CN112128164A - Triaxial test loading hydraulic cylinder with adjustable maximum output load - Google Patents

Triaxial test loading hydraulic cylinder with adjustable maximum output load Download PDF

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Publication number
CN112128164A
CN112128164A CN202011154433.4A CN202011154433A CN112128164A CN 112128164 A CN112128164 A CN 112128164A CN 202011154433 A CN202011154433 A CN 202011154433A CN 112128164 A CN112128164 A CN 112128164A
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China
Prior art keywords
cylinder body
output shaft
end cover
oil
chambers
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CN202011154433.4A
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Chinese (zh)
Inventor
桑勇
邹德高
岳亦锋
周晨光
刘京茂
宁凡伟
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Dalian University of Technology
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Dalian University of Technology
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Priority to CN202011154433.4A priority Critical patent/CN112128164A/en
Publication of CN112128164A publication Critical patent/CN112128164A/en
Pending legal-status Critical Current

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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
    • F15B15/1404—Characterised by the construction of the motor unit of the straight-cylinder type in clusters, e.g. multiple cylinders in one block
    • 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
    • F15B15/1409—Characterised by the construction of the motor unit of the straight-cylinder type with two or more independently movable working pistons
    • 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
    • F15B15/1428—Cylinders
    • 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
    • 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
    • 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
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01N—INVESTIGATING OR ANALYSING MATERIALS BY DETERMINING THEIR CHEMICAL OR PHYSICAL PROPERTIES
    • G01N15/00—Investigating characteristics of particles; Investigating permeability, pore-volume or surface-area of porous materials
    • G01N15/08—Investigating permeability, pore-volume, or surface area of porous materials
    • G01N15/0806—Details, e.g. sample holders, mounting samples for testing
    • G—PHYSICS
    • 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
    • G01N3/02—Details
    • G—PHYSICS
    • 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
    • G01N3/08—Investigating strength properties of solid materials by application of mechanical stress by applying steady tensile or compressive forces
    • G01N3/10—Investigating strength properties of solid materials by application of mechanical stress by applying steady tensile or compressive forces generated by pneumatic or hydraulic pressure

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Health & Medical Sciences (AREA)
  • Biochemistry (AREA)
  • General Health & Medical Sciences (AREA)
  • General Physics & Mathematics (AREA)
  • Immunology (AREA)
  • Pathology (AREA)
  • Dispersion Chemistry (AREA)
  • Actuator (AREA)

Abstract

The invention provides a triaxial test loading hydraulic cylinder with an adjustable maximum output load, and belongs to the field of mechanical engineering. The device specifically comprises an output shaft, an output shaft dustproof ring I, an output shaft sealing ring I, an output shaft guide sleeve I, a front end cover, a front cylinder body, a front end cover bolt, a front end cover sealing ring, an output shaft guide sleeve II, a connecting bolt component I, an output shaft sealing ring II, an output shaft dustproof ring II, a middle cylinder body, a front cylinder body plunger, a push plate, a connecting bolt component, a stop washer, a fastening nut, a rear cylinder body plunger group, a rear end cover bolt, a rear end cover sealing ring, a rear end cover and a one-way valve. The loading hydraulic cylinder provided by the invention can change the number of effective output plungers and indirectly change the maximum output load of the hydraulic cylinder by changing the flow direction and the on-off of oil liquid at different oil through ports under the condition that the high-pressure input of the hydraulic oil is not changed, so that the function of adjusting the maximum output load is realized.

Description

Triaxial test loading hydraulic cylinder with adjustable maximum output load
Technical Field
The invention belongs to the field of mechanical engineering, relates to a soil mechanics triaxial test, and particularly relates to a loading device with an adjustable maximum output load.
Background
A triaxial tester is frequently used for measuring the strength and deformation of soil, has wide application range, and can be used for measuring various parameters including shear strength characteristics, consolidation characteristics and soil permeability. The triaxial tester usually adopts the mode of electro-hydraulic servo loading, and the axial loading force needs to be set according to the magnitude of confining pressure in the experimental process. However, in the triaxial test, a very important test, namely the liquefaction test, needs to be continuously loaded back and forth, the dynamic strength is gradually reduced in the loading process, and the load characteristic is poor. Along with the continuous progress of loading, the loaded amplitude can be bigger and bigger, causes the phenomenon of out of control very easily, and the loading pneumatic cylinder produces the maximum output load easily when out of control takes place. Therefore, in order to protect equipment, a hydraulic cylinder with adjustable maximum output load is urgently needed in the practical experiment process.
At present, no related products exist at home and abroad. Generally, a pressure reduction control mode is adopted on the premise of engineering requirements, namely, the pressure of oil supply is reduced. However, this approach is not conducive to control of the servo valve, and the dynamic control performance of the control system is generally poor when the oil pressure is low. Therefore, it becomes very difficult to adjust the maximum output load under the precondition that the high-pressure oil source is supplied with oil.
Disclosure of Invention
The invention aims to provide a triaxial test loading hydraulic cylinder with an adjustable maximum output load. The hydraulic cylinder can adjust the maximum output load on the premise that the oil supply pressure of a high-pressure oil source is not changed.
In order to achieve the purpose, the invention adopts the technical scheme that:
the utility model provides a triaxial test loading pneumatic cylinder with adjustable maximum output load, triaxial test loading pneumatic cylinder includes output shaft 1, output shaft dust ring I2, output shaft sealing washer I3, output shaft uide bushing I4, front end housing 5, preceding cylinder body 6, front end cap bolt 7, front end cap sealing washer 8, output shaft uide bushing II9, connecting bolt subassembly I10, output shaft sealing washer II11, output shaft dust ring II12, middle cylinder body 13, preceding cylinder body plunger 14, push pedal 15, connecting bolt subassembly 16, lock washer 17, holding nut 18, back cylinder body 19, back cylinder body plunger group 20, back end cap bolt 21, back end cap sealing washer 22, back end cap 23, check valve 24.
The front end cover 5 is connected and fastened with the front cylinder body 6 through a front end cover bolt 7, an annular groove is formed in the outer surface of a central protruding part of the front end cover 5, and a front end cover sealing ring 8 is installed; the front cylinder body 6 is connected and fastened with the middle cylinder body 13 through a connecting bolt assembly I10; the middle cylinder body 13 is connected and fastened with the rear cylinder body 19 through a connecting bolt assembly II 16; the rear cylinder body 19 is connected and fastened with a rear end cover 23 through a rear end cover bolt 21, an annular groove is formed in the outer surface of the central protruding portion of the rear end cover 23, and a rear end cover sealing ring 22 is installed.
The interior of the front cylinder body 6 is provided with 8 cylindrical independent chambers which are circumferentially arranged, and 1 front cylinder body plunger 14 is respectively arranged and is in clearance fit with the front cylinder body plunger. The inner chambers of the front cylinder 6 are classified into A, B types. The number of the chambers A is 4, the chambers A are uniformly distributed at intervals of 90 degrees, and the four chambers are communicated through a groove at the front end face of the front cylinder body 6, so that free flow of oil can be realized; one of the cavities A is communicated with the oil port A. The number of the chambers B is 4, the chambers B are independent of each other and are arranged on the circumference in a staggered manner with the chambers A; the 4B chambers are respectively communicated with oil ports B1, B2, B3 and B4.
The inside of the rear cylinder body 19 is provided with 8 cylindrical independent chambers which are circumferentially arranged, and 1 rear cylinder body plunger piston 20 is respectively arranged and is in clearance fit with the rear cylinder body 19. The inner chambers of the rear cylinder 19 are classified into C, D types. The number of the chambers C is 4, the chambers C are uniformly distributed at intervals of 90 degrees, and the four chambers are communicated through a groove at the rear end face of the rear cylinder body 19 so as to realize free flow of oil; one of the chambers C is communicated with the oil port C. The number of the chambers D is 4, and the chambers D are independent and not communicated with each other; the D chambers are respectively and independently communicated with oil ports D1, D2, D3 and D4.
The center of the push plate 15 is provided with a threaded hole which is connected with the tail end of the output shaft 1 through a bolt, and the push plate is externally connected with a fastening nut 18 and a thrust washer 17 so as to realize the anti-loosening of threads. The front cylinder plunger 14 and the rear cylinder plunger 20 are in contact with both sides of the push plate 15, respectively. Through holes are formed in the center of the front cylinder body 6 and the center of the front end cover 5, and the output shaft 1 extends out of the hydraulic cylinder body through the center through holes of the front cylinder body 6 and the front end cover 5. The inner wall of the central through hole of the front cylinder body 6 is provided with 3 annular grooves, and the cylinder body is sequentially provided with an output shaft dustproof ring II12, an output shaft sealing ring II11 and an output shaft guide sleeve II9 from inside to outside. The inner wall of the central through hole of the front end cover 5 is also provided with 3 annular grooves, and the cylinder body is sequentially provided with an output shaft guide sleeve I4, an output shaft sealing ring I3 and an output shaft dustproof ring I2 from inside to outside. An annular groove is formed in the rear end face of the front cylinder body 6 and the front end face of the rear cylinder body 19 respectively and used for collecting oil overflowing from a cavity gap, and the leaked oil flows back to a groove communicated with the cavity A or the cavity C through a slit in the cylinder body and the check valve 24.
The hydraulic oil pushes the front cylinder plunger 14 or the rear cylinder plunger 20 to move, and then pushes the hydraulic cylinder output shaft 1 to move, thereby indirectly providing an output load.
The working process of the invention is as follows: (taking the example of the hydraulic cylinder output rod 1 extending out)
When the load is normally output to the maximum, high-pressure oil flows into the rear cylinder body 19 through the oil port C, D, the plunger 20 in the C, D chamber extends out to push the push plate 15 to move, and then the output shaft 1 is driven to extend out of the hydraulic cylinder; at this time, the front cylinder plunger 14 is pushed by the push plate 15 to retract into the front cylinder 6, the excess oil in the front cylinder chamber flows out through the oil port A, B, and the output shaft 1 outputs the maximum load.
When the maximum output load is adjusted, oil enters and exits from the oil through port A, C normally, the oil way outside the B, D cavity is cut off by the reversing valve, hydraulic oil in the B, D cavity is locked, the hydraulic oil cannot flow back to the oil tank, the B, D cavity is communicated, the oil can only flow in the B, D cavity, and the plunger in the B, D cavity can move under the action of external force. Because B, D chambers are communicated, oil pressure is equal, B, D chamber plunger to push plate 15 effort counteract each other, corresponding to the inefficacy, do not export the load outward, only A or C chamber plunger output load, externally show that the maximum output load reduces.
The invention has the advantages that: under the condition that the high-pressure input of hydraulic oil is not changed, the flow direction and the on-off of the hydraulic oil at different oil through ports are changed through the reversing valve, so that the number of effective output plungers is changed, the maximum output load is indirectly changed, and the function of adjusting the maximum output load is realized. Meanwhile, due to the fact that the oil pressure is high, good dynamic control performance can be achieved. And because the piston in the hydraulic cylinder is removed, partial friction force is reduced. Furthermore, by adding more plungers to the structural design, more stages of load adjustment options can be achieved.
Drawings
FIG. 1 is a semi-sectional view of a loading cylinder;
fig. 2 is a view of the loading hydraulic cylinder a (mainly for explaining the relative positions of the chambers, this view mainly shows the positional relationship of the chambers in the rear cylinder 19, the front and rear chambers A, C correspond to each other, and the position B, D corresponds to each other);
FIG. 3 is a schematic external view of the loading cylinder (the middle cylinder 13 and the bolt sets are removed to show the internal structure);
in the figure: 1 an output shaft; 2, an output shaft dustproof ring I; 3, an output shaft sealing ring I; 4, outputting an output shaft guide sleeve I; 5, a front end cover; 6, a front cylinder body; 7 front end cover bolts; 8, sealing rings of the front end covers; 9, outputting an output shaft guide sleeve II; 10 connecting the bolt assembly I; 11 output shaft seal ring II; 12 an output shaft dustproof ring II; 13 an intermediate cylinder; 14 front cylinder plunger; 15 pushing the plate; 16 connecting the bolt assembly; 17 a stop washer; 18 tightening the nut; 19 rear cylinder body; 20 rear cylinder plunger group; 21 rear end cap bolts; 22 rear end cap seal ring; 23, a rear end cover; 24 a one-way valve.
Detailed Description
The following detailed description of the invention refers to the accompanying drawings.
A triaxial test loading hydraulic cylinder with an adjustable maximum output load is shown in figure 1 and specifically comprises an output shaft 1, an output shaft dustproof ring I2, an output shaft sealing ring I3, an output shaft guide sleeve I4, a front end cover 5, a front cylinder body 6, a front end cover bolt 7, a front end cover sealing ring 8, an output shaft guide sleeve II9, a connecting bolt assembly I10, an output shaft sealing ring II11, an output shaft dustproof ring II12, a middle cylinder body 13, a front cylinder body plunger 14, a push plate 15, a connecting bolt assembly 16, a stop washer 17, a set nut 18, a rear cylinder body 19, a rear cylinder body plunger group 20, a rear end cover bolt 21, a rear end cover sealing ring 22, a rear end cover 23 and a one-way valve 24.
The front end cover 5 is connected and fastened with the front cylinder body 6 through 4 front end cover bolts 7, an annular groove is formed in the outer surface of a central protruding part of the front end cover 5, and a front end cover sealing ring 8 is installed to prevent oil in a cavity of the front cylinder body 6 from leaking; the front cylinder body 6 is connected and fastened with the middle cylinder body 13 through a connecting bolt assembly I10; the middle cylinder body 13 is connected and fastened with the rear cylinder body 19 through a connecting bolt assembly II 16; the rear cylinder 19 is connected and fastened with a rear end cover 23 through 4 rear end cover bolts 21, an annular groove is formed in the outer surface of a central protruding portion of the rear end cover 23, a rear end cover sealing ring 22 is installed, and oil in a cavity of the rear cylinder 19 is prevented from leaking.
As shown in fig. 2, the front cylinder 6 has 8 cylindrical independent chambers uniformly distributed on the circumference, and each front cylinder is provided with 1 front cylinder plunger 14, and the two are in clearance fit. The chambers fall into two categories A, B. The number of the cavities A is 4, the cavities A are respectively A1, A2, A3 and A4 and are uniformly distributed at intervals of 90 degrees, the four cavities are communicated through grooves at the front end face of the front cylinder body 6, and free flow of oil in the 4 cavities A can be realized; the A1 chamber is externally communicated with an oil port A. The number of the chambers B is 4, namely chambers B1, chambers B2, chambers B3 and chambers B4, the chambers B are independent from each other, are not communicated and are arranged in a staggered manner with the chambers A; the 4B chambers are respectively communicated with oil ports B1, B2, B3 and B4.
The inside of the rear cylinder body 19 is provided with 8 cylindrical independent chambers which are circumferentially arranged, and 1 rear cylinder body plunger piston 20 is respectively arranged and is in clearance fit with the rear cylinder body 19. The chambers in the rear cylinder 19 are classified into C, D types. The number of the chambers C is 4, the chambers C are respectively C1, C2, C3 and C4 and are uniformly distributed at intervals of 90 degrees, the four chambers are communicated through grooves at the rear end face of the rear cylinder body 19, and free flow of oil in the 4 chambers C can be realized; the C1 chamber is externally connected with an oil opening C. The number of the D chambers is 4, namely D1, D2, D3 and D4, the D chambers are independent and not communicated with each other, and C, D chambers are arranged in a staggered mode; the D chambers are respectively and independently communicated with oil ports D1, D2, D3 and D4.
The center of the push plate 15 is provided with a threaded hole which is connected with the tail end of the output shaft 1 through a bolt, and the push plate is externally connected with a fastening nut 18 and a thrust washer 17 so as to realize the anti-loosening of threads. The front cylinder plunger 14 and the rear cylinder plunger 20 are respectively contacted with two sides of the push plate 15; when the front cylinder 6 and the rear cylinder 19 enter and exit hydraulic oil through oil ports, the front and rear cylinder plungers can respectively realize the extending and retracting functions to push the push plate 15 to move, and the push plate 15 is connected with the output shaft 1, so that the extending and retracting movements of the output shaft 1 can be realized, and the output load of the hydraulic cylinder is externally provided.
Through holes are formed in the center of the front cylinder body 6 and the center of the front end cover 5, and the output shaft 1 extends out of the hydraulic cylinder through the through holes of the front cylinder body 6 and the front end cover 5. The inner wall of the central through hole of the front cylinder body 6 is provided with 3 annular grooves, and the cylinder body is sequentially provided with an output shaft dustproof ring II12, an output shaft sealing ring II11 and an output shaft guide sleeve II9 from inside to outside. The inner wall of the central through hole of the front end cover 5 is also provided with 3 annular grooves, and the cylinder body is sequentially provided with an output shaft guide sleeve I4, an output shaft sealing ring I3 and an output shaft dustproof ring I2 from inside to outside. An annular groove is formed in the rear end face of the front cylinder body 6 and the front end face of the rear cylinder body 19 respectively and used for collecting oil overflowing from the cavity, and the leaked oil flows back to the groove between the cavities A or C through a slit in the cylinder body and the check valve 24.
The specific working state of the hydraulic cylinder is as follows:
when the output load is normal and maximum, high-pressure oil flows into the rear cylinder 19 through the oil port C, D, the plunger 20 in the C, D chamber extends outwards to push the push plate 15 to move forwards, and then the output shaft 1 is driven to extend out of the hydraulic cylinder to provide the output load; the front cylinder plunger 14 retracts into the front cylinder 6 under the thrust action of the push plate 15, the front cylinder plunger 14 pushes redundant oil in the front cylinder 6 to be discharged through the oil port A, B, and at the moment, the output shaft 1 outputs the maximum load; the oil flowing direction of each oil through hole is changed, so that oil enters the oil through hole A, B, oil exits from the oil through hole C, D, and the output shaft 1 moves reversely to retract into the hydraulic cylinder; and (4) stopping oil inlet and outlet of each oil inlet, and stopping the motion of the output shaft 1.
When the output load state is adjusted, the oil passage between the oil through port B, D and the oil pump and the oil tank is cut off by the reversing valve, hydraulic oil in the B, D cavity is locked and cannot flow back to the oil tank, the cavity of the front cylinder body B and the cavity of the rear cylinder body D are communicated, the locked oil can freely flow in the B, D cavity, the oil pressure is equal because the front cavity and the rear cavity are communicated, and the acting forces of opposite plungers in the front cylinder body B, D cavity and the rear cylinder body B, D cavity on the push plate 15 are mutually offset, which is equivalent to failure. When the hydraulic cylinder works, oil enters the rear cylinder body 19 through the oil port C normally, the rear cylinder body plunger 20 in the cavity C extends out to push the push plate 15 to move, and further the output shaft 1 is pushed to extend out of the hydraulic cylinder; the front cylinder plunger 14 retracts into the front cylinder 6 under the action of the push plate 15, so that redundant oil in a cavity A of the front cylinder is pushed to be discharged through the oil port A, redundant oil in a cavity B of the front cylinder flows into a cavity D in the rear cylinder 19 through an oil way, and a small plunger in the cavity D is pushed to extend out; at this time, only the plunger in the A, C chamber outputs force outwards, the plunger acting force corresponding to the front and the back in the B, D chamber is mutually counteracted, and the maximum output load of the output shaft 1 is reduced outwards. And the oil flowing direction of each oil through port is changed, so that the oil through port A is fed, and when the oil C is discharged, the output shaft 1 reversely moves to retract into the hydraulic cylinder. And (4) stopping oil inlet and outlet of each oil inlet, and stopping the motion of the output shaft 1.
The drawings in the specification are not drawn strictly according to the reduction of designed real objects in proportion, the drawings mainly highlight the characteristics and structural characteristics of the cylinder body, such as the number of adopted front and rear plungers, the front and rear cylinder bodies in the drawings respectively use 8 plungers, and the structure can be properly changed according to needs to add the plungers, such as 10 plungers, 12 plungers and the like.
The invention is not limited to the above embodiments, and several variations and modifications made by the inventive concept fall within the scope of the present invention.

Claims (3)

1. The triaxial test loading hydraulic cylinder with the adjustable maximum output load is characterized by comprising an output shaft (1), an output shaft dustproof ring I (2), an output shaft sealing ring I (3), an output shaft guide sleeve I (4), a front end cover (5), a front cylinder body (6), an output shaft guide sleeve II (9), a connecting bolt assembly I (10), an output shaft sealing ring II (11), an output shaft dustproof ring II (12), a middle cylinder body (13), a front cylinder body plunger (14), a push plate (15), a connecting bolt assembly (16), a stop washer (17), a rear cylinder body (19), a rear cylinder body plunger group (20), a rear end cover (23) and a one-way valve (24);
the front end cover (5) is connected and fastened with the front cylinder body (6); the front cylinder body (6) is connected and fastened with the middle cylinder body (13) through a connecting bolt assembly I (10); the middle cylinder body (13) is connected and fastened with the rear cylinder body (19) through a connecting bolt assembly II (16); the rear cylinder body (19) is connected and fastened with the rear end cover (23);
8 cylindrical independent chambers which are circumferentially arranged are arranged in the front cylinder body (6), 1 front cylinder body plunger (14) is respectively arranged in the front cylinder body (6), and the front cylinder body plunger are in clearance fit; the inner chambers of the front cylinder body (6) are divided into A, B types, and each type is 4; the 4 cavities A are uniformly distributed at intervals of 90 degrees, and the 4 cavities are communicated through a groove at the front end face of the front cylinder body (6), so that free flow of oil can be realized; the A1 cavity is externally connected with an oil through hole A; the 4B chambers are independent from each other and are arranged in a staggered manner with the chamber A, and the 4B chambers are respectively communicated with oil ports B1, B2, B3 and B4; 8 cylindrical independent chambers which are circumferentially arranged are arranged in the rear cylinder body (19), 1 rear cylinder body plunger (20) is respectively arranged in the rear cylinder body (19), and the rear cylinder body plunger are in clearance fit; the inner chambers of the rear cylinder body (19) are divided into C, D types; the number of the chambers C is 4, the chambers C are uniformly distributed at intervals of 90 degrees, and the 4 chambers are communicated through a groove at the rear end face of the rear cylinder body (19) to realize free flow of oil; the C1 cavity is externally connected with an oil through hole C; the number of the D chambers is 4, and the D chambers are independent and not communicated with each other; the D chambers are respectively and independently communicated with oil ports D1, D2, D3 and D4;
the center of the push plate (15) is provided with a threaded hole which is connected with the tail end of the output shaft (1) through a bolt and is externally connected with a fastening nut (18) and a thrust washer (17); the 8 front cylinder body plungers (14) and the 8 rear cylinder body plungers (20) are respectively contacted with the two sides of the push plate (15); the output shaft (1) extends out of the hydraulic cylinder body through central through holes of the front cylinder body (6) and the front end cover (5); the inner wall of a central through hole of the front cylinder body (6) is provided with 3 annular grooves, and the cylinder body is sequentially provided with an output shaft dustproof ring II (12), an output shaft sealing ring II (11) and an output shaft guide sleeve II (9) from inside to outside; the inner wall of a central through hole of the front end cover (5) is also provided with 3 annular grooves, and the cylinder body is sequentially provided with an output shaft guide sleeve I (4), an output shaft sealing ring I (3) and an output shaft dustproof ring I (2) from inside to outside; the rear end face of the front cylinder body (6) and the front end face of the rear cylinder body (19) are respectively provided with an annular groove for collecting oil overflowing from a cavity gap, and the leaked oil flows back to a groove communicated with the cavity A or the cavity C through a slit in the cylinder body and a check valve (24);
the hydraulic oil pushes the front cylinder body plunger (14) or the rear cylinder body plunger (20) to move, and then pushes the hydraulic cylinder output shaft (1) to move, so that the output load is indirectly provided.
2. The adjustable maximum output load triaxial test loading cylinder of claim 1, wherein the maximum output load is reduced by varying the number of plungers pushing the output shaft (1).
3. The triaxial test loading hydraulic cylinder with the adjustable maximum output load according to claim 1 or 2, wherein the outer surfaces of the central protruding parts of the front end cover (5) and the rear end cover (23) are respectively provided with an annular groove for installing the front end cover sealing ring (8) and the rear end cover sealing ring (22).
CN202011154433.4A 2020-10-26 2020-10-26 Triaxial test loading hydraulic cylinder with adjustable maximum output load Pending CN112128164A (en)

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030024292A1 (en) * 2001-08-02 2003-02-06 Mikio Yamamoto Fluid pressure cylinder and rolling mill
CN106949104A (en) * 2017-04-07 2017-07-14 江苏师范大学 A kind of plunger type enters fuel-displaced flow four-way hydraulic transformer of Denging
CN110671385A (en) * 2019-09-05 2020-01-10 南京理工大学 Special dynamic and static combined hydraulic cylinder for rock-soil mechanical test equipment
CN213684773U (en) * 2020-10-26 2021-07-13 大连理工大学 Triaxial test loading hydraulic cylinder with adjustable maximum output load

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20030024292A1 (en) * 2001-08-02 2003-02-06 Mikio Yamamoto Fluid pressure cylinder and rolling mill
CN106949104A (en) * 2017-04-07 2017-07-14 江苏师范大学 A kind of plunger type enters fuel-displaced flow four-way hydraulic transformer of Denging
CN110671385A (en) * 2019-09-05 2020-01-10 南京理工大学 Special dynamic and static combined hydraulic cylinder for rock-soil mechanical test equipment
CN213684773U (en) * 2020-10-26 2021-07-13 大连理工大学 Triaxial test loading hydraulic cylinder with adjustable maximum output load

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
桑勇;邵龙潭: ""动静三轴试验仪"伺服加载系统研究", 大连理工大学学报, vol. 50, no. 2, 31 December 2010 (2010-12-31) *

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