CN113944678B - Double-rod linkage type hydraulic driving control system - Google Patents
Double-rod linkage type hydraulic driving control system Download PDFInfo
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- CN113944678B CN113944678B CN202111264236.2A CN202111264236A CN113944678B CN 113944678 B CN113944678 B CN 113944678B CN 202111264236 A CN202111264236 A CN 202111264236A CN 113944678 B CN113944678 B CN 113944678B
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- 238000007789 sealing Methods 0.000 claims description 11
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- 230000013011 mating Effects 0.000 claims description 4
- 239000000741 silica gel Substances 0.000 claims description 3
- 229910002027 silica gel Inorganic materials 0.000 claims description 3
- 238000005485 electric heating Methods 0.000 claims description 2
- 239000000463 material Substances 0.000 claims description 2
- 239000000565 sealant Substances 0.000 claims description 2
- 230000009977 dual effect Effects 0.000 claims 5
- 239000003921 oil Substances 0.000 description 42
- 239000010720 hydraulic oil Substances 0.000 description 21
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- 230000007797 corrosion Effects 0.000 description 4
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- 238000010586 diagram Methods 0.000 description 4
- 230000008602 contraction Effects 0.000 description 3
- 239000011550 stock solution Substances 0.000 description 3
- 230000001360 synchronised effect Effects 0.000 description 3
- 230000003139 buffering effect Effects 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 238000013016 damping Methods 0.000 description 2
- 239000007769 metal material Substances 0.000 description 2
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- -1 sand ions Chemical class 0.000 description 2
- CBVWMGCJNPPAAR-HJWRWDBZSA-N (nz)-n-(5-methylheptan-3-ylidene)hydroxylamine Chemical compound CCC(C)C\C(CC)=N/O CBVWMGCJNPPAAR-HJWRWDBZSA-N 0.000 description 1
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- 238000010276 construction Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 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
- 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
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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
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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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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/50—Photovoltaic [PV] energy
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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 a double-rod linkage type hydraulic drive control system which 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 rod-free cavities and rod-free cavities are formed in the first hydraulic cylinder and the second hydraulic cylinder, the rod-free cavities of the first hydraulic cylinder are connected with the rod-free cavities of the second hydraulic cylinder through pipelines, the first electromagnetic valve and the second electromagnetic valve, the rod-free cavities of the first hydraulic cylinder are connected with the oil tank through the seventh electromagnetic valve and the pipelines, the rod-free cavities of the second hydraulic cylinder are connected with the oil tank through the eighth electromagnetic valve and the pipelines, and the rod-free cavities of the first hydraulic cylinder are connected with the oil outlet of the oil pump through the pipelines and the fourth electromagnetic 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 hydraulic driving part commonly used at present, the hydraulic cylinder comprises a cylinder body, a piston and a plug rod, the piston is installed in the cylinder body in a sliding sealing manner, the plug rod is installed on the piston, the space in the cylinder body is divided into a rod cavity and a rodless cavity by the piston, but the hydraulic cylinder is used in a single-cylinder type mode or is used by only fixing a plurality of hydraulic cylinders together independently, the working modes among the hydraulic cylinders are always independent, and the working among the hydraulic cylinders lacks coordination 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:
The utility model provides a two pole coordinated type hydraulic drive control system, includes 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 rodless chamber and has the pole chamber, connect through pipeline and first solenoid valve and second solenoid valve between the rodless chamber of first pneumatic cylinder and the rodless chamber of second pneumatic cylinder, the rodless chamber of first pneumatic cylinder connects through seventh solenoid valve and pipeline and oil tank, the rodless chamber of second pneumatic cylinder connects through eighth solenoid valve and pipeline and oil tank, the pole chamber of first pneumatic cylinder connects through pipeline and fourth solenoid valve and oil pump's oil-out, the pole chamber of second pneumatic cylinder connects through third solenoid valve, fifth solenoid valve and pipeline and oil pump, the third solenoid valve is in the parallel state with the fifth solenoid valve, the oil tank meets through pipeline and sixth solenoid valve and oil tank, the first pneumatic cylinder meets with the oil tank through the big oil tank of first pneumatic cylinder and sixth solenoid valve.
The synchronous joint debugging of the two hydraulic rods is realized by using the corresponding oil pipes and the corresponding valves in the device, so that the device has higher safety coefficient and wider application range, and can be 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 installed on the oil pump.
The function of the frequency converter is to change the operating frequency of the oil pump according to the use requirement.
Optionally, still include clip groove plate, heat preservation subassembly piece and flexible soft cover, all overlap on first pneumatic cylinder and the second pneumatic cylinder and be equipped with flexible soft cover, the heat preservation subassembly piece overlaps and establishes on flexible soft cover, clip groove plate and heat preservation subassembly piece cooperation are in the same place, set up the screw on the clip groove plate, be provided with the air cushion membrane between clip groove plate and the heat preservation subassembly piece, clip groove plate has formed square enclosure around the heat preservation subassembly piece, flexible soft cover is the flexible soft cover of silica gel or rubber material, and all is provided with the tooth face on the inner wall and the outer wall of flexible soft cover, be provided with the cavity in the mantle wall of flexible soft cover.
Because solar photovoltaic system needs to use the pneumatic cylinder, so this kind of hydraulic drive control system of two pole coordinated type is often used on solar photovoltaic system (specifically install on photovoltaic support, and hydraulic telescoping rod is used for driving the rotation of photovoltaic expansion plate), in this kind of system, owing to used two pneumatic cylinders, in order to link up two pneumatic cylinders smoothly, so further set up the batten, utilize the batten to enclose square enclosure (be used for clamping fixed hydraulic telescoping rod), then set up the screw on the batten again, can utilize two pneumatic cylinders of connecting piece such as bolt screw to fix, so two pneumatic cylinders are fixed more steadily.
The system may need to be used in areas with grasslands, desert isothermal difference changes and large climate changes, so that the flexible sleeve is sleeved on the hydraulic cylinder in the structure, the heat-preserving assembly block is sleeved on the flexible sleeve, the heat-preserving assembly can generate heat, and heat generated by the heat-preserving assembly can preheat the hydraulic cylinder in extremely severe weather, so that hydraulic oil in the hydraulic cylinder can be prevented from being frozen. Simultaneously, the tooth surfaces are arranged on the inner wall and the outer wall of the flexible soft sleeve, and large gaps exist between the flexible soft sleeve and the hydraulic cylinder and between the flexible soft sleeve and the heat insulation assembly block due to the existence of the tooth surfaces, so that rainwater and sand particles can be prevented from being remained between the flexible soft sleeve and the hydraulic cylinder and between the flexible soft sleeve and the heat insulation assembly block (water vapor and sand ions can cause corrosion of the hydraulic cylinder and the heat insulation assembly block).
In the system, the air cushion film is arranged between the groove clamping plate and the heat preservation assembly block, firstly, the damping effect is achieved between the groove clamping plate and the heat preservation assembly block, and secondly, more gaps exist in the air cushion film (water and sand can leak), so that the air cushion film can be used for ensuring that water and sand cannot accumulate between the heat preservation assembly block and the groove clamping plate.
In the flexible soft sleeve, as the tooth surfaces are arranged on the inner wall and the outer wall of the flexible soft sleeve, and the cavity is arranged in the sleeve wall of the flexible soft sleeve, the design can ensure that the flexible soft sleeve has certain telescopic deformation capability, so that the flexible soft sleeve can be better ensured to be clamped between the heat insulation assembly block and the hydraulic cylinder, and the flexible soft sleeve can be suitable for hydraulic cylinders with different width sizes; and the flexible soft sleeve is only contacted with the heat insulation assembly block and the hydraulic cylinder, the flexible soft sleeve is not completely tightly attached to the heat insulation assembly block and the hydraulic cylinder, so that more gaps exist between the heat insulation assembly block and the hydraulic cylinder, when the heat insulation assembly block is impacted to deform (when the deformation amount is relatively smaller), the impact deformation is not transmitted to the hydraulic cylinder, so that the hydraulic cylinder can be prevented from being impacted, deformation is not generated (because the cavity can be compressed, and the occurrence of tooth surfaces can be wrongly twisted).
Optionally, the heat preservation subassembly piece includes the piece main part, offered the through-hole in the piece main part, flexible soft cover is located in the through-hole, set up the stock solution chamber in the piece main part, the stock solution intracavity stores the conduction oil, is provided with the electrothermal tube in the stock solution chamber.
The actual heat preservation assembly block can be actually seen as an oil heater, and the oil heater has the effect of generating heat during low-temperature weather, so that the generated heat can heat the hydraulic cylinder, and the service performance of the hydraulic cylinder is not influenced during low-temperature weather.
The influence of low temperature weather to the pneumatic cylinder has two types, one is that the hydraulic oil is frozen, but because the effect of heat expansion and cooling leads to the appearance of cooperation gap between each spare part, lead to the hydraulic oil to take place the seepage, based on above-mentioned reason, set up above-mentioned flexible soft cover and air cushion membrane in the both sides of thermal insulation subassembly piece, the flexible soft cover of above-mentioned structure and air cushion membrane can play the heat transfer effect, can guarantee like this that the hydraulic oil of pneumatic cylinder can not freeze, secondly because flexible soft cover and air cushion membrane all have great space, the existence in above-mentioned space can let the oil heater heat and scatter away nearby air, these scattered air that go out can form a relatively warm independent microclimate near the pneumatic cylinder, this independent microclimate can play certain protection to pneumatic cylinder, valve and pipeline, reduce spare part because the phenomenon that the difference appears in cooperation gap appears in the degree of heat expansion and cold shrinkage difference, reduce the probability of hydraulic oil leak.
Optionally, the first pneumatic cylinder includes barrel, end cover, piston assembly and cock stem, piston assembly sliding seal sets up in the barrel, the end cover seals up two nozzle departments that set up 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 outside.
Optionally, the piston subassembly includes block, sealed gum cover, a plurality of rubber backing ring, the block is cylindric metal block, has seted up the through-hole in the block, the through-hole cooperation in stopper pole and the block is in the same place, the cushion ring cover is established on the stopper pole, be provided with the nut on the stopper pole, the cushion ring presss from both sides between nut and block, the width of rubber backing ring is unequal, and the width of the rubber backing ring that is nearer apart from the block is wider, 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, the rubber cushion rings have certain flexibility and expansion deformation, so that the piston rod can not generate instantaneous extrusion stress on the block body at the moment of being subjected to tensile force or extrusion force, the block body can be ensured to have stronger service life, meanwhile, a plurality of rubber cushion rings are combined for use, the rubber cushion rings are piled together to form a circular table shape, after the piston rod is installed, the piston rod, the rubber cushion rings and the block body jointly form a structure similar to a spindle body (can be regarded as a circular table on two sides of the block body respectively), the piston similar to the spindle body is opposite to a completely cylindrical piston, the resistance of the moment of moving can be reduced, meanwhile, the weight of the piston assembly can be reduced as much as possible under the premise of ensuring the buffering effect between the piston rod and the block body, and the piston assembly can be ensured to stably slide.
Optionally, the end cover includes first end cover and second end cover, first end cover and second end cover are located two nozzle departments of barrel respectively, all be provided with round platform form chamfer face on first end cover and the second end cover.
The chamfer faces of the round table shape are arranged on the first end cover and the second end cover, so that the design is that the chamfer faces can be matched with the rubber backing ring, the rubber backing ring which is in the round table shape can be tightly attached to the chamfer faces, and the phenomenon that the rubber backing ring is deviated and damaged by extrusion can be avoided when the piston assembly moves to the limit position.
Optionally, the block body and the sealing gum cover are provided with concave and convex which can be mutually matched, and the concave and the convex are mutually embedded and matched together.
In the piston assembly, the block and the sealing rubber sleeve are matched in a protruding and concave embedded manner, so that the matching stability can be ensured, and the sealing rubber sleeve is not easy to fall off from the block.
Optionally, the block is provided with a sinking ring groove, and both sides of the block are provided with sinking ring grooves.
The center point of the sinking ring groove is a through hole on the block, the sinking ring groove is distributed around the through hole of the block, the ring groove has the following functions that firstly, the block body can be guaranteed to have certain expansion and deformation capacity (the width of the groove is reduced or increased, but the width is very tiny), so that the block body and the cylinder body can be stably matched together when the temperature suddenly changes, a matching gap cannot appear, and secondly, the weight of the whole piston assembly can be reduced.
The notch of the concrete sinking ring groove is blocked by the rubber cushion ring, so that when the pressure on one side of the block rises suddenly (a large amount of hydraulic oil is instantaneously poured in), a part of the rubber cushion ring can sink into the sinking ring groove, so that the hydraulic oil is reduced in pressure, the cylinder body and the end cover are prevented from being damaged by the hydraulic oil, and the rubber cushion ring can be restored to the original state when the hydraulic oil is discharged. The rubber cushion ring is deformed and embedded into the sinking ring groove only when the rubber cushion ring is stacked into the round table shape, and the rubber cushion ring above can be easily pressed into buckling deformation by the rubber cushion ring below only when the pressure on one side of the block body is overlarge, and the rubber cushion ring above is not pressed into buckling deformation by the rubber cushion ring below when the diameter is equal to the rubber cushion ring stacked into the cylindrical shape, so that the pressure relief can be realized by the rubber cushion ring which is only ensured to be sunk into the sinking ring groove when the pressure is overlarge by adopting the rubber cushion ring with different widths and stacking into the round table shape.
Optionally, the end cover is a metal end cover, the cylinder is a metal cylinder, and the end cover and the cylinder are made of the same metal.
The same metal material is adopted, so that the matching gap can be formed as much as possible due to thermal expansion and cold contraction, and corrosion caused by the primary battery effect can be avoided.
The beneficial effects of the invention are as follows: through the corresponding oil pipe and valve of combined use, realized the synchronous joint debugging of two hydraulic stems and used, factor of safety is higher, and accommodation is wider.
Drawings
Figure 1 is a schematic and simplified diagram of the working principle of a double-rod linkage type hydraulic drive control system,
Figure 2 is a schematic illustration of the construction of the first hydraulic cylinder,
Figure 3 is a schematic diagram of the first hydraulic cylinder in engagement with the fluted plate,
Figure 4 is a schematic diagram of the mating relationship of the cartridge and the end cap,
Figure 5 is a schematic illustration of the mating relationship of the plunger assembly and the stopper rod,
FIG. 6 is a schematic diagram of the mating relationship of the cartridge, flexible sleeve, and insulation block.
The reference numerals in the drawings are as follows: 101. a first electromagnetic valve; 102. a second electromagnetic valve; 103. a third electromagnetic valve; 104. a fourth electromagnetic valve; 105. a fifth electromagnetic valve; 106. a sixth electromagnetic valve; 107. a seventh electromagnetic valve; 108. an eighth electromagnetic 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 is arranged; 501. a cylinder; 502. a second end cap; 503. a third end cap; 504. a plug rod; 505. a thermal insulation assembly block; 506. a flexible soft sleeve; 507. a slot plate; 508. a nut; 509. a rubber backing ring; 5010. sealing the rubber sleeve; 5011. a block; 5012. and (5) sinking the ring groove.
Detailed Description
The present invention will be described in detail with reference to the accompanying drawings.
As shown in fig. 1, the dual-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 rod-free cavities 511 and rod-free cavities 512 are respectively arranged in the first hydraulic cylinder 51 and the second hydraulic cylinder 52, the rod-free cavities 511 of the first hydraulic cylinder 51 are connected with the rod-free cavities 511 of the second hydraulic cylinder 52 through pipelines and the first electromagnetic valve 101 and the second electromagnetic valve 102, the rod-free cavities 511 of the first hydraulic cylinder 51 are connected with the oil tank 2 through a seventh electromagnetic valve 107 and the pipelines, the rod-free cavities 511 of the second hydraulic cylinder 52 are connected with the oil tank through the eighth electromagnetic valve 108 and the pipelines, the rod-free cavities 512 of the first hydraulic cylinder 51 are connected with the oil pump 3 through the pipelines and the fourth electromagnetic valve 104, the rod-free cavities 512 of the second hydraulic cylinder 52 are connected with the third electromagnetic valve 103, the fifth electromagnetic valve 103 and the fifth electromagnetic valve 105 and the oil pump 3 through the pipelines and the third electromagnetic valve 3, the rod-free cavities 511 of the first hydraulic cylinder 51 are connected with the oil tank 2 in parallel with the third electromagnetic valve 2 and the oil tank 2, the rod-free cavities 511 of the first hydraulic cylinder 51 are connected with the fourth electromagnetic valve 2 through the pipeline and the fourth electromagnetic valve 2.
The synchronous joint debugging of the two hydraulic rods is realized by using the corresponding oil pipes and the corresponding valves in the device, so that the device has higher safety coefficient and wider application range, and can be 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, the oil pump 3 is provided with a frequency converter 4.
The function of the frequency converter 4 is to vary the operating frequency of the oil pump 3 according to the use requirements.
The hydraulic cylinder is structured as follows, the area of the piston in the rod chamber 512 is A1, the area of the rodless chamber 511 is A2, A1 < A2 (because the presence of the stopper rod 504 reduces the contact area between the piston and the hydraulic oil), the pressures in the rod chamber 512 and the rodless chamber 511 are P, the external force F1 is p×a2 when the hydraulic oil enters from the rodless chamber 511, and the external force F2 is p×a1 and F1 < F2 when the hydraulic oil enters from the rod chamber 512.
The cooperative working mode of the system is as follows.
When the oil pump 3 is reversed (oil is returned to the oil tank 2), the first electromagnetic valve 101, the second electromagnetic valve 102, the fifth electromagnetic valve 105 and the sixth electromagnetic valve 106 are opened, the other electromagnetic valves are closed, the plug rod 504 of the second hydraulic cylinder 52 is extended, the plug rod 504 of the first hydraulic cylinder 51 is retracted, the two hydraulic cylinders move synchronously, the resultant force of the first hydraulic cylinder 51 and the second hydraulic cylinder 52 is PxA1+PxA2 no matter the hydraulic cylinders are extended or retracted, the secondary operation mode can be used in the occasion that the extended and retracted forces are consistent,
The oil pump 3 rotates forward (pumps 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 stopper rod 504 of the second hydraulic cylinder 52 is retracted, and the stopper rod 504 of the first hydraulic cylinder 51 is retracted; the oil pump 3 is reversed, the third electromagnetic valve 103, the fourth electromagnetic valve 104, the seventh electromagnetic valve 107 and the eighth electromagnetic valve 108 are opened, other electromagnetic valves are closed, the plug rod 504 of the second hydraulic cylinder 52 is extended, the plug rod 504 of the first hydraulic cylinder 51 is extended, the two hydraulic cylinders synchronously move, and the secondary working mode can be used in occasions where the forces required to be extended and retracted are inconsistent and the two forces have larger difference.
As shown in fig. 3 and 6, the flexible hydraulic sleeve further comprises a slot plate 507, a heat insulation assembly block 505 and a flexible soft sleeve 506, wherein the flexible soft sleeve 506 is sleeved on the first hydraulic cylinder 51 and the second hydraulic cylinder 52, the heat insulation assembly block 505 is sleeved on the flexible soft sleeve 506, the slot plate 507 is matched with the heat insulation assembly block 505, screw holes are formed in the slot plate, an air cushion film is arranged between the slot plate and the heat insulation assembly block 505, a square enclosing part is formed around the heat insulation assembly block 505 by the slot plate, the flexible soft sleeve 506 is made of silica gel or rubber, tooth surfaces are arranged on the inner wall and the outer wall of the flexible soft sleeve 506, and a cavity is formed in the sleeve wall of the flexible soft sleeve 506.
Because solar photovoltaic system needs to use the pneumatic cylinder, so this kind of hydraulic drive control system of two pole coordinated type is often used on solar photovoltaic system (specifically install on photovoltaic support, and hydraulic telescoping rod is used for driving the rotation of photovoltaic expansion plate), in this kind of system, owing to used two pneumatic cylinders, in order to link up two pneumatic cylinders smoothly, so further set up the batten, utilize the batten to enclose square enclosure (be used for clamping fixed hydraulic telescoping rod), then set up the screw on the batten again, can utilize two pneumatic cylinders of connecting piece such as bolt screw to fix, so two pneumatic cylinders are fixed more steadily.
The system may need to be used in the areas with grasslands, desert isothermal difference changes and large climate changes, so the flexible sleeve 506 is sleeved on the hydraulic cylinder in the structure, the heat-preserving component block 505 is sleeved on the flexible sleeve 506, the heat-preserving component can generate heat, and the heat generated by the heat-preserving component can preheat the hydraulic cylinder in extremely severe weather, so that the hydraulic oil in the hydraulic cylinder can be prevented from being frozen. Simultaneously, the tooth surfaces are arranged on the inner wall and the outer wall of the flexible soft sleeve 506, and larger gaps exist between the flexible soft sleeve 506 and the hydraulic cylinder and between the flexible soft sleeve 506 and the heat insulation assembly block 505 due to the existence of the tooth surfaces, so that rainwater and sand particles can be prevented from being remained between the flexible soft sleeve 506 and the hydraulic cylinder and between the flexible soft sleeve 506 and the heat insulation assembly block 505 (water vapor and sand ions can cause corrosion of the hydraulic cylinder and the heat insulation assembly block 505).
In the system, the air cushion film is arranged between the groove clamping plate and the heat insulation assembly block 505, firstly, the damping effect is achieved between the groove clamping plate and the heat insulation assembly block 505, and secondly, more gaps (water and sand can leak) exist in the air cushion film, so that the air cushion film can be used for ensuring that water and sand cannot accumulate between the heat insulation assembly block 505 and the groove clamping plate.
In the flexible soft sleeve 506, as the tooth surfaces are arranged on the inner wall and the outer wall of the flexible soft sleeve 506, and the hollow cavity is arranged in the sleeve wall of the flexible soft sleeve 506, the design can ensure that the flexible soft sleeve 506 has a certain telescopic deformation capability, so that the flexible soft sleeve 506 can be better ensured to be clamped between the heat insulation assembly block 505 and the hydraulic cylinder, and the hydraulic cylinder with different width sizes can be adapted; and flexible soft cover 506 only contacts with insulation pack block 505 and pneumatic cylinder, flexible soft cover 506 is not closely the insulation pack block 505 and pneumatic cylinder completely, just so have more spaces between insulation pack block 505 and the pneumatic cylinder, when insulation pack block 505 is by striking take place deformation (deformation volume is when 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 tooth face can take place wrong turn round).
As shown in fig. 3 and 6, the heat insulation assembly block 505 comprises a block main body, wherein a through hole is formed in the block main body, a flexible soft sleeve 506 is positioned 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 assembly block 505 can be actually seen as an oil heater, and the oil heater is used for generating heat during low-temperature weather, so that the generated heat can heat the hydraulic cylinder, and the service performance of the hydraulic cylinder is not affected during low-temperature weather.
The influence of low temperature weather on the hydraulic cylinder is two types, one type is that hydraulic oil is frozen, but because the effect of thermal expansion and cooling causes the fit gap to appear between each spare part, the hydraulic oil leaks, based on the reason, set up above-mentioned flexible soft cover 506 and air cushion membrane in the both sides of thermal insulation subassembly piece 505, the flexible soft cover 506 and the air cushion membrane of above-mentioned structure can play the heat transfer effect, can guarantee like this that the hydraulic oil of hydraulic cylinder can not freeze, secondly because flexible soft cover 506 and air cushion membrane all have great space, the existence in above-mentioned space can let the oil heater heat nearby air and scatter away, these scattered air that go out can form a relatively warm independent microclimate near the hydraulic cylinder, this independent microclimate can play certain protection to hydraulic cylinder, valve and pipeline, reduce spare part because the phenomenon that the thermal expansion degree is different and the fit gap difference appears, reduce the probability of hydraulic oil leak.
As shown in fig. 2 and 3, the first hydraulic cylinder 51 includes a cylinder 501, an end cover, a piston assembly and a plug rod 504, the piston assembly is slidably sealed in the cylinder 501, the end cover is sealed at two cylinder ports of the cylinder 501, the plug rod 504 is mounted on the piston assembly, one end of the plug rod 504 is located in the cylinder 501, and the other end of the plug rod 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 gaskets 509, the block 5011 is a cylindrical metal block 5011, a through hole is formed in the block 5011, the plug rod 504 is matched with the through hole in the block 5011, the rubber gaskets 509 are sleeved on the plug rod 504, the plug rod 504 is provided with a nut 508, the rubber gaskets 509 are clamped between the nut 508 and the block 5011, the rubber gaskets 509 are unequal in width, and the width of the rubber gaskets 509 nearer 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 cushion rings 509 are arranged on two sides of a block 5011, the rubber cushion rings 509 have certain flexibility and expansion deformation, so that the piston rod 504 can not generate instantaneous extrusion stress on the block 5011 at the moment of being subjected to tensile force or extrusion force, the block 5011 can be ensured to have stronger service life, meanwhile, a plurality of rubber cushion rings 509 are combined to be used, the rubber cushion rings 509 are piled together to form a round table shape, after the piston rod 504 is installed, the rubber cushion rings 509 and the block 5011 jointly form a structure similar to a spindle body (namely, the two sides of the block 5011 can be respectively provided with a round table), the piston similar to the spindle body can reduce resistance at the moment of starting to move relative to a completely cylindrical piston, meanwhile, the weight of the piston assembly can be reduced as much as possible on the premise of ensuring the buffering effect between the piston rod 504 and the block 5011, and the piston assembly can slide stably.
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 ports of the cylinder 501, and truncated cone chamfer faces are respectively provided on the first end cap and the second end cap 502.
The round table-shaped chamfer surfaces are arranged on the first end cover and the second end cover 502, so that the round table-shaped chamfer surfaces can be matched with the rubber cushion rings 509, the rubber cushion rings 509 stacked in the round table shape can be tightly attached to the chamfer surfaces, and the phenomena that the rubber cushion rings 509 are deviated and damaged by extrusion can not occur when the piston assembly moves to the limit position are ensured.
As shown in fig. 5, the block 5011 and the sealant sleeve 5010 are provided with concave and convex parts which can be mutually matched, and the concave and the convex parts are mutually embedded and matched together.
In the piston assembly, the block 5011 and the sealing rubber sleeve 5010 are matched in a protruding and concave embedded manner, so that the matching stability can be ensured, and the sealing rubber sleeve 5010 is not easy to fall off from the block 5011.
As shown in fig. 5, the block 5011 is provided with a sink groove 5012, and both sides of the block 5011 are provided with a sink groove 5012.
The center point of the sinking ring groove 5012 is a through hole on the block 5011, the sinking ring groove 5012 is distributed around the through hole of the block 5011, the ring groove has the following functions, firstly, the block 5011 can be ensured to have certain expansion and contraction deformation capability (the width of the groove is reduced or increased, but the amplitude is very tiny), thus, the block 5011 and the cylinder 501 can be stably matched together when the temperature suddenly changes, no matching gap can be generated, and secondly, the weight of the whole piston assembly can be reduced.
The notch of the concrete sinking ring groove 5012 is blocked by the rubber cushion ring 509, so that when pressure sudden rise (a large amount of hydraulic oil is instantaneously poured into) occurs on one side of the block 5011, a part of the rubber cushion ring 509 can sink into the sinking ring groove 5012, thereby realizing the pressure reduction of the hydraulic oil, avoiding the pressure loss of the cylinder 501 and the end cover by the hydraulic oil, and when the hydraulic oil is discharged, the rubber cushion ring 509 can be restored to the original state. Only when the rubber cushion ring 509 is stacked into a circular truncated cone shape, the rubber cushion ring 509 can be deformed and embedded into the sinking ring groove 5012 when the pressure on one side of the block 5011 is overlarge, because only the stacked circular truncated cone shape is formed, the upper rubber cushion ring 509 is easy to press the lower rubber cushion ring 509 into warp deformation, and for the rubber cushion ring 509 with the same diameter and stacked into a cylindrical shape, the upper rubber cushion ring 509 does not press the lower rubber cushion ring 509 into warp deformation trend, so that only the rubber cushion rings 509 with different widths are adopted and stacked into the circular truncated cone shape, the rubber cushion ring 509 can be sunk into the sinking ring groove 5012 to realize pressure relief when the pressure is overlarge.
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 the matching gap can be formed as much as possible due to thermal expansion and cold contraction, and corrosion caused by the primary battery effect can be avoided.
The present embodiment provides a photovoltaic bracket using the double-rod linkage type hydraulic drive control system as described above.
The foregoing description is only of the preferred embodiments of the present invention, and is not intended to limit the scope of the invention, but is intended to cover all equivalent modifications, direct or indirect, as applied to other related technical fields.
Claims (9)
1. The 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 rod-free cavities and rod-free cavities are formed in the first hydraulic cylinder and the second hydraulic cylinder respectively, the rod-free cavities of the first hydraulic cylinder are connected with the rod-free cavities of the second hydraulic cylinder through pipelines and the first electromagnetic valve and the second electromagnetic valve, the rod-free cavities of the first hydraulic cylinder are connected with the oil tank through the seventh electromagnetic valve and the pipelines, the rod-free cavities of the second hydraulic cylinder are connected with the oil tank through the eighth electromagnetic valve and the pipelines, the rod-free cavities of the first hydraulic cylinder are connected with the oil pump through the third electromagnetic valve, the fifth electromagnetic valve and the pipelines, the third electromagnetic valve is in a parallel state with the fifth electromagnetic valve, the oil tank is connected with the oil pump, and the first rod-free cavities of the first hydraulic cylinder are connected with the oil tank through the sixth electromagnetic valve and the first hydraulic cylinder;
still include clip groove plate, heat preservation subassembly piece and flexible soft cover, all overlap on first pneumatic cylinder and the second pneumatic cylinder and be equipped with flexible soft cover, the heat preservation subassembly piece overlaps and establishes on flexible soft cover, clip groove plate and heat preservation subassembly piece cooperate together, set up the screw on the clip groove plate, be provided with the air cushion membrane between clip groove plate and the heat preservation subassembly piece, clip groove plate has formed square enclosure around the heat preservation subassembly piece, flexible soft cover is the flexible soft cover of silica gel or rubber material, and all is provided with the flank of tooth on the inner wall and the outer wall of flexible soft cover, be provided with the cavity in the mantle wall of flexible soft cover.
2. The dual lever linked hydraulic drive control system of 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, wherein the heat insulation 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.
4. The dual rod linked hydraulic drive control system of claim 1, wherein the first hydraulic cylinder comprises a barrel, an end cap, a piston assembly and a plug rod, the piston assembly is slidably sealed in the barrel, the end cap is sealed at two ports of the barrel, the plug rod is mounted on the piston assembly, one end of the plug rod is located in the barrel, and the other end of the plug rod is located outside the barrel.
5. The dual-rod linkage hydraulic drive control system according to claim 4, 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, through holes are formed in the block body, the plug rod is matched with the through holes in the block body, the rubber cushion rings are sleeved on the plug rod, nuts are arranged on the plug rod, the rubber cushion rings are clamped between the nuts and the block body, the widths of the rubber cushion rings are unequal, the width of the rubber cushion rings which are closer to the block body is wider, and the sealing rubber sleeve is sleeved on the outer wall of the block body.
6. The dual-rod linkage hydraulic drive control system according to claim 5, 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 positioned at two cylinder openings of the cylinder body, and truncated cone-shaped chamfer faces are arranged on the first end cap and the second end cap.
7. The dual lever linked hydraulic drive control system of claim 5, further comprising a recess and a protrusion on the block and the sealant sleeve that are capable of mating with each other, the recess and the protrusion being mated with each other.
8. The dual lever linked hydraulic drive control system of claim 5, wherein the block has a counter-sunk groove disposed thereon, and wherein the block has counter-sunk grooves disposed on both sides thereof.
9. The dual lever ganged-type hydraulic drive control system of claim 5, wherein the end cap is a metallic end cap, the cylinder is a metallic cylinder, and the end cap and the cylinder are made of the same metal.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410476157.5A CN118548273A (en) | 2021-10-28 | 2021-10-28 | Photovoltaic bracket |
| CN202111264236.2A CN113944678B (en) | 2021-10-28 | 2021-10-28 | Double-rod linkage type hydraulic driving control system |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202111264236.2A CN113944678B (en) | 2021-10-28 | 2021-10-28 | Double-rod linkage type hydraulic driving control system |
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| CN202410476157.5A Division CN118548273A (en) | 2021-10-28 | 2021-10-28 | Photovoltaic bracket |
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| CN202410476157.5A Pending CN118548273A (en) | 2021-10-28 | 2021-10-28 | Photovoltaic bracket |
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| CN118548273A (en) | 2024-08-27 |
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