Sensor with high pressure resistant capability

Abstract

The present application relates to the technical field of sensors, and specifically relates to a sensor with a high pressure resistant capability. The sensor with a high pressure resistant capability comprises a housing and a core, wherein the housing is provided with a first mounting port and a second mounting port, which are in communication with the interior of the housing, the first mounting port being configured to communicate with an outlet of a pressure vessel, the second mounting port being configured to mount the core therein, and the first mounting port and the second mounting port being respectively located at two opposite axial ends of the housing; and an inner wall of the housing is provided with an inner surface, an outer wall of the core is provided with an outer surface, and in a mounting state, the inner surface is in interference fit with the outer surface. By means of the above solution, the problem of damage to the core due to an overly-high welding temperature can be avoided, and the problem of limiting the connection strength between the housing and the core due to the limitation to the size of a welding spot can also be avoided.

Description

Sensors with high pressure resistance Technical Field

[0001] This application relates to the field of sensor technology, and more specifically, to a sensor with high pressure resistance. Background Technology

[0002] Existing sensors with high pressure resistance typically use welding to connect the core and the outer shell to achieve fixation and sealing between the core and the outer shell.

[0003] Laser welding or argon arc welding is typically used during welding. Energy is injected to melt adjacent metals together, and higher energy results in a larger weld zone and greater load-bearing capacity. However, the energy applied during welding also raises the core temperature. Excessive temperature can damage the seal formed by the glass and core material, causing it to lose electrical isolation and mechanical sealing. Furthermore, the limited size of the weld point and the welding method also restrict the connection strength between the outer shell and the core. Summary of the Invention

[0004] This application provides at least one sensor with high pressure resistance, which can avoid the problem of core damage caused by excessive welding temperature, and also avoid the problem of limiting the connection strength between the shell and the core due to the size of the welding point.

[0005] This application provides a sensor with high pressure resistance, including: a housing and a core. The housing is provided with a first mounting port and a second mounting port communicating with its interior. The first mounting port is used to communicate with the outlet of a pressure vessel, and the second mounting port is used to install the core. The first mounting port and the second mounting port are respectively located at opposite axial ends of the housing.

[0006] The inner wall of the outer shell has an inner surface, and the outer wall of the core has an outer surface. In the installed state, the inner surface and the outer surface are interference-fitted.

[0007] In one alternative embodiment, the inner surface includes a plurality of inner stepped surfaces, the outer surface includes an outer stepped surface, and at least one of the inner stepped surfaces and at least one of the outer stepped surfaces are interference-fitted.

[0008] In one alternative implementation, both the inner surface and the outer surface are conical surfaces.

[0009] In one alternative implementation, the inner conical surface and the outer conical surface have the same height.

[0010] In one alternative embodiment, the inner conical surface is located at one end of the housing near the second mounting port.

[0011] In one alternative embodiment, the housing is provided with a limiting surface for limiting the installation depth of the core.

[0012] In one alternative embodiment, a seal is formed between the outer casing and the core.

[0013] In one alternative embodiment, the outer shell and the core are sealed by welding.

[0014] In one alternative embodiment, the outer shell and the pressure vessel are an integral structure.

[0015] In one alternative embodiment, the end face of the core facing the pressure vessel is chamfered.

[0016] The above-mentioned technical solution of this application has the following beneficial technical effects:

[0017] The sensor with high compressive strength according to the present application embodiment is fixed between its shell and core by an interference fit, so that the shell and core are no longer fixed by welding. Therefore, during the assembly process, the problem of core damage caused by excessive welding temperature can be avoided. In addition, the problem of limiting the connection strength between the shell and core due to the size of the welding point can also be avoided, thereby improving the detection range of the sensor. Attached Figure Description

[0018] Figure 1 shows a schematic diagram of the structure of a sensor with high compressive strength provided in Embodiment 1 of this application;

[0019] Figure 2 shows an assembly diagram of a sensor with high compressive strength provided in Embodiment 1 of this application;

[0020] Figure 3 shows a top view of a sensor with high compressive strength provided in Embodiment 1 of this application;

[0021] Figure 4 shows a schematic diagram of the interference fit between the outer shell and the core provided in Embodiment 1 of this application;

[0022] Figure 5 shows a schematic diagram of another sensor with high compressive strength provided in Embodiment 1 of this application;

[0023] Figure 6 shows a schematic diagram of another sensor with high pressure resistance provided in Embodiment 1 of this application;

[0024] Figure 7 shows a schematic diagram of the outer shell and core provided in Embodiment 1 of this application;

[0025] Figure 8 shows a linear relationship between the interference friction force and the interference ratio provided in Embodiment 1 of this application;

[0026] Figure 9 shows a sensor without interference fit;

[0027] Figure 10 shows an interference fit sensor;

[0028] Figure 11 shows a schematic diagram of a sensor with high compressive strength provided in Embodiment 2 of this application;

[0029] Figure 12 shows an assembly diagram of a sensor with high compressive strength provided in Embodiment 2 of this application;

[0030] Figure 13 shows a top view of a sensor with high compressive strength provided in Embodiment 2 of this application;

[0031] Figure 14 shows a schematic diagram of the interference fit between the outer shell and the core provided in Embodiment 2 of this application;

[0032] Figure 15 shows a schematic diagram of another sensor with high compressive strength provided in Embodiment 2 of this application;

[0033] Figure 16 shows a schematic diagram of another sensor with high pressure resistance provided in Embodiment 2 of this application;

[0034] Figure 17 shows a schematic diagram of the outer shell and core provided in Embodiment 2 of this application;

[0035] Figure 18 shows a linear relationship between interference friction force and interference ratio provided in Embodiment 2 of this application;

[0036] Reference numerals: 10, outer shell; 11, first mounting port; 12, second mounting port; 13, inner surface; 14, limiting surface; 20, core; 21, outer surface; 22, chamfer; 30, sensitive element; 40, pin; 50, weld; 10', outer shell; 11', first mounting port; 12', second mounting port; 13', inner surface; 14', limiting surface; 20', core; 21', outer surface; 22', chamfer; 30', sensitive element; 40', pin; 50', weld. Embodiments of the present invention

[0037] Example 1

[0038] This application provides a sensor with high compressive strength, wherein the outer shell and the core of the sensor are fixed by an interference fit.

[0039] As shown in Figures 1 and 2, the sensor with high pressure resistance provided in this embodiment includes a housing 10 and a core 20. The housing 10 is provided with a first mounting port 11 and a second mounting port 12 communicating with its interior. The first mounting port 11 is used to connect to the outlet of a pressure vessel, and the second mounting port 12 is used to mount the core 20. The first mounting port 11 and the second mounting port 12 are located at opposite axial ends of the housing 10. The inner wall of the housing 10 is provided with an inner surface 13, and the outer wall of the core 20 is provided with an outer surface 21. In the installed state, the inner surface 13 and the outer surface 21 are interference-fitted.

[0040] According to the sensor described above, the outer shell 10 and the core 20 are fixed together by an interference fit, so that the outer shell 10 and the core 20 no longer rely on welding for fixation. Therefore, during the assembly process, the problem of damage to the core 20 due to excessive welding temperature can be avoided. In addition, the problem of limiting the connection strength between the outer shell 10 and the core 20 due to the size of the welding point can also be avoided, which is conducive to improving the detection range of the sensor.

[0041] It should be noted that the core 20 is typically a glass sintered base, and a sensing element 30 and pins 40 connected to the sensing element 30 are disposed on the core 20. For example, as shown in Figures 1 and 2, the sensing element 30 is located at the end of the core 20 facing the pressure vessel, and the pins 40 pass through the core 20 and are connected to the sensing element 30. In practical use, the sensing element 30 detects the measured parameters of the pressure vessel, such as pressure, temperature, and gas concentration, and transmits the data to a data processor or computer via the pins 40.

[0042] Optionally, in this embodiment, the inner surface 13 includes a plurality of inner stepped surfaces, and the outer surface 21 includes an outer stepped surface. At least one inner stepped surface and at least one outer stepped surface are interference-fitted.

[0043] Optionally, in this embodiment, there is an interference friction between the outer shell 10 and the core 20, and the interference friction is greater than the thrust experienced by the core 20 during detection. This prevents the core 20 from detaching from the outer shell 10 during detection, thus avoiding sensor failure.

[0044] It should be understood that, in specific settings, the interference friction between the outer shell 10 and the core 20 is related to the amount of interference between the two. The greater the amount of interference, the greater the interference friction between the outer shell 10 and the core 20.

[0045] Optionally, in this embodiment, the outer shell 10 is provided with a limiting surface 14, which is used to limit the installation depth of the core 20. Specifically, the limiting surface 14 can limit the core 20, and when the limiting surface 14 limits the core 20, the inner surface 13 and the outer surface 21 are in an interference fit position. This prevents the core 20 from affecting the interference fit between the inner surface 13 and the outer surface 21 due to excessive or insufficient installation depth.

[0046] Yes, the housing 10 may have a limiting surface 14 inside, as shown in Figures 1 and 5. Specifically, the limiting surface 14 may be a stepped surface formed on the inner wall of the housing 10.

[0047] Alternatively, a limiting surface 14 is provided on the end face of the housing 10, as shown in Figures 5 and 6. Specifically, the limiting surface 14 can be the end face of the housing 10 near the second mounting port 12.

[0048] Optionally, in this embodiment, a seal can be formed between the outer shell 10 and the core 20. This avoids gaps between the interference surfaces from affecting the airtightness, which helps improve the reliability of the sensor.

[0049] Yes, the outer shell 10 and the core 20 can be sealed by welding. Specifically, the gap between the core 20 and the outer shell 10 is welded circumferentially, as shown in Figure 3. This not only improves the airtightness between the core 20 and the outer shell 10, but also allows for two connection methods: welding and interference fit. Compared to a single connection method, this arrangement, while maintaining the same connection strength, allows for a suitable reduction in the interference fit between the core 20 and the outer shell 10, avoiding design failure due to excessive plastic deformation. It also allows for a suitable reduction in the size of the welding point, thereby reducing the temperature rise caused by energy injection during welding and lowering the risk of damage to the core 20.

[0050] It should be understood that, depending on the different construction of the core 20, the weld 50 between the core 20 and the outer shell 10 can be located on the end face or side face of both, as shown in Figures 1, 5 and 6.

[0051] Optionally, in this embodiment, the outer shell 10 is a tubular structure.

[0052] Optionally, in this embodiment, the outer casing 10 is disposed on the pressure vessel and connected and fixed to the pressure vessel.

[0053] Yes, the housing 10 can be connected to the pressure vessel via an adapter. Specifically, the housing 10 and the pressure vessel are connected in a detachable manner. This facilitates the installation and removal of the sensor.

[0054] Alternatively, the outer shell 10 and the pressure vessel can be integrated into a single structure. In this embodiment, it is preferable to have the outer shell 10 and the pressure vessel integrated into a single structure. This improves the connection strength between the outer shell 10 and the pressure vessel.

[0055] Optionally, in this embodiment, the end face of the core 20 facing the pressure vessel is provided with a chamfer 22. For example, as shown in FIG2, the edge of the end face between the first stepped surface and the second stepped surface of the core 20 is provided with a chamfer 22. The chamfer 22 can play a guiding and positioning role during assembly, making it easier to install the core 20 into the outer shell 10.

[0056] This application provides a packaging method for a sensor with high pressure resistance, used to prepare a sensor with high pressure resistance according to the first aspect.

[0057] The packaging method for a sensor with high pressure resistance provided in this application includes:

[0058] S100. A housing 10 and a core 20 are provided. The housing 10 is provided with a first mounting port 11 and a second mounting port 12 communicating with its interior. The first mounting port 11 is used to communicate with the outlet of the pressure vessel, and the second mounting port 12 is used to install the core 20. The inner wall of the housing 10 is provided with an inner surface 13, and the outer wall of the core 20 is provided with an outer surface 21. The diameter of the outer surface 21 is larger than the diameter of the inner surface 13, as shown in Figure 2.

[0059] S200. Install the core 20 inside the outer casing 10 so that the outer surface 21 and the inner surface 13 achieve an interference fit, as shown in Figure 1.

[0060] The sensor prepared according to the above method is fixed and sealed between the outer shell 10 and the core 20 by an interference fit, so that the outer shell 10 and the core 20 no longer rely on welding for fixing and sealing. Therefore, during the assembly process, the problem of damage to the core 20 due to excessive welding temperature can be avoided. In addition, the problem of limiting the connection strength between the outer shell 10 and the core 20 due to the size of the welding point can also be avoided, which is conducive to improving the detection range of the sensor.

[0061] It should be noted that the core 20 is typically a glass sintered base, and a sensing element 30 and pins 40 connected to the sensing element 30 are disposed on the core 20. For example, as shown in Figures 1 and 2, the sensing element 30 is located at the end of the core 20 facing the pressure vessel, and the pins 40 pass through the core 20 and are connected to the sensing element 30. In practical use, the sensing element 30 detects the measured parameters of the pressure vessel, such as pressure, temperature, and gas concentration, and transmits the data to a data processor or computer via the pins 40.

[0062] Optionally, in this embodiment, in order to install the core 20 inside the outer casing 10, the outer casing 10 can be heated to expand it before installation. Specifically, the method includes: heating the outer casing 10 to expand it until the diameter of the inner surface 13 is greater than the diameter of the outer surface 21; installing the core 20 inside the outer casing 10; and restoring the outer casing 10 to room temperature so that the outer surface 21 and the inner surface 13 achieve an interference fit.

[0063] Optionally, in this embodiment, in order to install the core 20 inside the outer casing 10, the core 20 can be frozen to shrink it before installation. Specifically, the method includes: cooling the core 20 to shrink it until the diameter of the outer surface 21 is smaller than the diameter of the inner surface 13; installing the core 20 inside the outer casing 10; and restoring the core 20 to room temperature so that the outer surface 21 and the inner surface 13 achieve an interference fit.

[0064] Alternatively, in this embodiment, in order to install the core 20 inside the housing 10, the core 20 can also be pressed into the housing 10 by means of external force.

[0065] Optionally, in this embodiment, after the core 20 is installed inside the housing 10, the gap between the core 20 and the housing 10 can be sealed. This avoids the airtightness being affected by gaps between the interference surfaces, which helps to improve the reliability of the sensor.

[0066] Yes, the gap between the core 20 and the outer shell 10 can be sealed, specifically by welding. Specifically, the gap between the core 20 and the outer shell 10 is welded circumferentially, as shown in Figure 3. This not only improves the airtightness between the core 20 and the outer shell 10 but also allows for two connection methods: welding and interference fit. Compared to a single connection method, this arrangement, while maintaining the same connection strength, allows for a reduction in the interference fit between the core 20 and the outer shell 10, preventing design failure due to excessive plastic deformation. It also allows for a reduction in the size of the welding point, thereby reducing the temperature rise caused by energy injection during welding and lowering the risk of damage to the core 20.

[0067] It should be understood that, depending on the different construction of the core 20, the weld 50 between the core 20 and the outer shell 10 can be located on the end face or side face of both, as shown in Figures 1, 5 and 6.

[0068] The feasibility of the sensor in the embodiments of this application will be verified below.

[0069] For ease of demonstration, we assume that the average internal compressive stress caused by the interference fit is: The radius of the contact surface is The height of the internal compressive stress region is The coefficient of friction between metals is The pressure of the pressure vessel is The pressure vessel then exerts a thrust on the core. and maximum friction As follows;

[0070] Eq. 1

[0071] Eq. 2

[0072] With reasonable design parameters, and if there is sufficient internal stress and contact area, friction force... It can fully handle the entire load. However, welding is not required. In reality, because the surfaces of the core and shell have varying degrees of irregularity, there is a risk of gas or liquid leakage. Therefore, welding is still necessary to seal one end of the interference fit to cut off possible leakage paths. This can be any of the welding methods shown in Figures 1, 5, and 6. It is also conceivable that in special cases, if the gap created by the interference fit is small enough, welding sealing becomes unnecessary, such as when the medium inside the pressure vessel is highly viscous or a liquid-solid mixture. These situations do not affect the effectiveness of the invention. In the case of welding, because the core and shell undergo elastic deformation under the pressure of the pressure vessel, this deformation will create a certain stress load on the welded part. Obviously, under the same conditions, the interference fit can significantly reduce the thrust that the weld point needs to withstand. This allows the weld point size to be very small, thereby reducing the temperature rise caused by energy injection during welding and effectively protecting the glass sintering core.

[0073] It is important to note that welding operations may affect the internal compressive stress generated by the pre-weld interference fit. It is conceivable that when the metal temperature near the weld fusion zone rises to near melting point, the pre-existing internal compressive stress will far exceed the local yield strength at that temperature, thus causing plastic deformation. After the temperature returns to normal, the previously existing interference internal stress is affected. Therefore, there will be a certain transition between the welded area and the effective interference fit area. Subsequent analysis assumes that the effective interference contact area does not include the weld fusion zone. This is a detail of the design analysis and implementation and will not be elaborated here, nor does it affect the effectiveness of the invention.

[0074] Effective design requires defining the parameters included in Eq 1 and Eq 2, and considering the transition region as described above. This process includes theoretical analysis and experimental verification.

[0075] Using modern finite element analysis (FEA) simulation tools, mechanical design parameters and geometric optimization can be performed through simulation modeling to calculate the required interference fit (dimensions) to achieve frictional force. It is important to note that the internal compressive stress caused by the interference fit should not exceed the material's yield strength within the operating temperature range, and a certain safety factor must be maintained. If the internal stress caused by the interference fit exceeds the material's yield strength, the core and shell will undergo plastic deformation. After plastic deformation, the material will not return to its initial state, thus reducing the interference fit and weakening the magnitude of the internal stress caused by the interference. Excessive plastic deformation can lead to design failure.

[0076] Below, we will demonstrate the selection of design parameters using a classic and elegant calculation formula. It should be emphasized that this is a demonstration with strong idealized assumptions. The purpose is to illustrate the logic. Therefore, the effectiveness of this invention is not limited by the idealization of the following analysis or the selection of parameters.

[0077] For simplicity, we assume that the core and outer shell are sufficiently long cylinders, thus ignoring the effect of length. As shown in Figure 7, we define the following parameters associated with Figure 7:

[0078] Inner diameter of the outer casing

[0079] Inner diameter after shell assembly

[0080] Outer diameter of the outer shell

[0081] Outer diameter after shell assembly

[0082] Core outer diameter

[0083] Young's modulus

[0084] Poisson's ratio

[0085] Internal pressure stress caused by interference fit

[0086] : Interference fit amount of inner diameter

[0087] coefficient of friction

[0088] Because the inner cylindrical core is subjected to uniform force under pure water pressure with zero bias, it remains undeformed in this idealized scenario (in actual applications, the core will deform due to the influence of length. Therefore, this analysis is for demonstration purposes and does not affect the validity of the patent).

[0089] The inner diameter of the outer cylindrical shell before assembly is: Smaller than the outer diameter of the core Because of the outer diameter of the core Under this ideal condition, it remains unchanged, and the inner diameter of the assembled outer shell is... The interference fit produced by this mechanical assembly is:

[0090]

[0091] Based on the parameters defined above, the changes in the inner and outer diameters of the outer cylindrical shell after interference fit are related to the compressive stress generated at the contact surface as follows (these calculation formulas are from Roark's Formulas of Stress and Strain by Warren C. Young):

[0092]

[0093]

[0094] Let's further calculate an instance, assuming the following parameters...

[0095] : variables, and Related

[0096] 20 mm

[0097] 20 mm

[0098] 200 MPa

[0099] : 0.3

[0100] : variables, and Related

[0101] : Inner diameter interference fit amount, and Related

[0102] : 0.4

[0103] 20 MPa (pressure vessel pressure)

[0104] Using the above relationships, we derive the friction force and interference ratio. The relationship is shown in Figure 8.

[0105] In this example, the pressure vessel exerts a thrust of approximately 8000 Newtons on the core. If this thrust is supported by interference friction, a specific interference ratio is required. Approximately 0.03 mm, which translates to an interference fit of 0.6 mm. This is a demonstration; in practical applications, finite element analysis (FEA) would be more accurate.

[0106] The effectiveness of this invention has been experimentally verified. Figure 9 shows a design without an interference fit. This design failed after six overload pressure tests, with the failure point being a weld contact fracture. Figure 10 shows a design utilizing an interference fit, with all other parameters identical to the left side, but using an interference fit of 0.03 mm. This design withstood 15 million overload pressure tests and remained intact, maintaining its original design state, proving the effectiveness of the invention.

[0107] For the sake of simplicity, the core of this example (shown in Figure 7) is an all-metal part, excluding the glass, pins, etc. of the glass-sintered core, which does not affect the effectiveness of the invention.

[0108] Example 2

[0109] This application provides a sensor with high pressure resistance. Unlike embodiment 1, the inner surface of the outer shell and the outer surface of the core in this embodiment are both conical surfaces.

[0110] Specifically, as shown in Figures 11 and 12, the sensor with high pressure resistance provided in this embodiment includes a housing 10' and a core 20'. The housing 10' is provided with a first mounting port 11' and a second mounting port 12' communicating with its interior. The first mounting port 11' is used to connect to the outlet of a pressure vessel, and the second mounting port 12' is used to mount the core 20'. The first mounting port 11' and the second mounting port 12' are located at opposite axial ends of the housing 10'. The inner wall of the housing 10' is provided with an inner conical surface 13', and the outer wall of the core 20' is provided with an outer conical surface 21'. In the installed state, the inner conical surface 13' and the outer conical surface 21' are interference-fitted.

[0111] According to the sensor described above, the outer shell 10' and the core 20' are fixed together by an interference fit, so that the outer shell 10' and the core 20' no longer rely on welding for fixation. Therefore, during the assembly process, the problem of damage to the core 20' due to excessive welding temperature can be avoided. In addition, the problem of limiting the connection strength between the outer shell 10' and the core 20' due to the size of the welding point can also be avoided, which is conducive to improving the detection range of the sensor.

[0112] In addition, since the interference fit surfaces of the outer shell 10' and the core 20' are both conical, the conical surfaces can play a guiding and positioning role during the process of installing the core 20' into the outer shell 10', thus making the process of installing the core 20' into the outer shell 10' more convenient.

[0113] It should be noted that the core 20' is typically a glass sintered base, and a sensing element 30' and pins 40' connected to the sensing element 30' are mounted on the core 20'. For example, as shown in Figures 1 and 2, the sensing element 30' is located at the end of the core 20' facing the pressure vessel, and the pins 40' pass through the core 20' and connect to the sensing element 30'. In practical use, the sensing element 30' detects the measured parameters of the pressure vessel, such as pressure, temperature, and gas concentration, and transmits this data to a data processor or computer via the pins 40'.

[0114] Optionally, in this embodiment, the inner conical surface 13' and the outer conical surface 21' have the same height.

[0115] Optionally, in this embodiment, the inner conical surface 13' may be part of the inner wall of the outer casing 10'. For example, the inner wall of the outer casing 10' may sequentially include a plurality of inner stepped surfaces from the second mounting opening 12' to the first mounting opening 11', and one of the plurality of inner stepped surfaces may be the inner conical surface 13'. In this embodiment, the inner conical surface 13' is preferably located at the end of the outer casing 10' near the second mounting opening 12'.

[0116] Optionally, in this embodiment, the outer conical surface 21' may be a portion of the outer wall of the core 20'. For example, the outer wall of the core 20' may sequentially include multiple outer stepped surfaces from the second mounting port 12' to the first mounting port 11', and one of the multiple outer stepped surfaces may be the outer conical surface 21'. In this embodiment, it is preferable to set the first outer stepped surface as the outer conical surface 21', that is, the outer conical surface 21' is located at the end of the core 20' near the second mounting port 12'.

[0117] Optionally, in this embodiment, the outer shell 10' is provided with a limiting surface 14', which is used to limit the installation depth of the core 20'. Specifically, the limiting surface 14' can limit the core 20', and when the limiting surface 14' limits the core 20', the inner and outer surfaces are in an interference fit position. This prevents the interference fit between the inner and outer surfaces from being affected by excessive or insufficient installation depth.

[0118] Yes, the limiting surface 14' can be located inside the outer shell 10', as shown in Figure 11. Specifically, the limiting surface 14' can be a stepped surface formed by the inner wall of the outer shell 10'.

[0119] Alternatively, the limiting surface 14' is located on the end face of the housing 10', as shown in Figures 15 and 16. Specifically, the limiting surface 14' can be the end face of the housing 10' near the second mounting port 12'.

[0120] This application also provides a method for packaging a sensor with high pressure resistance, the method comprising:

[0121] S100. A housing 10' and a core 20' are provided. The housing 10' is provided with a first mounting port 11' and a second mounting port 12' that communicate with its interior. The first mounting port 11' is used to communicate with the outlet of the pressure vessel, and the second mounting port 12' is used to install the core 20'. The inner wall of the housing 10' is provided with an inner conical surface 13', and the outer wall of the core 20' is provided with an outer conical surface 21'. The tapers of the outer conical surface 21' and the inner conical surface 13' are equal, as shown in Figure 12.

[0122] S200. Install the core 20' inside the outer shell 10' so that the outer conical surface 21' and the inner conical surface 13' achieve an interference fit, as shown in Figure 11.

[0123] The sensor prepared according to the above method is fixed between its outer shell 10' and core 20' by an interference fit, so that the outer shell 10' and core 20' no longer rely on welding for fixation. Therefore, during the assembly process, the problem of damage to the core 20' due to excessive welding temperature can be avoided. In addition, the problem of limiting the connection strength between the outer shell 10' and core 20' due to the size of the welding point can also be avoided, which is conducive to improving the detection range of the sensor.

[0124] In addition, since the interference fit surfaces of the outer shell 10' and the core 20' are both conical, the conical surfaces can play a guiding and positioning role during the process of installing the core 20' into the outer shell 10', thus making the process of installing the core 20' into the outer shell 10' more convenient.

[0125] Optionally, in this embodiment, in order to install the core 20' inside the outer casing 10', the outer casing 10' can be heated to expand it before installation. Specifically, the method includes: heating the outer casing 10' to expand it until the diameter of the inner conical surface 13' is greater than the diameter of the outer conical surface 21'; installing the core 20' inside the outer casing 10'; and restoring the outer casing 10' to room temperature, so that the outer conical surface 21' and the inner conical surface 13' achieve an interference fit.

[0126] Optionally, in this embodiment, in order to install the core 20' inside the outer casing 10', the core 20' can be frozen to shrink it before installation. Specifically, the method includes: cooling the core 20' to shrink it until the diameter of the outer conical surface 21' is smaller than the diameter of the inner conical surface 13'; installing the core 20' inside the outer casing 10'; and restoring the core 20' to room temperature so that the outer conical surface 21' and the inner conical surface 13' achieve an interference fit.

[0127] Alternatively, in this embodiment, in order to install the core 20' inside the outer casing 10', the core 20' can also be pressed into the outer casing 10' by means of external force.

[0128] Optionally, in this embodiment, after the core 20' is installed inside the housing 10', the gap between the core 20' and the housing 10' can be sealed. This avoids the airtightness being affected by gaps between the interference surfaces, which helps improve the reliability of the sensor.

[0129] Yes, the gap between the core 20' and the outer shell 10' can be sealed, specifically by welding. Specifically, the gap between the core 20' and the outer shell 10' is welded circumferentially, as shown in Figure 13. This not only improves the airtightness between the core 20' and the outer shell 10' but also allows for two connection methods: welding and interference fit. Compared to a single connection method, this arrangement, while maintaining the same connection strength, allows for a reduction in the interference fit between the core 20' and the outer shell 10', preventing design failure due to excessive plastic deformation. It also allows for a reduction in the size of the welding point, thereby reducing the temperature rise caused by energy injection during welding and lowering the risk of damage to the core 20'.

[0130] It should be understood that, depending on the different construction of the core 20', the weld 50' between the core 20' and the outer shell 10' can be located on the end face or side face of both, as shown in Figures 11, 15 and 16.

[0131] The feasibility of the sensor in the embodiments of this application will be verified below.

[0132] For ease of demonstration, we assume that the average internal compressive stress caused by the interference fit is: The radius of the contact surfaces at both ends of the cone is and The height of the internal compressive stress region is h, and the coefficient of friction between the metals is... The container pressure is The angle of the cone is then... The lateral surface area of ​​the cone is A, and the thrust exerted by the container on the core is... and maximum friction As follows;

[0133] Eq. 1

[0134] Eq. 2

[0135] Eq. 3

[0136] With reasonable design parameters, and if there is sufficient internal stress and contact area, friction force... It can fully handle the entire load. However, welding is not required. In reality, because the surfaces of the core and shell have varying degrees of irregularity, there is a risk of gas or liquid leakage. Therefore, welding is still necessary to seal one end of the interference fit to cut off possible leakage paths. This can be any welding method shown in Figure 2. It is also conceivable that in special cases, if the gap created by the interference fit is small enough, welding sealing becomes unnecessary, such as when the medium inside the container is highly viscous or a liquid-solid mixture. These situations do not affect the effectiveness of the invention. In the case of welding, because the core and shell undergo elastic deformation under container pressure, this deformation will create a certain stress load on the welded part. Obviously, under the same conditions, the interference fit can significantly reduce the thrust that the weld point needs to withstand. This allows the weld point size to be very small, thereby reducing the temperature rise caused by energy injection during welding and effectively protecting the glass sintering core.

[0137] It is important to note that welding operations may affect the internal compressive stress generated by the pre-weld interference fit. It is conceivable that when the metal temperature near the weld fusion zone rises to near melting point, the pre-existing internal compressive stress will far exceed the local yield strength at that temperature, thus causing plastic deformation. After the temperature returns to normal, the previously existing interference internal stress is affected. Therefore, there will be a certain transition between the welded area and the effective interference fit area. Subsequent analysis assumes that the effective interference contact area does not include the weld fusion zone. This is a detail of the design analysis and implementation and will not be elaborated here, nor does it affect the effectiveness of the invention.

[0138] Effective design requires defining the parameters included in Eq 1, Eq 2, and Eq 3, and considering the transition region as described above. This process includes theoretical analysis and experimental verification.

[0139] Using modern finite element analysis (FEA) simulation tools, mechanical design parameters and geometric optimization can be performed through simulation modeling to calculate the required interference fit (dimensions) to achieve frictional force. It is important to note that the internal compressive stress caused by the interference fit should not exceed the material's yield strength within the operating temperature range, and a certain safety factor must be maintained. If the internal stress caused by the interference fit exceeds the material's yield strength, the core and shell will undergo plastic deformation. After plastic deformation, the material will not return to its initial state, thus reducing the interference fit and weakening the magnitude of the internal stress caused by the interference. Excessive plastic deformation can lead to design failure.

[0140] Below, we will demonstrate the selection of design parameters using a classic and elegant calculation formula. It should be emphasized that this is a demonstration with strong idealized assumptions. The purpose is to illustrate the logic. Therefore, the effectiveness of this invention is not limited by the idealization of the following analysis or the selection of parameters.

[0141] For simplicity, we assume that the core and outer shell are sufficiently long cylinders, thus neglecting the effect of length. In this analysis, we also ignore the effect of the cone angle on stress. As shown in Figure 17, we define the following parameters associated with Figure 17:

[0142] Inner diameter of the outer casing

[0143] Inner diameter after shell assembly

[0144] Outer diameter of the outer shell

[0145] Outer diameter after shell assembly

[0146] Core outer diameter

[0147] Young's modulus

[0148] Poisson's ratio

[0149] Internal pressure stress caused by interference fit

[0150] : Interference fit amount of inner diameter

[0151] coefficient of friction

[0152] Because the inner cylindrical core is subjected to uniform force under pure water pressure with zero bias, it remains undeformed in this idealized scenario (in actual applications, the core will deform due to the influence of length. Therefore, this analysis is for demonstration purposes and does not affect the validity of the patent).

[0153] The inner diameter of the outer cylindrical shell before assembly is: Smaller than the outer diameter of the core Because of the outer diameter of the core Under this ideal condition, it remains unchanged, and the inner diameter of the assembled outer shell is... The interference fit produced by this mechanical assembly is:

[0154]

[0155] Based on the parameters defined above, the changes in the inner and outer diameters of the outer cylindrical shell after interference fit are related to the compressive stress generated at the contact surface as follows (these calculation formulas are from Roark's Formulas of Stress and Strain by Warren C. Young):

[0156]

[0157]

[0158] Let's further calculate an instance, assuming the following parameters...

[0159] : variables, and Related

[0160] 20 mm

[0161] 20 mm

[0162] 200 MPa

[0163] : 0.3

[0164] : variables, and Related

[0165] : Inner diameter interference fit amount, and Related

[0166] : 0.4

[0167] 20 MPa (container pressure)

[0168] Using the above relationships, we derive the friction force and interference ratio. The relationship is shown in Figure 18.

[0169] In this example, the container exerts a thrust of approximately 8000 Newtons on the core. If this thrust is supported by interference friction, a certain interference ratio is required. Approximately 0.03 mm, which translates to an interference fit of 0.6 mm. This is a demonstration; in practical applications, finite element analysis (FEA) would be more accurate.

[0170] When selecting the cone angle, the "friction self-locking" phenomenon must be considered. If the cone angle is too large, the internal stress caused by the interference fit will overcome the friction of the contact surface, causing the core to pop out on its own. As shown in Figure 17, if the total internal stress is... Then the following relationship holds.

[0171]

[0172] Its radial and axial components are,

[0173]

[0174]

[0175] The frictional force along the direction of the cone surface is

[0176]

[0177] Its radial and axial components are,

[0178]

[0179]

[0180] To prevent the core from ejecting on its own, the component of the total internal stress in the axial direction... It needs to be less than the component of friction in the axial direction. ,

[0181]

[0182]

[0183] This leads to the conclusion that...

[0184]

[0185] Assuming friction coefficient The cone angle needs to be less than 21.8°. In practical applications, this angle can be much smaller than this critical value. Using the example above, if the average core diameter is 20 mm and the cone height is 5 mm, for ease of assembly, a diameter difference of 0.5 mm between the two ends of the cone, resulting in a cone angle of 5.7°, can be achieved. This is far less than the critical value required for a friction coefficient of 0.4. If the friction coefficient changes, the critical value will change accordingly.

[0186] One or more embodiments in this specification are intended to cover all such substitutions, modifications, and variations that fall within the broad scope of the appended claims. Therefore, any omissions, modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of one or more embodiments in this specification should be included within the protection scope of this application.

[0187] The above are merely specific embodiments of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the scope of the technology disclosed in this application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. A sensor with high compressive strength, characterized in that, include: The outer shell and the core are provided. The outer shell is provided with a first mounting port and a second mounting port that communicate with its interior. The first mounting port is used to communicate with the outlet of the pressure vessel, and the second mounting port is used to install the core. The first mounting port and the second mounting port are respectively located at opposite ends of the axial direction of the outer shell. The inner wall of the outer shell has an inner surface, and the outer wall of the core has an outer surface. In the installed state, the inner surface and the outer surface are interference-fitted.

2. The sensor with high compressive strength according to claim 1, characterized in that, The inner surface includes multiple inner stepped surfaces, and the outer surface includes an outer stepped surface, with at least one inner stepped surface and at least one outer stepped surface in an interference fit.

3. The sensor with high compressive strength according to claim 1, characterized in that, Both the inner and outer surfaces are conical.

4. The sensor with high compressive strength according to claim 3, characterized in that, The inner conical surface and the outer conical surface have the same height.

5. The sensor with high compressive strength according to claim 3, characterized in that, The inner conical surface is located at one end of the outer casing near the second mounting port.

6. The sensor with high compressive strength according to claim 1, characterized in that, The outer shell is provided with a limiting surface, which is used to limit the installation depth of the core.

7. The sensor with high compressive strength according to claim 1, characterized in that, A seal is formed between the outer shell and the core.

8. The sensor with high compressive strength according to claim 7, characterized in that, The outer shell and the core are sealed by welding.

9. The sensor with high compressive strength according to claim 1, characterized in that, The outer shell and the pressure vessel are an integral structure.

10. The sensor with high compressive strength according to claim 1, characterized in that, The end face of the core facing the pressure vessel is chamfered.

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