High-temperature and high-pressure mechanical property test equipment and test method for deep well drilling tool

Abstract

The invention relates to the technical field of mechanical property testing equipment for deep well drilling tools, in particular to high-temperature and high-pressure mechanical property testing equipment for a deep well drilling tool and a testing method. At least two pairs of auxiliary pressure sealing cavities which are symmetrical about the main pressure sealing cavity are formed in the two axial sides of the kettle body by taking the main pressure sealing cavity as a reference, and drilling tool insertion holes are formed between every two adjacent pressure sealing cavities in the axial direction of the kettle body and in the end parts of the pressure sealing cavities at the head end and the tail end; all the pressure sealing cavities and all the drilling tool insertion holes are axially connected to form a drilling tool insertion channel; the kettle body is provided with a pressure conveying pipeline corresponding to each pressure sealing chamber and communicated with the pressure sealing chamber, the kettle body is provided with a heating mechanism corresponding to the main pressure sealing chamber, every two adjacent pressure sealing chambers are communicated through a differential pressure valve, and the pressure sealing chambers at the head end and the tail end of the kettle body are respectively provided with an overflow valve.

Description

Technical Field

[0001] This invention relates to the technical field of mechanical performance testing equipment for deep well drilling tools, specifically to a high-temperature and high-pressure mechanical performance testing device and method for deep well drilling tools. Background Technology

[0002] Against the backdrop of the ongoing advancements in energy exploration and extraction towards deeper levels, ultra-deep geological exploration and the development of oil and gas wells at depths of tens of thousands of meters are flourishing. Ultra-deep geological exploration aims to uncover the geological structures and resource distribution at deeper depths of the Earth, while the development of oil and gas wells at depths of tens of thousands of meters seeks to extract abundant oil and gas resources buried thousands of meters underground. However, these deep operations place extremely stringent demands on downhole tools and surface testing equipment. These devices must undergo comprehensive and rigorous durability and reliability verification under extreme environmental conditions of ultra-high temperature and ultra-high pressure. In recent years, to accurately simulate the tensile, compressive, and torsional mechanical properties of drilling tools in deep-earth environments of tens of thousands of meters, and to provide a realistic and effective testing environment for downhole tools and surface testing equipment, related testing devices often have to withstand temperatures as high as 300°C and pressures as high as 175 MPa. Under such extreme conditions, traditional test well casings and sealing structures face unprecedented challenges. Under the continuous action of high temperature and high pressure, the material properties of traditional test well casings may change, affecting the strength and stability of the casing and posing a huge test to the sealing performance. The slightest carelessness may lead to leakage and other problems, which in turn affect the accuracy and safety of the entire test.

[0003] In high-temperature and high-pressure sealing scenarios, the common sealing method at the sealing positions of each chamber of the testing equipment (each chamber is linearly connected in sequence) is multi-stage series sealing. However, multi-stage series sealing generally lacks active pressure distribution or pressure balancing design. This design deficiency creates a risk of cascading failure in the entire sealing system. Traditional multi-stage sealing typically achieves effective isolation of high pressure by connecting multiple sealing rings in series. However, this method has significant drawbacks. In actual operation, the total pressure difference is randomly distributed among the sealing stages. This random distribution leads to uneven pressure distribution. Specifically, a particular seal often experiences a pressure difference exceeding its allowable pressure difference. Once this occurs, that seal will fail first. Because the pressure difference experienced by the remaining seals increases sharply after one seal fails, under this pressure difference exceeding the normal tolerance range, the remaining seals will fail sequentially. Ultimately, the entire sealing system will fail completely, unable to perform its intended sealing function, severely affecting the normal operation of the equipment and the smooth conduct of the test. Summary of the Invention

[0004] (a) Technical problems to be solved

[0005] In view of the above-mentioned shortcomings and deficiencies of the prior art, the present invention provides a high-temperature and high-pressure mechanical performance testing device and method for deep well drilling tools, which solves the technical problem that the existing high-temperature and high-pressure mechanical performance testing devices for deep well drilling tools adopt a multi-stage series sealing method, which has the potential for cascading failure.

[0006] (II) Technical Solution

[0007] To achieve the above objectives, the high-temperature and high-pressure mechanical performance testing equipment for deep well drilling tools of the present invention includes a vessel body;

[0008] The vessel body is provided with a main pressure sealing chamber in the middle, and with the main pressure sealing chamber as the reference, at least two pairs of auxiliary pressure sealing chambers are provided symmetrical about the main pressure sealing chamber on both sides of the vessel body along the axial direction. Drill insertion holes are provided between two adjacent pressure sealing chambers along the axial direction of the vessel body and at the ends of the pressure sealing chambers at both ends. All pressure sealing chambers and all drill insertion holes are axially connected to form a drill insertion channel.

[0009] Each pressure sealing chamber on the vessel body is provided with a pressure conveying pipeline connected to it. A heating mechanism is provided on the vessel body corresponding to the main pressure sealing chamber. Each pair of adjacent pressure sealing chambers is connected by a differential pressure valve. Overflow valves are provided in the pressure sealing chambers at both ends of the vessel body.

[0010] When the test drill bit is inserted into the drill bit insertion channel, the two adjacent pressure-sealed chambers are connected only through the differential pressure valve.

[0011] Optionally, the pressure-sealed chambers at both ends of the vessel body are respectively provided with end cooling seals;

[0012] The end cooling seal includes a vessel flange, an end cover flange, an end sealing ring, and a stepped conical annular sealing strip;

[0013] The first end of the vessel flange is screwed to one end of the vessel body, and the end sealing ring is clamped between the two.

[0014] The second end of the vessel flange is screwed to the end cover flange, and the stepped conical annular sealing strip is sandwiched between the two.

[0015] Along the axial direction of the vessel body, both the vessel body flange and the end cover flange are provided with the drill insertion hole.

[0016] Optionally, the end cooling seal further includes a serpentine baffle and a nickel-titanium alloy wire;

[0017] Along the axial direction of the vessel body, the serpentine baffle is arranged in a serpentine shape between the vessel body flange and the end cap flange, so that the three form a serpentine groove; the nickel-titanium alloy wire is disposed inside the serpentine groove;

[0018] The serpentine baffle is located at one end of the stepped conical annular sealing strip near the vessel body.

[0019] Optionally, a spiral cooling channel is provided on the vessel flange and / or the end cover flange; the inlet and outlet ends of the spiral cooling channel are connected to the outer wall of the end cooling seal.

[0020] The spiral cooling channel has a built-in turbulence promoter.

[0021] Optionally, a plurality of retaining rings are coaxially arranged on the inner wall of the vessel; the inner wall of the vessel and a pair of adjacent retaining rings form a pressure-sealed chamber;

[0022] The retaining ring includes a sealing ring and a foot-shaped slip ring arranged coaxially, and both are interference-fitted with the wall of the test drill bit, so that the inner ring of the retaining ring is the insertion hole of the drill bit;

[0023] The foot-shaped slip ring is coaxially connected to the inner wall of the vessel body, and the opening of the foot-shaped slip ring faces the axis of the vessel body;

[0024] The sealing ring engages with the opening of the foot-shaped slip ring.

[0025] Optionally, the pair of sealing rings provided at both ends of the main pressure sealing chamber are silicone rubber sealing rings;

[0026] The sealing ring disposed between two adjacent auxiliary pressure sealing chambers is a fluororubber sealing ring;

[0027] The end sealing ring and / or the stepped conical annular sealing strip are nitrile rubber sealing rings.

[0028] Optionally, the heating mechanism includes an oil bath heating cylinder coaxially sleeved on the vessel body;

[0029] Along the axial direction of the vessel body, the inner cavity of the oil bath heating cylinder covers the main pressure sealing chamber.

[0030] Optionally, the high-temperature and high-pressure mechanical performance testing equipment for deep well drilling tools further includes a force loading mechanism; the force loading mechanism includes a test bench, and an axial load loading mechanism, a torque loading mechanism, and a clamping mechanism disposed on the test bench;

[0031] The vessel body is vertically mounted on the platform; the gripper of the clamping mechanism is positioned directly above the drill insertion hole;

[0032] The output shaft of the axial load loading mechanism is coaxially positioned above the drill bit insertion hole;

[0033] The output end of the torque loading mechanism is located above the drill insertion hole.

[0034] Furthermore, the present invention also provides a test method for a high-temperature and high-pressure mechanical property testing device for deep well drilling tools. The test method is based on the high-temperature and high-pressure mechanical property testing device for deep well drilling tools described above, and includes:

[0035] The test drill bit is inserted through the drill bit insertion channel;

[0036] During the pressurization stage of the pressure sealing chamber, pressurization is completed step by step through multiple pressure conveying pipes from the auxiliary pressure sealing chamber at the end of the vessel body to the main pressure sealing chamber.

[0037] During the depressurization phase of the pressure-sealed chamber, the path of step-by-step depressurization is the opposite of the path of step-by-step pressurization during the pressurization phase.

[0038] The heating mechanism is activated to heat the test drill inside the reactor vessel;

[0039] The mechanical properties of the test drill were tested.

[0040] Optionally, the high-temperature and high-pressure mechanical property testing equipment is set vertically, and its bottom part is buried in a pit.

[0041] (III) Beneficial Effects

[0042] The beneficial effects of this invention are:

[0043] This invention can accurately simulate a high-temperature and high-pressure environment. The high-temperature and high-pressure mechanical property testing equipment is used to simulate the mechanical properties of test drills under high-temperature and high-pressure conditions. A heating mechanism heats the vessel to a preset high temperature, and the vessel can conduct heat to the test drill inside, achieving high-temperature simulation. A pressure delivery pipeline delivers a medium to the vessel, pressurizing each chamber to a preset high pressure, achieving high-pressure simulation. After completing the high-temperature and high-pressure simulation, mechanical property tests can be performed.

[0044] Multiple chambers are connected in series along the axial direction, and adjacent chambers are connected by multiple differential pressure valves, forming a pyramid-shaped gradient sealing system. This gradient sealing system ensures a reasonable distribution of pressure among the chambers, so that even if the sealing structure of one chamber temporarily fails, the remaining chambers can still withstand the pressure, thereby reducing the risk of seal fatigue and system failure, and enhancing the durability and applicability of the equipment. Pressure transmission pipelines are used to transport the medium and increase the internal pressure of the chambers. Overflow valves are located at the end of the vessel body to release abnormally high pressure.

[0045] In its structural design, the sealing system employs a clever layout that allows each chamber to be both interconnected and relatively independent. When a problem occurs in one stage, the total pressure difference is shared by the remaining chambers, enabling them to actively distribute pressure and ensuring continued operation even in the event of partial sealing failure. Furthermore, the special design of the gradient chambers absorbs energy generated by pressure fluctuations, thus balancing the pressure. This design effectively reduces fatigue caused by frequent pressure fluctuations, significantly extending the service life of the sealing structure.

[0046] This invention enables precise control of the differential pressure at each sealing stage under high temperature and high pressure conditions, real-time monitoring of the pressure at each sealing stage, and dynamic adjustment of the sealing structure to ensure that the total differential pressure is rationally distributed across each sealing stage. Compared with existing technologies, this precise differential pressure control effectively avoids uneven pressure distribution caused by random sharing of the total differential pressure among sealing stages when pressure fluctuations occur. It distributes the differential pressure of the failed chamber to the remaining chambers, effectively reducing pressure fluctuations in the failed chamber. Overall pressure fluctuations are eliminated through pressure relief valves, thereby significantly reducing the risk of sealing failure due to excessive differential pressure on any sealing structure and significantly improving the reliability of the entire sealing system. Attached Figure Description

[0047] Figure 1 This is a schematic diagram of the high-temperature and high-pressure mechanical performance testing equipment for deep well drilling tools according to the present invention.

[0048] Figure 2 This is a cross-sectional view of the high-temperature and high-pressure mechanical property testing equipment of the present invention after removing the force loading mechanism;

[0049] Figure 3 for Figure 2 Enlarged view of point A in the middle;

[0050] Figure 4 for Figure 2 Enlarged view of point B in the middle;

[0051] Figure 5 This is a schematic diagram showing the connection between the end of the vessel body and the end cooling seal of the present invention;

[0052] Figure 6 This is a side view of the end cooling seal of the present invention;

[0053] Figure 7 This is a schematic diagram showing the connection between the serpentine baffle and the nickel-titanium alloy wire of the present invention;

[0054] Figure 8 This is a schematic diagram of the turbulence promoter of the present invention;

[0055] Figure 9 This is a schematic diagram of the connection of the retaining ring of the present invention;

[0056] Figure 10 A schematic diagram of the force loading mechanism of the present invention.

[0057] Explanation of reference numerals in the attached figures

[0058] 1: Force loading mechanism; 2: Clamping mechanism; 3: Heating mechanism; 4: Vessel body; 401: Main pressure sealing chamber; 402: Auxiliary pressure sealing chamber; 5: Pressure connection channel; 6: Differential pressure valve; 7: Pressure transmission pipeline; 8: Overflow valve; 9: Spiral cooling channel; 10: Turbulence promoter; 11: Vessel body flange; 12: End sealing ring; 13: Stepped conical annular sealing strip; 14: Snap ring; 1401: Sealing ring; 1402: Foot-shaped slip ring; 15: End cover flange; 1601: Serpentine baffle; 1602: Nickel-titanium alloy wire; 17: Sealing ring; 18: Test drill. Detailed Implementation

[0059] To better explain and facilitate understanding of the present invention, the present invention will be described in detail below with reference to the accompanying drawings and specific embodiments.

[0060] It should be noted that all directional indications (such as up, down, left, right, front, back, etc.) in the embodiments of the present invention are only used to explain the relative positional relationship and movement of each component in a certain specific posture (as shown in the figure). If the specific posture changes, the directional indication will also change accordingly.

[0061] Furthermore, in this invention, descriptions involving "first," "second," etc., are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0062] In this invention, unless otherwise explicitly specified and limited, the terms "connection," "fixed," etc., should be interpreted broadly. For example, "fixed" can mean a fixed connection, a detachable connection, or an integral part; "connection" can mean a mechanical connection or an electrical connection; it can mean a direct connection or an indirect connection through an intermediate medium; it can mean the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0063] See Figures 1 to 5 The present invention provides a high-temperature and high-pressure mechanical performance testing device for deep well drilling tools. The high-temperature and high-pressure mechanical performance testing device for deep well drilling tools includes a force loading mechanism 1, a vessel body 4, a heating mechanism 3, an end cooling seal, a differential pressure valve 6, a pressure conveying pipeline 7, and an overflow valve 8. Along the axial direction of the vessel body 4, a through drilling tool insertion channel is provided inside the vessel body 4.

[0064] In this embodiment, the drill insertion channel is formed by multiple drill insertion holes and multiple chambers connected axially. Specifically, multiple retaining rings 14 are coaxially arranged on the inner wall of the vessel body 4. The inner wall of the vessel body 4 and the opposing annular sidewalls of each pair of adjacent retaining rings 14 form a pressure-sealed chamber (hereinafter referred to as a chamber). The chamber in the vessel body 4 includes a main pressure-sealed chamber 401 and a pair of auxiliary pressure-sealed chambers 402. The pair of auxiliary pressure-sealed chambers 402 are connected to both ends of the main pressure-sealed chamber 401 in a one-to-one correspondence. Along one side of the axial direction of the vessel body 4, the main pressure-sealed chamber 401 and the multiple auxiliary pressure-sealed chambers 402 are connected sequentially, and the pressure decreases sequentially during operation. As shown in the figure, in this embodiment, two pairs of auxiliary pressure sealing chambers 402 are provided. The two auxiliary pressure sealing chambers 402 adjacent to the two ends of the main pressure sealing chamber 401 are symmetrical about the main pressure sealing chamber 401, forming a pair of auxiliary pressure sealing chambers 402. At the opposite end of the pair of auxiliary pressure sealing chambers 402 from the main pressure sealing chamber 401, another auxiliary pressure sealing chamber 402 is provided, forming a second pair of auxiliary pressure sealing chambers 402. The two adjacent chambers (including the adjacent main pressure sealing chamber 401 and auxiliary pressure sealing chamber 402, and the two adjacent auxiliary pressure sealing chambers 402) are connected by the inner ring of the retaining ring 14. The inner ring of the retaining ring 14 forms a drill insertion hole for the interference fit insertion test drill 18. At the same time, drill insertion holes are also provided at both ends of the vessel body 4 for the insertion and exit of the drill into and out of the vessel body 4. Therefore, in this embodiment, the drill insertion hole at the end of the vessel body 4, the auxiliary pressure sealing chamber 402, the drill insertion hole formed by the retaining ring, the main pressure sealing chamber 401, the drill insertion hole formed by the retaining ring, the auxiliary pressure sealing chamber 402, the drill insertion hole formed by the retaining ring, the auxiliary pressure sealing chamber 402, and the drill insertion hole at the end of the vessel body 4 are connected end to end to form a drill insertion channel.

[0065] Furthermore, the outer wall of the vessel body 4 is equipped with a pair of overflow valves 8, multiple differential pressure valves 6, and multiple pressure conveying pipes 7; a pair of adjacent chambers are connected by differential pressure valves 6, and this connection is made when the differential pressure valves 6 are open; the differential pressure valves 6 are normally closed and are only opened when the pressure fluctuation is large, that is, when the pressure difference between adjacent chambers is too large; the chambers at both ends of the vessel body 4 are connected to a pair of overflow valves 8 respectively; the free ends of the chambers at both ends of the vessel body 4 are sealed by end cooling seals; the inner ring of the end cooling seal serves as the drill insertion hole at the end of the vessel body 4, and like the inner ring of the retaining ring 14, it is used to engage with the test drill 18 to form a dynamic sealing structure. Thus, when the drill is inserted into the drill insertion channel, the adjacent chambers are no longer connected through the drill insertion hole between them, and the drill insertion hole at the end is no longer connected to the adjacent chambers and the outside. The adjacent chambers can only be connected through the differential pressure valves 6. Multiple pressure conveying pipes 7 are connected to multiple chambers in a one-to-one correspondence; the heating mechanism 3 is set on the vessel body 4 so as to heat the main pressure sealing chamber 401.

[0066] Multiple auxiliary pressure sealing chambers 402 are symmetrically arranged on both sides of the main pressure sealing chamber 401. The main pressure sealing chamber 401 is the core chamber for high-temperature and high-pressure mechanical performance testing and also the main chamber where pressure fluctuations occur. In this embodiment, the inner diameters of the main pressure sealing chamber 401 and the auxiliary pressure sealing chambers 402 are equal, but the axial length of the main pressure sealing chamber 401 is greater than the axial length of the auxiliary pressure sealing chambers 402; each auxiliary pressure sealing chamber 402 is a chamber of the same size. The multiple auxiliary pressure sealing chambers 402 are symmetrically arranged on both sides of the main pressure sealing chamber 401. Compared with the method of arranging multiple auxiliary pressure sealing chambers 402 sequentially on only one side of the main pressure sealing chamber 401, the symmetrical arrangement can improve the speed at which the failed chamber releases abnormal pressure difference, thereby achieving the purpose of quickly eliminating abnormal pressure fluctuations.

[0067] This embodiment can accurately simulate a high-temperature and high-pressure environment, providing a reliable environmental simulation basis for research and production in related fields. In this embodiment, the high-temperature and high-pressure mechanical performance testing equipment is used to simulate the mechanical performance of the test drill bit 18 under high-temperature and high-pressure conditions. The test drill bit 18 penetrates the interior of the vessel body 4 and is placed as a test object in the high-temperature and high-pressure testing environment to simulate the working state of the downhole drilling assembly under extreme conditions such as high temperature, hydrostatic pressure, and drilling pressure. The test drill bit 18 includes components such as a steel drill pipe and its connected coring system, and can be tested for performance under axial tensile / compression and torsional loads applied in the wellbore. The heating mechanism 3 heats the vessel body 4 to a preset high temperature, and the vessel body 4 can conduct heat to the test drill bit 18 inside it to achieve high-temperature simulation; the pressure conveying pipeline 7 conveys the medium to the vessel body 4, pressurizing each cavity to a preset high pressure to achieve high-pressure simulation; the force loading mechanism 1 applies axial tensile or compressive loads and torque to the test drill bit 18 to achieve external force simulation. During the test, the vessel body 4 is placed on the test drill 18, and then the vessel body 4 is installed on the force loading mechanism 1. After the high temperature and high pressure reach the standard, the mechanical properties test can be carried out.

[0068] The differential pressure valve 6, pressure transmission pipeline 7, overflow valve 8, and various chambers combine to form a pressure control system. The main pressure sealing chamber 401, located in the middle of the vessel body 4, is the maximum pressure chamber. The pressure of multiple auxiliary pressure sealing chambers 402 along the axial direction of the vessel body 4 gradually decreases, forming a pressure gradient distribution, so that the overall pressure of the vessel body 4 is distributed in a pyramid shape.

[0069] Differential pressure valve 6 is connected to a pair of adjacent chambers via a pair of pressure connection channels 5, ensuring the maximum pressure difference between the two adjacent chambers through automatic pressure relief. During testing, under the influence of high temperature and high pressure, the pressure in a certain chamber may become abnormal. At this time, differential pressure valve 6 can automatically open to relieve pressure, that is, to distribute the increased pressure in the abnormal chamber to its adjacent chambers. These adjacent chambers then distribute the pressure to the chambers at the end of the vessel body 4 in stages. Finally, the abnormal pressure is discharged through the overflow valve 8 until the pressure returns to normal, and then all differential pressure valves 6 close. Multiple chambers are connected in series along the axial direction, and adjacent chambers are connected to each other through multiple differential pressure valves 6, forming a pyramid-shaped gradient sealing system. This gradient sealing system mechanism ensures the reasonable distribution of pressure among the chambers at each level, so that even if the sealing structure of a certain chamber temporarily fails, the remaining chambers can still bear the pressure, thereby reducing the risk of seal fatigue and system failure, and enhancing the durability and applicability of the equipment. Pressure transmission pipeline 7 is used to transport the medium and increase the internal pressure of the chamber. Overflow valve 8 is located at the end of the vessel body 4 to release abnormal high pressure. Optionally, the overflow valve 8 is an ultra-high pressure pilot-operated overflow valve, which should be installed as directly and simply as possible on the outlet of the end chamber of the vessel body 4.

[0070] The pressure regulation system employs a gradient sealing system, exhibiting superior performance advantages. In actual high-temperature and high-pressure environments, sealing structures inevitably face various complex factors, leading to frequent failures of certain sealing stages. In traditional sealing system designs, failure of a single sealing stage often severely impacts the entire system, potentially causing system collapse. The gradient sealing system of this invention effectively solves this problem. When a sealing stage fails, the fault only affects adjacent chambers. This is because the sealing system's structural design, through clever layout, ensures that the chambers are both interconnected and relatively independent. When a problem occurs at one stage, the total pressure difference is shared by the remaining chambers, achieving active pressure distribution and ensuring continued operation even with localized sealing failures. Furthermore, the special design of the gradient chambers absorbs energy generated by pressure fluctuations, balancing the pressure. This design significantly reduces fatigue caused by frequent pressure fluctuations, greatly extending the service life of the sealing structure.

[0071] Compared to the pressure-equalizing connection method of multiple chambers sealed in series, the present invention uses a gradient-graded differential pressure connection method for multiple chambers in series, and the differential pressure valve 6 can buffer the pressure. Specifically, during the test, when the force loading mechanism 1 applies a force to the test drill bit 18, it may cause pressure fluctuations in a certain chamber, leading to the failure of the sealing structure, and this chamber becomes the failed chamber. If the pressure-equalizing connection method is used, the pressure in the failed chamber will quickly enter the adjacent chambers or multiple adjacent chambers through the drill bit insertion hole, causing the adjacent chambers to fail rapidly, resulting in a cascading failure. The opening distance of the differential pressure valve 6 of the present invention is affected by the pressure difference of adjacent chambers, so it can play a role in buffering pressure, so that the pressure difference inside the failed chamber enters its adjacent chambers relatively slowly. On the one hand, it ensures that after the failed chamber fails, its adjacent chambers will not fail quickly, thus "locking" the abnormal pressure difference. On the other hand, its adjacent chambers further transmit the pressure difference to the end of the vessel body 4 through the gradient sealing system, and release the abnormal pressure difference through the overflow valve 8 until the pressure of each chamber returns to normal. This process not only ensures the sealing stability of the adjacent chambers, but also completes the discharge of abnormal pressure difference, so that the failed chamber returns to a normal sealed chamber.

[0072] This invention enables precise control of the differential pressure at each sealing level under high temperature and high pressure conditions, real-time monitoring of the pressure at each sealing level, and dynamic adjustment of the sealing structure to ensure that the total differential pressure is rationally distributed across each sealing level. Compared with existing technologies, this precise differential pressure control effectively avoids the uneven pressure distribution caused by the random sharing of the total differential pressure among each sealing stage (i.e., the sealing structure at the end of each cavity) when pressure fluctuations occur. It distributes the differential pressure of the failed cavity to the remaining cavities, effectively reducing the pressure fluctuation of the failed cavity. The overall pressure fluctuation is eliminated by the pressure relief valve 8, thereby greatly reducing the risk of sealing failure due to excessive differential pressure on a certain sealing structure and significantly improving the reliability of the entire sealing system.

[0073] The free ends of the chambers at both ends of the vessel body 4 are sealed by end cooling seals. These end cooling seals combine cooling and sealing functions, effectively reducing the temperature at the ends of the vessel body 4 and mitigating the impact of high temperatures on the material properties of the sealing structure. This improves the strength and stability of the well casing (i.e., vessel body 4) and prevents leakage at the ends of the vessel body 4. The end cooling seals can be cooled by air or liquid cooling; this invention is not limited to either.

[0074] This invention can simulate the high-temperature and high-pressure deep-earth environment of 300℃ and 175MPa at depths of tens of thousands of meters, enabling dynamic testing of drilling tools under such conditions and evaluating their strength and manufacturing process. In one embodiment, four auxiliary pressure sealing chambers 402 are provided. The pressure in the main pressure sealing chamber 401 is set at 175MPa, and the pressure is sequentially reduced to 100MPa and 50MPa in the auxiliary pressure sealing chambers 402 at both ends, forming a gradient pressure distribution.

[0075] like Figure 6 As shown, the pressure-sealed chambers at both ends of the vessel body 4 are respectively provided with end cooling seals; the end cooling seals include a vessel body flange 11, an end cap flange 15, an end sealing ring 12, and a stepped conical annular sealing strip 13; the first end of the vessel body flange 11 is screwed to one end of the vessel body 4, and the end sealing ring 12 is sandwiched between them; the second end of the vessel body flange 11 is screwed to the end cap flange 15, and the stepped conical annular sealing strip 13 is sandwiched between them; along the axial direction of the vessel body 4, both the vessel body flange 11 and the end cap flange 15 are provided with drill insertion holes. Specifically, the end sealing ring 12 serves as the first sealing structure at the end of the vessel body 4, the serpentine baffle 1601 and the nickel-titanium alloy wire 1602 serve as the second sealing structure at the end of the vessel body 4, and the stepped conical annular sealing strip 13 serves as the third sealing structure at the end of the vessel body 4.

[0076] The first sealing structure is a static sealing interface, made of high-temperature adaptable material. When the vessel flange 11 is tightened, the end sealing ring 12 fills the tiny gaps between the surfaces of the vessel flange 11 under compression. Its function is to prevent high-temperature and high-pressure media from leaking from the connection surface between the vessel body 4 and the vessel flange 11; at the same time, it can withstand high axial loads and radial deformation, adapt to thermal expansion caused by temperature and pressure changes, avoid deformation of the vessel flange 11, and thus ensure the integrity of the seal.

[0077] The stepped conical annular sealing strip 13 is composed of multiple coaxially arranged sealing rings stacked together. The stepped conical annular sealing strip 13 consists of multiple conical segments arranged in an axial stepped manner and integrally formed, securely clamped between the vessel flange 11 and the end cap flange 15. The outer or inner diameter of the stepped conical annular sealing strip 13 changes gradually along the axial direction, forming an annular structure that is "from thick to thin" or "from large to small." Each conical segment makes close contact with the wall surface of the vessel flange 11 or the end cap flange 15 during assembly, forming multiple sealing barriers. This structure has high sealing strength and, in conjunction with the first sealing structure, significantly improves the sealing strength at the four ends of the vessel.

[0078] When the vessel body flange 11 and the end cover flange 15 are bolted together, a hydraulic tensioner is used to install and pre-tighten these bolts. All sealing surfaces must be precision machined (Ra≤0.8μm). The bolt and nut surfaces are phosphated or blackened. A groove is opened in the middle and an O-ring is inserted to ensure that the O-ring maintains slight contact with the inner wall of the groove in the free state, which facilitates installation and positioning, and can deform quickly and evenly during pre-tightening.

[0079] See Figure 7 The end cooling seal also includes a serpentine baffle 1601 and a nickel-titanium alloy wire 1602. Along the axial direction of the vessel body 4, the serpentine baffle 1601 is arranged in a serpentine shape between the vessel body flange 11 and the end cap flange 15, forming a serpentine groove. The nickel-titanium alloy wire 1602 is disposed inside the serpentine groove. The serpentine baffle 1601 is located near one end of the stepped conical annular sealing strip 13 close to the vessel body 4. Specifically, the serpentine baffle 1601 is formed by connecting multiple S-shaped plates in an array, and is securely clamped between the vessel body flange 11 and the end cap flange 15. The serpentine groove extends the path of the medium from the first sealing structure to the third sealing structure. The nickel-titanium alloy wire 1602, disposed inside the serpentine groove, increases the flow resistance of the medium and improves the sealing effect. Furthermore, the nickel-titanium alloy wire 1602 can expand at high temperatures and fill the gaps in the serpentine groove, further improving the sealing effect of the end cooling seal.

[0080] See Figure 5 and Figure 8A spiral cooling channel 9 is correspondingly provided on the vessel flange 11 and / or end cover flange 15; the inlet and outlet ends of the spiral cooling channel 9 are connected to the outer wall of the end cooling seal; a turbulence promoter 10 is built into the spiral cooling channel 9. Specifically, the spiral cooling channel 9 is an annular cooling chamber, arranged around the outer side of the end sealing structure of the vessel 4. The spiral structure can promote fluid turbulence, and together with the internally arranged turbulence promoter 10, it can significantly improve the heat exchange efficiency. The turbulence promoter 10 is designed with a combination of spiral plate and annular groove. The spiral plate is arranged along the axial direction of the spiral cooling channel 9, and the vanes form a fluid reversal and rotation flow path along the inner side of the annular groove. This structure makes the cooling fluid generate strong disturbance in the channel, weaken the boundary layer thickness, and improve the local heat transfer coefficient. At the same time, considering the stability of the cooling system under high pressure and high temperature conditions, its vane material is selected from high temperature resistant alloys, and the fixing structure is firmly connected to the cooling pipe wall to prevent fatigue detachment during long-term operation.

[0081] For the structure outside the main pressure sealing chamber 401, high temperature is not required. Therefore, a cooling channel 9 is installed around the end sealing structure of the vessel body 4 to ensure the applicable temperature environment for the end sealing design and prevent end sealing structure failure. The inlet and outlet ends of the spiral cooling channel 9 are connected to external pipelines to locally cool the area near the auxiliary pressure sealing chamber 402 at the end of the vessel body flange 11 and vessel body 4, ensuring the sealing effect of the end cooling seal. The spiral cooling channel 9 works in conjunction with the turbulence promoter 10 to efficiently dissipate heat and control temperature, keeping the equipment operating within a safe temperature range. This temperature management function avoids structural deformation or decreased sealing performance caused by temperature fluctuations, thereby improving the stability of the equipment under extreme conditions. The heating mechanism 3 provides a high-temperature environment, and the spiral cooling channel 9, in conjunction with the turbulence promoter 10, achieves efficient heat dissipation and temperature control, ensuring stable operation of the equipment under extreme conditions.

[0082] like Figure 4 and Figure 9As shown, multiple retaining rings 14 are coaxially arranged on the inner wall of the vessel body 4; the inner wall of the vessel body 4 and a pair of adjacent retaining rings 14 form a pressure-sealed chamber; the retaining ring 14 includes a sealing ring 1401 and a foot-shaped slip ring 1402 coaxially arranged, and both are interference-fitted with the wall surface of the test drill 18 so that the inner ring of the retaining ring 14 is the drill insertion hole; the foot-shaped slip ring 1402 is coaxially connected to the inner wall of the vessel body 4, and the opening of the foot-shaped slip ring 1402 faces the axis of the vessel body 4; the sealing ring 1401 engages with the opening of the foot-shaped slip ring 1402. Specifically, the sealing ring 1401 and the foot-shaped slip ring 1402 are interference-fitted with the test drill 18 to ensure that the medium does not leak at the interface between the foot-shaped slip ring 1402 and the test drill 18 under high temperature and high pressure environment. The foot-shaped slip ring 1402 is an annular component that forms an interference fit with the wall of the test drill 18. That is, the foot-shaped slip ring 1402 is tightly mechanically fitted with the wall of the test drill 18 through an interference fit, thereby maintaining stable support and reliable sealing under dynamic working conditions (including axial tension, compression and torsional loads).

[0083] Furthermore, the pair of sealing rings 1401 at both ends of the main pressure sealing chamber 401 are silicone rubber sealing rings; the sealing ring 1401 between two adjacent auxiliary pressure sealing chambers 402 is a fluororubber sealing ring; and the end sealing ring 12 and / or the stepped conical annular sealing strip 13 are nitrile rubber sealing rings. Specifically, based on the requirements of high temperature resistance and pressure gradient, the materials of each sealing structure are optimized to give each sealing structure the performance of high temperature resistance, sealing, and elastic buffering. Through the special design of the gradient chamber, the energy generated by pressure fluctuations is absorbed. The gradient chamber uses materials with special elasticity and pressure resistance. These materials can undergo elastic deformation when pressure fluctuates, converting the energy of pressure fluctuations into their own elastic potential energy, thereby effectively reducing the impact of pressure fluctuations on the sealing rings. This design effectively reduces the fatigue phenomenon caused by frequent pressure fluctuations in the sealing structure, greatly extending the service life of the sealing rings.

[0084] Secondly, the heating mechanism 3 includes an oil bath heating cylinder coaxially sleeved on the vessel body 4; along the axial direction of the vessel body 4, the inner cavity of the oil bath heating cylinder covers the main pressure sealing chamber 401. In this embodiment, the oil bath heating cylinder is sleeved on the high-temperature and high-pressure vessel body 4, and the two form a cavity that can accommodate the heat transfer oil. The high-temperature heat transfer oil is uniformly heated to the target temperature in the external heating cylinder and then transported to the cavity. During the flow process, the heat transfer oil undergoes efficient heat exchange with the wall of the vessel body 4, transferring heat to the interior of the vessel body 4. The cooled heat transfer oil then flows back to the external heating cylinder for reheating, forming a closed loop.

[0085] The edge of the oil bath heating cylinder is located outside the main pressure sealing chamber 401 to ensure a stable high-temperature environment for the main pressure sealing chamber 401. For the structure outside the main pressure sealing chamber 401, high temperature is not required, so a spiral cooling channel 9 is provided around the end seal of the vessel body 4 to ensure the applicable temperature environment for the end seal design.

[0086] See Figure 10 The force loading mechanism 1 includes a frame, and an axial load loading mechanism, a torque loading mechanism, and a clamping mechanism 2 mounted on the frame. The vessel body 4 is vertically mounted on the frame. The clamping jaws of the clamping mechanism 2 are positioned directly above the uppermost drill insertion hole. The output shaft of the axial load loading mechanism is coaxially positioned above the uppermost drill insertion hole. The output end of the torque loading mechanism is positioned above the uppermost drill insertion hole. Specifically, the clamping mechanism 2 is used to clamp the top of the test drill 18, ensuring stable positioning of the test drill 18 through the frame and clamping mechanism 2. The frame has a high-rigidity structure and is equipped with force sensors and displacement sensors to achieve real-time monitoring and control of load and deformation. In this embodiment, the force loading mechanism 1 uses a combination of a hydraulic servo system and a screw device to achieve tensile / compression loading in the vertical direction, while simultaneously applying torque to the test drill 18. A motor drives the hydraulic servo system, which in turn drives a hydraulic pump via a reduction gear to provide a high-pressure oil source to the hydraulic servo unit. The hydraulic system, controlled by a servo valve, converts hydraulic energy into mechanical force, driving the main loading shaft to apply tensile or compressive loads to the test drill bit 18 in the vertical direction. Simultaneously, a helical device connected to the end of the main shaft, driven by a motor or mechanical linkage, applies a torque load to the test drill bit while simultaneously applying tensile / compressive loads, thus achieving a combined dynamic loading of axial tensile / compressive and torsional loads. The axial load loading mechanism, torque loading mechanism, and clamping mechanism 2 cooperate to connect and fix the end of the test drill bit 18, ensuring stable installation under the aforementioned combined loads, thus forming a complete drill bit extreme condition simulation system.

[0087] Furthermore, the present invention also provides a test method for a high-temperature and high-pressure mechanical property testing device for deep well drilling tools. The test method for the high-temperature and high-pressure mechanical property testing device for deep well drilling tools is based on the aforementioned high-temperature and high-pressure mechanical property testing device for deep well drilling tools, and the test method includes:

[0088] according to Figure 2 As shown in the diagram, the remaining structures were installed ahead of schedule, except for the test drill bit 18.

[0089] Insert the test drill bit 18 through the drill bit insertion channel, so that the outer wall of the test drill bit 18 is engaged with the end cooling seal and the retaining ring 14; vertically install the test drill bit 18 and the vessel body 4 onto the force loading mechanism 1;

[0090] During the pressurization phase of the chamber, pressurization is achieved through multiple pressure delivery pipes 7;

[0091] S1. Pressurize all chambers and stop pressurizing all chambers when the pressure reaches the preset pressure value required for the two chambers at both ends of the vessel body 4.

[0092] S2. Exclude the two chambers at the beginning and end of all chambers that were pressurized last time, pressurize all other chambers from those two chambers inward, and pressurize to the preset pressure value required by the two chambers at the beginning and end of all chambers that are currently being pressurized, and stop pressurizing all chambers that are currently being pressurized.

[0093] S3, repeat S2 until only the main pressure sealing chamber 401 remains after excluding the two chambers at the beginning and end of all chambers that were pressurized last time. Then pressurize only the main pressure sealing chamber 401 until the required preset pressure value is reached.

[0094] The above can be summarized as follows: pressurization is completed step by step from the chamber at the end of the vessel body 4 to the main pressure sealing chamber 401, wherein the preset pressure value of each pressurization is greater than the preset pressure value of the previous pressurization.

[0095] Specifically, in the embodiment with two pairs of auxiliary pressure sealing chambers 402, during the pressurization stage, all chambers are first pressurized to a pressure of 50 MPa in the auxiliary pressure sealing chamber 402 at the end of the vessel body 4 through multiple pressure conveying pipes 7; then, the inner auxiliary pressure sealing chamber 402 and the main pressure sealing chamber 401 are pressurized simultaneously in sequence, increasing the pressure in the inner auxiliary pressure sealing chamber 402 and the main pressure sealing chamber 401 to 100 MPa; then, the main pressure sealing chamber 401 is pressurized to 175 MPa.

[0096] After pressurizing all cavities, the heating mechanism 3 is activated to heat up the test drill 18 inside the vessel body 4; the end cooling seal is activated to cool down both ends of the vessel body 4.

[0097] The starting force loading mechanism 1 is subjected to high temperature and high pressure mechanical performance testing.

[0098] By setting appropriate opening thresholds for each differential pressure valve 6 and overflow valve 8, when a pressure fluctuation occurs in a chamber during the test, and the pressure difference between it and its adjacent chambers reaches the opening threshold set by differential pressure valve 6, differential pressure valve 6 opens. The pressure fluctuation is then transmitted in a gradient to a pair of chambers at both ends of the vessel body 4, and finally depressurized through overflow valve 8. After depressurization, the pressure fluctuations in all chambers decrease, each differential pressure valve 6 closes, and the pressure fluctuations are eliminated. Of course, if the pressure fluctuation of the failed chamber is small, the pressure difference may only need to be distributed to a portion of the chambers, meaning the pressure difference is insufficient to be transmitted to the chambers at the ends of the vessel body 4, and depressurization through overflow valve 8 is not necessary.

[0099] The gradient sealing system can actively distribute pressure in all cavities when pressure fluctuations occur. The pressure distribution in each cavity is relatively uniform, and abnormal pressure is discharged through the overflow valve 8, achieving a pressure balance design and effectively avoiding the hidden danger of cascading failure.

[0100] The high-temperature and high-pressure mechanical performance testing equipment can simulate high-temperature and high-pressure testing environments and is specifically designed for composite load testing of drill string assemblies. A graded pressure distribution design avoids excessive pressure on single-stage seals. This design includes a gradient sealing system and a three-layer sealing structure with end-cooling seals, significantly improving sealing reliability and system safety. The heating mechanism 3 works in conjunction with the end-cooling seals to ensure precise temperature control and equipment stability. The force loading mechanism 1 can simultaneously apply tensile / compressive and torsional loads, improving the realism and comprehensiveness of the test. The pressure control system ensures reasonable pressure distribution in each sealing chamber, reducing fatigue and failure risks. This high-temperature and high-pressure mechanical performance testing equipment realistically simulates extreme downhole conditions, providing reliable data for drill string performance evaluation and optimization. In summary, this equipment integrates load simulation, thermal control management, sealing assurance, and pressure control, possessing high adaptability, high reliability, and high engineering application value. This testing method can provide quantifiable and verifiable performance data for deep well drill string assemblies, providing a solid basis for drill string design optimization, material selection, and operational condition evaluation, thereby enhancing the guidance for engineering practice and the transformation value of scientific research results.

[0101] After the test is completed, the entire equipment can be depressurized, gradually reducing the opening threshold of the overflow valve 8, thereby gradually reducing the pressure in all chambers. For the chambers near the center, further depressurization can be achieved through the pressure delivery pipe 7.

[0102] Furthermore, the high-temperature and high-pressure mechanical property testing equipment is vertically positioned, with its bottom portion buried in a pit to effectively lower the equipment's center of gravity, thereby enhancing its ability to withstand the enormous axial thrust generated by the internal high pressure. Space is reserved around the pit for the installation of pressure delivery pipes 7, used to connect the test medium to the high-pressure system; space is also reserved for an oil bath heating cylinder and a heat dissipation channel to support uniform heating of the vessel body 4 and heat dissipation under high-temperature conditions. Based on this, the oil bath heating cylinder is arranged around the side wall of the vessel body 4 to ensure that the temperature in the area where the test drill 18 is located reaches the predetermined high-temperature operating condition; the heat dissipation channel is placed between the outer shell of the vessel body 4 and the pit wall, and is equipped with a cooling device to ensure that the temperature is controllable and the equipment operates stably during the application of high-pressure loads.

[0103] It should be understood that the above description of specific embodiments of the present invention is only for illustrating the technical approach and features of the present invention, and is intended to enable those skilled in the art to understand the content of the present invention and implement it accordingly. However, the present invention is not limited to the specific embodiments described above. All changes or modifications made within the scope of the claims of the present invention should be covered within the protection scope of the present invention.

Claims

1. A high-temperature and high-pressure mechanical property testing device for deep well drilling tools, characterized in that, Including the vessel body (4); The vessel body (4) is provided with a main pressure sealing chamber (401) in the middle, and with the main pressure sealing chamber (401) as the reference, at least two pairs of auxiliary pressure sealing chambers (402) symmetrical about the main pressure sealing chamber (401) are provided on both sides of the axial direction of the vessel body (4). Drill insertion holes are provided between two adjacent pressure sealing chambers along the axial direction of the vessel body (4) and at the ends of the pressure sealing chambers at both ends. All pressure sealing chambers and all drill insertion holes are axially connected to form a drill insertion channel. The vessel body (4) is provided with a pressure conveying pipe (7) connected to each pressure sealing chamber. The vessel body (4) is provided with a heating mechanism (3) corresponding to the main pressure sealing chamber (401). Each two adjacent pressure sealing chambers are connected by a differential pressure valve (6). The pressure sealing chambers at both ends of the vessel body (4) are respectively provided with overflow valves (8). When the test drill bit (18) is inserted into the drill bit insertion channel, the two adjacent pressure-sealed chambers are connected only through the differential pressure valve (6).

2. The high-temperature and high-pressure mechanical property testing equipment for deep well drilling tools according to claim 1, characterized in that, The pressure-sealed chambers at both ends of the vessel body (4) are respectively provided with end cooling seals; The end cooling seal includes a vessel flange (11), an end cover flange (15), an end sealing ring (12), and a stepped conical annular sealing strip (13). The first end of the vessel flange (11) is screwed to one end of the vessel body (4), and the end sealing ring (12) is clamped between the two. The second end of the vessel flange (11) is screwed to the end cover flange (15), and the stepped conical annular sealing strip (13) is sandwiched between the two. Along the axial direction of the vessel body (4), both the vessel body flange (11) and the end cover flange (15) are provided with the drill insertion hole.

3. The high-temperature and high-pressure mechanical property testing equipment for deep well drilling tools according to claim 2, characterized in that, The end cooling seal also includes a serpentine baffle (1601) and a nickel-titanium alloy wire (1602). Along the axial direction of the vessel body (4), the serpentine baffle (1601) is arranged in a serpentine shape between the vessel body flange (11) and the end cap flange (15) so that the three form a serpentine groove; the nickel-titanium alloy wire (1602) is disposed inside the serpentine groove; The serpentine baffle (1601) is located at one end of the stepped conical annular sealing strip (13) near the vessel body (4).

4. The high-temperature and high-pressure mechanical property testing equipment for deep well drilling tools according to claim 2, characterized in that, Spiral cooling channels (9) are correspondingly provided on the vessel flange (11) and / or the end cover flange (15); the inlet end and outlet end of the spiral cooling channel (9) are connected to the outer wall of the end cooling seal; The spiral cooling channel (9) has a built-in turbulence promoter (10).

5. The high-temperature and high-pressure mechanical property testing equipment for deep well drilling tools according to claim 2, characterized in that, Multiple retaining rings (14) are coaxially arranged on the inner wall of the vessel body (4); the inner wall of the vessel body (4) and a pair of adjacent retaining rings (14) form a pressure-sealed chamber; The retaining ring (14) includes a sealing ring (1401) and a foot-shaped slip ring (1402) arranged coaxially, and both are interference-fitted with the wall of the test drill (18) so that the inner ring of the retaining ring (14) is the insertion hole of the drill. The foot-shaped slip ring (1402) is coaxially connected to the inner wall of the vessel body (4), and the opening of the foot-shaped slip ring (1402) faces the axis of the vessel body (4); The sealing ring (1401) engages with the opening of the foot-shaped slip ring (1402).

6. The high-temperature and high-pressure mechanical property testing equipment for deep well drilling tools according to claim 5, characterized in that, The pair of sealing rings (1401) provided at both ends of the main pressure sealing chamber (401) are silicone rubber sealing rings; The sealing ring (1401) disposed between two adjacent auxiliary pressure sealing chambers (402) is a fluororubber sealing ring; The end sealing ring (12) and / or the stepped conical annular sealing strip (13) are nitrile rubber sealing rings.

7. The high-temperature and high-pressure mechanical property testing equipment for deep well drilling tools according to any one of claims 1-4, characterized in that, The heating mechanism (3) includes an oil bath heating cylinder coaxially sleeved on the vessel body (4); Along the axial direction of the vessel body (4), the inner cavity of the oil bath heating cylinder covers the main pressure sealing chamber (401).

8. The high-temperature and high-pressure mechanical property testing equipment for deep well drilling tools according to any one of claims 1-4, characterized in that, The high-temperature and high-pressure mechanical performance testing equipment for deep well drilling tools also includes a force loading mechanism (1); the force loading mechanism (1) includes a test bench, and an axial load loading mechanism, a torque loading mechanism and a clamping mechanism (2) disposed on the test bench. The vessel body (4) is vertically mounted on the platform; the gripper of the clamping mechanism (2) is positioned directly above the drill insertion hole; The output shaft of the axial load loading mechanism is coaxially positioned above the drill bit insertion hole; The output end of the torque loading mechanism is located above the drill insertion hole.

9. A test method for a high-temperature and high-pressure mechanical property testing device for deep well drilling tools, characterized in that, The test method for the high-temperature and high-pressure mechanical property testing equipment for deep well drilling tools is implemented based on the high-temperature and high-pressure mechanical property testing equipment for deep well drilling tools according to any one of claims 1-8, and the test method includes: The test drill bit (18) is inserted through the drill bit insertion channel; During the pressurization stage of the pressure sealing chamber, the pressurization is completed step by step through multiple pressure conveying pipes (7) from the auxiliary pressure sealing chamber (402) at the end of the vessel body (4) to the main pressure sealing chamber (401). During the depressurization phase of the pressure-sealed chamber, the path of step-by-step depressurization is the opposite of the path of step-by-step pressurization during the pressurization phase. The heating mechanism (3) is activated to heat the test drill (18) inside the vessel body (4); The mechanical properties of the test drill (18) were tested.

10. The test method for the high-temperature and high-pressure mechanical property testing equipment for deep well drilling tools according to claim 9, characterized in that, The high-temperature and high-pressure mechanical property testing equipment is set vertically, and its bottom part is buried in a pit.

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