A heat-dissipating gear reducer

Abstract

This invention relates to the field of speed reducer technology and discloses a heat-dissipating gear reducer, including a housing composed of a detachable upper cover and a bottom shell, with a transmission system inside; one end of the secondary transmission unit is installed on the side wall of the upper cover through a shaft seal, and the other end has an axial locking groove; a form-changing assembly penetrating the upper cover is provided on the corresponding side, including a pin rod and a locking and releasing mechanism arranged circumferentially at the end, which can move axially to lock / unlock with the locking groove; a trapezoidal guide seat is rigidly connected to the surface of the pin rod on the outside of the locking and releasing mechanism, and an oil volume adjustment mechanism is provided around it and a flow guide assembly is provided between it and the secondary gear set; during operation, the locking and releasing mechanism couples with the locking groove, causing the trapezoidal guide seat to push the receiving and releasing spoon to expand outward, adjusting the oil immersion depth of the outer oil spoon; when the oil drain hole is aligned with the oil drain groove, a directional rinsing oil supply is formed, and the lubricating oil is diffused through gear meshing, significantly improving the system's heat dissipation and lubrication efficiency.

Description

Technical Field

[0001] This invention relates to the field of speed reducer technology, and more specifically to a heat-dissipating gear reducer. Background Technology

[0002] As a core precision mechanical device that achieves speed conversion and torque amplification through gear transmission, the speed reducer is widely used in various industrial transmission systems. Its performance directly affects the transmission efficiency, operational reliability, and service life of the entire system. During the long-term operation of the speed reducer, the continuous meshing between gears inevitably leads to wear on the contact surfaces. Therefore, optimizing the lubrication performance of gears, especially high-speed gears, is crucial for improving the overall performance of the speed reducer.

[0003] In the prior art, various lubrication structures have been developed to improve the lubrication of gears inside reducers and extend their service life. For example, Chinese Patent Publication No. CN221838824U discloses an RV reducer technical solution. This solution includes a connecting base, a transmission rod, a first gear, a second gear, a crankshaft, a transmission gear plate, a transmission pinwheel, and an oiling mechanism disposed inside the transmission pinwheel. Its core is that the oiling mechanism uses a water-absorbing material to absorb lubricant and conducts the lubricant to the oil supply component (such as the fluid transfer part) through the siphon effect. The aim is to continuously replenish lubricant to the gear meshing area without disassembling the reducer, so as to alleviate the wear problem.

[0004] However, this structure still has the following technical shortcomings:

[0005] When the transmission system is running at high speed, the temperature of the gear meshing surface rises sharply due to intense friction. At this time, relying solely on the adsorption and siphon effect of water-absorbing materials to passively supply lubricant is not only insufficient in supply and difficult to match the high-speed demand, but also the adsorption efficiency and fluidity of the lubricant may be further reduced at high temperatures. This results in the lubricant failing to form a sufficient and effective oil film on the gear surface, leading to a significant decrease in lubrication effect. At the same time, the lubricant, as a heat dissipation medium, also suffers from poor heat dissipation due to insufficient coverage, which exacerbates gear wear and ultimately restricts the improvement of equipment lifespan. Summary of the Invention

[0006] In order to overcome the above-mentioned defects of the prior art, the present invention provides a heat-dissipating gear reducer to solve the problems of poor lubrication and heat dissipation effect and accelerated gear wear caused by the passive siphon lubrication method in the background art.

[0007] This invention provides the following technical solution: a heat-dissipating gear reducer, including a housing, the housing being composed of a detachable upper cover and a bottom cover, a transmission system being assembled inside the upper cover, the transmission system being composed of a primary transmission part, a secondary transmission part and a tertiary transmission part meshing with each other, the secondary transmission part including a gear shaft, the surface of which is rigidly sleeved with a secondary gear set, one end of the gear shaft being rotatably mounted on the side wall of the upper cover through a shaft seal, the other end having an axially extending locking groove, a form-changing assembly being provided on the opposite side of the gear shaft, movably penetrating the other side wall of the upper cover, the form-changing assembly including a pin rod, the end of the pin rod being equipped with a circumferentially arranged locking and unlocking mechanism, the locking and unlocking mechanism being axially movable along the rotating locking groove to achieve locking or unlocking action; a trapezoidal guide seat being rigidly connected to the outside of the locking and unlocking mechanism, circumferentially arranged on the surface of the pin rod, an oil quantity adjustment mechanism being driven around the trapezoidal guide seat, and a flow guiding assembly being provided between it and the secondary gear set;

[0008] The oil volume adjustment mechanism includes a receiving tray, which is rotatably mounted on the side wall of the guide assembly. The receiving tray has conductive slides corresponding to the trapezoidal guide seat. A receiving and dispensing spoon is slidably sleeved in the conductive slide. The bottom end of each receiving and dispensing spoon is slidably engaged with the trapezoidal guide seat, and force is transmitted through complementary inclined contact surfaces. When the trapezoidal guide seat moves axially with the pin rod, it can push the receiving and dispensing spoon to expand outward along the conductive slide of the receiving tray, so that the oil immersion depth is reduced and the oil holding capacity is increased when the receiving and dispensing spoon rotates. An oil drain groove is opened at the top of the pipe.

[0009] Furthermore, the oil volume adjustment mechanism also includes a journal integrally formed on the side wall of the receiving tray, which is rotatably mounted to the flow guide assembly; the flow guide assembly includes a tube body whose bottom is fixed to the bottom wall of the upper cover by a mounting bracket rigidly connected to it, and the front side of the tube body is provided with a rotatable interface for the journal to be inserted and rotated.

[0010] Furthermore, the outer end of the mode switching assembly is provided with a linear actuator fixedly installed outside the upper cover. The telescopic shaft of the linear actuator is rigidly connected to the pin rod, which is used to drive the pin rod to move linearly along the inner cavity of the locking groove coaxially arranged therein.

[0011] Furthermore, the locking mechanism consists of a claw seat, a claw head, and a first spring, wherein the claw seat is rigidly connected to the end of the pin rod, the first spring is installed inside the claw seat, and the top of the first spring is connected to a claw head that can elastically extend and retract along the claw seat.

[0012] Furthermore, a rounded chamfer is provided at the top of the claw head to form a mating relationship with the groove on the surface of the locking groove. The rounded chamfer can fit with the cut edge of the groove.

[0013] Furthermore, the receiving spoon is composed of an inner sliding block, a middle sliding block, and an outer oil spoon, which are rigidly connected sequentially from the inside to the outside along the transmission slide. When the trapezoidal guide seat moves to fully fit with the inner sliding block, the outer edge of the outer oil spoon and the edge of the receiving tray form a close fit.

[0014] Furthermore, the outer oil spoon includes a spoon box, and a guide tube is provided on one side of the spoon box that rotates in the circumferential direction. The guide tube extends into the middle of the inner cavity of the spoon box and its diameter gradually decreases. An oil drain hole is provided on the bottom wall of the spoon box near the tube body, and the bottom wall of the spoon box is set as a downward-sloping spoon bottom.

[0015] Furthermore, a sealing ring connected to the oil drain groove is provided on the outer ring layer where the oil drain groove is located, and the length ratio of the oil drain groove to the sealing ring is 1:3; the bottom wall of the oil drain groove is provided with a drainage rib that slopes downward toward the tooth surface of the large gear ring section.

[0016] Furthermore, there is a gap between the inner wall of the middle slider rod and the conduction slide; an elastic partition is provided in the gap, with its bottom end fixedly connected to the inner wall of the conduction slide and its top end fixedly connected to the side of the bottom wall of the spoon box near the tube body.

[0017] Furthermore, the bottom of the tube is equipped with a bearing cavity, and a guide rail and a positioning post are fixedly installed on the bottom wall of the bearing cavity. A turbulence part that can slide along the guide rail is provided inside the bearing cavity. The turbulence part includes a contact brush plate attached to the bottom wall of the secondary gear set. The side of the contact brush plate away from the secondary gear set is rigidly connected to the contact head through a swing arm. A second spring is connected between the contact head and the positioning post. The contact head extends through the bearing cavity into the outer ring layer.

[0018] The technical effects and advantages of this invention are as follows:

[0019] This invention locks the locking mechanism with the locking groove by axial movement of the form-changing assembly. Under the action of the first spring, the claw head inserts into the locking groove, realizing coaxial coupling between the gear shaft and the form-changing assembly. Simultaneously, the trapezoidal guide seat pushes the receiving spoon to expand outward along the receiving tray slide, so that the oil immersion depth decreases and the oil holding capacity increases when the outer oil spoon rotates. When the oil drain hole moves to the oil drain groove, it forms a directional rinsing oil supply. Through the meshing transmission of the secondary gear set with the primary and tertiary transmission parts, the lubricating oil is diffused, significantly improving the system's heat dissipation and lubrication efficiency.

[0020] This invention utilizes the periodic contact of the outer oil spoon as it extends to the outer ring layer and moves circumferentially. This causes the swing arm and contact brush plate to reciprocate under the elastic restoring force of the second spring. This dynamic motion, combined with the rotational motion of the large gear ring segment, creates a composite trajectory, significantly enhancing the oil flow characteristics in the secondary gear set area and the oil film adhesion performance at the bottom of the large gear ring segment. This further improves the system's heat dissipation and lubrication efficiency. Attached Figure Description

[0021] Figure 1 This is a schematic diagram of the overall structure of the present invention.

[0022] Figure 2 This is a schematic diagram of the overall structure and housing of the present invention.

[0023] Figure 3 This is a schematic diagram of the connection structure of the secondary transmission unit, the injection system, and the turbulence unit of the present invention.

[0024] Figure 4 For the present invention Figure 3 A schematic diagram from the other side of the structure.

[0025] Figure 5 This is a schematic diagram of the injection system not connected to the secondary transmission unit in the standard mode of the present invention.

[0026] Figure 6 For the present invention Figure 5 Schematic diagram of the structure at point A in the middle.

[0027] Figure 7 This is a schematic diagram of the connection structure between the flow guiding assembly and the flow disturbance part of the present invention.

[0028] Figure 8 For the present invention Figure 7 A schematic diagram from the other side of the structure.

[0029] Figure 9 For the present invention Figure 7 A further analytical diagram of the structure.

[0030] Figure 10 For the present invention Figure 9 Schematic diagram of the structure at point B.

[0031] Figure 11 For the present invention Figure 5 Schematic diagram of the connection structure between the mid-mode switching assembly and the oil quantity adjustment mechanism.

[0032] Figure 12 This is a schematic diagram of the docking state between the injection system and the secondary transmission unit under the heat dissipation mode of the present invention.

[0033] Figure 13 For the present invention Figure 12 Schematic diagram of the structure at point C.

[0034] Figure 14 For the present invention Figure 12 Schematic diagram of the structure at point D.

[0035] Figure 15 For the present invention Figure 12 Schematic diagram of the connection structure between the central spoon and the trapezoidal guide seat.

[0036] The attached diagram is labeled as follows: 1. Housing; 11. Top cover; 12. Bottom shell; 2. Primary transmission unit; 3. Secondary transmission unit; 31. Gear shaft; 32. Secondary gear set; 321. Large gear ring segment; 322. Small gear ring segment; 33. Locking groove; 4. Tertiary transmission unit; 5. Mode switching assembly; 51. Pin rod; 52. Trapezoidal guide seat; 53. Locking and releasing mechanism; 531. Claw seat; 532. Claw head; 533. First spring; 6. Oil quantity adjustment mechanism; 61. Storage tray; 62. Storage spoon; 621. Inner slider. Section; 622, Middle slider rod; 623, Outer oil spoon; 6231, Spoon box; 6232, Guide tube; 6233, Downward tilting spoon bottom; 6234, Oil drain hole; 63, Journal; 64, Elastic partition; 7, Guide assembly; 71, Tube body; 72, Oil drain groove; 73, Sealing ring; 74, Adapter; 75, Bearing cavity; 76, Guide rail; 77, Positioning post; 8, Turbulence section; 81, Contact brush plate; 82, Swing arm; 83, Contact; 84, Second spring; 9, Mounting bracket; 10, Linear actuator. Detailed Implementation

[0037] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings. In addition, the forms of the various structures described in the following embodiments are merely illustrative. The heat dissipation gear reducer involved in the present invention is not limited to the structures described in the following embodiments. All other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0038] Reference Figure 1 - Figure 5 This invention provides a heat-dissipating gear reducer, including a housing 1, which is composed of a detachable upper cover 11 and a bottom cover 12. A transmission system is assembled inside the upper cover 11. The transmission system consists of a primary transmission unit 2, a secondary transmission unit 3, and a tertiary transmission unit 4 that are meshed with each other. The secondary transmission unit 3 includes a gear shaft 31, whose surface is rigidly sleeved with a secondary gear set 32. One end of the gear shaft 31 is rotatably mounted on the side wall of the upper cover 11 through a shaft seal, and the other end has an axially extending locking groove 33. Near the locking groove 33, there is a filling system composed of a mode switching assembly 5, an oil quantity adjustment mechanism 6, and a flow guiding assembly 7.

[0039] On the opposite side of the gear shaft 31, there is a form-changing assembly 5 that can move through the other side wall of the upper cover 11. The form-changing assembly 5 includes a pin rod 51. The end of the pin rod 51 is equipped with a circumferentially arranged locking and unlocking mechanism 53. The locking and unlocking mechanism 53 can move axially along the rotating locking groove 33 to achieve locking or unlocking. A trapezoidal guide seat 52 is rigidly connected to the outside of the locking and unlocking mechanism 53 and is circumferentially arranged on the surface of the pin rod 51. An oil quantity adjustment mechanism 6 is driven around the trapezoidal guide seat 52. A flow guide assembly 7 is fixedly installed on the bottom wall of the upper cover 11 between the oil quantity adjustment mechanism 6 and the secondary gear set 32.

[0040] In this embodiment, it should be noted that the first-stage transmission unit 2, the second-stage transmission unit 3, and the third-stage transmission unit 4 are all installed inside the upper cover 11 as rotating support components through shaft seals such as bearings, to ensure that each component achieves stable rotational motion with low friction and high coaxiality within the housing.

[0041] The secondary gear set 32 ​​adopts an integrated injection molding process for the large gear ring segment 321 and the small gear ring segment 322. The large gear ring segment 321 has a large radius structure as its main body, and forms a smooth and gradual mechanical load-bearing structure with the small gear ring segment 322 with a small radius through an inclined transition surface. This allows the large gear ring segment 321 to receive the lubricating oil supplied from the guide assembly 7 and guide it to the surface of the small gear ring segment 322 along the inclined transition surface. Through the meshing transmission of the secondary gear set 32 ​​with the primary transmission unit 2 and the tertiary transmission unit 4, the lubricating oil is diffused, achieving heat dissipation and lubrication efficiency.

[0042] The outer end of the form switching assembly 5 is provided with a linear actuator 10 fixedly installed outside the upper cover 11. The telescopic shaft of the linear actuator 10 is rigidly connected to the pin rod 51 and is used to drive the pin rod 51 to move linearly along the inner cavity of the locking groove 33 coaxially arranged therein. The linear actuator 10 can also be replaced by other equivalent structures that can realize the axial telescopic traction function of the pin rod 51.

[0043] To enable the locking and unlocking mechanism 53 to quickly lock or unlock with the rotating locking groove 33 when it moves axially with the pin 51, the structure of the locking and unlocking mechanism 53 is optimized: the structure consists of a claw seat 531, a claw head 532, and a first spring 533. The claw seat 531 is rigidly connected to the end of the pin 51, and the first spring 533 is installed inside the claw seat 531. The top of the first spring 533 is connected to the claw head 532, which can elastically extend and retract along the claw seat 531. This design ensures that the claw head 532 can quickly respond to changes in axial displacement and achieve engagement and disengagement with the locking groove 33.

[0044] A rounded chamfer is provided at the top of the claw 532, which forms a mating relationship with the slot on the surface of the locking groove 33. This rounded chamfer can fit with the cut edge of the slot. When the claw 532 moves in the slot and contacts the cut edge, it can move down along the cut edge and compress the first spring 533. When the claw 532 is completely disengaged from the slot, it is confined inside the claw seat 531 by the locking groove 33, thereby realizing the rapid unlocking of the locking and unlocking mechanism 53 and the locking groove 33. During reverse movement, this structure can effectively complete the locking action of the two, ensuring that the gear shaft 31 and the form switching assembly 5 achieve stable coaxial coupling. This optimized design significantly improves the reliability and response speed of the locking / unlocking action through the synergistic effect of geometric fit and the elastic element first spring 533 (see Figure 6 , Figure 11 and Figure 13 ).

[0045] Reference Figure 4 - Figure 11 , Figure 12 - Figure 15 The oil volume adjustment mechanism 6 includes a receiving tray 61, which is rotatably mounted on the side wall of the guide assembly 7. The receiving tray 61 is provided with conductive slides corresponding to the trapezoidal guide seat 52. A receiving spoon 62 is slidably sleeved in the conductive slide. The bottom end of each receiving spoon 62 is slidably engaged with the trapezoidal guide seat 52, and force is transmitted through complementary inclined contact surfaces. When the trapezoidal guide seat 52 moves axially with the pin rod 51, it can push the receiving spoon 62 to expand outward along the conductive slide of the receiving tray 61, so that the oil immersion depth of the receiving spoon 62 decreases and the oil holding capacity increases when the receiving spoon 62 rotates.

[0046] The oil level adjustment mechanism 6 also includes a journal 63 integrally formed on the side wall of the storage tray 61, which is rotatably mounted to the flow guide assembly 7; the flow guide assembly 7 includes a tube body 71 whose bottom is fixed to the bottom wall of the upper cover 11 by a mounting bracket 9 rigidly connected to it, and a rotatable interface 74 is provided on the front side of the tube body 71 for the journal 63 to be inserted and rotated; an oil drain groove 72 is provided on the top of the tube body 71.

[0047] In this embodiment, it should be specifically noted that the receiving spoon 62 is composed of an inner sliding block 621, a middle sliding block 622, and an outer oil spoon 623, which are rigidly connected sequentially from the inside to the outside along the transmission slide. When the trapezoidal guide seat 52 moves to fully engage with the inner sliding block 621, the outer edge of the outer oil spoon 623 forms a close fit with the circular edge of the storage tray 61. The circumferentially arranged trapezoidal guide seat 52 moves axially with the pin 51, which can gradually push up the receiving spoon 62 that is slidingly engaged with it in all directions, so that the receiving spoon 62 can retract outward along the transmission slide of the storage tray 61, causing the outer oil spoon 623 to expand from the inner ring layer to the outer ring layer (see...). Figure 6 );

[0048] To improve the leakage problem of the outer oil ladle 623 during the process of transferring oil from the lowest point to the highest point after being filled, the structure of the outer oil ladle 623 and the guide assembly 7 is further optimized. Specifically, the outer oil ladle 623 includes a ladle box 6231, and a guide tube 6232 is provided on the side of the ladle box 6231 that rotates circumferentially. The guide tube 6232 extends towards the middle of the inner cavity of the ladle box 6231 and its diameter gradually decreases. An oil drain hole 6234 is opened on the bottom wall of the ladle box 6231 near the tube body 71. The bottom wall of the ladle box 6231 is set as a downward-sloping ladle bottom 6233 (see...). Figure 13 );

[0049] A sealing ring 73 connected to the oil drain groove 72 is also provided on the outer ring layer. The length ratio of the oil drain groove 72 to the sealing ring 73 is 1:3. The bottom wall of the oil drain groove 72 is provided with a guide rib that slopes downward toward the tooth surface of the large gear ring section 321. When the oil drain hole 6234 of the outer oil spoon 623 moves to the outer ring layer where the oil drain groove 72 and the sealing ring 73 are located, it is blocked and sealed at the sealing ring 73. The lubricating oil collected can be discharged only when passing through the oil drain groove 72. The guide rib in the oil drain groove 72 guides the directional rinsing oil supply to the secondary gear set 32.

[0050] To further improve the drainage of oil at the highest point of the oil drain hole 6234 and prevent oil from flowing back through the gap between the spoon box 6231 and the guide slide, so as to fully introduce the oil into the oil drain groove 72; a gap is left between the inner wall of the middle slider rod 622 and the guide slide; an elastic partition 64 is provided in the gap, the bottom end of which is fixedly connected to the inner wall of the guide slide, and the top end is fixedly connected to the side of the bottom wall of the spoon box 6231 near the tube body 71 (see...). Figure 13 The elastic partition 64 can adapt to the expansion or contraction of the outer oil spoon 623, so that when the outer oil spoon 623 expands to the outer ring layer, the extended elastic partition 64 can seal the gap between the spoon box 6231 and the transmission slide, and fully introduce the oil into the oil drain trough 72.

[0051] To further improve the heat dissipation efficiency and lubrication effect of the transmission system, a bearing cavity 75 is assembled at the bottom of the tube body 71. A guide rail 76 and a positioning post 77 are fixedly installed on the bottom wall of the bearing cavity 75. A turbulence part 8 that can slide along the guide rail 76 is provided in the bearing cavity 75. The turbulence part 8 includes a contact brush plate 81 attached to the bottom wall of the secondary gear set 32. The side of the contact brush plate 81 away from the secondary gear set 32 ​​is rigidly connected to a contact head 83 through a swing arm 82. A second spring 84 is connected between the contact head 83 and the positioning post 77. The contact head 83 extends into the outer ring layer through the bearing cavity 75. When the outer oil spoon 623 extends to the outer ring layer and performs circumferential displacement, it triggers the contact brush plate 81 to swing. This swing and the autonomous rotation of the large gear ring segment 321 generate a composite trajectory. The dynamic swing enhances the oil flow characteristics in the area near the secondary gear set 32 ​​and strengthens the oil film adhesion performance at the bottom of the large gear ring segment 321.

[0052] Working principle of this invention:

[0053] To achieve intelligent monitoring of the reducer's temperature status, temperature sensors can be installed at key nodes in the transmission system, such as beside the secondary transmission unit 3. When the operating temperature exceeds a preset threshold, the temperature sensor automatically generates a high-temperature alarm signal and transmits it to the main control unit, triggering the linear actuator 10 to initiate a forced cooling program in the injection system. Simultaneously, a manual intervention channel is maintained. When operators subjectively perceive abnormally high temperatures in the reducer, they can directly trigger the same control command process via the operation panel, switching the injection system from standard mode to heat dissipation mode (i.e., the forced cooling program). All control commands are uniformly coordinated and executed through the main control unit, ensuring seamless integration of automatic warning and manual intervention.

[0054] When the transmission system experiences abnormally high temperatures, the filling system switches to a heat dissipation mode according to the following mechanical linkage sequence: the telescopic shaft of the linear actuator 10 carries the form-changing assembly 5 and moves axially toward the side closer to the secondary transmission unit 3, so that the locking mechanism 53 locks with the locking groove 33, and the receiving spoon 62 is pushed outward by the trapezoidal guide seat 52 to complete the expansion and transformation; specifically, the locking mechanism 53 moves with the pin rod 51 and inserts inward along the locking groove 33, the claw head 532 enters the groove area of ​​the locking groove 33, and as the shaft system of the gear shaft 31 rotates, when the claw head 532 is aligned with the groove, it loses the constraint of the side wall of the locking groove 33 and extends outward along the claw seat 531 under the elastic force of the first spring 533 to insert into the groove, realizing the coaxial rotational coupling of the gear shaft 31 and the form-changing assembly 5; at the same time, the circumferentially arranged trapezoidal guide seat 52 moves axially with the pin rod 51, and can gradually push up the receiving spoon 62 that slides and fits with it in all directions, so that The receiving spoon 62 can retract outward along the guide slide of the storage tray 61, causing the outer oil spoon 623 to expand from the inner ring layer to the outer ring layer. The expansion distance of the outer oil spoon 623 is positively correlated with the axial displacement of the pin rod 51. When the claw head 532 enters the slot and continues to slide inward, the pin rod 51 can also drive the receiving spoon 62, which is engaged with it, to move circumferentially through the trapezoidal guide seat 52, causing the receiving spoon 62 and the storage tray 61 to rotate around the pin rod 51 as the axis along the side wall of the tube body 71. As the outer oil spoon 623 extends further, its immersion depth decreases when it reaches its lowest point, thus increasing the amount of lubricating oil it can hold. This continues until the oil drain hole 6234 of the outer oil spoon 623 moves to the outer ring layer where the oil drain groove 72 and sealing ring 73 are located. At the sealing ring 73, it is blocked and sealed, allowing the collected lubricating oil to drain only when passing through the oil drain groove 72. The lubricating oil is then guided by the guide ribs within the oil drain groove 72 to form a directional rinsing oil supply to the secondary gear set 32. Figure 5 - Figure 11 Towards Figure 12 - Figure 15(The state transition shown); the large gear ring section 321 and the small gear ring section 322, through meshing with the first-stage transmission unit 2 and the third-stage transmission unit 4, diffuse the lubricating oil to the entire transmission system, significantly improving heat dissipation and lubrication efficiency;

[0055] When the outer oil spoon 623 extends to the outer ring layer and performs circumferential displacement, the contact action of its periodic pressing contact 83 will drive the linkage contact 83, swing arm 82 and contact brush plate 81 to form a reciprocating swing state under the elastic restoring force of the second spring 84. This swing and the autonomous rotation of the large gear ring section 321 generate a compound trajectory. Through dynamic swing, the oil flow characteristics in the area near the secondary gear set 32 ​​are enhanced, and the oil film adhesion performance at the bottom of the large gear ring section 321 is strengthened, thereby further improving the heat dissipation efficiency and lubrication effect of the transmission system.

[0056] When the temperature of the transmission system returns to the standard value, the filling system will switch to the standard mode according to the reverse operation mechanism: the linear actuator 10 telescopic shaft drives the form switching assembly 5 to move axially in the opposite direction to the secondary transmission part 3, causing the claw head 532 to move down along the tangent edge of the slot and compress the first spring 533. After the claw head 532 completely exits the slot, it is locked in the claw seat 531 by the locking groove 33, realizing the separation of the locking and releasing mechanism 53 from the locking groove 33; simultaneously, the axial outward movement of the trapezoidal guide seat 52 pulls the circumferentially arranged receiving and releasing spoons 62 to retract inward along the transmission slide of the receiving tray 61, and the outer oil spoon 623 gradually retracts into the receiving tray 61 and terminates the circumferential movement, which interrupts the oil delivery function and stops the oil swinging action of the contact brush plate 81, and finally makes the system completely reset to the initial state (from Figure 12 - Figure 15 Towards Figure 5 - Figure 11 (The state transition is shown).

[0057] The above is merely a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any equivalent substitutions or modifications made by those skilled in the art within the scope of the technology disclosed in the present invention, in accordance with the technical plan and its improved concept, should be included under the protection of the present invention.

Claims

1. A heat-dissipating gear reducer, comprising a housing (1), the housing (1) being composed of a detachably coverable upper cover (11) and a bottom cover (12), wherein a transmission system is assembled inside the upper cover (11), the transmission system being composed of a primary transmission unit (2), a secondary transmission unit (3), and a tertiary transmission unit (4) meshing with each other, the secondary transmission unit (3) including a gear shaft (31), the surface of which is rigidly sleeved with a secondary gear set (32), characterized in that: One end of the gear shaft (31) is rotatably mounted on the side wall of the upper cover (11) through a shaft seal, and the other end is provided with an axially extending locking groove (33). On the opposite side of the gear shaft (31), there is a form switching assembly (5) that can move through the other side wall of the upper cover (11). The form switching assembly (5) includes a pin rod (51). The end of the pin rod (51) is equipped with a circumferentially arranged locking and unlocking mechanism (53). The locking and unlocking mechanism (53) can move axially along the rotating locking groove (33) to achieve locking or unlocking. A trapezoidal guide seat (52) is rigidly connected to the outside of the locking and unlocking mechanism (53) and is circumferentially arranged on the surface of the pin rod (51). An oil quantity adjustment mechanism (6) is provided on the periphery of the trapezoidal guide seat (52), and a flow guide assembly (7) is provided between it and the secondary gear set (32). The oil volume adjustment mechanism (6) includes a receiving tray (61), which is rotatably mounted on the side wall of the guide assembly (7); the receiving tray (61) is provided with a transmission slide corresponding to the trapezoidal guide seat (52), and a receiving spoon (62) is slidably sleeved in the transmission slide. The bottom end of each receiving spoon (62) is slidably engaged with the trapezoidal guide seat (52), and force transmission is achieved through complementary inclined contact surfaces; when the trapezoidal guide seat (52) moves axially with the pin rod (51), it can push the receiving spoon (62) to expand outward along the transmission slide of the receiving tray (61), so that the oil immersion depth of the receiving spoon (62) decreases and the oil holding capacity increases when the receiving spoon (62) rotates; an oil drain groove (72) is opened at the top of the pipe body (71).

2. The heat-dissipating gear reducer according to claim 1, characterized in that: The oil volume adjustment mechanism (6) also includes a journal (63) integrally formed on the side wall of the storage tray (61), which is rotatably mounted with the flow guide assembly (7); the flow guide assembly (7) includes a tube (71) whose bottom is fixed to the bottom wall of the upper cover (11) by a mounting bracket (9) rigidly connected to it, and the front side of the tube (71) is provided with a rotatable interface (74) for the journal (63) to be inserted and rotated.

3. The heat-dissipating gear reducer according to claim 1 or 2, characterized in that: The outer end of the mode switching assembly (5) is provided with a linear actuator (10) fixedly installed outside the upper cover (11). The telescopic shaft of the linear actuator (10) is rigidly connected to the pin rod (51) and is used to drive the pin rod (51) to move linearly along the inner cavity of the locking groove (33) coaxially arranged therein.

4. The heat-dissipating gear reducer according to claim 3, characterized in that: The locking and releasing mechanism (53) consists of a claw seat (531), a claw head (532) and a first spring (533). The claw seat (531) is rigidly connected to the end of the pin rod (51). The first spring (533) is installed inside the claw seat (531), and the top of the first spring (533) is connected to the claw head (532) which can elastically extend and retract along the claw seat (531).

5. The heat-dissipating gear reducer according to claim 4, characterized in that: A rounded chamfer is provided at the top of the claw (532) to form a mating relationship with the slot opened on the surface of the locking groove (33). The rounded chamfer can fit with the cut edge of the slot.

6. The heat-dissipating gear reducer according to claim 1, characterized in that: The receiving spoon (62) consists of an inner sliding block (621), a middle sliding block (622), and an outer oil spoon (623) that are rigidly connected from the inside to the outside along the transmission slide. When the trapezoidal guide seat (52) moves to fully fit with the inner sliding block (621), the outer edge of the outer oil spoon (623) forms a close fit with the edge of the storage tray (61).

7. The heat-dissipating gear reducer according to claim 6, characterized in that: The outer oil spoon (623) includes a spoon box (6231). The spoon box (6231) is provided with a guide tube (6232) on one side of the circumferential rotation. The guide tube (6232) extends into the middle of the inner cavity of the spoon box (6231) and the diameter gradually decreases. The bottom wall of the spoon box (6231) near the tube body (71) is provided with an oil drain hole (6234). The bottom wall of the spoon box (6231) is set as a downward tilted spoon bottom (6233).

8. The heat-dissipating gear reducer according to claim 7, characterized in that: A sealing ring (73) connected to the outer ring layer where the oil drain groove (72) is located is also provided. The length ratio of the oil drain groove (72) to the sealing ring (73) is 1:

3. The bottom wall of the oil drain groove (72) is provided with a drainage rib that slopes downward toward the tooth surface of the large gear section (321).

9. The heat-dissipating gear reducer according to claim 8, characterized in that: There is a gap between the inner wall of the middle slider rod (622) and the transmission slide; an elastic partition (64) is provided in the gap, the bottom end of which is fixedly connected to the inner wall of the transmission slide, and the top end is fixedly connected to the side of the bottom wall of the spoon box (6231) near the tube body (71).

10. The heat-dissipating gear reducer according to claim 9, characterized in that: The bottom of the tube (71) is equipped with a bearing cavity (75). The bottom wall of the bearing cavity (75) is fixedly installed with a guide rail (76) and a positioning post (77). The bearing cavity (75) is provided with a turbulence part (8) that can slide along the guide rail (76). The turbulence part (8) includes a contact brush plate (81) attached to the bottom wall of the secondary gear set (32). The side of the contact brush plate (81) away from the secondary gear set (32) is rigidly connected to a contact head (83) through a swing arm (82). A second spring (84) is connected between the contact head (83) and the positioning post (77). The contact head (83) extends into the outer ring layer through the bearing cavity (75).

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