Deep sea reduction gear

Abstract

The application discloses a deep-sea speed reducer, which comprises a shell, an input shaft, an output shaft and a planetary gear assembly; the shell is provided with a shaft hole for the output shaft to pass through; a circulating heat dissipation device is arranged in the shaft hole; the circulating heat dissipation device comprises a driving member, a linkage ring, a clutch mechanism and a negative pressure conveying mechanism; the shell is provided with a first flow channel and a second flow channel for filling cooling liquid; the first flow channel and the second flow channel are connected together at one end close to the planetary gear assembly; the negative pressure conveying mechanism is provided with a water inlet and a water outlet; the first flow channel and the second flow channel are connected with the water inlet and the water outlet respectively at the other end away from the planetary gear assembly; the linkage ring is installed on the outer periphery of the output shaft in a circumferential linkage and can axially slide; the driving member is connected with the linkage ring and used for driving the linkage ring to axially move, so that the linkage ring has a clamping position matched with the clutch mechanism and a separation position separated from the clutch mechanism. The application can improve the heat dissipation effect of the speed reducer in the deep-sea environment and ensure stable operation.

Description

Technical Field

[0001] This invention relates to the field of speed reducer technology, and in particular to a deep-sea speed reducer. Background Technology

[0002] Gear reducers are widely used in various industries. Thanks to the continuous development of advanced design technology and theoretical research (such as gear strength calculation methods, profile modification technology, deformation calculation, optimization design methods, smooth transition of tooth roots, new structures, etc.), the improvement of material technology (the widespread use of various high-quality alloy steel forgings, and the improvement of material and heat treatment quality control), more reasonable structural design, improved machining accuracy (ISO 5-6 level), and improved bearing and lubricant quality and life, the world's reducer technology has also made great progress.

[0003] During operation, speed reducers generate significant heat due to meshing losses, bearing losses, oil churning losses, sealing losses, and fan losses. This excessive power loss leads to overheating, limiting system functionality and significantly impacting the reducer system. Applications of speed reducers include connecting the motor output to the reducer input, and connecting the reducer output to a water pump output. Land-based speed reducers typically utilize water cooling for effective heat dissipation at high input speeds. However, deep-sea speed reducers cannot utilize water cooling. Furthermore, the planetary gears generate significant localized heat, and even surrounded by water, comprehensive heat dissipation is impossible. This means the reducer's internal components contain both high-temperature and low-temperature areas, hindering rapid cooling. Rapid heat dissipation within the high-speed rotation of the input shaft of a deep-sea speed reducer has been a persistent challenge in this field. Therefore, it is necessary to develop a deep-sea speed reducer with superior heat dissipation performance to address these issues. Summary of the Invention

[0004] The purpose of this invention is to provide a deep-sea speed reducer that can improve the heat dissipation effect of the speed reducer in the deep-sea environment, thereby ensuring its stable operation.

[0005] To achieve the above objectives, the present invention provides the following technical solution: a deep-sea reducer, comprising a housing, an input shaft and an output shaft rotatably mounted on the housing, and a planetary gear assembly disposed within the housing for transmitting power between the input shaft and the output shaft; the housing has a shaft hole for the output shaft to pass through, and a circulating heat dissipation device is provided within the shaft hole, the circulating heat dissipation device comprising a driving component, a linkage ring, a clutch mechanism, and a negative pressure conveying mechanism; the housing has a first flow channel and a second flow channel for filling with coolant, both the first and second flow channels being arranged along the length direction of the housing, the first flow channel and the second flow channel being... The two flow channels are connected at their ends near the planetary gear assembly. The negative pressure conveying mechanism is provided with an inlet and an outlet. The ends of the first and second flow channels away from the planetary gear assembly are respectively connected to the inlet and outlet of the negative pressure conveying mechanism. The linkage ring is circumferentially linked and axially slidable on the outer periphery of the output shaft. The driving component is connected to the linkage ring to drive the linkage ring to move axially, so that the linkage ring has an engaged position that cooperates with the clutch mechanism to drive the negative pressure conveying mechanism to work and circulate coolant, and a disengaged position that disengages from the clutch mechanism to stop the negative pressure conveying mechanism from working.

[0006] By adopting the above technical solution, the coolant can be circulated through the motion of the output shaft itself, thereby achieving active heat transfer and efficient heat dissipation inside the reducer, thus overcoming the limitation that external water cooling cannot be relied upon in the deep-sea environment. Simultaneously, it can be used with a built-in control circuit board. The control circuit board is electrically connected to the drive motor and the drive component via wires. When the drive motor rotates at low speed (the speed range can be customized according to actual conditions), the control circuit board controls the movable end of the drive component to retract, causing the linkage ring to be in the disengaged position. At this time, when the output shaft drives the linkage ring to rotate, it will not drive the negative pressure conveying mechanism through the clutch mechanism. When the drive motor rotates at high speed (the speed range can be customized according to actual conditions), the control circuit board controls the movable end of the drive component to extend, causing the linkage ring to be in the engaged position. At this time, when the output shaft drives the linkage ring to rotate, it drives the negative pressure conveying mechanism through the clutch mechanism, causing the coolant in the first and second flow channels to circulate. Since the two flow channels are partly located in the heat-generating area and partly located in the non-heat-generating area, heat exchange between the two areas can be quickly achieved, and the heat is evenly distributed on the outer shell (increasing the effective heat dissipation area) for heat dissipation. This avoids ineffective flow of coolant and can significantly improve the heat dissipation effect of the reducer in the deep-sea environment, thereby ensuring its stable operation.

[0007] The present invention is further configured such that the driving component is an electromagnet, the movable end of the driving component is provided with a linkage head, and the end of the linkage ring near the driving component is provided with an annular groove for the outer periphery of the linkage head to be embedded.

[0008] By adopting the above technical solution, the driving component uses an electromagnet, which utilizes electromagnetic force to achieve rapid response and precise axial displacement of the moving end (iron core), ensuring the timeliness and accuracy of the linkage ring movement, thereby stably triggering the switching action of the clutch mechanism. Furthermore, the moving end of the driving component and the linkage ring achieve axial linkage through a snap-fit ​​connection, resulting in a simple connection structure and convenient assembly / disassembly.

[0009] The invention is further configured such that an installation groove is provided on the outer wall of the housing, the installation groove is connected to the shaft hole, and a pressure cap for pressing the driving component into the installation groove is connected to the outer end of the installation groove by screws, and a first sealing ring is provided between the pressure cap and the housing.

[0010] By adopting the above technical solution, the drive component can be fixedly installed. The installation structure is simple and reliable, and has good sealing performance, effectively preventing the intrusion of external seawater.

[0011] The present invention is further configured such that a guide block is provided on the outer circular surface of the output shaft, and a guide groove is provided on the inner circular surface of the linkage ring along the axial direction for forming a sliding fit with the guide block.

[0012] By adopting the above technical solution, the linkage ring can be directionally slid (axially) on the output shaft, realizing the switching between the engaging and disengaging positions.

[0013] The invention is further configured such that the negative pressure conveying mechanism includes a drive ring sleeved on the outer periphery of the output shaft, a fixed outer ring disposed on the outer periphery of the drive ring, and multiple sets of telescopic components disposed on the outer circular surface of the drive ring. The fixed outer ring is fixedly connected to the inner wall of the shaft hole, and the outer circular surface of the fixed outer ring is in contact with the inner circular surface of the shaft hole. The outer circular surface of the drive ring is in contact with the inner circular surface of the fixed outer ring. The outer circular surface of the drive ring is provided with multiple guide grooves, the number of which is equivalent to the number of telescopic components. The telescopic components include a compression spring and a slider. The compression spring and the slider are disposed in the corresponding guide grooves from the inside to the outside. The inner circular surface of the fixed outer ring is provided with an annular eccentric groove with a height equivalent to that of the slider. The water inlet and the water outlet are disposed on the fixed outer ring and are connected to the annular eccentric groove. Under the action of the compression spring, the outer end of the slider extends into the annular eccentric groove, and a variable cavity is formed between every two adjacent sliders. The water inlet and the water outlet are respectively connected to the corresponding variable cavity.

[0014] By adopting the above technical solution, the negative pressure delivery mechanism serves as the core structure for driving the coolant circulation. It uses the rotation of the output shaft as its power source, avoiding the introduction of an additional drive device. When the drive ring rotates, the outer end of each slider extends or retracts under the constraint of the inner circular surface of the annular eccentric groove. During the rotation of the drive ring, the variable cavity volume formed between each pair of adjacent sliders either increases or decreases accordingly. When the variable cavity volume increases, it connects to the inlet, and coolant is drawn into the variable cavity. When the variable cavity volume decreases, it connects to the outlet, and coolant is forced out of the variable cavity, thus achieving unidirectional self-circulation of the coolant. This ingenious structure ensures the continuous and efficient operation of the heat dissipation system.

[0015] The invention is further configured such that two second sealing rings are provided on the outer circular surface of the fixed outer ring for forming a sealing fit with the inner circular surface of the shaft hole, the water inlet and the water outlet are disposed between the two second sealing rings, and a third sealing ring is provided on the outer circular surface of the drive ring corresponding to the left and right sides of the guide groove for forming a sealing fit with the fixed outer ring.

[0016] By adopting the above technical solution, it can be ensured that coolant leakage will not occur at the component docking position when the coolant circulates in the first flow channel, inlet, variable cavity, outlet, and second flow channel.

[0017] The present invention is further configured such that a first limiting step is provided on the inner wall of the shaft hole, the fixed outer ring is connected to the first limiting step by a plurality of screws, one end of the driving ring near the outer circular surface abuts against the first limiting step, and a limiting flange is provided on the inner circular surface of the fixed outer ring for abutting against the other end of the driving ring near the outer circular surface.

[0018] By adopting the above technical solution, reliable installation of the fixed outer ring and axial limiting of the drive ring can be achieved.

[0019] The invention is further configured such that the clutch mechanism includes a docking ring, a follower ring, a return spring, and multiple steel balls. The docking ring and the follower ring are sleeved on the outer periphery of the output shaft and are coaxially arranged. The docking ring and the follower ring are respectively provided with multiple first conical grooves and second conical grooves. Part of the steel ball is disposed in the corresponding first conical groove, and the other part of the steel ball is disposed in the corresponding second conical groove. A second limiting step is provided on the inner wall of the shaft hole. The end of the docking ring away from the follower ring abuts against the second limiting step near the outer circular surface. The return spring is disposed between the follower ring and the drive ring. The linkage ring is provided with multiple first linkage grooves at the end near the docking ring. The docking ring is provided with multiple first linkage protrusions for cooperating with the first linkage grooves. The follower ring is provided with multiple second linkage protrusions at the end near the drive ring. The drive ring is provided with multiple second linkage grooves for cooperating with the second linkage protrusions.

[0020] By adopting the above technical solution, when the docking ring and the follower ring rotate relative to each other, the axial component force of the conical groove on the steel ball causes the docking ring and the follower ring to move in opposite directions, thereby increasing the axial distance. Then, the concave structure enables linkage with the drive ring. When the docking ring stops rotating, the follower ring can be reset by the return spring. The clutch structure is simple and reliable, and the structure supports differential rotation of the follower ring while it is axially displaced relative to the docking ring, thereby adaptively aligning with the drive ring (concave-convex fit), making the structure more reliable.

[0021] The present invention is further configured such that a damping ring for forming a damping fit with the inner circular surface of the shaft hole is snapped onto the outer circular surface of the follower ring.

[0022] By adopting the above technical solution, the damping ring can be made of rubber or silicone. The damping ring increases the circumferential damping of the follower ring, making it more difficult for it to rotate circumferentially, so that it can move more smoothly axially under the push of the steel ball.

[0023] The present invention is further configured such that the follower ring and the drive ring are respectively provided with a first annular positioning groove and a second annular positioning groove for engaging with the two ends of the return spring.

[0024] By adopting the above technical solution, the return spring can be positioned, thereby improving its stability during installation and movement. Attached Figure Description

[0025] Figure 1 This is a schematic diagram of the overall structure of the present invention;

[0026] Figure 2 for Figure 1 Enlarged structural diagram of section A in the middle;

[0027] Figure 3 This is a cross-sectional view of the negative pressure conveying mechanism of the present invention;

[0028] Figure 4 This is a cross-sectional view of the fixed outer ring of the present invention;

[0029] Figure 5 This is a schematic diagram of the cooperative structure of the linkage ring, clutch mechanism and negative pressure conveying mechanism of the present invention.

[0030] In the diagram: 1. Housing; 2. Input shaft; 3. Output shaft; 4. Planetary gear assembly; 5. Shaft hole; 6. Circulating cooling device; 7. Drive component; 8. Linkage ring; 9. Clutch mechanism; 10. Negative pressure conveying mechanism; 11. First flow channel; 12. Second flow channel; 13. Inlet; 14. Outlet; 15. Linkage head; 16. Annular groove; 17. Mounting groove; 18. Pressure cap; 19. First sealing ring; 20. Guide block; 21. Guide groove; 22. Drive ring; 23. Fixed outer ring; 24. Telescopic assembly; 25. Guide groove; 26. Compression 27. Spring; 28. Slider; 29. ​​Annular eccentric groove; 30. Variable cavity; 31. Second sealing ring; 32. Third sealing ring; 33. First limiting step; 34. Limiting flange; 35. Connecting ring; 36. Follower ring; 37. Return spring; 38. Steel ball; 39. First conical groove; 40. Second conical groove; 41. Second limiting step; 42. First linkage groove; 43. First linkage protrusion; 44. Second linkage protrusion; 45. Second linkage groove; 46. Damping ring; 47. First annular positioning groove; 48. Second annular positioning groove. Detailed Implementation

[0031] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0032] Example: As attached Figures 1 to 5The deep-sea speed reducer shown includes a housing 1, an input shaft 2 and an output shaft 3 rotatably mounted on the housing 1, and a planetary gear assembly 4 disposed within the housing 1 for transmitting power between the input shaft 2 and the output shaft 3. The housing 1 has a shaft hole 5 for the output shaft 3 to pass through, and a circulating cooling device 6 is disposed within the shaft hole 5. The circulating cooling device 6 includes a drive component 7, a linkage ring 8, a clutch mechanism 9, and a negative pressure conveying mechanism 10. The housing 1 has a first flow channel 11 and a second flow channel 12 for filling with coolant. Multiple first flow channels 11 and second flow channels 12 can be provided, evenly distributed on the surface of the housing 1. Multiple first flow channels 11 are connected end-to-end, and multiple second flow channels 12 are also connected end-to-end. Both the first flow channels 11 and the second flow channels 12 are along the length of the housing 1. The first flow channel 11 and the second flow channel 12 are connected at their ends near the planetary gear assembly 4. The negative pressure conveying mechanism 10 is provided with an inlet 13 and an outlet 14. The ends of the first flow channel 11 and the second flow channel 12 away from the planetary gear assembly 4 are respectively connected to the inlet 13 and the outlet 14 of the negative pressure conveying mechanism 10. The linkage ring 8 is circumferentially linked and axially slidable on the outer periphery of the output shaft 3, and the outer circular surface of the linkage ring 8 is in contact with the inner circular surface of the shaft hole 5. The driving component 7 is connected to the linkage ring 8 to drive the linkage ring 8 to move axially, so that the linkage ring 8 has an engaged position that cooperates with the clutch mechanism 9 to drive the negative pressure conveying mechanism 10 to work and circulate coolant, and a disengaged position that disengages from the clutch mechanism 9 to stop the negative pressure conveying mechanism 10 from working. The coolant circulation can be driven by the movement state of the output shaft 3 itself, realizing the active transfer and efficient heat dissipation of the internal heat of the reducer, thereby overcoming the limitation of not being able to rely on external water cooling in the deep sea environment. Simultaneously, it can be used with a built-in control circuit board. The control circuit board is electrically connected to the drive motor via wires, and also electrically connected to the drive component 7 via wires. When the drive motor rotates at low speed (the speed range can be customized according to actual conditions), the control circuit board controls the movable end of the drive component 7 to retract, causing the linkage ring 8 to be in the disengaged position. At this time, when the output shaft 3 drives the linkage ring 8 to rotate, it will not drive the negative pressure conveying mechanism 10 to work through the clutch mechanism 9. When the drive motor rotates at high speed (the speed range can be customized according to actual conditions), the control circuit board controls the movable end of the drive component 7 to extend, causing the linkage ring 8 to be in the engaged position. At this time, when the output shaft 3 drives the linkage ring 8 to rotate, it drives the negative pressure conveying mechanism 10 to work through the clutch mechanism 9, causing the coolant in the first flow channel 11 and the second flow channel 12 to circulate. Since the two flow channels are partly located in the heat-generating area and partly located in the non-heat-generating area, heat exchange between the two areas can be quickly realized, and the heat is evenly distributed on the outer shell 1 (increasing the effective heat dissipation area) for heat dissipation, avoiding ineffective flow of coolant, which can significantly improve the heat dissipation effect of the reducer in the deep-sea environment, thereby ensuring its stable operation.

[0033] As attachedFigure 1 and attached Figure 2 As shown, the driving component 7 is an electromagnet. A linkage head 15 is provided on the movable end of the driving component 7. The linkage head 15 can be a flat cylindrical structure. The linkage ring 8 has an annular groove 16 at one end near the driving component 7 for the outer periphery of the linkage head 15 to be embedded. The driving component 7 uses an electromagnet, utilizing electromagnetic force to achieve rapid response and precise axial displacement of the movable end (iron core), ensuring the timeliness and accuracy of the linkage ring 8's movement, thereby stably triggering the switching action of the clutch mechanism 9. Furthermore, the movable end of the driving component 7 and the linkage ring 8 achieve axial linkage through a snap-fit ​​connection, resulting in a simple connection structure and convenient assembly / disassembly.

[0034] As attached Figure 2 As shown, a mounting groove 17 is provided on the outer wall of the outer casing 1. The mounting groove 17 communicates with the shaft hole 5. A pressure cap 18 for pressing the drive component 7 into the mounting groove 17 is connected to the outer end of the mounting groove 17 by screws. A first sealing ring 19 is provided between the pressure cap 18 and the outer casing 1. This design can realize the fixed installation of the drive component 7. The installation structure is simple and reliable, and the sealing performance is good, effectively preventing the intrusion of external seawater.

[0035] As attached Figure 2 As shown, a guide block 20 (which can be a key and keyway structure) is provided on the outer circular surface of the output shaft 3, and a guide groove 21 is provided on the inner circular surface of the linkage ring 8 along the axial direction for sliding engagement with the guide block 20. This design enables the linkage ring 8 to slide directionally (axially) on the output shaft 3, and realizes the switching between the engaged and disengaged positions.

[0036] As attached Figure 1 and attached Figure 2As shown, the negative pressure conveying mechanism 10 includes a drive ring 22 sleeved around the output shaft 3, a fixed outer ring 23 disposed around the drive ring 22, and multiple sets of telescopic components 24 disposed on the outer circular surface of the drive ring 22. The fixed outer ring 23 is fixedly connected to the inner wall of the shaft hole 5, and the outer circular surface of the fixed outer ring 23 is in contact with the inner circular surface of the shaft hole 5. The outer circular surface of the drive ring 22 is in contact with the inner circular surface of the fixed outer ring 23. The outer circular surface of the drive ring 22 is provided with multiple guide grooves 25, the number of which is equivalent to the number of telescopic components 24. The telescopic components 24 include a compression spring 26 and a slider 27. The compression spring 26... The slider 27 is positioned in the corresponding guide groove 25 from the inside out. The inner circular surface of the fixed outer ring 23 has an annular eccentric groove 28 with a height equivalent to that of the slider 27. The inlet 13 and outlet 14 are located on the fixed outer ring 23 and communicate with the annular eccentric groove 28. Under the action of the compression spring 26, the outer end of the slider 27 extends into the annular eccentric groove 28, and a variable cavity 29 is formed between every two adjacent sliders 27. The volume of each variable cavity 29 increases and decreases as the drive ring 22 rotates. The inlet 13 and outlet 14 are respectively connected to the corresponding variable cavity 29. The negative pressure conveying mechanism 10 serves as the core structure and is used to drive the coolant circulation. It uses the rotation of the output shaft 3 as the power source, avoiding the introduction of an additional drive device. When the drive ring 22 rotates, the outer end of each slider 27 extends or retracts under the constraint of the inner circular surface of the annular eccentric groove 28. During the rotation of the drive ring 22, the volume of the variable cavity 29 formed between each pair of adjacent sliders 27 either increases or decreases accordingly. When the volume of the variable cavity 29 increases, it is connected to the inlet 13, and the coolant is drawn into the variable cavity 29. When the volume of the variable cavity 29 decreases, it is connected to the outlet 14, and the coolant is forced out of the variable cavity 29, thereby realizing the unidirectional self-circulation of the coolant. The ingenious structure ensures the continuous and efficient operation of the heat dissipation system.

[0037] As attached Figure 2 As shown, the outer surface of the fixed outer ring 23 is provided with two second sealing rings 30 for sealing with the inner surface of the shaft hole 5. The water inlet 13 and the water outlet 14 are located between the two second sealing rings 30. The outer surface of the drive ring 22 is provided with a third sealing ring 31 on each side of the guide groove 25 for sealing with the fixed outer ring 23. This design ensures that when the coolant circulates in the first flow channel 11, the water inlet 13, the variable cavity 29, the water outlet 14, and the second flow channel 12, coolant leakage will not occur at the component docking position.

[0038] As attached Figure 2As shown, a first limiting step 32 is provided on the inner wall of the shaft hole 5. The fixed outer ring 23 is connected to the first limiting step 32 by multiple screws. One end of the driving ring 22 near the outer circular surface abuts against the first limiting step 32. The inner circular surface of the fixed outer ring 23 is provided with a limiting flange 33 for abutting against the other end of the driving ring 22 near the outer circular surface. This design can achieve reliable installation of the fixed outer ring 23 and axial limiting of the driving ring 22.

[0039] As attached Figures 2 to 5 As shown, the clutch mechanism 9 includes a docking ring 34, a follower ring 35, a return spring 36, and multiple steel balls 37. The docking ring 34 and the follower ring 35 are sleeved on the outer periphery of the output shaft 3 and are coaxially arranged. The docking ring 34 and the follower ring 35 are respectively provided with multiple first conical grooves 38 and second conical grooves 39. Part of the steel balls 37 are disposed in the corresponding first conical grooves 38, and the other part of the steel balls 37 are disposed in the corresponding second conical grooves 39. A second limiting step 40 is provided on the inner wall of the shaft hole 5. The docking ring 34 is away from the follower ring. One end of ring 35 abuts against the second limiting step 40 near the outer circular surface. The reset spring 36 is disposed between the follower ring 35 and the drive ring 22. The linkage ring 8 is provided with a plurality of first linkage grooves 41 near the docking ring 34. The docking ring 34 is provided with a plurality of first linkage protrusions 42 for cooperating with the first linkage grooves 41. The follower ring 35 is provided with a plurality of second linkage protrusions 43 near the drive ring 22. The drive ring 22 is provided with a plurality of second linkage grooves 44 for cooperating with the second linkage protrusions 43. When the docking ring 34 and the follower ring 35 rotate relative to each other, the axial component of the force on the steel ball 37 through the conical groove causes the docking ring 34 and the follower ring 35 to move in opposite directions, thereby increasing the axial distance. Then, the linkage with the drive ring 22 is achieved through the concave structure. When the docking ring 34 stops rotating, the follower ring 35 can be reset by the return spring 36. The clutch structure is simple and reliable, and the structure supports the follower ring 35 to rotate differentially while displacing axially relative to the docking ring 34, thereby adaptively aligning with the drive ring 22 (concave-convex fit), making the structure more reliable.

[0040] As attached Figure 2 As shown, a damping ring 45 is engaged on the outer circular surface of the follower ring 35 to form a damping fit with the inner circular surface of the shaft hole 5. The damping ring 45 can be made of rubber or silicone. The damping ring 45 increases the circumferential damping of the follower ring 35, making it more difficult to rotate circumferentially, so that it can move more smoothly axially under the push of the steel ball 37.

[0041] As attached Figure 2As shown, the follower ring 35 and the drive ring 22 are respectively provided with a first annular positioning groove 46 and a second annular positioning groove 47 for engaging with both ends of the return spring 36. This design can position the return spring 36 and improve its stability during installation and movement.

Claims

1. A deep-sea speed reducer, comprising a housing (1), an input shaft (2) and an output shaft (3) rotatably mounted on the housing (1), and a planetary gear assembly (4) disposed within the housing (1) for transmitting power between the input shaft (2) and the output shaft (3); characterized in that: The outer casing (1) is provided with a shaft hole (5) for the output shaft (3) to pass through. A circulating heat dissipation device (6) is provided in the shaft hole (5). The circulating heat dissipation device (6) includes a drive component (7), a linkage ring (8), a clutch mechanism (9), and a negative pressure conveying mechanism (10). The outer casing (1) is provided with a first flow channel (11) and a second flow channel (12) for filling with coolant. The first flow channel (11) and the second flow channel (12) are both arranged along the length of the outer casing (1). The first flow channel (11) and the second flow channel (12) are connected together at one end near the planetary gear assembly (4). The negative pressure conveying mechanism (10) is provided with an inlet (13) and an outlet (14). The first flow channel (13) is provided with an inlet (13) and an outlet (14). 1) The end of the second flow channel (12) away from the planetary gear assembly (4) is connected to the inlet (13) and outlet (14) of the negative pressure conveying mechanism (10) respectively. The linkage ring (8) is circumferentially linked and axially slidable on the outer periphery of the output shaft (3). The driving member (7) is connected to the linkage ring (8) to drive the linkage ring (8) to move axially, so that the linkage ring (8) has an engaging position that cooperates with the clutch mechanism (9) to drive the negative pressure conveying mechanism (10) to work and circulate the coolant, and a disengaging position that disengages from the clutch mechanism (9) to stop the negative pressure conveying mechanism (10) from working. The negative pressure conveying mechanism (10) includes a drive ring (22) sleeved on the outer periphery of the output shaft (3) and a drive ring (22) set on the outer periphery of the output shaft (3). The drive ring (22) has a fixed outer ring (23) on its outer periphery and multiple sets of telescopic components (24) on the outer circular surface of the drive ring (22); the clutch mechanism (9) includes a docking ring (34), a follower ring (35), a return spring (36), and multiple steel balls (37). The docking ring (34) and the follower ring (35) are sleeved on the outer periphery of the output shaft (3) and are coaxially arranged. The docking ring (34) and the follower ring (35) are respectively provided with multiple first conical grooves (38) and second conical grooves (39). Part of the steel ball (37) is set in the corresponding first conical groove (38), and the other part of the steel ball (37) is set in the corresponding second conical groove (39). The inner wall of the shaft hole (5) is provided with The second limiting step (40) is located at the end of the docking ring (34) away from the follower ring (35) and near the outer surface, where it abuts against the second limiting step (40). The reset spring (36) is located between the follower ring (35) and the drive ring (22). The linkage ring (8) has multiple first linkage grooves (41) at the end near the docking ring (34). The docking ring (34) has multiple first linkage protrusions (42) for cooperating with the first linkage grooves (41). The follower ring (35) has multiple second linkage protrusions (43) at the end near the drive ring (22). The drive ring (22) has multiple second linkage grooves (44) for cooperating with the second linkage protrusions (43).

2. The deep-sea speed reducer according to claim 1, characterized in that: The driving component (7) is an electromagnet. The movable end of the driving component (7) is provided with a linkage head (15). The linkage ring (8) is provided with an annular groove (16) at one end near the driving component (7) for the outer periphery of the linkage head (15) to be embedded.

3. A deep-sea speed reducer according to claim 2, characterized in that: The outer wall of the outer casing (1) is provided with an installation groove (17), the installation groove (17) is connected to the shaft hole (5), and the outer end of the installation groove (17) is connected by screws to a pressure cap (18) for pressing the drive component (7) in the installation groove (17). A first sealing ring (19) is provided between the pressure cap (18) and the outer casing (1).

4. A deep-sea speed reducer according to claim 2, characterized in that: The output shaft (3) has a guide block (20) on its outer circular surface, and the linkage ring (8) has a guide groove (21) extending axially on its inner circular surface for sliding cooperation with the guide block (20).

5. A deep-sea speed reducer according to claim 2, characterized in that: The fixed outer ring (23) is fixedly connected to the inner wall of the shaft hole (5), and the outer circular surface of the fixed outer ring (23) is in contact with the inner circular surface of the shaft hole (5). The outer circular surface of the driving ring (22) is in contact with the inner circular surface of the fixed outer ring (23). The outer circular surface of the driving ring (22) is provided with a plurality of guide grooves (25) in a number equivalent to that of the telescopic component (24). The telescopic component (24) includes a compression spring (26) and a slider (27). The compression spring (26) and the slider (27) are arranged from the inside to the outside in the corresponding guide grooves (25). The inner circular surface of the fixed outer ring (23) is provided with an annular eccentric groove (28) with a height equivalent to that of the slider (27). The water inlet (13) and the water outlet (14) are provided on the fixed outer ring (23) and are connected to the annular eccentric groove (28). The outer end of the slider (27) extends into the annular eccentric groove (28) under the action of the compression spring (26), and a variable cavity (29) is formed between every two adjacent sliders (27). The water inlet (13) and the water outlet (14) are respectively connected to the corresponding variable cavity (29).

6. A deep-sea speed reducer according to claim 5, characterized in that: The outer surface of the fixed outer ring (23) is provided with two second sealing rings (30) for forming a sealing fit with the inner surface of the shaft hole (5). The water inlet (13) and the water outlet (14) are located between the two second sealing rings (30). The outer surface of the drive ring (22) is provided with a third sealing ring (31) for forming a sealing fit with the fixed outer ring (23) on the left and right sides of the guide groove (25).

7. A deep-sea speed reducer according to claim 5, characterized in that: The inner wall of the shaft hole (5) is provided with a first limiting step (32). The fixed outer ring (23) is connected to the first limiting step (32) by multiple screws. One end of the drive ring (22) near the outer circular surface abuts against the first limiting step (32). The inner circular surface of the fixed outer ring (23) is provided with a limiting flange (33) for abutting against the other end of the drive ring (22) near the outer circular surface.

8. A deep-sea speed reducer according to claim 1, characterized in that: The outer circular surface of the follower ring (35) is fitted with a damping ring (45) for forming a damping fit with the inner circular surface of the shaft hole (5).

9. A deep-sea speed reducer according to claim 1, characterized in that: The follower ring (35) and the drive ring (22) are respectively provided with a first annular positioning groove (46) and a second annular positioning groove (47) for engaging with both ends of the return spring (36).

Images