A large reduction ratio reduction device based on bevel gear commutation

Abstract

A large reduction ratio reduction device based on bevel gear commutation, belonging to the field of mechanical gear transmission. The input bevel gear shaft serves as the input end of the reduction device. Both of the first conversion bevel gears are meshed with the input bevel gear shaft. The first conversion bevel gear and the second conversion bevel gear connected by a torsion shaft have the same helix direction; the bevel gears of the bevel gear ring assembly are simultaneously meshed with the two second conversion bevel gears, and the bevel gears of the bevel gear ring assembly have a helix direction opposite to that of the input bevel gear shaft; the sun gear is connected to the input bevel gear shaft through a central transmission rod and has the same helix direction, and the planet gears are simultaneously meshed with the internal teeth of the ring of the bevel gear ring assembly and the sun gear; the planet carrier is used to support multiple planet gears at the same time; the planet carrier serves as the output end of the reduction device. It is used to achieve large reduction ratio transmission.

Description

Technical Field

[0001] The present invention relates to a high reduction ratio reduction device, belonging to the field of mechanical gear transmission. Background Art

[0002] Gear transmission is the most important speed matching device in industry, featuring stable transmission and accurate reduction ratio. Gear transmission mainly includes parallel-axis cylindrical gears, bevel gears, planetary internal meshing gears, etc. According to the characteristics of the helix angle, it can also be divided into spur gears, helical gears, herringbone gears, etc. Parallel-axis cylindrical gears are the most widely used due to their relatively simple structure and easy manufacturing. Bevel gears are mainly used in occasions with the need for reversing transmission. Planetary internal meshing gear transmission has a high power density due to the coaxial input and output and large reduction ratio. By combining various parallel-axis cylindrical gears, bevel gears, and planetary internal meshing gear transmissions, various transmission characteristics can be taken into account.

[0003] In the existing planetary high reduction ratio reducer on the market, the first stage has a fixed ring gear, a sun gear input, and a planetary carrier output. The first-stage planetary carrier is connected to the second-stage sun gear. The second-stage ring gear is fixed, and the second-stage planetary carrier outputs. Since the reduction ratio of a single-stage planet is limited, multi-stage reduction is required to achieve high reduction ratio reduction, making the structure relatively complex and the reliability insufficient. Summary of the Invention

[0004] The purpose of the present invention is to solve the problems of the complex structure and insufficient reliability of the existing planetary high reduction ratio reducer, and a high reduction ratio reduction device based on bevel gear commutation is proposed.

[0005] A high reduction ratio reduction device based on bevel gear commutation, characterized in that the device includes an input bevel gear shaft, 2 first conversion bevel gears, 2 second conversion bevel gears, 2 torsion shafts, a bevel gear ring assembly, multiple planetary gears, a planetary carrier, a sun gear, and a central transmission rod;

[0006] The input bevel gear shaft serves as the input end of the reduction device. Both 2 first conversion bevel gears are meshed with the input bevel gear shaft. One first conversion bevel gear and one second conversion bevel gear are sleeved on one torsion shaft, and the first conversion bevel gear and the second conversion bevel gear on one torsion shaft have the same helix direction;

[0007] The bevel gear of the bevel gear ring assembly is simultaneously meshed with 2 second conversion bevel gears, and the bevel gear of the bevel gear ring assembly has a helix direction opposite to that of the input bevel gear shaft; the sun gear is connected to the input bevel gear shaft through the central transmission rod and has the same helix direction, and the planetary gears are simultaneously meshed with the internal teeth of the ring gear of the bevel gear ring assembly and the sun gear;

[0008] The planet carrier is used to support multiple planet gears simultaneously; the support shaft of the planet carrier is rotationally connected to each planet gear through a support bearing; the planet carrier serves as the output end of the reduction device;

[0009] The speed ratio i of the input bevel gear shaft to the planet carrier OH :

[0010]

[0011] In the formula, Z 1 is the number of teeth of the input bevel gear shaft, Z 2 is the number of teeth of the first conversion bevel gear, Z 3 is the number of teeth of the second conversion bevel gear, Z 4 is the number of teeth of the bevel gear in the bevel gear ring assembly, Z 5 is the number of teeth of the gear ring in the bevel gear ring assembly, Z 6 is the number of teeth of the planet gear, Z 7 is the number of teeth of the sun gear.

[0012] Preferably, the specific process of obtaining the speed ratio i of the input bevel gear shaft to the planet carrier OH is as follows:

[0013] Based on the speed ratio of the input bevel gear shaft to the first conversion bevel gear, the speed ratio of the second conversion bevel gear to the bevel gear ring assembly, and the rotational speed of the input bevel gear shaft, the rotational speed of the bevel gear ring assembly is obtained; based on the rotational speed of the bevel gear ring assembly, the number of teeth of the gear ring in the bevel gear ring assembly, and the module of the planet gear planetary gear train, the pitch circle linear velocity of the gear ring in the bevel gear ring assembly is obtained;

[0014] Based on the rotational speed of the input bevel gear shaft, the module of the planet gear planetary gear train, and the number of teeth of the sun gear, the pitch circle linear velocity of the sun gear (8) is obtained;

[0015] Based on the pitch circle linear velocity of the gear ring in the bevel gear ring assembly and the pitch circle linear velocity of the sun gear, the center line velocity of the planet gear is obtained;

[0016] Based on the center line velocity of the planet gear and the center radius of the planet carrier, the rotational speed of the planet carrier is obtained;

[0017] Based on the rotational speed of the planet carrier and the rotational speed of the input bevel gear shaft, the speed ratio i of the input bevel gear shaft to the planet carrier is obtained OH .

[0018] The beneficial effects of the present invention are:

[0019] Taking the input bevel gear shaft as the input end, after two-stage bevel gear reduction and reverse conversion to the planet carrier, the sun gear of the planetary gear train is connected to the input bevel gear shaft through a transmission rod, and the planet carrier serves as the output end of the entire large speed ratio reduction device. At this time, the sun gear and the gear ring rotate in opposite directions, thereby obtaining a large speed ratio transmission between the planet carrier and the sun gear.

[0020] The reverse rotation of the sun gear and the ring gear of the planetary gear train is achieved by bevel gear transmission, realizing a large speed ratio transmission between the planet carrier and the sun gear. It has a high degree of structural integration and strong load-bearing capacity. The present invention can be widely applied to high-power and large speed ratio transmission fields such as ships and metallurgy.

[0021] By using two first conversion bevel gears with opposite helix directions, the speed ratio of the internal planetary gear transmission is significantly increased, and then a design scheme of a large speed ratio reduction device is obtained.

[0022] By using the corresponding second conversion bevel gears that are bilaterally meshed with the two first conversion bevel gears, the reverse rotation of the gear and the sun gear is achieved through the commutation of the two second conversion bevel gears, enabling the speed of the planet carrier to be extremely low, which is completely different from the prior art principle. Secondly, the present application uses the commutation function of the bevel gear to reverse the ring gear and the sun gear of the planet to reduce the speed of the planet carrier, and through tooth matching, the planet carrier can rotate forward or backward when the ring gear and the sun gear reverse, realizing a large forward or reverse speed ratio, and the speed of the planet carrier can tend to zero, thus obtaining an extremely large reduction ratio.

[0023] Therefore, the present application uses bevel gear transmission to achieve the reverse rotation of the sun gear and the ring gear of the planetary gear train, realizing a large speed ratio transmission between the planet carrier and the sun gear. It has a high degree of structural integration, strong load-bearing capacity and high reliability. The present application can be widely applied to high-power and large speed ratio transmission fields such as ships and metallurgy, with a wide range of applications. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 FIG. is a transmission principle diagram of a large speed ratio reduction device based on bevel gear commutation;

[0025] Figure 2 FIG. is a partial steering relationship diagram of the planetary stage used to illustrate the large speed ratio realization process. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0026] The following will clearly and completely describe the technical solutions in the embodiments of the present invention with reference to the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts shall fall within the protection scope of the present invention.

[0027] It should be noted that, without conflict, the embodiments in the present invention and the features in the embodiments can be combined with each other.

[0028] The following further illustrates the present invention with reference to the accompanying drawings and specific embodiments, but is not a limitation of the present invention.

[0029] Embodiment 1:

[0030] Combined with Figures 1 to 2 To illustrate this embodiment, a large reduction ratio reduction device based on bevel gear commutation, the device includes an input bevel gear shaft 1, 2 first conversion bevel gears 2, 2 second conversion bevel gears 3, 2 torsion shafts 4, a bevel gear ring assembly 5, multiple planet gears 6, a planet carrier 7, a sun gear 8 and a central drive rod 9;

[0031] The input bevel gear shaft 1 serves as the input end of the reduction device. Both of the 2 first conversion bevel gears 2 are meshed with the input bevel gear shaft 1. One first conversion bevel gear 2 and one second conversion bevel gear 3 are sleeved on one torsion shaft 4, and the first conversion bevel gear 2 and the second conversion bevel gear 3 on one torsion shaft 4 have the same helix direction;

[0032] The bevel gears of the bevel gear ring assembly 5 are simultaneously meshed with the 2 second conversion bevel gears 3, and the bevel gears of the bevel gear ring assembly 5 have a helix direction opposite to that of the input bevel gear shaft 1; The sun gear 8 is connected to the input bevel gear shaft 1 through the central drive rod 9 and has the same helix direction. The planet gears 6 are simultaneously meshed with the internal teeth of the ring of the bevel gear ring assembly 5 and the sun gear 8;

[0033] The planet carrier 7 is used to support multiple planet gears 6 at the same time; The support shaft of the planet carrier 7 and the axis of each planet gear 6 are rotationally connected through a support bearing 10; The planet carrier 7 serves as the output end of the reduction device;

[0034] The speed ratio i of the input bevel gear shaft 1 to the planet carrier 7 OH :

[0035]

[0036] In the formula, Z 1 is the number of teeth of the input bevel gear shaft 1, Z 2 is the number of teeth of the first conversion bevel gear 2, Z 3 is the number of teeth of the second conversion bevel gear 3, Z 4 is the number of teeth of the bevel gear of the bevel gear ring assembly 5, Z 5 is the number of teeth of the ring of the bevel gear ring assembly 5, Z 6 is the number of teeth of the planet gear 6, Z 7 is the number of teeth of the sun gear 8.

[0037] In this embodiment, Figure 2 is the steering relationship of the planetary stage of the invention. It can be seen that the sun gear 8 and the bevel gear ring assembly 5 have opposite helix directions, and their pitch circle linear velocities v 5 and v 7In the opposite direction, based on the meshing principle, the planet gear 6 performs pure rolling with the bevel gear ring assembly 5 and the sun gear 8 simultaneously. The linear velocity v at the center of the planet gear 6 H and v 5 and v 7 According to Figure 2 the velocity distribution of, v H is the linear velocity of the planet carrier 7. Since v 5 and v 7 are in the opposite direction, v H is very small, which makes the rotational speed of the planet carrier 7 relatively low, and finally realizes a large speed ratio reduction drive.

[0038] There are at least three planet gears 6, and generally, the number is determined according to the strength design.

[0039] In a preferred embodiment, the specific process of obtaining the speed ratio i OH between the input bevel gear shaft 1 and the planet carrier 7 is as follows:

[0040] According to the speed ratio between the input bevel gear shaft 1 and the first conversion bevel gear 2, the speed ratio between the second conversion bevel gear 3 and the bevel gear ring assembly 5, and the rotational speed of the input bevel gear shaft 1, the rotational speed of the bevel gear ring assembly 5 is obtained; according to the rotational speed of the bevel gear ring assembly 5, the number of teeth of the gear ring of the bevel gear ring assembly 5, and the module of the planetary gear train of the planet gear 6, the linear velocity of the pitch circle of the gear ring of the bevel gear ring assembly 5 is obtained;

[0041] According to the rotational speed of the input bevel gear shaft 1, the module of the planetary gear train of the planet gear 6, and the number of teeth of the sun gear 8, the linear velocity of the pitch circle of the sun gear 8 is obtained;

[0042] According to the linear velocity of the pitch circle of the gear ring of the bevel gear ring assembly 5 and the linear velocity of the pitch circle of the sun gear 8, the linear velocity of the center line of the planet gear 6 is obtained;

[0043] According to the linear velocity of the center line of the planet gear 6 and the central radius of the planet carrier 7, the rotational speed of the planet carrier 7 is obtained;

[0044] According to the rotational speed of the planet carrier 7 and the rotational speed of the input bevel gear shaft 1, the speed ratio i OH between the input bevel gear shaft 1 and the planet carrier 7 is obtained.

[0045] In a preferred embodiment, the speed ratio i 21 between the input bevel gear shaft 1 and the first conversion bevel gear 2 is:

[0046]

[0047] The speed ratio i 43 between the second conversion bevel gear 3 and the bevel gear ring assembly 5 is:

[0048]

[0049] Rotational speed n of the bevel gear ring assembly 5 5 :

[0050]

[0051] Wherein, n 0 is the rotational speed of the input bevel gear shaft 1.

[0052] In a preferred embodiment, the pitch circle linear velocity of the bevel gear ring assembly 5 is:

[0053]

[0054] Wherein, v 5 is the pitch circle linear velocity of the bevel gear ring assembly 5, m is the module of the planetary gear train of the planetary gear 6, and Z 5 is the number of teeth of the bevel gear ring of the bevel gear ring assembly 5.

[0055] In a preferred embodiment, the pitch circle linear velocity of the sun gear 8 is:

[0056]

[0057] Wherein, v 7 is the pitch circle linear velocity of the sun gear 8, Z 7 is the number of teeth of the sun gear 8, and n 0 is the rotational speed of the input bevel gear shaft 1.

[0058] In a preferred embodiment, the center linear velocity of the planetary gear 6 is:

[0059]

[0060] Wherein, v H is the center linear velocity of the planetary gear 6.

[0061] In a preferred embodiment, the rotational speed of the planet carrier 7 is:

[0062]

[0063] Wherein, n H is the rotational speed of the planet carrier 7, R H is the center radius of the planet carrier 7,

[0064] In this embodiment, the rotational speed and linear velocity calculation of the planet carrier 7 are derived to obtain the speed ratio relationship between the planet carrier 7 and the input bevel gear shaft 1.

[0065] Let the rotational speed n 0 and the number of teeth Z 1 of the input bevel gear shaft 1, the number of teeth Z 2 of the first conversion bevel gear 2, and the number of teeth Z 3, the number of teeth Z of the bevel gear in the bevel gear ring assembly 5 4 , the number of teeth Z of the ring gear in the bevel gear ring assembly 5 5 , the rotational speed n of the bevel gear ring assembly 5 5 , the linear velocity v of the pitch circle of the ring gear in the bevel gear ring assembly 5 5 , the number of teeth Z of the planet gear 6 6 , the number of teeth Z of the sun gear 8 7 , the linear velocity v of the pitch circle of the sun gear 8 7 , the rotational speed n of the output planet carrier 7 H , the linear velocity v of the center line of the planet gear 6 H , the center radius R of the planet gear H , the module m of the planetary gear train. All the above physical quantities are scalars, and the direction is according to Figure 2 .

[0066] The speed ratio of the input bevel gear shaft 1 and the first conversion bevel gear 2

[0067] The speed ratio of the second conversion bevel gear 3 and the bevel gear ring assembly 5

[0068] The rotational speed of the bevel gear ring assembly 5

[0069] The linear velocity of the pitch circle of the ring gear in the bevel gear ring assembly 5

[0070] The linear velocity of the pitch circle of the sun gear 8

[0071] Through Figure 2 the speed distribution, the linear velocity of the center line of the planet gear 6 can be calculated At this time, v 5 and v 7 are both scalars, and their directions are not considered;

[0072] Substitute into the above formulas,

[0073] The center radius of the planet carrier 7 is

[0074] The rotational speed of the planet carrier 7 can be obtained

[0075] It can be seen from the above formula that by matching the teeth, when the difference between Z 5 ·Z 1 ·Z 3 and Z 7 ·Z 2 ·Z 4 is smaller, n H is lower, and a larger speed ratio can be obtained. When Z 7 ·Z2 ·Z 4 -Z 5 ·Z 1 ·Z 3 When it is negative, the planet carrier 7 will reverse. Therefore, this device can not only achieve high reduction ratio deceleration with the same rotation direction of input and output, but also achieve high reduction ratio deceleration with opposite rotation directions of input and output.

[0076] From the above formula, the reduction ratio of the input and output of this device can be obtained as

[0077] In summary, this application provides a high reduction ratio deceleration device based on bevel gear commutation, which makes full use of the commutation and reverse function of bevel gears and combines the characteristic that the rotational speed of the planet carrier decreases when the tooth ring and the sun gear of the planetary gear train reverse, achieving a high reduction ratio deceleration effect. This structure can be widely applied to industrial fields such as ships and metallurgy with high power and high reduction ratio deceleration requirements.

[0078] Although the present invention has been described herein with reference to specific embodiments, it should be understood that these embodiments are merely examples of the principles and applications of the present invention. Therefore, it should be understood that many modifications can be made to the exemplary embodiments, and other arrangements can be designed, as long as they do not depart from the spirit and scope of the present invention as defined by the appended claims. It should be understood that different dependent claims and the features described herein can be combined in a manner different from that described in the original claims. It should also be understood that the features described in connection with a single embodiment can be used in other described embodiments.

Claims

1. A large reduction ratio reduction device based on bevel gear commutation, characterized in that, the device includes an input bevel gear shaft (1), two first conversion bevel gears (2), two second conversion bevel gears (3), two torque shafts (4), a bevel gear ring assembly (5), multiple planet gears (6), a planet carrier (7), a sun gear (8) and a central drive rod (9); The input bevel gear shaft (1) serves as the input end of the reduction device. Both of the two first conversion bevel gears (2) are meshed with the input bevel gear shaft (1). One first conversion bevel gear (2) and one second conversion bevel gear (3) are sleeved on one torque shaft (4), and the first conversion bevel gear (2) and the second conversion bevel gear (3) on one torque shaft (4) have the same helix direction; The bevel gears of the bevel gear ring assembly (5) are simultaneously meshed with the two second conversion bevel gears (3), and the bevel gears of the bevel gear ring assembly (5) have a helix direction opposite to that of the input bevel gear shaft (1); The sun gear (8) is connected to the input bevel gear shaft (1) through the central drive rod (9) and has the same helix direction. The planet gears (6) are simultaneously meshed with the internal teeth of the ring of the bevel gear ring assembly (5) and the sun gear (8); The planet carrier (7) is used to support multiple planet gears (6) simultaneously; The support shaft of the planet carrier (7) and each planet gear (6) are rotationally connected through a support bearing (10); The planet carrier (7) serves as the output end of the reduction device; The speed ratio i of the input bevel gear shaft (1) and the planet carrier (7) OH : Where, Z 1 is the number of teeth of the input bevel gear shaft (1), Z 2 is the number of teeth of the first conversion bevel gear (2), Z 3 is the number of teeth of the second conversion bevel gear (3), Z 4 is the number of teeth of the bevel gear of the bevel gear ring assembly (5), Z 5 is the number of teeth of the gear ring of the bevel gear ring assembly (5), Z 6 is the number of teeth of the planet gear (6), Z 7 is the number of teeth of the sun gear (8).

2. The large reduction ratio reduction device based on bevel gear commutation according to claim 1, characterized in that, Obtain the speed ratio \(i\) of the input bevel gear shaft (1) and the planet carrier (7). OH The specific process is as follows: According to the speed ratio of the input bevel gear shaft (1) and the first conversion bevel gear (2), the speed ratio of the second conversion bevel gear (3) and the bevel gear ring assembly (5), and the rotational speed of the input bevel gear shaft (1), the rotational speed of the bevel gear ring assembly (5) is obtained; According to the rotational speed of the bevel gear ring assembly (5), the number of teeth of the ring of the bevel gear ring assembly (5), and the modulus of the planet gear train of the planet gears (6), the pitch circle linear velocity of the ring of the bevel gear ring assembly (5) is obtained; According to the rotational speed of the input bevel gear shaft (1), the modulus of the planet gear train of the planet gears (6), and the number of teeth of the sun gear (8), the pitch circle linear velocity of the sun gear (8) is obtained; According to the pitch circle linear velocity of the ring of the bevel gear ring assembly (5) and the pitch circle linear velocity of the sun gear (8), the center line velocity of the planet gears (6) is obtained; According to the center line velocity of the planet gears (6) and the central radius of the planet carrier (7), the rotational speed of the planet carrier (7) is obtained; According to the rotational speed of the planet carrier (7) and the rotational speed of the input bevel gear shaft (1), the speed ratio i between the input bevel gear shaft (1) and the planet carrier (7) is obtained OH .

3. The large reduction ratio reduction device based on bevel gear commutation according to claim 2, characterized in that, The speed ratio i of the input bevel gear shaft (1) and the first-stage conversion bevel gear (2) 21 is as follows: The speed ratio i of the second conversion bevel gear (3) and the bevel gear ring assembly (5) 43 : Rotational speed n of the bevel gear ring assembly (5) 5 : In the formula, n 0 is the rotational speed of the input bevel gear shaft (1), and n 5 is the rotational speed of the bevel gear ring assembly (5).

4. The large reduction ratio reduction device based on bevel gear commutation according to claim 3, characterized in that, The pitch circle linear velocity of the ring of the bevel gear ring assembly (5) is: Where, v 5 is the pitch circle linear velocity of the ring gear of the bevel gear ring assembly (5), m is the module of the planetary gear train of the planetary gear (6), Z 5 is the number of teeth of the ring gear of the bevel gear ring assembly (5).

5. The large reduction ratio reduction device based on bevel gear commutation according to claim 4, characterized in that, The pitch circle linear velocity of the sun gear (8) is: where v 7 is the pitch circle linear velocity of the sun gear (8), Z 7 is the number of teeth of the sun gear (8), n 0 is the rotational speed of the input bevel gear shaft (1).

6. The large reduction ratio reduction device based on bevel gear commutation according to claim 5, characterized in that, The center line velocity of the planet gears (6) is: where v H is the center line speed of the planet gear (6).

7. The large reduction ratio reduction device based on bevel gear commutation according to claim 6, characterized in that, The rotational speed of the planet carrier (7) is: where n H is the rotational speed of the planet carrier (7), R H is the central radius of the planet carrier (7),

Images