A large-torque gear transmission system and petroleum drilling crawler

Abstract

This invention relates to the field of oil drilling technology, and more particularly to a high-torque gear transmission system and an oil drilling crawler. The high-torque gear transmission system, applied to an oil drilling crawler, includes a fixed-axis torque-increasing mechanism and a planetary torque-increasing mechanism. The fixed-axis torque-increasing mechanism includes an input gear, a reduction gear set, and an output gear that mesh sequentially. The input gear is used for transmission connection with a drive motor. The planetary torque-increasing mechanism includes a sun gear, planet gears, and an internal gear ring. The sun gear is transmissionally connected to the output gear, and the sun gear and the internal gear ring are transmissionally connected via planet gears. The planet gears are rotatably mounted on a fixed shaft, which is fixedly mounted on a crawler wheel. The internal gear ring is fixedly mounted on the crawler body. This invention effectively solves the technical problem that existing chain drives and single-gear linear drives have poor load capacity and cannot meet the high-thrust, high-load operation requirements of oil drilling crawlers.

Description

Technical Field

[0001] This invention relates to the field of pipeline crawler technology, and more particularly to a high-torque gear transmission system and an oil drilling crawler. Background Technology

[0002] The oil drilling crawler is a specialized downhole power delivery tool for oil and gas fields, integrating mechanical, electrical, and hydraulic systems. It is suitable for operations in complex well structures such as highly deviated wells and horizontal wells. It generates stable traction by adhering to the inner wall of the wellbore through its own power mechanism, driving downhole instruments and tools to complete the delivery, positioning, and associated construction operations for the corresponding well section. After the operation is completed, it can be safely retrieved from the wellbore along with the cable or coiled tubing.

[0003] Regarding the structural design of an oil drilling crawler, patent application publication number CN119333071A discloses an oil drilling crawler. The crawler mainly consists of a crawler body, a hydraulic cylinder, a connecting block, a sliding mechanism, and a stabilizing mechanism. The sliding mechanism includes a first connecting rod, a hollow connecting rod, a motor, a first gear, a second gear, and a moving wheel. The stabilizing mechanism includes a first rack, a fixed block, a rotating rod, a third gear, a second rack, a limiting block, a connecting plate, a second railing, and a support rod. When the crawler moves along the inner wall of the well, the hydraulic cylinder output shaft moves upward, causing the connecting block to move upward. This drives the hollow connecting rod to unfold outward through connecting rod one, making the moving wheel fit tightly against the inner wall of the well. The motor drives the moving wheel to rotate through the meshing transmission of gear one and gear two, thereby driving the crawler to move along the inner wall of the well. At the same time, rack one on the connecting block moves upward with the connecting block, and through gear three, it drives rack two to move downward. Then, through the connecting plate and railing two, it pulls the support rod inward to avoid contact with the inner wall of the well, ensuring the smooth movement of the crawler.

[0004] However, actual downhole operations require the crawler to have sufficient driving force to reliably move itself and the instruments it carries within the narrow wellbore. Currently, most existing oil drilling crawlers still use chain drive or single-gear linear drive. Chain drive is limited by meshing strength and chain flexibility, making it prone to tooth skipping or breakage under high torque. Single-gear linear drive, due to its limited meshing tooth surface and small transmission ratio, requires increasing the radial dimension of the gear to improve the transmission ratio, making it unable to output large torque within a limited radial space, resulting in poor overall load capacity. For situations requiring the propulsion of heavy instruments over long distances in horizontal or highly deviated well sections, the load capacity of these drive methods is clearly insufficient to meet the demands of high-thrust, high-load operations. Summary of the Invention

[0005] This invention provides a high-torque gear transmission system to solve the technical problem that the existing chain drive and single gear linear drive have poor load capacity and cannot meet the high thrust and high load operation requirements of oil drilling crawlers; the purpose of this invention is also to provide an oil drilling crawler.

[0006] To solve the above problems, the high-torque gear transmission system provided by the present invention adopts the following technical solution: A high-torque gear transmission system is used in an oil drilling crawler, comprising a fixed-axis torque increasing mechanism and a planetary torque increasing mechanism that are sequentially connected along the power input direction. The fixed-axis torque increasing mechanism includes an input gear, a reduction gear set, and an output gear that mesh sequentially. The input gear is used for transmission connection with the drive motor. The planetary torque-increasing mechanism includes a sun gear, planet gears, an internal gear ring, and a planet carrier. The planet carrier is fixedly mounted on the crawler wheel, the internal gear ring is fixedly mounted on the crawler body, the sun gear is connected to the output gear, and the planet gears are rotatably mounted on the planet carrier and mesh with the sun gear and the internal gear ring.

[0007] The beneficial effects of the high-torque gear transmission system provided by this invention are: First, by setting up a fixed-axis torque-increasing mechanism consisting of a sequentially meshing input gear, a reduction gear set, and an output gear, the rigid gear meshing eliminates the hidden dangers of slippage and tooth skipping during transmission, improving transmission stability and power transmission efficiency. By connecting the input gear to the drive motor, the high-speed, low-torque power output by the motor can be stably introduced into the transmission system. Then, through the multi-stage meshing transmission of the reduction gear set, the first stage of power reduction and torque amplification is achieved without significantly increasing the radial dimension of the transmission mechanism, initially improving the output torque and providing a stable power input for the subsequent second stage of torque amplification.

[0008] Secondly, by setting up a planetary torque amplification mechanism consisting of a sun gear, planetary gears, and an internal gear ring, the planetary torque amplification mechanism forms a series transmission structure with the fixed-axis torque amplification mechanism, achieving secondary power amplification. Specifically, the planetary torque amplification mechanism constitutes a planetary gear train, with the sun gear connected to the output gear. The planetary gears are rotatably mounted on the planetary carrier and simultaneously mesh with the sun gear and the internal gear ring fixedly mounted on the crawler body. Since the internal gear ring is stationary, the rotation of the sun gear drives the planetary gears to rotate, while simultaneously forcing the planetary carrier to revolve around the sun gear axis. According to the planetary gear transmission principle, the output speed of the planetary carrier is lower than the speed of the sun gear, and the output torque is proportionally amplified. The superposition of the two stages of torque amplification improves the overall transmission ratio of the system, effectively converting the high speed and low torque output of the motor into low speed and high torque, meeting the needs of the oil drilling crawler for high thrust and high load operations downhole.

[0009] In summary, this invention achieves a large reduction ratio and high torque output through two-stage gear torque amplification, effectively solving the technical problem that the existing chain drive and single gear linear drive have poor load capacity and cannot meet the high thrust and high load operation requirements of oil drilling crawlers.

[0010] Furthermore, the reduction gear set includes a first-stage reduction gear, a second-stage reduction gear, a third-stage reduction gear, and a fourth-stage reduction gear that mesh sequentially along the power output direction. The first-stage reduction gear meshes with the input gear, and the fourth-stage reduction gear meshes with the output gear.

[0011] Beneficial effects: First, the sequential transmission of primary, secondary, tertiary, and quaternary reduction gears achieves a large overall reduction ratio, converting the high speed and low torque output of the drive motor into low speed and high torque, thus improving the crawler's driving force and load capacity. Second, multi-stage reduction distributes the deceleration process across multiple sets of meshing gears, resulting in a more even load distribution on each gear and reduced tooth surface contact stress and bending stress, thereby improving gear lifespan and transmission reliability. Third, the multi-stage meshing structure allows for flexible arrangement of gear diameters and tooth counts within limited radial space, avoiding the need for excessively large diameter gears due to excessively large single-stage transmission ratios, thus adapting to the confined downhole installation space of oil drilling crawlers. Finally, multi-stage gear meshing provides higher transmission smoothness and lower meshing noise, reducing impact and vibration during power transmission and providing a stable and continuous power input for the subsequent planetary torque-increasing mechanism.

[0012] Furthermore, the gear ratios of the first-stage reduction gear and the output gear, the second-stage reduction gear and the first-stage reduction gear, the third-stage reduction gear and the second-stage reduction gear, the fourth-stage reduction gear and the third-stage reduction gear, and the output gear and the fourth-stage reduction gear are all 1.26 to 1.35.

[0013] Beneficial effects: By controlling the gear ratios between the input gear and the first-stage reduction gear, the second-stage reduction gear and the first-stage reduction gear, the third-stage reduction gear and the second-stage reduction gear, the fourth-stage reduction gear and the third-stage reduction gear, and the output gear and the fourth-stage reduction gear, the size proportions of each pair of related gears in the entire transmission chain are kept balanced and appropriate. The total reduction ratio of the five-stage reduction is approximately (1.26~1.35). 5 The ratio is 3.17 to 4.48 times. At the same time, the gear ratio of the output gear and the four-stage reduction gear are also within the same range, ensuring that the overall reduction ratio of the planetary torque increasing mechanism from the input end to the output end is reasonable. This can effectively increase the output torque and reduce the speed, meeting the high thrust requirements of the crawler.

[0014] Furthermore, both the secondary reduction gear and the tertiary reduction gear are double gears, and the large gear of the secondary reduction gear meshes with the primary reduction gear, while its small gear meshes with the large gear of the tertiary reduction gear, and the small gear of the tertiary reduction gear meshes with the quaternary reduction gear.

[0015] Beneficial effects: The double-gear structure achieves a compact arrangement of two-stage reduction within a limited radial space. The large gear of the second-stage reduction gear meshes with the first-stage reduction gear, and its small gear meshes with the large gear of the third-stage reduction gear. The small gear of the third-stage reduction gear then meshes with the fourth-stage reduction gear. Power is transmitted sequentially through the alternating large and small gears. Each meshing of the large and small gears results in a reduction and torque increase, thus achieving a large overall reduction ratio within a relatively small axial and radial dimension. This avoids the problem of using ultra-large diameter gears to pursue a large transmission ratio and is beneficial for adapting to the narrow downhole installation space of oil drilling crawlers.

[0016] Furthermore, the gear ratio between the planetary gear and the sun gear is 1.5 to 1.76.

[0017] Beneficial effects: By controlling the gear ratio between the planetary gear and the sun gear between 1.5 and 1.76, that is, the number of teeth of the planetary gear is greater than the number of teeth of the sun gear, a speed reduction transmission is formed between the sun gear and the planetary gear. This can effectively amplify the torque input from the sun gear, and avoid the problem of the planetary gear diameter increasing and occupying limited radial space due to the excessive single-stage transmission ratio.

[0018] Furthermore, the planetary carrier is located inside the internal gear ring, and a clearance groove is provided on its side wall; the planetary gear is located inside the planetary carrier, and its teeth pass through the clearance groove and mesh with the internal gear ring.

[0019] Beneficial effects: On the one hand, by arranging the planet carrier inside the internal gear ring, the planet carrier provides a stable mounting base for the planet gears, ensuring the accurate axial position of the planet gears, thereby guaranteeing the meshing accuracy and transmission smoothness between the sun gear and planet gears, and between the planet gears and the internal gear ring. On the other hand, by creating clearance grooves on the sidewalls of the planet carrier, the planet gears can be mounted inside the planet carrier, with their teeth passing through the clearance grooves to mesh with the internal gear ring. This allows the planet gear teeth to pass through and mesh normally with the internal gear ring, while also limiting and guiding the movement of the planet gears, preventing interference between the teeth and the sidewalls of the planet carrier.

[0020] To solve the above problems, the oil drilling crawler provided by this invention adopts the following technical solution: An oil drilling crawler includes a crawler body, a drive motor, and crawler wheels. The drive motor is fixedly mounted on the crawler body. The crawler also includes a high-torque gear transmission system, through which the drive motor is connected to the crawler wheels. The high-torque gear transmission system includes a fixed-axis torque increasing mechanism and a planetary torque increasing mechanism that are sequentially connected along the power input direction. The fixed-axis torque increasing mechanism includes an input gear, a reduction gear set, and an output gear that mesh sequentially. The input gear is used for transmission connection with the drive motor. The planetary torque-increasing mechanism includes a sun gear, planet gears, an internal gear ring, and a planet carrier. The planet carrier is fixedly mounted on the crawler wheel, the internal gear ring is fixedly mounted on the crawler body, the sun gear is connected to the output gear, and the planet gears are rotatably mounted on the planet carrier and mesh with the sun gear and the internal gear ring.

[0021] The beneficial effects of the oil drilling crawler provided by this invention are as follows: A high-torque gear transmission system, including a fixed-axis torque-increasing mechanism and a planetary torque-increasing mechanism, is used to connect the drive motor and the crawler wheel. The high-speed, low-torque output of the motor first enters the fixed-axis torque-increasing mechanism. Through multiple stages of meshing between the input gear, reduction gear set, and output gear, the first stage of speed reduction and torque increase is achieved, reducing the speed and increasing the torque. This increased torque is then transmitted to the sun gear in the planetary torque-increasing mechanism. Since the internal gear ring remains stationary, when the sun gear rotates, it drives the planet gears to rotate, thereby forcing the planet carrier to revolve around the axis of the sun gear. According to the transmission law of planetary gear trains, the output speed of the planet carrier is lower than the input speed of the sun gear, while the output torque is proportionally increased. The cumulative torque increase of the two stages results in a high overall transmission ratio for the entire transmission system, converting the high-speed, low-torque output of the motor into low-speed, high-torque output, thus meeting the requirements of the oil drilling crawler for high-thrust, high-load operations downhole.

[0022] In summary, this invention achieves a larger overall transmission ratio through a two-stage pitch increase, and the meshing surface between the internal gear ring and the planetary gears is large, resulting in high load-bearing capacity. This avoids the problems of excessively large single-stage transmission ratios or excessively large gear diameters, thereby achieving stable output of high torque and high load within the limited radial space of the oil drilling crawler. This meets the operational requirements for propelling heavier instruments over long distances in horizontal or highly inclined well sections, effectively solving the technical problem that existing chain drives and single-gear linear drives have poor load-bearing capacity and cannot meet the high thrust and high load operation requirements of oil drilling crawlers.

[0023] Furthermore, the reduction gear set includes a first-stage reduction gear, a second-stage reduction gear, a third-stage reduction gear, and a fourth-stage reduction gear that mesh sequentially along the power output direction. The first-stage reduction gear meshes with the input gear, and the fourth-stage reduction gear meshes with the output gear.

[0024] Beneficial effects: On the one hand, the successive meshing of primary, secondary, tertiary, and quaternary reduction gears creates a large overall reduction ratio, converting the high-speed, low-torque output of the drive motor into low-speed, high-torque output, thereby enhancing the crawler's traction and load-bearing capacity. On the other hand, the multi-stage reduction method distributes the reduction process across multiple sets of meshing gears, resulting in a more balanced load on each gear stage, reducing tooth surface contact stress and tooth root bending stress, extending gear service life, and improving the reliability of the transmission system. Furthermore, the multi-stage meshing structure allows for flexible adjustment of the diameter and number of teeth of each gear within a limited radial space, avoiding the use of excessively large diameter gears in pursuit of a large single-stage transmission ratio, thus adapting to the narrow downhole installation conditions of oil drilling crawlers.

[0025] Furthermore, the gear ratios of the first-stage reduction gear and the output gear, the second-stage reduction gear and the first-stage reduction gear, the third-stage reduction gear and the second-stage reduction gear, the fourth-stage reduction gear and the third-stage reduction gear, and the output gear and the fourth-stage reduction gear are all 1.26 to 1.35.

[0026] Furthermore, both the secondary reduction gear and the tertiary reduction gear are double gears, and the large gear of the secondary reduction gear meshes with the primary reduction gear, while its small gear meshes with the large gear of the tertiary reduction gear, and the small gear of the tertiary reduction gear meshes with the quaternary reduction gear.

[0027] Beneficial effects: By adopting a double gear structure, the large gear of the second-stage reduction gear meshes with the first-stage reduction gear, and its small gear meshes with the large gear of the third-stage reduction gear. The small gear of the third-stage reduction gear meshes with the fourth-stage reduction gear. Each time the power passes through the meshing of the large and small gears, a first-stage reduction and torque increase can be completed. The compact arrangement of the two-stage reduction is achieved within a limited radial space.

[0028] Furthermore, the gear ratio between the planetary gear and the sun gear is 1.5 to 1.76.

[0029] Furthermore, the planetary carrier is located inside the internal gear ring, and a clearance groove is provided on its side wall; the planetary gear is located inside the planetary carrier, and its teeth pass through the clearance groove and mesh with the internal gear ring.

[0030] Beneficial effects: On the one hand, the planetary carrier is fixedly mounted on the crawler wheel and located inside the internal gear ring, providing a stable mounting base for the planetary gears and ensuring the accurate axial position of the planetary gears. This guarantees the meshing accuracy and transmission smoothness among the sun gear, planetary gears, and internal gear ring. On the other hand, a clearance groove is provided on the side wall of the planetary carrier. The planetary gears are mounted inside the planetary carrier, and their teeth pass through the clearance groove to mesh with the internal gear ring. The clearance groove not only provides a passage for the teeth to pass through, allowing them to mesh normally with the internal gear ring, but also limits and guides the movement of the planetary gears, effectively preventing interference between the teeth and the side wall of the planetary carrier. Attached Figure Description

[0031] Figure 1 This is a schematic diagram of the structure of the oil drilling crawler provided by the present invention; Figure 2 Schematic diagram of the application structure of the oil drilling crawler provided by the present invention Figure 1 ; Figure 3 Schematic diagram of the application structure of the oil drilling crawler provided by the present invention Figure 2 ; Figure 4 for Figure 3 The main view; Figure 5 for Figure 3 Top view; Figure 6 A schematic diagram of the planetary torque-increasing mechanism provided by the present invention. Figure 1 ; Figure 7 A schematic diagram of the planetary torque-increasing mechanism provided by the present invention. Figure 2 ; Figure 8 A schematic diagram of the planetary torque-increasing mechanism provided by the present invention. Figure 3 ; Figure 9 for Figure 8 The main view; Figure 10 for Figure 8 Top view.

[0032] Explanation of reference numerals in the attached figures: 1. Crawler body; 11. Drive motor; 12. Gearbox; 121. Bevel gear; 122. Transition gear; 123. Bearing; 124. Shaft 1; 13. Crawling wheel; 2. Fixed-axis torque increasing mechanism; 21. Input gear; 22. First-stage reduction gear; 23. Second-stage reduction gear; 24. Third-stage reduction gear; 25. Fourth-stage reduction gear; 26. Output gear; 3. Planetary torque increasing mechanism; 31. Sun gear; 311. Connecting shaft; 32. Planetary gears; 33. Internal gear ring; 34. Planet carrier; 341. Relief groove; 342. Shaft 2; 343. Fixed shaft. Detailed Implementation

[0033] The principles and spirit of the present invention will be explained in detail below with reference to several representative embodiments.

[0034] An embodiment of the high-torque gear transmission system provided by the present invention: like Figures 1 to 10 As shown, the high-torque gear transmission system is applied to an oil drilling crawler. It includes a fixed-axis torque increasing mechanism 2 and a planetary torque increasing mechanism 3 that are sequentially connected along the power input direction. The fixed-axis torque increasing mechanism 2 is connected to the drive motor 11 of the crawler body 1, and the planetary torque increasing mechanism 3 is connected to the crawler wheel 13 of the crawler body 1.

[0035] like Figures 2 to 5 As shown, in this embodiment, the fixed-axis torque increasing mechanism 2 includes an input gear 21, a reduction gear set, and an output gear 26 that mesh sequentially from left to right. The input gear 21 is used for transmission connection with the drive motor 11.

[0036] like Figures 2 to 5 As shown, in this embodiment, the output end of the drive motor 11 is connected to a gearbox 12. The gearbox 12 is provided with a bevel gear 121 and a transition gear 122. The bevel gear 121 is connected to the output end of the drive motor 11. There are two transition gears 122. Each transition gear 122 is used to drive the bevel gear 121 and the corresponding input gear 21.

[0037] like Figures 3 to 5 As shown, in this embodiment, the transition gear 122 is coaxial with the corresponding input gear 21, and the transition gear 122 meshes with the bevel gear 121; a bearing 123 is installed on the gearbox 12, and the shaft 124 for connecting the transition gear 122 and the corresponding input gear 21 is installed in the bearing 123, so as to provide reliable radial and axial support for the shaft 124 through the bearing 123, and to provide positioning for the installation of the shaft 124.

[0038] like Figures 2 to 5As shown, in this embodiment, the reduction gear set includes a first-stage reduction gear 22, a second-stage reduction gear 23, a third-stage reduction gear 24, and a fourth-stage reduction gear 25 that mesh sequentially along the power output direction (from left to right). The first-stage reduction gear 22 meshes with the input gear 21, and the fourth-stage reduction gear 25 meshes with the output gear 26. In other embodiments, the number of reduction gears is determined according to specific circumstances.

[0039] like Figures 2 to 5 As shown, in this embodiment, the gear ratios of the first-stage reduction gear 22 and the output gear 26, the second-stage reduction gear 23 and the first-stage reduction gear 22, the third-stage reduction gear 24 and the second-stage reduction gear 23, the fourth-stage reduction gear 25 and the third-stage reduction gear 24, and the output gear 26 and the fourth-stage reduction gear 25 are all 1.26 to 1.35.

[0040] like Figures 2 to 5 As shown, in this embodiment, both the second-stage reduction gear 23 and the third-stage reduction gear 24 are double gears. The large gear of the second-stage reduction gear 23 meshes with the first-stage reduction gear 22, and its small gear meshes with the large gear of the third-stage reduction gear 24. The small gear of the third-stage reduction gear 24 meshes with the fourth-stage reduction gear 25. In other embodiments, only the second-stage reduction gear 23 is a double gear, or only the third-stage reduction gear 24 is a double gear, or all reduction gears are single gears.

[0041] Specifically, in this embodiment, the input gear 21 has 17 teeth, the first-stage reduction gear 22 has 23 teeth, the second-stage reduction gear 23 has 30 teeth on its large gear and 23 teeth on its small gear, the third-stage reduction gear 24 has 30 teeth on its large gear and 17 teeth on its small gear, the fourth-stage reduction gear 25 has 23 teeth, and the output gear 26 has 29 teeth. It can be calculated that the tooth ratio between the first-stage reduction gear 22 and the input gear 21 is 1.35, the tooth ratio between the large gear of the second-stage reduction gear 23 and the first-stage reduction gear 22 is 1.30, the tooth ratio between the large gear of the third-stage reduction gear 24 and the small gear of the second-stage reduction gear 23 is 1.30, the tooth ratio between the fourth-stage reduction gear 25 and the small gear of the third-stage reduction gear 24 is 1.35, and the tooth ratio between the output gear 26 and the fourth-stage reduction gear 25 is 1.26.

[0042] In other embodiments, the gear ratios of the first-stage reduction gear 22 and the output gear 26, the second-stage reduction gear 23 and the first-stage reduction gear 22, the third-stage reduction gear 24 and the second-stage reduction gear 23, the fourth-stage reduction gear 25 and the third-stage reduction gear 24, and the output gear 26 and the fourth-stage reduction gear 25 are determined according to specific circumstances, and it is only necessary to ensure that the reduction ratio is between 1.26 and 1.35.

[0043] like Figures 6 to 10As shown, in this embodiment, the planetary torque-increasing mechanism 3 includes a sun gear 31, planet gears 32, an internal gear ring 33, and a planet carrier 34. The planet carrier 34 is fixedly mounted on the crawler wheel 13, and the internal gear ring 33 is fixedly mounted on the crawler body 1. The sun gear 31 is connected to the output gear 26 for transmission. The planet gears 32 are rotatably mounted on the planet carrier 34 and mesh with the sun gear 31 and the internal gear ring 33. In this embodiment, the gear ratio between the planet gears 32 and the sun gear 31 is 1.5 to 1.76.

[0044] like Figure 6 and Figure 7 As shown, in this embodiment, there are four planetary gears 32, each with 18 teeth, and the sun gear 31 has 12 teeth. The ratio of the number of teeth of the planetary gears 32 to the sun gear 31 is 1.5. In other embodiments, the ratio of the number of teeth of the planetary gears 32 to the sun gear 31 is 1.76, or any value between 1.5 and 1.76. In other embodiments, the number of planetary gears 32 may be two, three, five, six, etc., depending on the specific circumstances.

[0045] like Figure 6 , Figure 8 , Figure 9 and Figure 10 As shown, in this embodiment, the planet carrier 34 is located inside the internal gear ring 33, and a clearance groove 341 is provided on its side wall; the planet gear 32 is located inside the planet carrier 34, and its teeth pass through the clearance groove 341 and mesh with the internal gear ring 33.

[0046] like Figure 6 , Figure 8 , Figure 9 and Figure 10 As shown, in this embodiment, a second rotating shaft 342 is fixedly provided at the center of the planetary carrier 34. The second rotating shaft 342 is located on the rotation center line of the crawler wheel 13. The sun gear 31 is rotatably mounted on the second rotating shaft 342. The end of the sun gear 31 away from the crawler wheel 13 has a connecting shaft 311, and the output gear 26 is fixedly mounted on the connecting shaft 311.

[0047] like Figure 6 , Figure 8 and Figure 9 As shown, in this embodiment, four fixed shafts 343 are fixedly mounted on the planet carrier 34, and four planetary gears 32 are rotatably mounted on the four fixed shafts 343 respectively; the two ends of the fixed shafts 343 are mounted on two opposite side walls of the planet carrier 34.

[0048] like Figure 6 , Figure 8 and Figure 9As shown, in this embodiment, four fixed shafts 343 are evenly spaced around the rotation axis of the sun gear 31 on the inner side of the internal gear ring 33 in the circumferential direction, and the radial distance between each fixed shaft 343 and the rotation axis of the sun gear 31 is equal; two adjacent fixed shafts 343 are respectively connected to the rotation axis of the sun gear 31, and the included angle between the two connecting lines is 90°, so that the four fixed shafts 343 are arranged in a cross symmetrical manner.

[0049] It should be noted that in this embodiment, the bevel gear 121, transition gear 122, input gear 21, first-stage reduction gear 22, second-stage reduction gear 23, third-stage reduction gear 24, fourth-stage reduction gear 25, output gear 26, sun gear 31, planet gear 32, and internal gear ring 33 have the same module.

[0050] The working principle of the high-torque gear transmission system provided by this invention is as follows: the drive motor 11 transmits power to the input gears 21 on the left and right sides via bevel gears 121 and two transition gears 122, achieving synchronous drive of the crawling wheels 13 on both sides. The input gears 21 sequentially drive the first-stage reduction gear 22, the second-stage reduction gear 23, the third-stage reduction gear 24, and the fourth-stage reduction gear 25 to mesh and transmit power, completing the first reduction and torque increase. The fourth-stage reduction gear 25 transmits the amplified torque to the output gear 26, which then transmits the amplified torque to the sun gear 31, causing the sun gear 31 to rotate. When the sun gear 31 rotates, it drives the planetary gears 32 meshing with it to rotate. The planetary gears 32 are subjected to the reaction force of the internal gear ring 33, forcing the planet carrier 34 and the crawling wheels 13 to revolve around the axis of the sun gear 31. According to the transmission principle of the planetary gear 32 system, when the internal gear ring 33 is fixed, the output speed of the planet carrier 34 is lower than the speed of the sun gear 31, and the output torque is proportionally amplified, achieving the second reduction and torque increase.

[0051] Embodiments of the oil drilling crawler provided by the present invention: like Figures 1 to 10 As shown, the oil drilling crawler includes a crawler body, a drive motor, crawler wheels, and a high-torque gear transmission system. The drive motor is connected to the crawler wheels via the high-torque gear transmission system.

[0052] The high-torque gear transmission system is exactly the same as the high-torque gear transmission system described above, and will not be repeated here.

[0053] Based on the above description in this specification, those skilled in the art will also understand that the following terms, such as "upper," "lower," "front," "back," "left," "right," "inner," and "outer," which indicate orientation or positional relationship, are based on the orientation or positional relationship shown in the accompanying drawings of this specification and should not be understood or interpreted as limiting the present invention.

[0054] In addition, in the description of this specification, "multiple" means at least two, such as two, three or more, etc., unless otherwise expressly and specifically defined.

Claims

1. A high-torque gear transmission system, applied to an oil drilling crawler, characterized in that, This includes a fixed-axis torque increasing mechanism and a planetary torque increasing mechanism that are sequentially connected along the power input direction; The fixed-axis torque increasing mechanism includes an input gear, a reduction gear set, and an output gear that mesh sequentially. The input gear is used for transmission connection with the drive motor. The planetary torque-increasing mechanism includes a sun gear, planet gears, an internal gear ring, and a planet carrier. The planet carrier is fixedly mounted on the crawler wheel, the internal gear ring is fixedly mounted on the crawler body, the sun gear is connected to the output gear, and the planet gears are rotatably mounted on the planet carrier and mesh with the sun gear and the internal gear ring.

2. The high-torque gear transmission system according to claim 1, characterized in that, The reduction gear set includes a first-stage reduction gear, a second-stage reduction gear, a third-stage reduction gear, and a fourth-stage reduction gear that mesh sequentially along the power output direction. The first-stage reduction gear meshes with the input gear, and the fourth-stage reduction gear meshes with the output gear.

3. The high-torque gear transmission system according to claim 2, characterized in that, The gear ratios of the first-stage reduction gear to the output gear, the second-stage reduction gear to the first-stage reduction gear, the third-stage reduction gear to the second-stage reduction gear, the fourth-stage reduction gear to the third-stage reduction gear, and the output gear to the fourth-stage reduction gear are all between 1.26 and 1.

35.

4. The high-torque gear transmission system according to claim 2, characterized in that, Both the second-stage reduction gear and the third-stage reduction gear are double gears. The large gear of the second-stage reduction gear meshes with the first-stage reduction gear, and its small gear meshes with the large gear of the third-stage reduction gear. The small gear of the third-stage reduction gear meshes with the fourth-stage reduction gear.

5. The high-torque gear transmission system according to any one of claims 1 to 4, characterized in that, The ratio of the number of teeth of the planetary gear to that of the sun gear is 1.5 to 1.

76.

6. The high-torque gear transmission system according to any one of claims 1 to 4, characterized in that, The planetary carrier is located inside the internal gear ring, and a clearance groove is provided on its side wall; the planetary gear is located inside the planetary carrier, and its teeth pass through the clearance groove and mesh with the internal gear ring.

7. An oil drilling crawler, comprising a crawler body, a drive motor, and crawler wheels, wherein the drive motor is fixedly mounted on the crawler body, characterized in that, It also includes the high-torque gear transmission system according to any one of claims 1 to 6, wherein the drive motor is connected to the crawling wheel via the high-torque gear transmission system.

8. The oil drilling crawler according to claim 7, characterized in that, The reduction gear set includes a first-stage reduction gear, a second-stage reduction gear, a third-stage reduction gear, and a fourth-stage reduction gear that mesh sequentially along the power output direction. The first-stage reduction gear meshes with the input gear, and the fourth-stage reduction gear meshes with the output gear.

9. The oil drilling crawler according to claim 8, characterized in that, The gear ratios of the first-stage reduction gear to the output gear, the second-stage reduction gear to the first-stage reduction gear, the third-stage reduction gear to the second-stage reduction gear, the fourth-stage reduction gear to the third-stage reduction gear, and the output gear to the fourth-stage reduction gear are all between 1.26 and 1.

35.

10. The oil drilling crawler according to claim 8, characterized in that, Both the second-stage reduction gear and the third-stage reduction gear are double gears. The large gear of the second-stage reduction gear meshes with the first-stage reduction gear, and its small gear meshes with the large gear of the third-stage reduction gear. The small gear of the third-stage reduction gear meshes with the fourth-stage reduction gear.

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