Straight tooth planetary reducer with high reliability

Abstract

The invention discloses a high-reliability straight tooth planetary reducer which comprises an input end base, an output end base and a shell arranged between the input end base and the output end base. A sun gear is rotationally arranged in the input end seat; a gear ring is arranged on the inner wall of the shell; a first straight tooth planet set and a second straight tooth planet set are rotationally arranged in the shell. The first straight tooth planet set comprises an output shaft and a plurality of first straight gears rotationally arranged on the output shaft. The first straight gear is meshed with the sun gear and the gear ring; the second straight tooth planet set comprises a planet carrier, a rotating disc rotationally arranged on the planet carrier and a plurality of second straight gears movably arranged between the planet carrier and the rotating disc. The planet carrier is coaxially sleeved on the output shaft; a coupling unit is arranged between the planet carrier and the turntable; the coupling unit comprises a thermosensitive elastic piece; high-load pressure can be dispersed to the contact faces of the multiple sets of gears, the operation reliability and stability of the speed reducer under the high-load working condition are improved, and the service life of the speed reducer can be prolonged.

Description

Technical Field

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

[0002] In the traditional spur planetary reducer design, a single spur planetary gear set is generally used to complete the transmission task. This design performs well when facing a small load, but when the load increases, the pressure on the single spur planetary gear set as the only transmission unit increases sharply. Due to the limited contact area of ​​the gear, as the load increases, the contact stress also increases, resulting in increased wear on the gear tooth surface.

[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 high-reliability 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 scheme of the present invention is as follows:

[0006] A high-reliability spur-tooth planetary reducer comprises 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-tooth planetary group and a second spur-tooth planetary group are rotatably arranged in the housing;

[0007] The first spur gear planetary set comprises 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 group includes a planet carrier, a rotating disk rotatably arranged on the planet carrier, and a plurality of second spur gears movably arranged between the planet carrier and the rotating disk; the planet carrier is coaxially sleeved on the output shaft; a coupling unit is arranged between the planet carrier and the rotating disk; 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 rotating disk to rotate, and the rotating disk causes the second spur gear to move radially to mesh with the gear ring.

[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; the 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 a magnetic property opposite to that of the first permanent magnet is embedded in the position of the rotating disk corresponding to the first permanent magnet;

[0012] When the thermosensitive elastic member is deformed and elongated, the thermosensitive elastic member pushes the first permanent magnet to move toward the second permanent magnet, so that the first permanent magnet and the second permanent magnet are 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 separated from the magnetic attraction.

[0013] Optionally, the second permanent magnet is in an arc shape.

[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 the first spur planetary group and the second spur planetary group, 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 are meshed for transmission, and then the working state of the second spur planetary group is automatically adjusted. The whole 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 the traditional single-group gear transmission, the high load pressure can be dispersed to the contact surfaces of multiple groups of gears, thereby improving the reliability and stability of the reducer under high load conditions, and helping to extend the service life of the reducer. BRIEF DESCRIPTION OF THE DRAWINGS

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

[0022] Figure 2 is a cross-sectional schematic diagram of the present invention when the second spur gear planetary group 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 It 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 is a structural schematic diagram of another perspective when the second spur gear planetary set of the present invention is in a transmission state;

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

[0028] Explanation of the reference numerals: 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 in conjunction with the accompanying drawings and specific embodiments, but the implementation scope 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 arranged in the input end seat 1; a ring gear 31 is arranged on the inner wall of the housing 3; a first spur-tooth planetary group 4 and a second spur-tooth planetary group 5 are rotatably arranged 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 disposed on the output shaft 41; the first spur gears 42 are meshed 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 disposed on the planet carrier 51, and a plurality of second spur gears 53 movably disposed 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 disposed between the planet carrier 51 and the rotating disk 52; the coupling unit includes a thermosensitive 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 moves the second spur gear 53 radially to mesh 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 under low load condition, the sun gear 11 drives each first spur gear 42 to rotate. Since each first spur gear 42 is meshed 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 meshed 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, such as 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 the first spur planetary group 4 and the second spur planetary group 5, the present 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 and the ring gear 31 are meshed and transmitted, thereby automatically adjusting the working state of the second spur planetary group 5. The whole 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-group gear transmission, the high load pressure can be dispersed to the contact surfaces of multiple groups of gears, 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 column 542 vertically arranged on the planet carrier 51, a sliding member slidably arranged on the guide column 542, a driving pin 544 arranged on the sliding member, and a spiral hole 545 arranged on the turntable 52; the thermosensitive elastic member 541 is arranged between the sliding member and the planet carrier 51; and the driving pin 544 is movably embedded in the spiral hole 545. The guide column 542 is provided to provide guidance and limit for the sliding member, and the driving pin 544 is provided to cooperate with the spiral hole 545, so as to realize the linkage between the sliding member and the turntable 52, so as to realize the state switching of the second spur gear 53.

[0038] Specifically, when the reducer is under a high load state, 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, each second spur gear 53 is synchronously driven to move radially outward, so that each second spur gear 53 moves outward to mesh with the gear ring 31, thereby increasing the contact area of ​​the gear transmission and improving the operating 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 reverse direction, the sliding member drives the driving pin 544 to move in the reverse direction. At this time, the driving pin 544 moves relatively in the reverse direction along the trajectory of the spiral hole 545, thereby driving the turntable 52 to rotate in the reverse direction, so that each second spur gear 53 is disengaged from the gear ring 31 to reduce the wear of the gears.

[0040] like Figure 2 , Figure 3 , Figures 5 to 7 As shown, in the spur planetary reducer of this embodiment, in some implementations, 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 in an arc shape.

[0041] Specifically, when the thermosensitive elastic member 541 is deformed and elongated, the thermosensitive elastic member 541 pushes the first permanent magnet 543 to move 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 be kept 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 disengage 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 disengaging from the meshing transmission with the ring gear 31 to reduce the wear of the gear under low load conditions.

[0042] Another implementation method of this embodiment is to configure the sliding member as the first permanent magnet 543. In this embodiment, the sliding member is configured as a non-magnetic member, and the first permanent magnet 543 is embedded 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, the number of coupling units is set to be multiple, and the multiple coupling units are evenly distributed along the circumferential direction, and the coupling units are located between two adjacent second spur gears 53. In this embodiment, by providing multiple coupling units, the rotating disk 52 can be reliably driven to rotate under high load conditions, so that the second spur gears 53 and the ring gear 31 are meshed for transmission.

[0044] like Figure 5 As shown, in the spur planetary reducer of this embodiment, in some implementations, the number of the second spur gears 53 is set to three; the number of the 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 implementations, an arc hole 521 is respectively provided on the turntable 52 corresponding to each second spur gear 53; a strip hole 511 extending radially 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 strip 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 reliably engage 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 the spur planetary reducer of this embodiment, in some implementations, the journal of the sun gear 11 is connected with a coupling 12; the coupling 12 is rotatably connected to the input end seat 1 through a first bearing 13. In this embodiment, the coupling 12 is provided so that power can be reliably transmitted to the sun gear 11 to drive the sun gear 11 to rotate. The first bearing 13 is provided to ensure the stability of the rotation of the sun gear 11.

[0047] like Figure 2 and Figure 3 As shown, in the spur planetary reducer of this embodiment, in some embodiments, the output shaft 41 is rotatably connected to the output end seat 2 through the second bearing 21. In this embodiment, the second bearing 21 is provided to ensure the stability and reliability of the rotation of the output shaft 41. Preferably, the number of the second bearings 21 is set to two to ensure the stability, reliability and accuracy 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 shell 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 shell; a first spur gear planetary group and a second spur gear planetary group are rotatably arranged in the shell; The first spur gear planetary set comprises 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 group includes a planet carrier, a rotating disk rotatably arranged on the planet carrier, and a plurality of second spur gears movably arranged between the planet carrier and the rotating disk; the planet carrier is coaxially sleeved on the output shaft; a coupling unit is arranged between the planet carrier and the rotating disk; 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 rotating disk to rotate, and the rotating disk causes the second spur gear to move radially to mesh with the gear ring.

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 thermosensitive 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 a magnetic property opposite to that of the first permanent magnet is embedded in the position of the turntable corresponding to the first permanent magnet; When the thermosensitive elastic member is deformed and elongated, the thermosensitive elastic member pushes the first permanent magnet to move toward the second permanent magnet, so that the first permanent magnet and the second permanent magnet are 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 separated from the magnetic attraction.

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

5. A 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 planetary reducer according to any one of claims 1 to 5, characterized in that: The thermosensitive elastic member is a thermosensitive spring or a thermosensitive spring.

7. A 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. A high-reliability spur planetary reducer according to claim 2, characterized in that: The rotating disk is provided with an arc hole corresponding to each second spur gear; the planet carrier is provided with a strip hole extending in the radial direction for each second spur gear; and the two ends of the second spur gear journal are movably embedded in the arc hole and the strip hole respectively.

9. A 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 with the input end seat through a first bearing.

10. A 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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