CN108896401B - High-pressure gas driven rock mechanical testing machine loading head - Google Patents
High-pressure gas driven rock mechanical testing machine loading head Download PDFInfo
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Abstract
The invention discloses a high-pressure gas driven loading head for a rock mechanical testing machine, which comprises a cylinder body, a piston and a loading rod, wherein an outer cylinder is fixedly arranged in an oil pressure chamber, an inner cylinder is arranged in the outer cylinder in a sliding manner, a first damping hole and a second damping hole are respectively arranged at the bottom end and the side wall of the inner cylinder, a one-way oil inlet hole and a one-way oil outlet hole are arranged on the cylinder body, the one-way oil inlet hole, the outer cylinder, the first damping hole, the inner cylinder, the second damping hole, the oil pressure chamber and the one-way oil outlet hole are sequentially communicated to form a damping oil circuit, a gas pressure chamber is communicated with an external high-pressure gas source through a high-pressure gas servo valve arranged on the cylinder body, an oil seal layer is arranged in the gas. The invention overcomes the defect that the hydraulic loading head of the current testing machine cannot be used for driving the testing machine device by high-pressure gas, reduces the energy consumption and cost of test and test, and improves the loading precision and the stability and reliability of the system.
Description
Technical Field
The invention belongs to the technical field of rock mechanics testing equipment, and particularly relates to a high-pressure gas driven rock mechanics testing machine loading head.
Background
The electrohydraulic servo testing machine is widely applied to the field of rock mechanical test, and is characterized in that a motor drives a booster pump to press hydraulic oil into an oil cylinder, so as to apply acting force to a piston in the oil cylinder and apply load to a rock sample through a pressure rod connected to the piston. Because the volume compression modulus of the hydraulic oil is extremely large (in the order of GPa), when a rock sample is slightly compressed and deformed under the action of load, the pressure of the hydraulic oil is rapidly reduced due to volume expansion, and in order to maintain the condition that the hydraulic oil applies load according to a test scheme, the motor and the booster pump always keep working, which is also the main reason of high energy consumption and high noise of a rock mechanics test project.
The gas has the property of spontaneously flowing from the high-pressure region to the low-pressure region without external interference, i.e. the high-pressure gas spontaneously flows to the low-pressure region without external energy supply. Therefore, if high-pressure or ultrahigh-pressure gas is used as power to drive hydraulic oil to apply acting force to the piston, the problem of high energy consumption in rock mechanical tests can be solved, but the hydraulic loading head of the existing testing machine cannot be used for the high-pressure gas drive testing machine because: according to a gaseous equation, when the temperature is unchanged, the volume of the gas is doubled, and the pressure is reduced by half; after the rock test piece yields, because the pressure of high-pressure gas is not reduced basically, under the effect of high-pressure gas, hydraulic oil can continue to drive the piston to move in the oil cylinder, but because the rock test piece has lost bearing capacity, can not provide resistance to lead to the piston can strike the oil cylinder base fast.
The hydraulic loading head of the existing testing machine does not need to worry about the problem because the volume of hydraulic oil only needs to be expanded to a minimum amount to completely unload the pressure after the resistance of a rock sample is lost, the initial speed of the piston pressure head is not large, the hydraulic loading head can stop moving in a short descending stroke, and special protective measures are not needed to be taken for the hydraulic loading head. This also means that: in order to reduce energy consumption in the rock mechanical test process, when high-pressure gas is used as power to perform the rock mechanical test, the hydraulic loading head of the existing testing machine needs to be redesigned.
Disclosure of Invention
The present application is directed to solving at least one of the problems in the prior art. Therefore, one of the purposes of the present invention is to provide a loading head for a high pressure gas driven rock mechanical testing machine, so as to solve the problem that the hydraulic loading head of the existing hydraulic servo testing machine cannot be directly used for the high pressure gas driven testing machine.
In order to solve the technical problems, the invention adopts the following technical scheme:
a high-pressure gas driven rock mechanical testing machine loading head comprises:
a cylinder body with a closed cavity formed inside;
the piston can axially reciprocate and is arranged in the cylinder body so as to divide the closed cavity into an upper air pressure chamber and a lower oil pressure chamber which are independent from each other;
the loading rod is fixedly connected with the piston and penetrates out of the oil pressure chamber to the outside of the cylinder body;
the utility model discloses a hydraulic cylinder, including the oil pressure chamber, the oil pressure chamber is equipped with the urceolus, match in the urceolus slide be provided with the inner tube of piston interlock, be equipped with first damping hole and second damping hole on the bottom of inner tube and the lateral wall respectively, be equipped with one-way inlet port and one-way oil outlet on the cylinder body, one-way inlet port, urceolus, first damping hole, inner tube, second damping hole, oil pressure chamber and one-way oil outlet communicate in order and constitute the damping oil circuit, the atmospheric pressure chamber communicates with outside high pressurized air source through the high-pressure gas servo valve that sets up on the cylinder body, the atmospheric pressure indoor position of being located the top of piston is equipped with the oil blanket, be located on the piston the oil blanket in situ be.
Furthermore, the outer cylinder is in sealed butt joint with the bottom of the oil pressure chamber, and one end, extending out of the outer cylinder, of the inner cylinder is in sealed butt joint with the piston.
Furthermore, be located in the airtight cavity the both sides of piston are equipped with and carry out spacing locating part to piston motion stroke, the locating part towards the piston end is equipped with the cushion.
Further, the elastic pad is a rubber pad.
Furthermore, the number of the outer cylinders is multiple, and the outer cylinders are uniformly arranged on the periphery of the loading rod
Furthermore, the end face, facing the piston, of the elastic pad is provided with corrugated fluctuation.
Further, when the piston contacts with a limiting part in the air pressure chamber, the length of the inner cylinder inserted into the outer cylinder is not less than 2 times of the outer diameter of the inner cylinder.
Furthermore, the second damping holes are close to the piston and are uniformly distributed along the circumferential direction of the inner cylinder.
Furthermore, the one-way oil inlet hole and the one-way oil outlet hole are respectively connected with the oil tank through an external oil pipe, and an oil pump is arranged on the external oil pipe of the one-way oil inlet hole.
Furthermore, the high-pressure gas servo valve is provided with an independent air inlet and an independent air outlet, the air inlet is communicated with an external high-pressure gas source, and the air outlet is communicated with the atmosphere through an oil gas filtering device.
Furthermore, when the piston contacts with a limiting part in the air pressure chamber, a gap exists between the oil seal layer and the top wall of the air pressure chamber.
Compared with the prior art, the invention has the following beneficial effects:
1. the high-pressure gas drives the hydraulic oil to do work on the piston, so that the energy consumption is low, the noise is low, and the precision is high;
2. the impact energy of the piston can be absorbed, and the piston and the oil cylinder are protected;
3. the control principle is simple, the structure composition is simple, and the reliability is high.
Drawings
FIG. 1 is a schematic three-dimensional overall view of a loading head according to an embodiment of the present invention;
FIG. 2 is a schematic longitudinal section of a loading head according to an embodiment of the present invention;
FIG. 3 is a schematic view of the structure of the lower part inside the loading head in the embodiment of the invention;
FIG. 4 is a schematic view of the upper structure in the loading head in the embodiment of the present invention;
fig. 5 is a detailed structure schematic diagram of the piston protection damper in the embodiment of the invention.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Referring to fig. 1-5, a high-pressure gas driven loading head for a rock mechanics testing machine comprises a cylinder body 1, a piston 2, a buffer stop member 3, a high-pressure gas servo valve 4, a hydraulic oil pressure gauge 5, a one-way oil inlet hole 6 and a one-way oil outlet hole 7, wherein a closed cavity is formed inside the cylinder body 1. The piston 2 can axially reciprocate in the closed cavity, thereby dividing the closed cavity into an upper air pressure chamber 8 and a lower oil pressure chamber 9 which are independent from each other, a loading rod 10 penetrating out of the cylinder 1 from the bottom end of the oil pressure chamber 9 is fixedly connected with the bottom of the piston 2, a buffering stopping member 3 is arranged in the oil pressure chamber 9 and comprises an outer cylinder 301 and an inner cylinder 302, the outer cylinder 301 is fixedly arranged in the oil pressure chamber 9, the inner cylinder 302 is arranged in the outer cylinder 301 in a matching and sliding way and is linked with the piston 2, a first damping hole 303 and a second damping hole 304 are respectively arranged on the bottom end and the side wall of the inner cylinder 302, a one-way oil inlet 6 and a one-way oil outlet 7 are arranged at the bottom end of the cylinder 1, the one-way oil inlet 6, the outer cylinder 301, the first damping hole 303, the inner cylinder 302, the second damping hole 304, the oil pressure chamber 9 and the one-way oil outlet 7 are sequentially communicated to form, the air pressure chamber 8 is communicated with an external high-pressure air source through the high-pressure air servo valve 4, an oil seal layer 11 is arranged above the piston 2 in the air pressure chamber 8, the oil seal layer 11 is a hydraulic oil layer filled in the air pressure chamber 9, the hydraulic oil pressure gauge 5 is arranged above the piston 2 in the oil seal layer 11 and is in communication connection with the high-pressure air servo valve 4 through an external computer, the hydraulic oil layer 11 is arranged to prevent high-pressure air from entering the oil pressure chamber 9, and accordingly the damping force of a damping oil path can be improved. In this embodiment, the high-pressure gas servo valve 4 is a conventional structure and is not described in detail herein.
In the actual manufacturing process, the cylinder body 1 is composed of a hollow cylinder body 101, and an upper end cover 102 and a lower end cover 103 which are hermetically arranged at two ends of the hollow cylinder body, and because the air pressure chamber 8 needs to bear larger pressure, the upper end cover 102 can be connected with the hollow cylinder body 101 in a welding mode, the oil pressure cavity 9 bears smaller pressure relatively, and the lower end cover 103 can be connected with the hollow cylinder body 101 in a bolt connection mode.
The invention takes high-pressure gas as the power of the loading head for the first time, and has the characteristics of low energy consumption, low noise and high precision compared with the existing oil pressure loading mode. The real-time data fed back by the hydraulic oil pressure gauge is adopted to automatically control the air inlet rate of the high-pressure gas, so that the loading load is adjusted, and the hydraulic oil pressure gauge has the advantages of simple control principle, simple structure and high reliability. When the loading rod is used for loading a rock sample, after the rock sample is damaged, the flowing resistance generated by a damping oil path formed by the first damping hole, the second damping hole, the oil pressure chamber, the one-way oil outlet hole and the like acts on the piston, so that the impact load of the loading rod is reduced, and the purposes of absorbing the impact energy of the piston and protecting the piston and the oil cylinder are achieved.
Specifically, the outer cylinder 301 is in sealed abutment with the bottom of the oil pressure chamber 9, and the end of the inner cylinder 302 extending out of the outer cylinder 301 is in sealed abutment with the piston 2, so as to improve the damping force of the entire damping oil path. The arrangement of the second orifice 304 may be: the piston is arranged close to the piston and evenly distributed along the circumferential direction of the inner cylinder 302, so that the aim of reducing the impact load of the piston 2 can be fulfilled to the maximum extent.
In particular, when the buffering stoppers 3 are provided in plural numbers and uniformly arranged on the outer periphery of the charge rod 10, the impact load of the piston 2 can be uniformly absorbed, and the piston 2 can be further prevented from being broken.
Preferably, in the present embodiment, the one-way oil inlet 6 and the one-way oil outlet 7 are respectively connected to an oil tank (not shown in the figure) through an external oil pipe, and an oil pump (not shown in the figure) is disposed on the external oil pipe of the one-way oil inlet 6. The high-pressure gas servo valve 4 is provided with an independent gas inlet 401 and an independent gas outlet 402, the gas inlet 401 is communicated with an external high-pressure gas source, and the gas outlet 402 is communicated with the atmosphere through an oil gas filtering device (not shown in the figure).
It should be noted that, in practical application, an upper limit piece 12 may be further installed in the air pressure chamber 8, a lower limit piece 13 may be further installed in the oil pressure chamber 9, the piston 2 is disposed between the upper limit piece 12 and the lower limit piece 13, an elastic pad 14 may be further disposed on an end surface of the upper limit piece 12 corresponding to the lower limit piece 13, a maximum clear distance between the piston 2 and the lower limit piece 13 is smaller than a free stroke of the inner cylinder, a moving stroke of the piston 2 is limited by the upper limit piece 12 and the lower limit piece 13, so that the piston 2 can only move between the upper limit piece 12 and the lower limit piece 13, thereby preventing the piston from directly striking the cylinder, absorbing impact energy of the piston by elastic deformation generated by the elastic pad, and effectively protecting the piston 2 and the cylinder 1. Specifically, the elastic pad 14 may be made of a material having energy absorbing properties, such as rubber or polyurethane.
In practical design, the end surface of the elastic pad 14 facing the piston 2 is provided with corrugated undulations, so that the problem of difficult return of the piston 2 caused by the sucking disc phenomenon can be effectively prevented. When the piston 2 contacts the upper limiting part 12, a gap exists between the oil seal layer 11 and the top wall of the air pressure chamber 8, so that high-pressure gas can be quickly filled into the air pressure chamber to realize loading during loading, and the gas supply pressure of a high-pressure gas source can be effectively reduced.
In consideration of the sealing property between the inner cylinder 302 and the outer cylinder 301, the length of insertion of the inner cylinder 302 into the outer cylinder 301 when the piston 2 contacts the upper stopper 12 is not less than 2 times the outer diameter of the inner cylinder in order to prevent the hydraulic oil from flowing out from the gap between the inner cylinder 302 and the outer cylinder 301 and thereby reduce the damping force.
The working principle of the invention is as follows:
during preloading: the oil pressure chamber is filled with hydraulic oil, the one-way oil outlet hole 7 is opened, the air inlet 401 on the high-pressure gas servo valve 4 is opened, high-pressure gas is slowly injected into the air pressure cavity 8 and is maintained at a low pressure level, and after the loading rod 10 is in close contact with the rock sample, the air inlet switch is closed.
During loading: the opening states of the one-way oil outlet hole 7 and the air inlet 401 are kept, the pressure of the oil seal layer is monitored in real time through the hydraulic oil pressure meter 5 according to the preset loading rate, data are fed back to a control program in a computer in real time, the control program judges whether the flow needs to be increased or decreased according to the set loading rate, then the computer sends a command to the high-pressure gas servo valve to act until a rock sample is damaged, and meanwhile, the air inlet 401 is closed.
Loading protection: because the axial deformation of the rock sample is very small in the loading process, the descending speed of the piston 2 is very slow, and the inner cylinder 302 is driven to slowly descend in the outer cylinder 301, at the moment, hydraulic oil in the outer cylinder 301 enters the inner cylinder 302 through the first damping hole 303, hydraulic oil in the inner cylinder 302 enters the oil pressure chamber 9 through the second damping hole 304, hydraulic oil at the lower part of the oil pressure chamber 9 enters the external oil tank through the one-way oil outlet hole 7, and in the process, because the flow rate of the hydraulic oil is very small, the received resistance is negligible.
And (3) destruction protection: when a rock sample is damaged, the pressure in the high-pressure gas is hardly reduced, the hydraulic oil can be continuously driven to do work to the piston 2, the piston 2 can move downwards in an accelerated manner due to the loss of the resistance transmitted by the rock sample through the loading rod 10, and the inner cylinder 302 is pushed to move in the outer cylinder 301 in an accelerated manner, along with the increase of the descending speed, the flow velocity of the hydraulic oil passing through the first damping hole 303, the second damping hole 304 and the one-way oil outlet hole 7 is increased, the resistance is correspondingly increased, the purposes of reducing the impact load of the piston and absorbing energy are achieved, when the flowing resistance and the acting force of the high-pressure gas are balanced, the piston keeps moving at a constant speed, and the rubber pad 14 on the lower limiting piece 13 can bear the acting force of the.
And (4) return protection: the rubber pad 14 is provided with the corrugated fluctuation, so that the difficulty in returning the piston 2 caused by the sucking disc phenomenon can be effectively prevented.
The hydraulic loading head overcomes the defect that the hydraulic loading head of the current testing machine cannot be used for driving the testing machine device by high-pressure gas, can use the high-pressure gas as power to complete the rock mechanics test project by redesigning the structure of the loading head, reduces the test energy consumption and cost, and improves the loading precision and the stability and reliability of the system.
The above examples are merely illustrative of the present invention clearly and are not intended to limit the embodiments. Other variations and modifications will be apparent to persons skilled in the art in light of the above description. Nor is it intended to be exhaustive of all embodiments. And obvious variations or modifications of the invention may be made without departing from the scope of the invention.
Claims (6)
1. A high-pressure gas driven rock mechanical testing machine loading head comprises:
a cylinder body with a closed cavity formed inside;
the piston can axially reciprocate and is arranged in the cylinder body so as to divide the closed cavity into an upper air pressure chamber and a lower oil pressure chamber which are independent from each other;
the loading rod is fixedly connected with the piston and penetrates out of the oil pressure chamber to the outside of the cylinder body;
the method is characterized in that: an outer cylinder is fixedly arranged in the oil pressure chamber, an inner cylinder linked with the piston is arranged in the outer cylinder in a matching sliding manner, a first damping hole and a second damping hole are respectively formed in the bottom end and the side wall of the inner cylinder, a one-way oil inlet hole and a one-way oil outlet hole are formed in the cylinder body, the one-way oil inlet hole, the outer cylinder, the first damping hole, the inner cylinder, the second damping hole, the oil pressure chamber and the one-way oil outlet hole are sequentially communicated to form a damping oil path, the air pressure chamber is communicated with an external high-pressure air source through a high-pressure gas servo valve arranged on the cylinder body, an oil seal layer is arranged in the air pressure chamber and positioned above the piston, and a hydraulic oil pressure gauge communicated with the high-;
the outer cylinder is in sealed butt joint with the bottom of the oil pressure chamber, and one end of the inner cylinder, which extends out of the outer cylinder, is in sealed butt joint with the piston;
limiting parts for limiting the motion stroke of the piston are arranged on two sides of the piston in the closed cavity, and elastic pads are arranged on the limiting parts facing the piston end;
the end surface of the elastic pad facing the piston is provided with corrugated fluctuation;
when the piston is in contact with a limiting part in the air pressure chamber, the length of the inner cylinder inserted into the outer cylinder is not less than 2 times of the outer diameter of the inner cylinder.
2. The loading head of the high-pressure gas driven rock mechanical testing machine according to claim 1, characterized in that: the number of the outer cylinders is multiple, and the outer cylinders are uniformly arranged on the periphery of the loading rod.
3. The high-pressure gas driven rock mechanical tester loading head according to claim 1 or 2, characterized in that: the second damping hole is close to the piston and is circumferentially and uniformly distributed along the inner cylinder.
4. The high-pressure gas driven rock mechanical tester loading head according to claim 1 or 2, characterized in that: the one-way oil inlet hole and the one-way oil outlet hole are respectively connected with the oil tank through an external oil pipe, and an oil pump is arranged on the external oil pipe of the one-way oil inlet hole.
5. The high-pressure gas driven rock mechanical tester loading head according to claim 1 or 2, characterized in that: the high-pressure gas servo valve is provided with an independent gas inlet and an independent gas outlet, the gas inlet is communicated with an external high-pressure gas source, and the gas outlet is communicated with the atmosphere through an oil gas filtering device.
6. The high-pressure gas driven rock mechanical tester loading head according to claim 1 or 2, characterized in that: when the piston contacts with the limiting part in the air pressure chamber, a gap exists between the oil seal layer and the top wall of the air pressure chamber.
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| CN201811015269.1A CN108896401B (en) | 2018-08-31 | 2018-08-31 | High-pressure gas driven rock mechanical testing machine loading head |
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| CN201811015269.1A CN108896401B (en) | 2018-08-31 | 2018-08-31 | High-pressure gas driven rock mechanical testing machine loading head |
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| CN108896401A CN108896401A (en) | 2018-11-27 |
| CN108896401B true CN108896401B (en) | 2021-04-16 |
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| CN113984533B (en) * | 2021-10-26 | 2023-08-22 | 中国航发沈阳发动机研究所 | Component surface pressure loading device |
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