A high-reliability spur-tooth planetary reducer

Abstract

The present invention discloses a high-reliability spur-tooth planetary reducer, comprising an input end seat, an output end seat and a shell arranged between the input end seat and the output end seat; a sun gear is rotatably provided in the input end seat; a ring gear is provided on the inner wall of the shell; a first spur-tooth planetary group and a second spur-tooth planetary group are rotatably provided in the shell; the first spur-tooth planetary group comprises an output shaft and a plurality of first spur gears rotatably arranged on the output shaft; the first spur gear is meshed with the sun gear and the ring gear; the second spur-tooth planetary group comprises a planet carrier, a turntable rotatably arranged on the planet carrier and a plurality of second spur gears movably arranged between the planet carrier and the turntable; the planet carrier is coaxially sleeved on the output shaft; a coupling unit is provided between the planet carrier and the turntable; the coupling unit comprises a thermally sensitive elastic part; it can disperse high load pressure to the contact surfaces of multiple gear groups, thereby improving the reliability and stability of the reducer under high load conditions, and helping to extend the service life of the reducer.

Description

Technical Field

[0001] The present invention relates to the technical field of reducers, and in particular to a high-reliability spur-tooth planetary reducer. Background Art

[0002] Traditional spur planetary reducer designs generally utilize a single spur planetary gearset to complete transmission tasks. This design performs adequately under light loads, but as the load increases, the pressure on the single spur planetary gearset, acting as the sole transmission unit, rises dramatically. Due to the limited contact area of ​​the gears, increasing loads also increase contact stress, leading to increased wear on the gear tooth surfaces.

[0003] This kind of wear not only increases the risk of gear failure such as fatigue pitting and bonding, but also seriously affects the service life and operational reliability of the reducer. Summary of the Invention

[0004] The purpose of the present invention is to overcome the above-mentioned shortcomings and provide a highly reliable spur planetary reducer that can disperse high load pressure to multiple sets of gear contact surfaces, thereby improving the reliability and stability of the reducer under high load conditions and extending the service life of the reducer.

[0005] To achieve the above object, the specific solutions of the present invention are as follows:

[0006] A high-reliability spur-tooth planetary reducer comprises an input end seat, an output end seat, and a housing disposed between the input end seat and the output end seat; a sun gear is rotatably disposed within the input end seat; a ring gear is disposed on the inner wall of the housing; a first spur-tooth planetary group and a second spur-tooth planetary group are rotatably disposed within the housing;

[0007] The first spur gear planetary set includes an output shaft and a plurality of first spur gears rotatably disposed on the output shaft; the first spur gears are meshed with both the sun gear and the ring gear;

[0008] The second spur gear planetary set includes a planet carrier, a turntable rotatably mounted on the planet carrier, and a plurality of second spur gears movably mounted between the planet carrier and the turntable; the planet carrier is coaxially sleeved on the output shaft; a coupling unit is provided between the planet carrier and the turntable; the coupling unit includes a thermally sensitive elastic member;

[0009] When the temperature of the thermosensitive elastic member reaches its deformation threshold, the thermosensitive elastic member drives the turntable to rotate, and the turntable causes the second spur gear to move radially to mesh with the ring gear.

[0010] Optionally, the coupling unit also includes a guide column vertically arranged on the planetary frame, a sliding member slidably arranged on the guide column, a driving pin arranged on the sliding member, and a spiral hole arranged on the turntable; a thermosensitive elastic member is arranged between the sliding member and the planetary frame; and the driving pin is movably embedded in the spiral hole.

[0011] Optionally, the sliding member is a first permanent magnet; a second permanent magnet having opposite magnetic properties to the first permanent magnet is embedded in the position of the turntable corresponding to the first permanent magnet;

[0012] When the thermosensitive elastic member deforms and stretches, the thermosensitive elastic member pushes the first permanent magnet toward the second permanent magnet, causing the first permanent magnet and the second permanent magnet to be magnetically attracted; when the elastic force generated by the thermosensitive elastic member recovering its deformation is greater than the magnetic attraction between the first permanent magnet and the second permanent magnet, the first permanent magnet and the second permanent magnet are released from magnetic attraction.

[0013] Optionally, the second permanent magnet is arc-shaped.

[0014] Optionally, there are multiple coupling units, the multiple coupling units are evenly distributed along the circumferential direction, and the coupling units are located between two adjacent second spur gears.

[0015] Optionally, the thermosensitive elastic member is a thermosensitive spring or a thermosensitive spring.

[0016] Optionally, the number of the second spur gears is three; and the number of the coupling units is three.

[0017] Optionally, an arc hole is provided on the turntable corresponding to each second spur gear; a strip hole extending radially is provided on the planet carrier corresponding to each second spur gear; and both ends of the second spur gear journal are movably embedded in the arc hole and the strip hole respectively.

[0018] Optionally, a coupling is connected to the journal of the sun gear; the coupling is rotatably connected to the input end seat through a first bearing.

[0019] Optionally, the output shaft is rotatably connected to the output end seat via a second bearing.

[0020] The beneficial effects of the present invention are as follows: by setting up a first spur planetary set and a second spur planetary set, the present invention can utilize the heat increase under high load to trigger the thermosensitive elastic member to drive the turntable to rotate, so that the second spur gear and the ring gear engage and transmit, and then automatically adjust the working state of the second spur planetary set. The entire process does not require the intervention of an external complex electronic control system, and adaptive switching is achieved entirely based on the physical thermal effect generated by the load. Compared with the traditional single-set gear transmission, the high load pressure can be dispersed to the contact surfaces of multiple sets of gears, thereby improving the reliability and stability of the reducer under high load conditions, which is conducive to extending the service life of the reducer. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Figure 1 is a perspective view of the present invention;

[0022] Figure 2 1 is a cross-sectional schematic diagram of the present invention when the second spur gear planetary set is in a non-transmission state;

[0023] Figure 3 is a cross-sectional schematic diagram of the present invention when the second spur gear planetary set is in a transmission state;

[0024] Figure 4 It is a schematic structural diagram of the first spur gear planetary set of the present invention;

[0025] Figure 5 This is a schematic structural diagram of the second spur gear planetary set of the present invention when it is in a transmission state;

[0026] Figure 6 This is a structural schematic diagram of the second spur gear planetary set of the present invention in a transmission state from another perspective;

[0027] Figure 7 is a cross-sectional schematic diagram of the second spur gear planetary set of the present invention in a transmission state;

[0028] Explanation of the accompanying drawings: 1. Input end seat; 11. Sun gear; 12. Coupling; 13. First bearing; 2. Output end seat; 21. Second bearing; 3. Housing; 31. Ring gear; 4. First spur gear set; 41. Output shaft; 42. First spur gear; 5. Second spur gear set; 51. Planet carrier; 511. Bar hole; 52. Turntable; 521. Arc hole; 53. Second spur gear; 541. Thermosensitive elastic member; 542. Guide column; 543. First permanent magnet; 544. Drive pin; 545. Spiral hole; 546. Second permanent magnet. DETAILED DESCRIPTION

[0029] The present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments, but the scope of implementation of the present invention is not limited thereto.

[0030] like Figures 1 to 7 As shown, a high-reliability spur-tooth planetary reducer described in this embodiment includes an input end seat 1, an output end seat 2, and a housing 3 fixedly installed between the input end seat 1 and the output end seat 2; a sun gear 11 is rotatably provided in the input end seat 1; a ring gear 31 is provided on the inner wall of the housing 3; a first spur-tooth planetary set 4 and a second spur-tooth planetary set 5 are rotatably provided in the housing 3;

[0031] The first spur gear planetary set 4 includes an output shaft 41 and a plurality of first spur gears 42 rotatably mounted on the output shaft 41; the first spur gears 42 mesh with both the sun gear 11 and the ring gear 31. The second spur gear planetary set 5 includes a planet carrier 51, a rotating disk 52 rotatably mounted on the planet carrier 51, and a plurality of second spur gears 53 movably mounted between the planet carrier 51 and the rotating disk 52. The planet carrier 51 is coaxially sleeved on the output shaft 41. A coupling unit is provided between the planet carrier 51 and the rotating disk 52; the coupling unit includes a thermally sensitive elastic member 541.

[0032] When the temperature of the thermosensitive elastic member 541 reaches its deformation threshold, the thermosensitive elastic member 541 drives the turntable 52 to rotate, and the turntable 52 causes the second spur gear 53 to move radially to engage with the ring gear 31. Preferably, the thermosensitive elastic member 541 is a thermosensitive spring or a thermosensitive spring, which can be configured according to actual design requirements.

[0033] In this embodiment, Figure 4 As shown, the number of the first spur gears 42 is set to three to ensure the stability of power transmission.

[0034] Specifically, when the spur gear planetary reducer of this embodiment is in low-load working condition, the sun gear 11 drives each first spur gear 42 to rotate. Since each first spur gear 42 is engaged with the ring gear 31, and the ring gear 31 is fixed, each first spur gear 42 drives the output shaft 41 to rotate, and each first spur gear 42 synchronously makes a circular motion around the sun gear 11, and the output shaft 41 drives each second spur gear 53 to rotate synchronously around the axis of the output shaft 41. At this time, the second spur gear planetary set 5 is in a non-transmission state, that is, each second spur gear 53 is not engaged with the ring gear 31, as shown in FIG. Figure 2 As shown, this can meet the transmission requirements under low load conditions, thereby achieving power output;

[0035] When the load increases to a certain level, the high load will cause severe friction and generate a large amount of heat. The heat accumulation will cause the temperature of the thermosensitive elastic member 541 to rise. When the temperature reaches the deformation threshold of the thermosensitive elastic member 541, the thermosensitive elastic member 541 drives the turntable 52 to rotate, and the turntable 52 drives each second spur gear 53 to move radially outward until it meshes with the ring gear 31. At this time, the output shaft 41 drives each second spur gear 53 to rotate. Since each second spur gear 53 meshes with the ring gear 31, the ring gear 31 drives each second spur gear 53 to rotate. That is, at this time, the second spur planetary set 5 is in a transmission state, as shown in FIG. Figure 3 As shown, adding the second spur gear 53 for transmission increases the contact area of ​​the gear transmission, thereby improving the output stability, reliability and accuracy of the reducer under high load conditions.

[0036] By providing a first spur-tooth planetary set 4 and a second spur-tooth planetary set 5, this embodiment can utilize the heat increase under high load to trigger the thermosensitive elastic member 541 to drive the turntable 52 to rotate, so that the second spur gear 53 engages with the ring gear 31 for transmission, thereby automatically adjusting the working state of the second spur-tooth planetary set 5. The entire process does not require the intervention of a complex external electronic control system, and adaptive switching is achieved entirely based on the physical thermal effect generated by the load. Compared with a traditional single-set gear transmission, high load pressure can be dispersed to the contact surfaces of multiple gear sets, thereby improving the reliability and stability of the reducer under high-load conditions and helping to extend the service life of the reducer.

[0037] like Figure 2 、 Figure 3 、 Figures 5 to 7 As shown, in some embodiments of the spur planetary reducer of this embodiment, the coupling unit further includes a guide post 542 vertically mounted on the planet carrier 51, a sliding member slidably mounted on the guide post 542, a drive pin 544 mounted on the sliding member, and a spiral hole 545 mounted on the turntable 52; a thermosensitive elastic member 541 is disposed between the sliding member and the planet carrier 51; and the drive pin 544 is movably embedded in the spiral hole 545. The guide post 542 is provided to guide and limit the sliding member, and the drive pin 544 is provided to cooperate with the spiral hole 545 to achieve linkage between the sliding member and the turntable 52, thereby achieving state switching of the second spur gear 53.

[0038] Specifically, when the reducer is under high load, the temperature of the thermosensitive elastic member 541 reaches its deformation threshold and stretches, pushing the sliding member to slide, and the sliding member drives the driving pin 544 to move. The driving pin 544 cooperates with the spiral hole 545 to convert the linear motion of the sliding member into the rotational motion of the turntable 52. During the rotation of the turntable 52, the second spur gears 53 are synchronously driven to move radially outward, so that the second spur gears 53 move outward to mesh with the ring gear 31, thereby increasing the contact area of ​​the gear transmission and improving the operational stability and reliability of the reducer.

[0039] As the load decreases, the temperature of the thermosensitive elastic member 541 gradually decreases. When the thermosensitive elastic member 541 drives the sliding member to slide in the opposite direction, the sliding member drives the driving pin 544 to move in the opposite direction. At this time, the driving pin 544 moves relatively in the opposite direction along the trajectory of the spiral hole 545, thereby driving the turntable 52 to rotate in the opposite direction, so that each second spur gear 53 is disengaged from the ring gear 31 to reduce gear wear.

[0040] like Figure 2 、 Figure 3 、 Figures 5 to 7 As shown, in the spur planetary reducer of this embodiment, in some embodiments, the sliding member is a first permanent magnet 543; a second permanent magnet 546 with opposite magnetic properties to the first permanent magnet 543 is embedded in the position of the turntable 52 corresponding to the first permanent magnet 543; preferably, the second permanent magnet 546 is arc-shaped.

[0041] Specifically, when the thermosensitive elastic member 541 is deformed and elongated, the thermosensitive elastic member 541 pushes the first permanent magnet 543 toward the second permanent magnet 546 until the first permanent magnet 543 and the second permanent magnet 546 are magnetically attracted to each other. At this time, due to the magnetic attraction between the first permanent magnet 543 and the second permanent magnet 546, the planet carrier 51 and the turntable 52 are fixed as a whole, so that the second spur gear 53 can remain in meshing state with the ring gear 31, thereby ensuring the reliability of the meshing transmission between the second spur gear 53 and the ring gear 31; When the elastic force generated by the restoring deformation is greater than the magnetic attraction between the first permanent magnet 543 and the second permanent magnet 546, the thermosensitive elastic member 541 drives the first permanent magnet 543 to overcome the magnetic attraction and move away from the second permanent magnet 546, thereby causing the first permanent magnet 543 and the second permanent magnet 546 to break away from the magnetic attraction. At the same time, the driving pin 544 cooperates with the spiral hole 545 to drive the turntable 52 to rotate in the opposite direction, causing the second spur gear 53 to move radially inward, thereby breaking away from the meshing transmission with the ring gear 31, so as to reduce the wear of the gear under low load conditions.

[0042] This embodiment can also be configured in another implementation manner. Instead of configuring the sliding member as the first permanent magnet 543 , this embodiment can also configure the sliding member as a non-magnetic member, and instead embed the first permanent magnet 543 on the top of the sliding member.

[0043] like Figure 5 and Figure 6 As shown, in some embodiments of the spur planetary reducer of this embodiment, a plurality of coupling units are provided, the plurality of coupling units being evenly distributed along the circumference and located between two adjacent second spur gears 53. By providing multiple coupling units, this embodiment can reliably drive the turntable 52 to rotate under high load conditions, thereby meshing the second spur gears 53 with the ring gear 31 for transmission.

[0044] like Figure 5 As shown, in some embodiments of the spur planetary reducer of this embodiment, the number of second spur gears 53 is set to three, and the number of coupling units is set to three. Through the above arrangement, this embodiment can ensure the stability of power transmission under high load conditions.

[0045] like Figures 5 to 7As shown, in the spur planetary reducer of this embodiment, in some embodiments, an arc hole 521 is respectively provided on the turntable 52 corresponding to each second spur gear 53; a radially extending bar hole 511 is respectively provided on the planetary carrier 51 for each second spur gear 53; and both ends of the shaft neck of the second spur gear 53 are movably embedded in the arc hole 521 and the bar hole 511 respectively. In this embodiment, the arc hole 521 and the bar hole 511 are provided, so that when the first permanent magnet 543 slides toward the second permanent magnet 546, the driving pin 544 cooperates with the spiral hole 545 to drive the turntable 52 to rotate. During the rotation of the turntable 52, the second spur gear 53 is driven to move radially outward through the arc hole 521 under the limiting action of the bar hole 511, so that the second spur gear 53 can be reliably engaged with the ring gear 31; when the turntable 52 rotates in the opposite direction, similarly, the turntable 52 drives the second spur gear 53 to move radially inward through the arc hole 521, so that the second spur gear 53 is disengaged from the ring gear 31, thereby realizing the state conversion of the second spur gear 53.

[0046] like Figure 2 and Figure 3 As shown, in some embodiments of the spur planetary reducer of this embodiment, a coupling 12 is connected to the journal of the sun gear 11; the coupling 12 is rotatably connected to the input end seat 1 via a first bearing 13. In this embodiment, the provision of coupling 12 ensures reliable power transmission to the sun gear 11, thereby driving its rotation. The provision of first bearing 13 ensures the stability of the rotation of the sun gear 11.

[0047] like Figure 2 and Figure 3 As shown, in some embodiments of the spur planetary reducer of this embodiment, the output shaft 41 is rotatably connected to the output end seat 2 via a second bearing 21. In this embodiment, the provision of the second bearing 21 ensures the stability and reliability of the rotation of the output shaft 41. Preferably, two second bearings 21 are provided to ensure the stability, reliability, and precision of the rotation of the output shaft 41.

[0048] The above description is only a preferred embodiment of the present invention. Therefore, any equivalent changes or modifications made according to the structure, characteristics and principles described in the scope of the patent application of the present invention are included in the protection scope of the patent application of the present invention.

Claims

1. A high reliability spur planetary reducer, characterized in that: It includes an input end seat, an output end seat, and a housing arranged between the input end seat and the output end seat; a sun gear is rotatably arranged in the input end seat; a gear ring is arranged on the inner wall of the housing; a first spur gear planetary set and a second spur gear planetary set are rotatably arranged in the housing; The first spur gear planetary set includes an output shaft and a plurality of first spur gears rotatably disposed on the output shaft; the first spur gears are meshed with both the sun gear and the ring gear; The second spur gear planetary set includes a planet carrier, a turntable rotatably mounted on the planet carrier, and a plurality of second spur gears movably mounted between the planet carrier and the turntable; the planet carrier is coaxially sleeved on the output shaft; a coupling unit is provided between the planet carrier and the turntable; the coupling unit includes a thermally sensitive elastic member; When the temperature of the thermosensitive elastic member reaches its deformation threshold, the thermosensitive elastic member drives the turntable to rotate, and the turntable causes the second spur gear to move radially to mesh with the ring gear.

2. A high reliability spur planetary reducer according to claim 1, characterized in that: The coupling unit also includes a guide column vertically arranged on the planetary frame, a sliding member slidably arranged on the guide column, a driving pin arranged on the sliding member, and a spiral hole arranged on the turntable; the thermal elastic member is arranged between the sliding member and the planetary frame; and the driving pin is movably embedded in the spiral hole.

3. A high reliability spur planetary reducer according to claim 2, characterized in that: The sliding member is a first permanent magnet; a second permanent magnet having opposite magnetic properties to the first permanent magnet is embedded in the position of the turntable corresponding to the first permanent magnet; When the thermosensitive elastic member deforms and stretches, the thermosensitive elastic member pushes the first permanent magnet toward the second permanent magnet, causing the first permanent magnet and the second permanent magnet to be magnetically attracted; when the elastic force generated by the thermosensitive elastic member recovering its deformation is greater than the magnetic attraction between the first permanent magnet and the second permanent magnet, the first permanent magnet and the second permanent magnet are released from magnetic attraction.

4. A high-reliability spur-tooth planetary reducer according to claim 3, characterized in that: The second permanent magnet is in an arc shape.

5. The high-reliability spur planetary reducer according to claim 3, characterized in that: There are multiple coupling units, which are evenly distributed along the circumferential direction, and the coupling units are located between two adjacent second spur gears.

6. A high-reliability spur-tooth planetary reducer according to any one of claims 1 to 5, characterized in that: The thermally sensitive elastic member is a thermally sensitive spring or a thermally sensitive spring.

7. The high-reliability spur planetary reducer according to claim 5, characterized in that: The number of the second spur gears is three; the number of the coupling units is three.

8. The high-reliability spur planetary reducer according to claim 2, characterized in that: Each second spur gear is provided with an arc hole on the turntable; each second spur gear is provided with a strip hole extending radially on the planet carrier; and both ends of the second spur gear journal are movably embedded in the arc hole and the strip hole respectively.

9. The high-reliability spur planetary reducer according to claim 1, characterized in that: The journal of the sun gear is connected with a coupling; the coupling is rotatably connected to the input end seat through a first bearing.

10. The high-reliability spur planetary reducer according to claim 1, characterized in that: The output shaft is rotatably connected to the output end seat through a second bearing.

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