Method and apparatus for determining temperature of sucker rod heat pipe, electronic device, storage medium, and program product

Abstract

Embodiments of the present application relate to the technical field of petroleum exploitation devices, and provide a method and apparatus for determining the temperature of a sucker rod heat pipe, an electronic device, a storage medium, and a program product. The method comprises: acquiring attribute data of a sucker rod heat pipe in a target wellbore, and determining a heat exchange coefficient in the sucker rod heat pipe on the basis of the attribute data; on the basis of the heat exchange coefficient in the sucker rod heat pipe, calculating a total thermal resistance of the process of heat transfer from a heat absorption section of the sucker rod heat pipe to a wellhead of the target wellbore; on the basis of the total thermal resistance, determining a heat transfer rate of the sucker rod heat pipe; determining saturation temperature distribution sequence data in the sucker rod heat pipe; and on the basis of the saturation temperature distribution sequence data, the heat transfer rate and the heat exchange coefficient, determining temperature distribution sequence data corresponding to a pipe wall of the sucker rod heat pipe. In the present application, by acquiring the temperature distribution sequence data in the sucker rod heat pipe, the temperature change of an oil pipe in the wellbore can be effectively adjusted, so as to prevent paraffin deposition of crude oil near the wellhead.

Description

Methods, apparatus, electronic equipment, storage media, and program products for determining the temperature of sucker rod heat pipes.

[0001] This application claims priority to Chinese Patent Application No. 202411853766.4, filed on December 16, 2024, entitled “Temperature Determination Method, Apparatus, Electronic Equipment, Storage Medium and Program Product of Sucker Rod Heat Pipe”, the entire contents of which are incorporated herein by reference. Technical Field

[0002] This application relates to the field of oil extraction technology, and in particular to a method, apparatus, electronic device, storage medium, and program product for determining the temperature of a sucker rod heat pipe. Background Technology

[0003] During the process of produced fluid flowing from the bottom of the well to the wellhead in an oil production well, the flow resistance increases sharply due to factors such as high crude oil viscosity or wax deposition, which makes the crude oil less fluid. Near the wellhead, phenomena such as pumping unit overload and blockage often occur, thus affecting the normal production of the oil well.

[0004] The simplest and most feasible process is to heat the fluid inside the wellbore. The sucker rod heat pipe wellbore heating technology mainly uses the heat transfer technology based on the sucker rod heat pipe principle to heat the tubing in the wellbore to prevent the crude oil near the wellhead from waxing.

[0005] However, there are currently few methods for calculating the temperature distribution inside the heat pipe of the sucker rod, and the calculation accuracy is low. Therefore, it is difficult to accurately adjust the temperature change inside the tubing according to its own temperature distribution, and thus it is impossible to effectively improve the phenomenon of crude oil waxing near the wellhead. Summary of the Invention

[0006] This application provides a method, apparatus, electronic device, storage medium, and program product for determining the temperature of a sucker rod heat pipe, in order to solve the problem that it is difficult to accurately adjust the temperature change inside the tubing according to its own temperature distribution, thereby failing to effectively improve the phenomenon of crude oil wax deposition near the wellhead.

[0007] In a first aspect, embodiments of this application provide a data method, the method comprising:

[0008] Obtain the attribute data of the sucker rod heat pipe in the target wellbore, and determine the heat transfer coefficient inside the sucker rod heat pipe based on the attribute data;

[0009] Calculate the total thermal resistance of the process from the heat absorption section to the wellhead of the target wellbore in the sucker rod heat pipe based on the heat transfer coefficient in the sucker rod heat pipe.

[0010] Based on the total thermal resistance, the heat transfer rate of the sucker rod heat pipe is determined;

[0011] Determine the saturation temperature distribution sequence data inside the sucker rod heat pipe;

[0012] The temperature distribution sequence data corresponding to the heat pipe wall of the sucker rod is determined based on the saturated temperature distribution sequence data, the heat transfer rate, and the heat transfer coefficient.

[0013] In one possible design, the heat transfer coefficient within the sucker rod heat pipe includes the heat transfer coefficient of the heating section; the attribute data includes first attribute data;

[0014] Determining the heat transfer coefficient within the sucker rod heat pipe based on the attribute data includes:

[0015] Obtain the first pressure distribution sequence data within the liquid pool of the sucker rod heat pipe;

[0016] The heat transfer coefficient of the heating section is determined based on the ratio coefficient of the first attribute data, the first pressure distribution sequence data, and atmospheric pressure.

[0017] In one possible design, the first attribute data includes: the specific heat capacity, thermal conductivity, latent heat of vaporization, dynamic viscosity, density of the medium in the sucker rod heat pipe, and the radial heat flux density of the evaporation section corresponding to the heating section;

[0018] The heat transfer coefficient of the heating section is expressed as follows:

[0019] Among them, h e ρ is the heat transfer coefficient of the heating section of the sucker rod heat pipe; l ρ is the density of the liquid. v Where is the density of the steam; g is the acceleration due to gravity; C pl q represents the specific heat capacity of the liquid. e h is the radial heat flux density of the evaporation section. fg p represents the latent heat of vaporization of the liquid; p represents the first pressure distribution sequence data; p a Atmospheric pressure; λ l u is the thermal conductivity of the liquid. l The liquid is the dynamic viscosity of the liquid; the liquid is the medium in the heating section of the sucker rod heat pipe, and the vapor is the medium in the evaporation section corresponding to the heating section of the sucker rod heat pipe.

[0020] In one possible design, the heat transfer coefficient within the sucker rod heat pipe includes the heat transfer coefficient of the convection section;

[0021] The attribute data includes first attribute data and second attribute data, wherein the second attribute data includes the radial heat flux density of the evaporation section corresponding to the convection section and the height of the liquid pool inside the sucker rod heat pipe;

[0022] Determining the heat transfer coefficient within the sucker rod heat pipe based on the attribute data includes:

[0023] The radial heat flux density of the evaporation section corresponding to the convection section is compared with the critical heat flux density;

[0024] In response to the radial heat flux density of the evaporation section corresponding to the convection section being less than the critical heat flux density, the second pressure distribution sequence data corresponding to the convection section of the sucker rod heat pipe is obtained; the heat transfer coefficient of the convection section is determined based on the ratio coefficient of the first attribute data, the second pressure distribution sequence data and atmospheric pressure.

[0025] In response to the radial heat flux density of the evaporation section corresponding to the convection section being greater than or equal to the critical heat flux density, the first Reynolds number of the liquid film flow in the evaporation section of the convection section is calculated, and the heat transfer coefficient of the convection section is determined based on the first Reynolds number and the height of the liquid pool in the sucker rod heat pipe.

[0026] In one possible design, the first Reynolds number is expressed as follows:

[0027] Among them, Re f L represents the first Reynolds number; p L is the liquid pool height of the sucker rod heat pipe; f h is the length of the liquid film in the liquid film evaporation section. fg The latent heat of vaporization of the liquid; u l q represents the dynamic viscosity of the liquid. e The radial heat flux density is the evaporation section of the convection section; the liquid is the medium in the convection section of the sucker rod heat pipe.

[0028] In one possible design, when the radial heat flux density of the evaporation section corresponding to the convection section is greater than or equal to the critical heat flux density, the heat transfer coefficient of the convection section is expressed as follows:

[0029] Among them, h f Re is the heat transfer coefficient of the convection section; f v is the first Reynolds number; l λ is the dynamic viscosity of the liquid; l ρ is the thermal conductivity of the liquid; g is the acceleration due to gravity.

[0030] In one possible design, the attribute data includes: third attribute data, wherein the heat transfer coefficient within the sucker rod heat pipe includes the heat transfer coefficient of the condensing section;

[0031] Determining the heat transfer coefficient within the sucker rod heat pipe based on the attribute data includes:

[0032] Calculate the second Reynolds number for liquid film flow in the condensation section;

[0033] The heat transfer coefficient of the condensing section is determined based on the second Reynolds number and the third attribute data.

[0034] In one possible design, the second Reynolds number is expressed as follows:

[0035] Where Re is the second Reynolds number; q c The radial heat flux density of the condensation section; l c The length of the condensation section; μ l h is the dynamic viscosity of the gas liquefying into a liquid medium in the condensation section. fg It is the latent heat of vaporization of the liquid.

[0036] In one possible design, the third attribute data includes: the kinematic viscosity of the medium and the thermal conductivity of the medium;

[0037] The heat transfer coefficient of the condensation section is expressed as follows:

[0038] Among them, h c v is the heat transfer coefficient of the condensation section; e k is the kinematic viscosity of the liquid; l denoted as , where is the thermal conductivity of the liquid; Re is the second Reynolds number; g is the acceleration due to gravity; and the liquid is the medium corresponding to the condensation section in the sucker rod heat pipe.

[0039] In one possible design, calculating the total thermal resistance of the process from the heat-absorbing section to the wellhead of the target wellbore based on the heat transfer coefficient within the sucker rod heat pipe includes:

[0040] The thermal resistance of each sub-path during the heat transfer from the heat-absorbing section to the wellhead of the target wellbore is calculated based on the heat transfer coefficient within the sucker rod heat pipe. The sub-paths include: from the heat-absorbing section heat transfer medium in the tubing annular space to the outer wall of the heating section sucker rod heat pipe; from the outer wall of the heating section sucker rod heat pipe to the inner wall; from the inner wall of the heating section sucker rod heat pipe to the heat transfer medium in the liquid pool within the sucker rod heat pipe; from the heating section of the sucker rod heat pipe to the heat dissipation section; from the medium within the condensation section of the sucker rod heat pipe to the inner wall of the condensation section; from the inner wall of the condensation section of the sucker rod heat pipe to the outer wall; and from the outer wall of the condensation section of the sucker rod heat pipe to the heat-releasing section heat transfer medium in the tubing annular space.

[0041] The total thermal resistance is obtained by summing the thermal resistances corresponding to each sub-path.

[0042] In one possible design, if the flow path is from the heating section to the cooling section of the sucker rod heat pipe, the thermal resistance from the heating section to the cooling section of the sucker rod heat pipe is expressed as follows:

[0043] Where R4 is the thermal resistance from the heating section to the heat dissipation section of the sucker rod heat pipe; G rP is the Grasov number; r L is the Prandtl number; a K represents the length of the convection section. ha denoted as , where is the thermal conductivity of the medium.

[0044] In one possible design, the saturated temperature distribution sequence data includes a first saturated temperature distribution sequence data and a second saturated temperature distribution sequence data;

[0045] The determination of the saturation temperature distribution sequence data within the sucker rod heat pipe includes:

[0046] Obtain the first pressure distribution sequence data within the liquid pool of the sucker rod heat pipe;

[0047] The first saturation temperature distribution sequence data is determined based on the first preset mapping function and the first pressure distribution sequence data, wherein the first preset mapping function is a mapping function between saturation temperature and first pressure.

[0048] Acquire the second saturation temperature distribution sequence data collected by the temperature sensor.

[0049] In one possible design, the temperature distribution sequence data corresponding to the wall of the sucker rod heat pipe includes the temperature distribution sequence data corresponding to the first section of the pipe wall; the temperature distribution sequence data corresponding to the first section of the pipe wall is the temperature distribution sequence data of the section from the lower end of the sucker rod heat pipe to the liquid surface of the heat transfer medium in the liquid pool inside the heat pipe.

[0050] The temperature distribution sequence data corresponding to the first pipe wall segment is represented as follows: T2(x)=T0(x)+Q e / h e 0 < x ≤ L p

[0051] Where T2(x) is the temperature distribution sequence data corresponding to the first section of the pipe wall; Q e h is the heat transfer rate of the heating section of the heat pipe. e L is the heat transfer coefficient from the inner wall of the heat pipe to the surface of the heat transfer medium in the liquid pool inside the heat pipe; p The height of the liquid pool inside the heat pipe of the sucker rod; T0(x) is the first saturation temperature distribution sequence data.

[0052] In one possible design, the temperature distribution sequence data corresponding to the wall of the sucker rod heat pipe includes the temperature distribution sequence data corresponding to the second section of the pipe wall; the temperature distribution sequence data corresponding to the second section of the pipe wall is the temperature distribution sequence data of the section from the liquid surface of the heat transfer medium in the liquid pool inside the sucker rod heat pipe to the upper end of the heating section.

[0053] The temperature distribution sequence data corresponding to the heating section of the second pipe wall is shown below: T3(x)=T1(x)+Qe / h f L p <x≤L e

[0054] Where T3(x) represents the temperature distribution sequence data corresponding to the second section of the pipe wall; Q e L is the heat transfer rate of the heating section of the heat pipe. p h is the height of the liquid pool inside the heat pipe of the sucker rod. f The position of the heat transfer medium in the liquid pool inside the heat pipe is relative to the heat transfer coefficient of the evaporation section; L e T1(x) represents the length of the heating section of the sucker rod heat pipe; T1(x) represents the second saturation temperature distribution sequence data.

[0055] In one possible design, the temperature distribution sequence data corresponding to the heat pipe wall of the sucker rod includes the temperature distribution sequence data corresponding to the third section of the pipe wall; the temperature distribution sequence data corresponding to the third section of the pipe wall is the temperature distribution sequence data of the condensation section.

[0056] The temperature distribution sequence data corresponding to the heating section of the third pipe wall is represented as follows: T4(x)=T1(x)-Q c / h c L e +L a ≤L

[0057] Where T4(x) represents the temperature distribution sequence data corresponding to the pipe wall of the third pipe wall heating section; Q c h is the heat transfer rate of the condenser section of the sucker rod heat pipe. c L is the heat transfer coefficient of the condensing section. e Indicates the length of the heating section of the sucker rod heat pipe; L a denoted by ; L represents the total length of the heat pipe convection section of the sucker rod; T1(x) represents the second saturation temperature distribution sequence data.

[0058] In one possible design, the method further includes:

[0059] Based on the saturated temperature distribution sequence data, the temperature distribution sequence data corresponding to the fourth segment is determined. The temperature distribution sequence data corresponding to the fourth segment of the pipe wall is the temperature distribution sequence data from the upper end of the heating section to the upper end of the convection section.

[0060] The temperature distribution sequence data corresponding to the fourth section of the pipe wall is represented as follows: T5(x) = T1(x), L e <x≤L e +L a

[0061] Where T5(x) represents the temperature distribution sequence data corresponding to the fourth pipe wall segment; L eIndicates the length of the heating section of the sucker rod heat pipe; L a T1(x) represents the length of the convection section of the heat pipe in the sucker rod; T1(x) is the second saturation temperature distribution sequence data.

[0062] Secondly, embodiments of this application provide an apparatus in which a sucker rod heat pipe is located in a target wellbore, the apparatus comprising:

[0063] The acquisition module is used to acquire the attribute data of the sucker rod heat pipe in the target wellbore;

[0064] The determination module is used to determine the heat transfer coefficient inside the sucker rod heat pipe based on the attribute data;

[0065] The calculation module is used to calculate the total thermal resistance of the process from the heat absorption section to the wellhead of the target wellbore in the sucker rod heat pipe based on the heat transfer coefficient in the sucker rod heat pipe.

[0066] The determining module is also used to determine the heat transfer rate of the sucker rod heat pipe based on the total thermal resistance;

[0067] The determination module is also used to determine the saturation temperature distribution sequence data inside the sucker rod heat pipe;

[0068] The determination module is also used to determine the temperature distribution sequence data corresponding to the heat pipe wall of the sucker rod based on the saturated temperature distribution sequence data, the heat transfer rate and the heat transfer coefficient.

[0069] Thirdly, embodiments of this application provide an electronic device, including: a processor, and a memory communicatively connected to the processor;

[0070] The memory stores computer-executed instructions;

[0071] The processor executes computer execution instructions stored in the memory to implement the method as described in the first aspect.

[0072] Fourthly, embodiments of this application provide a computer-readable storage medium storing computer-executable instructions, which, when executed by a processor, are used to implement various possible implementations of the first aspect above.

[0073] Fifthly, this application provides a computer program product, including a computer program that, when executed by a processor, implements the method described in the first aspect.

[0074] This application provides a method, apparatus, electronic device, storage medium, and program product for determining the temperature of a sucker rod heat pipe. The method involves acquiring attribute data of the sucker rod heat pipe in a target wellbore and determining the heat transfer coefficient within the heat pipe based on this data; calculating the total thermal resistance of the heat pipe from the absorber section to the wellhead based on the heat transfer coefficient; determining the heat transfer rate of the heat pipe based on the total thermal resistance; determining the saturated temperature distribution sequence data within the heat pipe; and determining the temperature distribution sequence data corresponding to the pipe wall based on the saturated temperature distribution sequence data, the heat transfer rate, and the heat transfer coefficient. The method of this application can determine the precise heat transfer coefficient within the sucker rod heat pipe by using the property data of the sucker rod heat pipe in the target wellbore; then, based on the heat transfer coefficient within the sucker rod heat pipe, it can determine the total thermal resistance of the process from the heat absorption section to the wellhead of the target wellbore; and based on the total thermal resistance, it can determine the corresponding heat transfer rate of the sucker rod heat pipe; finally, based on the precise saturated temperature distribution sequence data, heat transfer rate, and heat transfer coefficient within the sucker rod heat pipe, it can confirm the precise temperature distribution sequence data corresponding to the sucker rod heat pipe wall. The method of this application improves the accuracy of calculating the temperature distribution sequence of the sucker rod heat pipe wall, and thus can accurately determine the temperature distribution inside the tubing based on the temperature distribution sequence data of the sucker rod heat pipe wall, thereby preventing wax deposition of crude oil near the wellhead. Attached Figure Description

[0075] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application.

[0076] Figure 1 is a schematic diagram of the structure of the wellbore provided in an embodiment of this application;

[0077] Figure 2 is an application scenario diagram of the method for determining the temperature of the sucker rod heat pipe provided in the embodiment of this application;

[0078] Figure 3 is a flowchart of a method for determining the temperature of a sucker rod heat pipe according to an embodiment of this application;

[0079] Figure 4 is a schematic diagram of a temperature determination device for a sucker rod heat pipe provided in an embodiment of this application;

[0080] Figure 5 is a schematic diagram of the structure of an electronic device provided in one embodiment of this application.

[0081] The accompanying drawings illustrate specific embodiments of this application, which will be described in more detail below. These drawings and descriptions are not intended to limit the scope of the concept in any way, but rather to illustrate the concept of this application to those skilled in the art through reference to particular embodiments. Detailed Implementation

[0082] Exemplary embodiments will now be described in detail, examples of which are illustrated in the accompanying drawings. When the following description relates to the drawings, unless otherwise indicated, the same numbers in different drawings denote the same or similar elements. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with this application. Rather, they are merely examples of apparatuses and methods consistent with some aspects of this application as detailed in the appended claims.

[0083] First, let me explain the terms used in this application:

[0084] Wellbore: The wellbore is the borehole from the wellhead to the bottom of the well, and is a core component in the oil extraction and production process. It can consist of casing, sucker rod heat pipe, and tubing. The casing and tubing form an annular structure; the sucker rod heat pipe is located inside the tubing, and the tubing is located inside the casing, forming two annular gaps. A heat transfer medium can be stored between the sucker rod heat pipe and the tubing; this heat transfer medium can be an oil-water mixture or other heat transfer media. A schematic diagram of the wellbore structure is shown in Figure 1. Where L... p Indicates the height of the liquid pool; L e Indicates the length of the heating section or the heat absorption section; L a Indicates the length of the convection section; L c This indicates the length of the condensation section or the length of the heat release section.

[0085] Casing: It is the main supporting part of the well casing, which is installed inside the well casing to form a ring-shaped pipe to maintain the stability of the well casing.

[0086] Pipelines: Important pipelines that transport crude oil to the ground.

[0087] A sucker rod heat pipe is a highly efficient heat transfer device. It may contain a liquid pool inside the pipe to store the liquid medium circulating and transferring heat within the heat pipe; this pool is located at the lower end of the sucker rod heat pipe. The liquid medium can be water, ethanol, acetone, etc. Based on the heat transfer principle, the heat transfer process of a sucker rod heat pipe can be divided into a heating section, a convection section, and a condensation section. The heating section is the area within the sucker rod heat pipe that absorbs and transfers heat; it can be located at the lower part of the heat pipe. The condensation section is the area within the sucker rod heat pipe that releases heat; it can be located at the upper part of the heat pipe. The convection section is the area where the heat transfer medium flows from the heating section to the condensation section or vice versa due to a small pressure difference formed inside the sucker rod heat pipe; it can be located in the middle of the heat pipe. The heat absorption section is located at the lower end of the annular space between the outer wall of the sucker rod heat pipe and the oil pipe, corresponding to the heating section; it is used to absorb the high-temperature heat from the oil pipe. It utilizes the heat transfer medium between the outer wall of the sucker rod heat pipe and the annular space between the tubing to absorb heat and transfer the absorbed heat to the heating section inside the sucker rod heat pipe, thus heating that section. The heat release section is located in the upper region of the annular space between the outer wall of the sucker rod heat pipe and the tubing, corresponding to the condensation section. It uses the heat transfer medium between the annular space between the sucker rod heat pipe and the tubing to transfer the heat released from the condensation section of the sucker rod heat pipe to the tubing, thereby heating the area near the wellhead.

[0088] The heat transfer principle of the sucker rod heat pipe is as follows: the heat-absorbing section absorbs high-temperature heat from the deep oil well through the heat transfer medium, and the heating section receives the heat transferred from the heat-absorbing section. As the absorbed heat increases, the liquid in the liquid pool at the lower end of the sucker rod heat pipe vaporizes into high-temperature gas. When the high-temperature gas flows within the pipe, its heat is transferred to the condensation section via convection. Because the inner wall of the condensation section is in constant contact with the low-temperature medium on the outer wall, the low temperature of the outer wall is transferred into the condensation section. Therefore, when the high-temperature hot gas reaches the condensation section, it liquefies upon cooling and releases heat; the released heat is then transferred through the pipe wall to the heat transfer medium in the heat-releasing section. After absorbing heat, the heat transfer medium can transfer it to the tubing to heat the tubing, thereby preventing the crude oil in the tubing from waxing. The liquefied liquid flows back to the liquid pool, repeating the above process to heat the area near the wellhead of the tubing.

[0089] To clearly understand the technical solution of this application, the solutions of the prior art will be described in detail first.

[0090] Sucker rod heat pipe wellbore heating technology is a fluid wellbore heating oil production technology that primarily utilizes the heat transfer principle of sucker rod heat pipes to heat the tubing within the wellbore. This technology involves using special processes such as filling hollow sucker rods with a medium, vacuuming, and sealing to create extra-long sucker rod heat pipes, which are then connected to the entire oil production rig's pumping system to heat the area near the wellhead. This technology can effectively improve the temperature field of the wellbore and features a simple well structure, no maintenance required, and self-operating operation. However, there are few methods for calculating the temperature distribution of sucker rod heat pipes, and the calculation accuracy is low, making it difficult to accurately control temperature changes within the tubing based on its own temperature distribution. Consequently, it cannot effectively improve the wax deposition phenomenon of crude oil near the wellhead.

[0091] Therefore, to improve the accuracy of temperature distribution sequence data calculation for sucker rod heat pipes when facing existing technical problems, it is first necessary to obtain accurate saturated temperature distribution sequence data, heat transfer rate, and heat transfer coefficient. Then, based on the saturated temperature distribution sequence data, heat transfer rate, and heat transfer coefficient, accurate temperature distribution sequence data corresponding to the sucker rod heat pipe wall is obtained. Since the heat transfer coefficient is related to the property data of the sucker rod heat pipe, and the heat transfer rate is closely related to the heat transfer coefficient, the heat transfer coefficient inside the sucker rod heat pipe can be determined based on the property data of the sucker rod heat pipe in the target wellbore. Then, based on the heat transfer coefficient inside the sucker rod heat pipe, the total thermal resistance of the heat transfer process from the heat absorption section to the wellhead of the target wellbore can be determined. The heat transfer rate of the sucker rod heat pipe is then determined based on the total thermal resistance. Finally, based on the determined saturated temperature distribution sequence data, heat transfer rate, and heat transfer coefficient inside the sucker rod heat pipe, the temperature distribution sequence data corresponding to the sucker rod heat pipe wall can be determined. This improves the accuracy of the temperature distribution sequence calculation for the sucker rod heat pipe wall.

[0092] Figure 2 illustrates an application scenario of the method for determining the temperature of a sucker rod heat pipe according to an embodiment of this application. This application scenario may include a server 201, a database 202, and a terminal device 203 corresponding to the temperature distribution sequence data of the sucker rod heat pipe. The database 202 can be integrated into the server 201; the server 201 establishes a communication connection with the terminal device 203. The database 202 can be used to store attribute data of the sucker rod heat pipe. Optionally, the server 201 can communicate with a sensor device installed on the sucker rod heat pipe; by communicating with the sensor device, it can acquire in real-time attribute data of the sucker rod heat pipe changing with temperature, collected by the sensor device.

[0093] Specifically, the user inputs the corresponding sucker rod heat pipe model into the client of the sucker rod heat pipe temperature determination method on the terminal device 203, triggering the terminal device 203 to send a sucker rod heat pipe temperature determination request to the server 201. The determination request may include the sucker rod heat pipe model. Upon receiving the request, the server 201 sends the sucker rod heat pipe model to the database 202. The database 202 retrieves the corresponding attribute data based on the sucker rod heat pipe model field. After obtaining the attribute data corresponding to the sucker rod heat pipe model, the server 201 calculates the heat transfer coefficient of the sucker rod heat pipe based on the attribute data; then, based on the heat transfer coefficient, it calculates the total thermal resistance of the heat pipe's heat absorption section to the wellhead; and finally, based on the heat... The total thermal resistance of the heat transfer process from the heat-absorbing section of the tube to the wellhead is used to determine the heat transfer rate of the sucker rod heat pipe. Furthermore, the saturated temperature distribution sequence data of the sucker rod heat pipe is determined, and based on the saturated temperature distribution sequence data, heat transfer rate, and heat transfer coefficient, the temperature distribution sequence data corresponding to the sucker rod heat pipe wall is determined. This allows the temperature distribution sequence data corresponding to the sucker rod heat pipe wall to be determined and stored in tabular form. A temperature determination response for the sucker rod heat pipe is then sent to the terminal device, which can include the temperature distribution sequence data. The terminal device can then display the temperature distribution sequence data in tabular form, allowing the user to view the temperature distribution sequence data for this type of sucker rod heat pipe.

[0094] It should be noted that the terminal device can also obtain the attribute data of the sucker rod heat pipe of this model from the server and then execute the temperature determination method of the sucker rod heat pipe of this application. This embodiment does not limit this.

[0095] The technical solution of this application and how the technical solution of this application solves the above-mentioned technical problems are described in detail below with specific embodiments. These specific embodiments can be combined with each other, and the same or similar concepts or processes may not be described again in some embodiments. The embodiments of this application will now be described with reference to the accompanying drawings.

[0096] Figure 3 is a flowchart of a method for determining the temperature of a sucker rod heat pipe according to an embodiment of the application. As shown in Figure 3, the executing entity of this embodiment is a temperature determining device for the sucker rod heat pipe. This device can be implemented by a computer program; it can also be implemented by a medium storing the relevant computer program, such as a USB flash drive and / or optical disc; or it can be implemented by a physical device integrating or installing the relevant computer program, such as a chip or a temperature determining device for the sucker rod heat pipe. The temperature determining device for the sucker rod heat pipe can be a server, a server cluster, a terminal device, or other electronic equipment. The method for determining the temperature of the sucker rod heat pipe provided in this embodiment includes the following steps:

[0097] Step 301: Obtain the attribute data of the sucker rod heat pipe in the target wellbore, and determine the heat transfer coefficient inside the sucker rod heat pipe based on the attribute data.

[0098] The target wellbore refers to the wellbore whose temperature distribution is to be determined.

[0099] The attribute data of a sucker rod heat pipe refers to its own hardware structural parameters, heat transfer data related to the medium inside the pipe, and physical data, etc.; it may include: density, thermal conductivity, specific heat capacity, viscosity, atmospheric pressure, latent heat of vaporization, etc.; the corresponding data can be stored in the attribute data table of the sucker rod heat pipe.

[0100] The heat transfer coefficient describes the heat transfer capacity per unit time and per unit area. Since temperature changes within the wellbore are non-uniform, the heat transfer coefficient corresponding to different sub-paths can be calculated based on different sub-paths. The heat transfer coefficient within the sucker rod heat pipe can include: the heat transfer coefficient of the heating section, the heat transfer coefficient of the convection section, and the heat transfer coefficient of the condensation section within the sucker rod heat pipe; it can also include the heat transfer coefficient from the outer wall to the inner wall of the heating section of the sucker rod heat pipe; and the heat transfer coefficient from the medium within the condensation section of the sucker rod heat pipe to the inner wall of the condensation section, etc. Here, a sub-path refers to a sub-path divided according to the heat transfer path; it can be divided according to the heating section, convection section, and condensation section of the sucker rod heat pipe; it can also be divided according to other segments, which is not limited in this embodiment.

[0101] Specifically, based on the model of the sucker rod heat pipe in the target wellbore, the corresponding model field is queried in the sucker rod heat pipe attribute data table, and the attribute data of the sucker rod heat pipe corresponding to the model field is used as the attribute data of the sucker rod heat pipe in the target wellbore. Then, based on the obtained attributes of the sucker rod heat pipe in the target wellbore, the heat transfer coefficient of each sub-path is calculated according to the set formula. The set formula can be an experimental measurement derivation formula, a numerical simulation formula, or other methods; this embodiment does not limit the specific methods used.

[0102] Step 302: Calculate the total thermal resistance in the sucker rod heat pipe from the heat absorption section to the wellhead of the target wellbore based on the heat transfer coefficient in the sucker rod heat pipe.

[0103] The total thermal resistance of the heat transfer process from the heat-absorbing section to the wellhead of the target wellbore is the sum of the resistances encountered during the heat transfer process from the heat-absorbing section to the wellhead of the target wellbore.

[0104] Specifically, the heat transfer process from the heat-absorbing section of the sucker rod heat pipe to the wellhead of the target wellbore can be divided into sub-paths according to the heat transfer path; and the thermal resistance of each sub-path can be calculated based on the heat transfer coefficient of each sub-path and the corresponding attribute data, and the thermal resistance of all sub-paths can be summed as the total thermal resistance of the process from the heat-absorbing section to the wellhead of the target wellbore.

[0105] For example, the thermal resistance of the sub-path may include the heat transfer resistance between the heat transfer medium inside the sucker rod heat pipe and the heat transfer resistance between the inner or outer wall of the sucker rod heat pipe and the heat transfer medium.

[0106] Optionally, the thermal resistance between the heat transfer medium inside the sucker rod heat pipe, the thermal resistance between the inner wall of the sucker rod heat pipe and the heat transfer medium, and the thermal resistance between the outer wall of the sucker rod heat pipe and the heat transfer medium can all be calculated based on the heat transfer coefficient.

[0107] Optionally, the thermal resistance of the branch path may also include the thermal resistance between the inner and outer walls of the sucker rod heat pipe, and the thermal resistance between the inner and outer walls of the sucker rod heat pipe can be calculated based on the corresponding thermal conductivity of the heat-conducting material of the sucker rod heat pipe.

[0108] Step 303: Determine the heat transfer rate of the sucker rod heat pipe based on the total thermal resistance.

[0109] The heat transfer rate describes the amount of heat transferred per unit area per unit time within the sucker rod heat pipe; it can be calculated by the ratio of the temperature change within the sucker rod heat pipe to the total thermal resistance, as shown in formula (1):

[0110] Among them, Q hp ΔT represents the heat transfer rate of the sucker rod heat pipe; ΔT represents the temperature change inside the sucker rod heat pipe. For L e The integral average value of the oil temperature curve over its length; For L c The integral average value of the oil temperature curve over its length; R represents the total thermal resistance. According to L e Integral over the length range of the oil temperature profile with L e Calculation of the ratio of lengths; accordingly, According to L c Integral length range over oil temperature profile with respect to L c Calculation of the length ratio. The oil temperature curve is a function of oil temperature changing with time. It can be derived from experimental measurement formulas or obtained through other calculation methods; this embodiment does not impose specific limitations.

[0111] This is understandable, since the heating section of the sucker rod heat pipe absorbs heat while the condensing section releases heat. Therefore, the temperature change inside the sucker rod heat pipe can be considered as the temperature difference between the heating section and the condensing section above the sucker rod.

[0112] Step 304: Determine the internal saturation temperature distribution sequence data inside the sucker rod heat pipe.

[0113] The internal saturation temperature of the sucker rod heat pipe refers to the highest temperature inside the sucker rod heat pipe that gradually rises as the liquid medium in the liquid pool inside the sucker rod heat pipe vaporizes into gas, reaching the boiling point.

[0114] The internal saturation temperature distribution sequence data refers to the saturation temperature of the medium at different locations inside the sucker rod heat pipe, which can be represented as a sequence of numbers corresponding to the depth inside the sucker rod heat pipe and the temperature.

[0115] Specifically, when the temperature inside the sucker rod heat pipe reaches its maximum, the heat transfer medium in the liquid pool inside the sucker rod heat pipe consists of incompletely evaporated liquid and gas formed by evaporation above the liquid; above the heat transfer medium in the liquid pool inside the sucker rod heat pipe is the gaseous medium formed by evaporation. Therefore, the internal saturated temperature distribution sequence data inside the sucker rod heat pipe can include the temperature distribution sequence data of the gaseous and liquid media in the liquid pool of the sucker rod heat pipe, as well as the temperature distribution sequence data of the gas formed above the heat transfer medium in the liquid pool of the sucker rod heat pipe. The temperature distribution sequence data of the gaseous and liquid media in the liquid pool of the sucker rod heat pipe, as well as the temperature distribution sequence data of the gas above the heat transfer medium in the liquid pool of the sucker rod heat pipe, can be calculated using methods such as establishing a temperature distribution model and numerical calculation; this embodiment does not impose any limitations on these methods.

[0116] Step 305: Determine the temperature distribution sequence data corresponding to the heat pipe wall of the sucker rod based on the saturated temperature distribution sequence data, heat transfer rate and heat transfer coefficient.

[0117] Specifically, since the saturated heat and heat transfer capacity of each sub-path inside the sucker rod heat pipe are different, the temperature distribution sequence data corresponding to each sub-path can be calculated. The combination of the temperature distribution sequence data corresponding to all sub-paths is then used as the temperature distribution sequence data of the sucker rod heat pipe wall. The temperature distribution sequence data corresponding to each sub-path can be calculated by inputting the saturated temperature distribution sequence data, heat transfer rate, and heat transfer coefficient obtained in steps 301-304 into a preset formula. This preset formula can be an experimental derivation or other theoretical formula; this embodiment does not impose any limitations.

[0118] In this embodiment, a method for determining the temperature of a sucker rod heat pipe located in a target wellbore includes: acquiring attribute data of the sucker rod heat pipe in the target wellbore and determining the heat transfer coefficient within the sucker rod heat pipe based on the attribute data; calculating the total thermal resistance of the sucker rod heat pipe during the process of heat transfer from the heat-absorbing section to the wellhead of the target wellbore based on the heat transfer coefficient; determining the heat transfer rate of the sucker rod heat pipe based on the total thermal resistance; determining the saturated temperature distribution sequence data within the sucker rod heat pipe; and determining the temperature distribution sequence data corresponding to the pipe wall of the sucker rod heat pipe based on the saturated temperature distribution sequence data, the heat transfer rate, and the heat transfer coefficient. Based on the heat transfer principle of the sucker rod heat pipe, the process for calculating the temperature distribution sequence data corresponding to the pipe wall of the sucker rod heat pipe in this embodiment is reasonably designed. Since the heat transfer coefficient is related to the property data of the sucker rod heat pipe, and the heat transfer rate is closely related to the heat transfer coefficient, the heat transfer coefficient inside the sucker rod heat pipe can be determined based on the property data of the sucker rod heat pipe in the target wellbore. Then, based on the heat transfer coefficient inside the sucker rod heat pipe, the total thermal resistance of the heat transfer process from the absorber section to the wellhead of the target wellbore can be determined. The heat transfer rate of the sucker rod heat pipe can then be determined based on the total thermal resistance. Finally, based on the determined saturated temperature distribution sequence data, heat transfer rate, and heat transfer coefficient inside the sucker rod heat pipe, the temperature distribution sequence data corresponding to the sucker rod heat pipe wall can be determined. This improves the accuracy of the temperature distribution sequence calculation for the sucker rod heat pipe wall.

[0119] As an optional implementation, based on the above embodiments, the heat transfer coefficient in the sucker rod heat pipe includes the heat transfer coefficient of the heating section; the attribute data includes the first attribute data;

[0120] Determining the heat transfer coefficient within the sucker rod heat pipe based on attribute data includes: acquiring first pressure distribution sequence data within the liquid pool of the sucker rod heat pipe; and determining the heat transfer coefficient of the heating section based on the first attribute data, the ratio coefficient of the first pressure distribution sequence data to atmospheric pressure.

[0121] The first attribute data refers to the heat transfer parameters and physical parameters related to the heat transfer medium in the heat transfer pool of the sucker rod heat pipe.

[0122] The first pressure distribution sequence data refers to the pressure distribution of the heat transfer medium in the liquid pool of the sucker rod heat pipe, which can be represented as a series of data corresponding to the liquid pool height and pressure of the sucker rod heat pipe. The calculation of the first pressure distribution sequence data p(x) can be referenced by formula (2): p(x)=p v +ρ l gx, 0 < x < L p (2)

[0123] Where, p v x represents the gas pressure; x represents the liquid medium height; L represents the gas pressure. p The height of the liquid pool is represented by g; g is the acceleration due to gravity.

[0124] Optionally, p v The pressure sensor installed in a sensor device mounted on the sucker rod heat pipe can be used for measurement. The liquid medium height x, which decreases as the liquid evaporates, can also be measured in real time by the pressure sensor. v x can also be obtained through other methods, which are not limited in this embodiment. The server can read the aforementioned data corresponding to the sensor device's data interface in real time and save it to the attribute data table.

[0125] Specifically, an optimal mathematical model is derived based on experimental measurement data to relate the first attribute data, the first pressure distribution sequence data, and atmospheric pressure; this model is then used to calculate the heat transfer coefficient of the heating section. The heat transfer coefficient of the heating section can also be calculated using other methods, which are not limited in this embodiment.

[0126] As an optional implementation, based on the above embodiments, the first attribute data includes: the specific heat capacity, thermal conductivity, latent heat of vaporization, dynamic viscosity, density of the medium in the sucker rod heat pipe, and the radial heat flux density of the evaporation section corresponding to the heating section;

[0127] The heat transfer coefficient of the heating section is expressed as follows:

[0128] Among them, h e ρ is the heat transfer coefficient of the heating section of the sucker rod heat pipe; l ρ is the density of the liquid. v Where is the density of the steam; g is the acceleration due to gravity; C pl q represents the specific heat capacity of the liquid. e h is the radial heat flux density of the evaporation section. fg p represents the latent heat of vaporization of the liquid; p represents the first pressure distribution sequence data; p a Atmospheric pressure; λ l u is the thermal conductivity of the liquid. l is the dynamic viscosity of the liquid; the liquid is the medium in the heating section of the sucker rod heat pipe, and the vapor is the medium in the corresponding evaporation section of the heating section of the sucker rod heat pipe.

[0129] The radial heat flux density of the evaporation section represents the amount of heat passing through its radial cross-section per unit time. The evaporation section refers to the vapor film formed by the gas produced during liquid evaporation; part of this vapor film is located above the heat transfer medium in the heating section's liquid pool, and part is located below the convection section.

[0130] The radial heat flux density of the evaporation section corresponding to the heating section refers to the heat in the radial cross section above the heat transfer medium in the liquid pool through the sucker rod heat pipe.

[0131] Among them, the radial heat flux density q in the evaporation section eThe latent heat of vaporization of liquids, h fg The density ρ of a dense liquid l The density of steam ρ v and the specific heat capacity C of the liquid medium pl All measurements can be taken in real time using sensors installed in a sensor device mounted on the sucker rod heat pipe; other methods may also be used, which are not limited in this embodiment. The server can read the aforementioned data corresponding to the sensor device's data interface in real time and save it to the attribute data table. It should be noted that all measurements involving radial heat flux density, latent heat of vaporization of liquids, density of dense liquids, density of vapors, and specific heat capacity of liquid media in this application are measured by sensors, and the measurement data is saved to the corresponding data table; this will not be repeated hereafter.

[0132] Among them, gravitational acceleration g and atmospheric pressure p a The thermal conductivity λ of the liquid medium l All of these are known fixed values ​​that can be directly obtained from the attribute data table, and will not be elaborated further.

[0133] Specifically, the density ρ of the dense liquid is obtained from the attribute data table. l The density of steam ρ v Specific heat capacity C of liquid medium pl Atmospheric pressure p l The thermal conductivity λ of the liquid medium l The radial heat flux density q of the evaporation section corresponding to the heating section at the corresponding temperature. e and the corresponding viscosity u l and the latent heat of vaporization h at the corresponding temperature fg The heat transfer coefficient of the heating section can be determined by inputting the formula (3) into the preset formula.

[0134] In this embodiment, the heat transfer coefficient within the sucker rod heat pipe includes the heat transfer coefficient of the heating section; the attribute data includes first attribute data; determining the heat transfer coefficient within the sucker rod heat pipe based on the attribute data includes: acquiring first pressure distribution sequence data within the liquid pool of the sucker rod heat pipe; determining the heat transfer coefficient of the heating section based on the first attribute data, the ratio coefficient of the first pressure distribution sequence data to atmospheric pressure. The first attribute data includes: the specific heat capacity, thermal conductivity, latent heat of vaporization, dynamic viscosity, density of the medium in the sucker rod heat pipe, and the radial heat flux density of the evaporation section corresponding to the heating section; by comprehensively considering various physical properties of the medium and the pressure distribution within the sucker rod heat pipe, the heat transfer coefficient of the heating section can be calculated more accurately, thereby more precisely describing the heat transfer process of the heating section within the sucker rod heat pipe.

[0135] In this embodiment, the heat transfer coefficient of the heating section is expressed as follows:

[0136] Among them, h e ρ is the heat transfer coefficient of the heating section of the sucker rod heat pipe; l ρ is the density of the liquid. v Where is the density of the steam; g is the acceleration due to gravity; C pl q represents the specific heat capacity of the liquid. e h is the radial heat flux density of the evaporation section. fg p represents the latent heat of vaporization of the liquid; p represents the first pressure distribution sequence data; p a Atmospheric pressure; λ l u is the thermal conductivity of the liquid. l Here, represents the dynamic viscosity of the liquid; the liquid is the medium in the heating section of the sucker rod heat pipe; and the vapor is the medium in the corresponding evaporation section of the heating section of the sucker rod heat pipe. This formula allows for a more accurate calculation of the heat transfer coefficient of the heating section, ensuring more precise data derived from it.

[0137] As an optional implementation, based on the above embodiments, the heat transfer coefficient in the sucker rod heat pipe includes the heat transfer coefficient of the convection section; the attribute data includes first attribute data and second attribute data, the second attribute data including the radial heat flux density of the evaporation section corresponding to the convection section and the liquid pool height in the sucker rod heat pipe; determining the heat transfer coefficient in the sucker rod heat pipe based on the attribute data includes: comparing the radial heat flux density of the evaporation section corresponding to the convection section with the critical heat flux density; in response to the radial heat flux density of the evaporation section corresponding to the convection section being less than the critical heat flux density, obtaining the second pressure distribution sequence data corresponding to the convection section of the sucker rod heat pipe; determining the heat transfer coefficient of the convection section based on the ratio coefficient of the first attribute data, the second pressure distribution sequence data and atmospheric pressure; in response to the radial heat flux density of the evaporation section corresponding to the convection section being greater than or equal to the critical heat flux density, calculating the first Reynolds number of the liquid film flow in the evaporation section of the convection section, and determining the heat transfer coefficient of the convection section based on the first Reynolds number and the liquid pool height in the sucker rod heat pipe.

[0138] The critical heat flux density refers to the heat flux density at which the boiling state of the liquid medium changes significantly and transitions to a transitional boiling state when the radial heat flux density in the evaporation section increases to a certain value. This critical heat flux density can be an empirical value.

[0139] The second pressure distribution sequence data refers to the pressure distribution sequence data of the gas heat transfer medium above the liquid pool, which can be measured by the pressure sensor in the sensor device. The server can read the pressure distribution sequence data corresponding to the sensor device's data interface in real time and save it to the attribute data table.

[0140] Alternatively, the second pressure distribution sequence data p2(x) can be expressed as formula (4): p2(x)=p v L p<x<L (4)

[0141] Where, p v It can be expressed as the pressure value measured by the pressure sensor in the sensor device.

[0142] The first Reynolds number is a parameter used to calculate the heat transfer coefficient of the convection section. It characterizes the stability of the flow of the heat transfer medium during evaporation within the corresponding evaporation section. The first Reynolds number is related to the dynamic viscosity of the heat transfer medium, which is affected by factors such as temperature; the dynamic viscosity decreases as temperature increases. The first Reynolds number can be measured experimentally or calculated using theoretical models; this embodiment does not limit this calculation.

[0143] As an optional implementation, the first Reynolds number is expressed as follows:

[0144] Among them, Re f L represents the first Reynolds number; p L is the liquid pool height of the sucker rod heat pipe; f h is the length of the liquid film in the liquid film evaporation section. fg The latent heat of vaporization of the liquid; u l q represents the dynamic viscosity of the liquid. e The radial heat flux density is the evaporation section of the convection section; the liquid is the medium in the convection section of the sucker rod heat pipe.

[0145] Among them, the liquid film in the liquid film evaporation section refers to the liquid film formed by the liquid during the evaporation process in the evaporation section; it can be the liquid film formed during the evaporation process in the corresponding evaporation section inside the sucker rod heat pipe.

[0146] The liquid film length in the liquid film evaporation section refers to the length of the liquid film formed by the liquid medium during the evaporation process. In this embodiment, part of the evaporation section is located in the heating section, and another part is located in the convection section. Therefore, the liquid film length should be the sum of the liquid film lengths of the evaporation section corresponding to the heating section and the liquid film lengths corresponding to the convection section; it can be approximately expressed as L. f =L e -L P +L a .

[0147] Optionally, the liquid pool height, liquid film length of the liquid film evaporation section, latent heat of vaporization of the liquid, dynamic viscosity of the liquid, and radial heat flux density of the convection section evaporation section of the corresponding sucker rod heat pipe can be obtained from the attribute data table, and the first Reynolds number can be calculated by the preset formula (5).

[0148] Specifically, the radial heat flux density of the corresponding evaporation section is obtained and compared with a preset critical heat flux density threshold. When the radial heat flux density is less than the critical heat flux density, it indicates that the liquid medium has not fully reached the boiling state; this can be determined based on the ratio coefficient of a property data, the pressure distribution data of the evaporation section, and the atmospheric pressure. When the radial heat flux density is greater than or equal to the critical heat flux density, it indicates that the evaporating gas has fully reached the boiling state; in this case, the first Reynolds number of the liquid film flow in the evaporation section can be calculated first according to the preset formula (5), and then the heat transfer coefficient of the convection section can be calculated according to the experimentally derived formula based on the first Reynolds number and the height of the liquid pool in the sucker rod heat pipe. In this embodiment, the method for obtaining the heat transfer coefficient of the convection section can also be other, and is not limited in this embodiment.

[0149] Optionally, when the radial heat flux density is less than the critical heat flux density, the heat transfer coefficient h of the convection section is... f It can be calculated using formula (3). Where p is taken from the second pressure distribution sequence data; as shown in formula (6):

[0150] As an optional implementation, when the radial heat flux density of the evaporation section corresponding to the convection section is greater than or equal to the critical heat flux density, the heat transfer coefficient of the convection section is expressed as follows:

[0151] Among them, h f Re is the heat transfer coefficient of the convection section; f v is the first Reynolds number; l λ is the dynamic viscosity of the liquid; l ρ is the thermal conductivity of the liquid; g is the acceleration due to gravity.

[0152] Understandably, the Reynolds number characterizes changes in the liquid flow state. When the radial heat flux density of the evaporation section corresponding to the convection section is greater than or equal to the critical heat flux density, it indicates that the liquid has reached a transitional boiling state. At this point, heat transfer efficiency is higher, and the convective heat transfer coefficient may also increase; therefore, changes in the Reynolds number affect the heat transfer coefficient. An increase in dynamic viscosity increases the resistance to flow of the heat transfer medium, leading to a greater thermal resistance; a decrease in dynamic viscosity also decreases the resistance to flow of the heat transfer medium, leading to a smaller thermal resistance. Changes in thermal resistance also affect heat transfer, thus affecting the heat transfer coefficient. Therefore, through the analysis and experimental derivation of the above factors affecting the heat transfer coefficient, the corresponding mathematical formula can be obtained.

[0153] Optionally, formula (7) can be used to accurately calculate the heat transfer coefficient of the convection section when the radial heat flux density of the evaporation section corresponding to the convection section is greater than or equal to the critical heat flux density. The aforementioned heat transfer coefficient can also be calculated in other ways; this embodiment does not limit its calculation. Specifically, the dynamic viscosity v of the liquid is obtained from the attribute data table. l The thermal conductivity λ of a liquid land the first Reynolds number Re f ; and the above dynamic viscosity v l The thermal conductivity λ of a liquid l The first Reynolds number Re f Inputting the formula (7) into the preset formula can calculate the heat transfer coefficient of the convection section when the radial heat flux density of the evaporation section corresponding to the convection section is greater than or equal to the critical heat flux density.

[0154] Understandably, when the radial heat flux density is greater than or equal to the critical heat flux density, both the evaporation section above the heat transfer medium in the liquid pool of the oil extraction pipe and the evaporation section above the convection section are in a transitional boiling state. At this time, the heat transfer coefficient of the evaporation section above the heat transfer medium in the liquid pool of the oil extraction pipe can also be expressed as h calculated by formula (7). f .

[0155] In this embodiment, the heat transfer coefficient within the sucker rod heat pipe includes the heat transfer coefficient of the convection section; the attribute data includes first attribute data and second attribute data, the second attribute data including the radial heat flux density of the evaporation section corresponding to the convection section and the liquid pool height within the sucker rod heat pipe; determining the heat transfer coefficient within the sucker rod heat pipe based on the attribute data includes: comparing the radial heat flux density of the evaporation section corresponding to the convection section with the critical heat flux density; in response to the radial heat flux density of the evaporation section corresponding to the convection section being less than the critical heat flux density, obtaining the second pressure distribution sequence data corresponding to the convection section of the sucker rod heat pipe; determining the heat transfer coefficient of the convection section based on the ratio coefficient of the first attribute data, the second pressure distribution sequence data, and atmospheric pressure; in response to the radial heat flux density of the evaporation section corresponding to the convection section being greater than or equal to the critical heat flux density, calculating the first Reynolds number of the liquid film flow in the evaporation section of the convection section, and determining the heat transfer coefficient of the convection section based on the first Reynolds number and the liquid pool height within the sucker rod heat pipe. When the radial heat flux density is less than the critical heat flux density, it indicates that the evaporation section corresponding to the convection section has not yet reached a fully boiling state. In this case, the second pressure distribution data corresponding to the convection section can be obtained, and combined with the first attribute data and the ratio coefficient of atmospheric pressure, the heat transfer coefficient of the convection section can be accurately determined. When the radial heat flux density is greater than or equal to the critical heat flux density, it indicates that the evaporation section corresponding to the convection section has reached a fully boiling state, which may lead to unstable liquid film flow. In this case, it is necessary to calculate the first Reynolds number of the liquid film flow in the evaporation section of the convection section, and then determine the heat transfer coefficient corresponding to the convection section based on the first Reynolds number and the first attribute data. Therefore, by comprehensively considering multiple parameters such as radial heat flux density, liquid pool height, and the Reynolds number of the liquid film flow, the heat transfer coefficient of the convection section can be calculated more accurately, thus providing a more precise description of the heat transfer process in the convection section within the sucker rod heat pipe.

[0156] In this embodiment, the first Reynolds number is expressed as follows: Among them, Re f L represents the first Reynolds number;p L is the liquid pool height of the sucker rod heat pipe; f h is the length of the liquid film in the liquid film evaporation section. fg The latent heat of vaporization of the liquid; u l Let q be the dynamic viscosity of the liquid. e The radial heat flux density is denoted as , where is the heat flux density of the evaporation section within the convection section, and is the liquid medium within the convection section of the sucker rod heat pipe. The above formula better characterizes the effect of dynamic viscosity on the first Reynolds number, thus obtaining a more accurate first Reynolds number; consequently, it ensures more accurate data derived from the first Reynolds number.

[0157] In this embodiment, when the radial heat flux density of the evaporation section corresponding to the convection section is greater than or equal to the critical heat flux density, the heat transfer coefficient of the convection section is expressed as follows: Among them, h f Re is the heat transfer coefficient of the convection section; f v is the first Reynolds number; l λ is the dynamic viscosity of the liquid; l Where is the thermal conductivity of the liquid; g is the acceleration due to gravity. The above formula provides a more accurate method for calculating the heat transfer coefficient of the convection section when the radial heat flux density of the corresponding evaporation section is greater than or equal to the critical heat flux density.

[0158] As an optional implementation, based on the above embodiments, the attribute data includes: third attribute data, which includes: the kinematic viscosity and thermal conductivity of the medium in the sucker rod heat pipe, including:

[0159] The heat transfer coefficient within the sucker rod heat pipe includes the heat transfer coefficient of the condensing section. Determining the heat transfer coefficient within the sucker rod heat pipe based on attribute data includes: calculating the second Reynolds number for liquid film flow in the condensing section; and determining the heat transfer coefficient of the condensing section based on the second Reynolds number and the third attribute data. Similarly, in the condensing section, the gas liquefies and releases heat due to the low-temperature pipe wall; the heat transfer coefficient of the condensing section is still affected by factors such as the Reynolds number and the dynamic viscosity of the medium. Therefore, by analyzing the factors affecting the heat transfer coefficient and establishing a mathematical model, a more accurate heat transfer coefficient for the condensing section can be obtained. Specifically, the second Reynolds number for liquid film flow in the condensing section can be calculated in advance; a relationship model between the second Reynolds number and the third attribute data can be established to determine the heat transfer coefficient of the condensing section. The relationship model between the second Reynolds number and the third attribute data can be derived theoretically or simulated using experimental data; this embodiment does not impose any limitations.

[0160] As an alternative implementation, the second Reynolds number is expressed as follows:

[0161] Where Re is the second Reynolds number; q c The radial heat flux density of the condensation section; l cThe length of the condensation section; μ l h is the dynamic viscosity of the gas liquefying into a liquid medium in the condensation section. fg It is the latent heat of vaporization of the liquid.

[0162] The second Reynolds number is a parameter used to calculate the heat transfer coefficient of the condensing section; the second Reynolds number can characterize the stability of the heat transfer medium flow during the heat release process in the condensing section. The calculation principle of the second Reynolds number is the same as that of the first Reynolds number, and will not be repeated in this embodiment; there are many methods to determine the second Reynolds number, and no limitation is made in this embodiment.

[0163] Optionally, the radial heat flux density of the condensing section, the length of the condensing section, the latent heat of vaporization of the liquid, and the dynamic viscosity of the liquid can be obtained from the attribute data table and input into the preset formula (8) to calculate the second Reynolds number.

[0164] As an optional implementation, the third attribute data includes: the kinematic viscosity of the medium and the thermal conductivity of the medium; the heat transfer coefficient of the condensation section is expressed as follows:

[0165] Among them, h c v is the heat transfer coefficient of the condensing section. e k is the kinematic viscosity of the liquid; l denoted as , where is the thermal conductivity of the liquid; Re is the second Reynolds number; g is the acceleration due to gravity; and the liquid is the medium corresponding to the condensation section in the sucker rod heat pipe.

[0166] Optionally, the second Reynolds number, the kinematic viscosity of the liquid medium, and the thermal conductivity of the liquid medium can be input into a preset formula (9) to accurately calculate the heat transfer coefficient of the condensing section. The heat transfer coefficient of the condensing section can also be calculated in other ways, which are not limited in this embodiment.

[0167] In this embodiment, the attribute data includes: third attribute data, which includes: the kinematic viscosity and thermal conductivity of the medium in the sucker rod heat pipe, including: the heat transfer coefficient within the sucker rod heat pipe, including the heat transfer coefficient of the condensation section; determining the heat transfer coefficient within the sucker rod heat pipe based on the attribute data includes: calculating the second Reynolds number of the liquid film flow in the evaporation section of the condensation section; determining the heat transfer coefficient of the condensation section based on the second Reynolds number and the third attribute data. Calculating the heat transfer coefficient of the condensation section using the second Reynolds number and the third attribute data takes into account the influence of flow characteristics and the physical properties of the medium on the heat transfer process, thus enabling a more accurate calculation of the heat transfer coefficient of the condensation section.

[0168] In this embodiment, the second Reynolds number is expressed as follows: Where Re is the second Reynolds number; q c The radial heat flux density of the condensation section; l cThe length of the condensation section; μ l h is the dynamic viscosity of the gas liquefying into a liquid medium in the condensation section. fg This represents the latent heat of vaporization of the liquid. This pre-defined formula allows for a better characterization of the effect of dynamic viscosity on the second Reynolds number, resulting in a more accurate second Reynolds number and providing an effective method for its calculation.

[0169] In this embodiment, the third attribute data includes: the kinematic viscosity of the medium and the thermal conductivity of the medium; the heat transfer coefficient of the condensation section is expressed as follows: Among them, h c v is the heat transfer coefficient of the condensing section. e k is the kinematic viscosity of the liquid; l Let be the thermal conductivity of the liquid; Re be the second Reynolds number; g be the acceleration due to gravity; and the liquid be the medium corresponding to the condensation section in the sucker rod heat pipe. This preset formula characterizes the kinematic viscosity of the liquid medium and the relationship between the second Reynolds number and the heat transfer coefficient of the condensation section, thereby enabling a more accurate calculation of the heat transfer coefficient of the condensation section.

[0170] As an optional implementation, based on the above embodiments, the total thermal resistance of the process from the heat-absorbing section to the wellhead of the target wellbore is calculated according to the heat transfer coefficient within the sucker rod heat pipe, including:

[0171] Based on the thermal resistance of each sub-path in the heat transfer path; the sub-paths include: from the heat transfer medium in the heat absorption section of the tubing annular space to the outer wall of the sucker rod heat pipe in the heating section; from the outer wall of the sucker rod heat pipe in the heating section to the inner wall; from the inner wall of the sucker rod heat pipe in the heating section to the heat transfer medium in the liquid pool of the sucker rod heat pipe; from the heating section of the sucker rod heat pipe to the heat dissipation section; from the medium in the condensation section of the sucker rod heat pipe to the inner wall of the condensation section; from the inner wall of the condensation section of the sucker rod heat pipe to the outer wall; and from the outer wall of the condensation section of the sucker rod heat pipe to the heat transfer medium in the heat release section of the tubing annular space; the thermal resistances corresponding to each sub-path are summed to obtain the total thermal resistance.

[0172] Specifically, as shown in Figure 1, the following thermal resistances can be calculated sequentially: the heat transfer resistance R1 from the heat-absorbing section of the tubing heat pipe to the outer wall of the heating section sucker rod heat pipe; the thermal conductivity resistance R2 from the outer wall to the inner wall of the heating section sucker rod heat pipe; the heat transfer resistance R3 from the inner wall of the heating section sucker rod heat pipe to the heat transfer medium in the liquid pool of the heating section sucker rod heat pipe; the heat transfer resistance R4 from the heating section to the heat dissipation section of the sucker rod heat pipe; the heat transfer resistance R5 from the medium in the condensation section of the sucker rod heat pipe to the inner wall of the condensation section; the thermal conductivity resistance R6 from the inner wall to the outer wall of the condensation section of the sucker rod heat pipe; and the heat transfer resistance R7 from the outer wall of the condensation section of the sucker rod heat pipe to the heat transfer medium in the annular space of the tubing. These thermal resistances are then summed to obtain the total thermal resistance. The heat transfer medium in the annular space of the tubing and on the outer wall of the sucker rod heat pipe can be an oil-water mixture.

[0173] Alternatively, the total thermal resistance R is calculated as shown in formula (10):

[0174] Where k represents the total number of sub-paths; R n This represents the thermal resistance value corresponding to each sub-path; n indicates that the calculation starts from the n0th sub-path. For example, when n0 = 1 and k = 7, it means calculating the sum of the thermal resistances from the 1st sub-path to the 7th sub-path.

[0175] Optionally, the heat transfer resistance R 换热 It can be calculated according to formula (11):

[0176] Where d is the cross-sectional length of the heat transfer surface; L represents the longitudinal length of the heat conduction surface; h represents the heat transfer coefficient between the heat conduction surfaces; and π is pi.

[0177] Specifically, based on the calculated heat transfer coefficient h of the outer wall of the sucker rod heat pipe and the annular space of the oil pipe... e,o The d value is obtained by identifying the field corresponding to the outer diameter of the sucker rod heat pipe in the attribute data table. i And obtain L by identifying the corresponding field for the length of the heat absorption section of the sucker rod heat pipe in the attribute data table. e By inputting the above data into the preset formula (11), the heat transfer resistance R1 of the heat transfer medium in the annular space of the oil pipe to the outer wall of the sucker rod heat pipe in the heating section can be calculated.

[0178] Among them, h e,o The calculation can be referenced from formula (12): h e,o =3.66×λ / D e (12)

[0179] Where λ is the thermal conductivity of the heat transfer medium in the annular space between the outer wall of the sucker rod heat pipe and the oil pipe. e The equivalent diameter of the annular space between the sucker rod heat pipe and the oil pipe can be calculated according to formula (13).

[0180] Among them, D i d is the inner diameter of the oil pipe. o Sucker rod heat pipe outer diameter.

[0181] Specifically, the heat transfer coefficient h of the heat transfer medium in the liquid pool of the heating section from the inner wall of the sucker rod heat pipe to the heat transfer medium in the heating section of the sucker rod heat pipe is calculated. e,i ; and in the attribute data table, identify the field corresponding to the outer diameter of the sucker rod heat pipe to obtain d. i And obtain L by identifying the corresponding field for the length of the heat absorption section of the sucker rod heat pipe in the attribute data table. eThe data is input into the preset formula (11) to calculate the heat transfer resistance R3 of the heat transfer medium in the liquid pool of the heating section from the inner wall of the sucker rod heat pipe to the heating section of the sucker rod heat pipe.

[0182] Among them, h e,i The calculation can be referenced in formula (14): h e,i =3.66×λ e / d i (14)

[0183] Where, λ e d is the thermal conductivity of the liquid medium in the heat pipe pool of the sucker rod; i Sucker rod heat pipe outer diameter.

[0184] Specifically, the heat transfer coefficient h from the medium in the condensing section of the sucker rod heat pipe to the inner wall of the condensing section is calculated. c,i ; Identify the field corresponding to the outer diameter of the sucker rod heat pipe in the attribute data table to obtain d i And obtain L by identifying the corresponding field for the length of the condenser section of the sucker rod heat pipe in the attribute data table. c The heat transfer resistance R5 from the medium in the condensing section of the sucker rod heat pipe to the inner wall of the condensing section can be calculated from the above data according to the above preset formula (11).

[0185] In this heat pipe, the condensation section contains a gaseous medium and a liquefied liquid medium; the heating section also contains a liquid medium and an evaporated gaseous medium. Therefore, the heat transfer coefficient h... c,i equal to h e,i .

[0186] Specifically, the heat transfer coefficient h from the outer wall of the condenser section of the sucker rod heat pipe to the annular space of the tubing is calculated. c,o ; Identify the field corresponding to the outer diameter of the sucker rod heat pipe in the attribute data table to obtain d i And obtain L by identifying the corresponding field for the length of the condenser section of the sucker rod heat pipe in the attribute data table. c The above data can be input into the preset formula (11) to calculate the heat transfer resistance R7 from the outer wall of the condensing section of the sucker rod heat pipe to the annular space of the oil pipe.

[0187] In the condensation section, both the outer wall of the sucker rod heat pipe heating element and the annular heat transfer medium of the oil pipe are oil-water mixtures; therefore, h can be directly taken as h. c,o =h e,o .

[0188] Optionally, the thermal resistance from the outer wall to the inner wall of the sucker rod heat pipe in the heating section, and the thermal resistance from the inner wall to the outer wall of the sucker rod heat pipe in the condensing section, can be calculated according to formula (15):

[0189] Among them, R 导 Indicates thermal resistance; λ w This represents the thermal conductivity of the heat pipe wall corresponding to the sucker rod.

[0190] Specifically, when calculating the thermal resistance from the outer wall to the inner wall of the heating section of the sucker rod heat pipe, L is taken as the length L of the heating section of the sucker rod heat pipe. e When calculating the thermal resistance from the inner wall to the outer wall of the condensing section of the sucker rod heat pipe, L is taken as the length of the condensing section of the sucker rod heat pipe. c The outer wall to the inner wall of the heating section of the sucker rod heat pipe and the inner wall to the outer wall of the condensing section of the sucker rod heat pipe are the same pipe wall. Therefore, they correspond to d0 and d... i , λ w The acquisition method is the same, so it will not be described again. The above L... e Or L c ,d0,d i , λ w By inputting into the preset formula (15), the thermal resistance R2 from the outer wall to the inner wall of the heating section of the sucker rod heat pipe or the thermal resistance R6 from the inner wall to the outer wall of the condensing section of the sucker rod heat pipe can be calculated.

[0191] As an optional implementation, if the flow path is from the heating section to the heat dissipation section of the sucker rod heat pipe, the thermal resistance from the heating section to the heat dissipation section of the sucker rod heat pipe is expressed as follows:

[0192] Where R4 is the thermal resistance from the heating section to the heat dissipation section of the sucker rod heat pipe, and G r P is the Grasov number; r L is the Prandtl number; a K represents the length of the convection section. ha denoted as , where is the thermal conductivity of the medium.

[0193] Among them, G r This characterizes the resistance within the heat transfer medium that hinders flow during convective heat transfer. It can be calculated using formula (17) as follows:

[0194] Where, ρ an For the convection section inside the sucker rod heat pipe at the average temperature The density of the sample is expressed in kg / m³. 3 μ an For the gas medium in the convection section of the sucker rod heat pipe at the average temperature The viscosity is given by mPa·s; β is the volume change coefficient, which, under ideal conditions, is equal to the reciprocal of the absolute temperature of the gas; g is the acceleration due to gravity, in m / s². 2 .

[0195] Among them, Pr These are parameters that influence convective heat transfer through the physical properties of the heat transfer medium itself. They can be calculated using formula (18), as follows:

[0196] Among them, C an For the heat transfer medium of the sucker rod heat pipe at the average temperature The specific heat capacity below.

[0197] Specifically, first obtain the condensation section length L from the attribute data table. c and heating section length L e ; through L e Integral length range over oil temperature profile with respect to L e The ratio of lengths was calculated. Accordingly, through L c Integral length range over oil temperature profile with respect to L c The ratio of lengths was calculated. Then calculate at the average temperature Viscosity μ an Density ρ an Specific heat capacity C an Then obtain the condensation section length L from the attribute data table. a , constant volume change coefficient β, gravitational acceleration g, thermal conductivity K of the heat transfer medium in the sucker rod heat pipe ha The above data can be input into the preset formula (17) to calculate the Grasov number G. r ; at the average temperature Viscosity μ an And C an The Prandtl number P can be obtained by inputting the specific heat capacity into the preset formula (18). r Finally, the Grasov number G can be calculated. r The Glasov number G is calculated. r The thermal conductivity K of the heat transfer medium in the sucker rod heat pipe ha and the length L of the condensation section a Input the formula (16) into the preset formula to calculate the thermal resistance R4 from the heating section to the heat dissipation section.

[0198] It is understandable that there may be multiple methods for calculating the thermal resistance of each path in this embodiment, and no limitation is made in this embodiment.

[0199] In this embodiment, the total thermal resistance of the sucker rod heat pipe from the heat-absorbing section to the wellhead of the target wellbore is calculated based on the heat transfer coefficient within the heat transfer pipe. This includes: calculating the thermal resistance corresponding to each sub-path in the heat transfer path; the sub-paths include: from the heat transfer medium in the heat-absorbing section of the tubing annular space to the outer wall of the heating section of the sucker rod heat pipe; from the outer wall of the heating section of the sucker rod heat pipe to the inner wall; from the inner wall of the heating section of the sucker rod heat pipe to the heat transfer medium in the liquid pool of the heating section of the sucker rod heat pipe; from the heating section of the sucker rod heat pipe to the heat dissipation section; from the medium in the condensation section of the sucker rod heat pipe to the inner wall of the condensation section; from the inner wall of the condensation section of the sucker rod heat pipe to the outer wall; and from the outer wall of the condensation section of the sucker rod heat pipe to the heat transfer medium in the heat-releasing section of the tubing annular space. The thermal resistances corresponding to each sub-path are summed to obtain the total thermal resistance. By dividing the heat transfer path in detail and calculating the thermal resistance of each sub-path, the heat transfer efficiency of the sucker rod heat pipe can be evaluated more accurately.

[0200] In this embodiment, if the flow path is from the heating section to the heat dissipation section of the sucker rod heat pipe, the thermal resistance from the heating section to the heat dissipation section of the sucker rod heat pipe is expressed as follows: Where R4 is the thermal resistance from the heating section to the heat dissipation section of the sucker rod heat pipe, and G r P is the Grasov number; r L is the Prandtl number; a K represents the length of the convection section. ha Let be the thermal conductivity of the medium. Introducing the Grashof number and Prandtl number into the calculation of thermal resistance allows for a more comprehensive consideration of the influence of the physical characteristics of the heat transfer medium and its internal resistance on the convective heat transfer process; thus, a more accurate thermal resistance can be obtained from the heating section to the heat dissipation section of the sucker rod heat pipe.

[0201] As an optional implementation, based on the above embodiments, the saturated temperature distribution sequence data includes first saturated temperature distribution sequence data and second saturated temperature distribution sequence data;

[0202] Determining the saturated temperature distribution sequence data inside the sucker rod heat pipe includes: acquiring the first pressure distribution sequence data inside the liquid pool of the sucker rod heat pipe; determining the first saturated temperature distribution sequence data based on the first preset mapping function and the first pressure distribution sequence data, wherein the first preset mapping function is a mapping function between saturated temperature and first pressure; and acquiring the second saturated temperature distribution sequence data collected by a temperature sensor.

[0203] The first saturation temperature is the saturation temperature of the section from the lower end of the sucker rod heat pipe to the surface of the heat transfer medium in the liquid pool inside the heat pipe.

[0204] Optionally, the first preset mapping function T0(x) is expressed as in formula (19):

[0205] Where x represents the value of the corresponding first pressure distribution sequence data; k represents the slope of the curve; b represents the intercept of the curve; this formula is determined by fitting experimental data, and the first preset mapping function can also be determined by other methods, which is not limited in this embodiment.

[0206] The second saturated temperature distribution sequence data is the saturated temperature from the lower end of the sucker rod heat pipe to the liquid level of the heat transfer medium in the liquid pool inside the heat pipe, and then to the condensation section. It can be obtained by reading the temperature sensor interface data in the sensor device installed on the sucker rod heat pipe in real time. The server can read the second saturated temperature distribution sequence data corresponding to the sensor device data interface in real time and save it to the attribute data table.

[0207] Optionally, the second saturation temperature distribution sequence data is represented as shown in formula (20): T1(x)=T v L p <x<L (20)

[0208] Optionally, experimental data on the pressure at different saturation temperatures can be collected from the lower end of the heat pipe to the surface of the heat transfer medium in the liquid pool inside the heat pipe; then, the pressure data at different saturation temperatures can be fitted, and the fitting result can be used as the first preset mapping function. There are various methods for establishing the first preset mapping function, and this embodiment does not limit it.

[0209] Optionally, the first pressure distribution sequence data calculated according to the preset formula (2) can be obtained; then the first pressure distribution sequence data can be input into the first preset mapping function as shown in formula (19) to calculate the first saturation temperature distribution sequence data.

[0210] As an optional implementation, based on the above embodiments, the temperature distribution sequence data corresponding to the wall of the sucker rod heat pipe includes the temperature distribution sequence data corresponding to the first section of the pipe wall; the temperature distribution sequence data corresponding to the first section of the pipe wall is the temperature distribution sequence data of the section from the lower end of the sucker rod heat pipe to the liquid surface of the heat transfer medium in the liquid pool inside the heat pipe;

[0211] The temperature distribution sequence data corresponding to the first section of the pipe wall is represented as follows: T2(x)=T0(x)+Q e / h e 0 < x ≤ L p (twenty one)

[0212] Where T2(x) is the temperature distribution sequence data corresponding to the first section of the pipe wall; Q e h is the heat transfer rate of the heating section of the heat pipe. e L is the heat transfer coefficient from the inner wall of the heat pipe to the surface of the heat transfer medium in the liquid pool inside the heat pipe; pThe height of the liquid pool inside the heat pipe of the sucker rod; T0(x) is the first saturation temperature distribution sequence data.

[0213] Understandably, according to the law of conservation of energy, the heat energy absorbed should equal the heat energy released. Therefore, the temperature change within the heat pipe of the sucker rod is the same, and the total thermal resistance is the same. Therefore, Q... hp =Q e .

[0214] The temperature distribution sequence data corresponding to the first section of the pipe wall can be represented as the sum of the change in the first saturation temperature and the amount of absorbed heat in the section from the lower end of the sucker rod heat pipe to the liquid surface of the heat transfer medium in the liquid pool inside the heat pipe.

[0215] Specifically, the calculated first saturation temperature sequence distribution and the calculated heat transfer coefficient h of the sucker rod heat pipe heating section can be used as the reference. e And Q e The temperature distribution sequence data corresponding to the first section of the pipe wall can be calculated by inputting the data into the preset formula (21). Among them, Q e / h e It can be characterized as the change in the amount of heat absorbed.

[0216] As an optional implementation, based on the above embodiments, the temperature distribution sequence data corresponding to the wall of the sucker rod heat pipe includes the temperature distribution sequence data corresponding to the second section of the pipe wall; the temperature distribution sequence data corresponding to the second section of the pipe wall is the temperature distribution sequence data from the liquid surface of the heat transfer medium in the liquid pool inside the sucker rod heat pipe to the evaporation section.

[0217] The temperature distribution sequence data corresponding to the pipe wall of the second pipe wall heating section is shown below: T3(x)=T1(x)+Q e / h f L p <x≤L e (twenty two)

[0218] Where T3(x) represents the temperature distribution sequence data corresponding to the second section of the pipe wall; Q e L is the heat transfer rate of the heating section of the heat pipe. p h is the height of the liquid pool inside the heat pipe of the sucker rod. f The position of the heat transfer medium in the liquid pool inside the heat pipe is relative to the heat transfer coefficient of the evaporation section; L e T1(x) represents the length of the heating section of the sucker rod heat pipe; T1(x) represents the second saturation temperature distribution sequence data.

[0219] The temperature distribution sequence data corresponding to the second section of the pipe wall can be represented as the sum of the second saturation temperature above the liquid surface of the heat transfer medium in the heat transfer medium pool inside the sucker rod heat pipe and the change in heat absorbed when evaporating into gas.

[0220] Specifically, the calculated second saturation temperature sequence distribution and the calculated heat transfer coefficient h of the heating section are... f And Q e Inputting this into the preset formula (22) allows for the calculation of the temperature distribution sequence data corresponding to the second section of the pipe wall. Where Q... e / h f This represents the change in heat absorbed from above the liquid level of the heat transfer medium in the heat transfer medium pool inside the sucker rod heat pipe to above the heating section.

[0221] As an optional implementation, based on the above embodiments, the temperature distribution sequence data corresponding to the heat pipe wall of the sucker rod includes the temperature distribution sequence data corresponding to the third section of the pipe wall; the temperature distribution sequence data corresponding to the third section of the pipe wall is the temperature distribution sequence data of the condensation section;

[0222] The temperature distribution sequence data corresponding to the heating section of the pipe wall in the third section is shown below: T4(x)=T1(x)-Q c / h c L e +L a ≤L (23)

[0223] Where T4(x) represents the temperature distribution sequence data corresponding to the pipe wall of the third pipe wall heating section; Q c h is the heat transfer rate of the condenser section of the sucker rod heat pipe. c L is the heat transfer coefficient of the condensing section. e Indicates the length of the heating section of the sucker rod heat pipe; L a denoted by ; L represents the total length of the heat pipe convection section of the sucker rod; T1(x) represents the second saturation temperature distribution sequence data.

[0224] Among them, the temperature distribution sequence data corresponding to the third section of the pipe wall can be represented as the difference between the second saturated temperature distribution data of the condensation section of the sucker rod heat pipe and the change in heat released in the condensation section.

[0225] Optionally, the calculated first saturation temperature sequence distribution and the calculated heat transfer coefficient h of the condensing section are used as input. c Inputting the data into the preset formula (23) can calculate the temperature distribution sequence data corresponding to the third section of the pipe wall; where Q c / h f This can be characterized as the change in heat released during the condensation phase. Similarly, Q hp =Q c .

[0226] As an optional implementation, based on the above embodiments, it further includes:

[0227] The temperature distribution sequence data based on the heat pipe wall of the sucker rod includes the temperature distribution sequence data corresponding to the fourth segment, which is the temperature distribution sequence data from the upper end of the heating section to the upper end of the convection section.

[0228] The temperature distribution sequence data corresponding to the fourth pipe wall is shown below: T5(x) = T1(x), L e <x≤L e +L a (twenty four)

[0229] Where T5(x) represents the temperature distribution sequence data corresponding to the fourth pipe wall segment; L e Indicates the length of the heating section of the sucker rod heat pipe; L a T1(x) represents the length of the convection section of the heat pipe in the sucker rod; T1(x) is the second saturation temperature distribution sequence data.

[0230] Understandably, since there is no other heat absorption or release in the convection section, the temperature distribution sequence data corresponding to the fourth pipe wall can be directly characterized by the second saturation temperature sequence distribution.

[0231] In this embodiment, the saturated temperature distribution sequence data includes first saturated temperature distribution sequence data and second saturated temperature distribution sequence data. Determining the saturated temperature distribution sequence data within the sucker rod heat pipe includes: acquiring first pressure distribution sequence data within the liquid pool of the sucker rod heat pipe; determining first saturated temperature distribution sequence data based on a first preset mapping function and the first pressure distribution sequence data, wherein the first preset mapping function is a mapping function between saturated temperature and first pressure; and acquiring second saturated temperature distribution sequence data collected by a temperature sensor. Based on the physical relationship between saturated temperature and pressure, a mapping relationship is established between the first pressure distribution sequence data and the first saturated temperature distribution sequence data. This mapping function is determined based on thermodynamic principles and can accurately reflect the influence of pressure changes on saturated temperature, thereby obtaining accurate first saturated temperature distribution sequence data.

[0232] In this embodiment, the temperature distribution sequence data corresponding to the heat pipe wall of the sucker rod includes the temperature distribution sequence data corresponding to the first section of the pipe wall; the temperature distribution sequence data corresponding to the first section of the pipe wall is the temperature distribution sequence data of the section from the lower end of the heat pipe to the liquid surface of the heat transfer medium in the liquid pool inside the heat pipe; the temperature distribution sequence data corresponding to the first section of the pipe wall is expressed as follows: T2(x)=T0(x)+Q e / h e 0 < x ≤ L p Where T2(x) is the temperature distribution sequence data corresponding to the first section of the pipe wall; Q e h is the heat transfer rate of the heating section of the heat pipe. eL is the heat transfer coefficient from the inner wall of the heat pipe to the surface of the heat transfer medium in the liquid pool inside the heat pipe; p The height of the liquid pool inside the heat pipe of the sucker rod is denoted as T0(x); T0(x) represents the first saturated temperature distribution sequence data. By obtaining the accurate heat transfer coefficient and transmission rate of the heating section, the temperature distribution sequence data corresponding to the first section of the pipe wall can be calculated more accurately; the influence of the medium absorbing heat in the heating section on the temperature distribution sequence data of the first section of the pipe wall can be intuitively characterized.

[0233] In this embodiment, the temperature distribution sequence data corresponding to the wall of the sucker rod heat pipe includes the temperature distribution sequence data corresponding to the second section of the pipe wall; the temperature distribution sequence data corresponding to the second section of the pipe wall is the temperature distribution sequence data from the liquid surface of the heat transfer medium in the liquid pool inside the sucker rod heat pipe to the evaporation section; the temperature distribution sequence data corresponding to the heating section of the second pipe wall is represented as follows: T3(x)=T1(x)+Q e / h f L p <x≤L e Q e L is the heat transfer rate of the heating section of the heat pipe. p h is the height of the liquid pool inside the heat pipe of the sucker rod. f The position of the heat transfer medium in the liquid pool inside the heat pipe is relative to the heat transfer coefficient of the evaporation section; L e T1(x) represents the length of the heating section of the sucker rod heat pipe; T1(x) represents the second saturated temperature distribution sequence data. The calculated precise temperature distribution sequence data corresponding to the second pipe wall represents the heat transfer coefficient and transmission rate from the liquid surface of the heat transfer medium in the liquid pool within the sucker rod heat pipe to the evaporation section. This allows for a more accurate calculation of the temperature distribution sequence data corresponding to the second pipe wall; it also intuitively characterizes the impact of medium evaporation on the temperature distribution sequence data of the second pipe wall.

[0234] In this embodiment, the temperature distribution sequence data corresponding to the heat pipe wall of the sucker rod includes the temperature distribution sequence data corresponding to the third section of the pipe wall; the temperature distribution sequence data corresponding to the third section of the pipe wall is the temperature distribution sequence data of the condensation section; the temperature distribution sequence data corresponding to the heating section of the third section of the pipe wall is represented as follows: T4(x)=T1(x)-Q c / h c L e +L a ≤L where T4(x) is the temperature distribution sequence data corresponding to the heating section of the third pipe wall; Q c h is the heat transfer rate of the condenser section of the sucker rod heat pipe. c L is the heat transfer coefficient of the condensing section. e Indicates the length of the heating section of the sucker rod heat pipe; L aThe length of the convection section of the sucker rod heat pipe is represented by ; L represents the total length of the sucker rod heat pipe; T1(x) is the second saturated temperature distribution sequence data. Based on the accurate heat transfer coefficient and transmission rate of the condensation section, the temperature distribution sequence data corresponding to the third pipe wall can be calculated more precisely; this intuitively represents the impact of heat release in the condensation section on the temperature distribution sequence data of the third pipe wall. Furthermore, by calculating the temperature distribution sequence data corresponding to the first, second, and third pipe walls, the distribution of the pipe wall under different heat transfer conditions is intuitively reflected; knowing the changes in pipe wall temperature, the heating of the tubing can be effectively controlled to prevent wax deposition in crude oil near the wellhead. The pipe wall temperature can also provide a basis for the structural design of the sucker rod heat pipe. For example, based on the changes in pipe wall temperature, the lengths of the heating and condensation sections of the sucker rod heat pipe, as well as the thickness and shape of the pipe wall, can be adjusted to optimize the heat transfer performance of the sucker rod heat pipe; improved heat transfer performance of the sucker rod heat pipe also helps prevent wax deposition in crude oil near the wellhead.

[0235] As can be understood, the formula above also shows that the wall temperature of the heating section of the sucker rod heat pipe increases with the increase of heat flow, while the wall temperature of the condensation section decreases with the increase of condensation heat transfer. Therefore, the heat input to the heating section of the sucker rod heat pipe and the condensation conditions of the condensation section are the factors that have the greatest impact on the heat pipe wall temperature.

[0236] In this embodiment, the temperature distribution sequence data corresponding to the heat pipe wall of the sucker rod includes the temperature distribution sequence data corresponding to the fourth segment. The temperature distribution sequence data corresponding to the fourth segment of the pipe wall is the temperature distribution sequence data from the upper end of the heating section to the upper end of the convection section. The temperature distribution sequence data corresponding to the fourth segment of the pipe wall is represented as follows: T5(x) = T1(x), L e <x≤L e +L a Where T5(x) represents the temperature distribution sequence data corresponding to the fourth pipe wall segment; L e Indicates the length of the heating section of the sucker rod heat pipe; L a The length of the heat pipe convection section is represented by T1(x); T1(x) represents the second saturation temperature distribution sequence data. The second saturation temperature can effectively characterize the temperature distribution data of the fourth section of the pipe wall; by accurately measuring and analyzing the temperature distribution data of the fourth section of the pipe wall, the heat transfer performance of the heat pipe convection section can be evaluated more accurately.

[0237] As an optional implementation, basic oil well data can be acquired, and wellbore temperature distribution data before heating with the sucker rod heat pipe can be obtained based on the basic oil well parameters. The depth parameters of the sucker rod heat pipe can then be designed based on the obtained wellbore temperature distribution data and crude oil wax deposition point parameters. The basic oil well data includes: well depth, surface temperature, geothermal gradient, tubing specifications, casing specifications, thermal conductivity, mass flow rate of the heat transfer medium in the wellbore, density and viscosity of the heat transfer medium, and wax deposition point temperature of the heat transfer medium.

[0238] Specifically, the corresponding well number is input, and the corresponding well basic data is matched in the database based on the well number. The water equivalent of the heat transfer medium is determined based on the mass flow rate of the heat transfer medium in the well basic parameters; the wellbore temperature distribution data sequence is determined based on the water equivalent data and the well basic parameters; the wellbore depth corresponding to the point where the oil wax deposition point parameter is the same as the wellbore temperature distribution data sequence is used as the depth of the sucker rod heat pipe in the wellbore, i.e., the sucker rod heat pipe depth parameter, and heating by the sucker rod heat pipe is used to prevent the crude oil in the tubing from wax deposition.

[0239] Optionally, based on the mass of the heat transfer medium, the water equivalent of the heat transfer medium is calculated as shown in formula (25): W=M1×C1+M g ×C g (25)

[0240] Where C1 is the specific heat of the produced liquid, in J / (kg·℃); C g The specific heat of the produced gas is expressed in J / (kg·℃); M l The mass flow rate of the well fluid is expressed in kg / s; M g M1 represents the mass flow rate of gas in the wellbore, expressed in kg / s. Optionally, when the heat transfer medium contains only gas, M1 can be 0; when the heat transfer medium contains only liquid, M1 can be 0. g It can be 0.

[0241] Based on the obtained water equivalent data of the heat transfer medium and the surface temperature, temperature gradient, and thermal conductivity, the wellbore temperature distribution data is obtained through the following formula (26):

[0242] Where T is the temperature of the crude oil at depth x in the tubing, in °C; W is the water equivalent, in W / °C; k1 is the overall heat transfer coefficient, in W / (m·°C); th is the surface temperature, in °C; m is the formation temperature gradient, in °C / m; H is the oil layer depth, in m; and x is the calculation well depth, in m.

[0243] Therefore, the solution of this invention can accurately obtain parameters such as the insertion depth of the sucker rod heat pipe heating string, the heat transfer rate, and the temperature and pressure distribution inside the string after implementation. It can effectively determine the heating parameters of the sucker rod heat pipe. Combined with the implementation of the heating string, it can replace the existing high-energy-consuming hot wire heating process and reduce the heating cost of auxiliary lifting in oil fields.

[0244] Figure 4 is a schematic diagram of the structure of a temperature determination device for a sucker rod heat pipe according to an embodiment of this application. In this embodiment, the sucker rod heat pipe is located in the target wellbore. The temperature determination device for the sucker rod heat pipe is located within a temperature determination equipment for the sucker rod heat pipe. The temperature determination device for the sucker rod heat pipe provided in this embodiment includes: an acquisition module 401, a determination module 402, and a calculation module 403.

[0245] The acquisition module 401 is used to acquire the attribute data of the sucker rod heat pipe in the target wellbore.

[0246] The determination module 402 is used to determine the heat transfer coefficient inside the sucker rod heat pipe based on the attribute data.

[0247] The calculation module 403 is used to calculate the total thermal resistance of the process from the heat absorption section to the wellhead of the target wellbore based on the heat transfer coefficient in the sucker rod heat pipe.

[0248] The determination module 402 is also used to determine the heat transfer rate of the sucker rod heat pipe based on the total thermal resistance.

[0249] The determination module 402 is also used to determine the saturation temperature distribution sequence data inside the sucker rod heat pipe.

[0250] The determination module 402 is also used to determine the temperature distribution sequence data corresponding to the heat pipe wall of the sucker rod based on the saturated temperature distribution sequence data, heat transfer rate and heat transfer coefficient.

[0251] Optionally, the heat transfer coefficient within the sucker rod heat pipe includes the heat transfer coefficient of the heating section; the attribute data includes the first attribute data.

[0252] Accordingly, the determination module, when determining the heat transfer coefficient within the sucker rod heat pipe based on attribute data, is specifically used for:

[0253] Acquire the first pressure distribution sequence data within the liquid pool of the sucker rod heat pipe; determine the heat transfer coefficient of the heating section based on the first attribute data and the ratio coefficient between the first pressure distribution sequence data and atmospheric pressure. The heat transfer coefficient within the sucker rod heat pipe includes the heat transfer coefficient of the heating section; the attribute data includes the first attribute data.

[0254] Optionally, the first attribute data includes: the specific heat capacity, thermal conductivity, latent heat of vaporization, dynamic viscosity, and radial heat flux density of the medium in the sucker rod heat pipe, as well as the radial heat flux density of the evaporation section corresponding to the heating section.

[0255] Accordingly, the heat transfer coefficient of the heating section is expressed as shown in formula (3).

[0256] Optionally, the heat transfer coefficient within the sucker rod heat pipe includes the heat transfer coefficient of the convection section. The attribute data includes first attribute data and second attribute data, whereby the second attribute data includes the radial heat flux density of the evaporation section corresponding to the convection section and the liquid pool height within the sucker rod heat pipe.

[0257] Accordingly, module 402, when determining the heat transfer coefficient within the sucker rod heat pipe based on attribute data, is specifically used for:

[0258] The radial heat flux density of the evaporation section corresponding to the convection section is compared with the critical heat flux density. In response to the radial heat flux density of the evaporation section corresponding to the convection section being less than the critical heat flux density, the second pressure distribution sequence data corresponding to the convection section of the sucker rod heat pipe is obtained. The heat transfer coefficient of the convection section is determined based on the ratio coefficient of the first attribute data, the second pressure distribution sequence data and atmospheric pressure. In response to the radial heat flux density of the evaporation section corresponding to the convection section being greater than or equal to the critical heat flux density, the first Reynolds number of the liquid film flow in the evaporation section of the convection section is calculated, and the heat transfer coefficient of the convection section is determined based on the first Reynolds number and the liquid pool height in the sucker rod heat pipe.

[0259] Optionally, the first Reynolds number is expressed as shown in Equation (5).

[0260] Optionally, when the radial heat flux density is greater than or equal to the critical heat flux density, the heat transfer coefficient of the convection section is expressed as shown in formula (7).

[0261] Optionally, the attribute data includes: third attribute data; optionally, the third attribute data includes: the heat transfer coefficient within the sucker rod heat pipe, including the heat transfer coefficient of the condensing section.

[0262] Accordingly, module 402, when determining the heat transfer coefficient within the sucker rod heat pipe based on attribute data, is specifically used for:

[0263] Calculate the second Reynolds number for liquid film flow in the condensation section; determine the heat transfer coefficient of the condensation section based on the second Reynolds number and the third property data.

[0264] Optionally, the second Reynolds number is expressed as shown in Equation (8).

[0265] Optionally, the third attribute data includes: the kinematic viscosity of the medium and the thermal conductivity of the medium.

[0266] Accordingly, the heat transfer coefficient of the condensing section is expressed as shown in formula (9).

[0267] Optionally, the sub-path includes: from the heat transfer medium in the heat absorption section of the tubing annular space to the outer wall of the sucker rod heat pipe in the heating section; from the outer wall of the sucker rod heat pipe in the heating section to the inner wall; from the inner wall of the sucker rod heat pipe in the heating section to the heat transfer medium in the liquid pool of the sucker rod heat pipe; from the heating section of the sucker rod heat pipe to the heat dissipation section; from the medium in the condensation section of the sucker rod heat pipe to the inner wall of the condensation section; from the inner wall of the condensation section of the sucker rod heat pipe to the outer wall; and from the outer wall of the condensation section of the sucker rod heat pipe to the heat transfer medium in the heat release section of the tubing annular space.

[0268] Accordingly, the calculation module 403, when calculating the total thermal resistance of the process from the heat-absorbing section to the wellhead of the target wellbore based on the heat transfer coefficient within the sucker rod heat pipe, is specifically used for:

[0269] The heat transfer coefficient in the sucker rod heat pipe is calculated, and the thermal resistance corresponding to each sub-path is calculated during the heat transfer from the heat absorption section to the wellhead of the target wellbore. The thermal resistances corresponding to each sub-path are summed to obtain the total thermal resistance.

[0270] Optionally, if the flow path is from the heating section to the heat dissipation section of the sucker rod heat pipe, the thermal resistance from the heating section to the heat dissipation section of the sucker rod heat pipe is expressed as shown in formula (16).

[0271] Optionally, the saturated temperature distribution sequence data includes first saturated temperature distribution sequence data and second saturated temperature distribution sequence data.

[0272] Accordingly, module 402, when determining the saturation temperature distribution sequence data inside the sucker rod heat pipe, is specifically used for:

[0273] Acquire first pressure distribution sequence data in the liquid pool of the sucker rod heat pipe; determine first saturated temperature distribution sequence data based on a first preset mapping function and the first pressure distribution sequence data, wherein the first preset mapping function is a mapping function between saturated temperature and first pressure; acquire second saturated temperature distribution sequence data collected by a temperature sensor.

[0274] Optionally, the temperature distribution sequence data corresponding to the wall of the sucker rod heat pipe includes the temperature distribution sequence data corresponding to the first section of the pipe wall; the temperature distribution sequence data corresponding to the first section of the pipe wall is the temperature distribution sequence data of the section from the lower end of the sucker rod heat pipe to the liquid surface of the heat transfer medium in the liquid pool inside the heat pipe.

[0275] Accordingly, the temperature distribution sequence data corresponding to the first section of the pipe wall is expressed as shown in formula (21).

[0276] Optionally, the temperature distribution sequence data corresponding to the wall of the sucker rod heat pipe includes the temperature distribution sequence data corresponding to the second section of the pipe wall; the temperature distribution sequence data corresponding to the second section of the pipe wall is the temperature distribution sequence data from the liquid surface of the heat transfer medium in the liquid pool inside the sucker rod heat pipe to the upper end of the heating section.

[0277] Correspondingly, the temperature distribution sequence data of the second section of the pipe wall heating section is represented as shown in formula (22).

[0278] Optionally, the temperature distribution sequence data corresponding to the heat pipe wall of the sucker rod includes the temperature distribution sequence data corresponding to the third section of the pipe wall; the temperature distribution sequence data corresponding to the third section of the pipe wall is the temperature distribution sequence data of the condensation section.

[0279] Correspondingly, the temperature distribution sequence data of the heating section of the third pipe wall is represented as shown in formula (23).

[0280] Optionally, the temperature distribution sequence data corresponding to the fourth segment is determined based on the saturated temperature distribution sequence data; the temperature distribution sequence data corresponding to the pipe wall of the fourth segment is the temperature distribution sequence data of the segment from the upper end of the heating segment to the upper end of the convection segment.

[0281] Correspondingly, the temperature distribution sequence data corresponding to the fourth pipe wall is represented as shown in formula (24).

[0282] Figure 5 is a schematic diagram of the structure of an electronic device provided in an embodiment of this application. As shown in Figure 5, the electronic device 50 provided in this embodiment includes: a processor 501 and a memory 502 communicatively connected to the processor 501. In a specific implementation, at least one processor 501 executes computer execution instructions stored in the memory 502, causing at least one processor 501 to perform the above-described method.

[0283] The specific implementation process of processor 501 can be found in the above method embodiments, and its implementation principle and technical effect are similar. It will not be repeated here.

[0284] In the above embodiments, it should be understood that the processor can be a Central Processing Unit (CPU), or other general-purpose processors, digital signal processors (DSPs), application-specific integrated circuits (ASICs), etc. The general-purpose processor can be a microprocessor or any conventional processor. The steps of the method disclosed in this invention can be directly implemented by a hardware processor, or implemented by a combination of hardware and software modules within the processor.

[0285] The memory may include random access memory (RAM) and may also include non-volatile memory (NVM), such as at least one disk storage device.

[0286] The bus can be an Industry Standard Architecture (ISA) bus, a Peripheral Component Interconnect (PCI) bus, or an Extended Industry Standard Architecture (EISA) bus, etc. Buses can be categorized as address buses, data buses, control buses, etc. For ease of illustration, the buses shown in the accompanying drawings are not limited to a single bus or a single type of bus.

[0287] This application also provides a computer program product, including a computer program that, when executed by a processor, implements the above-described method.

[0288] This application also provides a computer-readable storage medium storing computer-executable instructions, which, when executed by a processor, implement the above-described method.

[0289] It should be noted that, for the sake of simplicity, the foregoing method embodiments are all described as a series of actions. However, those skilled in the art should understand that this application is not limited to the described order of actions, as some steps may be performed in other orders or simultaneously according to this application. Furthermore, those skilled in the art should also understand that the embodiments described in the specification are all optional embodiments, and the actions and modules involved are not necessarily essential to this application.

[0290] It should be further noted that although the steps in the flowchart are shown sequentially according to the arrows, these steps are not necessarily executed in the order indicated by the arrows. Unless explicitly stated herein, there is no strict order restriction on the execution of these steps, and they can be executed in other orders. Moreover, at least some steps in the flowchart may include multiple sub-steps or multiple stages. These sub-steps or stages are not necessarily completed at the same time, but can be executed at different times. The execution order of these sub-steps or stages is not necessarily sequential, but can be performed alternately or in turn with other steps or at least some of the sub-steps or stages of other steps.

[0291] It should be understood that the above-described device embodiments are merely illustrative, and the device of this application can also be implemented in other ways. For example, the division of units / modules in the above embodiments is only a logical functional division, and there may be other division methods in actual implementation. For example, multiple units, modules, or components may be combined, or integrated into another system, or some features may be ignored or not executed.

[0292] Furthermore, unless otherwise specified, the functional units / modules in the various embodiments of this application can be integrated into one unit / module, or each unit / module can exist physically separately, or two or more units / modules can be integrated together. The integrated units / modules described above can be implemented in hardware or as software program modules.

[0293] When integrated units / modules are implemented in hardware, the hardware can be digital circuits, analog circuits, etc. The physical implementation of the hardware structure includes, but is not limited to, transistors, memristors, etc. Unless otherwise specified, the processor can be any suitable hardware processor, such as a CPU, GPU, FPGA, DSP, and ASIC, etc. Unless otherwise specified, the storage unit can be any suitable magnetic or magneto-optical storage medium, such as Resistive Random Access Memory (RRAM), Dynamic Random Access Memory (DRAM), Static Random Access Memory (SRAM), Enhanced Dynamic Random Access Memory (EDRAM), High-Bandwidth Memory (HBM), Hybrid Memory Cube (HMC), etc.

[0294] If the integrated unit / module is implemented as a software program module and sold or used as an independent product, it can be stored in a computer-readable storage device (CMD). Based on this understanding, the technical solution of this application, in essence, or the part that contributes to the prior art, or all or part of the technical solution, can be embodied in the form of a software product. This computer software product is stored in a memory and includes several instructions to cause a computer device (which may be a personal computer, server, or network device, etc.) to execute all or part of the steps of the methods of the various embodiments of this application. The aforementioned memory includes various media capable of storing program code, such as a USB flash drive, read-only memory (ROM), random access memory (RAM), portable hard drive, magnetic disk, or optical disk.

[0295] In the above embodiments, the descriptions of each embodiment have their own emphasis. For parts not described in detail in a certain embodiment, please refer to the relevant descriptions of other embodiments. The technical features of the above embodiments can be combined arbitrarily. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as these combinations of technical features do not contradict each other, they should be considered within the scope of this specification. Those skilled in the art, upon considering the specification and practicing the invention disclosed herein, will readily conceive of other embodiments of this application. This application is intended to cover any variations, uses, or adaptations of this application that follow the general principles of this application and include common knowledge or customary technical means in the art not disclosed in this application. The specification and embodiments are considered exemplary only, and the true scope and spirit of this application are indicated by the following claims. It should be understood that this application is not limited to the precise structures described above and shown in the drawings, and various modifications and changes can be made without departing from its scope. The scope of this application is limited only by the appended claims.

Claims

1. A method for determining the temperature of a sucker rod heat pipe, wherein the sucker rod heat pipe is located in a target wellbore, characterized in that, The method includes: Obtain the attribute data of the sucker rod heat pipe in the target wellbore, and determine the heat transfer coefficient inside the sucker rod heat pipe based on the attribute data; Calculate the total thermal resistance of the process from the heat absorption section to the wellhead of the target wellbore in the sucker rod heat pipe based on the heat transfer coefficient in the sucker rod heat pipe. Based on the total thermal resistance, the heat transfer rate of the sucker rod heat pipe is determined; Determine the saturation temperature distribution sequence data inside the sucker rod heat pipe; The temperature distribution sequence data corresponding to the heat pipe wall of the sucker rod is determined based on the saturated temperature distribution sequence data, the heat transfer rate, and the heat transfer coefficient.

2. The method according to claim 1, characterized in that, The heat transfer coefficient within the sucker rod heat pipe includes the heat transfer coefficient of the heating section; the attribute data includes the first attribute data. Determining the heat transfer coefficient within the sucker rod heat pipe based on the attribute data includes: Obtain the first pressure distribution sequence data within the liquid pool of the sucker rod heat pipe; The heat transfer coefficient of the heating section is determined based on the ratio coefficient of the first attribute data, the first pressure distribution sequence data, and atmospheric pressure.

3. The method according to claim 2, characterized in that, The first attribute data includes: the specific heat capacity, thermal conductivity, latent heat of vaporization, dynamic viscosity, density of the medium in the sucker rod heat pipe, and the radial heat flux density of the evaporation section corresponding to the heating section; The heat transfer coefficient of the heating section is expressed as follows: Among them, h e ρ is the heat transfer coefficient of the heating section of the sucker rod heat pipe; l ρ is the density of the liquid. v Where is the density of the steam; g is the acceleration due to gravity; C pl q represents the specific heat capacity of the liquid. e h is the radial heat flux density of the evaporation section. fg p represents the latent heat of vaporization of the liquid; p represents the first pressure distribution sequence data; p a Atmospheric pressure; λ l u is the thermal conductivity of the liquid. l The liquid is the dynamic viscosity of the liquid; the liquid is the medium in the heating section of the sucker rod heat pipe, and the vapor is the medium in the evaporation section corresponding to the heating section of the sucker rod heat pipe.

4. The method according to claim 1, characterized in that, The heat transfer coefficient within the sucker rod heat pipe includes the heat transfer coefficient of the convection section. The attribute data includes first attribute data and second attribute data, wherein the second attribute data includes the radial heat flux density of the evaporation section corresponding to the convection section and the height of the liquid pool inside the sucker rod heat pipe; Determining the heat transfer coefficient within the sucker rod heat pipe based on the attribute data includes: The radial heat flux density of the evaporation section corresponding to the convection section is compared with the critical heat flux density; In response to the radial heat flux density of the evaporation section corresponding to the convection section being less than the critical heat flux density, the second pressure distribution sequence data corresponding to the convection section of the sucker rod heat pipe is obtained; the heat transfer coefficient of the convection section is determined based on the ratio coefficient of the first attribute data, the second pressure distribution sequence data and atmospheric pressure. In response to the radial heat flux density of the evaporation section corresponding to the convection section being greater than or equal to the critical heat flux density, the first Reynolds number of the liquid film flow in the evaporation section of the convection section is calculated, and the heat transfer coefficient of the convection section is determined based on the first Reynolds number and the height of the liquid pool in the sucker rod heat pipe.

5. The method according to claim 4, characterized in that, The first Reynolds number is expressed as follows: Among them, Re f L represents the first Reynolds number; p L is the liquid pool height of the sucker rod heat pipe; f h is the length of the liquid film in the liquid film evaporation section. fg The latent heat of vaporization of the liquid; u l q represents the dynamic viscosity of the liquid. e The radial heat flux density is the evaporation section of the convection section; the liquid is the medium in the convection section of the sucker rod heat pipe.

6. The method according to claim 4, characterized in that, When the radial heat flux density of the evaporation section corresponding to the convection section is greater than or equal to the critical heat flux density, the heat transfer coefficient of the convection section is expressed as follows: Among them, h f Re is the heat transfer coefficient of the convection section; f v is the first Reynolds number; l λ is the dynamic viscosity of the liquid; l ρ is the thermal conductivity of the liquid; g is the acceleration due to gravity.

7. The method according to claim 1, characterized in that, The attribute data includes: third attribute data, and the heat transfer coefficient in the sucker rod heat pipe includes the heat transfer coefficient of the condensing section; Determining the heat transfer coefficient within the sucker rod heat pipe based on the attribute data includes: Calculate the second Reynolds number for liquid film flow in the condensation section; The heat transfer coefficient of the condensing section is determined based on the second Reynolds number and the third attribute data.

8. The method according to claim 7, characterized in that, The second Reynolds number is expressed as follows: Where Re is the second Reynolds number; q c The radial heat flux density of the condensation section; l c The length of the condensation section; μ l h is the dynamic viscosity of the gas liquefying into a liquid medium in the condensation section. fg It is the latent heat of vaporization of the liquid.

9. The method according to claim 7, characterized in that, The third attribute data includes: the kinematic viscosity of the medium and the thermal conductivity of the medium; The heat transfer coefficient of the condensation section is expressed as follows: Among them, h c v is the heat transfer coefficient of the condensation section; e k is the kinematic viscosity of the liquid; l denoted as , where is the thermal conductivity of the liquid; Re is the second Reynolds number; g is the acceleration due to gravity; and the liquid is the medium corresponding to the condensation section in the sucker rod heat pipe.

10. The method according to claim 1, characterized in that, The calculation of the total thermal resistance in the sucker rod heat pipe from the heat-absorbing section to the wellhead of the target wellbore based on the heat transfer coefficient in the sucker rod heat pipe includes: The thermal resistance of each sub-path during the heat transfer from the heat-absorbing section to the wellhead of the target wellbore is calculated based on the heat transfer coefficient within the sucker rod heat pipe. The sub-paths include: from the heat-absorbing section heat transfer medium in the tubing annular space to the outer wall of the heating section sucker rod heat pipe; from the outer wall of the heating section sucker rod heat pipe to the inner wall; from the inner wall of the heating section sucker rod heat pipe to the heat transfer medium in the liquid pool within the sucker rod heat pipe; from the heating section of the sucker rod heat pipe to the heat dissipation section; from the medium within the condensation section of the sucker rod heat pipe to the inner wall of the condensation section; from the inner wall of the condensation section of the sucker rod heat pipe to the outer wall; and from the outer wall of the condensation section of the sucker rod heat pipe to the heat-releasing section heat transfer medium in the tubing annular space. The total thermal resistance is obtained by summing the thermal resistances corresponding to each sub-path.

11. The method according to claim 10, characterized in that, If the flow path is from the heating section to the cooling section of the sucker rod heat pipe, then the thermal resistance from the heating section to the cooling section of the sucker rod heat pipe is expressed as follows: Where R4 is the thermal resistance from the heating section to the heat dissipation section of the sucker rod heat pipe; G r P is the Grasov number; r L is the Prandtl number; a K represents the length of the convection section. ha denoted as , where is the thermal conductivity of the medium.

12. The method according to claim 1, characterized in that, The saturated temperature distribution sequence data includes the first saturated temperature distribution sequence data and the second saturated temperature distribution sequence data. The determination of the saturation temperature distribution sequence data within the sucker rod heat pipe includes: Obtain the first pressure distribution sequence data within the liquid pool of the sucker rod heat pipe; The first saturation temperature distribution sequence data is determined based on the first preset mapping function and the first pressure distribution sequence data, wherein the first preset mapping function is a mapping function between saturation temperature and first pressure. Acquire the second saturation temperature distribution sequence data collected by the temperature sensor.

13. The method according to claim 12, characterized in that, The temperature distribution sequence data corresponding to the heat pipe wall of the sucker rod includes the temperature distribution sequence data corresponding to the first section of the pipe wall; the temperature distribution sequence data corresponding to the first section of the pipe wall is the temperature distribution sequence data of the section from the lower end of the heat pipe to the liquid surface of the heat transfer medium in the liquid pool inside the heat pipe. The temperature distribution sequence data corresponding to the first section of the pipe wall is shown below: T2(x)=T0(x)+Q e / h e ,0<x≤L p Where T2(x) is the temperature distribution sequence data corresponding to the first section of the pipe wall; Q e h is the heat transfer rate of the heating section of the heat pipe. e L is the heat transfer coefficient from the inner wall of the heat pipe to the surface of the heat transfer medium in the liquid pool inside the heat pipe; p The height of the liquid pool inside the heat pipe of the sucker rod; T0(x) is the first saturation temperature distribution sequence data.

14. The method according to claim 12, characterized in that, The temperature distribution sequence data corresponding to the wall of the sucker rod heat pipe includes the temperature distribution sequence data corresponding to the second section of the pipe wall; the temperature distribution sequence data corresponding to the second section of the pipe wall is the temperature distribution sequence data of the section from the liquid surface of the heat transfer medium in the liquid pool inside the sucker rod heat pipe to the upper end of the heating section. The temperature distribution sequence data corresponding to the second section of the pipe wall heating section is shown below: T3(x)=T1(x)+Q e / h f ,L p <x≤L e Where T3(x) represents the temperature distribution sequence data corresponding to the second section of the pipe wall; Q e L is the heat transfer rate of the heating section of the heat pipe. p h is the height of the liquid pool inside the heat pipe of the sucker rod. f The position of the heat transfer medium in the liquid pool inside the heat pipe is relative to the heat transfer coefficient of the evaporation section; L e T1(x) represents the length of the heating section of the sucker rod heat pipe; T1(x) represents the second saturation temperature distribution sequence data.

15. The method according to claim 12, characterized in that, The temperature distribution sequence data corresponding to the heat pipe wall of the sucker rod includes the temperature distribution sequence data corresponding to the third section of the pipe wall; the temperature distribution sequence data corresponding to the third section of the pipe wall is the temperature distribution sequence data of the condensation section. The temperature distribution sequence data corresponding to the third section of the heated pipe wall is shown below: T4(x)=T1(x)-Q c / h c ,L e +L a ≤L Where T4(x) represents the temperature distribution sequence data corresponding to the pipe wall of the third pipe wall heating section; Q c h is the heat transfer rate of the condenser section of the sucker rod heat pipe. c L is the heat transfer coefficient of the condensing section. e Indicates the length of the heating section of the sucker rod heat pipe; L a denoted by ; L represents the total length of the heat pipe convection section of the sucker rod; T1(x) represents the second saturation temperature distribution sequence data.

16. The method according to claim 12, characterized in that, The method further includes: Based on the saturated temperature distribution sequence data, the temperature distribution sequence data corresponding to the fourth segment is determined. The temperature distribution sequence data corresponding to the fourth segment of the pipe wall is the temperature distribution sequence data from the upper end of the heating section to the upper end of the convection section. The temperature distribution sequence data corresponding to the fourth section of the pipe wall is shown below: T5(x)=T1(x), L e <x≤L e +L a Where T5(x) represents the temperature distribution sequence data corresponding to the fourth pipe wall segment; L e Indicates the length of the heating section of the sucker rod heat pipe; L a T1(x) represents the length of the convection section of the heat pipe in the sucker rod; T1(x) is the second saturation temperature distribution sequence data.

17. A temperature determination device for a sucker rod heat pipe, wherein the sucker rod heat pipe is located in a target wellbore, characterized in that, The device includes: The acquisition module is used to acquire the attribute data of the sucker rod heat pipe in the target wellbore; The determination module is used to determine the heat transfer coefficient inside the sucker rod heat pipe based on the attribute data; The calculation module is used to calculate the total thermal resistance of the process from the heat absorption section to the wellhead of the target wellbore in the sucker rod heat pipe based on the heat transfer coefficient in the sucker rod heat pipe. The determining module is also used to determine the heat transfer rate of the sucker rod heat pipe based on the total thermal resistance; The determination module is also used to determine the saturation temperature distribution sequence data inside the sucker rod heat pipe; The determination module is also used to determine the temperature distribution sequence data corresponding to the heat pipe wall of the sucker rod based on the saturated temperature distribution sequence data, the heat transfer rate and the heat transfer coefficient.

18. An electronic device, characterized in that, include: A processor, and a memory communicatively connected to the processor; The memory stores computer-executed instructions; The processor executes computer execution instructions stored in the memory to implement the method as described in any one of claims 1-16.

19. A computer-readable storage medium, characterized in that, The computer-readable storage medium stores computer-executable instructions, which, when executed by a processor, are used to implement the method as described in any one of claims 1-16.

20. A computer program product, characterized in that, Includes a computer program that, when executed by a processor, implements the method of any one of claims 1-16.

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