Design method of parallel and vertical reducer output speed zero rotation difference for scraper conveyor

Abstract

A parallel and vertical speed reducer output rotation speed zero rotation difference design method for a scraper conveyor, comprising the following steps: determining the transmission ratio i of a parallel planetary gear reducer 平 , determining the transmission ratio i of a parallel planetary gear reducer 平 , determining the transmission ratio i of a vertical planetary gear reducer 垂 , setting the transmission ratios of the parallel planetary gear reducer and the vertical planetary gear reducer to be equal, and the output rotation speed zero rotation difference, so that i 平 = i 垂 , and determining the gear tooth numbers of each stage transmission gear pair; the present application can ensure that the output ends of the parallel and vertical speed reducers have equal transmission ratios, so as to ensure transmission efficiency; and multiple sets of rotation ratios can be adjusted to adapt to different chain speed requirements of the scraper conveyor; by using the transmission ratio calculation method, the same or different power parallel and vertical speed reducers can be configured for the same scraper conveyor according to actual requirements.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of speed reducer, in particular to a parallel and vertical speed reducer output speed zero rotation difference design method for a scraper conveyor. BACKGROUND

[0002] With the continuous development of coal mining technology, the requirements for the scraper conveyor for underground working face raw coal conveying are also getting higher and higher. Some equipment has high transportation capacity, and a pair of parallel and vertical speed reducers are configured at the machine head. In order to improve the transmission efficiency, the transmission ratios of the two speed reducers are required to be the same, and the output speed rotation difference is required to be zero. At present, there is no suitable calculation method for the zero rotation difference of the designed speed ratio of the parallel and vertical speed reducers used in pairs in the scraper conveyor. Usually, different tooth numbers are used for repeated tests to calculate the required speed ratio, so that the transmission ratios of the two speed reducers are close, and the output speed is usually required to be the same, and the high-speed shaft rotation difference is not greater than 1, which is acceptable. However, the unequal speed ratios of the two speed reducers directly affect the transmission efficiency, especially for the scraper conveyor driven by the three power parts. The output ends of the parallel and vertical speed reducers are connected at both ends of the chain wheel shaft group of the machine head, and the unequal transmission ratios of the two speed reducers have a greater impact on the transmission efficiency. SUMMARY

[0003] In order to solve the above technical problems, it is necessary to provide a parallel and vertical speed reducer output speed zero rotation difference design method for a scraper conveyor.

[0004] A parallel and vertical speed reducer output speed zero rotation difference design method for a scraper conveyor, comprising the following steps,

[0005] S1: determining the transmission ratio i of the parallel planetary gear reducer 平 , the transmission ratio i of the parallel planetary gear reducer 平 is calculated according to the following formula,

[0006] i.e. i 平 =i1×i2×i3(1);

[0007] Wherein, i1 is the transmission ratio of the first stage bevel gear; Z2 is the gear tooth number of the parallel planetary gear reducer, and Z1 is the gear tooth number of the parallel planetary gear reducer;

[0008] i2 is the transmission ratio of the second stage bevel gear, i.e. Z4 is the gear tooth number of the large cylindrical gear of the parallel planetary gear reducer, and Z3 is the gear tooth number of the small cylindrical gear of the parallel planetary gear reducer;

[0009] i3 is the transmission ratio of the low-speed planetary gear, i.e. Z6 is the gear tooth number of the internal gear of the parallel planetary gear reducer, and Z5 is the gear tooth number of the sun gear of the parallel planetary gear reducer;

[0010] S2: determining the transmission ratio i of the vertical planetary gear reducer 垂 , the transmission ratio i of the vertical planetary gear reducer is determined as 垂 According to the following formula,

[0011] i.e. i 垂 = i4x i3 (2);

[0012] wherein i4 is the transmission ratio of the high-speed stage planetary gear of the vertical reducer;

[0013] S3: setting the transmission ratio of the parallel planetary gear reducer and the vertical planetary gear reducer to be equal, and the output rotation speed to be zero rotation difference, i 平 = i 垂 ,

[0014] i.e. i 平 = i1x i2x i3 = i 垂 = i4x i3 (3);

[0015] From this, the relationship between the transmission ratio i4 of the high-speed stage planetary gear of the vertical planetary gear reducer, the transmission ratio i1 of the first stage bevel gear, and the transmission ratio i2 of the second stage bevel gear can be derived,

[0016] i.e. i4= i1x i2 (4);

[0017] wherein, Z9 is the tooth number of the high-speed stage planetary transmission inner gear of the vertical planetary gear reducer, and Z8 is the tooth number of the high-speed stage sun gear of the vertical planetary gear reducer;

[0018] Substituting the corresponding calculation formulas of i1, i2, and i4 into formula (4), the following formula can be obtained,

[0019]

[0020] wherein, Z k = Z9+ Z8, i.e. Z k is the sum of the tooth number of the high-speed stage planetary transmission inner gear of the vertical planetary gear reducer and the tooth number of the high-speed stage sun gear of the vertical planetary gear reducer;

[0021] S4: determining the tooth number of each stage transmission gear pair;

[0022] ①, setting the tooth number Z3 of the small cylindrical gear of the second stage transmission pair of the parallel planetary gear reducer to be equal to the tooth number Z8 of the high-speed stage sun gear of the high-speed stage planetary transmission pair of the vertical planetary gear reducer, i.e. Z3= Z8, the relationship between the tooth number of each stage gear pair of the parallel planetary gear reducer and the vertical planetary gear reducer can be determined by formula (5),

[0023] i.e. Further variations can be obtained,

[0024] ②、According to the power and the primary selection transmission ratio, the tooth number Z2 of the bevel gear of the parallel planetary gear reducer and the tooth number Z1 of the bevel gear of the parallel planetary gear reducer in the first stage bevel gear transmission pair of the parallel planetary gear reducer are determined;

[0025] ③、According to the formula (6), if Z1 is an odd number, Z4 takes the value of Z4=K1×Z1, wherein K1 takes an integer, and then Z4 can be calculated. k ; at the same time, Z k can be evenly divided by the number N of planet gears of the high-speed stage planetary transmission of the vertical planetary gear reducer;

[0026] ④、According to the formula (6), if Z1 is an even number, Z4 takes the value of Z4=K2×Z1, wherein K2 is a multiple of the greatest common divisor of Z1, and then Z4 can be calculated. k ; at the same time, Z k can be evenly divided by the number N of planet gears of the high-speed stage planetary transmission of the vertical planetary gear reducer;

[0027] ⑤、The tooth number Z9 of the inner gear of the high-speed stage planetary transmission of the vertical planetary gear reducer is determined;

[0028] wherein it is recommended that Z3=Z8>15, according to Z3=Z8, Z k =Z9+Z8, and then the tooth number Z9 of the inner gear of the high-speed stage planetary transmission of the vertical planetary gear reducer can be calculated.

[0029] ⑥、The tooth number of the low-speed stage planetary transmission gear of the parallel planetary gear reducer is determined;

[0030] wherein it is recommended that Z5>15, the transmission ratio i3 of the low-speed stage planetary gear is 5, according to i.e. the tooth number Z6 of the inner gear of the parallel planetary gear reducer can be calculated; the sum of the tooth number Z6 of the inner gear of the parallel planetary gear reducer and the tooth number Z5 of the sun gear of the parallel planetary gear reducer can be evenly divided by the number M of planet gears of the low-speed stage planetary transmission of the parallel planetary gear reducer;

[0031] ⑦、According to the determined tooth numbers of each gear of the parallel planetary gear reducer and the tooth numbers of each gear of the vertical planetary gear reducer, the total transmission ratio of the parallel planetary gear reducer and the vertical planetary gear reducer is calculated.

[0032] Preferably, in the step S4, if the required transmission ratio range is not reached, the tooth number of the small cylindrical gear Z3 of the second stage transmission pair of the parallel planetary gear reducer and the tooth number of the high-speed stage sun gear Z8 of the vertical planetary gear reducer are simultaneously increased.

[0033] Preferably, in the step S4, if the required transmission ratio range is not reached, the tooth number of the cylindrical gear Z3 of the second stage transmission pair of the parallel planetary gear reducer and the tooth number of the sun gear Z8 of the high speed stage of the vertical planetary gear reducer are simultaneously reduced.

[0034] Preferably, in the step S4, if the required transmission ratio range is not reached, the values of K1 and K2 are adjusted, and Z is recalculated. k .

[0035] Preferably, in the step S4, if the required transmission ratio range is not reached, the tooth number of the cylindrical gear Z3 of the second stage transmission pair of the parallel planetary gear reducer and the tooth number of the sun gear Z8 of the high speed stage of the vertical planetary gear reducer are simultaneously reduced.

[0036] Preferably, in the step S4, the high speed stage planetary transmission of the vertical planetary gear reducer is three planetary wheel transmission, that is, N=3.

[0037] Preferably, in the step S4, the low speed stage planetary transmission of the parallel planetary gear reducer is three planetary wheel transmission, that is, M=3.

[0038] Preferably, in the step S4, the low speed stage planetary transmission of the parallel planetary gear reducer is four planetary wheel transmission, that is, M=4.

[0039] From the above technical solution, it can be seen that the parallel and vertical reducer output rotation speed zero rotation difference design method for the scraper conveyor provided by the application can ensure that the output ends of the parallel and vertical reducers have equal transmission ratios of the two reducers, so as to ensure transmission efficiency; and multiple sets of rotation ratios can be adjusted to adapt to different chain speed requirements of the scraper conveyor; by using this method to calculate the transmission ratio, the same or different power parallel and vertical reducers can be configured for the same scraper conveyor according to actual requirements. DETAILED DESCRIPTION

[0040] The technical solutions in the embodiments of the application will be clearly and completely described below with reference to the embodiments of the application. Obviously, the described embodiments are only part of the embodiments of the application, rather than all the embodiments of the application. Based on the embodiments in the application, all other embodiments obtained by those skilled in the art without creative labor fall within the scope of protection of the application.

[0041] In the description of the application, it should be understood that the terms "upper", "middle", "outer", "inner", "lower" and the like indicate the orientation or positional relationship, which are only used to facilitate the description of the application and simplify the description, and do not indicate or imply that the components or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation of the application.

[0042] Embodiment 1:

[0043] The application provides a parallel and vertical speed reducer output rotation speed zero rotation difference design method for a scraper conveyor, comprising the following steps,

[0044] S1: determining the transmission ratio i of the parallel planetary gear reducer 平 , the transmission ratio i of the parallel planetary gear reducer 平 is calculated according to the following formula,

[0045] That is, i 平 = i1x i2x i3 (1) ;

[0046] Wherein, i1 is the transmission ratio of the first-stage bevel gear; Z2 is the bevel gear tooth number of the parallel planetary gear reducer, and Z1 is the bevel gear tooth number of the parallel planetary gear reducer;

[0047] i2 is the transmission ratio of the second-stage bevel gear, that is, Z4 is the large cylindrical gear tooth number of the parallel planetary gear reducer, and Z3 is the small cylindrical gear tooth number of the parallel planetary gear reducer;

[0048] i3 is the transmission ratio of the low-speed stage planetary gear, that is, Z6 is the internal gear tooth number of the parallel planetary gear reducer, and Z5 is the sun gear tooth number of the parallel planetary gear reducer;

[0049] S2: determining the transmission ratio i of the vertical planetary gear reducer 垂 , the transmission ratio i of the vertical planetary gear reducer is set to be equal to the transmission ratio of the low-speed stage planetary gear transmission of the parallel reducer, so that 垂 is calculated according to the following formula,

[0050] That is, i 垂 = i4x i3 (2) ;

[0051] Wherein, i4 is the transmission ratio of the high-speed stage planetary gear of the vertical reducer;

[0052] S3: setting the transmission ratio of the parallel planetary gear reducer and the transmission ratio of the vertical planetary gear reducer to be equal, and the output rotation speed zero rotation difference, so that i 平 = i 垂 ,

[0053] That is, i 平 = i1x i2x i3 = i 垂 = i4x i3 (3) ;

[0054] Therefore, the relationship between the transmission ratio i4 of the high-speed planetary gear of the vertical planetary gear reducer, the transmission ratio i1 of the first-stage bevel gear, and the transmission ratio i2 of the second-stage bevel gear can be deduced as

[0055] That is, i4 = i1 x i2 (4).

[0056] Wherein, Z9 is the number of teeth of the high-speed planetary transmission inner gear of the vertical planetary gear reducer, and Z8 is the number of teeth of the sun gear of the high-speed planetary transmission of the vertical planetary gear reducer.

[0057] Substituting the corresponding calculation formulas of i1, i2, and i4 into formula (4), the following formula can be obtained,

[0058]

[0059] Wherein, Z k = Z9 + Z8, that is, Z k is the sum of the number of teeth of the high-speed planetary transmission inner gear of the vertical planetary gear reducer and the number of teeth of the sun gear of the high-speed planetary transmission of the vertical planetary gear reducer.

[0060] S4: Determine the number of teeth of each transmission gear pair;

[0061] The number of teeth Z3 of the small cylindrical gear of the second-stage transmission pair of the parallel planetary gear reducer is equal to the number of teeth Z8 of the high-speed sun gear of the high-speed planetary transmission pair of the vertical planetary gear reducer, that is, Z3 = Z8. The relationship between the number of teeth of each gear pair of the parallel planetary gear reducer and the vertical planetary gear reducer can be determined by formula (5),

[0062] That is, Further changes can be made,

[0063] According to the power and the initially selected transmission ratio, the number of teeth Z2 of the bevel gear of the parallel planetary gear reducer and the number of teeth Z1 of the bevel gear of the parallel planetary gear reducer in the first-stage bevel gear transmission gear pair of the parallel planetary gear reducer are determined. Wherein, Z2 can be 33, and Z1 can be 12.

[0064] According to formula (6), Z4 can be Z4 = K2 x Z1, wherein K2 can be 4, that is, Z4 = 4 x 12 = 48, At the same time, it is verified that Z k can be divided by the number N of planetary gears of the high-speed planetary transmission of the vertical planetary gear reducer, wherein N = 3, that is, Therefore, the calculated value of Z k is correct.

[0065] Determine the number of teeth Z9 of the high-speed planetary transmission inner gear of the vertical planetary gear reducer.

[0066] Wherein, recommended Z3=Z8>15, Z3=Z8 can take the value of 17, according to Z3=Z8, Z k =Z9+Z8, that is, the high-speed level of the vertical planetary gear reducer planet transmission inner gear teeth Z9=115 can be calculated out;

[0067] Determine the low-speed level of the parallel planetary gear reducer planet transmission gear teeth;

[0068] Wherein, recommended Z5>15, Z5 can take the value of 18, the low-speed level of the planetary gear transmission ratio i3=5, according to That is, the parallel planetary gear reducer inner gear teeth Z6=(5-1)×18=72 can be calculated out; At the same time, the sum of the parallel planetary gear reducer inner gear teeth Z6 and the parallel planetary gear reducer sun gear teeth Z5 can be divided by the number of planetary gears M of the low-speed level of the parallel planetary gear reducer; Wherein, M=3, that is, Therefore, the calculated value of Z6+Z5 is correct;

[0069] According to the determined gear teeth of the parallel planetary gear reducer and the gear teeth of the vertical planetary gear reducer, the total transmission ratio of the parallel planetary gear reducer and the vertical planetary gear reducer is calculated;

[0070] Therefore, the total transmission ratio of the parallel planetary gear reducer is

[0071]

[0072] The total transmission ratio of the vertical planetary gear reducer is

[0073]

[0074] From the above calculation, i 平 = i 垂 .

[0075] If the required transmission ratio value range is not reached, the number of small cylindrical gear teeth Z3 of the second stage transmission pair of the parallel planetary gear reducer and the number of high-speed level sun gear teeth Z8 of the vertical planetary gear reducer need to be increased at the same time.

[0076] If the required transmission ratio value range is not reached, the number of small cylindrical gear teeth Z3 of the second stage transmission pair of the parallel planetary gear reducer and the number of high-speed level sun gear teeth Z8 of the vertical planetary gear reducer need to be reduced at the same time.

[0077] If the required transmission ratio value range is not reached, the values of K1 and K2 need to be adjusted, and Z k .

[0078] If the required transmission ratio range is not reached, the tooth number Z6 of the inner gear of the parallel planetary gear reducer and the tooth number Z5 of the sun gear of the parallel planetary gear reducer are required.

[0079] Embodiment 2:

[0080] The application provides a parallel and vertical reducer output rotation speed zero rotation difference design method for a scraper conveyor, comprising the following steps,

[0081] S1: determining the transmission ratio i of the parallel planetary gear reducer 平 , the transmission ratio i of the parallel planetary gear reducer 平 is calculated according to the following formula,

[0082] That is, i 平 = i1x i2x i3 (1) ;

[0083] Wherein, i1 is the transmission ratio of the first stage bevel gear; Z2 is the tooth number of the bevel gear of the parallel planetary gear reducer, and Z1 is the tooth number of the bevel gear of the parallel planetary gear reducer;

[0084] i2 is the transmission ratio of the second stage bevel gear, that is, Z4 is the tooth number of the large cylindrical gear of the parallel planetary gear reducer, and Z3 is the tooth number of the small cylindrical gear of the parallel planetary gear reducer;

[0085] i3 is the transmission ratio of the low-speed stage planetary gear, that is, Z6 is the tooth number of the inner gear of the parallel planetary gear reducer, and Z5 is the tooth number of the sun gear of the parallel planetary gear reducer;

[0086] S2: determining the transmission ratio i of the vertical planetary gear reducer 垂 , the transmission ratio i of the low-speed stage planetary gear of the vertical reducer is set to be the same as the transmission ratio of the low-speed stage planetary gear of the parallel reducer, so that the transmission ratio i of the vertical planetary gear reducer 垂 is calculated according to the following formula,

[0087] That is, i 垂 = i4x i3 (2) ;

[0088] Wherein, i4 is the transmission ratio of the high-speed stage planetary gear of the vertical reducer;

[0089] S3: setting the transmission ratio of the parallel planetary gear reducer and the transmission ratio of the vertical planetary gear reducer to be equal, and the output rotation speed zero rotation difference, so that i 平 = i 垂 ,

[0090] That is, i 平 = i1x i2x i3 = i 垂 = i4x i3 (3) ;

[0091] Thus, it can be concluded that the relationship between the high-speed planetary gear transmission ratio i4 of the vertical planetary gear reducer, the first-stage bevel gear transmission ratio i1, and the second-stage bevel gear transmission ratio i2 is

[0092] That is, i4 = i1 x i2 (4);

[0093] Wherein, Z9 is the number of teeth of the high-speed planetary transmission inner gear of the vertical planetary gear reducer, and Z8 is the number of teeth of the sun gear of the high-speed planetary transmission of the vertical planetary gear reducer;

[0094] Substituting the corresponding calculation formulas of i1, i2, and i4 into formula (4), the following formula can be obtained,

[0095]

[0096] Wherein, Z k = Z9 + Z8, that is, Z k is the sum of the number of teeth of the high-speed planetary transmission inner gear of the vertical planetary gear reducer and the number of teeth of the sun gear of the high-speed planetary transmission of the vertical planetary gear reducer;

[0097] S4: Determine the number of teeth of each transmission gear pair;

[0098] It is assumed that the number of teeth Z3 of the small cylindrical gear of the second-stage transmission pair of the parallel planetary gear reducer is equal to the number of teeth Z8 of the high-speed sun gear of the high-speed planetary transmission pair of the vertical planetary gear reducer, that is, Z3 = Z8. The relationship between the number of teeth of each gear pair of the parallel planetary gear reducer and the vertical planetary gear reducer can be determined by formula (5),

[0099] That is, Further changes can be made,

[0100] According to the power and the initially selected transmission ratio, the number of teeth Z2 of the bevel gear of the parallel planetary gear reducer and the number of teeth Z1 of the bevel gear of the parallel planetary gear reducer in the first-stage bevel gear transmission gear pair of the parallel planetary gear reducer are determined; wherein Z2 is 33, and Z1 is 13;

[0101] According to formula (6), Z4 is 4 x 13 = 52, wherein K2 is 4; At the same time, it is verified that Z k can be divided by the number N of planetary gears of the high-speed planetary transmission of the vertical planetary gear reducer; wherein N = 3; that is, Therefore, it can be known that the calculated value of Z k is correct;

[0102] Determine the number of teeth Z9 of the high-speed planetary transmission inner gear of the vertical planetary gear reducer;

[0103] Wherein, recommended Z3=Z8>15, Z3=Z8 take value 17, according to Z3=Z8, Z k =Z9+Z8, that is, the number of teeth Z9 of the high-speed stage planetary transmission inner gear of the vertical planetary gear reducer can be calculated; Z9=132-17=115;

[0104] Determine the number of teeth of the low-speed stage planetary gear of the parallel planetary gear reducer;

[0105] Wherein, recommended Z5>15, Z5 can take value 18, the low-speed stage planetary gear transmission ratio i3=5, according to That is, the number of teeth Z6 of the inner gear of the parallel planetary gear reducer can be calculated as Z6=(5-1)×18=72; at the same time, it is verified that the sum of the number of teeth Z6 of the inner gear of the parallel planetary gear reducer and the number of teeth Z5 of the sun gear of the parallel planetary gear reducer can be divided by the number of planetary gears M of the low-speed stage planetary transmission of the parallel planetary gear reducer; wherein, M=3, that is, Therefore, the calculated value of Z6+Z5 is correct;

[0106] According to the determined number of teeth of each gear of the parallel planetary gear reducer and the number of teeth of each gear of the vertical planetary gear reducer, the total transmission ratio of the parallel planetary gear reducer and the vertical planetary gear reducer is calculated;

[0107] Therefore, the total transmission ratio of the parallel planetary gear reducer is

[0108]

[0109] The total transmission ratio of the vertical planetary gear reducer is

[0110]

[0111] From the above calculation, i 平 = i 垂 .

[0112] If the required transmission ratio value range is not reached, the number of teeth of the small cylindrical gear Z3 of the second stage transmission pair of the parallel planetary gear reducer and the number of teeth of the high-speed stage sun gear Z8 of the vertical planetary gear reducer need to be increased at the same time.

[0113] If the required transmission ratio value range is not reached, the number of teeth of the small cylindrical gear Z3 of the second stage transmission pair of the parallel planetary gear reducer and the number of teeth of the high-speed stage sun gear Z8 of the vertical planetary gear reducer need to be reduced at the same time.

[0114] If the required transmission ratio value range is not reached, the values of K1 and K2 need to be adjusted, and Z k .

[0115] If the required transmission ratio range is not reached, the number of teeth Z6 of the internal gear of the parallel-axle gear reducer and the number of teeth Z5 of the sun gear of the parallel-axle gear reducer are required.

[0116] The above disclosure is only the preferred embodiment of the present application, of course, cannot be limited by this, the person skilled in the art can understand that the whole or part of the above-mentioned embodiment is realized, and the equivalent change made according to the claims of the present application still belongs to the scope covered by the present application.

Claims

1. A parallel and vertical reducer output speed zero rotation difference design method for a flight conveyor, characterized in that: The steps include: S1: determining the transmission ratio i of the parallel planetary gear reducer 平 , the transmission ratio i of the parallel planetary gear reducer 平 is calculated according to the following formula, i.e. i 平 = i1x i2x i3(1); Wherein, i1 is the first bevel gear transmission ratio; Z2 is the bevel gear tooth number of the parallel planetary gear reducer, and Z1 is the bevel gear tooth number of the parallel planetary gear reducer. i2 is the second stage bevel gear transmission ratio, i.e. Z4 is the number of gear teeth of the large cylindrical gear of the parallel planetary gear reducer, and Z3 is the number of gear teeth of the small cylindrical gear of the parallel planetary gear reducer. i3 is a low-speed planetary gear transmission ratio, i.e. Z6 is the number of gear teeth of the internal gear of the parallel planetary gear reducer, and Z5 is the number of gear teeth of the sun gear of the parallel planetary gear reducer. S2: Determine the transmission ratio i of the vertical planetary gear reducer 垂 The parameters of each gear in the low-speed stage planetary gear transmission of the vertical reducer are set to be the same as the number of teeth of each gear in the low-speed stage planetary gear transmission of the parallel reducer. Therefore, the transmission ratio i of the vertical planetary gear reducer is... 垂 Calculate according to the following formula. i.e. i 垂 = i4x i3(2); Wherein, i4 is the high-speed planetary gear ratio of the vertical planetary gear reducer; S3: Set the parallel planetary gear reducer, vertical planetary gear reducer transmission ratio is equal, the output speed zero rotation difference, can be derived i 平 = i 垂 , i.e. i 平 = i1× i2× i3= i 垂 = i4× i3(3); From which, the relationship between the high-speed planetary gear ratio i4, the first-stage bevel gear ratio i1, and the second-stage bevel gear ratio i2 of the vertical planetary gear reducer can be derived, That is, i4 = i1 x i2 (4); wherein, Z9 is the number of teeth of the inner gear of the high-speed stage planetary transmission of the vertical planetary gear reducer, and Z8 is the number of teeth of the sun gear of the high-speed stage of the vertical planetary gear reducer. By substituting the corresponding calculation formulas of i1, i2, and i4 into formula (4), the following formula can be obtained, wherein Z is set k = Z9+ Z8, i.e. Z k is the sum of the number of teeth of the inner gear of the planetary transmission of the high speed stage of the vertical planetary gear reducer and the number of teeth of the sun gear of the high speed stage of the vertical planetary gear reducer; S4: Determine the gear tooth number of each stage transmission gear pair; ①, Set the cylindrical gear tooth number Z3 of the second-stage transmission pair of the parallel planetary gear reducer equal to the high-speed sun gear tooth number Z8 of the high-speed planetary transmission pair of the vertical planetary gear reducer, that is, Z3 = Z8, and the relationship between the gear tooth numbers of each gear pair of the parallel planetary gear reducer and the vertical planetary gear reducer can be determined by formula (5), That is Further variations are available, ②, According to the power and the primary selected transmission ratio, determine the bevel gear tooth number Z2 of the parallel planetary gear reducer and the bevel gear tooth number Z1 of the parallel planetary gear reducer in the first-stage bevel gear transmission pair of the parallel planetary gear reducer; ③、According to formula (6), if Z1 is an odd number, Z4 takes the value of Z4=K1*Z1, wherein K1 takes an integer, and Z4 can be calculated k ; at the same time, Z k can be divided by the number of planetary gears N of the high-speed planetary transmission of the vertical planetary gear reducer. ④、According to formula (6), if Z1 is even, Z4 takes the value of Z4=K2*Z1, wherein K2 is a multiple of the greatest common divisor of Z1, and Z4 can be calculated k ; at the same time, Z k can be divided by the number of planetary gears N of the high-speed planetary transmission of the vertical planetary gear reducer. ⑤, Determine the high-speed planetary transmission inner gear tooth number Z9 of the vertical planetary gear reducer; Wherein, the recommended Z3=Z8>15, according to Z3=Z8, Z k =Z9+Z8, the high-speed planetary gear reducer vertical planetary transmission inner gear teeth Z9 can be calculated; ⑥, Determine the low-speed planetary transmission gear tooth number of the parallel planetary gear reducer; Wherein, the recommended Z5>15, the low-speed stage planetary gear transmission ratio i3=5, according to The number of teeth Z6 of the internal gear of the parallel planetary gear reducer can be calculated; the sum of the number of teeth Z6 of the internal gear of the parallel planetary gear reducer and the number of teeth Z5 of the sun gear of the parallel planetary gear reducer can be divided by the number of planetary gears M of the low-speed stage planetary transmission of the parallel planetary gear reducer. ⑦, According to the determined gear tooth numbers of the parallel planetary gear reducer and the gear tooth numbers of the vertical planetary gear reducer, calculate the total transmission ratio of the parallel planetary gear reducer and the vertical planetary gear reducer.

2. The parallel and vertical reducer output rotation speed zero rotation difference design method for a scraper conveyor according to claim 1, characterized in that: In step S4, if the required transmission ratio range is not reached, the tooth numbers of the cylindrical gear tooth number Z3 of the second-stage transmission pair of the parallel planetary gear reducer and the high-speed sun gear tooth number Z8 of the vertical planetary gear reducer need to be increased simultaneously.

3. The parallel and vertical reducer output rotation speed zero rotation difference design method for a scraper conveyor according to claim 1, characterized in that: In step S4, if the required transmission ratio range is not reached, the tooth numbers of the cylindrical gear tooth number Z3 of the second-stage transmission pair of the parallel planetary gear reducer and the high-speed sun gear tooth number Z8 of the vertical planetary gear reducer need to be reduced simultaneously.

4. The parallel and vertical reducer output rotation speed zero rotation difference design method for a scraper conveyor according to claim 1, characterized in that: If the required range of transmission ratio values is not reached in step S4, the values of K1 and K2 are adjusted and Z is recalculated k .

5. The parallel and vertical reducer output speed zero rotation difference design method for a scraper conveyor according to claim 1, characterized in that: In step S4, if the required transmission ratio range is not reached, the tooth numbers of the cylindrical gear tooth number Z3 of the second-stage transmission pair of the parallel planetary gear reducer and the high-speed sun gear tooth number Z8 of the vertical planetary gear reducer need to be increased simultaneously.

6. The parallel and vertical reducer output speed zero rotation difference design method for a scraper conveyor according to claim 1, characterized in that: In step S4, the high-speed planetary transmission of the vertical planetary gear reducer is three planetary gear transmission, that is, N = 3.

7. The parallel and vertical reducer output speed zero rotation difference design method for a scraper conveyor according to claim 1, characterized in that: In step S4, the low-speed planetary transmission of the parallel planetary gear reducer is three planetary gear transmission, that is, M = 3.

8. The parallel and vertical reducer output speed zero rotation difference design method for a scraper conveyor according to claim 1, characterized in that: In step S4, the low-speed planetary transmission of the parallel planetary gear reducer is four planetary gear transmission, that is, M = 4.

Images