CN116733794B - Load self-adaptive rotary buffer valve and hydraulic system - Google Patents
Load self-adaptive rotary buffer valve and hydraulic system Download PDFInfo
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- CN116733794B CN116733794B CN202310684644.6A CN202310684644A CN116733794B CN 116733794 B CN116733794 B CN 116733794B CN 202310684644 A CN202310684644 A CN 202310684644A CN 116733794 B CN116733794 B CN 116733794B
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- 239000003921 oil Substances 0.000 claims abstract description 364
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 31
- 230000001502 supplementing effect Effects 0.000 claims abstract description 28
- 238000013016 damping Methods 0.000 claims description 52
- 230000007246 mechanism Effects 0.000 claims description 19
- 230000003044 adaptive effect Effects 0.000 claims description 7
- 229910000831 Steel Inorganic materials 0.000 claims description 6
- 239000010959 steel Substances 0.000 claims description 6
- 230000035939 shock Effects 0.000 claims 1
- 238000000034 method Methods 0.000 description 6
- 230000003111 delayed effect Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 229920006395 saturated elastomer Polymers 0.000 description 1
- 238000012216 screening Methods 0.000 description 1
Classifications
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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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
-
- 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
-
- 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
- F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a load self-adaptive rotary buffer valve and a hydraulic system, wherein the load self-adaptive rotary buffer valve comprises: the oil inlet P is used for connecting an oil supply pipeline of hydraulic oil; the oil return port T is used for connecting a hydraulic oil tank; the working oil port A is used for connecting one end of the rotary motor; the working oil port B is used for connecting the other end of the rotary motor; the P port of the oil inlet control valve is connected with the oil inlet P; the P1 port of the oil inlet control valve is connected with a hydraulic oil tank through a pressure equalizing valve; the inlet A of the oil inlet control valve is respectively connected with the working oil port A, the inlet of the first oil supplementing overflow valve and the inlet A of the oil return control valve; the port B of the oil inlet control valve is respectively connected with the working oil port B, the inlet of the second oil supplementing overflow valve and the port B of the oil return control valve; the outlet of the first oil supplementing overflow valve, the outlet of the second oil supplementing overflow valve and the T port of the oil return control valve are respectively connected with the oil return port T. The invention has the characteristics that the control section of the rotary control handle is not affected by load, the stop impact is small, and the like.
Description
Technical Field
The invention belongs to the technical field of hydraulic valves, and particularly relates to a load self-adaptive rotary buffer valve and a hydraulic system.
Background
Engineering machinery with large inertia slewing mechanisms such as an automobile crane, a crawler crane and a lorry-mounted crane has inconsistent slewing inertia due to different length and hoisting weight of a lifting arm, and can cause small control interval of a slewing control handle and large slewing swing caused by stopping impact under the working conditions of a middle and long arm and heavy load, thereby seriously affecting the operability and safety of the whole machine operation.
Disclosure of Invention
In order to solve the defects in the prior art, the invention provides a load self-adaptive rotary buffer valve and a hydraulic system, and the load self-adaptive rotary buffer valve has the characteristics that the control section of a rotary control handle is not affected by load, the stop impact is small and the like.
In order to achieve the above purpose, the technical scheme adopted by the invention is as follows:
In a first aspect, there is provided a load adaptive swing trim valve comprising: the oil inlet P is used for connecting an oil supply pipeline of hydraulic oil; the oil return port T is used for connecting a hydraulic oil tank; the working oil port A is used for connecting one end of the rotary motor; the working oil port B is used for connecting the other end of the rotary motor; the P port of the oil inlet control valve is connected with the oil inlet P; the P1 port of the oil inlet control valve is connected with a hydraulic oil tank through a pressure equalizing valve; the inlet A of the oil inlet control valve is respectively connected with the working oil port A, the inlet of the first oil supplementing overflow valve and the inlet A of the oil return control valve; the port B of the oil inlet control valve is respectively connected with the working oil port B, the inlet of the second oil supplementing overflow valve and the port B of the oil return control valve; the outlet of the first oil supplementing overflow valve, the outlet of the second oil supplementing overflow valve and the T port of the oil return control valve are respectively connected with the oil return port T.
Further, the method further comprises the following steps: a control oil port a used for connecting with a pilot handle oil port for controlling the right rotation; the control oil port b is used for connecting with a pilot handle oil port for controlling left rotation; the control oil port a and the control oil port b are respectively connected with two control oil ports of the oil inlet control valve.
Further, the method further comprises the following steps: the inlet of the first electromagnetic directional valve is connected with the oil inlet P, the outlet of the first electromagnetic directional valve is connected with the shuttle valve through a fifth one-way valve, and the outlet of the first electromagnetic directional valve is connected with the hydraulic oil tank through a soft overflow valve and a second electromagnetic directional valve; and the shuttle valve is connected between the working oil port A and the working oil port B.
Further, when the pilot handle is not operated, the control oil port a and the control oil port b have no pressure, and the oil inlet control valve and the oil return control valve keep the middle position and do not change direction; the first electromagnetic directional valve and the second electromagnetic directional valve are not electrified; the hydraulic oil enters the pressure equalizing valve through the P1 port of the oil inlet control valve, and returns to the hydraulic oil tank through the pressure equalizing valve.
Further, when the crane hangs a heavy object, if the steel wire rope is not vertical to the heavy object, the first electromagnetic directional valve is electrified, the working oil port A and the working oil port B are communicated with the oil inlet P through the first electromagnetic directional valve, and the centering of the steel wire rope and the heavy object is realized.
Further, an Lsa port of the oil inlet control valve is respectively connected with the first gap damper, the first one-way valve and the third one-way valve through the first damper; the third one-way valve is connected with a spring cavity of the pressure equalizing valve through a third damping and connected with a hydraulic oil tank through a fourth damping; the third one-way valve is also connected with a second damping, a second clearance damping and a second one-way valve through a fourth one-way valve; the second damping is connected with an Lsb port of the oil inlet control valve; the sa port of the oil return control valve is connected with the first clearance damping and the first one-way valve, and the sb port of the oil return control valve is connected with the second clearance damping and the second one-way valve.
Further, when the pilot handle is controlled to rotate to the right, the pressure of the control oil port a is gradually increased, at the moment, the oil inlet control valve is gradually reversed, the throttle opening from the oil inlet P to the P1 port of the oil inlet control valve is gradually closed to be closed, the throttle opening from the oil inlet P to the working oil port A is gradually increased to be fully opened, the loop between the ls a port of the oil inlet control valve and the oil return port T is cut off, the ls B port of the oil inlet control valve is communicated with the oil return port T, the B port of the oil inlet control valve is closed, the A port of the oil inlet control valve establishes pressure, the pressure of the working oil port A is fed back to the sa port of the oil return control valve through the ls a port of the oil inlet control valve, the first damping, the first clearance damping and the first one-way valve, the oil return control valve is pushed to reverse, the B port of the oil return control valve is gradually opened through the T port of the oil return control valve, the A port of the oil return control valve is closed, and the pressure of the working oil port A is fed back to the spring cavity of the pressure balance valve through the ls a port of the oil inlet control valve, the third one-way valve and the third damping valve is closed; at the moment, hydraulic oil of the oil inlet P is output to the working oil port A through the oil inlet control valve and is used for controlling the rotary mechanism to rotate rightwards; the hydraulic oil of the working oil port B enters the hydraulic oil tank through the oil return control valve.
Further, when the pressure at the working oil port A exceeds a set value, the corresponding first oil supplementing overflow valve is opened, and the pressure of the system is prevented from exceeding the set value.
Further, when the rightward rotation of the slewing mechanism is stopped, the pressure of the working oil port A is reduced, and at the moment, hydraulic oil is supplemented to the working oil port A through the first oil supplementing overflow valve, so that the slewing mechanism is prevented from sucking air.
Further, when the turning mechanism stops turning rightwards, the oil return control valve is closed, the pressure of the working oil port B rises, the second electromagnetic directional valve is closed in a delayed mode, and the pressure of the working oil port B is unloaded through the shuttle valve, the fifth one-way valve, the soft overflow valve and the second electromagnetic directional valve to avoid stopping impact.
The second aspect provides a load-adaptive rotary hydraulic system, which comprises the load-adaptive rotary buffer valve in the first aspect, wherein an oil inlet P of the load-adaptive rotary buffer valve is connected with an outlet of a quantitative pump through an oil supply pipeline, and an oil return port T of the load-adaptive rotary buffer valve is connected with a hydraulic oil tank; the working oil port A of the load self-adaptive rotary buffer valve is connected with the port A of the rotary motor; the working oil port B of the load self-adaptive rotary buffer valve is connected with the port B of the rotary motor; the control oil port a of the load self-adaptive rotation buffer valve is connected with the pilot handle oil port for controlling the right rotation; the control oil port b of the load self-adaptive rotation buffer valve is connected with the pilot handle oil port for controlling the left rotation.
Compared with the prior art, the invention has the beneficial effects that: the invention is connected with an oil inlet P through a P port of an oil inlet control valve; the P1 port of the oil inlet control valve is connected with a hydraulic oil tank through a pressure equalizing valve; the inlet A of the oil inlet control valve is respectively connected with the working oil port A, the inlet of the first oil supplementing overflow valve and the inlet A of the oil return control valve; the port B of the oil inlet control valve is respectively connected with the working oil port B, the inlet of the second oil supplementing overflow valve and the port B of the oil return control valve; the outlet of the first oil supplementing overflow valve, the outlet of the second oil supplementing overflow valve and the T port of the oil return control valve are respectively connected with the oil return port T, so that the aim that the control section of the rotary control handle of the large-inertia rotary mechanism is not influenced by load is fulfilled, and the device has the characteristics of small stop impact and the like.
Drawings
FIG. 1 is a schematic diagram of a load adaptive swing damper and hydraulic system provided by an embodiment of the present invention;
FIG. 2 is a schematic cross-sectional view of a load adaptive rotary damping valve according to an embodiment of the present invention;
in the figure: 1. a fixed displacement pump; 2. an oil feed control valve; 3. an oil return control valve; 4. a first damping; 5. a second damping; 6. a first gap damping; 7. a second gap damping; 8. a first one-way valve; 9. a second one-way valve; 10. a third one-way valve; 11. a fourth one-way valve; 12. a third damping; 13. fourth damping; 14. a pressure equalization valve; 15. a first oil-compensating overflow valve; 16. a second oil-compensating overflow valve; 17. a first electromagnetic directional valve; 18. a second electromagnetic directional valve; 19. a soft overflow valve; 20. a fifth check valve; 21. a shuttle valve; 22. a rotary motor; 23. a left end cover; 24. a right end cover; 25. and a valve body.
Detailed Description
The invention is further described below with reference to the accompanying drawings. The following examples are only for more clearly illustrating the technical aspects of the present invention, and are not intended to limit the scope of the present invention.
It should be noted that, in the description of the present invention, the directions or positional relationships indicated by the terms "front", "rear", "left", "right", "upper", "lower", "inner", "outer", etc. are based on the directions or positional relationships shown in the drawings, are merely for convenience of describing the present invention and do not require that the present invention must be constructed and operated in a specific direction, and thus should not be construed as limiting the present invention. The terms "front", "back", "left", "right", "upper", "lower" as used in the description of the present invention refer to directions in the drawings, and the terms "inner", "outer" refer to directions toward or away from the geometric center of a particular component, respectively.
Embodiment one:
as shown in fig. 1 and 2, the load adaptive swing buffer valve includes: the hydraulic oil filling system comprises an oil inlet control valve 2, an oil return control valve 3, a first damping 4, a second damping 5, a first clearance damping 6, a second clearance damping 7, a first one-way valve 8, a second one-way valve 9, a third one-way valve 10, a fourth one-way valve 11, a third damping 12, a fourth damping 13, a pressure equalization valve 14, a first oil supplementing overflow valve 15, a second oil supplementing overflow valve 16, a first electromagnetic directional valve 17, a second electromagnetic directional valve 18, a soft overflow valve 19, a fifth one-way valve 20 and a shuttle valve 21.
The high-pressure oil from the constant delivery pump 1 is connected with the P port of the oil inlet control valve 2 through the oil inlet P of the load self-adaptive rotary buffer valve, and is also connected with the first electromagnetic directional valve 17. The port A of the oil inlet control valve 2 is connected with the port A of the rotary motor 22 through a working oil port A, and the port B of the oil inlet control valve 2 is connected with the port B of the rotary motor 22 through a working oil port B; 2T ports of the oil inlet control valve 2 are connected with an oil return port T of the load self-adaptive rotary buffer valve; the Lsa port of the oil inlet control valve 2 is connected with the sa port of the oil return control valve 3 after passing through the first damping 4, the first clearance damping 6 and the first one-way valve 8, and meanwhile, the Lsa port of the oil inlet control valve 2 is connected with a spring cavity of the pressure equalizing valve 14 through the third one-way valve 10 and the third damping 12; the Lsb port of the oil inlet control valve 2 is connected with the sb port of the oil return control valve 3 after passing through the second damping 5, the second clearance damping 7 and the second one-way valve 9, and the Lsa port of the oil inlet control valve 2 is connected with the spring cavity of the pressure equalizing valve 14 through the fourth one-way valve 11 and the third damping 12; the P1 port of the oil inlet control valve 2 is connected with one end of the pressure equalizing valve 14; the T port of the oil return control valve 3 is connected with the T port of the load self-adaptive rotary buffer valve, the A port of the oil return control valve 3 is connected with the A port of the rotary motor 22 through a working oil port A, and the B port of the oil return control valve 3 is connected with the B port of the rotary motor 22 through a working oil port B; the other end of the pressure equalizing valve 14 is connected with an oil return port T of the load self-adaptive rotary buffer valve, and a spring cavity of the pressure equalizing valve 14 is connected with the T port of the load self-adaptive rotary buffer valve through a third damping 12 and a fourth damping 13; one end of the first oil supplementing overflow valve 15 is connected with an A port of the rotary motor 22 through a working oil port A, and the other end of the first oil supplementing overflow valve is connected with a T port of the load self-adaptive rotary buffer valve; one end of the second oil compensating overflow valve 16 is connected with a port B of the rotary motor 22 through a working oil port B, and the other end is connected with a port T of the load self-adaptive rotary buffer valve; two oil ports of the rotary motor 22 are respectively connected with two ends of the shuttle valve 21, and high pressure screened by the shuttle valve 21 is respectively connected with the first electromagnetic directional valve 17 and the soft overflow valve 19 after passing through the fifth one-way valve 20; one end of the soft overflow valve 19 is connected with the fifth one-way valve 20 and the first electromagnetic directional valve 17, and the other end is connected with the second electromagnetic directional valve 18; the other end of the second electromagnetic directional valve 18 is connected with an oil return port T of the load self-adaptive rotary buffer valve.
The control oil port a of the load self-adaptive rotation buffer valve is connected with the pilot handle oil port for controlling the right rotation, and the control oil port b is connected with the pilot handle oil port for controlling the left rotation.
When the rotary pilot handle is not operated, the control oil port a and the control oil port b of the load self-adaptive rotary buffer valve have no pressure, and the oil inlet control valve 2 and the oil return control valve 3 keep the middle position and do not change direction; the solenoid valves of the first electromagnetic directional valve 17 and the second electromagnetic directional valve 18 are not energized. The oil from the metering pump 1 passes through the P1 port of the oil inlet control valve 2 to the pressure equalizing valve 14, and the pressure equalizing valve 14 is opened to return oil.
When the crane hangs a weight and the steel wire rope is not vertical to the weight, the first electromagnetic directional valve 17 is electrified to enable the port A and the port B of the rotary motor 22 to be communicated with the port P of the load self-adaptive rotary buffer valve through the first electromagnetic directional valve 17, so that the centering of the steel wire rope and the weight is realized.
When a pilot handle for controlling right rotation is gradually pushed, the pressure of a control oil port a of a load self-adaptive rotary buffer valve is gradually increased, at the moment, an oil inlet control valve 2 gradually commutates, a throttling port from a P port of the oil inlet control valve 2 to a P1 port of the oil inlet control valve 2 is gradually closed to be closed, a throttling port from the P port of the oil inlet control valve 2 to an A port of the oil inlet control valve 2 is gradually increased to be fully opened, a loop of an ls a port and a T port of the oil inlet control valve 2 is cut off, an Lsb port of the oil inlet control valve 2 is communicated with the T port, a B port of the oil inlet control valve 2 is closed, a port A of the oil inlet control valve 2 establishes pressure, an A port of a rotary motor 22 feeds back to a sa port of an oil return control valve 3 through an Lsa port of the oil inlet control valve 2, a first damping 4, a first clearance damping 6 and a first one-way valve 8, the oil return control valve 3 is gradually opened, the A port of the oil return control valve 3 is closed, and the A port of the oil return control valve 22 feeds back to the balance valve 12 through the oil inlet control valve 2, the third damping valve 14 and the balance valve 14; at this time, the oil of the constant delivery pump 1 pushes the rotary motor 22 to rotate rightwards through the oil inlet control valve 2, and the oil of the port B of the rotary motor 22 passes through the oil return control valve 3 to the port T.
In the rightward rotation process of the slewing mechanism, if the pressure of the opening A of the load self-adaptive slewing buffer valve is too high, the corresponding first oil supplementing overflow valve 15 is opened, and the pressure of the protection system cannot exceed a set value.
When the control handle for controlling the right rotation is reset gradually, the pressure of a control oil port a of the load self-adaptive rotation buffer valve is gradually reduced, at the moment, the oil inlet control valve 2 is gradually restored to the middle position from the reversing position, the orifice from the P port to the P1 port of the oil inlet control valve 2 is gradually increased, the orifice from the P port to the A port of the oil inlet control valve 2 is gradually closed to be closed, the Lsa of the oil inlet control valve 2 is communicated with the T port, the Lsb port of the oil inlet control valve 2 is communicated with the T port, the A port of the oil inlet control valve 2 is gradually reduced, the pressure of the A port of the rotation motor 22 is gradually reduced through the Lsa port of the oil inlet control valve 2, the first damping 4, the first clearance damping 6 and the first one-way valve 8, the pressure fed back to the sa port of the oil return control valve 3 is gradually reduced, the oil return control valve 3 is gradually changed to the middle position from the reversing position, the B port of the oil return control valve 3 is gradually closed to be closed through the orifice of the T port, the A port of the oil return valve 22 is simultaneously communicated with the T port, the pressure of the oil inlet of the rotation motor 22 is gradually reduced through the Lsa port of the third one-way valve 10 and the third damping 12 to the pressure equalizing valve 14, and the pressure of the pressure equalizing cavity is greatly reduced; at this time, the oil of the constant displacement pump 1 passes through the port P1 of the oil inlet control valve 2 to the pressure equalizing valve 14, and the pressure equalizing valve 14 is opened to return oil, and the rotation of the rotary motor 22 is stopped.
When the rotation of the rotation mechanism to the right is stopped, the rotation mechanism still rotates due to inertia, the pressure of the opening A of the rotation motor 22 is reduced, and at the moment, the oil is supplemented to the opening A of the rotation motor 22 through the first oil supplementing overflow valve 15, so that the rotation motor 22 is prevented from sucking air.
When the rotation of the rotary mechanism to the right is stopped, the rotary mechanism is still rotating due to inertia, the oil return control valve 3 is closed, the pressure of the port B of the rotary motor 22 is increased, the second electromagnetic directional valve 18 is closed in a delayed mode, the pressure of the port B of the rotary motor 22 is unloaded through the shuttle valve 21, the fifth one-way valve 20, the soft overflow valve 19 and the second electromagnetic directional valve 18, and stop impact is avoided.
The turning motor turns left to start and stop in the same manner as described above.
As shown in fig. 2, the load-adaptive rotary buffer valve is a sectional structure diagram of the load-adaptive rotary buffer valve, and the load-adaptive rotary buffer valve is composed of a left end cover 23, a right end cover 24 and a valve body 25, wherein the sectional diagram comprises an oil inlet control valve 2, an oil return control valve 3, a pressure equalizing valve 14, a first oil compensating overflow valve 15, a second oil compensating overflow valve 16, a first electromagnetic directional valve 17 and a second electromagnetic directional valve 18.
The left end cover 23 and the right end cover 24 are arranged at two ends of the valve body 25 through bolts, valve cores of the oil inlet control valve 2 and the oil return control valve 3 are arranged in valve core holes of the valve body 25, and the first oil supplementing overflow valve 15, the second oil supplementing overflow valve 16, the first electromagnetic directional valve 17 and the second electromagnetic directional valve 18 are arranged on the valve body 25 through threads.
When the control oil port a and the control oil port b of the load self-adaptive rotary buffer valve have no pressure, the oil inlet control valve 2 and the oil return control valve 3 keep the middle position and do not change direction; the solenoid valves of the first electromagnetic directional valve 17 and the second electromagnetic directional valve 18 are not energized. The oil in the P port of the oil inlet control valve 2 passes through the P1 port of the oil inlet control valve 2 to the pressure equalizing valve 14, and the pressure equalizing valve 14 moves upwards to open the oil return to the T port.
When the pressure of a control oil port a of an oil inlet control valve 2 of the load self-adaptive rotary buffer valve is gradually increased, a valve core of the oil inlet control valve 2 is gradually reversed to the right, a throttle port from a port P to a port P1 of the oil inlet control valve 2 is gradually closed to be closed, a throttle port from the port P to the port A is gradually increased to be fully opened, a loop of an Lsa port and a T port of the oil inlet control valve 2 is cut off, an Lsb port is communicated with the T port, a port B of the oil inlet control valve 2 is closed, a port A of the oil inlet control valve 2 establishes pressure, a port A of a rotary motor feeds back to a port sa of an oil return control valve 3 through the Lsa port of the oil inlet control valve 2, the oil return control valve 3 is moved to the right and reversed, a port B of the oil return control valve 3 is gradually opened through the T port oil return throttle, a port A of the oil return control valve 3 is closed, and simultaneously the port A of the rotary motor feeds back to an upper cavity of a pressure equalizing valve 14 through the Lsa port of the oil inlet control valve 2, and the opening of the pressure equalizing valve 14 is small; the oil in the P port of the oil inlet control valve 2 passes through the oil inlet control valve 2 to the A port, and the oil in the B port passes through the oil return control valve 3 to the T port.
When the pressure of the working oil port A of the load self-adaptive rotary buffer valve is too high, the corresponding first oil supplementing overflow valve 15 is opened, and the pressure of the system is prevented from exceeding a set value.
When the pressure of a control oil port a of the load self-adaptive rotary buffer valve is gradually reduced, the oil inlet control valve 2 gradually moves leftwards from a reversing position to return to the middle position, a throttle port from a port P to a port P1 of the oil inlet control valve 2 gradually increases, a throttle port from the port P to a port A gradually closes to be closed, an Lsa of the oil inlet control valve 2 is communicated with a port T, an Lsb port is communicated with the port T, the pressure of the port A of the rotary motor is gradually reduced, the pressure fed back to a port sa of the oil return control valve 3 through the Lsa of the oil inlet control valve 2 gradually reduces, the oil return control valve 3 gradually moves leftwards from the reversing position to the middle position, a port B of the oil return control valve 3 gradually closes to be closed through the port T oil return throttle port, meanwhile the pressure fed back to an upper cavity of the pressure equalizing valve 14 through the Lsa of the oil inlet control valve 2 gradually reduces, and the opening of the pressure equalizing valve 14 increases; at this time, the oil in the P of the oil inlet control valve 2 pushes the pressure equalizing valve 14 to move upwards through the P1 port of the oil inlet control valve 2, and opens the pressure equalizing valve 14 to return oil to the T port.
When the pressure of the port A is reduced due to inertia of the load self-adaptive rotary buffer valve, oil is supplemented to the port A through the first oil supplementing overflow valve 15, and suction is avoided.
When the pressure of the control oil port b of the oil inlet control valve 2 of the load self-adaptive rotary buffer valve is increased to be completely reversed, the pressure is reduced to be restored to the middle position, and the process is the same as that described above.
The oil inlet control valve 2 on the load self-adaptive rotary buffer valve adopts an open center structure, so that the flow rigidity during reversing is reduced, and the impact during reversing is small.
The pressure equalizing valve 14 is designed on the P-T oil way, so that the pressure difference at two ends of the throttling ports of P-A/B and P-T are approximately equal, the control flow of the rotary valve is only related to the area of the throttling groove and is not influenced by load pressure, the control interval during rotary heavy load is improved, the control interval is not changed under saturated flow, and the operability is better.
According to the invention, the load feedback cavity of the pressure equalizing valve 14 is connected with the T-port through the fourth damping 13, and when the load self-adaptive rotary buffer valve is in the middle position, the spring cavity of the pressure equalizing valve 14 is decompressed, so that the pressure holding of the load self-adaptive rotary buffer valve is avoided.
According to the invention, the valve core of the oil inlet control valve 2 is used for screening the load signal, the pressure of the load signal cavity in the middle position of the valve core can be released through the T port, only the load pressure of one cavity of the A port or the B port is fed back in the reversing process, and the other cavity is released through the T port, so that the flow error distribution caused by feeding back the pressure of the oil return port due to high impact pressure of the oil return port in the reversing process is avoided.
According to the invention, the oil inlet control valve is adopted to screen the oil inlet load pressure to control the opening of the throttling groove of the oil return control valve, so that the self-adaptive control of different inertial loads is realized, the rotation stopping operability is better, and the operation interval is larger.
According to the invention, the pressure of the rotary oil inlet is controlled to be opened and closed by the one-way clearance damping formed by the first clearance damping 6 (the second clearance damping 7) and the first one-way valve 8 (the second one-way valve 9), when the pressure of the rotary oil inlet fluctuates, the clearance damping can filter the pressure fluctuation, and the one-way valve can realize the quick closing of the valve core.
According to the invention, the soft overflow valve 19 and the second electromagnetic directional valve 18 are adopted to reduce the stopping impact of the rotation, when the self-adaptive rotation mechanism starts to stop, the second electromagnetic directional valve 18 is closed in a delayed mode, at the moment, the return oil impact pressure of the rotation is relieved through the soft overflow valve 19, when the rotation mechanism speed is high, the pressure of the soft overflow valve 19 is high, and when the rotation mechanism speed is low, the pressure of the soft overflow valve 19 is low, so that the stopping impact of the rotation mechanism is avoided.
Embodiment two:
Based on the load-adaptive rotary buffer valve in the first embodiment, the present embodiment provides a load-adaptive rotary hydraulic system, which includes the load-adaptive rotary buffer valve in the first embodiment, an oil inlet P of the load-adaptive rotary buffer valve is connected to an outlet of the constant delivery pump 1 through an oil supply pipeline, and an oil return port T of the load-adaptive rotary buffer valve is connected to a hydraulic oil tank; the working oil port A of the load self-adaptive rotary buffer valve is connected with the port A of the rotary motor 22; the working oil port B of the load self-adaptive rotary buffer valve is connected with the port B of the rotary motor 22; the control oil port a of the load self-adaptive rotation buffer valve is connected with the pilot handle oil port for controlling the right rotation; the control oil port b of the load self-adaptive rotation buffer valve is connected with the pilot handle oil port for controlling the left rotation.
The foregoing is merely a preferred embodiment of the present invention, and it should be noted that modifications and variations could be made by those skilled in the art without departing from the technical principles of the present invention, and such modifications and variations should also be regarded as being within the scope of the invention.
Claims (11)
1. A load adaptive slew buffer valve comprising:
the oil inlet P is used for connecting an oil supply pipeline of hydraulic oil;
The oil return port T is used for connecting a hydraulic oil tank;
The working oil port A is used for connecting one end of the rotary motor;
The working oil port B is used for connecting the other end of the rotary motor;
The P port of the oil inlet control valve (2) is connected with the oil inlet P; the P1 port of the oil inlet control valve (2) is connected with a hydraulic oil tank through a pressure equalizing valve (14); the A port of the oil inlet control valve (2) is respectively connected with the working oil port A, the inlet of the first oil supplementing overflow valve (15) and the A port of the oil return control valve (3); the port B of the oil inlet control valve (2) is respectively connected with the working oil port B, the inlet of the second oil supplementing overflow valve (16) and the port B of the oil return control valve (3); the outlet of the first oil supplementing overflow valve (15), the outlet of the second oil supplementing overflow valve (16) and the T port of the oil return control valve (3) are respectively connected with an oil return port T.
2. The load adaptive slew buffer valve of claim 1, further comprising:
a control oil port a used for connecting with a pilot handle oil port for controlling the right rotation;
The control oil port b is used for connecting with a pilot handle oil port for controlling left rotation;
the control oil port a and the control oil port b are respectively connected with two control oil ports of the oil inlet control valve (2).
3. The load adaptive slew buffer valve of claim 2, further comprising:
The hydraulic oil tank is characterized by comprising a first electromagnetic directional valve (17), wherein an inlet of the first electromagnetic directional valve (17) is connected with an oil inlet P, an outlet of the first electromagnetic directional valve (17) is connected with a shuttle valve (21) through a fifth one-way valve (20), and the first electromagnetic directional valve is connected with a hydraulic oil tank through a soft overflow valve (19) and a second electromagnetic directional valve (18); the shuttle valve (21) is connected between the working oil port A and the working oil port B.
4. The load self-adaptive rotary buffer valve according to claim 3, wherein when the pilot handle is not operated, the control oil port a and the control oil port b have no pressure, and the oil inlet control valve (2) and the oil return control valve (3) keep the middle position and do not change direction; the first electromagnetic directional valve (17) and the second electromagnetic directional valve (18) are not electrified; the hydraulic oil enters the pressure equalizing valve (14) through the P1 port of the oil inlet control valve (2), and returns to the hydraulic oil tank through the pressure equalizing valve (14).
5. A load-adaptive rotary buffer valve according to claim 3, wherein when a crane is used for hanging a heavy object, if the steel wire rope is not vertical to the heavy object, the first electromagnetic directional valve (17) is powered, and the working oil port a and the working oil port B are communicated with the oil inlet P through the first electromagnetic directional valve (17) so as to realize centering of the steel wire rope and the heavy object.
6. A load-adaptive rotary buffer valve according to claim 3, characterized in that the Lsa port of the oil inlet control valve (2) is connected with the first gap damper (6), the first check valve (8) and the third check valve (10) respectively through the first damper (4); the third one-way valve (10) is connected with a spring cavity of the pressure equalizing valve (14) through a third damping (12) and is connected with a hydraulic oil tank through a fourth damping (13); the third one-way valve (10) is also connected with the second damping (5), the second clearance damping (7) and the second one-way valve (9) through a fourth one-way valve (11); the second damping (5) is connected with an Lsb port of the oil inlet control valve (2); the sa port of the oil return control valve (3) is connected with the first clearance damping (6) and the first one-way valve (8), and the sb port of the oil return control valve (3) is connected with the second clearance damping (7) and the second one-way valve (9).
7. The load-adaptive rotary buffer valve according to claim 6, wherein when the pilot handle is controlled to rotate right, the pressure of the control oil port a is gradually increased, at this time, the oil inlet control valve (2) is gradually turned over, the throttle port from the oil inlet P to the P1 port of the oil inlet control valve (2) is gradually closed to be closed, the throttle port from the oil inlet P to the working oil port a is gradually increased to be fully opened, the loop of the ls a port and the oil return port T of the oil inlet control valve (2) is cut off, the ls B port of the oil inlet control valve (2) is communicated with the oil return port T, the B port of the oil inlet control valve (2) is closed, the a port of the oil inlet control valve (2) is established with pressure, the pressure of the working oil port a is fed back to the sa port of the oil return control valve (3) through the ls a port of the oil inlet control valve (2), the first damping valve (4), the first clearance damping valve (6) and the first one-way valve (8), the oil return control valve (3) is pushed to be turned over, the B port of the oil return control valve (3) is gradually opened through the T port of the oil return control valve (3), the port of the oil return control valve (2) is gradually opened, the pressure of the oil port a is opened through the T port of the oil return control valve (3), and the pressure of the oil inlet valve (2) is balanced through the third damping valve (14) is opened, and the pressure of the valve (12) is balanced; at the moment, hydraulic oil of the oil inlet P is output to the working oil port A through the oil inlet control valve (2) and is used for controlling the rotary mechanism to rotate rightwards; the hydraulic oil of the working oil port B enters the hydraulic oil tank through the oil return control valve (3).
8. The load-adaptive swing damper valve according to claim 6, wherein when the pressure at the working port a exceeds a set value, the corresponding first oil compensating relief valve (15) is opened to protect the system pressure from exceeding the set value.
9. The load-adaptive swing buffer valve according to claim 6, wherein when the swing mechanism stops turning to the right, the pressure of the working port a is reduced, and at this time, hydraulic oil is replenished to the working port a through the first oil replenishment overflow valve (15) to avoid the swing mechanism from sucking empty.
10. The load-adaptive swing buffer valve according to claim 6, wherein when the swing mechanism stops turning to the right, the pressure of the working port B rises due to the oil return control valve (3) having been closed, and at this time, the second electromagnetic directional valve (18) is closed with a delay, and the pressure of the working port B is unloaded through the shuttle valve (21), the fifth check valve (20), the soft overflow valve (19), and the second electromagnetic directional valve (18) to avoid a stop shock.
11. A load-adaptive rotary hydraulic system, which is characterized by comprising the load-adaptive rotary buffer valve according to any one of claims 1-10, wherein an oil inlet P of the load-adaptive rotary buffer valve is connected with an outlet of a constant delivery pump (1) through an oil supply pipeline, and an oil return port T of the load-adaptive rotary buffer valve is connected with a hydraulic oil tank; the working oil port A of the load self-adaptive rotary buffer valve is connected with the port A of the rotary motor (22); the working oil port B of the load self-adaptive rotary buffer valve is connected with the port B of the rotary motor (22); the control oil port a of the load self-adaptive rotation buffer valve is connected with the pilot handle oil port for controlling the right rotation; the control oil port b of the load self-adaptive rotation buffer valve is connected with the pilot handle oil port for controlling the left rotation.
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN104533863A (en) * | 2014-12-30 | 2015-04-22 | 浙江大学 | Rotary system control valve of crane |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US6334308B1 (en) * | 1998-03-04 | 2002-01-01 | Komatsu Ltd. | Pressure compensating valve, unloading pressure control valve and hydraulically operated device |
| JP5049496B2 (en) * | 2006-01-23 | 2012-10-17 | 株式会社小松製作所 | Control circuit |
| JP2009036300A (en) * | 2007-08-01 | 2009-02-19 | Kobelco Contstruction Machinery Ltd | Turn controlling device |
| CN106414306B (en) * | 2014-03-04 | 2018-10-09 | 马尼托瓦克起重机有限责任公司 | Electric-controlled type hydraulic rocking system |
| CN104564885B (en) * | 2015-01-08 | 2017-04-05 | 宁波宇洲液压科技有限公司 | A kind of highly integrated Double-directional back rotary valve for pilot control pattern |
| JP6398863B2 (en) * | 2015-05-14 | 2018-10-03 | 株式会社豊田自動織機 | Hydraulic control device for forklift |
| CN106870473B (en) * | 2017-04-07 | 2018-04-03 | 江苏师范大学 | A kind of pressure-transforming energy-saving four-way proportional flow commutator of recyclable inertia kinetic energy |
| CN109236782B (en) * | 2018-11-16 | 2019-12-24 | 徐州徐工液压件有限公司 | Novel rotary control valve |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN104533863A (en) * | 2014-12-30 | 2015-04-22 | 浙江大学 | Rotary system control valve of crane |
Non-Patent Citations (1)
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| 大惯量负载回转液压***启制动平稳性的实验研究;刘锋;黄长征;罗昕;周宏兵;;液压与气动;20170115(第01期);全文 * |
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