CN110987673B - High-pressure hard rock low-frequency disturbance true triaxial test mechanism - Google Patents
High-pressure hard rock low-frequency disturbance true triaxial test mechanism Download PDFInfo
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- CN110987673B CN110987673B CN201911257135.5A CN201911257135A CN110987673B CN 110987673 B CN110987673 B CN 110987673B CN 201911257135 A CN201911257135 A CN 201911257135A CN 110987673 B CN110987673 B CN 110987673B
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- G01—MEASURING; TESTING
- G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
- G01N3/00—Investigating strength properties of solid materials by application of mechanical stress
- G01N3/30—Investigating strength properties of solid materials by application of mechanical stress by applying a single impulsive force, e.g. by falling weight
- G01N3/313—Investigating strength properties of solid materials by application of mechanical stress by applying a single impulsive force, e.g. by falling weight generated by explosives
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- G—PHYSICS
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- G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
- G01N2203/00—Investigating strength properties of solid materials by application of mechanical stress
- G01N2203/0001—Type of application of the stress
- G01N2203/001—Impulsive
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
- G01N2203/00—Investigating strength properties of solid materials by application of mechanical stress
- G01N2203/02—Details not specific for a particular testing method
- G01N2203/025—Geometry of the test
- G01N2203/0256—Triaxial, i.e. the forces being applied along three normal axes of the specimen
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Abstract
A high-pressure hard rock low-frequency disturbance true triaxial test mechanism comprises a true triaxial loading assembly and a parallel oil source assembly, wherein a rigid frame body of the true triaxial loading assembly is provided with six dynamic servo hydraulic actuators; the parallel oil source assembly comprises an oil tank, a pump station and a cooler, wherein the inner cavity of the oil tank is divided into six areas marked as areas I-II by partition plates; the top of the area is communicated, the bottom of the area is communicated, the top of the area is communicated, and the top of the area is communicated; the pump station comprises five hydraulic pumps, four high-flow pumps and one low-flow pump, and when a 0-20 Hz dynamic test needs to be carried out, the four high-flow pumps are connected in parallel to meet the flow requirement; and the region No. five is connected with a hot oil hydraulic pump through a pipeline, the hot oil hydraulic pump is connected with a cooler through a pipeline, the hot oil hydraulic pump pumps the hot oil in the region No. five to the cooler for cooling, and after cooling, the cold oil flows back to the region No. sixty percent to realize oil cooling circulation.
Description
Technical Field
The invention belongs to the technical field of rock mechanics tests, and particularly relates to a high-pressure hard rock low-frequency disturbance true triaxial test mechanism.
Background
In deep rock engineering, rock mass is in a three-dimensional high stress state, and high static stress provides a stress foundation for inoculation and occurrence of deep rock engineering disasters. Meanwhile, blasting excavation is always one of the main methods for deep rock engineering construction excavation due to the characteristics of high efficiency and good economy. Therefore, during the construction period, the rock mass is inevitably affected by the disturbance wave generated by blasting. When the disturbance wave generated by blasting attenuates along with the propagation, the disturbance wave is gradually attenuated into low-frequency blasting seismic wave, and the frequency of the blasting seismic wave is within the range of 0-20 Hz and the amplitude of the blasting seismic wave is within the range of 0.1-30 MPa according to the prior literature. Although the frequency and amplitude range of the blasting seismic waves are small, deep rock engineering disasters such as rock burst, zonal rupture, disturbance type collapse, continuous rock cracking and the like can still be triggered. In addition to blasting seismic waves, according to actually measured data on site, the frequency of disturbance waves generated by certain large rock explosions is within the range of 0-20 Hz, and the amplitude is within the range of 0.1-30 MPa. While such large rock bursts occur, secondary rock bursts often occur at locations remote from the large rock burst area. In addition, according to literature research, occurrence of other disturbances such as fault slippage and earthquake can cause disturbance type rock burst, and the frequency of the disturbance type rock burst is also in the range of 0-20 Hz.
Aiming at the problem that the rock is subjected to low-frequency disturbance load under high static stress load, related technicians develop a series of rock disturbance true triaxial test equipment, and the test equipment has the capability of simulating the action process of the disturbed load under the high static stress load of the rock from the angle that the disturbance mode is point disturbance or local surface disturbance, but has limitations. Because the disturbance load of each infinitesimal in the site rock mass is applied to the whole surface of the infinitesimal, but the existing equipment is generally limited by the flow of an oil source and the control performance, the disturbance force adopts a mode of applying the disturbance force by a small oil cylinder, the disturbance force is not completely loaded to the whole surface of a sample on the basis of loading a static load to the sample, and compared with the application mode of the disturbance of the whole surface, the application method of the point disturbance and the local surface disturbance can make the test result far away from the site reality. Meanwhile, the amplitude value of the disturbance wave on the site is alternately positive and negative, namely the stress on the site is increased and decreased on the basis of the static stress, namely the stress is loaded and unloaded on the basis of the static stress. However, in the existing devices, a single static load oil cylinder plus reaction frame and a dynamic small oil cylinder structure in the same direction are adopted, and the structure can only simulate the disturbance force loading process on the basis of static load but cannot simulate the unloading process on the basis of static stress.
Therefore, in order to simulate the disturbed dynamic action process of the on-site rock mass more truly, the true triaxial test equipment capable of realizing surface disturbance and loading and unloading on the basis of high static stress load needs to be developed urgently.
Disclosure of Invention
Aiming at the problems in the prior art, the invention provides a high-pressure hard rock low-frequency disturbance true triaxial test mechanism which can simulate the plane disturbance loading action process of a rock body under high static stress load, such as blasting seismic waves, disturbance waves generated by large rock burst, fault slip and the like within the frequency range of 0-20 Hz from the angle of indoor test, and is true triaxial test equipment capable of more truly simulating the disturbed dynamic action process of the on-site rock body.
In order to achieve the purpose, the invention adopts the following technical scheme: a high-pressure hard rock low-frequency disturbance true triaxial test mechanism comprises a true triaxial loading assembly and a parallel oil source assembly, wherein the true triaxial loading assembly and the parallel oil source assembly are both arranged on a mechanism base; the true triaxial loading assembly comprises a rigid base, a horizontal rigid frame body, a vertical rigid frame body, a cast iron damping table and a dynamic servo hydraulic actuator; the number of the dynamic servo hydraulic actuators is six; the cast iron damping table is horizontally and fixedly arranged on the mechanism base, the rigid base is horizontally clamped on the cast iron damping table, the vertical rigid frame body is vertically screwed and fixed on the upper surface of the rigid base, and the vertical rigid frame body consists of a top plate, a bottom plate and four stand columns; the horizontal rigid frame body is of an annular structure, the horizontal rigid frame body is sleeved on the outer side of the vertical rigid frame body, and the horizontal rigid frame body is fixed on the upper surface of the rigid base in a threaded connection mode; a top plate and a bottom plate of the vertical rigid frame body are respectively provided with a dynamic servo hydraulic actuator, and an upper dynamic servo hydraulic actuator and a lower dynamic servo hydraulic actuator are symmetrically distributed; four dynamic servo hydraulic actuators are uniformly distributed and installed on the horizontal rigid frame body along the circumferential direction; the dynamic servo hydraulic actuator is provided with a reversing valve block, the end part of a piston rod of the dynamic servo hydraulic actuator is provided with a dynamic load sensor, and the piston rod of the dynamic servo hydraulic actuator is of a hollow rod structure.
The parallel oil source assembly comprises an oil tank, a pump station and a cooler; the inner cavity of the oil tank is divided into six areas by partition plates, and the six areas are respectively marked as a No. I area, a No. II area, a No. III area, a No. IV area, a No. V area and a No. sixteenth area; the top parts of the area I, the area II and the area III are communicated with each other, the top parts of the area IV and the area V are communicated with each other, the bottom parts of the area V and the area IV are communicated with each other, the top parts of the area I and the area V are communicated with each other, the top parts of the area II and the area V are communicated with each other, and the top parts of the area III and the area IV are communicated with each other; the hydraulic system comprises a pump station, a dynamic servo hydraulic actuator, a hydraulic control system and a control system, wherein the pump station comprises five hydraulic pumps which are respectively marked as a first high-flow hydraulic pump, a second high-flow hydraulic pump, a third high-flow hydraulic pump, a fourth high-flow hydraulic pump and a low-flow hydraulic pump; hydraulic oil suction ports of the first high-flow hydraulic pump, the second high-flow hydraulic pump, the third high-flow hydraulic pump, the fourth high-flow hydraulic pump and the low-flow hydraulic pump are communicated with the bottom of an inner cavity of the oil tank through pipelines and used for extracting hydraulic oil in the area I, the area II and the area III; overflow valves are respectively arranged between the hydraulic oil output ports of the first high-flow hydraulic pump, the second high-flow hydraulic pump, the third high-flow hydraulic pump, the fourth high-flow hydraulic pump and the low-flow hydraulic pump and the corresponding flow control valves, and overflow ports of the overflow valves are communicated with a region No. four, a region No. five and a region No. sixty percent through overflow pipelines; when the first high-flow hydraulic pump, the second high-flow hydraulic pump, the third high-flow hydraulic pump and the fourth high-flow hydraulic pump perform dynamic disturbance, the outflow hydraulic oil is converged to the oil inlet end of the oil return valve seat through a pipeline, and the oil outlet end of the oil return valve seat is communicated with the No. four area through a pipeline; the bottom of the region fifthly is connected with a hot oil output pipeline, an oil outlet of the hot oil output pipeline is connected with a hot oil hydraulic pump, an oil outlet of the hot oil hydraulic pump is communicated with a cooler through a pipeline, the hot oil in the region fifthly is pumped into the cooler through the hot oil hydraulic pump to be cooled, and an oil outlet of the cooler is communicated with the bottom of the region sixthly through a cold oil return pipeline.
The invention has the beneficial effects that:
the high-pressure hard rock low-frequency disturbance true triaxial test mechanism can simulate the surface disturbance loading action process of a rock body in the frequency range of 0-20 Hz of disturbance waves such as blasting seismic waves, disturbance waves generated by large rock blasting, fault slippage and the like under high static stress load from the angle of an indoor test, and is true triaxial test equipment capable of more truly simulating the action process of disturbed power of the on-site rock body.
Drawings
FIG. 1 is a schematic structural diagram of a high-pressure hard rock low-frequency disturbance true triaxial test mechanism according to the present invention;
FIG. 2 is a schematic diagram of a parallel oil source assembly (first view) according to the present invention;
FIG. 3 is a schematic diagram of a parallel oil source assembly (second perspective) according to the present invention;
in the figure, 1-mechanism base, 2-rigid base, 3-horizontal rigid frame body, 4-vertical rigid frame body, 5-cast iron damping table, 6-dynamic servo hydraulic actuator, 7-oil tank, 8-pump station, 9-cooler, No. 10-No. zone, No. 11-No. zone, No. 12-No. zone, No. 13-No. 4 zone, No. 14-No. 5 zone, No. 15-No. 16-first high-flow hydraulic pump, 17-second high-flow hydraulic pump, 18-third high-flow hydraulic pump, 19-fourth high-flow hydraulic pump, 20-low-flow hydraulic pump, 21-shunt valve seat, 22-overflow pipeline, 23-oil return valve seat, 24-hot oil output pipeline, 25-hot oil hydraulic pump, and 26-cold oil return pipeline.
Detailed Description
The invention is described in further detail below with reference to the figures and the specific embodiments.
As shown in fig. 1-3, the high-pressure hard rock low-frequency disturbance true triaxial test mechanism comprises a true triaxial loading assembly and a parallel oil source assembly, wherein the true triaxial loading assembly and the parallel oil source assembly are both arranged on a mechanism base 1; the true triaxial loading assembly comprises a rigid base 2, a horizontal rigid frame body 3, a vertical rigid frame body 4, a cast iron damping table 5 and a dynamic servo hydraulic actuator 6; after the actuator adopts the dynamic servo hydraulic actuator 6, the static loading function and the dynamic loading function can be realized; the number of the dynamic servo hydraulic actuators 6 is six; the cast iron damping table 5 is horizontally and fixedly arranged on the mechanism base 1, the rigid base 2 is horizontally clamped on the cast iron damping table 5, the vertical rigid frame body 4 is vertically screwed and fixed on the upper surface of the rigid base 2, and the vertical rigid frame body 4 consists of a top plate, a bottom plate and four stand columns; the horizontal rigid frame body 3 adopts an annular structure, the horizontal rigid frame body 3 is sleeved outside the vertical rigid frame body 4, and the horizontal rigid frame body 3 is fixed on the upper surface of the rigid base 2 in a threaded manner; a top plate and a bottom plate of the vertical rigid frame body 4 are respectively provided with a dynamic servo hydraulic actuator 6, and the upper dynamic servo hydraulic actuator 6 and the lower dynamic servo hydraulic actuator 6 are symmetrically distributed; four dynamic servo hydraulic actuators 6 are uniformly distributed and installed on the horizontal rigid frame body 3 along the circumferential direction; the dynamic servo hydraulic actuator 6 is provided with a reversing valve block, the end part of a piston rod of the dynamic servo hydraulic actuator 6 is provided with a dynamic load sensor, the piston rod of the dynamic servo hydraulic actuator 6 is of a hollow rod structure, the hollow rod structure can reduce the inertia of the piston rod and improve the dynamic corresponding characteristics of the actuator.
The parallel oil source assembly comprises an oil tank 7, a pump station 8 and a cooler 9; the inner cavity of the oil tank 7 is divided into six areas by partition plates, and the six areas are respectively marked as a No. 10 area, a No. 11 area, a No. 12 area, a No. 13 area, a No. 14 area and a No. 15 area; the tops of the No. 10 area, the No. 11 area and the No. 12 area are communicated with each other, the tops of the No. 13 area and the No. 14 area are communicated with each other, the bottoms of the No. 14 area and the No. 15 area are communicated with each other, the tops of the No. 10 area and the No. 13 area are communicated with each other, the tops of the No. 11 area and the No. 14 area are communicated with each other, and the tops of the No. 12 area and the No. 15 area are communicated with each other; the pump station 8 comprises five hydraulic pumps which are respectively marked as a first high-flow hydraulic pump 16, a second high-flow hydraulic pump 17, a third high-flow hydraulic pump 18, a fourth high-flow hydraulic pump 19 and a low-flow hydraulic pump 20; in this embodiment, the flow rates of the first high-flow hydraulic pump 16, the second high-flow hydraulic pump 17, the third high-flow hydraulic pump 18, and the fourth high-flow hydraulic pump 19 are all 100L/min, and the flow rate of the low-flow hydraulic pump 20 is 30L/min; the 30L/min low-flow hydraulic pump 20 can be used for static tests, and when 0-20 Hz dynamic tests are required, the flow of 400L/min can be realized by connecting four 100L/min high-flow hydraulic pumps in parallel; hydraulic oil output ports of the first high-flow hydraulic pump 16, the second high-flow hydraulic pump 17, the third high-flow hydraulic pump 18, the fourth high-flow hydraulic pump 19 and the low-flow hydraulic pump 20 are all connected with flow control valves, the hydraulic oil output ports of the hydraulic pumps are connected to the oil inlet end of the shunt valve seat 21 in a tandem mode through pipelines, and front and rear cavity oil ports of the dynamic servo hydraulic actuator 6 are connected to the oil outlet end of the shunt valve seat 21 through a reversing valve block and a pipeline; hydraulic oil suction ports of the first high-flow hydraulic pump 16, the second high-flow hydraulic pump 17, the third high-flow hydraulic pump 18, the fourth high-flow hydraulic pump 19 and the low-flow hydraulic pump 20 are communicated with the bottom of an inner cavity of the oil tank 7 through pipelines and used for extracting hydraulic oil in the first area 10, the second area 11 and the third area 12; overflow valves are respectively arranged between the hydraulic oil output ports of the first high-flow hydraulic pump 16, the second high-flow hydraulic pump 17, the third high-flow hydraulic pump 18, the fourth high-flow hydraulic pump 19 and the low-flow hydraulic pump 20 and the corresponding flow control valves, and overflow ports of the overflow valves are communicated with a No. four area 13, a No. five area 14 and a No. 15 area through overflow pipelines 22; when the first high-flow hydraulic pump 16, the second high-flow hydraulic pump 17, the third high-flow hydraulic pump 18 and the fourth high-flow hydraulic pump 19 perform dynamic disturbance, the flowing hydraulic oil is converged to the oil inlet end of the oil return valve seat 23 through a pipeline, and the oil outlet end of the oil return valve seat 23 is communicated with the region # r 13 through a pipeline; the bottom of the region (14) is connected with a hot oil output pipeline (24), the oil outlet of the hot oil output pipeline (24) is connected with a hot oil hydraulic pump (25), the oil outlet of the hot oil hydraulic pump (25) is communicated with a cooler (9) through a pipeline, hot oil in the region (14) is pumped into the cooler (9) through the hot oil hydraulic pump (25) to be cooled, and the oil outlet of the cooler (9) is communicated with the bottom of the region (15) through a cold oil return pipeline (26); and the cooling hydraulic oil which flows back to the No. 15 area flows into the No. 12 area communicated with the cooling hydraulic oil again through the top, and then flows into the No. 11 area and the No. 10 area in sequence, so that the cooling circulation flow of the hydraulic oil is finally realized, and continuous power is provided for the dynamic disturbance of 0-20 Hz.
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 (1)
1. The utility model provides a true triaxial test mechanism of high pressure hard rock low frequency disturbance which characterized in that: the device comprises a true triaxial loading assembly and a parallel oil source assembly, wherein the true triaxial loading assembly and the parallel oil source assembly are both arranged on a mechanism base; the true triaxial loading assembly comprises a rigid base, a horizontal rigid frame body, a vertical rigid frame body, a cast iron damping table and a dynamic servo hydraulic actuator; the number of the dynamic servo hydraulic actuators is six; the cast iron damping table is horizontally and fixedly arranged on the mechanism base, the rigid base is horizontally clamped on the cast iron damping table, the vertical rigid frame body is vertically screwed and fixed on the upper surface of the rigid base, and the vertical rigid frame body consists of a top plate, a bottom plate and four stand columns; the horizontal rigid frame body is of an annular structure, the horizontal rigid frame body is sleeved on the outer side of the vertical rigid frame body, and the horizontal rigid frame body is fixed on the upper surface of the rigid base in a threaded connection mode; a top plate and a bottom plate of the vertical rigid frame body are respectively provided with a dynamic servo hydraulic actuator, and an upper dynamic servo hydraulic actuator and a lower dynamic servo hydraulic actuator are symmetrically distributed; four dynamic servo hydraulic actuators are uniformly distributed and installed on the horizontal rigid frame body along the circumferential direction; the dynamic servo hydraulic actuator is provided with a reversing valve block, the end part of a piston rod of the dynamic servo hydraulic actuator is provided with a dynamic load sensor, and the piston rod of the dynamic servo hydraulic actuator is of a hollow rod structure; the parallel oil source assembly comprises an oil tank, a pump station and a cooler; the inner cavity of the oil tank is divided into six areas by partition plates, and the six areas are respectively marked as a No. I area, a No. II area, a No. III area, a No. IV area, a No. V area and a No. sixteenth area; the top parts of the area I, the area II and the area III are communicated with each other, the top parts of the area IV and the area V are communicated with each other, the bottom parts of the area V and the area IV are communicated with each other, the top parts of the area I and the area V are communicated with each other, the top parts of the area II and the area V are communicated with each other, and the top parts of the area III and the area IV are communicated with each other; the hydraulic system comprises a pump station, a dynamic servo hydraulic actuator, a hydraulic control system and a control system, wherein the pump station comprises five hydraulic pumps which are respectively marked as a first high-flow hydraulic pump, a second high-flow hydraulic pump, a third high-flow hydraulic pump, a fourth high-flow hydraulic pump and a low-flow hydraulic pump; hydraulic oil suction ports of the first high-flow hydraulic pump, the second high-flow hydraulic pump, the third high-flow hydraulic pump, the fourth high-flow hydraulic pump and the low-flow hydraulic pump are communicated with the bottom of an inner cavity of the oil tank through pipelines and used for extracting hydraulic oil in the area I, the area II and the area III; overflow valves are respectively arranged between the hydraulic oil output ports of the first high-flow hydraulic pump, the second high-flow hydraulic pump, the third high-flow hydraulic pump, the fourth high-flow hydraulic pump and the low-flow hydraulic pump and the corresponding flow control valves, and overflow ports of the overflow valves are communicated with a region No. four, a region No. five and a region No. sixty percent through overflow pipelines; when the first high-flow hydraulic pump, the second high-flow hydraulic pump, the third high-flow hydraulic pump and the fourth high-flow hydraulic pump perform dynamic disturbance, the outflow hydraulic oil is converged to the oil inlet end of the oil return valve seat through a pipeline, and the oil outlet end of the oil return valve seat is communicated with the No. four area through a pipeline; the bottom of the region fifthly is connected with a hot oil output pipeline, an oil outlet of the hot oil output pipeline is connected with a hot oil hydraulic pump, an oil outlet of the hot oil hydraulic pump is communicated with a cooler through a pipeline, the hot oil in the region fifthly is pumped into the cooler through the hot oil hydraulic pump to be cooled, and an oil outlet of the cooler is communicated with the bottom of the region sixthly through a cold oil return pipeline.
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