CN113944678A - Double-rod linkage type hydraulic drive control system - Google Patents
Double-rod linkage type hydraulic drive control system Download PDFInfo
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- CN113944678A CN113944678A CN202111264236.2A CN202111264236A CN113944678A CN 113944678 A CN113944678 A CN 113944678A CN 202111264236 A CN202111264236 A CN 202111264236A CN 113944678 A CN113944678 A CN 113944678A
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- 239000002184 metal Substances 0.000 claims description 12
- 238000007789 sealing Methods 0.000 claims description 12
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- 238000005485 electric heating Methods 0.000 claims description 3
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- 229910002027 silica gel Inorganic materials 0.000 claims description 3
- 230000009977 dual effect Effects 0.000 claims 2
- 239000003921 oil Substances 0.000 description 51
- 239000010720 hydraulic oil Substances 0.000 description 21
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- 230000001360 synchronised effect Effects 0.000 description 3
- 238000010521 absorption reaction Methods 0.000 description 2
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- 231100000817 safety factor Toxicity 0.000 description 1
- -1 sand ions Chemical class 0.000 description 1
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
- F15B21/087—Control strategy, e.g. with block diagram
-
- 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
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/22—Synchronisation of the movement of two or more 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
- 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
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more 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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
-
- 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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1438—Cylinder to end cap assemblies
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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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1438—Cylinder to end cap assemblies
- F15B15/1442—End cap sealings
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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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1447—Pistons; Piston to piston rod assemblies
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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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1447—Pistons; Piston to piston rod assemblies
- F15B15/1452—Piston sealings
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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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1485—Special measures for cooling or heating
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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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/149—Fluid interconnections, e.g. fluid connectors, passages
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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
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
- F16F15/0232—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means with at least one gas spring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L59/00—Thermal insulation in general
- F16L59/02—Shape or form of insulating materials, with or without coverings integral with the insulating materials
- F16L59/028—Composition or method of fixing a thermally insulating material
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Actuator (AREA)
Abstract
The application discloses two pole coordinated type hydraulic drive control system, including first pneumatic cylinder, second pneumatic cylinder, oil pump, oil tank, first solenoid valve, second solenoid valve, third solenoid valve, fourth solenoid valve, fifth solenoid valve, sixth solenoid valve, seventh solenoid valve and eighth solenoid valve, the inside of first pneumatic cylinder and second pneumatic cylinder all is provided with no pole chamber and has the pole chamber, meet through pipeline and first solenoid valve and second solenoid valve between the no pole chamber of first pneumatic cylinder and the no pole chamber of second pneumatic cylinder, the no pole chamber of first pneumatic cylinder meets with the oil tank through seventh solenoid valve and pipeline, the no pole chamber of second pneumatic cylinder meets with the oil tank through eighth solenoid valve and pipeline, the pole chamber of first pneumatic cylinder meets with the oil-out of oil pump through pipeline and fourth solenoid valve.
Description
Technical Field
The invention relates to the field of hydraulic systems, in particular to a double-rod linkage type hydraulic drive control system.
Background
The hydraulic cylinder is a commonly used hydraulic driving part at present, the hydraulic cylinder at present comprises a cylinder body, a piston and a piston rod, the piston is installed in the cylinder body in a sliding and sealing mode, the piston rod is installed on the piston, the piston divides the space in the cylinder body into a rod cavity and a rodless cavity, but the hydraulic cylinder at present is in a single-cylinder use mode when in use, or only a plurality of hydraulic cylinders are fixed together for use, the working modes of the hydraulic cylinders are always independent, and the work among the hydraulic cylinders lacks coordination and linkage.
Disclosure of Invention
The invention provides a double-rod linkage type hydraulic drive control system aiming at the problems.
The technical scheme adopted by the invention is as follows:
a double-rod linkage type hydraulic drive control system comprises a first hydraulic cylinder, a second hydraulic cylinder, an oil pump, an oil tank, a first electromagnetic valve, a second electromagnetic valve, a third electromagnetic valve, a fourth electromagnetic valve, a fifth electromagnetic valve, a sixth electromagnetic valve, a seventh electromagnetic valve and an eighth electromagnetic valve, wherein rodless cavities and rod cavities are arranged inside the first hydraulic cylinder and the second hydraulic cylinder, the rodless cavities of the first hydraulic cylinder and the second hydraulic cylinder are connected through a pipeline, the first electromagnetic valve and the second electromagnetic valve, the rodless cavities of the first hydraulic cylinder are connected with the oil tank through the seventh electromagnetic valve and the pipeline, the rodless cavities of the second hydraulic cylinder are connected with the oil tank through the eighth electromagnetic valve and the pipeline, the rod cavities of the first hydraulic cylinder are connected with an oil outlet of the oil pump through the pipeline and the fourth electromagnetic valve, and the rod cavities of the second hydraulic cylinder are connected with the oil pump through the third electromagnetic valve, The fifth electromagnetic valve and the pipeline are connected with an oil pump, the third electromagnetic valve and the fifth electromagnetic valve are in a parallel state, the oil tank is connected with the oil pump, the rod cavity of the first hydraulic cylinder is connected with the oil tank through the pipeline and the sixth electromagnetic valve, the oil tank is connected with the oil pump, and the first hydraulic cylinder and the second hydraulic cylinder are consistent in structure and size.
Corresponding oil pipes and valves are used in the device in a combined mode, synchronous joint debugging of the two hydraulic rods is achieved, the safety coefficient is higher, the application range is wider, and the device is suitable for areas with large climate change and large temperature difference change (such as grasslands, deserts, tropical rain forests and other areas).
Optionally, a frequency converter is mounted on the oil pump.
The frequency converter is used for changing the working frequency of the oil pump according to the use requirement.
Optionally, the flexible heat insulation structure further comprises a groove clamping plate, a heat insulation assembly block and a flexible soft sleeve, the flexible soft sleeve is sleeved on the first hydraulic cylinder and the second hydraulic cylinder, the heat insulation assembly block is sleeved on the flexible soft sleeve, the groove clamping plate and the heat insulation assembly block are matched together, a screw hole is formed in the groove clamping plate, an air cushion film is arranged between the groove clamping plate and the heat insulation assembly block, the groove clamping plate surrounds the heat insulation assembly block to form a square enclosure part, the flexible soft sleeve is made of silica gel or rubber, tooth surfaces are arranged on the inner wall and the outer wall of the flexible soft sleeve, and a cavity is formed in the wall of the flexible soft sleeve.
Because the hydraulic cylinder is needed to be used by the solar photovoltaic system, the double-rod linkage type hydraulic drive control system is often used on the solar photovoltaic system (specifically, the hydraulic telescopic rod is arranged on a photovoltaic support and used for driving the photovoltaic telescopic plate to rotate).
This system probably needs to use in grassland, desert isothermal difference change, the big region of climatic change, so flexible soft cover is established to the cover on the pneumatic cylinder in this structure to at the flexible soft cover on the cover insulating element piece, insulating element can generate heat, and when extreme severe cold weather, the heat that insulating element produced can preheat the pneumatic cylinder, can avoid the hydraulic oil in the pneumatic cylinder to freeze like this. Simultaneously all be provided with the flank of tooth on flexible soft cover's the inner wall and the outer wall, the existence of flank of tooth makes to have great space between flexible soft cover and the pneumatic cylinder and between flexible soft cover and the insulation component piece, and such design can guarantee that rainwater and grit granule can not remain between flexible soft cover and the pneumatic cylinder and between flexible soft cover and the insulation component piece (steam and grit ion can lead to the corruption of pneumatic cylinder and insulation component piece).
In the system, the air cushion film is arranged between the groove clamping plate and the heat insulation component block, so that the effect of shock absorption is achieved between the groove clamping plate and the heat insulation component block, and the air cushion film has more gaps (water leakage and sand leakage can be achieved), so that the air cushion film can be used for ensuring that water and sand accumulation cannot occur between the heat insulation component block and the groove clamping plate.
In the flexible soft sleeve, because the inner wall and the outer wall of the flexible soft sleeve are both provided with the tooth surfaces, and the sleeve wall of the flexible soft sleeve is internally provided with the cavity, the design can ensure that the flexible soft sleeve has certain telescopic deformation capacity, so that the flexible soft sleeve can be better ensured to be clamped between the heat-insulating component block and the hydraulic cylinder, and can adapt to hydraulic cylinders with different width sizes; and flexible soft cover only with insulation assembly piece and pneumatic cylinder contact, flexible soft cover is not completely hugged closely insulation assembly piece and pneumatic cylinder, just so has existed more space between insulation assembly piece and the pneumatic cylinder, when insulation assembly piece is strikeed and takes place deformation (deformation volume is less relatively), striking deformation can not transmit for the pneumatic cylinder, can guarantee like this that the pneumatic cylinder can not receive the striking, can not produce deformation (because the cavity can be compressed, and the existence of flank of tooth can take place the mistake and turn round).
Optionally, the heat preservation assembly block comprises a block main body, a through hole is formed in the block main body, the flexible soft sleeve is located in the through hole, a liquid storage cavity is formed in the block main body, heat conduction oil is stored in the liquid storage cavity, and an electric heating tube is arranged in the liquid storage cavity.
The actual heat preservation subassembly piece can actually be regarded as an oil spit of fland, and the effect of oil spit of fland is when low temperature weather, and the production heat can heat the pneumatic cylinder, ensures that low temperature weather can not influence the performance of pneumatic cylinder.
The hydraulic cylinder is influenced by low-temperature weather, one is that hydraulic oil is frozen, but a fit gap is formed between each part due to the thermal expansion and the thermal contraction, so that the hydraulic oil leaks, on the basis of the reason, the flexible soft sleeve and the air cushion film are arranged on the two sides of the heat insulation assembly block, the flexible soft sleeve and the air cushion film with the structures can play a role in heat transfer, so that the hydraulic oil of the hydraulic cylinder can be ensured not to be frozen, secondly, because the flexible soft sleeve and the air cushion film have larger gaps, the gaps can allow the oil heater to heat and diffuse nearby air, the diffused air can form a relatively warm independent microclimate nearby the hydraulic cylinder, the independent microclimate can protect the hydraulic cylinder, the valve and the pipeline to a certain extent, and the phenomenon that the fit gap difference of the parts due to the different thermal expansion and cold contraction degrees is reduced, and the probability of oil leakage of hydraulic oil is reduced.
Optionally, first pneumatic cylinder includes barrel, end cover, piston assembly and cock stem, piston assembly sliding seal sets up in the barrel, end cover seal sets up two tube mouth departments at the barrel, the cock stem is installed on piston assembly, and cock stem one end is located the barrel, and the cock stem other end is located the barrel externally.
Optionally, the piston assembly includes block, sealed gum cover, a plurality of cushion ring, the block is cylindric metal block, has seted up the through-hole in the block, the through-hole cooperation in cock stem and the block is in the same place, the cushion ring cover is established on the cock stem, be provided with the nut on the cock stem, the cushion ring presss from both sides between nut and block, the width inequality of cushion ring, and the width of the cushion ring that is closer to the block is wider more, and sealed gum cover is established on the outer wall of block.
The piston assembly is an important part of the hydraulic cylinder, compared with the traditional hydraulic cylinder, in the hydraulic cylinder, rubber cushion rings are arranged on two sides of a block body and have certain flexible telescopic deformation, so that the plug rod can not generate instant extrusion stress on the block body when the plug rod is subjected to tension or extrusion force, the block body can be ensured to have longer service life, meanwhile, a plurality of rubber cushion rings are adopted to be combined for use, the rubber cushion rings are piled together into a circular table shape, after the plug rod is installed, the plug rod, the rubber cushion rings and the block body jointly form a structure similar to a spindle body (namely, the two sides of the block body are respectively provided with a circular table), the piston similar to the spindle body can reduce the resistance which is just moved in the moment relative to a cylindrical complete piston, and meanwhile, the rubber cushion rings are piled into the circular table shape, so that the weight of the piston assembly can be reduced as much as possible on the premise of ensuring the buffering effect between the plug rod and the block body, ensuring stable sliding of the piston assembly.
Optionally, the end cover includes a first end cover and a second end cover, the first end cover and the second end cover are respectively located at two openings of the barrel, and the first end cover and the second end cover are both provided with a circular truncated cone-shaped chamfer surface.
Set up the chamfer face of round platform form on first end cap and second end cap, such design is in order to can with cushion ring looks adaptation, pile the cushion ring that is the round platform form and can paste tight chamfer face, guarantee that piston assembly can not appear cushion ring skew and extrusion bad phenomenon when moving extreme position.
Optionally, the block body and the sealing rubber sleeve are provided with an inner concave and an outer convex which can be matched with each other, and the inner concave and the outer convex are mutually embedded and matched together.
In this piston assembly, the block adopts protruding and indent gomphosis complex mode can guarantee cooperation stability with sealed gum cover, ensures that sealed gum cover is difficult for droing from the block.
Optionally, be provided with the heavy annular groove on the block, the both sides of block all are provided with the heavy annular groove.
The central point of concrete heavy ring groove is exactly the through-hole on the block, and the heavy ring groove is around the through-hole distribution of block, and the effect of annular is as follows, then can guarantee that the block can have certain flexible deformability (the width through making the groove diminishes or the grow, but the range is very little), can guarantee still when the temperature shock of like this that block and barrel can be stable the cooperation be in the same place, cooperation gap can not appear, then can reduce whole piston assembly's weight.
The notch of concrete heavy annular is stopped up by the cushion ring, can guarantee like this that block one side pressure shock rise (gush into hydraulic oil in a large number in the twinkling of an eye) the time, partly cushion ring can be absorbed in heavy annular to the realization is to the step-down of hydraulic oil, avoids hydraulic oil to lose barrel and end cover pressure, and when hydraulic oil discharged, the cushion ring can resume to the original state. Have and only when the cushion ring folds into the round platform form, just can the cushion ring take place to deform when block one side pressure is too big and imbed in the heavy annular, because only fold into the round platform form, the cushion ring of top is pressed into warpage deformation with the cushion ring of below easily, and pile into cylindric cushion ring to the diameter equals, the cushion ring of top does not press into warpage deformation's trend with the cushion ring of below, so only adopt the cushion ring of different width and fold into the round platform form, just can ensure when pressure is too big, the cushion ring can sink into the heavy annular and realize the pressure release.
Optionally, the end cover is a metal end cover, the cylinder body is a metal cylinder body, and the end cover and the cylinder body are made of the same metal.
The same metal material is adopted, so that a matching gap can be caused by expansion with heat and contraction with cold as much as possible, and corrosion caused by a primary battery effect can be avoided.
The invention has the beneficial effects that: corresponding oil pipes and valves are used in a combined mode, synchronous joint adjustment of the two hydraulic rods is achieved, safety factors are higher, and the application range is wider.
Description of the drawings:
FIG. 1 is a schematic diagram of the working principle of a double-rod linkage type hydraulic drive control system,
figure 2 is a diagrammatic and schematic illustration of the construction of the first hydraulic cylinder,
figure 3 is a schematic view of the mating relationship of the first hydraulic cylinder and the channel plate,
figure 4 is a schematic view of the mating relationship of the cartridge body and the end cap,
figure 5 is a schematic view of the mating relationship of the piston assembly and the stopper rod,
FIG. 6 is a schematic view showing the fitting relationship among the cylinder, the flexible soft cover and the heat-insulating assembly block.
The figures are numbered: 101. a first solenoid valve; 102. a second solenoid valve; 103. a third electromagnetic valve; 104. a fourth solenoid valve; 105. a fifth solenoid valve; 106. a sixth electromagnetic valve; 107. a seventh electromagnetic valve; 108. an eighth solenoid valve; 2. an oil tank; 3. an oil pump; 4. a frequency converter; 51. a first hydraulic cylinder; 52. a second hydraulic cylinder; 511. a rodless cavity; 512. a rod cavity; 501. a barrel; 502. a second end cap; 503. a third end cap; 504. a stopper rod; 505. a heat-insulating component block; 506. a flexible soft sleeve; 507. a slot clamping plate; 508. a nut; 509. a rubber cushion ring; 5010. sealing the rubber sleeve; 5011. a block body; 5012. and (5) sinking a ring groove.
The specific implementation mode is as follows:
the present invention will be described in detail below with reference to the accompanying drawings.
As shown in figure 1, a double-rod linkage type hydraulic drive control system comprises a first hydraulic cylinder 51, a second hydraulic cylinder 52, an oil pump 3, an oil tank 2, a first electromagnetic valve 101, a second electromagnetic valve 102, a third electromagnetic valve 103, a fourth electromagnetic valve 104, a fifth electromagnetic valve 105, a sixth electromagnetic valve 106, a seventh electromagnetic valve 107 and an eighth electromagnetic valve 108, wherein the first hydraulic cylinder 51 and the second hydraulic cylinder 52 are internally provided with a rodless cavity 511 and a rod cavity 512, the rodless cavity 511 of the first hydraulic cylinder 51 is connected with the rodless cavity 511 of the second hydraulic cylinder 52 through a pipeline and the first electromagnetic valve 101 and the second electromagnetic valve 102, the rodless cavity 511 of the first hydraulic cylinder 51 is connected with the oil tank 2 through the seventh electromagnetic valve 107 and the pipeline, the rodless cavity 511 of the second hydraulic cylinder 52 is connected with the oil tank through the eighth electromagnetic valve 108 and the pipeline, the rod cavity 512 of the first hydraulic cylinder 51 is connected with an oil outlet of the oil pump 3 through a pipeline and the fourth electromagnetic valve 104, the rod chamber 512 of the second hydraulic cylinder 52 is connected with the oil pump 3 through the third electromagnetic valve 103, the fifth electromagnetic valve 105 and the pipeline, the third electromagnetic valve 103 and the fifth electromagnetic valve 105 are in a parallel state, the oil tank 2 is connected with the oil pump 3, the rod chamber 512 of the first hydraulic cylinder 51 is connected with the oil tank 2 through the pipeline and the sixth electromagnetic valve 106, the oil tank 2 is connected with the oil pump 3, and the first hydraulic cylinder 51 and the second hydraulic cylinder 52 are consistent in structure and size.
Corresponding oil pipes and valves are used in the device in a combined mode, synchronous joint debugging of the two hydraulic rods is achieved, the safety coefficient is higher, the application range is wider, and the device is suitable for areas with large climate change and large temperature difference change (such as grasslands, deserts, tropical rain forests and other areas).
As shown in fig. 1, an inverter 4 is mounted on the oil pump 3.
The frequency converter 4 is used for changing the working frequency of the oil pump 3 according to the use requirement.
The hydraulic cylinder has the structure that the area of a piston in a rod cavity 512 is A1, the area of a rodless cavity 511 is A2, A1 is larger than A2 (the contact area of the piston and hydraulic oil is reduced due to the existence of a plug rod 504), the pressures of the rod cavity 512 and the rodless cavity 511 are both P, the external force F1 is P A1 when hydraulic oil enters from the rodless cavity 511, the external force F2 is P A2 when the hydraulic oil enters from the rod cavity 512, and F1 is larger than F2.
The cooperative operation mode of the system is as follows.
When the oil pump 3 rotates reversely (returns oil to the oil tank 2), the first electric valve, the second electromagnetic valve 102, the fifth electromagnetic valve 105 and the sixth electromagnetic valve 106 are opened, other electromagnetic valves are closed, the plug rod 504 of the second hydraulic cylinder 52 is retracted, the plug rod 504 of the first hydraulic cylinder 51 is retracted, the two hydraulic cylinders synchronously move, the resultant force of the first hydraulic cylinder 51 and the second hydraulic cylinder 52 is P A1+ P A2 no matter the hydraulic cylinders extend or retract, the secondary working mode can be used for occasions needing the consistent extending and retracting force,
the oil pump 3 rotates forward (draws oil out of the oil tank 2), the third electromagnetic valve 103, the fourth electromagnetic valve 104, the seventh electromagnetic valve 107, and the eighth electromagnetic valve 108 are opened, the other electromagnetic valves are closed, the plug rod 504 of the second hydraulic cylinder 52 retracts, and the plug rod 504 of the first hydraulic cylinder 51 retracts; the oil pump 3 is reversely rotated, the third electromagnetic valve 103, the fourth electromagnetic valve 104, the seventh electromagnetic valve 107 and the eighth electromagnetic valve 108 are opened, other electric valves are closed, the plug rod 504 of the second hydraulic cylinder 52 extends out, the plug rod 504 of the first hydraulic cylinder 51 extends out, the two hydraulic cylinders synchronously move, and the secondary working mode can be used for occasions where the extending and retracting forces are different and the two forces have larger difference.
As shown in fig. 3 and 6, the thermal insulation module further includes a slot clamping plate 507, a thermal insulation module 505 and a flexible soft sleeve 506, the flexible soft sleeve 506 is sleeved on each of the first hydraulic cylinder 51 and the second hydraulic cylinder 52, the thermal insulation module 505 is sleeved on the flexible soft sleeve 506, the slot clamping plate 507 is matched with the thermal insulation module 505, a screw hole is formed in the slot clamping plate, an air cushion film is disposed between the slot clamping plate and the thermal insulation module 505, the slot clamping plate surrounds the thermal insulation module 505 to form a square enclosure, the flexible soft sleeve 506 is a flexible soft sleeve 506 made of silica gel or rubber, tooth surfaces are disposed on an inner wall and an outer wall of the flexible soft sleeve 506, and a cavity is disposed in a sleeve wall of the flexible soft sleeve 506.
Because the hydraulic cylinder is needed to be used by the solar photovoltaic system, the double-rod linkage type hydraulic drive control system is often used on the solar photovoltaic system (specifically, the hydraulic telescopic rod is arranged on a photovoltaic support and used for driving the photovoltaic telescopic plate to rotate).
The system can be used in areas with large changes of isothermal differences in grasslands and deserts and large climate changes, so that the flexible soft sleeve 506 is sleeved on the hydraulic cylinder in the structure, the heat insulation component block 505 is sleeved on the flexible soft sleeve 506, the heat insulation component can generate heat, and the heat generated by the heat insulation component can preheat the hydraulic cylinder in extreme cold weather, so that hydraulic oil in the hydraulic cylinder can be prevented from being frozen. Meanwhile, tooth surfaces are arranged on the inner wall and the outer wall of the flexible soft sleeve 506, and large gaps are formed between the flexible soft sleeve 506 and the hydraulic cylinder and between the flexible soft sleeve 506 and the heat insulation component block 505 due to the tooth surfaces, so that rainwater and sand particles can be prevented from remaining between the flexible soft sleeve 506 and the hydraulic cylinder and between the flexible soft sleeve 506 and the heat insulation component block 505 (water vapor and sand ions can cause corrosion of the hydraulic cylinder and the heat insulation component block 505).
In the system, the air cushion film is arranged between the slot clamping plate and the heat insulation component block 505, so that the shock absorption effect is achieved between the slot clamping plate and the heat insulation component block 505, and the air cushion film has more gaps (water leakage and sand leakage can be achieved), so that the water accumulation and sand accumulation between the heat insulation component block 505 and the slot clamping plate can be avoided by using the air cushion film.
In the flexible soft sleeve 506, because the inner wall and the outer wall of the flexible soft sleeve 506 are both provided with tooth surfaces, and a cavity is arranged in the sleeve wall of the flexible soft sleeve 506, the design can ensure that the flexible soft sleeve 506 has certain telescopic deformation capacity, so that the flexible soft sleeve 506 can be better ensured to be clamped between the heat-insulating component block 505 and the hydraulic cylinder, and can adapt to hydraulic cylinders with different width sizes; and the soft cover 506 of flexibility only contacts with insulating component piece 505 and pneumatic cylinder, the soft cover 506 of flexibility is not totally hugged closely insulating component piece 505 and pneumatic cylinder, just so make to have more space between insulating component piece 505 and the pneumatic cylinder, when insulating component piece 505 is strikeed and takes place deformation (deformation volume is relatively less), striking deformation can not be transmitted for the pneumatic cylinder, can guarantee like this that the pneumatic cylinder can not receive the striking, can not produce deformation (because the cavity can be compressed, and the existence of flank of tooth can take place the wrong turn round).
As shown in fig. 3 and 6, the heat preservation assembly block 505 comprises a block main body, a through hole is formed in the block main body, the flexible soft sleeve 506 is located in the through hole, a liquid storage cavity is formed in the block main body, heat conduction oil is stored in the liquid storage cavity, and an electric heating tube is arranged in the liquid storage cavity.
The actual heat preservation subassembly piece 505 can actually be regarded as an oil spit of fland, and the effect of oil spit of fland is when low temperature weather, and the production heat can heat the pneumatic cylinder, ensures that low temperature weather can not influence the performance of pneumatic cylinder.
The hydraulic cylinder is affected by low-temperature weather, one is that hydraulic oil is frozen, but a fit gap occurs between each part due to the thermal expansion and the thermal contraction, so that the hydraulic oil leaks, for the above reasons, the flexible soft sleeve 506 and the air cushion film are arranged on both sides of the heat-insulating assembly block 505, the flexible soft sleeve 506 and the air cushion film of the above structure can play a role in heat transfer, so that the hydraulic oil of the hydraulic cylinder can be ensured not to be frozen, secondly, because the flexible soft sleeve 506 and the air cushion film have large gaps, the gaps can allow the oil heater to heat and diffuse nearby air, the diffused air can form a relatively warm independent microclimate near the hydraulic cylinder, the independent microclimate can protect the hydraulic cylinder, the valve and the pipeline to a certain extent, and the phenomenon that the fit gap difference occurs due to different degrees of thermal expansion and cold contraction of the parts is reduced, and the probability of oil leakage of hydraulic oil is reduced.
As shown in fig. 2 and 3, the first hydraulic cylinder 51 includes a cylinder 501, end caps, a piston assembly and a plug 504, the piston assembly is slidably and hermetically disposed in the cylinder 501, the end caps are hermetically disposed at two openings of the cylinder 501, the plug 504 is mounted on the piston assembly, one end of the plug 504 is located in the cylinder 501, and the other end of the plug 504 is located outside the cylinder 501.
As shown in fig. 4 and 5, the piston assembly includes a block 5011, a sealing rubber sleeve 5010, and a plurality of rubber gasket rings 509, the block 5011 is a cylindrical metal block 5011, through holes are formed in the block 5011, the plug rod 504 is matched with the through holes in the block 5011, the rubber gasket rings 509 are sleeved on the plug rod 504, the plug rod 504 is provided with a nut 508, the rubber gasket rings 509 are clamped between the nut 508 and the block 5011, the widths of the rubber gasket rings 509 are different, the width of the rubber gasket ring 509 closer to the block 5011 is wider, and the sealing rubber sleeve 5010 is sleeved on the outer wall of the block 5011.
The piston assembly is an important part of the hydraulic cylinder, compared with the traditional hydraulic cylinder, in the hydraulic cylinder, rubber gasket rings 509 are arranged on two sides of a block 5011, the rubber gasket rings 509 have certain flexible telescopic deformation, so that the plug rod 504 can not generate instantaneous extrusion stress on the block 5011 at the moment when the plug rod 504 is subjected to tensile force or extrusion force, the block 5011 can be ensured to have longer service life, meanwhile, a plurality of rubber gasket rings 509 are adopted for combined use, the rubber gasket rings 509 are stacked together in a circular truncated cone shape, after the plug rod 504 is installed, the plug rod 504, the rubber gasket rings 509 and the block 5011 jointly form a structure similar to a spindle body (which can be seen as that two sides of the block 5011 are respectively provided with a circular truncated cone), the piston similar to the spindle body can reduce the instantaneous resistance caused by the beginning of moving compared with a completely cylindrical piston, and meanwhile, the rubber gasket rings 509 are stacked in a circular truncated cone shape, it is possible to reduce the weight of the piston assembly as much as possible while ensuring the buffering effect between the plug rod 504 and the block 5011, and to ensure the stable sliding of the piston assembly.
As shown in fig. 2, 4 and 5, the end caps include a first end cap and a second end cap 502, the first end cap and the second end cap 502 are respectively located at two openings of the cylinder 501, and the first end cap and the second end cap 502 are both provided with a truncated cone-shaped chamfer surface.
The first end cover and the second end cover 502 are provided with the truncated cone-shaped chamfer surfaces, the design is that the chamfer surfaces can be matched with the rubber gasket ring 509, the rubber gasket ring 509 stacked in the truncated cone shape can be tightly attached to the chamfer surfaces, and the phenomenon that the rubber gasket ring 509 is deviated and extruded to be damaged when the piston assembly moves to the limit position is avoided.
As shown in fig. 5, the block 5011 and the sealing rubber sleeve 5010 are provided with an indent and a protrusion which can be engaged with each other, and the indent and the protrusion are engaged with each other.
In the piston assembly, the block 5011 and the sealing rubber sleeve 5010 can ensure the matching stability by adopting a convex and concave embedded matching mode, and the sealing rubber sleeve 5010 is not easy to fall off from the block 5011.
As shown in FIG. 5, block 5011 is provided with countersunk grooves 5012 and both sides of block 5011 are provided with countersunk grooves 5012.
The central point of the specific sinking ring slot 5012 is the through hole in the block 5011, the sinking ring slot 5012 surrounds the through holes in the block 5011 and is used for ensuring that the block 5011 can have certain telescopic deformation capacity (the width of the slot is reduced or enlarged, but the width is very small), so that the block 5011 and the cylinder 501 can be stably matched together when the temperature suddenly changes, a matching gap cannot occur, and the weight of the whole piston assembly can be reduced.
The notch of concrete sink ring groove 5012 is plugged up by cushion ring 509, can guarantee like this that when block 5011 one side pressure shock (gush into hydraulic oil in a large number in the twinkling of an eye), partly cushion ring 509 can be absorbed into in sink ring groove 5012 to the realization is to the step-down of hydraulic oil, avoids hydraulic oil to lose barrel 501 and end cover pressure, and when hydraulic oil discharged, cushion ring 509 can resume to the original state. Only when the rubber gasket rings 509 are stacked into a circular truncated cone shape, the rubber gasket rings 509 can deform and be embedded into the sinking ring grooves 5012 when the pressure on one side of the block 5011 is too high, because only when the rubber gasket rings 509 are stacked into the circular truncated cone shape, the upper rubber gasket rings 509 easily press the lower rubber gasket rings 509 into buckling deformation, and for the rubber gasket rings 509 with the same diameter and stacked into the cylindrical shape, the upper rubber gasket rings 509 do not have the tendency of pressing the lower rubber gasket rings 509 into buckling deformation, so only when the rubber gasket rings 509 with different widths are adopted and stacked into the circular truncated cone shape, the rubber gasket rings 509 can be ensured to sink into the sinking ring grooves 5012 to realize pressure relief when the pressure is too high.
As shown in fig. 5, the end cap is a metal end cap, the cylinder 501 is a metal cylinder 501, and the end cap and the cylinder 501 are made of the same metal.
The same metal material is adopted, so that a matching gap can be caused by expansion with heat and contraction with cold as much as possible, and corrosion caused by a primary battery effect can be avoided.
This embodiment provides a photovoltaic support that uses a dual-bar linkage hydraulic drive control system as described above.
The above description is only a preferred embodiment of the present invention, and not intended to limit the scope of the present invention, which is defined by the claims and their equivalents, and can be directly or indirectly applied to other related fields of technology.
Claims (10)
1. A double-rod linkage type hydraulic drive control system is characterized by comprising a first hydraulic cylinder, a second hydraulic cylinder, an oil pump, an oil tank, a first electromagnetic valve, a second electromagnetic valve, a third electromagnetic valve, a fourth electromagnetic valve, a fifth electromagnetic valve, a sixth electromagnetic valve, a seventh electromagnetic valve and an eighth electromagnetic valve, wherein rodless cavities and rod cavities are arranged inside the first hydraulic cylinder and the second hydraulic cylinder, the rodless cavities of the first hydraulic cylinder and the second hydraulic cylinder are connected through a pipeline, the first electromagnetic valve and the second electromagnetic valve, the rodless cavities of the first hydraulic cylinder are connected with the oil tank through the seventh electromagnetic valve and the pipeline, the rodless cavities of the second hydraulic cylinder are connected with the oil tank through the eighth electromagnetic valve and the pipeline, the rod cavities of the first hydraulic cylinder are connected with an oil outlet of the oil pump through the pipeline and the fourth electromagnetic valve, and the rod cavities of the second hydraulic cylinder are connected with the oil outlet of the oil pump through the third electromagnetic valve, The fifth electromagnetic valve and the pipeline are connected with an oil pump, the third electromagnetic valve and the fifth electromagnetic valve are in a parallel state, the oil tank is connected with the oil pump, the rod cavity of the first hydraulic cylinder is connected with the oil tank through the pipeline and the sixth electromagnetic valve, the oil tank is connected with the oil pump, and the first hydraulic cylinder and the second hydraulic cylinder are consistent in structure and size.
2. The double-linkage hydraulic drive control system as claimed in claim 1, wherein a frequency converter is mounted on the oil pump.
3. The dual-rod linkage hydraulic drive control system according to claim 1, further comprising a slot clamping plate, a heat insulation component block, and a flexible soft sleeve, wherein the flexible soft sleeve is sleeved on each of the first hydraulic cylinder and the second hydraulic cylinder, the heat insulation component block is sleeved on the flexible soft sleeve, the slot clamping plate is matched with the heat insulation component block, a screw hole is formed in the slot clamping plate, an air cushion film is arranged between the slot clamping plate and the heat insulation component block, the slot clamping plate surrounds the heat insulation component block to form a square enclosure, the flexible soft sleeve is a flexible soft sleeve made of silica gel or rubber, tooth surfaces are arranged on the inner wall and the outer wall of the flexible soft sleeve, and a cavity is formed in the sleeve wall of the flexible soft sleeve.
4. The dual-rod linkage hydraulic drive control system according to claim 3, wherein the heat-insulating assembly block comprises a block main body, a through hole is formed in the block main body, the flexible soft sleeve is located in the through hole, a liquid storage cavity is formed in the block main body, heat conduction oil is stored in the liquid storage cavity, and an electric heating tube is arranged in the liquid storage cavity.
5. The dual-rod linkage hydraulic drive control system of claim 1, wherein the first hydraulic cylinder comprises a cylinder body, an end cover, a piston assembly and a plug rod, the piston assembly is arranged in the cylinder body in a sliding sealing mode, the end cover seals are arranged at two openings of the cylinder body, the plug rod is arranged on the piston assembly, one end of the plug rod is located in the cylinder body, and the other end of the plug rod is located outside the cylinder body.
6. The dual-rod linkage hydraulic drive control system according to claim 5, wherein the piston assembly comprises a block body, a sealing rubber sleeve and a plurality of rubber cushion rings, the block body is a cylindrical metal block body, a through hole is formed in the block body, the plug rod is matched with the through hole in the block body, the rubber cushion rings are sleeved on the plug rod, a nut is arranged on the plug rod, the rubber cushion rings are clamped between the nut and the block body, the width of the rubber cushion rings is unequal, and the width of the rubber cushion ring closer to the block body is wider, and the sealing rubber sleeve is sleeved on the outer wall of the block body.
7. The dual-bar linkage hydraulic drive control system according to claim 6, wherein the end caps comprise a first end cap and a second end cap, the first end cap and the second end cap are respectively located at two openings of the cylinder, and the first end cap and the second end cap are both provided with truncated cone-shaped chamfer surfaces.
8. The dual-bar linkage hydraulic drive control system as claimed in claim 6, further comprising a concave part and a convex part which are mutually matched and arranged on the block body and the sealing rubber sleeve, wherein the concave part and the convex part are mutually embedded and matched together.
9. The dual bar linkage hydraulic drive control system of claim 6, wherein the block is provided with a counter sink groove, and wherein the block is provided with counter sink grooves on both sides.
10. The dual bar linkage hydraulic drive control system of claim 6, wherein the end cap is a metal end cap, the cylinder is a metal cylinder, and the end cap and the cylinder are made of the same metal.
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| CN202111264236.2A CN113944678A (en) | 2021-10-28 | 2021-10-28 | Double-rod linkage type hydraulic drive control system |
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Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4237688A (en) * | 1978-05-30 | 1980-12-09 | Koninklijke Bos Kalis Westminster Group N.V. | Hydraulic synchronous driving mechanism |
| JP2002144943A (en) * | 2000-11-14 | 2002-05-22 | Shinmeiwa Auto Engineering Ltd | Cylinder synchronous device of gate lifter |
| JP2002364604A (en) * | 2001-06-08 | 2002-12-18 | Shinmeiwa Auto Engineering Ltd | Cylinder synchronization device of gate lifter provided with gate sinking prevention mechanism |
| US20040066058A1 (en) * | 2002-10-08 | 2004-04-08 | Frank George Joseph | Single valve hydraulic operator for convertible top with movable rear bow |
| CN101749300A (en) * | 2009-12-18 | 2010-06-23 | 沈阳东北电力调节技术有限公司 | Integrating electro-hydraulic actuator |
| CN203161691U (en) * | 2013-02-01 | 2013-08-28 | 佛山市南海兴迪机械制造有限公司 | Synchronous oil cylinder hydraulic system capable of achieving single-cylinder adjustment without need for reducing working pressure |
| CN103807237A (en) * | 2014-02-28 | 2014-05-21 | 贵州詹阳动力重工有限公司 | Double-hydraulic-motor switching control system |
| CN105179366A (en) * | 2015-10-09 | 2015-12-23 | 济南大学 | Flexible vortex power, automatic-deslagging and backlog-free hydraulic cylinder |
| CN106337849A (en) * | 2016-11-23 | 2017-01-18 | 中冶赛迪工程技术股份有限公司 | TRT machine static-blade direct-drive electro-hydraulic servo control system |
| CN108679039A (en) * | 2018-07-20 | 2018-10-19 | 芜湖清柏白露智能信息科技有限公司 | A kind of water proofing property hydraulic cylinder sealing device |
| CN110701118A (en) * | 2019-09-29 | 2020-01-17 | 燕山大学 | Hydraulic clamping mechanism for coiled tubing |
| CN110864016A (en) * | 2018-08-27 | 2020-03-06 | 菜鸟智能物流控股有限公司 | Self-locking device, chassis structure, logistics distribution robot and control method |
-
2021
- 2021-10-28 CN CN202111264236.2A patent/CN113944678A/en active Pending
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4237688A (en) * | 1978-05-30 | 1980-12-09 | Koninklijke Bos Kalis Westminster Group N.V. | Hydraulic synchronous driving mechanism |
| JP2002144943A (en) * | 2000-11-14 | 2002-05-22 | Shinmeiwa Auto Engineering Ltd | Cylinder synchronous device of gate lifter |
| JP2002364604A (en) * | 2001-06-08 | 2002-12-18 | Shinmeiwa Auto Engineering Ltd | Cylinder synchronization device of gate lifter provided with gate sinking prevention mechanism |
| US20040066058A1 (en) * | 2002-10-08 | 2004-04-08 | Frank George Joseph | Single valve hydraulic operator for convertible top with movable rear bow |
| CN101749300A (en) * | 2009-12-18 | 2010-06-23 | 沈阳东北电力调节技术有限公司 | Integrating electro-hydraulic actuator |
| CN203161691U (en) * | 2013-02-01 | 2013-08-28 | 佛山市南海兴迪机械制造有限公司 | Synchronous oil cylinder hydraulic system capable of achieving single-cylinder adjustment without need for reducing working pressure |
| CN103807237A (en) * | 2014-02-28 | 2014-05-21 | 贵州詹阳动力重工有限公司 | Double-hydraulic-motor switching control system |
| CN105179366A (en) * | 2015-10-09 | 2015-12-23 | 济南大学 | Flexible vortex power, automatic-deslagging and backlog-free hydraulic cylinder |
| CN106337849A (en) * | 2016-11-23 | 2017-01-18 | 中冶赛迪工程技术股份有限公司 | TRT machine static-blade direct-drive electro-hydraulic servo control system |
| CN108679039A (en) * | 2018-07-20 | 2018-10-19 | 芜湖清柏白露智能信息科技有限公司 | A kind of water proofing property hydraulic cylinder sealing device |
| CN110864016A (en) * | 2018-08-27 | 2020-03-06 | 菜鸟智能物流控股有限公司 | Self-locking device, chassis structure, logistics distribution robot and control method |
| CN110701118A (en) * | 2019-09-29 | 2020-01-17 | 燕山大学 | Hydraulic clamping mechanism for coiled tubing |
Non-Patent Citations (2)
| Title |
|---|
| 郑珍泉: "多泵—多速马达速度控制回路的理论研究与分析", 中国优秀硕士学位论文全文数据库工程科技Ⅱ辑, no. 2015, 15 January 2015 (2015-01-15), pages 029 - 164 * |
| 龚国芹: "国内液压同步驱动回路专利技术综述", 中阿科技论坛(中英文), no. 08, 31 August 2021 (2021-08-31), pages 110 - 113 * |
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