CN114483703A - Rock mechanics high-amplitude-frequency response characteristic hydraulic actuator - Google Patents
Rock mechanics high-amplitude-frequency response characteristic hydraulic actuator Download PDFInfo
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- CN114483703A CN114483703A CN202210190037.XA CN202210190037A CN114483703A CN 114483703 A CN114483703 A CN 114483703A CN 202210190037 A CN202210190037 A CN 202210190037A CN 114483703 A CN114483703 A CN 114483703A
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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
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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
- F15B15/1457—Piston rods
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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
- F15B15/1457—Piston rods
- F15B15/1461—Piston rod 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
- F15B15/149—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
- F15B15/202—Externally-operated valves mounted in or on the actuator
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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
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
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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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0629—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion
- F16C32/064—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a liquid cushion, e.g. oil cushion the liquid being supplied under pressure
- F16C32/0651—Details of the bearing area per se
- F16C32/0655—Details of the bearing area per se of supply openings
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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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0681—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load
- F16C32/0685—Construction or mounting aspects of hydrostatic bearings, for exclusively rotary movement, related to the direction of load for radial load only
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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
- F16N—LUBRICATING
- F16N1/00—Constructional modifications of parts of machines or apparatus for the purpose of lubrication
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Abstract
A hydraulic actuator with high amplitude-frequency response characteristics in rock mechanics is characterized in that a piston rod is of a lightweight composite structure and consists of an inner rod body and an outer rod body which are fixedly sleeved, wherein the inner rod body is of a hollow rod structure and is made of titanium alloy; a piston is arranged in the middle of the outer rod body, a plurality of annular oil grooves are uniformly distributed on the circumferential surface of the piston along the axial direction, and the piston is in clearance fit with the inner surface of the cylinder barrel; the outer rod body and the piston are of an integrated structure and made of carbon fibers; ceramic coating films are arranged on the outer surfaces of the outer rod body and the piston; a lubricating oil film and a gap seal are formed in a gap between the piston and the inner surface of the cylinder barrel, and the piston is separated from the inner surface of the cylinder barrel to be in direct contact through the lubricating oil film; the inner surfaces of piston rod through holes of the upper and lower cylinder covers are in clearance fit with the piston rods, and static oil grooves are uniformly distributed along the circumferential direction on the inner surfaces of the piston rod through holes; the static pressure oil groove is used for forming a static pressure lubrication supporting oil pad, and the piston rod is separated from the inner surface of the piston rod penetrating hole of the upper cylinder cover and the lower cylinder cover through the static pressure lubrication supporting oil pad.
Description
Technical Field
The invention belongs to the technical field of rock mechanics experimental instruments, and particularly relates to a rock mechanics high amplitude-frequency response characteristic hydraulic actuator.
Background
The engineering activities of human beings in the rock crib are increasingly frequent, and the depth is continuously deepened, for example, the engineering activities of deep scientific drilling, deep oil and gas resource development, deep geothermal development, deep metal mining and coal mining, deep railway tunnel burying and the like in the continental/ocean rock crib. Deep rock masses serving as engineering objects bear the combined action of initial three-dimensional orthogonal ground stress static load and dynamic load excited by engineering blasting/mechanical rock breaking and the like, and only by developing rock mechanics experiment simulation research oriented to dynamic disturbance triggering rock breaking can the understanding of a rock critical instability dynamic induction mechanism be facilitated, and the rock structure dynamics experiment basic data of an earthquake induction mechanism can be obtained more beneficially.
After a rock engineering enters a deep part, the three-dimensional orthogonal ground stress of an original rock is obviously improved, under the stress environment, the engineering rock is influenced by dynamic disturbance generated in the rock breaking process of a TBM (tunnel boring machine) and a drilling and blasting method when being excavated/tunneled, a plurality of dynamic disasters such as rock explosion, collapse and the like are generated on surrounding rocks of a tunnel, and the dynamic disasters can not only cause equipment damage and economic loss and endanger the life safety of constructors, but also can influence the structural stability of the engineering rock with large scale, so that the disturbance type dynamic disasters of the deep engineering rock become a key bottleneck problem restricting the safety construction of the deep engineering.
In the process of rock breaking by a drilling and blasting method, the frequency during mechanical impact drilling can reach hundreds of Hz, the high-frequency component of the blasting impact load frequency can reach MHz level, and the TBM mechanical rock breaking can generate circulating low-frequency vibration waves from a few Hz to hundreds of Hz. In addition, in the process of mechanical rock breaking by TBM and rock breaking by drilling and blasting, the generated shock wave can form medium and low frequency disturbance stress wave with the frequency range of 1-100Hz in the rock mass due to multiple oscillation and attenuation, and the rock mass with critical strength can be damaged under the strain rate.
Therefore, the experiment of high-frequency dynamic load of the rock under the high stress condition is necessary, only through the experiment of the high-frequency dynamic load under the high stress condition, progressive fracture and rapid dynamic fracture mechanism under the deep hard rock dynamic disturbance can be better known, a hydraulic actuator with high (large) load output, high speed, high frequency and long-time cyclic excitation becomes a key part for developing relevant rock mechanics experiment research, because the hydraulic actuator has high energy conversion efficiency, large output load and easy control, more than 98 percent of rock mechanics experiment machines adopt a loading mode based on the hydraulic actuator, and only few parts of soft rock mechanics experiment machines with low load output adopt electric servo cylinders.
From the 20 th century and the 70 th century, the hydraulic actuator gradually develops from meeting the requirements of a static force tester to meeting the requirements of a power tester with certain low load, low frequency and low amplitude performance, and the dynamic load of the commercial hydraulic actuator meeting the requirements at the stage at present can maximally output 200 plus 2000kN and the amplitude can output 1-5mm under the frequency band of 5-10 Hz, but nevertheless, the commercial hydraulic actuators still can not meet the rock mechanics experiment conditions required by higher amplitude frequency characteristics, so that the high (large) load and high-frequency dynamic rock triaxial/true triaxial tester capable of simultaneously simulating the disturbance failure behavior of deep engineering at the present stage can not be made into the market all the time. Therefore, the response frequency of the dynamic hydraulic actuator has become an experimental bottleneck problem which restricts the development of medium and low frequency dynamic loads.
Disclosure of Invention
Aiming at the problems in the prior art, the invention provides a hydraulic actuator with rock mechanics high amplitude-frequency response characteristic, which greatly improves the dynamic response capability of the hydraulic actuator through a lightweight and low-friction design scheme, can simulate the experimental requirements of hard rock on dynamic load output of 500kN and vibration amplitude of 1mm when high static load is 3000kN and the upper limit frequency is 100Hz, provides necessary conditions for the dynamic disturbance and destruction experimental study of deep hard rock, and provides technical support for a high (large) load and high-frequency dynamic rock triaxial/true triaxial experimental machine capable of simultaneously simulating the disturbance and destruction behaviors of deep engineering.
In order to achieve the purpose, the invention adopts the following technical scheme: a hydraulic actuator with rock mechanics high amplitude-frequency response characteristics comprises a piston rod, a cylinder barrel, an upper cylinder cover and a lower cylinder cover, wherein the cylinder barrel is coaxially sleeved on the outer side of the piston rod, the upper cylinder cover is arranged at an upper cylinder opening of the cylinder barrel, the lower cylinder cover is arranged at a lower cylinder opening of the cylinder barrel, the upper end of the piston rod penetrates through the upper cylinder cover in a sealing manner, the lower end of the piston rod penetrates through the lower cylinder cover in a sealing manner, and the upper cylinder cover and the lower cylinder cover are identical in structure and are distributed in mirror symmetry; the piston rod is of a lightweight composite structure and comprises an inner rod body and an outer rod body, and the outer rod body is fixedly sleeved on the outer side of the inner rod body; the inner rod body is of a hollow rod structure and is made of titanium alloy; a piston is arranged in the middle of the outer rod body, a plurality of annular oil grooves are uniformly distributed on the circumferential surface of the piston along the axial direction, and the piston is in clearance fit with the inner surface of the cylinder barrel; the outer rod body and the piston are of an integrated structure and made of carbon fibers; and ceramic coating films are arranged on the outer surfaces of the outer rod body and the piston.
The clearance between the piston and the inner surface of the cylinder barrel is used for forming a lubricating oil film and a clearance seal, and the piston is separated from the inner surface of the cylinder barrel to be directly contacted through the lubricating oil film; the annular oil groove is used for dynamically storing hydraulic oil required by the formation of the lubricating oil film.
The upper cylinder cover is tightly connected with the upper opening of the cylinder barrel through a plurality of high-strength bolts which are uniformly distributed in the circumferential direction, and a sealing ring is arranged between the upper cylinder cover and the upper opening of the cylinder barrel; the lower cylinder cover is also fastened and connected with the lower opening of the cylinder barrel through a plurality of high-strength bolts which are uniformly distributed in the circumferential direction, and a sealing ring is also arranged between the lower cylinder cover and the lower opening of the cylinder barrel.
The inner surface of a piston rod penetrating hole of the upper cylinder cover is in clearance fit with the piston rod; the inner surface of a piston rod penetrating hole of the upper cylinder cover is provided with a plurality of upper static pressure oil grooves which are uniformly distributed along the circumferential direction; an upper static pressure oil supply pipeline is arranged in the upper cylinder cover and is directly communicated with the upper static pressure oil groove; an upper static pressure oil return pipeline is arranged in the upper cylinder cover, and the upper static pressure oil return pipeline is communicated with the upper static pressure oil groove through a gap between the inner surface of a piston rod penetrating hole of the upper cylinder cover and the piston rod; a throttle valve is arranged in the upper static pressure oil supply pipeline; and sealing rings are respectively arranged on the inner surfaces of the piston rod penetrating holes on the two axial sides of the upper static pressure oil groove, and dust rings are also arranged on the outer sides of the outer end sealing rings.
The inner surface of a piston rod penetrating hole of the lower cylinder cover is in clearance fit with the piston rod; a plurality of lower static pressure oil grooves are formed in the inner surface of a piston rod penetrating hole of the lower cylinder cover, and the plurality of lower static pressure oil grooves are uniformly distributed along the circumferential direction; a lower static pressure oil supply pipeline is arranged in the lower cylinder cover and is directly communicated with the lower static pressure oil groove; a lower static pressure oil return pipeline is arranged in the lower cylinder cover, and the lower static pressure oil return pipeline is communicated with a lower static pressure oil groove through a gap between the inner surface of a piston rod penetrating hole of the lower cylinder cover and the piston rod; a throttle valve is arranged in the lower static pressure oil supply pipeline; and sealing rings are respectively arranged on the inner surfaces of the piston rod penetrating holes on the two axial sides of the lower static pressure oil groove, and dust rings are also arranged on the outer sides of the outer end sealing rings.
An oil return communication pipeline is arranged in the cylinder barrel, and the upper static pressure oil return pipeline is communicated with the lower static pressure oil return pipeline through the oil return communication pipeline.
And the upper static pressure oil groove and the lower static pressure oil groove are internally used for forming a static pressure lubrication supporting oil pad, and the piston rod is separated from the inner surfaces of the piston rod penetrating holes of the upper cylinder cover and the lower cylinder cover by the static pressure lubrication supporting oil pad.
The hydraulic cylinder is characterized in that an integrated valve block is arranged on the outer surface of the cylinder barrel, two servo valves are installed on the integrated valve block in parallel, an oil cavity of the hydraulic cylinder is connected with a hydraulic system sequentially through the integrated valve block and the servo valves, and an energy accumulator used for stabilizing the pressure of the hydraulic system is further installed on the integrated valve block.
And the top end of the piston rod is provided with a force measuring sensor, and the force measuring sensor is fixedly connected with the piston rod through a switching adapter.
The piston rod bottom is provided with displacement sensor, and displacement sensor one end passes through protection casing and lower cylinder cap fixed connection, and the displacement sensor other end is connected with the piston rod cooperation.
The invention has the beneficial effects that:
according to the hydraulic actuator with the rock mechanics high amplitude-frequency response characteristic, the dynamic response capability of the hydraulic actuator is greatly improved through a lightweight and low-friction design scheme, the experimental requirements that the dynamic load output can reach 500kN and the vibration amplitude can reach 1mm when the hard rock is under a high static load of 3000kN and the upper limit frequency is 100Hz can be simulated, necessary conditions are provided for the dynamic disturbance and destruction experimental research of deep hard rock, and technical support is provided for a high (large) load and high-frequency dynamic rock triaxial/true triaxial experimental machine capable of simultaneously simulating the disturbance and destruction behaviors of deep engineering.
Drawings
FIG. 1 is a perspective view of a hydraulic actuator with high amplitude-frequency response characteristics for rock mechanics according to the present invention;
FIG. 2 is a cross-sectional view of a hydraulic actuator with high amplitude-frequency response characteristics for rock mechanics according to the present invention;
FIG. 3 is a perspective view of the piston rod of the present invention;
FIG. 4 is a cross-sectional view of the piston rod of the present invention;
FIG. 5 is an enlarged view of portion I of FIG. 4;
FIG. 6 is a graph of an amplitude-frequency performance test of a hydraulic actuator with high amplitude-frequency response characteristics in rock mechanics according to the present invention;
in the figure, 1-piston rod, 1-inner rod body, 1-2-outer rod body, 1-3-piston, 1-4-annular oil groove, 2-cylinder barrel, 2-1-oil return communication pipeline, 3-upper cylinder cover, 3-1-upper static pressure oil groove, 3-2-upper static pressure oil supply pipeline, 3-upper static pressure oil return pipeline, 4-lower cylinder cover, 4-1-lower static pressure oil groove, 4-2-lower static pressure oil supply pipeline, 4-3-lower static pressure oil return pipeline, 5-high-strength bolt, 6-sealing ring, 7-throttling valve, 8-dust-proof ring, 9-integrated valve block, 10-servo valve, 11-energy accumulator, 12-force measuring sensor, 13-adapter, 14-displacement sensor and 15-protective cover.
Detailed Description
The invention is described in further detail below with reference to the figures and the specific embodiments.
As shown in fig. 1 to 5, the hydraulic actuator with high amplitude-frequency response characteristics for rock mechanics comprises a piston rod 1, a cylinder barrel 2, an upper cylinder cover 3 and a lower cylinder cover 4, wherein the cylinder barrel 2 is coaxially sleeved outside the piston rod 1, the upper cylinder cover 3 is arranged at an upper cylinder opening of the cylinder barrel 2, the lower cylinder cover 4 is arranged at a lower cylinder opening of the cylinder barrel 2, the upper end of the piston rod 1 penetrates through the upper cylinder cover 3 in a sealing manner, the lower end of the piston rod 1 penetrates through the lower cylinder cover 4 in a sealing manner, and the upper cylinder cover 3 and the lower cylinder cover 4 are completely identical in structure and are distributed in mirror symmetry; the piston rod 1 is of a light composite structure and comprises an inner rod body 1-1 and an outer rod body 1-2, and the outer rod body 1-2 is fixedly sleeved on the outer side of the inner rod body 1-1; the inner rod body 1-1 is of a hollow rod structure, and the inner rod body 1-1 is made of titanium alloy; the middle part of the outer rod body 1-2 is provided with a piston 1-3, a plurality of annular oil grooves 1-4 are uniformly distributed on the circumferential surface of the piston 1-3 along the axial direction, and the piston 1-3 is in clearance fit with the inner surface of the cylinder barrel 2; the outer rod body 1-2 and the piston 1-3 are of an integrated structure and made of carbon fibers; and ceramic coating films are arranged on the outer surfaces of the outer rod body 1-2 and the piston 1-3.
Specifically, because the piston rod 1 adopts the lightweight composite structure, the whole mass of the piston rod 1 is greatly reduced, the energy consumption of the piston rod 1 during movement is further reduced, and the inertia influence is reduced to the maximum extent. The inner rod body 1-1 is made of a titanium alloy material, the outer rod body 1-2 and the piston 1-3 which are of an integrated structure are made of carbon fibers, the lightweight requirement is met, the outer rod body 1-2 and the piston 1-3 have excellent corrosion resistance, the hollow structure of the inner rod body 1-1 further achieves lightweight on the structural level, and the final purpose of lightweight design is that the hydraulic actuator is easy to achieve low-frequency disturbance and impact damage and the loading strain rate is improved. The ceramic coating films on the outer surfaces of the outer rod body 1-2 and the piston 1-3 can further reduce friction and improve the corrosion resistance of the piston rod 1.
A lubricating oil film and a gap seal are formed in a gap between the piston 1-3 and the inner surface of the cylinder barrel 2, and the piston 1-3 is separated from the inner surface of the cylinder barrel 2 to be in direct contact through the lubricating oil film; the annular oil grooves 1-4 are used for dynamically storing hydraulic oil required by the formation of the lubricating oil film.
Specifically, as the pistons 1 to 3 and the inner surface of the cylinder barrel 2 are in clearance fit, hydraulic oil leakage clearances are formed between oil cavities of the cylinder barrel 2 on two sides of the pistons 1 to 3, but the clearance leakage quantity of the hydraulic oil has very little influence on pressure change in the oil cavities through calculation of Bernoulli equation and can be ignored, and the hydraulic oil leaked from the clearances can be compensated by a special main hydraulic oil source through a servo valve, so that the clearances between the pistons 1 to 3 and the inner surface of the cylinder barrel 2 can fully utilize the formed lubricating oil film to reduce the friction force between the pistons and the cylinder barrel 2.
The upper cylinder cover 3 is tightly connected with the upper opening of the cylinder barrel 2 through a plurality of high-strength bolts 5 which are uniformly distributed in the circumferential direction, and a sealing ring 6 is arranged between the upper cylinder cover 3 and the upper opening of the cylinder barrel 2; the lower cylinder cover 4 is also fastened and connected with the lower opening of the cylinder barrel 2 through a plurality of high-strength bolts 5 which are uniformly distributed in the circumferential direction, and a sealing ring 6 is also arranged between the lower cylinder cover 4 and the lower opening of the cylinder barrel 2.
The inner surface of a piston rod 1 penetrating hole of the upper cylinder cover 3 is in clearance fit with the piston rod 1; the inner surface of a through hole of a piston rod 1 of the upper cylinder cover 3 is provided with a plurality of upper static pressure oil grooves 3-1, and the plurality of upper static pressure oil grooves 3-1 are uniformly distributed along the circumferential direction; an upper static pressure oil supply pipeline 3-2 is arranged in the upper cylinder cover 3, and the upper static pressure oil supply pipeline 3-2 is directly communicated with an upper static pressure oil groove 3-1; an upper static pressure oil return pipeline 3-3 is arranged in the upper cylinder cover 3, and the upper static pressure oil return pipeline 3-3 is communicated with an upper static pressure oil groove 3-1 through a gap between the inner surface of a through hole of a piston rod 1 of the upper cylinder cover 3 and the piston rod 1; a throttle valve 7 is arranged in the upper static pressure oil supply pipeline 3-2; sealing rings 6 are respectively arranged on the inner surfaces of the penetrating holes of the piston rods 1 on the two axial sides of the upper static pressure oil groove 3-1, and dust rings 8 are arranged on the outer sides of the outer end sealing rings 6.
The inner surface of a piston rod 1 penetrating hole of the lower cylinder cover 4 is in clearance fit with the piston rod 1; a plurality of lower static pressure oil grooves 4-1 are arranged on the inner surface of a penetrating hole of a piston rod 1 of the lower cylinder cover 4, and the plurality of lower static pressure oil grooves 4-1 are uniformly distributed along the circumferential direction; a lower static pressure oil supply pipeline 4-2 is arranged in the lower cylinder cover 4, and the lower static pressure oil supply pipeline 4-2 is directly communicated with a lower static pressure oil groove 4-1; a lower static pressure oil return pipeline 4-3 is arranged in the lower cylinder cover 4, and the lower static pressure oil return pipeline 4-3 is communicated with a lower static pressure oil groove 4-1 through a gap between the inner surface of a penetrating hole of a piston rod 1 of the lower cylinder cover 4 and the piston rod 1; a throttle valve 7 is arranged in the lower static pressure oil supply pipeline 4-2; sealing rings 6 are respectively arranged on the inner surfaces of the penetrating holes of the piston rods 1 on the two axial sides of the lower static pressure oil groove 4-1, and dust rings 8 are arranged on the outer sides of the outer end sealing rings 6.
An oil return communication pipeline 2-1 is arranged in the cylinder barrel 2, and the upper static pressure oil return pipeline 3-3 is communicated with the lower static pressure oil return pipeline 4-3 through the oil return communication pipeline 2-1.
The upper static pressure oil groove 3-1 and the lower static pressure oil groove 4-1 are used for forming a static pressure lubrication supporting oil pad, and the piston rod 1 is separated from direct contact with the inner surfaces of the penetrating holes of the piston rod 1 of the upper cylinder cover 3 and the lower cylinder cover 4 through the static pressure lubrication supporting oil pad.
Specifically, the number of the upper hydrostatic oil grooves 3-1 and the lower hydrostatic oil grooves 4-1 is preferably four, and the hydrostatic oil grooves are rectangular in shape. After the static pressure lubrication supporting oil pads are formed in the upper static pressure oil groove 3-1 and the lower static pressure oil groove 4-1, the static pressure lubrication supporting oil pads can separate the piston rod 1 from the inner surfaces of the through holes of the piston rod 1 of the upper cylinder cover 3 and the piston rod 1 of the lower cylinder cover 4 no matter the piston rod 1 is in a static state or a moving state, so that direct friction contact is avoided. In addition, the upper static pressure oil groove 3-1 and the lower static pressure oil groove 4-1 are uniformly distributed in the circumferential direction, so that the piston rod 1 can bear radial loads in any direction, and technical support is provided for further improving the lateral deflection resistance of the hydraulic cylinder. Because the static pressure lubrication supporting oil pads formed in the upper static pressure oil groove 3-1 and the lower static pressure oil groove 4-1 have extremely high oil film rigidity, the piston rod 1 can have better supporting performance when biased load is applied, and the amplitude-frequency characteristic of the hydraulic actuator is further improved.
An integrated valve block 9 is arranged on the outer surface of the cylinder barrel 2, two servo valves 10 are installed on the integrated valve block 9 in parallel, an oil cavity of the hydraulic cylinder is connected with a hydraulic system sequentially through the integrated valve block 9 and the servo valves 10, and an energy accumulator 11 used for stabilizing the pressure of the hydraulic system is further installed on the integrated valve block 9.
Concretely, through the parallelly connected scheme of two servo valves, can further improve the hydraulic oil flow, realize further improvement actuator piston start speed's purpose, can promote the effective frequency of traditional actuator piston motion to 100Hz from 10Hz, satisfy acceleration-frequency characteristic, satisfy simultaneously that the dynamic load output can reach 500kN, vibration amplitude 1 mm's experimental needs.
A load cell 12 is installed at the top end of the piston rod 1, and the load cell 12 is fixedly connected with the piston rod 1 through a switching adapter 13.
The bottom end of the piston rod is provided with a displacement sensor 14, one end of the displacement sensor 14 is fixedly connected with the lower cylinder cover 4 through a protective cover 15, and the other end of the displacement sensor 14 is connected with the piston rod 1 in a matched mode.
Specifically, the displacement sensor 14 is preferably a magnetostrictive displacement sensor, a main body part of the magnetostrictive displacement sensor is fixedly connected with the protective cover 15, and a magnetic ring of the magnetostrictive displacement sensor is fixed in a hollow rod cavity of the piston rod 1. When the hydraulic cylinder works, the load of the hydraulic cylinder can be detected and fed back by using the force measuring sensor 12, the position of the piston rod 1 can be detected and fed back by using the displacement sensor 14, the flow is automatically adjusted by using the servo valve 10, and the servo valve 10 plays a role of a reversing valve and a flow control valve, so that the control of various physical quantities such as position, speed, acceleration, force, pressure and the like can be realized, the problem that the traditional liquid actuator cannot generate high-amplitude frequency characteristic excitation in a rock dynamic loading experiment is solved, and a curve shown in fig. 6 can be obtained by performing performance test on the hydraulic actuator.
The embodiments are not intended to limit the scope of the present invention, and all equivalent implementations or modifications without departing from the scope of the present invention are intended to be included in the scope of the present invention.
Claims (10)
1. A hydraulic actuator with rock mechanics high amplitude-frequency response characteristics is characterized in that: the cylinder barrel is coaxially sleeved outside the piston rod, the upper cylinder cover is arranged at an upper cylinder opening of the cylinder barrel, the lower cylinder cover is arranged at a lower cylinder opening of the cylinder barrel, the upper end of the piston rod penetrates through the upper cylinder cover in a sealing manner, the lower end of the piston rod penetrates through the lower cylinder cover in a sealing manner, and the upper cylinder cover and the lower cylinder cover are identical in structure and are distributed in a mirror symmetry manner; the piston rod is of a lightweight composite structure and comprises an inner rod body and an outer rod body, and the outer rod body is fixedly sleeved on the outer side of the inner rod body; the inner rod body is of a hollow rod structure and is made of titanium alloy; a piston is arranged in the middle of the outer rod body, a plurality of annular oil grooves are uniformly distributed on the circumferential surface of the piston along the axial direction, and the piston is in clearance fit with the inner surface of the cylinder barrel; the outer rod body and the piston are of an integrated structure and made of carbon fibers; and ceramic coating films are arranged on the outer surfaces of the outer rod body and the piston.
2. The hydraulic actuator with high amplitude-frequency response characteristic for rock mechanics as claimed in claim 1, wherein: a lubricating oil film and a gap seal are formed in a gap between the piston and the inner surface of the cylinder barrel, and the piston is separated from the inner surface of the cylinder barrel to be in direct contact through the lubricating oil film; the annular oil groove is used for dynamically storing hydraulic oil required by the formation of the lubricating oil film.
3. The hydraulic actuator with high amplitude-frequency response characteristics for rock mechanics as claimed in claim 2, wherein: the upper cylinder cover is tightly connected with the upper opening of the cylinder barrel through a plurality of high-strength bolts which are uniformly distributed in the circumferential direction, and a sealing ring is arranged between the upper cylinder cover and the upper opening of the cylinder barrel; the lower cylinder cover is also fastened and connected with the lower opening of the cylinder barrel through a plurality of high-strength bolts which are uniformly distributed in the circumferential direction, and a sealing ring is also arranged between the lower cylinder cover and the lower opening of the cylinder barrel.
4. A hydraulic actuator with high amplitude-frequency response characteristics for rock mechanics as claimed in claim 3, wherein: the inner surface of a piston rod penetrating hole of the upper cylinder cover is in clearance fit with the piston rod; the inner surface of a piston rod penetrating hole of the upper cylinder cover is provided with a plurality of upper static pressure oil grooves which are uniformly distributed along the circumferential direction; an upper static pressure oil supply pipeline is arranged in the upper cylinder cover and is directly communicated with the upper static pressure oil groove; an upper static pressure oil return pipeline is arranged in the upper cylinder cover, and the upper static pressure oil return pipeline is communicated with the upper static pressure oil groove through a gap between the inner surface of a piston rod penetrating hole of the upper cylinder cover and the piston rod; a throttle valve is arranged in the upper static pressure oil supply pipeline; and sealing rings are respectively arranged on the inner surfaces of the piston rod penetrating holes on the two axial sides of the upper static pressure oil groove, and dust rings are also arranged on the outer sides of the outer end sealing rings.
5. The hydraulic actuator with high amplitude-frequency response characteristics in rock mechanics according to claim 4, wherein: the inner surface of a piston rod penetrating hole of the lower cylinder cover is in clearance fit with the piston rod; a plurality of lower static pressure oil grooves are formed in the inner surface of a piston rod penetrating hole of the lower cylinder cover, and the plurality of lower static pressure oil grooves are uniformly distributed along the circumferential direction; a lower static pressure oil supply pipeline is arranged in the lower cylinder cover and is directly communicated with the lower static pressure oil groove; a lower static pressure oil return pipeline is arranged in the lower cylinder cover, and the lower static pressure oil return pipeline is communicated with a lower static pressure oil groove through a gap between the inner surface of a piston rod penetrating hole of the lower cylinder cover and the piston rod; a throttle valve is arranged in the lower static pressure oil supply pipeline; and sealing rings are respectively arranged on the inner surfaces of the piston rod penetrating holes on the two axial sides of the lower static pressure oil groove, and dust rings are also arranged on the outer sides of the outer end sealing rings.
6. The hydraulic actuator with high amplitude-frequency response characteristics for rock mechanics as claimed in claim 5, wherein: an oil return communication pipeline is arranged in the cylinder barrel, and the upper static pressure oil return pipeline is communicated with the lower static pressure oil return pipeline through the oil return communication pipeline.
7. The hydraulic actuator with high amplitude-frequency response characteristics for rock mechanics as claimed in claim 6, wherein: and the upper static pressure oil groove and the lower static pressure oil groove are internally used for forming a static pressure lubrication supporting oil pad, and the piston rod is separated from the inner surfaces of the piston rod penetrating holes of the upper cylinder cover and the lower cylinder cover by the static pressure lubrication supporting oil pad.
8. The hydraulic actuator with high amplitude-frequency response characteristics for rock mechanics as claimed in claim 7, wherein: the hydraulic cylinder is characterized in that an integrated valve block is arranged on the outer surface of the cylinder barrel, two servo valves are installed on the integrated valve block in parallel, an oil cavity of the hydraulic cylinder is connected with a hydraulic system sequentially through the integrated valve block and the servo valves, and an energy accumulator used for stabilizing the pressure of the hydraulic system is further installed on the integrated valve block.
9. The hydraulic actuator with high amplitude-frequency response characteristics for rock mechanics as claimed in claim 8, wherein: and the top end of the piston rod is provided with a force measuring sensor, and the force measuring sensor is fixedly connected with the piston rod through a switching adapter.
10. The hydraulic actuator with high amplitude-frequency response characteristics for rock mechanics as claimed in claim 9, wherein: the piston rod bottom is provided with displacement sensor, and displacement sensor one end passes through protection casing and lower cylinder cap fixed connection, and the displacement sensor other end is connected with the piston rod cooperation.
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| CN202210190037.XA CN114483703B (en) | 2022-02-28 | 2022-02-28 | Rock mechanics high-amplitude-frequency response characteristic hydraulic actuator |
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| CN202210190037.XA CN114483703B (en) | 2022-02-28 | 2022-02-28 | Rock mechanics high-amplitude-frequency response characteristic hydraulic actuator |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115898827A (en) * | 2022-11-24 | 2023-04-04 | 上海羿弓氢能科技有限公司 | Novel high-frequency action decompression cylinder for diaphragm compressor |
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| CN101529101A (en) * | 2006-05-30 | 2009-09-09 | 祖姆罗有限公司 | Pressure cylinder with composite piston rod and method for preparing a composite piston rod |
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