CN113586539A - Control valve group and oil supply valve group - Google Patents
Control valve group and oil supply valve group Download PDFInfo
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- CN113586539A CN113586539A CN202110681675.7A CN202110681675A CN113586539A CN 113586539 A CN113586539 A CN 113586539A CN 202110681675 A CN202110681675 A CN 202110681675A CN 113586539 A CN113586539 A CN 113586539A
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- 239000003921 oil Substances 0.000 claims abstract description 274
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 38
- 239000012530 fluid Substances 0.000 claims abstract description 18
- 238000001514 detection method Methods 0.000 claims description 21
- 230000001105 regulatory effect Effects 0.000 claims description 11
- 230000000694 effects Effects 0.000 abstract description 5
- 238000010586 diagram Methods 0.000 description 3
- 238000005265 energy consumption Methods 0.000 description 3
- 238000007689 inspection Methods 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
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- Engineering & Computer Science (AREA)
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- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The application relates to a valve unit sets up on the valve block, be equipped with oil inlet P, oil return T on the valve block and be used for the first hydraulic fluid port A that the intercommunication hydro-cylinder has the pole chamber and be used for the second hydraulic fluid port B that the intercommunication hydro-cylinder does not have the pole chamber, the valve unit includes the control assembly who changes the hydraulic oil flow through changing the oil circuit, just oil inlet P, oil return T, first hydraulic fluid port A and second hydraulic fluid port B pass through two liang of intercommunications of control assembly. This application has the speed that accelerates the hydro-cylinder and move back worker, improves the effect of the efficiency of hydro-cylinder work.
Description
Technical Field
The application relates to the field of valves, in particular to a control valve group and an oil supply valve group.
Background
The valve is a control part in a pipeline fluid conveying system, is used for changing the size of the section of a passage and the flowing direction of a medium, and has the functions of diversion, cut-off, throttling, non-return, flow splitting, overflow pressure relief and the like. Wherein, multiple valve can constitute the valves through the combination, makes the valves have multiple functions simultaneously.
In the related technology for providing hydraulic oil for the oil cylinder, a pipeline system communicated with the oil cylinder comprises an oil inlet P, an oil return port T, a first oil port A used for communicating a rod cavity of the oil cylinder and a second oil port B used for communicating a rodless cavity of the oil cylinder, wherein the oil inlet P, the oil return port T, the first oil port A and the second oil port B are communicated through a three-position four-way electromagnetic reversing valve, and the communication relation corresponding to the oil inlet P, the oil return port T, the first oil port A and the second oil port B is adjusted under the action of the three-position four-way electromagnetic reversing valve, so that the work stop, work feeding and work returning states of the oil cylinder are controlled.
In view of the above related technologies, the inventor believes that in a fluid delivery system controlled only by a three-position four-way electromagnetic directional valve, a single three-position four-way electromagnetic directional valve only plays a role in reversing, so that the liquid flow of an oil cylinder in a working feeding state and a working withdrawing state is the same, that is, the working feeding speed and the withdrawing speed are the same, and the function of increasing the return oil flow cannot be played for the fluid delivery system, so that the working requirement of quick withdrawal of the oil cylinder cannot be met, and the working efficiency is insufficient.
Disclosure of Invention
In order to accelerate the speed that the hydro-cylinder moved back to the worker, improve the efficiency of hydro-cylinder work, this application provides a valve unit and fuel feeding valves.
In a first aspect, the present application provides a control valve group, which adopts the following technical scheme:
the utility model provides a control valve group, sets up on the valve block, be equipped with oil inlet P, oil return T and be used for communicateing the first hydraulic fluid port A that the hydro-cylinder has the pole chamber and be used for communicateing the second hydraulic fluid port B that the hydro-cylinder does not have the pole chamber on the valve block, control valve group includes the control assembly who changes the hydraulic oil flow through changing the oil circuit, just oil inlet P, oil return T, first hydraulic fluid port A and second hydraulic fluid port B are through two liang of intercommunications of control assembly.
Through adopting above-mentioned technical scheme, the different oil circuit of valve unit control, and the variation in size of the flow that different oil circuit corresponds, when oil inlet P intercommunication oil return opening T, the hydro-cylinder is out of work, when oil inlet P intercommunication second hydraulic fluid port B, when first hydraulic fluid port A intercommunication oil return opening T, the rodless chamber oil feed of hydro-cylinder, the pole chamber of hydro-cylinder produces oil, make the hydro-cylinder be in the state that the worker that the speed is slower advances, when oil inlet P intercommunication first hydraulic fluid port A, when second hydraulic fluid port B intercommunication oil return opening T, the oil output of control module increase second hydraulic fluid port B, thereby improve the speed that the hydro-cylinder moved back, make the hydro-cylinder can accomplish the process that the worker advanced and moved back fast, and improve work efficiency.
Optionally, the control assembly includes a reversing unit and a logic flow control unit, and the reversing unit is communicated with the oil inlet P, the oil return port T, the first oil port a and the second oil port B through the logic flow control unit.
By adopting the technical scheme, the reversing unit controls the connection relation of the oil inlet P, the oil return port T, the first oil port A and the second oil port B, and meanwhile, the logic flow control unit controls the flow line and flow of hydraulic oil according to the selection of the reversing unit, so that the reversing unit and the logic flow control unit jointly act to complete the required working state of the oil cylinder.
Optionally, the reversing unit includes a three-position four-way electromagnetic reversing valve and a two-position two-way electromagnetic reversing valve, and the logic flow control unit includes a first logic valve, a second logic valve, a third logic valve, a fourth logic valve, a fifth logic valve and a sixth logic valve;
the oil inlet P is communicated with an A111 of the first logic valve, an A121 of the second logic valve, an A131 of the third logic valve, a P1 of the two-position two-way electromagnetic directional valve and a P2 of the three-position four-way electromagnetic directional valve at the same time;
the oil return port T is communicated with A122 of the second logic valve, A141 of the fourth logic valve, 151 of the fifth logic valve, A161 of the sixth logic valve and T2 of the three-position four-way electromagnetic directional valve;
the first oil port A is communicated with A132 of the third logic valve and A142 of the fourth logic valve;
the second port B is communicated with A112 of the first logic valve, A152 of the fifth logic valve and A162 of the sixth logic valve;
the T1 of the two-position two-way electromagnetic directional valve is communicated with the B121 of the second logic valve, and the A1 of the two-position two-way electromagnetic directional valve is communicated with an oil discharge port L2;
the A2 of the three-position, four-way solenoid directional valve communicates with the B111 of the first logic valve and the B141 of the fourth logic valve, and the B2 of the three-position, four-way solenoid directional valve communicates with the B131 of the third logic valve, the B151 of the fifth logic valve and the B161 of the sixth logic valve.
By adopting the technical scheme, when the oil cylinder is in a non-working state, gears of the three-position four-way electromagnetic reversing valve are changed, so that P2 is communicated with A2 and B2 at the same time, A1 on the two-position two-way electromagnetic reversing valve is communicated with T1, at the moment, an oil inlet P can be directly communicated with B111, B131, B141, B151 and B161, a channel is closed by the first logic valve, the third logic valve, the fourth logic valve, the fifth logic valve and the sixth logic valve, B121 of the second logic valve is communicated with the oil unloading port L2, the channel where the second logic valve is located is opened, the oil inlet P is communicated with the oil return port T through the second logic valve, and hydraulic oil cannot enter the oil cylinder;
when the oil cylinder is in working, P2 on the three-position four-way electromagnetic directional valve is communicated with B2, A2 is communicated with T2, P1 and T1 of the two-position two-way electromagnetic directional valve are communicated, so that the second logic valve, the third logic valve, the fifth logic valve and the sixth logic valve are closed, the first logic valve and the fourth logic valve are opened, an oil inlet P is communicated with a second oil port B through the first logic valve, the first oil port A is communicated with an oil return port T, oil enters a rodless cavity of the oil cylinder, and oil exits from a rod cavity of the oil cylinder;
when the oil cylinder fast moves back, P2 on the three-position four-way electromagnetic directional valve is communicated with A2, B2 is communicated with T2, P1 and T1 of the two-position two-way electromagnetic directional valve are communicated, so that the first logic valve, the second logic valve and the fourth logic valve are closed, the third logic valve, the fifth logic valve and the sixth logic valve are opened, an oil inlet P is communicated with the first oil port A through the third logic valve, the second oil port B is communicated with an oil return port T through the fifth logic valve and the sixth logic valve at the same time, oil enters a rod cavity of the oil cylinder, and double oil outlet is realized in a rodless cavity of the oil cylinder.
Optionally, an overflow valve for communicating the oil inlet P and the oil return port is arranged between the oil inlet P and the oil return port, the overflow valve is located between the oil inlet and the control assembly, and the overflow valve and the control assembly are arranged in parallel.
By adopting the technical scheme, the overflow valve plays a safety protection role, and when the oil pressure is too high or external force impact is received, the pressure higher than a set value is discharged by the overflow valve, so that the whole hydraulic system is protected.
In a second aspect, the present application provides an oil supply valve group, which adopts the following technical scheme:
an oil supply valve group is arranged on a valve block and comprises a high-pressure oil port PH and a low-pressure oil port PL which are communicated with an oil inlet P, wherein a pressure regulating assembly is arranged on the low-pressure oil port PL, and the low-pressure oil port PL is communicated with an oil return port T through the pressure regulating assembly.
By adopting the technical scheme, when hydraulic oil is introduced into the hydraulic system, high-pressure oil port PH introduces high-pressure small-flow hydraulic oil to oil inlet P, low-pressure oil port PL simultaneously introduces low-pressure large-flow hydraulic oil to oil inlet P, make hydraulic system be full of hydraulic oil fast, make hydraulic system actuating mechanism feed fast, when pressure in the hydraulic system reaches the pressure value that pressure regulating assembly set for, pressure regulating assembly makes low-pressure oil port PL directly communicate oil return port T, hydraulic system is supplied with only by high-pressure small-flow hydraulic oil, from this the large-flow hydraulic oil of low pressure directly flows from oil return port T, the large-flow pump motor of low pressure is unloaded, reduce the electric energy loss, play energy-conserving effect.
Optionally, the pressure regulating assembly includes a check valve and an unloading valve which are arranged in parallel, the low-pressure oil port PL is communicated with the oil inlet P through the check valve, the low-pressure oil port PL is communicated with the oil return port T through the unloading valve, and a control piston of the unloading valve is communicated with the oil inlet P.
By adopting the technical scheme, when the pressure of the low-pressure large-flow hydraulic oil and the high-pressure small-flow hydraulic oil after confluence is less than the rated pressure of the unloading valve, the unloading valve is closed, the low-pressure large-flow hydraulic oil passes through the one-way valve and is converged with the high-pressure small-flow hydraulic oil for supplying to a hydraulic system, and when the confluence pressure is greater than the rated pressure of the unloading valve, the unloading valve is opened, so that the low-pressure large-flow hydraulic oil directly flows into the oil return port T through the unloading valve, and the load is unloaded through the low-pressure oil port PL.
Optionally, an oil discharge port L1 is formed in the valve block, and the oil discharge port L1 is communicated with a piston cavity of the unloading valve.
By adopting the technical scheme, when the pressure in the system is overlarge, the hydraulic oil in the unloading valve is unloaded through the oil unloading port L1, so that the unloading valve and the whole system are protected.
Optionally, an oil inlet detection hole MP, a first detection hole MA and a second detection hole MB are formed in the valve block, the oil inlet detection hole MP is communicated with the oil inlet P, the first detection hole MA is communicated with the first oil port a, and the second detection hole MB is communicated with the second oil port B.
Through adopting above-mentioned technical scheme, the pressure of each department in oil feed inspection hole MP, first inspection hole MA and the second inspection hole MB detecting system to protection valve piece and valves.
In summary, the present application includes at least one of the following beneficial technical effects:
1. the control valve group controls different oil paths, the flow rates corresponding to the different oil paths are different, and after the work feeding action is completed, the second oil port B quickly returns oil with a large flow rate, so that the quick return action is realized, and the working efficiency of the hydraulic system is improved;
2. the oil supply valve group can quickly feed hydraulic oil by adopting high-pressure and low-pressure double oil ways for supplying oil, and the hydraulic oil with low pressure and large flow can directly return to the oil tank through the one-way valve and the unloading valve, so that the motor of the low-pressure large-flow pump is in no-load state, the electric energy loss is reduced, and the energy-saving effect is good.
Drawings
Fig. 1 is a schematic diagram of a hydraulic system in a standby state.
Fig. 2 is a schematic diagram of a hydraulic system in a working state.
Fig. 3 is a schematic diagram of a hydraulic system in a fast-reverse state.
Description of reference numerals: 1. a valve block; 2. a one-way valve; 3. an unloading valve; 4. an overflow valve; 5. A three-position four-way electromagnetic directional valve; 6. a two-position two-way electromagnetic directional valve; 7. a first logic valve; 8. a second logic valve; 9. a third logic valve; 10. a fourth logic valve; 11. a fifth logic valve; 12. a sixth logic valve.
Detailed Description
The present application is described in further detail below with reference to figures 1-3.
The embodiment of the application discloses a control valve group and an oil supply valve group.
The broken line in the figure represents the control oil passage with a small flow rate, and the solid line in the figure represents the main oil passage with a large flow rate.
Referring to fig. 1, a control valve group and an oil supply valve group are arranged on the same valve block 1, and an oil inlet P, an oil return port T, a first oil port a and a second oil port B are formed in the valve block 1. The first oil port A is communicated with a rod cavity of the oil cylinder, and the second oil port B is communicated with a rodless cavity of the oil cylinder. The hydraulic oil enters through the oil inlet P, sequentially passes through the oil supply valve group and the control valve group, is communicated with the first oil port A or the second oil port B under the selection of the control valve group, and then flows back to the oil return port T through the control valve group again from the second oil port B or the first oil port A, so that the circulation of the hydraulic oil is completed.
The oil supply valve group comprises a high-pressure oil port PH and a low-pressure oil port PL, and the high-pressure oil port PH and the low-pressure oil port PL are converged to form an oil inlet P. The oil supply valve group further comprises a pressure regulating assembly arranged on the low-pressure oil port PL, and the low-pressure oil port is connected with the oil return port T through the pressure regulating assembly.
The pressure regulating assembly comprises a check valve 2 and an unloading valve 3 which are fixed on the valve block 1 in parallel, the low-pressure oil port PL is communicated with the high-pressure oil port PH through the check valve 2, and the check valve 2 enables hydraulic oil to flow towards the high-pressure oil port PH from the low-pressure oil port PL but not flow towards the low-pressure oil port PL from the high-pressure oil port PH.
The low pressure port PL communicates with the oil return port T through the unloading valve 3, an oil inlet P formed by the confluence of the high pressure port PH and the low pressure port PL communicates with the control piston of the unloading valve 3, a piston chamber of the unloading valve 3 in which the control piston is provided communicates with an oil discharge port L1, and an oil discharge port L1 is opened in the valve block 1. When the pressure in the piston cavity is too high, the oil discharge port L1 can be discharged, reducing the internal pressure, thereby protecting the unloading valve 3 and the hydraulic system.
The low-pressure oil port PL pumps low-pressure large-flow hydraulic oil into the hydraulic system through the pump, and the high-pressure oil port PH also pumps high-pressure small-flow hydraulic oil into the hydraulic system through the pump. And setting the rated pressure of the unloading valve 3, and when the external force is greater than the rated pressure, moving a control piston of the unloading valve 3 and opening an oil way where the unloading valve 3 is located, or closing the oil way.
When the pressure of the oil inlet P is smaller than the rated pressure of the unloading valve 3, the unloading valve 3 is closed, and the low-pressure high-flow hydraulic oil is converged with the high-pressure low-flow hydraulic oil through the check valve 2 and flows to the control valve group. When the pressure of the oil inlet P is greater than the rated pressure of the unloading valve 3, the unloading valve 3 is opened, the low-pressure large-flow hydraulic oil directly flows into the oil return port T from the low-pressure oil port PL through the unloading valve 3, so that the pump with the low-pressure large-flow pump is in no-load, the energy consumption is reduced, and at the moment, the high-pressure oil port PH independently supplies the high-pressure small-flow hydraulic oil to the system, so that the system works.
Hydraulic oil is pumped into the hydraulic system through the high-pressure oil circuit and the low-pressure oil circuit of the oil supply valve group, so that the hydraulic oil can be quickly filled into the hydraulic system, the execution mechanism can quickly feed, and the unloading valve 3 and the one-way valve 2 are matched to reduce energy consumption.
In order to protect the hydraulic system and reduce the damage of the hydraulic system caused by overlarge pressure, an overflow valve 4 fixed on the valve block 1 is arranged between the oil inlet P and the oil return port T, and the overflow valve 4 is connected with the control valve group in parallel. When the internal pressure of the hydraulic system is too high, the overflow valve 4 discharges the pressure higher than the set value, so that the whole hydraulic system is protected.
When hydraulic oil flows to the control valve group through the oil supply valve group, the control valve group controls a flow line of the hydraulic oil, and the control valve group comprises a control assembly which changes the flow of the hydraulic oil by changing an oil way. The control assembly comprises a reversing unit and a logic flow control unit, and the reversing unit is communicated with the oil inlet P, the oil return port T, the first oil port A and the second oil port B through the logic flow control unit.
The reversing unit comprises a three-position four-way electromagnetic reversing valve 5 and a two-position two-way electromagnetic reversing valve 6 which are fixed on the valve block 1, and the logic flow control unit comprises a first logic valve 7, a second logic valve 8, a third logic valve 9, a fourth logic valve 10, a fifth logic valve 11 and a sixth logic valve 12 which are fixed on the valve block 1.
The oil inlet P is simultaneously communicated with A111 of the first logic valve 7, A121 of the second logic valve 8, A131 of the third logic valve 9, P1 of the two-position two-way electromagnetic directional valve 6 and P2 of the three-position four-way electromagnetic directional valve 5;
the oil return port T communicates with a122 of the second logic valve 8, a141 of the fourth logic valve 10, a151 of the fifth logic valve 11, a161 of the sixth logic valve 12, and T2 of the three-position, four-way electromagnetic directional valve 5;
the first port a communicates with a132 of the third logic valve 9 and a142 of the fourth logic valve 10;
the second port B communicates with a112 of the first logic valve 7, a152 of the fifth logic valve 11 and a162 of the sixth logic valve 12;
the T1 of the two-position two-way electromagnetic directional valve 6 is communicated with the B121 of the second logic valve 8, and the A1 of the two-position two-way electromagnetic directional valve 6 is communicated with an oil discharge port L2;
the a2 of the three-position, four-way electromagnetic directional valve 5 communicates with the B111 of the first logic valve 7 and the B141 of the fourth logic valve 10, and the B2 of the three-position, four-way electromagnetic directional valve 5 communicates with the B131 of the third logic valve 9, the B151 of the fifth logic valve 11, and the B161 of the sixth logic valve 12.
In the control valve group, the oil passages of B111, B121, B131, B141, B151, B161 and L2 are control oil passages, and the oil passages are main oil passages through which hydraulic oil flows.
Referring to fig. 1, when the hydraulic system is in a standby state, the three-position, four-way electromagnetic directional valve 5 is in the middle gear position, so that P2 is communicated with a2 and B2 at the same time, and the oil inlet P can be directly communicated with B111, B131, B141, B151 and B161, so that the first logic valve 7, the third logic valve 9, the fourth logic valve 10, the fifth logic valve 11 and the sixth logic valve 12 close the passages. And the A1 on the two-position two-way electromagnetic directional valve 6 is communicated with the T1, and the B121 of the second logic valve 8 is communicated with the oil outlet L2, so that the channel where the second logic valve 8 is located is opened. Therefore, the oil inlet P is communicated with the oil return port T through the second logic valve 8, so that the interior of the oil cylinder is not communicated with the hydraulic oil and is in a standby state.
Referring to fig. 2, when the hydraulic system is in a power-on state, the three-position, four-way electromagnetic directional valve 5 is shifted such that P2 communicates with B2 and a2 communicates with T2 such that the oil inlet P can communicate directly with B131, B151 and B161 such that the third logic valve 9, the fifth logic valve 11 and the sixth logic valve 12 close the passages and B111 and B141 communicate directly with the oil return T such that the first logic valve 7 and the fourth logic valve 10 passages are opened. Simultaneously, the two-position two-way electromagnetic directional valve 6 shifts, so that P1 is communicated with T1, the oil inlet P is directly communicated with B121, and the second logic valve 8 closes the channel.
Therefore, the oil inlet P is communicated with the second oil port B through the first logic valve 7, the first oil port A is communicated with the oil return port T through the fourth logic valve 10, so that oil enters the rodless cavity of the oil cylinder, oil exits from the rod cavity, and the oil cylinder is in a working-in state.
Referring to fig. 3, when the hydraulic system is in a retracted state after completion of machining, the three-position, four-way electromagnetic directional valve 5 is shifted such that P2 communicates with a2, B2 communicates with T2, the oil inlet P can communicate directly with B111 and B141, so that the first logic valve 7 and the fourth logic valve 10 are closed, and B131, B151, and B161 communicate directly with the oil return port T, so that the third logic valve 9, the fifth logic valve 11, and the sixth logic valve 12 are opened. Simultaneously, the two-position two-way electromagnetic directional valve 6 shifts, so that P1 is communicated with T1, the oil inlet P is directly communicated with B121, and the second logic valve 8 closes the channel.
Therefore, the oil inlet P is communicated with the first oil port A through the third logic valve 9, the second oil port B is communicated with the oil return port T through the fifth logic valve 11 and the sixth logic valve 12 at the same time, so that oil is fed into a rod cavity of the oil cylinder, and double oil is discharged from a rodless cavity of the oil cylinder, and the oil cylinder can return quickly.
The quick-advancing, working-advancing and quick-retreating actions of the hydraulic system are realized through the oil supply valve group and the control valve group, the working efficiency is improved, the small-flow electromagnetic valve is combined with the large-flow logic valve, the small-flow control effect is realized, and meanwhile, the one-way valve 2 and the unloading valve 3 are matched for use, so that the energy consumption is reduced.
In addition, an oil inlet detection hole MP, a first detection hole MA and a second detection hole MB are formed in the valve block 1, the oil inlet detection hole MP is communicated with the oil inlet P, the first detection hole MA is communicated with the first oil port A, and the second detection hole MB is communicated with the second oil port B. The oil inlet detection hole MP, the first detection hole MA and the second detection hole MB are used for detecting the pressure at each position in the system, so that the valve block 1, the control valve group and the oil supply valve group are protected.
The implementation principle of a control valve group and an oil supply valve group in the embodiment of the application is as follows: the hydraulic system is quickly filled by converging high-pressure small-flow hydraulic oil and low-pressure large-flow hydraulic oil, and the flow pipelines and the flow in the hydraulic system are controlled by matching with the control valve group, so that the actions of quick feeding, working feeding and quick retreating of the hydraulic system are realized.
The above embodiments are preferred embodiments of the present application, and the protection scope of the present application is not limited by the above embodiments, so: all equivalent changes made according to the structure, shape and principle of the present application shall be covered by the protection scope of the present application.
Claims (8)
1. The utility model provides a valve unit sets up on valve block (1), be equipped with oil inlet P, oil return port T and be used for communicateing the first hydraulic fluid port A that the hydro-cylinder has the pole chamber and be used for communicateing the second hydraulic fluid port B in hydro-cylinder rodless chamber on valve block (1), its characterized in that: the control valve group comprises a control assembly for changing the flow of hydraulic oil by changing an oil way, and the oil inlet P, the oil return port T, the first oil port A and the second oil port B are communicated with each other through the control assembly.
2. A control valve assembly as claimed in claim 1, wherein: the control assembly comprises a reversing unit and a logic flow control unit, and the reversing unit is communicated with the oil inlet P, the oil return port T, the first oil port A and the second oil port B through the logic flow control unit.
3. A control valve assembly as claimed in claim 1, wherein: the reversing unit comprises a three-position four-way electromagnetic reversing valve (5) and a two-position two-way electromagnetic reversing valve (6), and the logic flow control unit comprises a first logic valve (7), a second logic valve (8), a third logic valve (9), a fourth logic valve (10), a fifth logic valve (11) and a sixth logic valve (12);
the oil inlet P is communicated with A111 of the first logic valve (7), A121 of the second logic valve (8), A131 of the third logic valve (9), P1 of the two-position two-way electromagnetic directional valve (6) and P2 of the three-position four-way electromagnetic directional valve (5) at the same time;
the oil return port T is communicated with A122 of the second logic valve (8), A141 of the fourth logic valve (10), A151 of the fifth logic valve (11), A161 of the sixth logic valve (12) and T2 of the three-position four-way electromagnetic directional valve (5);
the first oil port A is communicated with A132 of the third logic valve (9) and A142 of the fourth logic valve (10);
the second oil port B is communicated with A112 of the first logic valve (7), A152 of the fifth logic valve (11) and A162 of the sixth logic valve (12);
the T1 of the two-position two-way electromagnetic directional valve (6) is communicated with the B121 of the second logic valve (8), and the A1 of the two-position two-way electromagnetic directional valve (6) is communicated with an oil discharge port L2;
the A2 of the three-position four-way electromagnetic directional valve (5) is communicated with the B111 of the first logic valve (7) and the B141 of the fourth logic valve (10), and the B2 of the three-position four-way electromagnetic directional valve (5) is communicated with the B131 of the third logic valve (9), the B151 of the fifth logic valve (11) and the B161 of the sixth logic valve (12).
4. A control valve assembly as claimed in claim 1, wherein: an overflow valve (4) communicated with the oil inlet P and the oil return port is arranged between the oil inlet P and the oil return port, the overflow valve (4) is located between the oil inlet and the control assembly, and the overflow valve (4) and the control assembly are connected in parallel.
5. An oil supply valve group for supplying oil to a control valve group according to any one of claims 1 to 4, arranged on a valve block (1), characterized in that: the oil return device comprises a high-pressure oil port PH and a low-pressure oil port PL which are both communicated with an oil inlet P, wherein a pressure regulating assembly is arranged on the low-pressure oil port PL, and the low-pressure oil port PL is communicated with an oil return port T through the pressure regulating assembly.
6. An oil supply valve group according to claim 5, characterized in that: the pressure regulating assembly comprises a check valve (2) and an unloading valve (3) which are arranged in parallel, the low-pressure oil port PL is communicated with an oil inlet P through the check valve (2), the low-pressure oil port PL is communicated with an oil return port T through the unloading valve (3), and a control piston of the unloading valve (3) is communicated with the oil inlet P.
7. An oil supply valve group according to claim 6, characterized in that: an oil discharge port L1 is formed in the valve block (1), and the oil discharge port L1 is communicated with a piston cavity of the unloading valve (3).
8. An oil supply valve group according to claim 5, characterized in that: an oil inlet detection hole MP, a first detection hole MA and a second detection hole MB are formed in the valve block (1), the oil inlet detection hole MP is communicated with the oil inlet P, the first detection hole MA is communicated with the first oil port A, and the second detection hole MB is communicated with the second oil port B.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110681675.7A CN113586539A (en) | 2021-06-19 | 2021-06-19 | Control valve group and oil supply valve group |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110681675.7A CN113586539A (en) | 2021-06-19 | 2021-06-19 | Control valve group and oil supply valve group |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN113586539A true CN113586539A (en) | 2021-11-02 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110681675.7A Pending CN113586539A (en) | 2021-06-19 | 2021-06-19 | Control valve group and oil supply valve group |
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| CN (1) | CN113586539A (en) |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN202031895U (en) * | 2011-01-29 | 2011-11-09 | 马保庆 | Oil-way system of a mould locking oil cylinder |
| CN102748335A (en) * | 2012-07-02 | 2012-10-24 | 三一重型装备有限公司 | Hydraulic system and heading machine |
| CN104235091A (en) * | 2014-07-24 | 2014-12-24 | 江苏科技大学 | Hydraulic control system of anchor chain tension tester |
| CN210461214U (en) * | 2019-07-02 | 2020-05-05 | 江苏恒立液压科技有限公司 | Super-large flow hydraulic execution system |
| CN211778269U (en) * | 2019-09-25 | 2020-10-27 | 中船重型装备有限公司 | Rotary three-stage speed regulation hydraulic control loop of shield machine screw machine |
-
2021
- 2021-06-19 CN CN202110681675.7A patent/CN113586539A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN202031895U (en) * | 2011-01-29 | 2011-11-09 | 马保庆 | Oil-way system of a mould locking oil cylinder |
| CN102748335A (en) * | 2012-07-02 | 2012-10-24 | 三一重型装备有限公司 | Hydraulic system and heading machine |
| CN104235091A (en) * | 2014-07-24 | 2014-12-24 | 江苏科技大学 | Hydraulic control system of anchor chain tension tester |
| CN210461214U (en) * | 2019-07-02 | 2020-05-05 | 江苏恒立液压科技有限公司 | Super-large flow hydraulic execution system |
| CN211778269U (en) * | 2019-09-25 | 2020-10-27 | 中船重型装备有限公司 | Rotary three-stage speed regulation hydraulic control loop of shield machine screw machine |
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