A differential large-torque gear reducer

Abstract

The present invention discloses a differential type large torque gear reducer, which includes a first small cylindrical gear arranged on an input shaft; a first and a second large cylindrical gears arranged on an output shaft, the first large cylindrical gear meshing with the first small cylindrical gear; a second small cylindrical gear respectively meshing with the first small cylindrical gear and the second large cylindrical gear; a first and a second large bevel gears fixedly connected to the first and the second large cylindrical gears respectively, and a small bevel gear respectively meshing with the first large bevel gear; the transmission ratio of the transmission system composed of the first small cylindrical gear, the first large cylindrical gear, the first large bevel gear and the small bevel gear is different from the transmission ratio of the transmission system composed of the second small cylindrical gear, the second large cylindrical gear, the second large bevel gear and the small bevel gear. The reducer disclosed by the present invention has the advantages of simple structure, small volume and large output torque, etc.

Description

Technical Field

[0001] The present invention relates to the technical field of speed reducers, and in particular to a differential large-torque gear speed reducer. Background Art

[0002] As one of the important functional components of precision machine tools, the accuracy and performance parameters of milling heads directly affect the product grade of machine tools. At present, the milling heads on the market are mainly direct-drive type with torque motors. The main reason is that its structure is simple and the cost is low. However, the most important disadvantage of the direct-drive milling head is that its torque is small and heavy-duty cutting cannot be achieved. Therefore, the mechanical milling head with large torque as the main feature has great advantages in heavy-duty machining. The traditional mechanical milling head reducer needs multi-stage speed reduction to achieve large-torque transmission, so it causes the problem of large structural size. Summary of the Invention

[0003] The present invention proposes a differential large-torque gear speed reducer for the above problems.

[0004] The technical means adopted by the present invention are as follows:

[0005] A differential large-torque gear speed reducer includes a first small cylindrical gear arranged on an input shaft;

[0006] A first large cylindrical gear and a second large cylindrical gear oppositely arranged on an output shaft. The first large cylindrical gear and the second large cylindrical gear can rotate on the output shaft, and the first large cylindrical gear meshes with the first small cylindrical gear;

[0007] A second small cylindrical gear meshing with the first small cylindrical gear and the second large cylindrical gear respectively;

[0008] A first large bevel gear and a second large bevel gear oppositely arranged on the output shaft. The first large bevel gear is fixedly connected to one end face of the first large cylindrical gear facing the second large cylindrical gear, and the second large bevel gear is fixedly connected to one end face of the second large cylindrical gear facing the first large cylindrical gear;

[0009] A small bevel gear fixedly connected to the output shaft through a bevel gear frame. The small bevel gear meshes with the first large bevel gear and the second large bevel gear respectively;

[0010] The transmission ratio of the transmission system composed of the first small cylindrical gear, the first large cylindrical gear, the first large bevel gear and the small bevel gear is different from the transmission ratio of the transmission system composed of the second small cylindrical gear, the second large cylindrical gear, the second large bevel gear and the small bevel gear.

[0011] Furthermore, at least one pair of gears among the first small cylindrical gear and the second small cylindrical gear, and the first large cylindrical gear and the second large cylindrical gear have different numbers of teeth.

[0012] Furthermore, the first small cylindrical gear and the second small cylindrical gear have the same number of teeth, and the first large cylindrical gear and the second large cylindrical gear have different numbers of teeth.

[0013] Furthermore, it further includes a third small cylindrical gear arranged on the same gear shaft as the second small cylindrical gear. The third small cylindrical gear meshes with the first small cylindrical gear, and a backlash elimination structure is provided between the second small cylindrical gear and the third small cylindrical gear.

[0014] Furthermore, the first small cylindrical gear, the second small cylindrical gear, the third small cylindrical gear, the first large cylindrical gear, and the second large cylindrical gear are all helical cylindrical gears.

[0015] Furthermore, the backlash elimination structure is a disc spring provided between the second small cylindrical gear and the third small cylindrical gear.

[0016] Furthermore, a lever fixing block is provided on the outer diameter of the output shaft, and a lever is provided on the lever fixing block;

[0017] At least one end of the lever is provided with the bevel gear holder.

[0018] Furthermore, the bevel gear holder is perpendicularly arranged with respect to the lever, such that the central axis of the small bevel gear passes through the center of the output shaft.

[0019] Furthermore, a first large bevel gear mounting groove is provided on the side of the first large cylindrical gear facing the second large cylindrical gear, and the first large bevel gear is placed in the first large bevel gear mounting groove;

[0020] A second large bevel gear mounting groove is provided on the side of the second large cylindrical gear facing the first large cylindrical gear, and the second large bevel gear is placed in the second large bevel gear mounting groove.

[0021] Furthermore, it further includes a radial backlash elimination structure for eliminating radial backlash between the first small cylindrical gear and the first large cylindrical gear and between the first small cylindrical gear and the first large cylindrical gear.

[0022] Compared with the prior art, the differential large-torque gear reducer disclosed in the present invention has the following beneficial effects: Due to the provision of two transmission systems with different transmission ratios, the small bevel gear can be driven to rotate and revolve, thereby realizing the output of the reducer. The reducer disclosed in the present invention has the advantages of simple structure, small volume, and large output torque. Brief Description of the Drawings

[0023] Figure 1 It is the overall structure diagram of the differential large-torque gear reducer disclosed by the present invention;

[0024] Figure 2 It is the front view of the differential large-torque gear reducer disclosed by the present invention;

[0025] Figure 3 It is the first axonometric view of the differential large-torque gear reducer disclosed by the present invention;

[0026] Figure 4 It is the second axonometric view of the differential large-torque gear reducer disclosed by the present invention;

[0027] Figure 5 It is the sectional view of the differential large-torque gear reducer disclosed by the present invention, and it is the sectional view along the axis of the output shaft in the figure;

[0028] Figure 6 It is the view along the axis direction of the output shaft, and the first large cylindrical gear and the first large bevel gear are not shown in the figure;

[0029] Figure 7 It is the structure diagram of the differential large-torque gear reducer disclosed by the present invention with radial backlash elimination.

[0030] In the figure: 1. input shaft, 2. first small cylindrical gear, 3. output shaft, 4. first large cylindrical gear, 5. second large cylindrical gear, 6. second small cylindrical gear, 7. first large bevel gear, 8. second large bevel gear, 9. bevel gear frame, 10. small bevel gear, 11. third small cylindrical gear, 12. disc spring, 13. elastic adjusting rod, 14. gear frame, 15. adjusting screw, 16. bearing, 30. lever fixing block, 31. lever, 40. first large bevel gear mounting groove, 50. second large bevel gear mounting groove. Detailed Embodiments

[0031] As Figure 1 、 Figure 2 、 Figure 3 and Figure 4 shown, the differential large-torque gear reducer disclosed by the present invention includes a first small cylindrical gear 2 arranged on an input shaft 1. The input shaft 1 is connected to a driving device such as a driving motor, and the input shaft 1 can drive the first small cylindrical gear 2 to rotate;

[0032] A first large cylindrical gear 4 and a second large cylindrical gear 5 oppositely arranged on an output shaft 3. The first large cylindrical gear 4 and the second large cylindrical gear 5 can rotate on the output shaft 3, and the first large cylindrical gear 4 meshes with the first small cylindrical gear 2. In this embodiment, asFigure 5 As shown, the first large cylindrical gear 4 and the second large cylindrical gear 5 are respectively installed at both ends of the output shaft 3 through bearings 16. The input shaft 1 can drive the first small cylindrical gear 2 to rotate, and the first small cylindrical gear drives the first large cylindrical gear to rotate;

[0033] A second small cylindrical gear 6 that meshes with the first small cylindrical gear 2 and the second large cylindrical gear 5 respectively. Specifically, the second small cylindrical gear 6 is installed on the reducer housing through a gear shaft, and the second small cylindrical gear 6 meshes with the first small cylindrical gear 2 and the second large cylindrical gear 5 respectively. The input shaft 1 can drive the first small cylindrical gear 2 to rotate, the first small cylindrical gear 2 drives the second small cylindrical gear 6 to rotate, and then the second small cylindrical gear 6 drives the second large cylindrical gear 5 to rotate;

[0034] A first large bevel gear 7 and a second large bevel gear 8 that are oppositely arranged on the output shaft 3. The first large bevel gear 7 is fixedly connected to the end face of the first large cylindrical gear 4 facing the second large cylindrical gear 5, and the second large bevel gear 8 is fixedly connected to the end face of the second large cylindrical gear 5 facing the first large cylindrical gear 4. That is, the first large bevel gear 7 and the second large bevel gear 8 are placed between the first large cylindrical gear and the second large cylindrical gear and are respectively fixedly connected to the first large cylindrical gear and the second large cylindrical gear. The rotation of the first large cylindrical gear can drive the first large bevel gear to rotate, and the rotation of the second large cylindrical gear can drive the second large bevel gear to rotate;

[0035] A small bevel gear 10 fixedly connected to the output shaft 3 through a bevel gear frame 9. The small bevel gear 10 meshes with the first large bevel gear 7 and the second large bevel gear 8 respectively. That is, the small bevel gear is placed between the two large bevel gears and is fixedly connected to the output shaft;

[0036] The transmission ratio of the transmission system composed of the first small cylindrical gear 2, the first large cylindrical gear 4, the first large bevel gear 7 and the small bevel gear 10 is different from the transmission ratio of the transmission system composed of the second small cylindrical gear 6, the second large cylindrical gear 5, the second large bevel gear 8 and the small bevel gear 10. Since the transmission ratios of the two transmission systems are different, when the driving device is driven through the input shaft, the speeds transmitted to the small bevel gear by the two transmission systems are different. Furthermore, the self-rotation of the small bevel gear can be realized. At the same time, the small bevel gear can drive the output shaft to revolve around the axis of the output shaft through the bevel gear frame, and then drive the output shaft to output.

[0037] The differential large-torque gear reducer disclosed by the present invention realizes the output of the output shaft of the reducer by different transmission ratios of two transmission systems. Therefore, the difference in the transmission ratios of the two transmission systems can be designed to be small, and thus the revolution speed of the small bevel gear can be low and the torque can be large, and further the driving of heavy loads by the reducer can be realized. The reducer can be used to drive the swing head to rotate in a machine tool to achieve the cutting effect of heavy loads.

[0038] The different transmission ratios of the two transmission systems in the differential large-torque gear reducer disclosed by the present invention can be realized in the following various ways: at least one pair of gears among the first small cylindrical gear and the second small cylindrical gear, and the first large cylindrical gear and the second large cylindrical gear have different numbers of teeth.

[0039] In this embodiment, preferably, the first small cylindrical gear and the second small cylindrical gear have the same number of teeth, the first large cylindrical gear and the second large cylindrical gear have different numbers of teeth, and the first large bevel gear and the second large bevel gear have the same number of teeth to realize different transmission ratios of the two transmission systems. Since the first large cylindrical gear and the second large cylindrical gear have different numbers of teeth, a larger transmission ratio can be obtained, and further a larger reduction ratio of the reducer can be obtained, so as to output high torque and heavy loads. Two synchronous small cylindrical helical gears are respectively meshed with two large cylindrical helical gears with different numbers of teeth to realize the first speed reduction and torque increase process. Two large bevel gears with the same specifications are installed coaxially and respectively keep synchronous operation with the two large cylindrical gears. At this time, the two large bevel gears realize differential rotation. The small bevel gear is simultaneously meshed with the two large bevel gears. As the large bevel gears run differentially, the small bevel gear rotates around its own axis while revolving around the axis of the large bevel gear. And because the tooth difference between the two large cylindrical gears is small, the revolution speed of the small bevel gear is very low, realizing the second speed reduction and torque increase. During the bevel gear transmission process, the small bevel gear adopts the axial adjustment method of the conical sleeve to eliminate the meshing clearance, ensuring the accuracy and stability of the bevel gear transmission.

[0040] Furthermore, it further includes a third small cylindrical gear 11 arranged on the same gear shaft as the second small cylindrical gear 6. The third small cylindrical gear 11 meshes with the first small cylindrical gear 2. A reverse backlash elimination structure is provided between the second small cylindrical gear 6 and the third small cylindrical gear 11. Since the third small cylindrical gear 11 is provided and the reverse backlash elimination structure is provided between the second small cylindrical gear and the third small cylindrical gear, the first small cylindrical gear can be closely meshed with the second small cylindrical gear or the third small cylindrical gear whether it rotates forward or backward, that is, the forward and reverse meshing clearances between the second small cylindrical gear and the third small cylindrical gear and the first small cylindrical gear are eliminated, ensuring the synchronicity of the input and achieving the effect of precise transmission.

[0041] Furthermore, the first small cylindrical gear 2, the second small cylindrical gear 6, the third small cylindrical gear 11, the first large cylindrical gear 4, and the second large cylindrical gear 5 are all cylindrical helical gears. Using helical gears provides smooth transmission, low noise, large contact ratio, and high load-carrying capacity.

[0042] Furthermore, in this embodiment, the backlash elimination structure is a pair of disc springs 12 disposed between the second small cylindrical gear 6 and the third small cylindrical gear 11. Specifically, the second small cylindrical gear is fixed on the gear shaft, and the third small cylindrical gear is also installed on the gear shaft and has a certain axial movement clearance along the axial direction of the gear shaft. The disc springs are disposed between the second small cylindrical gear 6 and the third small cylindrical gear 11, which enables both the second small cylindrical gear 6 and the third small cylindrical gear 11 to mesh with the first small cylindrical gear, ensuring the synchronization of the input and achieving the effect of precise transmission.

[0043] Furthermore, as Figure 5 and Figure 6 shown, a lever fixing block 30 is provided on the outer diameter of the output shaft 3. A lever 31 is provided on the lever fixing block 30. In this embodiment, the outer diameter of the output shaft is a polygonal structure. Two radially outward protruding lever fixing blocks are provided on the outer diameter of the output shaft. Lever mounting holes are provided on the lever fixing blocks, and the lever is inserted into the lever mounting holes;

[0044] At least one end of the lever 31 is provided with the bevel gear holder 9. In this embodiment, the lever is disposed within the lever mounting block and is fixed at one end by a gasket and a nut, and a bevel gear holder 9 is installed at the other end. A small bevel gear 10 is installed on the bevel gear holder. The small bevel gear meshes with the large bevel gears on both sides. Then, the large bevel gears drive the small bevel gear. Since the lever fixing block is provided on the outer diameter of the output shaft, the small bevel gear drives the output shaft to rotate through the bevel gear holder and the lever. The bevel gear holder and the lever increase the lever arm of the small bevel gear on the output shaft, further achieving the output effect of large torque and heavy load. Preferably, the bevel gear holder is perpendicular to the lever, such that the central axis of the small bevel gear passes through the center of the output shaft to obtain a better output effect of large torque and heavy load.

[0045] Furthermore, a first large bevel gear mounting groove 40 is provided on the side of the first large cylindrical gear 4 facing the second large cylindrical gear 5. The first large bevel gear 7 is placed within the first large bevel gear mounting groove 40. In this embodiment, the first large bevel gear 7 is placed within the first large bevel gear mounting groove 40 and is fixedly connected to the first large cylindrical gear by a plurality of bolts;

[0046] On one side of the second large cylindrical gear 5 facing the first large cylindrical gear 4, there is a second large bevel gear mounting groove 50. The second large bevel gear 8 is placed in the second large bevel gear mounting groove 50. In this embodiment, the second large bevel gear 8 is placed in the second large bevel gear mounting groove 50 and fixedly connected to the second large cylindrical gear by a plurality of bolts. By providing the bevel gear mounting groove, the volume and weight of the reducer can be effectively reduced.

[0047] Furthermore, it also includes a radial backlash elimination structure for eliminating radial backlash between the first small cylindrical gear and the first large cylindrical gear and between the first small cylindrical gear and the first large cylindrical gear.

[0048] Specifically, as Figure 7 shown, the first small cylindrical gear is mounted on the first gear rack 64 through the input shaft. The other end of the first gear rack 64 is hinged to the reducer housing through the first hinge shaft 60. The second small cylindrical gear is mounted on the second gear rack 65 through the gear shaft. The other end of the second gear rack 65 is hinged to the reducer housing through the second hinge shaft 61. One side of the first gear rack 64 is provided with a first elastic lever 62. One end of the first elastic lever 62 is hinged to the first hinge shaft 60, and the other end is placed on the side of the second gear rack 65 facing the second large cylindrical gear 5 and abuts against the side of the second gear rack 5 facing the large cylindrical gear. One side of the second gear rack 65 is provided with the second elastic lever 63. One end of the second elastic lever 63 is hinged to the second hinge shaft 61, and the other end is placed on the side of the first gear rack 64 facing the first large cylindrical gear 4 and abuts against the side of the first gear rack 64 facing the large cylindrical gear. The first elastic lever 62 and the second elastic lever 63 are located on different sides of the first gear rack. An adjustment screw 66 is respectively provided on the first elastic lever and the second elastic lever. In the present invention, since the elastic lever and the gear rack are hinged by sharing a hinge shaft, and the relative position of the elastic lever and the gear rack is adjusted by the adjustment screw, the radial pressing of the meshing of the small cylindrical gear and the large cylindrical gear can be realized, and the meshing clearance can be eliminated. At the same time, for the two sets of meshing small gear systems, they are "locked" with each other through the elastic lever to form an internal acting force. When the small gear system receives the reaction force from the large gear, it can not only make the small gear receive a downward acting force to prevent the occurrence of meshing clearance, but also prevent the downward force received by the small gear from being too large, resulting in excessive meshing of the gear and causing tooth surface wear.

[0049] The above is only the preferred specific embodiment of the present invention, but the protection scope of the present invention is not limited thereto. Any person skilled in the art within the technical scope disclosed by the present invention, according to the technical solution and inventive concept of the present invention, makes equivalent substitutions or changes, and all should be covered within the protection scope of the present invention.

Claims

1. A differential large-torque gear reducer, characterized in that: including a first small cylindrical gear disposed on an input shaft; a first large cylindrical gear and a second large cylindrical gear oppositely disposed at two ends of an output shaft, the first large cylindrical gear and the second large cylindrical gear being rotatable on the output shaft, and the first large cylindrical gear meshing with the first small cylindrical gear; a second small cylindrical gear meshing with the first small cylindrical gear and the second large cylindrical gear respectively; a first large bevel gear and a second large bevel gear oppositely disposed on the output shaft, the first large bevel gear being fixedly connected to one end face of the first large cylindrical gear facing the second large cylindrical gear, and the second large bevel gear being fixedly connected to one end face of the second large cylindrical gear facing the first large cylindrical gear; a small bevel gear fixedly connected to the output shaft through a bevel gear bracket, the small bevel gear meshing with the first large bevel gear and the second large bevel gear respectively; the transmission ratio of the transmission system composed of the first small cylindrical gear, the first large cylindrical gear, the first large bevel gear and the small bevel gear is different from the transmission ratio of the transmission system composed of the second small cylindrical gear, the second large cylindrical gear, the second large bevel gear and the small bevel gear; a first large bevel gear mounting groove is provided on one side of the first large cylindrical gear facing the second large cylindrical gear, and the first large bevel gear is placed in the first large bevel gear mounting groove; a second large bevel gear mounting groove is provided on one side of the second large cylindrical gear facing the first large cylindrical gear, and the second large bevel gear is placed in the second large bevel gear mounting groove.

2. The differential large-torque gear reducer according to claim 1, characterized in that: At least one pair of gears among the first small cylindrical gear and the second small cylindrical gear and the first large cylindrical gear and the second large cylindrical gear have different numbers of teeth.

3. The differential large-torque gear reducer according to claim 2, characterized in that: The first small cylindrical gear and the second small cylindrical gear have the same number of teeth, and the first large cylindrical gear and the second large cylindrical gear have different numbers of teeth.

4. The differential large-torque gear reducer according to any one of claims 1 to 3, characterized in that: further including a third small cylindrical gear disposed on the same gear shaft as the second small cylindrical gear, the third small cylindrical gear meshing with the first small cylindrical gear, and a backlash elimination structure is provided between the second small cylindrical gear and the third small cylindrical gear.

5. The differential large-torque gear reducer according to claim 4, characterized in that: The first small cylindrical gear, the second small cylindrical gear, the third small cylindrical gear, the first large cylindrical gear and the second large cylindrical gear are all cylindrical helical gears.

6. The differential large-torque gear reducer according to claim 5, characterized in that: The backlash elimination structure is a disc spring disposed between the second small cylindrical gear and the third small cylindrical gear.

7. The differential large-torque gear reducer according to claim 1, characterized in that: a lever fixing block is provided on the outer diameter of the output shaft, and a lever is provided on the lever fixing block; at least one end of the lever is provided with the bevel gear bracket.

8. The differential large-torque gear reducer according to claim 7, characterized in that: The bevel gear bracket is perpendicularly disposed with respect to the lever, so that the central axis of the small bevel gear passes through the center of the output shaft.

9. The differential large-torque gear reducer according to claim 1, characterized in that: further including a radial backlash elimination structure for performing radial backlash elimination between the first small cylindrical gear and the first large cylindrical gear and between the second small cylindrical gear and the second large cylindrical gear.

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