Noise reduction self-lubricating type reduction motor

Abstract

This invention discloses a noise-reducing self-lubricating geared motor, belonging to the technical field of geared motors. The noise-reducing self-lubricating geared motor includes a mounting base mechanism, a drive mechanism, a sliding gear mechanism, a shift gear mechanism, a shift fork mechanism, a reduction gear mechanism, an oil pumping mechanism, an oil delivery mechanism, and an oil supply mechanism. The drive mechanism is mounted on the mounting base mechanism, and the sliding gear mechanism is slidably connected to the drive mechanism. This invention, through the arrangement of the oil pumping mechanism, oil delivery mechanism, and oil supply mechanism, pumps lubricating oil to the gear set of the gearbox using the motor's own power, thereby achieving self-lubrication and long-term stable oil supply, effectively reducing maintenance frequency and difficulty. The sliding gear mechanism, shift gear mechanism, and reduction gear mechanism effectively increase the oil storage capacity of the gears, improve the transmission effect of lubricating oil between gears, thereby improving the lubrication effect and reducing operating noise.

Description

Technical Field

[0001] This invention belongs to the field of geared motor technology, specifically relating to a noise-reducing self-lubricating geared motor. Background Technology

[0002] Geared motors are power devices that integrate a micro motor with a reduction gearbox. By reducing the output speed and increasing the output torque through the gear set, they meet the drive requirements of low speed and high torque. They are widely used in automation equipment, smart homes, medical devices, automotive parts and various small transmission mechanisms. They can precisely control speed and torque, improve the overall stability and service life of the machine, and are suitable for low-speed drive scenarios under various working conditions.

[0003] In practical applications, most existing geared motors do not have a self-supplying oil pump structure and rely on splash lubrication, which easily leads to uneven oil supply, insufficient local lubrication, rapid tooth surface wear, loud noise, and inability to provide continuous and stable oil supply. Frequent manual maintenance and oil replenishment are required, and the gearbox housing must be disassembled for oil replenishment, which is cumbersome and can easily cause dust and impurities to enter the housing, damaging the seal and aggravating component wear, resulting in poor long-term reliability.

[0004] Existing gear reducer lubricants mostly use splash lubrication to conduct between gears, which does not have the function of directional oil throwing to the tooth surface. This easily leads to uneven oil supply and insufficient lubrication of local tooth surfaces. Long-term operation can easily aggravate wear and generate greater transmission noise. At the same time, the gear oil storage capacity of the traditional gear motor lubrication structure is limited, and the lubricant is difficult to effectively guide between transmission components. Summary of the Invention

[0005] The technical problem to be solved by the present invention is to overcome the shortcomings of the prior art and provide a noise-reducing self-lubricating geared motor.

[0006] The technical solution adopted to solve the above-mentioned technical problems is: a noise-reducing self-lubricating geared motor, including a mounting base mechanism, a drive mechanism, a reduction gear mechanism, an oil pumping mechanism, an oil conveying mechanism, and an oil supply mechanism; the drive mechanism is connected to the reduction gear mechanism; the oil pumping mechanism is linked to the reduction gear mechanism to pump lubricating oil to the oil conveying mechanism; the oil conveying mechanism delivers lubricating oil to each gear meshing part; at least some gears are provided with oil storage grooves; the geared motor preferably also includes a sliding gear mechanism, a shift gear mechanism, and a shift fork mechanism for realizing gear shifting and speed change; the drive mechanism is mounted on the mounting base mechanism; the sliding gear mechanism is slidably connected to the drive mechanism; the sliding gear mechanism includes a first flat gear, and the first flat gear is provided with an inclined oil storage groove hole;

[0007] The reduction gear mechanism includes a large coupling gear, one end of which has an end face capillary groove;

[0008] A pumping mechanism is rotatably connected to the reduction gear mechanism. The pumping mechanism includes a connecting rod body, and a plunger is rotatably connected to the end of the connecting rod body. A sealing cavity is sleeved on the outside of the plunger. A first check valve is fixed on one side of the sealing cavity, and a second check valve is fixed on the other side of the sealing cavity.

[0009] Furthermore, the mounting base mechanism includes a base plate, on which a gearbox housing is fixed, a connecting rod compartment is fixed on the gearbox housing, a spring catch is installed on the gearbox housing, an anti-rotation slot is also provided on the gearbox housing, and a mounting positioning slot is fixed on the base plate.

[0010] Through the above technical solution, the mounting base mechanism provides stable mounting support for all components of the machine. The base plate serves as the basic load-bearing component, and the gearbox housing fixed on it is used to accommodate the sliding gear mechanism, shift gear mechanism, and reduction gear mechanism, playing a protective and positioning role. The connecting rod compartment fixed on the gearbox housing provides stable movement space for the connecting rod body of the oil pump mechanism, avoiding interference during operation. The spring clip is used to cooperate with the shift gear mechanism to lock the gear position and prevent gear displacement after shifting.

[0011] Furthermore, the drive mechanism includes a motor body fixed to the gearbox housing, a motor shaft coaxially fixed to the output shaft of the motor body, and an integral key formed on the motor shaft.

[0012] Through the above technical solution, the motor body is fixed to the gearbox housing, providing stable power input for the whole machine. The motor shaft is fixed coaxially with the motor body to achieve precise power transmission. Its one-piece molded shaft key, in conjunction with the sliding gear mechanism, not only ensures circumferential synchronous transmission and reliable torque transmission, but also allows the sliding gear mechanism to slide axially to achieve gear shifting. Moreover, the one-piece structure has high strength and small gap, which can reduce transmission noise and wear, and improve the operating stability of the drive mechanism.

[0013] Furthermore, a first sliding sleeve is coaxially fixed to the inner side of the first spur gear. The first sliding sleeve is slidably connected to the motor shaft. A first annular groove is provided on the first sliding sleeve. A keyway is provided on the inner side of the first sliding sleeve. The keyway and the integrated shaft key can prevent relative rotation between the sliding gear mechanism and the motor shaft. An inclined oil storage groove hole is provided on the tooth root surface of the first spur gear. The opening of the inclined oil storage groove hole is inclined in the same direction as the rotation direction of the gear and faces the working tooth surface.

[0014] Preferably, the depth of the inclined oil storage groove is 0.5mm to 2.0mm, the groove width is 0.8mm to 1.5mm, the angle between its center line and the radial direction of the gear is 30° to 60°, and the cross-sectional shape of the inclined oil storage groove can be semi-circular, rectangular or V-shaped. Experimental verification shows that the centrifugal oil ejection efficiency is the highest when the angle is 45°.

[0015] Through the above technical solution, the first sliding sleeve is slidably connected to the motor shaft, and its inner keyway cooperates with the integrated shaft key to effectively prevent the sliding gear mechanism from rotating relative to the motor shaft, ensuring stable torque transmission. At the same time, it allows the first sliding sleeve to drive the first flat gear to slide axially. The first annular groove on the first sliding sleeve is for the shift fork mechanism to be embedded to realize the shifting operation. The inclined oil storage groove hole on the root surface of the first flat gear has the opening direction consistent with the gear rotation direction and facing the working tooth surface. During operation, it can store lubricating oil and throw the lubricating oil to the tooth surface through centrifugal force to achieve self-lubrication, reduce tooth surface wear and transmission noise, and improve the stability of the mechanism operation.

[0016] Furthermore, the shift gear mechanism includes a fixed shaft fixed to the gearbox housing, a second sliding sleeve slidably and rotatably connected to the fixed shaft, a second annular groove being formed on the second sliding sleeve, a second spur gear and a third spur gear being coaxially fixed to the outside of the second sliding sleeve, the number of teeth and radius of the third spur gear being smaller than those of the second spur gear, and inclined oil reservoirs with the same structure as the first spur gear being formed on the second and third spur gears, the second spur gear meshing with the first spur gear.

[0017] Through the above technical solution, the fixed shaft is fixed on the gearbox housing to provide sliding and rotational support for the second sliding sleeve. The second annular groove on the second sliding sleeve is used to cooperate with the shift fork mechanism to achieve axial displacement. The second and third spur gears are coaxially fixed outside the second sliding sleeve. The two gears have different numbers of teeth and radii, which can cooperate with the sliding gear mechanism to form different transmission ratios, thereby realizing gear shifting and speed regulation of the geared motor. At the same time, both gears are provided with inclined oil reservoirs with the same structure as the first spur gear, which can synchronously guide oil to lubricate the tooth surface during operation, reduce meshing impact and noise, and improve the smoothness and service life of gear shifting transmission.

[0018] Furthermore, the shift fork mechanism includes a sliding lever that is slidably connected to the anti-rotation slot. The sliding lever has two position slots and a limit anti-rotation strip is integrally fixed on it. One end of the sliding lever is fixed with a pull ring, and the other end of the sliding lever is fixed with a first shift fork and a second shift fork. The first shift fork is rotatably connected to a first annular groove, and the second shift fork is rotatably connected to a second annular groove.

[0019] Through the above technical solution, the sliding lever slides in conjunction with the anti-rotation slot, and works with the limiting anti-rotation strip to achieve linear movement and circumferential anti-rotation, ensuring stable and non-deviation-prone shifting. The two gear slots on it cooperate with the spring clip to achieve gear positioning. The pull ring facilitates manual shifting. The first shift fork at the end of the sliding lever is connected to the first annular groove, and the second shift fork is connected to the second annular groove. Pushing and pulling the sliding lever can synchronously drive the sliding gear mechanism and the shifting gear mechanism to move axially, completing the switching of different gears. The structure is compact and the transmission is synchronous and reliable.

[0020] Furthermore, a small gear is fixed to one end of the large gear near the capillary groove on the end face. Inclined oil reservoirs, identical in structure to the first spur gear, are formed on both the large and small gears. The capillary groove on the end face connects the inclined oil reservoirs of the large and small gears. An output gear is meshed with the outer side of the small gear. A rotatable connection is fixed to one side of the output gear, and a power output shaft is coaxially fixed to the other side of the output gear. The power output shaft passes through the gearbox housing and is rotatably connected to it. A gear shaft is coaxially fixed to the large gear, and the gear shaft is rotatably connected to the gearbox housing. The large gear meshes with the third spur gear.

[0021] Through the above technical solution, the end-face capillary groove extends radially along the end face of the large gear of the coupling. Its inner end connects to the end of the inclined oil reservoir hole of the large gear, and its outer end extends to the root of the small gear of the coupling and connects to the starting end of the inclined oil reservoir hole of the small gear. The cross-sectional shape of the end-face capillary groove is preferably rectangular or semi-circular, with a groove width of 0.1mm-0.5mm and a groove depth of 0.2mm-1.0mm, to ensure that sufficient capillary force is generated at the normal operating speed of the gear (such as 500-3000rpm) to draw the lubricating oil in the oil reservoir of the large gear into the oil reservoir of the small gear. The large gear and the small gear of the coupling are coaxially linked, and both are provided with the same inclined oil reservoir as the first flat gear, and are connected by the end-face capillary groove. This not only increases the oil storage capacity of the gear, but also allows the lubricating oil to be transferred between the large and small gears of the coupling, achieving uniform distribution of lubricating oil and continuous lubrication of the meshing tooth surface, solving the problem of traditional The problem of insufficient lubrication caused by the difficulty in transmitting lubricating oil between the large and small gears in a coupling can be solved by allowing the lubricating oil to flow directionally between the double gears, continuously providing lubrication to the gear surfaces. The small gear meshes with the output gear, and after multi-stage reduction, the power is transmitted outward from the power output shaft. The rotating connection ensures smooth rotation, and the gear shaft rotates in conjunction with the gearbox housing, providing stable support for the reduction gear mechanism. The overall structure achieves speed reduction output while reducing friction and noise through a connected oil storage structure, thereby improving transmission efficiency and service life. When it is necessary to change the output of the device, the user can pull the pull ring outward, causing the spring clip to lock with another gear slot. At this time, the first and second shift forks drive the first, second, and third spur gears to move circumferentially. The large gear of the coupling no longer meshes with the third spur gear, and the small gear meshes with the second spur gear, thereby changing the transmission ratio to achieve speed change.

[0022] Furthermore, the sealing cavity is fixed to the connecting rod chamber, and the plunger is slidably connected to the sealing cavity.

[0023] Through the above technical solution, the oil pumping mechanism is linked with the reduction gear mechanism. The operation of the reduction gear mechanism drives the connecting rod body to swing, which in turn drives the plunger to slide in the sealing cavity. The sealing cavity and the connecting rod chamber are fixed, providing a stable installation base for the oil pumping components. The sealing fit between the plunger and the sealing cavity can prevent lubricating oil leakage. When the plunger reciprocates, the first check valve and the second check valve work together to realize the directional intake and discharge of lubricating oil, forming a forced circulation oil supply. This continuously delivers lubricating oil to the meshing parts and sliding joints of all gears in the machine, making up for the shortcomings of uneven splash lubrication in traditional methods, further enhancing the self-lubricating effect, reducing wear and noise, and ensuring the stable and efficient operation of all mechanisms.

[0024] Furthermore, the oil delivery mechanism includes an oil delivery pipe sealed to the second check valve. Multiple branch pipes are connected to the oil delivery pipe, and a throttling cap is fixed to the end of each branch pipe. The throttling cap has a throttling orifice, which is aligned with the first spur gear, the coupling pinion, and the output gear, respectively. The throttling orifice on the throttling cap is aligned with the root circle of the gear teeth, and its specific position corresponds to the opening of the inclined oil reservoir hole. This allows the lubricating oil flowing out of the throttling orifice to directly enter the inclined oil reservoir hole, preventing the lubricating oil from leaking out and spilling, and improving the oil supply efficiency.

[0025] Through the above technical solution, the oil delivery pipe is sealed and connected to the second check valve, stably delivering the lubricating oil output by the pump mechanism, and multiple branch pipes realize oil circuit diversion. The throttling cap at the end of each branch pipe controls the oil output through the throttling orifice, avoiding oil overflow or insufficient oil supply. The throttling orifice is respectively aligned with the first spur gear, the coupling pinion, and the output gear, which can accurately deliver the lubricating oil to the gear meshing parts, improving the problem of uneven lubrication caused by traditional splashing. Together with the inclined oil reservoir hole and the end face capillary groove, a complete lubrication circuit is formed, effectively reducing tooth surface wear and transmission noise, and improving the reliability and durability of the geared motor.

[0026] Furthermore, the oil supply mechanism includes a lubricating oil tank embedded and fixed inside the mounting positioning groove, a transparent scale window embedded and fixed on the lubricating oil tank, an oil supply pipe connected to the lubricating oil tank, the end of the oil supply pipe being sealed and connected to a first check valve, an air inlet valve installed on the top of the lubricating oil tank, and a lubricating oil filling port provided on the lubricating oil tank.

[0027] Through the above technical solution, the lubricating oil tank is embedded in the installation positioning groove, which is compact and stable. The transparent scale window allows for intuitive observation of the oil level, facilitating timely oil replenishment. The lubricating oil tank is sealed to the first check valve through the oil supply pipe, continuously supplying lubricating oil to the pumping mechanism. The top air inlet valve balances the air pressure in the tank, ensuring smooth oil supply. The lubricating oil filling port is used to replenish lubricating oil. The entire oil supply mechanism, together with the oil delivery mechanism, forms a closed-loop oil circuit, realizing forced circulation lubrication, further improving the lubrication effect and noise reduction performance of the geared motor.

[0028] The beneficial effects of this invention are as follows:

[0029] 1. This invention, through the arrangement of an oil pumping mechanism, an oil conveying mechanism, and an oil supply mechanism, uses the power of the motor itself to pump lubricating oil to the gear set of the reduction gearbox, thereby achieving self-lubrication and long-term stable oil supply, effectively reducing maintenance frequency and maintenance difficulty;

[0030] 2. By incorporating a sliding gear mechanism, a shifting gear mechanism, and a reduction gear mechanism, this invention effectively increases the oil storage capacity of the gears, improves the transmission effect of lubricating oil between gears, thereby enhancing the lubrication effect and reducing operating noise. Attached Figure Description

[0031] Figure 1 This is a three-dimensional structural diagram of the present invention;

[0032] Figure 2 This is a structural diagram of the mounting base mechanism of the present invention;

[0033] Figure 3 This is a schematic diagram of the drive mechanism, sliding gear mechanism, shift gear mechanism, shift fork mechanism and reduction gear mechanism of the present invention;

[0034] Figure 4 This is a schematic diagram of the drive mechanism structure of the present invention;

[0035] Figure 5 This is a schematic diagram of the sliding gear mechanism, shift gear mechanism and shift fork mechanism of the present invention;

[0036] Figure 6 This is a schematic diagram of the sliding gear mechanism of the present invention;

[0037] Figure 7 This is a schematic diagram of the shift gear mechanism of the present invention;

[0038] Figure 8 This is a schematic diagram of the shift fork mechanism of the present invention;

[0039] Figure 9 This is a schematic diagram of the reduction gear mechanism of the present invention;

[0040] Figure 10 This is a schematic diagram of the pumping mechanism and the oil delivery mechanism of the present invention;

[0041] Figure 11 This is a schematic diagram of the oil supply mechanism of the present invention.

[0042] Reference numerals: 1. Mounting base mechanism; 101. Base plate; 102. Gearbox housing; 103. Connecting rod compartment; 104. Spring pin; 105. Anti-rotation slot; 106. Mounting positioning slot; 2. Drive mechanism; 201. Motor body; 202. Motor shaft; 203. Integrated shaft key; 3. Sliding gear mechanism; 301. First spur gear; 302. Inclined oil reservoir hole; 303. First sliding sleeve; 304. First annular groove; 305. Keyway; 4. Shift gear mechanism; 401. Fixed shaft; 402. Second sliding sleeve; 403. Second annular groove; 404. Second spur gear; 405. Third spur gear; 5. Shift fork mechanism; 501. Sliding lever; 502. Gear slot; 503. 504. Limiting anti-rotation strip; 505. Pull ring; 506. First shift fork; 507. Second shift fork; 6. Reduction gear mechanism; 601. Coupling large gear; 602. End face capillary groove; 603. Coupling small gear; 604. Output gear; 605. Rotary connection part; 606. Gear shaft; 607. Power output shaft; 7. Oil pumping mechanism; 701. Connecting rod body; 702. Plunger; 703. Sealing cavity; 704. First check valve; 705. Second check valve; 8. Oil supply mechanism; 801. Oil supply pipe; 802. Branch pipe; 803. Throttle cover; 9. Oil supply mechanism; 901. Lubricating oil tank; 902. Transparent scale window; 903. Oil supply pipe; 904. Air intake valve; 905. Lubricating oil filling port. Detailed Implementation

[0043] To make the objectives, technical solutions, and advantages of this invention clearer, the invention will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative and not intended to limit the invention.

[0044] like Figures 1-11As shown, a noise-reducing self-lubricating geared motor includes a mounting base mechanism 1, a drive mechanism 2, a sliding gear mechanism 3, a shift gear mechanism 4, a shift fork mechanism 5, a reduction gear mechanism 6, an oil pump mechanism 7, an oil delivery mechanism 8, and an oil supply mechanism 9. The mounting base mechanism 1 includes a base plate 101, on which a gearbox housing 102 is fixed. A connecting rod compartment 103 is fixed on the gearbox housing 102. A spring catch 104 is installed on the gearbox housing 102. An anti-rotation slot 105 is also provided on the gearbox housing 102. The base plate 101 is fixed with... The mounting base mechanism 1 provides a stable mounting support for all components of the machine, with a mounting positioning groove 106. The base plate 101 serves as a basic load-bearing component, and the gearbox housing 102 fixed on it is used to accommodate the sliding gear mechanism 3, the shift gear mechanism 4, and the reduction gear mechanism 6, serving as a protection and positioning function. The connecting rod compartment 103 fixed on the gearbox housing 102 provides a stable movement space for the connecting rod body 701 of the oil pump mechanism 7, avoiding interference during operation. The spring clip 104 is used to cooperate with the shift gear mechanism 4 to lock the gear position and prevent gear position deviation after shifting.

[0045] like Figure 1 , Figure 2 and Figure 4 As shown, a drive mechanism 2 is mounted on the mounting base mechanism 1. The drive mechanism 2 includes a motor body 201 fixed to the gearbox housing 102. A motor shaft 202 is coaxially fixed to the output shaft of the motor body 201. An integral key 203 is integrally formed on the motor shaft 202. The motor body 201 is fixed to the gearbox housing 102 to provide stable power input for the whole machine. The motor shaft 202 and the motor body 201 are coaxially fixed to achieve precise power transmission. The integral key 203 cooperates with the sliding gear mechanism 3 to ensure circumferential synchronous transmission and reliable torque transmission, while allowing the sliding gear mechanism 3 to slide axially to achieve gear shifting. Moreover, the integral structure has high strength and small gap, which can reduce transmission noise and wear and improve the operating stability of the drive mechanism 2.

[0046] like Figure 3 , Figure 5 and Figure 6As shown, a sliding gear mechanism 3 is slidably connected to the drive mechanism 2. The sliding gear mechanism 3 includes a first spur gear 301, on which an inclined oil reservoir hole 302 is formed. A first sliding sleeve 303 is coaxially fixed to the inner side of the first spur gear 301. The first sliding sleeve 303 is slidably connected to the motor shaft 202. A first annular groove 304 is formed on the first sliding sleeve 303. A keyway 305 is formed on the inner side of the first sliding sleeve 303. The keyway 305 cooperates with the integral shaft key 203 to prevent relative rotation between the sliding gear mechanism 3 and the motor shaft 202. An inclined oil reservoir hole 302 is formed on the root surface of the first spur gear 301. The opening of the inclined oil reservoir hole 302 is inclined in the same direction as the rotation direction of the gear. The first sliding sleeve 303 is slidably connected to the motor shaft 202, and its inner keyway 305 cooperates with the integrated shaft key 203 to effectively prevent the sliding gear mechanism 3 from rotating relative to the motor shaft 202, ensuring stable torque transmission. At the same time, it allows the first sliding sleeve 303 to drive the first spur gear 301 to slide axially. The first annular groove 304 on the first sliding sleeve 303 is for the shift fork mechanism 5 to be embedded to realize gear shifting operation. The inclined oil storage groove hole 302 on the root surface of the first spur gear 301 has the opening direction consistent with the gear rotation direction and faces the working tooth surface. During operation, it can store lubricating oil and throw the lubricating oil to the tooth surface through centrifugal force to achieve self-lubrication, reduce tooth surface wear and transmission noise, and improve the stability of the mechanism operation.

[0047] like Figure 3 , Figure 5 and Figure 7 As shown, the gear shifting mechanism 4 includes a fixed shaft 401 fixed to the gearbox housing 102. A second sliding sleeve 402 is slidably and rotatably connected to the fixed shaft 401. A second annular groove 403 is formed on the second sliding sleeve 402. A second spur gear 404 and a third spur gear 405 are coaxially fixed to the outside of the second sliding sleeve 402. The number of teeth and radius of the third spur gear 405 are smaller than those of the second spur gear 404. An inclined oil reservoir with the same structure as the first spur gear 301 is formed on the second spur gear 404 and the third spur gear 405. The second spur gear 404 meshes with the first spur gear 301. The fixed shaft 401... Fixed to the gearbox housing 102, it provides sliding and rotational support for the second sliding sleeve 402. The second annular groove 403 on the second sliding sleeve 402 is used to cooperate with the shift fork mechanism 5 to achieve axial displacement. The second spur gear 404 and the third spur gear 405 are coaxially fixed outside the second sliding sleeve 402. The two have different numbers of teeth and radii, and can cooperate with the sliding gear mechanism 3 to form different transmission ratios, so as to realize the geared motor shifting speed regulation. At the same time, both gears are provided with inclined oil storage grooves with the same structure as the first spur gear 301, which can synchronously guide oil to lubricate the tooth surface during operation, reduce meshing impact and noise, and improve the smoothness and service life of shifting transmission.

[0048] like Figure 3 , Figure 5 and Figure 8 As shown, the shift fork mechanism 5 includes a sliding lever 501 slidably connected to the anti-rotation slot 105. Two position slots 502 are formed on the sliding lever 501. A limit anti-rotation strip 503 is integrally fixed on the sliding lever 501. A pull ring 504 is fixed to one end of the sliding lever 501, and a first shift fork 505 and a second shift fork 506 are fixed to the other end of the sliding lever 501. The first shift fork 505 is rotatably connected to the first annular groove 304, and the second shift fork 506 is rotatably connected to the second annular groove 403. The sliding lever 501 slides within the anti-rotation slot 105. The mechanism works in conjunction with the limit stop bar 503 to achieve linear movement and circumferential anti-rotation, ensuring stable and non-deviation-prone shifting. The two gear slots 502 on the lever 501 cooperate with the spring clip 104 to achieve gear positioning. The pull ring 504 facilitates manual gear shifting. The first shift fork 505 at the end of the sliding lever 501 is connected to the first annular groove 304, and the second shift fork 506 is connected to the second annular groove 403. Pushing and pulling the sliding lever 501 can synchronously drive the sliding gear mechanism 3 and the shift gear mechanism 4 to move axially, completing the switching of different gears. The structure is compact and the transmission is synchronous and reliable.

[0049] like Figure 3 and Figure 9As shown, the reduction gear mechanism 6 includes a large coupling gear 601. One end of the large coupling gear 601 has an end face capillary groove 602. A small coupling gear 603 is fixed to the end of the large coupling gear 601 near the end face capillary groove 602. Inclined oil reservoirs, identical in structure to the first spur gear 301, are formed on both the large coupling gear 601 and the small coupling gear 603. The end face capillary groove 602 connects the inclined oil reservoirs of the large coupling gear 601 and the small coupling gear 603. An output gear 604 is meshed with the outer side of the small coupling gear 603. A rotating connection part 605 is fixed to one side of the output gear 604. On the other side of gear 604, a power output shaft 607 is coaxially fixed. The power output shaft 607 passes through the gearbox housing 102 and is rotatably connected to the gearbox housing 102. A gear shaft 606 is coaxially fixed to the large coupling gear 601. The gear shaft 606 is rotatably connected to the gearbox housing 102. The large coupling gear 601 meshes with the third spur gear 405. The end face capillary groove 602 extends radially along the end face of the large coupling gear 601. Its inner end is connected to the end of the inclined oil storage groove hole 302 of the large gear, and its outer end extends to the root of the small coupling gear 603 and is connected to the starting end of the inclined oil storage groove hole 302 of the small gear. The cross-sectional shape of the end-face capillary groove 602 is preferably rectangular or semi-circular, with a groove width of 0.1mm-0.5mm and a groove depth of 0.2mm-1.0mm. This ensures that sufficient capillary force is generated at the normal operating speed of the gears, such as 500-3000rpm, to draw the lubricating oil in the large gear oil reservoir into the small gear oil reservoir. The large gear 601 and the small gear 603 of the coupling are coaxially linked, and both are provided with the same inclined oil reservoir as the first flat gear 301, and are connected by the end-face capillary groove 602. This not only increases the oil reservoir capacity of the gears, but also allows the lubricating oil to be transferred between the large and small gears of the coupling, achieving uniform distribution of lubricating oil and continuous lubrication of the meshing tooth surfaces. This solves the problem of difficult lubricating oil transfer and insufficient lubrication between the large and small gears of traditional couplings. It enables directional flow of lubricating oil between the double gears, continuously providing lubrication to the tooth surfaces. The small gear 603 of the coupling... Engaging with the output gear 604, the power is transmitted outward through the power output shaft 607 after multi-stage reduction. The rotating connection 605 ensures smooth rotation. The gear shaft 606 rotates with the gearbox housing 102, providing stable support for the reduction gear mechanism 6. While achieving speed reduction output, the overall structure reduces friction and noise by relying on the connected oil storage structure, thereby improving transmission efficiency and service life. When it is necessary to change the output of the device, the user can pull the pull ring 504 outward, so that the spring clip 104 locks with another gear slot 502. At this time, the first shift fork 505 and the second shift fork 506 drive the first spur gear 301, the second spur gear 404 and the third spur gear 405 to move circumferentially. The coupling large gear 601 no longer meshes with the third spur gear 405, and the coupling small gear 603 meshes with the second spur gear 404, thereby changing the transmission ratio to achieve speed change.

[0050] like Figure 3 and Figure 10 As shown, a pumping mechanism 7 is rotatably connected to the reduction gear mechanism 6. The pumping mechanism 7 includes a connecting rod body 701, with a plunger 702 rotatably connected to the end of the connecting rod body 701. A sealing cavity 703 is sleeved on the outside of the plunger 702. A first check valve 704 is fixed on one side of the sealing cavity 703, and a second check valve 705 is fixed on the other side of the sealing cavity 703. The sealing cavity 703 is fixed to the connecting rod chamber 103, and the plunger 702 is slidably connected to the sealing cavity 703. The pumping mechanism 7 is linked with the reduction gear mechanism 6, and the operation of the reduction gear mechanism 6 drives the connecting rod body 701 to swing, thereby driving... The plunger 702 slides within the sealing cavity 703, which is fixed to the connecting rod chamber 103, providing a stable mounting base for the oil pump components. The sealing fit between the plunger 702 and the sealing cavity 703 prevents lubricating oil leakage. When the plunger 702 reciprocates, the first check valve 704 and the second check valve 705 work together to achieve directional intake and discharge of lubricating oil, forming a forced circulation oil supply. This continuously delivers lubricating oil to the meshing parts and sliding joints of all gears in the machine, making up for the unevenness of traditional splash lubrication, further enhancing the self-lubricating effect, reducing wear and noise, and ensuring the stable and efficient operation of all mechanisms.

[0051] like Figure 1 and Figure 10 As shown, the oil delivery mechanism 8 includes an oil delivery pipe 801 sealed to the second check valve 705. Multiple branch pipes 802 are connected to the oil delivery pipe 801. A throttling cap 803 is fixed to the end of each branch pipe 802. A throttling orifice is provided on the throttling cap 803, and the throttling orifice is aligned with the first spur gear 301, the coupling pinion 603, and the output gear 604, respectively. The throttling orifice on the throttling cap 803 is aligned with the root circle of the gear teeth. The specific position corresponds to the opening of the inclined oil storage tank hole 302, so that the lubricating oil flowing out from the throttling orifice can directly enter the inclined oil storage tank hole 302, avoiding the loss and spillage of lubricating oil and improving the oil supply efficiency. The oil delivery pipe 801 is sealed to the second check valve 705 to stably deliver the lubricating oil output by the oil pumping mechanism 7. The multiple branch pipes 802 realize the oil circuit diversion. The throttling caps 803 at the ends of each branch pipe 802 control the oil output through throttling orifices to prevent oil overflow or insufficient oil supply. The throttling orifices are respectively aligned with the first spur gear 301, the coupling pinion 603 and the output gear 604, which can accurately deliver lubricating oil to the gear meshing parts, improving the problem of uneven lubrication caused by traditional splashing. Together with the inclined oil reservoir hole 302 and the end face capillary groove 602, a complete lubrication circuit is formed, which effectively reduces tooth surface wear and transmission noise, and improves the reliability and durability of the geared motor.

[0052] like Figure 1 and Figure 11As shown, the oil supply mechanism 9 includes a lubricating oil tank 901 embedded and fixed inside the mounting positioning groove 106. A transparent scale window 902 is embedded and fixed on the lubricating oil tank 901. An oil supply pipe 903 is connected to the lubricating oil tank 901, and the end of the oil supply pipe 903 is sealed to the first check valve 704. An air inlet valve 904 is installed on the top of the lubricating oil tank 901. A lubricating oil filling port 905 is provided on the lubricating oil tank 901. The lubricating oil tank 901 is embedded in the mounting positioning groove 106, and the structure is compact. The system is compact and securely installed. The transparent scale window 902 allows for direct observation of the oil level, facilitating timely oil replenishment. The lubricating oil tank 901 is sealed to the first check valve 704 via the oil supply pipe 903, continuously supplying lubricating oil to the oil pumping mechanism 7. The top air inlet valve 904 balances the air pressure inside the tank, ensuring smooth oil supply. The lubricating oil filling port 905 is used to replenish lubricating oil. The entire oil supply mechanism 9, together with the oil delivery mechanism 8, forms a closed-loop oil circuit, achieving forced circulation lubrication and further improving the lubrication effect and noise reduction performance of the geared motor.

[0053] In use, the operator first adds an appropriate amount of lubricating oil to the lubricating oil tank 901 through the lubricating oil filling port 905, and observes the oil level through the transparent scale window 902 to ensure that the oil supply mechanism 9 is storing oil normally. Then, the drive mechanism 2 is started, and the motor body 201 drives the motor shaft 202 and the integrated shaft key 203 to rotate synchronously, driving the sliding gear mechanism 3 to rotate and transmit power. According to the actual load conditions, the pull ring 504 of the shift fork mechanism 5 is pulled, and the spring pin 104 engages with the gear slot 502 for positioning, driving the first shift fork 505 and the second shift fork 506 to move synchronously, switching the first flat gear 301 with the second flat gear 404 and the third flat gear 406. The meshing position of gear 405 enables transmission ratio adjustment and high / low speed shifting; after multi-stage meshing reduction of the power by the reduction gear mechanism 6, the power is stably output by the power output shaft 607; during continuous operation of the equipment, the coupling large gear 601 drives the oil pump mechanism 7 to work, driving the plunger 702 to reciprocate pump oil, and with the help of the first check valve 704 and the second check valve 705, the oil is delivered in a directional manner. The lubricating oil is accurately delivered to each gear meshing point through the oil delivery pipe 801 and the branch pipe 802, and with the continuous circulation and self-lubrication of various oil storage tanks, the meshing wear and transmission noise are effectively reduced. The entire process is stable and does not require frequent manual maintenance and oil replenishment, making it suitable for long-term continuous operation.

[0054] The various technical features of this invention are synergistic and work together to form a complete self-lubricating system. Specifically: the oil pumping mechanism 7, driven by the reduction gear mechanism 6, pumps lubricating oil from the oil supply mechanism 9 to the oil delivery mechanism 8; the oil delivery mechanism 8 precisely delivers lubricating oil to the vicinity of the tooth surfaces of the first spur gear 301, the coupling pinion 603, and the output gear 604 through the throttling orifice of the throttling cap 803; the inclined oil storage grooves 302 opened on the first spur gear 301, the coupling large gear 601, and the coupling pinion 603 can store lubricating oil, and when the gears rotate, the centrifugal force is used to throw the lubricating oil onto the working tooth surfaces to achieve directional lubrication; the end face capillary groove 602 opened on the end face of the coupling large gear 601 connects the inclined oil storage grooves 302 of the coupling large gear 601 and the coupling pinion 603, so that the lubricating oil can be transferred between the double gears, solving the technical problem that the small gear in the traditional double gear is difficult to obtain sufficient lubrication. The five stages of oil pumping, oil delivery, oil storage, oil throwing, and oil guiding mentioned above are interdependent and interconnected, working together to achieve the self-lubricating function of the geared motor. Each stage is indispensable, resulting in a synergistic technical effect that surpasses the sum of the individual functions of each stage.

[0055] To fully verify the lubrication performance, noise reduction performance, double gear oil guiding capability, and long-term operational reliability of the noise-reducing self-lubricating geared motor of this invention under actual working conditions, the following quantitative verification of the core structural technology effect of this application is carried out by combining multiple sets of comparative experiments. All experimental conditions are uniform, the testing standards are consistent, and the experimental data are authentic and traceable. The specific experiments are as follows.

[0056] Experiment Example 1: Comparison Experiment of Lubrication Effect

[0057] 1. Experimental objective: To verify that the inclined oil reservoir hole 302 structure of this application has a better meshing lubrication capability than the traditional ordinary gear without an oil reservoir hole, and to verify the synergistic effect between the forced circulation pump oil supply mechanism 9 and the inclined oil reservoir hole 302.

[0058] 2. Experimental materials: Noise-reducing self-lubricating geared motor prototypes of the same batch and specifications; ordinary gears without oil reservoirs and 302 gears with inclined oil reservoir holes were prepared by processing standard gear blanks; standard lubricating oil, precision wear detection instruments, infrared thermometers and oil metering devices were provided.

[0059] 3. Experimental grouping: Three parallel control groups were set up. The control group used the traditional splash lubrication method with ordinary gears without oil reservoirs; Experimental group 1 used the traditional splash lubrication method with the gear with inclined oil reservoir hole 302 of this application; Experimental group 2 used the forced circulation oil supply system of pumping mechanism 7 and oil delivery mechanism 8 of this application with the gear with inclined oil reservoir hole 302 of this application.

[0060] 4. Experimental Method: The three prototypes were simultaneously placed under rated standard load conditions and operated continuously at the same speed for 100 hours without additional oil replenishment or interruption for maintenance. After the experiment, the wear of the gear meshing positions of each group of gears was detected by precision testing equipment. Steady-state working gear surface temperature rise data were collected simultaneously, and the total lubricant consumption throughout the process was statistically analyzed. The data were then archived and compared.

[0061] 5. Experimental Results: After 100 hours of continuous operation under the same rated load and speed, the measured lubrication data for each group are as follows: The control group used traditional splash lubrication with ordinary gears without oil reservoirs. After 100 hours of operation, the tooth surface wear was 12.5 μm and the tooth surface temperature rise was 28.6℃. Experimental group 1 used traditional splash lubrication with the gear with the inclined oil reservoir 302 structure of this application. After 100 hours of operation, the tooth surface wear was 8.2 μm and the tooth surface temperature rise was 22.3℃. Experimental group 2 used the forced circulation oil supply structure of this application with the inclined oil reservoir 302 synergistic structure. After 100 hours of operation, the tooth surface wear was only 3.1 μm and the tooth surface temperature rise was only 15.8℃. The differences between the three groups are obvious, and the gradient law of lubrication improvement is clear.

[0062] 5. Experimental Results: After 100 hours of continuous operation under the same rated load and speed, the measured lubrication data for each group are as follows: The control group used traditional splash lubrication with ordinary gears without oil reservoirs. After 100 hours of operation, the tooth surface wear was 12.5 μm and the tooth surface temperature rise was 28.6℃. Experimental group 1 used traditional splash lubrication with the gear with the inclined oil reservoir 302 structure of this application. After 100 hours of operation, the tooth surface wear was 8.2 μm and the tooth surface temperature rise was 22.3℃. Experimental group 2 used the forced circulation oil supply structure of this application with the inclined oil reservoir 302 synergistic structure. After 100 hours of operation, the tooth surface wear was only 3.1 μm and the tooth surface temperature rise was only 15.8℃. The differences between the three groups are obvious, and the gradient law of lubrication improvement is clear.

[0063] The experimental data show that, compared with the control group, the wear and temperature rise of the tooth surface in experimental group 1 were significantly reduced, proving that the inclined oil reservoir 302 can effectively store and centrifugally deliver lubricating oil, improving basic lubrication conditions. Experimental group 2 had the best performance in all aspects, with tooth surface wear reduced by 75.2% and tooth surface temperature rise reduced by 44.8% compared with the control group. This proves that the forced circulation oil supply system of this application and the inclined oil reservoir 302 form a good synergy, which can continuously and accurately replenish the lubricating oil in the meshing area, greatly improve the tooth surface friction conditions, and significantly enhance the overall lubrication and protection effect.

[0064] Experiment Example 2: Noise Reduction Comparison Experiment

[0065] 1. Experimental objective: To quantitatively verify the actual noise reduction effect of the overall self-lubricating noise reduction structure of the present invention at different operating speeds, and to demonstrate the effect of structural optimization and circulating lubrication on suppressing meshing impact noise.

[0066] 2. Experimental materials: conventional ordinary geared motor of the same specification, prototype of the noise-reducing self-lubricating geared motor of this application, high-precision noise detector, constant load tooling platform.

[0067] 3. Experimental groups: The control group was a traditional geared motor, which used conventional splash lubrication with a common smooth gear structure; the experimental group was the integrated self-lubricating noise reduction geared motor of this application, equipped with an inclined oil reservoir gear, a 602 end face capillary groove guide structure and a fully automatic pump oil circulation supply structure.

[0068] 4. Experimental Method: Fix the two sets of motors on the same noise testing laboratory fixture table, keep the ambient temperature, background noise and installation alignment accuracy completely consistent, apply the same rated load at the rated common speeds of 1000rpm, 2000rpm and 3000rpm respectively, use the A-weighted sound pressure level standard, and collect noise values ​​at multiple fixed points 1m away from the outside of the motor housing, and take the average value as the final experimental data.

[0069] 5. Experimental Results: Under full gradient test speeds, the operating noise of the experimental group was consistently 3-8 dB(A) lower than that of the control group. Low-speed meshing was smooth with no impact noise, and high-speed operation was free of whistling noise. The experiment demonstrates that this application, by optimizing tooth surface lubrication conditions, reducing meshing clearance frictional impact, and stabilizing gear dynamic balance operation, can effectively suppress gear meshing vibration and frictional noise, resulting in significant overall noise reduction and a substantial improvement in acoustic comfort.

[0070] Experiment Example 3: Verification Experiment on the Flow Guiding Effect of 602 Capillary Groove on the End Face

[0071] 1. Experimental objective: To verify that the capillary groove 602 on the end face of the large gear 601 can stably and continuously guide the lubricating oil in the oil reservoir of the large gear 601 to the tooth surface of the small gear 603 by utilizing the synergistic effect of capillary adsorption force and gear rotation centrifugal force, thereby solving the technical problems of uneven oil supply and easy dry friction and heat generation of the small gear in the double coaxial gear pair.

[0072] 2. Experimental materials: Paired coupling large gear 601 and coupling small gear 603 components, two types of gear samples: 602 gear with end face capillary groove and conventional gear, special lubricating oil for dyeing and tracing, high-magnification industrial observation mirror, and uniform speed gear meshing experimental table.

[0073] 3. Experimental groups: The control group uses a coupling large gear 601 and coupling small gear 603 assembly structure, with no capillary guide grooves on the end face; the experimental group uses a coupling large gear 601 and coupling small gear 603 of the same specifications, with only a connected end face capillary groove 602 machined on the mating end face.

[0074] 4. Experimental method: The same batch of dyed lubricating oil was added quantitatively into the inclined oil reservoir of the large gear 601 of each group of couplings. The two groups of double gears were installed on the same experimental table and run continuously without load for 30 minutes with the same meshing clearance and the same speed. After stopping the machine, the dyed coverage of the entire tooth surface of the small gear 603 of the two groups of couplings was observed, and the lubricating oil guiding distribution effect was compared.

[0075] 5. Experimental Results: In the experimental group, the entire tooth surface, tooth root, and meshing working area of ​​the coupling pinion 603 exhibited a uniformly stained oil film. The lubricating oil was rapidly and continuously guided across the gears via the end-face capillary groove 602, resulting in good oil supply uniformity. In contrast, the control group's coupling pinion 603 showed virtually no obvious staining marks on its tooth surface, with only trace amounts of oil at local edges, failing to form an effective continuous lubricating oil film. This demonstrates that the end-face capillary groove 602 possesses excellent directional flow guidance and cross-gear oil delivery capabilities, effectively improving the overall lubrication uniformity of the double gear pair.

[0076] Experiment Example 4: Long-term continuous operation stability verification experiment

[0077] 1. Experimental objective: To verify that the overall forced circulation self-lubricating system of the present invention can maintain stable oil supply pressure, oil film thickness and oil tank level for a long time under rated working conditions and continuous operation, without the need for manual oil replenishment and maintenance, thus demonstrating the long-term maintenance-free operation advantage of the equipment.

[0078] 2. Experimental materials: The noise-reducing self-lubricating geared motor, high-precision oil pressure sensor, online oil film thickness detector, high-precision liquid level gauge, and rated load simulation tooling equipment of this application.

[0079] 3. Experimental method: The geared motor of this application was fixed in the standard test position, fully loaded and connected to the rated working condition, and kept running continuously at the rated speed for 500 hours. The test was conducted with the chamber closed, without opening the cover, adding oil, or stopping the machine. Every 50 hours, the real-time oil level of the lubricating oil tank 901, the oil supply pressure at the outlet of the oil pipe end, and the average thickness of the working oil film of the main meshing gear pair were collected at fixed points, and the data change trend was recorded throughout the process.

[0080] 4. Experimental Results: During 500 hours of continuous operation, the oil level in the lubricating oil tank 901 decreased evenly and slowly, without any sudden oil leakage or cross-contamination. The oil pressure fluctuation range at the oil pipe outlet was minimal, remaining stable within the designed operating range. The oil film thickness on the working surfaces of each meshing gear was uniform and controllable, with no abnormalities such as oil shortage, dry film, or localized oil deficiency. No manual lubrication or maintenance intervention was required throughout the entire process. The machine operated smoothly, with normal temperature rise and no abnormal noise, fully verifying the reliable and stable long-term circulation of the self-lubricating oil circuit system of this invention, making it suitable for long-term continuous heavy-load industrial operations.

[0081] The above four sets of comparative experiments show that the present invention, through the inclined oil storage groove hole 302, the end face capillary groove 602 and the pump oil forced circulation supply structure, can simultaneously achieve efficient and uniform self-lubrication, significantly reduce transmission noise, balance double gear oil supply, and long-term maintenance-free stable operation. The overall structure has outstanding synergistic effect, and its practicality and reliability are significantly better than traditional similar geared motor products.

[0082] The above description is merely a preferred embodiment of the present invention and is not intended to limit the scope of protection of the present invention.

Claims

1. A noise-reducing self-lubricating geared motor, comprising a mounting base mechanism (1), a drive mechanism (2), a sliding gear mechanism (3), a shift gear mechanism (4), a shift fork mechanism (5), a reduction gear mechanism (6), an oil pump mechanism (7), an oil delivery mechanism (8), and an oil supply mechanism (9), characterized in that: The mounting base mechanism (1) is equipped with a drive mechanism (2), and a sliding gear mechanism (3) is slidably connected to the drive mechanism (2). The sliding gear mechanism (3) includes a first flat gear (301), and an inclined oil storage groove hole (302) is opened on the first flat gear (301). The reduction gear mechanism (6) includes a large coupling gear (601), and one end of the large coupling gear (601) is provided with an end face capillary groove (602). A pumping mechanism (7) is rotatably connected to the reduction gear mechanism (6). The pumping mechanism (7) includes a connecting rod body (701). A plunger (702) is rotatably connected to the end of the connecting rod body (701). A sealing cavity (703) is sleeved on the outside of the plunger (702). A first check valve (704) is fixed on one side of the sealing cavity (703), and a second check valve (705) is fixed on the other side of the sealing cavity (703).

2. The noise-reducing self-lubricating geared motor according to claim 1, characterized in that, The mounting base mechanism (1) includes a base plate (101), a gearbox housing (102) is fixed on the base plate (101), a connecting rod compartment (103) is fixed on the gearbox housing (102), a spring clip (104) is installed on the gearbox housing (102), an anti-rotation slot (105) is also provided on the gearbox housing (102), and a mounting positioning slot (106) is fixed on the base plate (101).

3. The noise-reducing self-lubricating geared motor according to claim 2, characterized in that, The drive mechanism (2) includes a motor body (201) fixed on the gearbox housing (102), a motor shaft (202) is coaxially fixed on the output shaft of the motor body (201), and an integral shaft key (203) is integrally formed on the motor shaft (202).

4. The noise-reducing self-lubricating geared motor according to claim 1, characterized in that, The first spur gear (301) is coaxially fixed with a first sliding sleeve (303) on its inner side. The first sliding sleeve (303) is slidably connected to the motor shaft (202). The first sliding sleeve (303) has a first annular groove (304) and a keyway (305) on its inner side. The keyway (305) and the integral shaft key (203) cooperate to prevent the sliding gear mechanism (3) from rotating relative to the motor shaft (202). The root surface of the first spur gear (301) has an inclined oil storage groove hole (302). The opening of the inclined oil storage groove hole (302) is inclined in the same direction as the rotation direction of the gear and faces the working tooth surface. Preferably, the depth of the inclined oil storage groove hole (302) is 0.5mm to 2.0mm, the groove width is 0.8mm to 1.5mm, and the angle between its center line and the radial direction of the gear is 30° to 60°. The cross-sectional shape of the inclined oil storage groove hole (302) can be semi-circular, rectangular or V-shaped.

5. A noise-reducing self-lubricating geared motor according to claim 2, characterized in that, The shift gear mechanism (4) includes a fixed shaft (401) fixed to the gearbox housing (102). A second sliding sleeve (402) is slidably and rotatably connected to the fixed shaft (401). A second annular groove (403) is provided on the second sliding sleeve (402). A second spur gear (404) and a third spur gear (405) are coaxially fixed to the outside of the second sliding sleeve (402). The number of teeth and radius of the third spur gear (405) are smaller than those of the second spur gear (404). An inclined oil reservoir with the same structure as the first spur gear (301) is provided on the second spur gear (404) and the third spur gear (405). The second spur gear (404) meshes with the first spur gear (301).

6. The noise-reducing self-lubricating geared motor according to claim 1, characterized in that, The shift fork mechanism (5) includes a sliding lever (501) slidably connected to the anti-rotation slot (105). Two gear slots (502) are provided on the sliding lever (501). A limit anti-rotation strip (503) is integrally fixed on the sliding lever (501). A pull ring (504) is fixed at one end of the sliding lever (501). A first shift fork (505) and a second shift fork (506) are fixed at the other end of the sliding lever (501). The first shift fork (505) is rotatably connected to the first annular groove (304), and the second shift fork (506) is rotatably connected to the second annular groove (403).

7. A noise-reducing self-lubricating geared motor according to claim 1, characterized in that, A small gear (603) is fixed to one end of the large coupling gear (601) near the end face capillary groove (602). The large coupling gear (601) and the small coupling gear (603) have inclined oil reservoirs with the same structure as the first spur gear (301). The end face capillary groove (602) connects the inclined oil reservoirs of the large coupling gear (601) and the small coupling gear (603). An output gear (604) is meshed with the outer side of the small coupling gear (603). A rotating connection part (605) is fixed to one side of the output gear (604), and a power output shaft (607) is coaxially fixed to the other side of the output gear (604). The power output shaft (607) passes through the gearbox housing (102) and is rotatably connected to the gearbox housing (102). The large coupling gear (601)... A gear shaft (606) is coaxially fixed and rotatably connected to the gearbox housing (102). The large gear (601) of the coupling is meshed with the third flat gear (405). The end face capillary groove (602) extends radially along the end face of the large gear (601). Its inner end is connected to the end of the inclined oil storage groove hole (302) of the large gear, and its outer end extends to the root of the small gear (603) and is connected to the starting end of the inclined oil storage groove hole (302) of the small gear. The cross-sectional shape of the end face capillary groove (602) is preferably rectangular or semi-circular, with a groove width of 0.1mm-0.5mm and a groove depth of 0.2mm-1.0mm, to ensure that sufficient capillary force is generated at the normal operating speed of the gear, such as 500-3000rpm, to draw the lubricating oil in the oil storage groove of the large gear into the oil storage groove of the small gear.

8. A noise-reducing self-lubricating geared motor according to claim 1, characterized in that, The sealing cavity (703) is fixed to the connecting rod chamber (103), and the plunger (702) is in a sealed sliding connection with the sealing cavity (703).

9. A noise-reducing self-lubricating geared motor according to claim 1, characterized in that, The oil delivery mechanism (8) includes an oil delivery pipe (801) that is sealed to the second check valve (705). Multiple branch pipes (802) are connected to the oil delivery pipe (801). A throttling cap (803) is fixed at the end of each branch pipe (802). A throttling hole is provided on the throttling cap (803), and the throttling hole is aligned with the first spur gear (301), the coupling pinion (603), and the output gear (604), respectively. The throttling hole on the throttling cap (803) is aligned with the root circle of the gear. The specific position corresponds to the opening of the inclined oil storage tank hole (302), so that the lubricating oil flowing out from the throttling hole can directly enter the inclined oil storage tank hole (302), avoiding the loss and spillage of lubricating oil and improving the oil supply efficiency.

10. A noise-reducing self-lubricating geared motor according to claim 2, characterized in that, The oil supply mechanism (9) includes a lubricating oil tank (901) embedded and fixed inside the mounting positioning groove (106). A transparent scale window (902) is embedded and fixed on the lubricating oil tank (901). An oil supply pipe (903) is connected to the lubricating oil tank (901). The end of the oil supply pipe (903) is sealed and connected to the first check valve (704). An air inlet valve (904) is installed on the top of the lubricating oil tank (901). A lubricating oil filling port (905) is provided on the lubricating oil tank (901).

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