-position four-way electromagnetic reversing valve and a fourth three-position four-way electromagnetic reversing valve.
9. The high pressure, high flow synchronous diverter valve hydraulic system of claim 8,
when the first hydraulic cylinder, the second hydraulic cylinder, the third hydraulic cylinder or the fourth hydraulic cylinder need to be supplemented with oil, the first hydraulic pump is communicated with the hydraulic cylinders through the fifth two-position three-way electromagnetic directional valve.
10. The high pressure, high flow synchronous diverter valve hydraulic system of claim 1,
and a sealing ring for sealing is arranged between the end cover and the outer valve sleeve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202322121614.2U CN220415859U (en) | 2023-08-08 | 2023-08-08 | High-pressure high-flow synchronous diverter valve hydraulic system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202322121614.2U CN220415859U (en) | 2023-08-08 | 2023-08-08 | High-pressure high-flow synchronous diverter valve hydraulic system |
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| Publication Number | Publication Date |
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| CN220415859U true CN220415859U (en) | 2024-01-30 |
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|---|---|---|---|
| CN202322121614.2U Active CN220415859U (en) | 2023-08-08 | 2023-08-08 | High-pressure high-flow synchronous diverter valve hydraulic system |
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| Country | Link |
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| CN (1) | CN220415859U (en) |
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2023
- 2023-08-08 CN CN202322121614.2U patent/CN220415859U/en active Active
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