阅读说明：本技术 变位混合锥齿差速减速法 (Variable-position mixed bevel gear differential speed reduction method ) 是由 赵晓东 于 2020-12-17 设计创作，主要内容包括：本发明是一种变位混合锥齿差速减速法,其涉及一种减速方法,所述减速法采用通用部件分别与对比侧混合锥齿轮部件、对比侧变位混合锥齿轮部件、对比侧变位直连锥齿轮部件组合成混合锥齿差速减速器、变位混合锥齿差速减速器、变位直连锥齿差速减速器,三种减速器的传动比范围不同,所述减速法采用改变锥齿轮分度圆锥角使一个锥齿轮能够分别与两个齿数不相等的锥齿轮啮合,利用两个齿数不相等锥齿轮之间的轴线偏心距离调节减速器内齿轮与外齿轮之间的啮合偏心距离,实现增加减速器传动比范围、相同规格的产品仅需更换部分零部件即能改变传动比的功能。(The invention discloses a deflection mixed bevel differential speed reduction method, which relates to a speed reduction method, wherein a general component is adopted in the speed reduction method to be respectively combined with a comparison side mixed bevel gear component, a comparison side deflection mixed bevel gear component and a comparison side deflection direct connection bevel gear component to form a mixed bevel differential speed reducer, a deflection mixed bevel differential speed reducer and a deflection direct connection bevel differential speed reducer, the transmission ratio ranges of the three speed reducers are different, the speed reduction method adopts the mode of changing the indexing conical angle of a bevel gear to enable one bevel gear to be respectively meshed with two bevel gears with unequal tooth numbers, the meshing eccentric distance between an inner gear and an outer gear of the speed reducer is adjusted by utilizing the axis eccentric distance between the two bevel gears with unequal tooth numbers, and the functions of increasing the transmission ratio range of the speed reducer and changing the transmission ratio of products with the same specification.)

1. A differential speed reduction method of a modified hybrid bevel gear comprises a fixed cylinder component, a planet carrier component, a reference side hybrid bevel gear component and a comparison side hybrid bevel gear component; the fixed cylinder component comprises a fixed cylinder (27), a direction-changing bevel gear (22), a bearing gland (23), a spline I (24), an input shaft I (25) and a bearing V (26), the planet support component comprises an output shaft (17), a planet support (37), a planet shaft (38), a shaft sleeve III (39) and a planet bevel gear (40), the reference side mixed bevel gear component comprises a bearing III (28), an end cover I (29), a spline II (30), an input shaft II (31), an input gear II (32), a bearing I (33), a shaft sleeve I (34), a mixed bevel gear I (35) and a mixed bevel gear III (36), the comparison side mixed bevel gear component comprises a mixed bevel gear IV (14), a mixed bevel gear II (15), a bearing II (16), a shaft sleeve II (18), an end cover II (20) and a bearing IV (21), the planet support component is arranged in an inner cavity of the fixed, the reference side hybrid bevel gear component is arranged at the right end of the fixed cylinder component in the axial direction and comprises a fixed cylinder component, a planet support component and a reference side hybrid bevel gear component which form a general component, the comparison side hybrid bevel gear component is arranged at the left end of the fixed cylinder component in the axial direction and comprises a hybrid bevel gear differential speed reducer and a comparison side hybrid bevel gear component; the method is characterized in that: the deceleration method also comprises a contrast side modified hybrid bevel gear component and a contrast side modified direct-connected bevel gear component; the contrast side deflection mixing bevel gear component comprises a deflection mixing bevel gear (47), a mixing bevel gear five (48), a bearing six (49), a shaft sleeve four (50), an end cover three (51), a bearing seven (52) and an eccentric ring one (53), is arranged at the left end of the fixed cylinder component, and consists of a universal component and a contrast side deflection mixing bevel gear component to form a deflection mixing bevel gear differential speed reducer; the contrast side modified direct bevel gear component comprises a modified direct bevel gear (55), a direct bevel gear (56), a bearing eight (57), a shaft sleeve five (58), an end cover four (59), a bearing nine (60) and an eccentric ring two (61), and is arranged at the left end of the fixed cylinder component, and the modified direct bevel gear differential speed reducer consists of a general component and a contrast side modified direct bevel gear component; the speed reduction method adopts the steps that the indexing conical angle of a bevel gear is changed to enable one bevel gear to be meshed with two bevel gears with different tooth numbers respectively, the axis eccentric distance between the two bevel gears with different tooth numbers is utilized to adjust the meshing eccentric distance between an inner gear and an outer gear of the speed reducer, and the transmission ratio range of the speed reducer is enlarged;

a third mixing bevel gear (36) of the mixing bevel gear differential speed reducer is arranged in a right section (44) of an inner cavity of a fixed cylinder (27) through a third bearing (28), a fourth mixing bevel gear (14) is arranged in a left section (42) of the inner cavity of the fixed cylinder (27) through a fourth bearing (21), the third mixing bevel gear (36) and the fourth mixing bevel gear (14) are coaxial with the inner cavity of the fixed cylinder (27), a middle section (43) of the inner cavity of the fixed cylinder (27) is provided with a fixed platform shaft hole vertical to the axis (67) of the fixed cylinder, a direction-changing bevel gear (22) is arranged in the fixed platform shaft hole on the radial inner side of the fixed cylinder (27) through a fifth bearing (26), a bearing gland (23) is arranged in the fixed platform shaft hole on the radial outer side of the fixed cylinder (27), a first input shaft (25) is connected with the direction-changing bevel gear (22) through a first key strip (24), a first mixing bevel gear (35), a first mixing bevel gear (35) is installed on the radial outer side, close to the right end, of an output shaft (17) through a first shaft sleeve (34), the journal of the right end of the output shaft (17) is installed in a first bearing hole of a first end cover (29) through a first bearing (33), a second mixing bevel gear (15) is installed on the radial outer side, close to the left end, of the output shaft (17) through a second shaft sleeve (18), the journal of the left end of the output shaft (17) is installed in a second bearing hole of a second end cover (20) through a second bearing (16), the shaft head of the left end of the output shaft (17) penetrates through the second bearing hole and is located on the axial outer side of the second end cover (20), and a; the planet carrier (37) is annular, a plurality of carrier mounting planes are uniformly distributed on the radial inner surface of the planet carrier (37), a carrier fixing shaft hole is arranged at the center of each carrier mounting plane, a plurality of planet bevel gears (40) are arranged in the inner cavity of the planet carrier (37), the planet shaft (38) passes through a third shaft sleeve (39) at the radial inner side of the planet bevel gear (40), one end of the planet shaft (38) is arranged in a bracket fixing shaft hole of the planet bracket (37), the other end of the planet shaft (38) is arranged in a fixed shaft hole of the output shaft (17) to enable the planet bevel gears (40) to rotate around the planet shaft axis (70), when the number of the planet bevel gears (40) is less than three, the planet carrier component also comprises at least one positioning pin (19), one end of the positioning pin (19) is arranged in a carrier fixing shaft hole of the planet carrier (37), the other end of the positioning pin (19) is arranged in a fixing shaft hole of the output shaft (17);

the first mixing bevel gear (35), the second mixing bevel gear (15), the third mixing bevel gear (36) and the fourth mixing bevel gear (14) are respectively provided with a cylindrical gear tooth and a conical gear tooth, the cylindrical gear teeth and the conical gear teeth are coaxial, the inner side gear teeth of the first mixing bevel gear (35) are conical gear teeth, the outer side gear teeth of the first mixing bevel gear (35) are cylindrical gear teeth, the inner side gear teeth of the second mixing bevel gear (15) are conical gear teeth, the outer side gear teeth of the second mixing bevel gear (15) are cylindrical gear teeth, the inner side gear teeth of the third mixing bevel gear (36) are cylindrical gear teeth, and the third gear tooth on the inner side is an internal gear, the third gear tooth on the outer side of the third mixing bevel gear (36) is a conical gear tooth, the fourth gear tooth on the inner side of the fourth mixing bevel gear (14) is a cylindrical gear tooth, the fourth gear tooth on the inner side is an internal gear, and the fourth gear tooth on the outer side of the fourth mixing bevel gear (14) is a conical gear tooth;

the number of the outer side gear teeth of the fourth mixing bevel gear (14) is equal to the number of the outer side gear teeth of the third mixing bevel gear (36), the number of the inner side gear teeth of the second mixing bevel gear (15) is equal to the number of the inner side gear teeth of the first mixing bevel gear (35), the direction-changing bevel gear (22) is respectively meshed with the outer side gear teeth of the fourth mixing bevel gear (14) and the outer side gear teeth of the third mixing bevel gear (36), and the planetary bevel gear (40) is respectively meshed with the inner side gear teeth of the second mixing bevel gear (15) and the inner side gear teeth of the first mixing bevel gear (35);

the number of the second outer gear teeth of the second mixing bevel gear (15) and the number of the first outer gear teeth of the first mixing bevel gear (35) are in a small gear difference corresponding relationship, the difference between the number of the second outer gear teeth and the number of the first outer gear teeth is defined as a small gear difference I, the number of the fourth inner gear teeth of the fourth mixing bevel gear (14) and the number of the third inner gear teeth of the third mixing bevel gear (36) are in a small gear difference corresponding relationship, the difference between the number of the fourth inner gear teeth and the number of the third inner gear teeth is defined as a small gear difference II, the first outer gear teeth of the first mixing bevel gear (35) are meshed with the third inner gear teeth of the third mixing bevel gear (36), a first meshing eccentric distance is reserved between the axis of the first mixing bevel gear (35) and the axis of the third mixing bevel gear (36), the second outer gear teeth of the second mixing bevel gear (15) are meshed with the fourth inner gear teeth of the fourth mixing bevel gear (;

the modulus of the first outer gear tooth of the first mixing bevel gear (35) and the modulus of the third inner gear tooth of the third mixing bevel gear (36) are a modulus one, the difference between the number of the third inner gear tooth of the third mixing bevel gear (36) and the number of the first outer gear tooth of the first mixing bevel gear (35) is defined as an eccentric distance tooth difference one, and the meshing eccentric distance one is equal to half of the product of the eccentric distance tooth difference one and the modulus one; the modulus of the outer gear teeth II of the second mixing bevel gear (15) and the modulus of the inner gear teeth IV of the fourth mixing bevel gear (14) are a modulus II, the difference between the number of the teeth of the inner gear teeth IV of the fourth mixing bevel gear (14) and the number of the teeth of the outer gear teeth II of the second mixing bevel gear (15) is defined as an eccentric distance gear difference II, and the meshing eccentric distance II is equal to half of the product of the eccentric distance gear difference II and the modulus II;

if the axis of the first mixing bevel gear (35) is arranged below the axis of the third mixing bevel gear (36) and the axis of the second mixing bevel gear (15) is arranged below the axis of the fourth mixing bevel gear (14), the meshing eccentric distance II of the comparison side mixing bevel gear component is equal to the meshing eccentric distance I of the reference side mixing bevel gear component, and the meshing eccentric distance II is equal to the eccentric distance between the axis (68) of the output shaft and the axis (67) of the fixed cylinder, the assembly condition that the first mixing bevel gear (35), the second mixing bevel gear (15) and the output shaft (17) are coaxial is met;

the input gear II (32) is connected with the input shaft II (31) through a key strip II (30), the input gear II (32) is cylindrical gear teeth, the input gear II (32) is meshed with the gear teeth III on the inner side of the mixing bevel gear III (36), the shaft head at the right end of the input shaft II (31) penetrates through the input shaft hole of the end cover I (29) and is positioned on the axial outer side of the end cover I (29), and the axis of the input shaft II (31) is parallel to the axis (68) of the output shaft;

when the hybrid bevel gear differential speed reducer operates, the first input shaft (25) is driven by the prime motor to rotate or the second input shaft (31) is driven by the prime motor to rotate, if the first input shaft (25) is driven by the prime motor to rotate along the rotation direction (63) of the direction-changing bevel gear, the first input shaft (25) respectively drives the third hybrid bevel gear (36) and the fourth hybrid bevel gear (14) to rotate through the direction-changing bevel gear (22), the fourth hybrid bevel gear rotation direction (46) is opposite to the third hybrid bevel gear rotation direction (66), the rotation speed of the fourth hybrid bevel gear (14) is equal to that of the third hybrid bevel gear (36), the third hybrid bevel gear (36) drives the first hybrid bevel gear (35) to rotate in the same direction, the fourth hybrid bevel gear (14) drives the second hybrid bevel gear (15) to rotate in the same direction, and the second hybrid bevel gear rotation direction (76) is opposite to that of the first, the factors of the small tooth difference I and the small tooth difference II enable the rotating speed of the second mixing bevel gear (15) to be unequal to the rotating speed of the first mixing bevel gear (35), and the difference between the rotational speed of the second mixing bevel gear (15) and the rotational speed of the first mixing bevel gear (35) is small, the second mixing bevel gear (15) and the first mixing bevel gear (35) drive the planetary bevel gear (40) to rotate together, the planetary bevel gear (40) rotates around the planetary shaft axis (70), the planet bevel gear (40) also revolves around the axis (68) of the output shaft, the planet bevel gear (40) drives the planet support (37) to rotate at a low speed, the rotation speed of the planet support (37) is equal to half of the difference between the rotation speed of the second mixing bevel gear (15) and the rotation speed of the first mixing bevel gear (35), and the planet support (37) drives the output shaft (17) to rotate at a low speed in the same direction through the planet shaft (38);

on the premise that the meshing eccentric distance II of the comparison side hybrid bevel gear component is equal to the meshing eccentric distance I of the reference side hybrid bevel gear component, changing the eccentric distance tooth difference II and the module II or changing the eccentric distance tooth difference I and the module I can change the difference between the rotating speed of the hybrid bevel gear II (15) and the rotating speed of the hybrid bevel gear I (35), and finally changing the transmission ratio of the hybrid bevel gear differential speed reducer;

a contrast side mixed bevel gear component in the mixed bevel gear differential speed reducer is replaced by a contrast side mixed bevel gear component to form a modified mixed bevel gear differential speed reducer; the deflection mixing bevel gear (47) is installed in the inner cavity of a first eccentric ring (53) through a seventh bearing (52), the first eccentric ring (53) is installed in the left section (42) of the inner cavity of the fixed cylinder (27), one end of a fixed pin (54) is installed in a first fixed pin hole (41) of the fixed cylinder (27), the other end of the fixed pin (54) is installed in a second fixed pin hole (78) of the first eccentric ring (53), the deflection mixing bevel gear (47) is not coaxial with the inner cavity of the fixed cylinder (27), a fifth mixing bevel gear (48) is installed on the radial outer side, close to the left end, of the output shaft (17) through a fourth shaft sleeve (50), a left end shaft neck of the output shaft (17) is installed in a third bearing hole of a third end cover (51) through a sixth bearing (49), and a left end shaft head of the output shaft (17) penetrates through the third;

the fifth mixing bevel gear (48) and the sixth shifting mixing bevel gear (47) are respectively provided with a cylindrical gear tooth and a conical gear tooth, the cylindrical gear tooth and the conical gear tooth are coaxial, the fifth inner gear tooth of the fifth mixing bevel gear (48) is a conical gear tooth, the fifth outer gear tooth of the fifth mixing bevel gear (48) is a cylindrical gear tooth, the sixth inner gear tooth of the fifth shifting mixing bevel gear (47) is a cylindrical gear tooth, the sixth inner gear tooth is an internal gear, and the sixth outer gear tooth of the sixth shifting mixing bevel gear (47) is a conical gear tooth;

the six teeth of the outer teeth of the deflection mixing bevel gear (47) are not equal to the three teeth of the outer teeth of the mixing bevel gear III (36), the direction-changing bevel gear (22) is respectively meshed with the six teeth of the outer teeth of the deflection mixing bevel gear (47) and the three teeth of the outer teeth of the mixing bevel gear III (36), and the indexing cone angle of the direction-changing bevel gear (22) and the three indexing cone angle of the outer teeth of the mixing bevel gear III (36) are valued according to a method specified by a bevel gear standard, so that the six indexing cone angle of the outer teeth of the deflection mixing bevel gear (47) is equal to the three indexing cone angle of the outer teeth of the mixing bevel; if the six teeth of the outer gear teeth of the deflection mixing bevel gear (47) are smaller than the three teeth of the outer gear teeth of the mixing bevel gear III (36), the axis of the deflection mixing bevel gear (47) is arranged on the upper side of the axis of the mixing bevel gear III (36);

the modulus of the outer gear teeth III of the direction-changing bevel gear (22) and the mixing bevel gear III (36) and the modulus of the outer gear teeth six of the deflection mixing bevel gear (47) are modulus III, the difference between the number of the outer gear teeth III of the mixing bevel gear III (36) and the number of the outer gear teeth six of the deflection mixing bevel gear (47) is defined as an eccentric distance gear difference III, and the axial eccentric distance III between the axial line of the mixing bevel gear III (36) and the axial line of the deflection mixing bevel gear (47) is equal to half of the product of the eccentric distance gear difference III and the modulus III;

the number of teeth of the inner side gear teeth five of the mixing bevel gear five (48) is equal to the number of teeth of the inner side gear teeth one of the mixing bevel gear I (35), and the planetary bevel gear (40) is meshed with the inner side gear teeth five of the mixing bevel gear five (48) and the inner side gear teeth one of the mixing bevel gear I (35) respectively; the difference between the six tooth numbers of the inner side gear teeth of the deflection mixing bevel gear (47) and the three tooth numbers of the inner side gear teeth of the mixing bevel gear III (36) is large, the six tooth numbers of the inner side gear teeth and the three tooth numbers of the inner side gear teeth are not in small tooth difference corresponding relation, the difference between the five tooth numbers of the outer side gear teeth of the mixing bevel gear V (48) and the one tooth number of the outer side gear teeth of the mixing bevel gear I (35) is large, and the five tooth numbers of the outer side gear teeth and the one tooth number of the outer;

the six inner gear teeth of the deflection mixing bevel gear (47) are meshed with the five outer gear teeth of the five mixing bevel gear (48), the modulus of the six inner gear teeth of the deflection mixing bevel gear (47) and the modulus of the five outer gear teeth of the five mixing bevel gear (48) are four, the difference between the six inner gear teeth of the deflection mixing bevel gear (47) and the five outer gear teeth of the five mixing bevel gear (48) is defined as an eccentric distance tooth difference of four, a meshing eccentric distance of three is arranged between the axis of the five mixing bevel gear (48) and the axis of the deflection mixing bevel gear (47), and the meshing eccentric distance of three is equal to half of the product of the four eccentric distance tooth difference and the four modulus;

if the meshing eccentric distance III is larger than the meshing eccentric distance I, the axis of a fifth mixing bevel gear (48) is arranged on the lower side of the axis of the third mixing bevel gear (36), the difference between the meshing eccentric distance III and the axis eccentric distance III is the comprehensive eccentric distance III of the reference side displacement mixing bevel gear part, the comprehensive eccentric distance III is equal to the meshing eccentric distance I of the reference side mixing bevel gear part, the comprehensive eccentric distance III is equal to the eccentric distance between the axis (68) of the output shaft and the axis (67) of the fixed cylinder, and the assembly conditions that the first mixing bevel gear (35), the fifth mixing bevel gear (48) and the output shaft (17) are coaxial are met;

when the modified hybrid bevel differential speed reducer operates, if the same rotating speed is input into the modified hybrid bevel differential speed reducer and the hybrid bevel differential speed reducer through the input shaft I (25), in the hybrid bevel differential speed reducer, the number of four outer gear teeth of the hybrid bevel gear II (14) is equal to the number of three outer gear teeth of the hybrid bevel gear III (36), the rotating speed of the hybrid bevel gear II (14) is equal to the rotating speed of the hybrid bevel gear III (36), and the difference between the rotating speed of the hybrid bevel gear II (15) and the rotating speed of the hybrid bevel gear I (35) is small due to the corresponding relation of the small gear difference I and the small gear difference II, so the transmission ratio of the hybrid bevel differential speed reducer is large; in the differential speed reducer with the modified mixing bevel gears, six teeth on the outer side of a modified mixing bevel gear (47) are less than three teeth on the outer side of a mixing bevel gear (36), the rotating speed of the modified bevel gear (47) is larger than that of the bevel gear three (36), the torque is accelerated from the modified bevel gear (47) to the bevel gear five (48), the meshing eccentric distance three is larger than the meshing eccentric distance one, if the modulus four is equal to the modulus one, the eccentric distance tooth difference four is larger than the eccentric distance tooth difference one, the transmission ratio between the deflection mixing bevel gear (47) and the mixing bevel gear five (48) is smaller than the transmission ratio between the mixing bevel gear three (36) and the mixing bevel gear one (35), the difference between the rotating speed of the mixing bevel gear five (48) and the rotating speed of the mixing bevel gear one (35) is large, and therefore the transmission ratio of the deflection mixing bevel gear differential speed reducer is small;

on the premise that the comprehensive eccentric distance III of the comparison side deflection bevel gear component is equal to the meshing eccentric distance I of the reference side bevel gear component, changing the eccentric distance tooth difference III and the module III, or changing the eccentric distance tooth difference IV and the module IV, or changing the eccentric distance tooth difference I and the module I, the difference between the rotating speed of the bevel gear V (48) and the rotating speed of the bevel gear I (35) can be changed, and finally the transmission ratio of the deflection bevel gear differential speed reducer is changed;

the method comprises the following steps that a contrast side modified direct bevel gear component replaces a contrast side mixed bevel gear component in a mixed bevel gear differential speed reducer to form a modified direct bevel gear differential speed reducer, the installation angles of a planet support component and a reference side mixed bevel gear component in the modified direct bevel gear differential speed reducer rotate one hundred eighty degrees along the axis (67) of a fixed cylinder, and the axis of a first mixed bevel gear (35) of the modified direct bevel gear differential speed reducer is arranged on the upper side of the axis of a third mixed bevel gear (36); the deflection direct-connection bevel gear (55) is installed in the inner cavity of the eccentric ring II (61) through a bearing nine (60), the eccentric ring II (61) is installed in the left section (42) of the inner cavity of the fixed cylinder (27), one end of the fixed pin (54) is installed in a fixed pin hole I (41) of the fixed cylinder (27), the other end of the fixed pin (54) is installed in a fixed pin hole II (78) of the eccentric ring II (61), the deflection direct-connection bevel gear (55) is not coaxial with the inner cavity of the fixed cylinder (27), the direct-connection bevel gear (56) is installed on the radial outer side, close to the left end, of the output shaft (17) through a shaft sleeve five (58), a shaft neck at the left end of the output shaft (17) is installed in a bearing hole IV of an end cover IV (59) through a bearing eight (57), and a shaft head at the left end of;

an inner side gear tooth seventh at one end of the axial inner side of the direct-connection bevel gear (56) is a conical gear tooth, the other end of the axial direction of the direct-connection bevel gear (56) is an external spline, the inner side gear tooth seventh is coaxial with the external spline, an outer side gear tooth eighth at the radial outer side of the modified direct-connection bevel gear (55) is a conical gear tooth, the radial inner side of the modified direct-connection bevel gear (55) is an internal spline, and the outer side gear tooth eighth is coaxial;

the eight teeth of the outer side teeth of the modified direct-connection bevel gear (55) are not equal to the three teeth of the outer side teeth of the mixed bevel gear III (36), the direction-changing bevel gear (22) is respectively meshed with the eight teeth of the outer side teeth of the modified direct-connection bevel gear (55) and the three teeth of the outer side teeth of the mixed bevel gear III (36), and the indexing cone angle of the direction-changing bevel gear (22) and the three indexing cone angle of the outer side teeth of the mixed bevel gear III (36) are valued according to a method specified by a bevel gear standard, so that the eight indexing cone angle of the outer side teeth of the modified direct-connection bevel gear (55) is equal to the; if the eight outer gear teeth of the modified direct-connected bevel gear (55) are less than the three outer gear teeth of the mixed bevel gear III (36), the axis of the modified direct-connected bevel gear (55) is arranged on the upper side of the axis of the mixed bevel gear III (36);

the modulus of the outer gear teeth III of the direction-changing bevel gear (22) and the mixed bevel gear III (36) and the modulus of the outer gear teeth eight of the position-shifted direct-connected bevel gear (55) are modulus III, the difference between the number of the outer gear teeth III of the mixed bevel gear III (36) and the number of the outer gear teeth eight of the position-shifted direct-connected bevel gear (55) is defined as an eccentric distance tooth difference V, and the eccentric distance IV of the axis between the axis of the mixed bevel gear III (36) and the axis of the position-shifted direct-connected bevel gear (55) is equal to half of the product of the eccentric;

the number of teeth of an inner side gear tooth seven of the direct connection bevel gear (56) is equal to the number of teeth of an inner side gear tooth one of the mixing bevel gear I (35), and the planetary bevel gear (40) is meshed with the inner side gear tooth seven of the direct connection bevel gear (56) and the inner side gear tooth one of the mixing bevel gear I (35) respectively; the outer spline of the direct-connected bevel gear (56) is arranged in the inner spline of the shifted direct-connected bevel gear (55), the direct-connected bevel gear (56) and the shifted direct-connected bevel gear (55) are coaxial, the comprehensive eccentric distance IV of a comparison side shifted direct-connected bevel gear component is equal to the axis eccentric distance IV, the comprehensive eccentric distance IV is equal to the meshing eccentric distance I of a reference side mixed bevel gear component, the comprehensive eccentric distance IV is equal to the eccentric distance between an output shaft axis (68) and a fixed cylinder axis (67), and the coaxial assembly conditions of the mixed bevel gear I (35), the direct-connected bevel gear (56) and an output shaft (17) are met;

when the modified direct-connection bevel gear differential speed reducer runs, if eight outer gear teeth of the modified direct-connection bevel gear (55) are less than three outer gear teeth of a mixed bevel gear III (36) in the modified direct-connection bevel gear differential speed reducer when the same rotating speed is input by the input shaft I (25) respectively, the rotating speed of the modified direct-connection bevel gear (55) is greater than the rotating speed of the mixed bevel gear III (36), the rotating speed of the direct-connection bevel gear (56) is equal to the rotating speed of the modified direct-connection bevel gear (55), so that the difference between the rotating speed of the direct-connection bevel gear (56) and the rotating speed of the mixed bevel gear I (35) is large, and because no accelerating transmission exists between the torque from the modified direct-connection bevel gear (55) to the direct-connection bevel gear (56), the rotating speed of the direct-connection bevel gear (56) of the modified direct-connection bevel gear differential speed reducer is, the transmission ratio of the modified direct-connected bevel differential speed reducer is between the mixed bevel differential speed reducer and the modified mixed bevel differential speed reducer;

on the premise that the comprehensive eccentric distance four of the comparison side modified direct-connection bevel gear component is equal to the meshing eccentric distance one of the reference side mixed bevel gear component, the eccentric distance tooth difference five and the module three are changed, or the eccentric distance tooth difference one and the module one are changed, the difference between the rotating speed of the direct-connection bevel gear (56) and the rotating speed of the mixed bevel gear one (35) can be changed, and finally the transmission ratio of the modified direct-connection bevel gear differential speed reducer is changed.

2. The differential speed reduction method of modified mixed bevel gear according to claim 1, characterized in that: in the mixed bevel gear differential reduction gear that shifts, in the direct bevel gear differential reduction gear that shifts, change bevel gear (22) is replaced respectively with cylindrical gear D (10), the outside teeth of a cogwheel three of the mixed bevel gear three (36) of general part and the outside teeth of a cogwheel four of mixed bevel gear four (14), the outside teeth of a cogwheel six of the mixed bevel gear that shifts (47) of the mixed bevel gear part that shifts of contrast side, the outside teeth of a cogwheel eight of the direct bevel gear that shifts (55) of the direct bevel gear part that shifts of contrast side are replaced by the terminal surface teeth by the conical teeth respectively, can realize the meshing of a cylindrical gear with two terminal surface gears that the number of teeth is unequal respectively, and constitute mixed bevel gear differential reduction gear of terminal surface respectively, terminal surface direct-connected bevel gear.

Technical Field

The invention discloses a differential speed reduction method for a modified mixed bevel gear, which relates to a speed reduction method, in particular to a method for increasing the transmission ratio range of a speed reducer by changing the indexing cone angle of a bevel gear to enable one bevel gear to be meshed with two bevel gears with different tooth numbers respectively and adjusting the meshing eccentric distance between an inner gear and an outer gear of the speed reducer by utilizing the axial line eccentric distance between the two bevel gears with different tooth numbers.

Background

The bevel gear has three basic deflection types, namely height deflection, tangential deflection and angle deflection, the most practical application is the comprehensive deflection of the height deflection, the height deflection and the tangential deflection, the angle deflection refers to the deflection type that a gear meshing angle is not equal to a gear pressure angle, and the deflection type of an indexing cone angle is not changed at present. The reference cone angle is the included angle between the axis of the bevel gear and the generatrix of the reference cone, and is related to the gear ratio of the two bevel gears meshed in pairs. The technical proposal that a bevel gear A is respectively meshed with a bevel gear B and a bevel gear C is designed, wherein the indexing cone angle of the bevel gear A and the bevel gear B is taken according to the method specified by the bevel gear standard, the bevel gear A and the bevel gear B are a pair of standard bevel gears, when the tooth numbers of the bevel gear C and the bevel gear B are not equal, the indexing conical angle of the bevel gear C is not equal to the indexing conical angle of the bevel gear B, the bevel gear C cannot be meshed with the bevel gear A, if the indexing conical angle of the bevel gear C is changed, the indexing conical angle of the bevel gear C becomes the modified bevel gear C, the indexing conical angle of the modified bevel gear C is equal to the indexing conical angle of the bevel gear B, the bevel gear A can be meshed with the bevel gear B and the modified bevel gear C respectively, and an axis eccentric distance is formed between the axis of the bevel gear B and the axis of the modified bevel gear C and is related to the difference between the tooth numbers of the bevel gear B and the modified bevel gear C.

Under the prerequisite that the modulus equals, cylindrical gear D can mesh with face gear, if cylindrical gear D meshes with a face gear E and a face gear F respectively, even the number of teeth of face gear E and face gear F is unequal, cylindrical gear D also can mesh with two face gears, has the eccentric distance of axis between face gear E axis and the face gear F axis this moment, and this eccentric distance of axis is relevant with the difference of the number of teeth of face gear E and face gear F.

The parallel shaft hybrid bevel gear differential speed reduction mechanism of application publication No. CN109737185A and the hybrid bevel gear differential speed reduction mechanism of application publication No. CN 109764108A's drive ratio is big, can be applied to joint robot as accurate reduction gear, the intelligence equips the field, this technical scheme is not suitable for the little general reduction gear of drive ratio, accurate reduction gear market share only accounts for five percent in reduction gear product market structure, if carry out accurate reduction gear research and development with replacing RV reduction gear and harmonic reduction gear as the purpose, research and development mechanism need amortize research and development cost very big. If the structure and the principle of the reducer are innovated, the transmission ratio range of the reducer is increased, products with the same specification can change the transmission ratio only by replacing part of parts, so that the products can be used as a precision reducer to be applied to the fields of joint robots and intelligent equipment when the transmission ratio is large, and can be used as a universal reducer to be applied to various industries when the transmission ratio is small, the research and development cost, the production cost and the equipment cost are amortized in the huge requirements of various industries on the universal reducer, and the vicious circle that the research and development mechanism increases the research and development investment and weakens the profitability is avoided.

Disclosure of Invention

The invention aims to overcome the defects that the prior precision speed reducer technology has a small transmission ratio range and can not be used as a universal speed reducer in various industries, and provides a speed reducing method which has a large transmission ratio range, can change the transmission ratio of products with the same specification only by replacing part of parts, can be used as the precision speed reducer in the fields of joint robots and intelligent equipment when the transmission ratio is large, and can be used as the universal speed reducer in various industries when the transmission ratio is small. The embodiments of the present invention are as follows:

the technical scheme of the differential speed reduction method of the modified hybrid bevel gear comprises a fixed cylinder component, a planet support component, a reference side hybrid bevel gear component and a comparison side hybrid bevel gear component. The fixed cylinder part comprises a fixed cylinder, a direction-changing bevel gear, a bearing gland, a first keybar, a first input shaft and a fifth bearing, the planet support part comprises an output shaft, a planet support, a planet shaft, a third shaft sleeve and a planet bevel gear, the reference side mixing bevel gear part comprises a third bearing, a first end cover, a second keybar, a second input shaft, a second input gear, a first bearing, a first shaft sleeve, a first mixing bevel gear and a third mixing bevel gear, the comparison side mixing bevel gear part comprises a fourth mixing bevel gear, a second bearing, a second shaft sleeve, a second end cover and a fourth bearing, the planet support part is arranged in the inner cavity of the fixed cylinder part, the reference side mixing bevel gear part is arranged at the axial right end of the fixed cylinder part, the universal part consists of the fixed cylinder part, the planet support part and the reference side mixing bevel gear part, the hybrid bevel gear differential speed reducer is composed of a universal component and a hybrid bevel gear component on a comparison side. The speed reducing method also comprises a contrast side modified hybrid bevel gear component and a contrast side modified direct-connection bevel gear component. The contrast side deflection mixing bevel gear component comprises a deflection mixing bevel gear, a mixing bevel gear five, a bearing six, a shaft sleeve four, an end cover three, a bearing seven and an eccentric ring one, the contrast side deflection mixing bevel gear component is installed at the left end of the shaft of the fixed cylinder component, and the deflection mixing bevel gear differential speed reducer is composed of a general component and a contrast side deflection mixing bevel gear component. The contrast side directly connected bevel gear part that shifts includes directly connected bevel gear that shifts, directly connects bevel gear, bearing eight, axle sleeve five, end cover four, bearing nine, eccentric ring two, and contrast side directly connected bevel gear part that shifts installs at fixed cylinder part axle left end, comprises general part, contrast side directly connected bevel gear part that shifts and becomes directly connected bevel gear differential speed reducer that shifts. The speed reduction method adopts the steps that the indexing conical angle of the bevel gear is changed to enable one bevel gear to be meshed with two bevel gears with different tooth numbers respectively, the axis eccentric distance between the two bevel gears with different tooth numbers is utilized to adjust the meshing eccentric distance between the inner gear and the outer gear of the speed reducer, and the transmission ratio range of the speed reducer is enlarged.

A mixing bevel gear tee joint of a mixing bevel gear differential speed reducer is installed in the right section of an inner cavity of a fixed cylinder through a third bearing, a mixing bevel gear tee joint is installed in the left section of the inner cavity of the fixed cylinder through a fourth bearing, the mixing bevel gear tee joint and the mixing bevel gear tee joint are coaxial with the inner cavity of the fixed cylinder, a fixed platform shaft hole perpendicular to the axis of the fixed cylinder is arranged in the middle section of the inner cavity of the fixed cylinder, a direction changing bevel gear is installed in the fixed platform shaft hole on the radial inner side of the fixed cylinder through a fifth bearing, a bearing gland is installed in the fixed platform shaft hole on the radial outer side of the fixed cylinder, an input shaft I is connected with the direction changing bevel gear through a first key bar, a mixing bevel gear I and a mixing bevel gear II are coaxial with an output shaft, the mixing bevel gear I is installed on the radial outer side of the right end of the, the left end journal of the output shaft is arranged in a bearing hole II of the end cover II through a bearing II, the left end shaft head of the output shaft penetrates through the bearing hole II and is positioned on the axial outer side of the end cover II, and a plurality of radial fixed shaft holes are uniformly distributed on the outer surface of the axial middle of the output shaft. The planet support is annular, a plurality of support mounting planes are uniformly distributed on the radial inner surface of the planet support, a support fixing shaft hole is formed in the center of each support mounting plane, a plurality of planet bevel gears are mounted in the inner cavity of the planet support, a planet shaft penetrates through a third shaft sleeve on the radial inner side of each planet bevel gear, one end of the planet shaft is mounted in the support fixing shaft hole of the planet support, the other end of the planet shaft is mounted in the fixing shaft hole of the output shaft, the planet bevel gears can rotate around the axis of the planet shaft, when the number of the planet bevel gears is less than three, the planet support component further comprises at least one positioning pin, one end of the positioning pin is mounted in the support fixing shaft hole of the planet support.

Mixing bevel gear one, mixing bevel gear two, mixing bevel gear three, mixing bevel gear four has a cylindrical teeth and a conical teeth respectively, and this cylindrical teeth and conical teeth are coaxial, mixing bevel gear one's inboard teeth is conical teeth, mixing bevel gear one's outside teeth is cylindrical teeth, mixing bevel gear two's inboard teeth is conical teeth, mixing bevel gear two's outside teeth is cylindrical teeth, mixing bevel gear three's inboard teeth is cylindrical teeth, and inboard teeth three is the internal gear, mixing bevel gear three's outside teeth is conical teeth, mixing bevel gear four's inboard teeth is cylindrical teeth, and inboard teeth four is the internal gear, mixing bevel gear four's outside teeth four is conical teeth.

The number of the four outer gear teeth of the fourth mixing bevel gear is equal to the number of the three outer gear teeth of the third mixing bevel gear, the number of the two inner gear teeth of the second mixing bevel gear is equal to the number of the one inner gear teeth of the first mixing bevel gear, the direction changing bevel gear is respectively meshed with the four outer gear teeth of the fourth mixing bevel gear and the three outer gear teeth of the third mixing bevel gear, and the planetary bevel gear is respectively meshed with the two inner gear teeth of the second mixing bevel gear and the one inner gear teeth of the first mixing bevel gear.

The number of the outer teeth of the second mixing bevel gear and the number of the outer teeth of the first mixing bevel gear are in a small tooth difference corresponding relationship, the difference between the number of the outer teeth of the second mixing bevel gear and the number of the outer teeth of the first mixing bevel gear is defined as a small tooth difference I, the number of the inner teeth of the fourth mixing bevel gear and the number of the inner teeth of the third mixing bevel gear are in a small tooth difference corresponding relationship, the difference between the number of the inner teeth of the fourth mixing bevel gear and the number of the inner teeth of the third mixing bevel gear is defined as a small tooth difference II, the outer teeth of the first mixing bevel gear are meshed with the inner teeth of the third mixing bevel gear, a meshing eccentric distance I is arranged between the axis of the first mixing bevel gear and the axis of the third mixing bevel gear, the outer teeth of the second mixing bevel gear are meshed.

The modulus of the first outer gear teeth of the first mixing bevel gear and the modulus of the third inner gear teeth of the third mixing bevel gear are a modulus one, the difference between the number of the third inner gear teeth of the third mixing bevel gear and the number of the first outer gear teeth of the first mixing bevel gear is defined as an eccentric distance tooth difference one, and the meshing eccentric distance one is equal to half of the product of the eccentric distance tooth difference one and the modulus one. The modulus of the outer gear teeth II of the second mixing bevel gear and the modulus of the inner gear teeth IV of the fourth mixing bevel gear are two, the difference between the number of the inner gear teeth IV of the fourth mixing bevel gear and the number of the outer gear teeth II of the second mixing bevel gear is defined as an eccentric distance gear difference II, and the meshing eccentric distance II is equal to half of the product of the eccentric distance gear difference II and the modulus two.

If the first axis of the mixing bevel gear is arranged on the lower side of the three axes of the mixing bevel gear and the second axis of the mixing bevel gear is arranged on the lower side of the four axes of the mixing bevel gear, the meshing eccentric distance II of the comparison side mixing bevel gear component is equal to the meshing eccentric distance I of the reference side mixing bevel gear component, and the meshing eccentric distance II is equal to the eccentric distance between the axis of the output shaft and the axis of the fixed cylinder, the assembly condition that the first mixing bevel gear, the second mixing bevel gear and the output shaft are coaxial is met.

The input gear II is connected with the input shaft II through a key strip II, the input gear II is cylindrical gear teeth, the input gear II is meshed with the gear teeth III on the inner side of the mixing bevel gear III, a shaft head at the right end of the input shaft II penetrates through an input shaft hole of the end cover I and is positioned on the axial outer side of the end cover I, and the axis of the input shaft II is parallel to the axis of the output shaft.

When the hybrid bevel differential speed reducer operates, the prime motor drives the first input shaft to rotate or drives the second input shaft to rotate, if the first input shaft is driven by the prime motor to rotate along the rotation direction of the direction-changing bevel gear, the first input shaft drives the third hybrid bevel gear and the fourth hybrid bevel gear to rotate respectively through the direction-changing bevel gear, the fourth hybrid bevel gear rotates in the direction opposite to the third hybrid bevel gear, the fourth hybrid bevel gear rotates in the same direction as the third hybrid bevel gear, the third hybrid bevel gear drives the second hybrid bevel gear to rotate in the same direction, the second hybrid bevel gear rotates in the direction opposite to the first hybrid bevel gear, the second hybrid bevel gear rotates in the same direction as the first hybrid bevel gear due to the factors of small tooth difference I and small tooth difference II, the rotation speed of the second hybrid bevel gear is not equal to that of the first hybrid bevel gear, and the difference between the, the second mixing bevel gear and the first mixing bevel gear drive the planetary bevel gears to rotate together, the planetary bevel gears revolve around the axis of the output shaft while rotating around the axis of the planetary shaft, the planetary bevel gears drive the planetary support to rotate at a low speed, the rotating speed of the planetary support is equal to half of the difference between the second rotating speed of the mixing bevel gears and the first rotating speed of the first mixing bevel gears, and the planetary support drives the output shaft to rotate at the low speed in the same direction through the planetary shaft.

On the premise that the meshing eccentric distance II of the comparison side hybrid bevel gear component is equal to the meshing eccentric distance I of the reference side hybrid bevel gear component, the difference between the rotating speed of the hybrid bevel gear II and the rotating speed of the hybrid bevel gear I can be changed by changing the eccentric distance tooth difference II and the module II or changing the eccentric distance tooth difference I and the module I, and finally the transmission ratio of the hybrid bevel gear differential speed reducer is changed.

The differential speed reducer with modified bevel gears is formed by replacing a gear part on the modified bevel gears on the opposite side in the differential speed reducer with modified bevel gears on the opposite side. The deflection mixing bevel gear is installed in an inner cavity of the eccentric ring I through a bearing VII, the eccentric ring I is installed in the left section of the inner cavity of the fixed cylinder, one end of the fixed pin is installed in a fixed pin hole I of the fixed cylinder, the other end of the fixed pin is installed in a fixed pin hole II of the eccentric ring I, the deflection mixing bevel gear and the inner cavity of the fixed cylinder are not coaxial, the mixing bevel gear V is installed on the radial outer side, close to the left end, of the output shaft through a shaft sleeve IV, a shaft neck at the left end of the output shaft is installed in a bearing hole III of the end cover III through a bearing VI, and.

The fifth mixing bevel gear and the sixth shifting mixing bevel gear are respectively provided with a cylindrical gear and a conical gear, the cylindrical gear and the conical gear are coaxial, the fifth inner gear of the fifth mixing bevel gear is a conical gear, the fifth outer gear of the fifth mixing bevel gear is a cylindrical gear, the sixth inner gear of the sixth shifting mixing bevel gear is a cylindrical gear, the sixth inner gear is an internal gear, and the sixth outer gear of the sixth shifting mixing bevel gear is a conical gear.

And the indexing cone angle of the turning bevel gear and the three-indexing cone angle of the outer gear teeth of the third mixing bevel gear are valued according to a method specified by a bevel gear standard, so that the six-indexing cone angle of the outer gear teeth of the shifting mixing bevel gear is equal to the three-indexing cone angle of the outer gear teeth of the third mixing bevel gear. If the six teeth of the outer side gear teeth of the deflection mixing bevel gear are less than the three teeth of the outer side gear teeth of the third mixing bevel gear, the axis of the deflection mixing bevel gear is arranged on the upper side of the three axes of the mixing bevel gear.

The modulus of the outer gear teeth III of the direction-changing bevel gear and the mixing bevel gear III and the modulus of the outer gear teeth six of the deflection mixing bevel gear are modulus III, the difference between the number of the outer gear teeth III of the mixing bevel gear III and the number of the outer gear teeth six of the deflection mixing bevel gear is defined as the eccentric distance gear difference III, and the axis eccentric distance III between the axis of the mixing bevel gear and the axis of the deflection mixing bevel gear is equal to half of the product of the eccentric distance gear difference III and the modulus III.

The number of teeth of the inner side gear teeth five of the mixing bevel gear five is equal to the number of teeth of the inner side gear teeth one of the mixing bevel gear I, and the planetary bevel gear is meshed with the inner side gear teeth five of the mixing bevel gear five and the inner side gear teeth one of the mixing bevel gear I respectively. The difference between the six tooth numbers of the inner gear teeth of the deflection mixing bevel gear and the three tooth numbers of the inner gear teeth of the mixing bevel gear III is large, the six tooth numbers of the inner gear teeth and the three tooth numbers of the inner gear teeth are not in small tooth difference corresponding relation, the difference between the five tooth numbers of the outer gear teeth of the mixing bevel gear V and the one tooth number of the outer gear teeth of the mixing bevel gear I is large, and the five tooth numbers of the outer gear teeth and the one tooth number of the outer gear teeth are not in small tooth.

The inner gear teeth six of the deflection mixing bevel gear are meshed with the outer gear teeth five of the mixing bevel gear five, the modulus of the inner gear teeth six of the deflection mixing bevel gear and the modulus of the outer gear teeth five of the mixing bevel gear are four, the difference between the number of the inner gear teeth six of the deflection mixing bevel gear and the number of the outer gear teeth five of the mixing bevel gear is defined as an eccentric distance gear difference four, a meshing eccentric distance three is arranged between the five axis of the mixing bevel gear and the axis of the deflection mixing bevel gear, and the meshing eccentric distance three is equal to half of the product of the eccentric distance gear difference four and the modulus four.

If the meshing eccentric distance III is larger than the meshing eccentric distance I, the five axis of the mixing bevel gear is arranged on the lower side of the three axis of the mixing bevel gear, the difference between the meshing eccentric distance III and the axis eccentric distance III is the comprehensive eccentric distance III of the reference side deflection mixing bevel gear component, the comprehensive eccentric distance III is equal to the meshing eccentric distance I of the reference side mixing bevel gear component, the comprehensive eccentric distance III is equal to the eccentric distance between the axis of the output shaft and the axis of the fixed cylinder, and the assembly condition that the first mixing bevel gear, the fifth mixing bevel gear and the output shaft are coaxial is met.

When the modified mixed bevel differential speed reducer operates, if the same rotating speed is input by the first input shaft of the modified mixed bevel differential speed reducer and the mixed bevel differential speed reducer respectively, in the mixed bevel differential speed reducer, the number of the four outer gear teeth of the fourth mixed bevel gear is equal to the number of the three outer gear teeth of the third mixed bevel gear, the four rotating speed of the mixed bevel gear is equal to the three rotating speed of the mixed bevel gear, and the difference between the two rotating speeds of the second mixed bevel gear and the first rotating speed of the mixed bevel gear is small due to the corresponding relation of the small gear difference I and the small gear difference II, so the transmission ratio of the mixed bevel differential speed reducer is large. In the modified mixed bevel gear differential speed reducer, the six outer gear teeth of a modified mixed bevel gear are less than the three outer gear teeth of a mixed bevel gear, the rotating speed of the modified mixed bevel gear is greater than the three rotating speed of the mixed bevel gear, the torque is accelerated from the modified mixed bevel gear to the fifth mixed bevel gear, the meshing eccentric distance is three and is greater than the meshing eccentric distance, if the modulus is four and is equal to the modulus, the eccentric distance tooth difference is four and is greater than the eccentric distance tooth difference, the transmission ratio between the modified mixed bevel gear and the fifth mixed bevel gear is less than the transmission ratio between the third mixed bevel gear and the first mixed bevel gear, the difference between the rotating speed of the fifth mixed bevel gear and the rotating speed of the first mixed bevel gear is large, and therefore the transmission ratio of the modified.

On the premise that the comprehensive eccentric distance three of the comparison side modified mixed bevel gear component is equal to the meshing eccentric distance one of the reference side mixed bevel gear component, the difference between the five rotating speeds of the mixed bevel gear and the first rotating speed of the mixed bevel gear can be changed by changing the eccentric distance tooth difference three and the modulus three, or changing the eccentric distance tooth difference four and the modulus four, or changing the eccentric distance tooth difference one and the modulus one, and finally changing the transmission ratio of the modified mixed bevel gear differential speed reducer.

The differential speed reducer with the shifted direct-connection bevel gears is formed by replacing a mixed bevel gear part on the contrast side in the mixed bevel gear differential speed reducer with a direct-connection bevel gear part on the contrast side, a planet support part in the differential speed reducer with the shifted direct-connection bevel gear and a mixed bevel gear part on the reference side rotate for one hundred and eighty degrees along the axis of the fixed cylinder, and one axis of the mixed bevel gear is arranged on the upper side of the three axis of the mixed bevel gear. The deflection direct-connection bevel gear is installed in an inner cavity of the eccentric ring II through the bearing nine, the eccentric ring II is installed in an inner cavity left section of the fixed cylinder, one end of the fixed pin is installed in a fixed pin hole I of the fixed cylinder, the other end of the fixed pin is installed in a fixed pin hole II of the eccentric ring II, the deflection direct-connection bevel gear and an inner cavity of the fixed cylinder are not coaxial, the direct-connection bevel gear is installed on the radial outer side, close to the left end, of the output shaft through a shaft sleeve five, the left end shaft neck of the output shaft is installed in a bearing hole four of the end cover four through a bearing eight, and.

The seventh gear tooth of inboard wheel tooth that directly links the bevel gear inboard one end is the conical gear tooth, and the axial other end of directly linking the bevel gear is the external spline, and the seventh gear tooth of inboard wheel tooth is coaxial with the external spline, and the radial outside gear tooth eight that directly links the bevel gear that shifts is the conical gear tooth to the outside, and the radial inboard of directly linking the bevel gear that shifts is the internal spline, and the eight gear teeth of outboard wheel tooth are coaxial with the internal spline.

And the indexing cone angle of the direction-changing bevel gear and the three-indexing cone angle of the outer gear teeth of the three mixed bevel gear are valued according to a method specified by a bevel gear standard, so that the eight-indexing cone angle of the outer gear teeth of the direction-changing direct-connected bevel gear is equal to the three-indexing cone angle of the outer gear teeth of the three mixed bevel gear. And if the eight teeth number of the outer side gear teeth of the modified direct-connected bevel gear is less than the three teeth number of the outer side gear teeth of the third mixed bevel gear, the axis of the modified direct-connected bevel gear is arranged on the upper side of the three axes of the mixed bevel gear.

The modulus of the outer side gear teeth III of the direction-changing bevel gear and the mixed bevel gear III and the modulus of the outer side gear teeth eight of the modified direct-connected bevel gear are modulus III, the difference between the number of the outer side gear teeth III of the mixed bevel gear III and the number of the outer side gear teeth eight of the modified direct-connected bevel gear is defined as an eccentric distance gear difference V, and the axis eccentric distance IV between the axis of the mixed bevel gear III and the axis of the modified direct-connected bevel gear is equal to half of the product of the eccentric distance gear difference V.

The number of teeth of the inner side gear teeth seven of the direct-connected bevel gear is equal to the number of teeth of the inner side gear teeth one of the mixed bevel gear I, and the planetary bevel gear is meshed with the inner side gear teeth seven of the direct-connected bevel gear and the inner side gear teeth one of the mixed bevel gear I respectively. The outer spline of the direct-connected bevel gear is arranged in the inner spline of the deflection direct-connected bevel gear, the direct-connected bevel gear is coaxial with the deflection direct-connected bevel gear, the comprehensive eccentric distance IV of the comparison side deflection direct-connected bevel gear component is equal to the axis eccentric distance IV, the comprehensive eccentric distance IV is equal to the meshing eccentric distance I of the reference side mixing bevel gear component, the comprehensive eccentric distance IV is equal to the eccentric distance between the axis of the output shaft and the axis of the fixed cylinder, and the assembly conditions that the first mixing bevel gear, the direct-connected bevel gear and the output shaft are coaxial.

When the modified direct-connected bevel gear differential speed reducer operates, if the modified direct-connected bevel gear differential speed reducer and the modified mixed bevel gear differential speed reducer input the same rotating speed respectively through the input shaft I, in the modified direct-connected bevel gear differential speed reducer, the eight teeth number of the outer side teeth of the modified direct-connected bevel gear is smaller than the three teeth number of the outer side teeth of the mixed bevel gear III, the rotating speed of the modified direct-connected bevel gear is larger than the three rotating speed of the mixed bevel gear, the rotating speed of the direct-connected bevel gear is equal to the rotating speed of the modified direct-connected bevel gear, the difference between the rotating speed of the direct-connected bevel gear and the rotating speed of the mixed bevel gear is large, and no accelerated transmission exists between the modified direct-connected bevel gear and the direct-connected bevel gear due to the torque, the rotating speed of the direct-connected bevel gear of the modified direct- And (3) removing the solvent.

On the premise that the comprehensive eccentric distance four of the comparison side modified direct-connection bevel gear component is equal to the meshing eccentric distance one of the reference side mixed bevel gear component, the eccentric distance tooth difference five and the module three are changed, or the eccentric distance tooth difference one and the module one are changed, the difference between the rotation speed of the direct-connection bevel gear and the rotation speed of the mixed bevel gear can be changed, and finally the transmission ratio of the modified direct-connection bevel gear differential speed reducer is changed.

In the mixed bevel gear differential reduction gear that shifts, in the direct-connected bevel gear differential reduction gear that shifts, change bevel gear with cylindrical gear D respectively, the outer teeth of a cogwheel three of the mixed bevel gear three of general part and the outer teeth of a cogwheel four of mixed bevel gear four, the outer teeth of a cogwheel six of the mixed bevel gear that shifts of the mixed bevel gear part that shifts of contrast side, the outer teeth of a cogwheel eight of the direct-connected bevel gear that shifts of contrast side is replaced by the terminal surface teeth of a cogwheel respectively, can realize the meshing of a cylindrical gear with two terminal gears that the number of teeth is unequal respectively, and constitute the mixed bevel gear differential reduction gear of terminal surface respectively, terminal surface direct-connected bevel gear differential reduction gear.

The speed reduction method adopts a general component to be respectively combined with a comparison side mixed bevel gear component, a comparison side modified mixed bevel gear component and a comparison side modified direct-connected bevel gear component to form a mixed bevel gear differential speed reducer, a modified mixed bevel gear differential speed reducer and a modified direct-connected bevel gear differential speed reducer, the transmission ratio ranges of the three speed reducers are different, the transmission ratio of the mixed bevel gear differential speed reducer is large, the transmission ratio of the modified mixed bevel gear differential speed reducer is small, the transmission ratio of the modified direct-connected bevel gear differential speed reducer is between the mixed bevel gear differential speed reducer and the modified mixed bevel gear differential speed reducer, the speed reduction method respectively provides a method for changing the transmission ratios of the three speed reducers, the speed reduction method adopts a bevel gear indexing conical angle to enable one bevel gear to be respectively meshed with two bevel gears with unequal tooth number, and utilizes the axis eccentric distance between the two bevel gears with unequal tooth number to adjust the meshing, the function of increasing the transmission ratio range of the speed reducer and changing the transmission ratio of products with the same specification only by replacing part of parts can be realized.

Drawings

Fig. 1 is a schematic view of the indexing of a modified indexing cone angle in which a bevel gear a meshes with a bevel gear B and a modified indexing bevel gear C, respectively.

Fig. 2 is a schematic view of the cylindrical gear D meshing with the face gear E and the face gear F, respectively.

FIG. 3 is a schematic view of a hybrid bevel differential speed reducer taken along the axis.

FIG. 4 is a schematic diagram of the input shaft I driving the mixing bevel gear III and the mixing bevel gear IV to rotate, and is a schematic diagram of the input shaft II driving the mixing bevel gear III to rotate and the input shaft II driving the direction-changing bevel gear to make the direction of rotation of the mixing bevel gear IV opposite to the direction of rotation of the mixing bevel gear III.

FIG. 5 is an axial cross-sectional view of a universal component.

Fig. 6 is an axial cross-sectional view of the stationary barrel part.

FIG. 7 is an isometric cross-sectional view of the reference side mixing bevel gear member.

FIG. 8 is an isometric cross-sectional view of a comparative side mixing bevel gear member.

FIG. 9 is a schematic view of a modified hybrid bevel differential speed reducer taken along the axis.

FIG. 10 is an isometric cross-sectional view of a comparative side-shifted hybrid bevel gear member.

FIG. 11 is a schematic view of a modified straight bevel differential speed reducer taken along the axis.

FIG. 12 is an isometric cross-sectional view of a comparative side-indexed direct connected bevel gear member.

FIG. 13 is an isometric view of the planet carrier assembly member showing the first and second mixing bevel gears driving the planet carrier member to rotate in the operating condition, where UII is greater than UII, and UIII rotate in the same direction.

FIG. 14 is an isometric view of either the eccentric ring one or the eccentric ring two.

FIG. 15 is a schematic illustration of the meshing eccentricity of the reference side hybrid bevel gear member-this illustration applies to both hybrid bevel differential reducers and modified hybrid bevel differential reducers.

FIG. 16 is a schematic illustration of the meshing eccentric distances of the comparative side hybrid bevel gear members, as applied to a hybrid bevel differential reduction gear.

FIG. 17 is a schematic diagram of the third meshing eccentric distance, the third axis eccentric distance, and the third combined eccentric distance of a comparative side-modified hybrid bevel gear member, which is suitable for a modified hybrid bevel differential reducer.

FIG. 18 is a schematic illustration of the meshing eccentricity of the reference side hybrid bevel gear member — this illustration is applicable to a modified direct attached bevel differential reduction gear.

FIG. 19 is a graph comparing the axis eccentricity four and the combined eccentricity four of a side modified direct connection bevel gear component, which is suitable for a modified direct connection bevel gear differential speed reducer.

In fig. 13, U i is the linear speed of the rotation at the position of the first pitch circle of the inner teeth of the first mixing bevel gear, U ii is the linear speed of the rotation at the position of the second pitch circle of the inner teeth of the second mixing bevel gear, and U iii is the linear speed of the rotation at the position on the planet carrier where the radius of the first pitch circle of the inner teeth of the first mixing bevel gear is equal to or equal to the radius of the second pitch circle of the inner teeth of the second mixing bevel gear.

In fig. 1, δ 1 is the bevel gear a reference cone angle, δ 2 is the bevel gear B reference cone angle, δ 2' is the modified bevel gear C reference cone angle, Δ o1 in fig. 1 is the first axial eccentricity distance between the bevel gear B axis and the modified bevel gear C axis, Δ o2 in fig. 2 is the second axial eccentricity distance between the face gear E axis and the face gear F axis, Δ o3 in fig. 17 is the third axial eccentricity distance between the hybrid bevel gear triaxial axis and the modified hybrid bevel gear axis, and Δ o4 in fig. 19 is the fourth axial eccentricity distance between the hybrid bevel gear triaxial axis and the modified direct bevel gear axis.

In fig. 15 to 19, Δ h1 is the first meshing eccentric distance between the first mixing bevel gear axis of the reference-side mixing bevel gear member and the third mixing bevel gear axis, Δ h2 is the second meshing eccentric distance between the second mixing bevel gear axis of the comparison-side mixing bevel gear member and the fourth mixing bevel gear axis, Δ h3 is the third meshing eccentric distance between the fifth mixing bevel gear axis of the comparison-side shifted mixing bevel gear member and the shifted mixing bevel gear axis, Δ h3 'is the third comprehensive eccentric distance of the comparison-side shifted mixing bevel gear member, and Δ h 4' is the fourth comprehensive eccentric distance of the comparison-side shifted direct-connected bevel gear member.

The drawing is marked with a modified bevel gear C axis 1, a modified bevel gear C2, a bevel gear A axis 3, a bevel gear A4, a bevel gear B5, a bevel gear B axis 6, a face gear F axis 7, a face gear F8, a cylindrical gear D axis 9, a cylindrical gear D10, a face gear E11, a face gear E axis 12, a screw 13, a hybrid bevel gear four 14, a hybrid bevel gear two 15, a bearing two 16, an output shaft 17, a bushing two 18, a positioning pin 19, an end cap two 20, a bearing four 21, a change bevel gear 22, a bearing gland 23, a spline one 24, an input shaft one 25, a bearing five 26, a fixed cylinder 27, a bearing three 28, an end cap one 29, a spline two 30, an input shaft two 31, an input gear two 32, a bearing one 33, a bushing one 34, a hybrid bevel gear one 35, a hybrid bevel gear three 36, a planet support 37, a planet shaft 38, a bushing three 39, a planet bevel gear 40, a fixed, Inner cavity left section 42, inner cavity middle section 43, inner cavity right section 44, mixed bevel gear four rotation trajectory 45, mixed bevel gear four rotation direction 46, modified mixed bevel gear 47, mixed bevel gear five 48, bearing six 49, sleeve four 50, end cap three 51, bearing seven 52, eccentric ring one 53, fixed pin 54, modified direct bevel gear 55, direct bevel gear 56, bearing eight 57, sleeve five 58, end cap four 59, bearing nine 60, eccentric ring two 61, modified bevel gear rotation trajectory 62, modified bevel gear rotation direction 63, input shaft axis 64, mixed bevel gear three rotation trajectory 65, mixed bevel gear three rotation direction 66, fixed cylinder axis 67, output shaft axis 68, planetary bevel gear rotation direction 69, planetary shaft axis 70, planetary bevel gear rotation trajectory 71, mixed bevel gear one rotation trajectory 72, mixed bevel gear one rotation direction 73, planet support rotation direction 74, The planet carrier rotation trajectory 75, the second mixing bevel gear rotation direction 76, the second mixing bevel gear rotation trajectory 77, the second fixing pin holes 78, the contour line 79 of the first mixing bevel gear axis, the contour line 80 of the third mixing bevel gear axis, the contour line 81 of the second mixing bevel gear axis, the contour line 82 of the fourth mixing bevel gear axis, the contour line 83 of the fifth mixing bevel gear axis, the contour line 84 of the modified mixing bevel gear axis, and the contour line 85 directly connecting the modified bevel gear axis.

Detailed Description

The invention is further described below with reference to the accompanying drawings.

Referring to fig. 3, 5, 9 and 11, the technical scheme of the differential speed reduction method of the modified hybrid bevel gear comprises a fixed cylinder component, a planet carrier component, a reference side hybrid bevel gear component and a comparison side hybrid bevel gear component. The fixed cylinder part comprises a fixed cylinder 27, a direction-changing bevel gear 22, a bearing gland 23, a spline I24, an input shaft I25 and a bearing V26, the planet support part comprises an output shaft 17, a planet support 37, a planet shaft 38, a shaft sleeve III 39 and a planet bevel gear 40, the reference side mixing bevel gear part comprises a bearing III 28, an end cover I29, a spline II 30, an input shaft II 31, an input gear II 32, a bearing I33, a shaft sleeve I34, a mixing bevel gear I35 and a mixing bevel gear III 36, the comparison side mixing bevel gear part comprises a mixing bevel gear IV 14, a mixing bevel gear II 15, a bearing II 16, a shaft sleeve II 18, an end cover II 20 and a bearing IV 21, the planet support part is arranged in the inner cavity of the fixed cylinder part, the reference side mixing bevel gear part is arranged at the axial right end of the fixed cylinder part, and the fixed cylinder part, the planet support part and, the contrast side hybrid bevel gear component is arranged at the left end of the fixed cylinder component shaft, and a hybrid bevel gear differential speed reducer is composed of a general component and a contrast side hybrid bevel gear component. The speed reducing method also comprises a contrast side modified hybrid bevel gear component and a contrast side modified direct-connection bevel gear component. The comparison side deflection mixing bevel gear component comprises a deflection mixing bevel gear 47, a mixing bevel gear five 48, a bearing six 49, a shaft sleeve four 50, an end cover three 51, a bearing seven 52 and an eccentric ring one 53, is arranged at the left end of the fixed cylinder component, and consists of a general component and a comparison side deflection mixing bevel gear component to form a deflection mixing bevel gear differential speed reducer. The contrast side directly connected bevel gear components with the modified positions comprise modified directly connected bevel gears 55, directly connected bevel gears 56, eight bearings 57, five shaft sleeves 58, four end covers 59, nine bearings 60 and two eccentric rings 61, the contrast side directly connected bevel gear components with the modified positions are installed at the left end of the shaft of the fixed cylinder component, and the modified directly connected bevel gear differential speed reducer is composed of general components and contrast side directly connected bevel gear components with the modified positions. The speed reduction method adopts the steps that the indexing conical angle of the bevel gear is changed to enable one bevel gear to be meshed with two bevel gears with different tooth numbers respectively, the axis eccentric distance between the two bevel gears with different tooth numbers is utilized to adjust the meshing eccentric distance between the inner gear and the outer gear of the speed reducer, and the transmission ratio range of the speed reducer is enlarged.

Referring to fig. 3 to 8 and 13 to 16, a third hybrid bevel gear 36 of the hybrid bevel differential speed reducer is mounted in a right section 44 of an inner cavity of the fixed cylinder 27 through a third bearing 28, a fourth hybrid bevel gear 14 is mounted in a left section 42 of the inner cavity of the fixed cylinder 27 through a fourth bearing 21, the third hybrid bevel gear 36 and the fourth hybrid bevel gear 14 are coaxial with the inner cavity of the fixed cylinder 27, a middle section 43 of the inner cavity of the fixed cylinder 27 is provided with a fixed table shaft hole perpendicular to the axis 67 of the fixed cylinder, a direction-changing bevel gear 22 is mounted in the fixed table shaft hole on the radial inner side of the fixed cylinder 27 through a fifth bearing 26, a bearing gland 23 is mounted in the fixed table shaft hole on the radial outer side of the fixed cylinder 27, a first input shaft 25 is connected with the direction-changing bevel gear 22 through a first spline 24, a first hybrid bevel gear 35 and a second hybrid bevel gear 15 are coaxial with, the right end journal of the output shaft 17 is installed in a bearing hole I of the end cover I29 through a bearing I33, the second hybrid bevel gear 15 is installed on the outer side, close to the radial direction of the left end, of the output shaft 17 through a shaft sleeve II 18, the left end journal of the output shaft 17 is installed in a bearing hole II of the end cover II 20 through a bearing II 16, the left end shaft head of the output shaft 17 penetrates through the bearing hole II and is located on the outer side, in the axial direction, of the end cover II 20, and a plurality of radial fixing shaft holes are. The planet carrier 37 is annular, a plurality of carrier mounting planes are uniformly distributed on the radial inner surface of the planet carrier 37, a carrier fixing shaft hole is formed in the center of each carrier mounting plane, a plurality of planet bevel gears 40 are mounted in the inner cavities of the planet carrier 37, the planet shafts 38 penetrate through the shaft sleeves III 39 on the radial inner sides of the planet bevel gears 40, one ends of the planet shafts 38 are mounted in the carrier fixing shaft holes of the planet carrier 37, the other ends of the planet shafts 38 are mounted in the fixing shaft holes of the output shaft 17, the planet bevel gears 40 can rotate around the axis 70 of the planet shafts, when the number of the planet bevel gears 40 is less than three, the planet carrier component further comprises at least one positioning pin 19, one end of the positioning pin 19 is mounted in the carrier fixing shaft hole of the planet carrier 37.

The first mixing bevel gear 35, the second mixing bevel gear 15, the third mixing bevel gear 36 and the fourth mixing bevel gear 14 respectively have a cylindrical gear tooth and a conical gear tooth, and the cylindrical gear tooth and the conical gear tooth are coaxial, the inner side gear tooth of the first mixing bevel gear 35 is a conical gear tooth, the outer side gear tooth of the first mixing bevel gear 35 is a cylindrical gear tooth, the inner side gear tooth of the second mixing bevel gear 15 is a conical gear tooth, the outer side gear tooth of the second mixing bevel gear 15 is a cylindrical gear tooth, the inner side gear tooth of the third mixing bevel gear 36 is a cylindrical gear tooth, the inner side gear tooth third is an internal gear, the outer side gear tooth third of the third mixing bevel gear 36 is a conical gear tooth, the inner side gear tooth fourth of the fourth mixing bevel gear 14 is a cylindrical gear tooth, the inner side gear.

The number of the outer gear teeth four of the fourth mixing bevel gear 14 is equal to the number of the outer gear teeth three of the third mixing bevel gear 36, the number of the inner gear teeth two of the second mixing bevel gear 15 is equal to the number of the inner gear teeth one of the first mixing bevel gear 35, the direction-changing bevel gear 22 is respectively meshed with the outer gear teeth four of the fourth mixing bevel gear 14 and the outer gear teeth three of the third mixing bevel gear 36, and the planetary bevel gear 40 is respectively meshed with the inner gear teeth two of the second mixing bevel gear 15 and the inner gear teeth one of the first mixing bevel gear 35.

The number of the second outer gear teeth of the second mixing bevel gear 15 and the number of the first outer gear teeth of the first mixing bevel gear 35 are in a small gear difference corresponding relationship, the difference between the number of the second outer gear teeth and the number of the first outer gear teeth is defined as a small gear difference I, the number of the fourth inner gear teeth of the fourth mixing bevel gear 14 and the number of the third inner gear teeth of the third mixing bevel gear 36 are in a small gear difference corresponding relationship, the difference between the number of the fourth inner gear teeth and the number of the third inner gear teeth is defined as a small gear difference II, the first outer gear teeth of the first mixing bevel gear 35 are meshed with the third inner gear teeth of the third mixing bevel gear 36, a first meshing eccentric distance is reserved between the axis of the first mixing bevel gear 35 and the axis of the third mixing bevel gear 36, the second outer gear teeth of the second mixing bevel gear 15 are meshed with the fourth inner gear.

The modulus of the first outer gear teeth of the first mixing bevel gear 35 and the modulus of the third inner gear teeth of the third mixing bevel gear 36 are modulus one, the difference between the number of the third inner gear teeth of the third mixing bevel gear 36 and the number of the first outer gear teeth of the first mixing bevel gear 35 is defined as an eccentric distance tooth difference one, and the meshing eccentric distance one is equal to half of the product of the eccentric distance tooth difference one and the modulus one. The modulus of the second outer gear teeth of the second mixing bevel gear 15 and the modulus of the fourth inner gear teeth of the fourth mixing bevel gear 14 are two, the difference between the number of the fourth inner gear teeth of the fourth mixing bevel gear 14 and the number of the second outer gear teeth of the second mixing bevel gear 15 is defined as an eccentric distance gear difference two, and the meshing eccentric distance two is equal to half of the product of the eccentric distance gear difference two and the modulus two.

If the first mixing bevel gear 35 axis is below the third mixing bevel gear 36 axis and the second mixing bevel gear 15 axis is below the fourth mixing bevel gear 14 axis, the second meshing eccentric distance of the reference side mixing bevel gear member is equal to the first meshing eccentric distance of the reference side mixing bevel gear member, and the second meshing eccentric distance is equal to the eccentric distance between the output shaft axis 68 and the fixed cylinder axis 67, the assembly condition that the first mixing bevel gear 35, the second mixing bevel gear 15 and the output shaft 17 are coaxial is satisfied.

The second input gear 32 is connected with the second input shaft 31 through the second spline 30, the second input gear 32 is cylindrical gear teeth, the second input gear 32 is meshed with the third internal gear teeth of the third mixing bevel gear 36, the shaft head at the right end of the second input shaft 31 penetrates through the input shaft hole of the first end cover 29 and is located on the axial outer side of the first end cover 29, and the axis of the second input shaft 31 is parallel to the axis 68 of the output shaft.

When the hybrid bevel differential speed reducer operates, the first input shaft 25 is driven by the prime mover to rotate or the second input shaft 31 is driven by the prime mover to rotate, if the first input shaft 25 is driven by the prime mover to rotate along the direction 63 of rotation of the direction-changing bevel gear, the first input shaft 25 drives the third hybrid bevel gear 36 and the fourth hybrid bevel gear 14 to rotate respectively through the direction-changing bevel gear 22, the fourth hybrid bevel gear 46 rotates in the direction opposite to the third hybrid bevel gear 66, the fourth hybrid bevel gear 14 rotates in the same direction as the third hybrid bevel gear 36, the third hybrid bevel gear 36 drives the first hybrid bevel gear 35 to rotate in the same direction, the fourth hybrid bevel gear 14 drives the second hybrid bevel gear 15 to rotate in the same direction, the second hybrid bevel gear rotating direction 76 is opposite to the first hybrid bevel gear rotating direction 73, and the rotational speeds of the second hybrid bevel gear 15 are not equal to the rotational speed of the first, and the difference between the rotation speed of the second mixing bevel gear 15 and the rotation speed of the first mixing bevel gear 35 is small, the second mixing bevel gear 15 and the first mixing bevel gear 35 drive the planetary bevel gear 40 to rotate together, the planetary bevel gear 40 rotates around the output shaft axis 68 while the planetary bevel gear 40 rotates around the planetary shaft axis 70, the planetary bevel gear 40 drives the planetary carrier 37 to rotate at a low speed, the rotation speed of the planetary carrier 37 is half of the difference between the rotation speed of the second mixing bevel gear 15 and the rotation speed of the first mixing bevel gear 35, and the planetary carrier 37 drives the output shaft 17 to rotate at a low speed in the same direction through the planetary shaft 38.

On the premise that the meshing eccentric distance II of the comparison side hybrid bevel gear component is equal to the meshing eccentric distance I of the reference side hybrid bevel gear component, the difference between the 15 rotating speed of the hybrid bevel gear II and the 35 rotating speed of the hybrid bevel gear I can be changed by changing the eccentric distance tooth difference II and the module II or changing the eccentric distance tooth difference I and the module I, and finally the transmission ratio of the hybrid bevel gear differential speed reducer is changed.

Referring to fig. 1-7, 9-17, a modified hybrid bevel differential reduction gear is formed by replacing a comparative side hybrid bevel gear member in a hybrid bevel differential reduction gear with a comparative side modified hybrid bevel gear member. The deflection mixing bevel gear 47 is installed in the inner cavity of the first eccentric ring 53 through a seventh bearing 52, the first eccentric ring 53 is installed in the left section 42 of the inner cavity of the fixed cylinder 27, one end of the fixed pin 54 is installed in the first fixed pin hole 41 of the fixed cylinder 27, the other end of the fixed pin 54 is installed in the second fixed pin hole 78 of the first eccentric ring 53, the deflection mixing bevel gear 47 is not coaxial with the inner cavity of the fixed cylinder 27, the fifth mixing bevel gear 48 is installed on the outer radial side, close to the left end, of the output shaft 17 through a fourth shaft sleeve 50, the left end shaft neck of the output shaft 17 is installed in the third bearing hole of the third end cover 51 through a sixth bearing 49, and the left end shaft.

The mixing bevel gear five 48 and the modified mixing bevel gear 47 have one cylindrical gear tooth and one conical gear tooth, respectively, and the cylindrical gear tooth and the conical gear tooth are coaxial, the inner gear tooth five of the mixing bevel gear five 48 is a conical gear tooth, the outer gear tooth five of the mixing bevel gear five 48 is a cylindrical gear tooth, the inner gear tooth six of the modified mixing bevel gear 47 is a cylindrical gear tooth, and the inner gear tooth six is an internal gear, and the outer gear tooth six of the modified mixing bevel gear 47 is a conical gear tooth.

The six teeth of the outer teeth of the deflection mixing bevel gear 47 are not equal to the three teeth of the outer teeth of the mixing bevel gear 36, the direction-changing bevel gear 22 is respectively meshed with the six teeth of the outer teeth of the deflection mixing bevel gear 47 and the three teeth of the outer teeth of the mixing bevel gear 36, the indexing cone angle of the direction-changing bevel gear 22 and the three indexing cone angle of the outer teeth of the mixing bevel gear 36 are calculated according to a method specified by a bevel gear standard, and the six indexing cone angle of the outer teeth of the deflection mixing bevel gear 47 is equal to the three indexing cone angle of the outer teeth of the mixing bevel gear. If the six teeth of the outer teeth of the modified bevel gear 47 are less than the three teeth of the outer teeth of the bevel gear III 36, the axis of the modified bevel gear 47 is above the axis of the bevel gear III 36.

The modulus of the outer teeth three of the direction-changing bevel gear 22 and the mixing bevel gear 36 and the modulus of the outer teeth six of the modified mixing bevel gear 47 are modulus three, the difference between the number of the outer teeth three of the mixing bevel gear 36 and the number of the outer teeth six of the modified mixing bevel gear 47 is defined as an eccentric distance tooth difference three, and the axial eccentric distance three between the axis of the mixing bevel gear 36 and the axis of the modified mixing bevel gear 47 is equal to half of the product of the eccentric distance tooth difference three and the modulus three.

The number of teeth of the inner gear teeth five of the mixing bevel gear five 48 is equal to the number of teeth of the inner gear teeth one of the mixing bevel gear one 35, and the planetary bevel gear 40 is respectively engaged with the inner gear teeth five of the mixing bevel gear five 48 and the inner gear teeth one of the mixing bevel gear one 35. The difference between the six teeth of the inner teeth of the modified mixing bevel gear 47 and the three teeth of the inner teeth of the mixing bevel gear three 36 is large, the six teeth of the inner teeth and the three teeth of the inner teeth are not in small tooth difference corresponding relation, the difference between the five teeth of the outer teeth of the mixing bevel gear five 48 and the one teeth of the outer teeth of the mixing bevel gear one 35 is large, and the five teeth of the outer teeth and the one teeth of the outer teeth are not in small tooth difference corresponding relation.

The inner gear teeth six of the deflection mixing bevel gear 47 are meshed with the outer gear teeth five of the mixing bevel gear five 48, the modulus of the inner gear teeth six of the deflection mixing bevel gear 47 and the modulus of the outer gear teeth five of the mixing bevel gear five 48 are four, the difference between the number of the inner gear teeth six of the deflection mixing bevel gear 47 and the number of the outer gear teeth five of the mixing bevel gear five 48 is defined as an eccentric distance gear difference four, a meshing eccentric distance three is arranged between the axis of the mixing bevel gear five 48 and the axis of the deflection mixing bevel gear 47, and the meshing eccentric distance three is equal to half of the product of the eccentric distance gear difference four and the modulus.

If the meshing eccentric distance III is larger than the meshing eccentric distance I, the axis of the mixing bevel gear five 48 is arranged on the lower side of the axis of the mixing bevel gear three 36, the difference between the meshing eccentric distance III and the axis eccentric distance III is the comprehensive eccentric distance III of the reference side shifting mixing bevel gear component, the comprehensive eccentric distance III is equal to the meshing eccentric distance I of the reference side mixing bevel gear component, the comprehensive eccentric distance III is equal to the eccentric distance between the output shaft axis 68 and the fixed cylinder axis 67, and the assembly condition that the mixing bevel gear I35, the mixing bevel gear five 48 and the output shaft 17 are coaxial is met.

When the modified mixed bevel differential speed reducer operates, if the same rotating speed is input into the modified mixed bevel differential speed reducer and the mixed bevel differential speed reducer respectively through the first input shaft 25, in the mixed bevel differential speed reducer, the number of the four outer gear teeth of the fourth mixed bevel gear 14 is equal to the number of the three outer gear teeth of the third mixed bevel gear 36, the rotating speed of the fourth mixed bevel gear 14 is equal to the rotating speed of the third mixed bevel gear 36, and due to the corresponding relation of the small gear difference I and the small gear difference II, the difference between the rotating speed of the second mixed bevel gear 15 and the rotating speed of the first mixed bevel gear 35 is small, so the transmission ratio of the mixed bevel differential speed reducer is large. In the modified hybrid bevel gear differential speed reducer, the six-tooth number of the outer teeth of the modified hybrid bevel gear 47 is smaller than the three-tooth number of the outer teeth of the hybrid bevel gear III 36, the rotating speed of the modified hybrid bevel gear 47 is greater than that of the hybrid bevel gear III 36, the torque is accelerated from the modified hybrid bevel gear 47 to the hybrid bevel gear V48, the meshing eccentric distance III is greater than the meshing eccentric distance I, if the modulus IV is equal to the modulus I, the eccentric distance tooth difference IV is greater than the eccentric distance tooth difference I, the transmission ratio between the modified hybrid bevel gear 47 and the hybrid bevel gear V48 is smaller than the transmission ratio between the hybrid bevel gear III 36 and the hybrid bevel gear I35, the difference between the rotating speed of the hybrid bevel gear V48 and the rotating speed of the hybrid bevel gear I35 is large, and the transmission ratio.

On the premise that the comprehensive eccentric distance three of the comparison side modified mixed bevel gear component is equal to the meshing eccentric distance one of the reference side mixed bevel gear component, the difference between the rotating speed of the fifth mixed bevel gear 48 and the rotating speed of the first mixed bevel gear 35 can be changed by changing the eccentric distance tooth difference three and the module three, or changing the eccentric distance tooth difference four and the module four, or changing the eccentric distance tooth difference one and the module one, and finally the transmission ratio of the modified mixed bevel gear differential speed reducer is changed.

Referring to fig. 1 to 7, 11 to 14, 18 and 19, a modified direct bevel differential reducer is composed of a modified direct bevel differential reducer in which the planet carrier members and the reference side hybrid bevel gear members are mounted at angles rotated one hundred and eighty degrees along the fixed cylinder axis 67 with the first hybrid bevel gear 35 axis on the upper side of the third hybrid bevel gear 36 axis, instead of the modified side hybrid bevel gear member in the hybrid bevel differential reducer. The deflection direct-connection bevel gear 55 is installed in the inner cavity of the eccentric ring II 61 through a bearing nine 60, the eccentric ring II 61 is installed in the left section 42 of the inner cavity of the fixed cylinder 27, one end of the fixed pin 54 is installed in the fixed pin hole I41 of the fixed cylinder 27, the other end of the fixed pin 54 is installed in the fixed pin hole II 78 of the eccentric ring II 61, the deflection direct-connection bevel gear 55 is not coaxial with the inner cavity of the fixed cylinder 27, the direct-connection bevel gear 56 is installed on the radial outer side, close to the left end, of the output shaft 17 through a shaft sleeve five 58, the left end journal of the output shaft 17 is installed in a bearing hole IV of the end cover IV 59 through a bearing eight 57, and.

The inside teeth of a cogwheel seven that directly links 56 axial inboard one end is the conical teeth of a cogwheel, and the other end that directly links 56 axial of bevel gear is the external spline, and inside teeth of a cogwheel seven is coaxial with the external spline, and the outside teeth of a cogwheel eight that directly links 55 radial outsides of gear that shifts is the conical teeth of a cogwheel, and the radial inboard of directly linking bevel gear 55 that shifts is the internal spline, and outside teeth of a cogwheel eight is coaxial with.

The eight teeth of the outer side teeth of the modified direct-connection bevel gear 55 are not equal to the three teeth of the outer side teeth of the third mixing bevel gear 36, the direction-changing bevel gear 22 is respectively meshed with the eight teeth of the outer side teeth of the modified direct-connection bevel gear 55 and the three teeth of the outer side teeth of the third mixing bevel gear 36, and the indexing cone angle of the direction-changing bevel gear 22 and the three indexing cone angle of the outer side teeth of the third mixing bevel gear 36 are obtained according to a method specified by a bevel gear standard, so that the eight indexing cone angle of the outer side teeth of the modified direct-connection bevel gear 55. If the eight teeth number of the outer side teeth of the modified direct-connection bevel gear 55 is smaller than the three teeth number of the outer side teeth of the third mixing bevel gear 36, the axis of the modified direct-connection bevel gear 55 is arranged on the upper side of the axis of the third mixing bevel gear 36.

The modulus of the outer gear teeth three of the direction-changing bevel gear 22 and the mixed bevel gear 36 and the modulus of the outer gear teeth eight of the modified direct-connected bevel gear 55 are modulus three, the difference between the number of the outer gear teeth three of the mixed bevel gear 36 and the number of the outer gear teeth eight of the modified direct-connected bevel gear 55 is defined as an eccentric distance gear difference five, and the axis eccentric distance four between the axis of the mixed bevel gear 36 and the axis of the modified direct-connected bevel gear 55 is equal to half of the product of the eccentric distance gear difference five and the modulus three.

The number of the inner teeth seven of the direct bevel gear 56 is equal to the number of the inner teeth one of the mixing bevel gear one 35, and the planetary bevel gear 40 is respectively meshed with the inner teeth seven of the direct bevel gear 56 and the inner teeth one of the mixing bevel gear one 35. The external splines of the direct-connection bevel gear 56 are arranged in the internal splines of the deflection direct-connection bevel gear 55, the direct-connection bevel gear 56 is coaxial with the deflection direct-connection bevel gear 55, the comprehensive eccentric distance IV of the comparison side deflection direct-connection bevel gear component is equal to the axis eccentric distance IV, the comprehensive eccentric distance IV is equal to the meshing eccentric distance I of the reference side mixing bevel gear component, the comprehensive eccentric distance IV is equal to the eccentric distance between the output shaft axis 68 and the fixed cylinder axis 67, and the coaxial assembling conditions of the mixing bevel gear 35, the direct-connection bevel gear 56 and the output shaft 17 are met.

When the modified direct-connection bevel gear differential speed reducer runs, if the same rotating speed is input into the modified direct-connection bevel gear differential speed reducer and the modified mixed bevel gear differential speed reducer respectively through the input shaft I25, in the modified direct-connection bevel gear differential speed reducer, the number of eight external teeth of a modified direct-connection bevel gear 55 is less than the number of three external teeth of a mixed bevel gear III 36, the rotating speed of the modified direct-connection bevel gear 55 is greater than that of the mixed bevel gear III 36, the rotating speed of a direct-connection bevel gear 56 is equal to that of the modified direct-connection bevel gear 55, so that the difference between the rotating speed of the direct-connection bevel gear 56 and the rotating speed of a mixed bevel gear I35 is large, and no acceleration transmission exists between the modified direct-connection bevel gear 55 and the direct-connection bevel gear 56, therefore, the transmission ratio of the modified direct-connected bevel differential speed reducer is between the mixed bevel differential speed reducer and the modified mixed bevel differential speed reducer.

On the premise that the comprehensive eccentric distance four of the comparison side modified direct-connection bevel gear component is equal to the meshing eccentric distance one of the reference side mixed bevel gear component, the eccentric distance tooth difference five and the module three are changed, or the eccentric distance tooth difference one and the module one are changed, the difference between the rotating speed of the direct-connection bevel gear 56 and the rotating speed of the mixed bevel gear one 35 can be changed, and finally the transmission ratio of the modified direct-connection bevel gear differential speed reducer is changed.

Referring to fig. 1 to 3, 5, 9 and 11, in the modified hybrid bevel differential speed reducer and the modified direct-coupled bevel differential speed reducer, the bevel gear 22 is replaced by a cylindrical gear D10, the outer gear tooth three of the hybrid bevel gear three 36 and the outer gear tooth four of the hybrid bevel gear four 14 of the general component, the outer gear tooth six of the modified hybrid bevel gear 47 of the modified hybrid bevel gear component on the contrast side and the outer gear tooth eight of the modified direct-coupled bevel gear 55 of the modified direct-coupled bevel gear component on the contrast side are replaced by end face gear teeth by conical gear teeth, so that one cylindrical gear can be engaged with two end face gears with different gear teeth respectively, the end face hybrid bevel differential speed reducer and the end face direct-coupled bevel differential speed reducer are formed respectively, and the transmission ratio range of the speed reducer is increased.

Taking the gear parameters in the attached drawings as examples, the module I, the module II, the module IV are equal to 1 mm, the module III is equal to 1.5 mm, the rotation speed of the change bevel gear 22 is equal to 100r/min, the tooth number Za0 of the change bevel gear 22 is equal to 18, the outer tooth number Za3 of the mixing bevel gear III 36 is equal to 50, the outer tooth number Za4 of the mixing bevel gear IV 14 is equal to 50, the inner tooth number Zb3 of the mixing bevel gear III is equal to 37, the outer tooth number Za1 of the mixing bevel gear I35 is equal to 29, the inner tooth number Zb4 of the mixing bevel gear IV 14 is equal to 36, the outer tooth number Za2 of the mixing bevel gear II 15 is equal to 28, the inner tooth number Zb6 of the modified mixing bevel gear 47 is equal to 34, the outer tooth number Za5 of the mixing bevel gear V48 is equal to 20, the outer tooth number Za6 of the modified mixing bevel gear 47 is equal to 46, the addendum modification direct-connected bevel gear 55 has eight external gear teeth Za8 equal to 45.

In the hybrid bevel differential speed reducer, the gear ratio i α = (Za 3 ÷ Za 0) × (Za 1 ÷ Zb 3) = (50 ÷ 18) × (29 ÷ 37) = 2.1772: 1 from the change bevel gear 22 to the reference-side hybrid bevel gear member,

the transmission ratio i β = (Za 4 ÷ Za 0) × (Za 2 ÷ Zb 4) = (50 ÷ 18) × (28 ÷ 36) = 2.1605: 1 of the change bevel gear 22 to the comparison side hybrid bevel gear member,

the rotational speed V1 of the mixing bevel gear wheel 35 is 100 r/min/2.177177 is 45.9306r/min,

the rotational speed V2 of the bevel gear mixer wheel two 15 is 100 r/min/2.160494 is 46.2856r/min,

the output shaft 17 of the hybrid bevel differential speed reducer has a rotation speed V3 ═ 0.1775r/min (46.2856 r/min-45.9306 r/min) ÷ 2,

the transmission ratio i1 of the hybrid bevel differential speed reducer is 100 r/min/0.1775 r/min ≈ 563: 1.

In the modified hybrid bevel differential speed reducer, the gear ratio i γ = (Za 6 ÷ Za 0) × (Za 5 ÷ Zb 6) = (46 ÷ 18) × (20 ÷ 34) = 1.5033: 1 from the change bevel gear 22 to the contrast side modified hybrid bevel gear part,

the rotational speed V4 of the mixing bevel gear five 48 is 100 r/min/1.5033 is 66.5203r/min,

the rotation speed V5 of the output shaft 17 of the modified mixed bevel differential speed reducer is (66.5203 r/min-45.9306 r/min) ÷ 2 is 10.2949r/min,

the transmission ratio i2 of the modified mixed bevel differential speed reducer is 100 r/min/10.2949 r/min which is approximately equal to 10: 1.

In the modified direct bevel differential reducer, the transmission ratio i epsilon = Za8 ÷ Za0=45 ÷ 18= 2.5: 1 of the change bevel gear 22 to the contrast side modified direct bevel gear component,

the rotating speed V6 of the direct-connected bevel gear 56 is 100 r/min/2.5 is 40r/min,

the rotating speed V7 of the output shaft 17 of the deflection direct-connection bevel gear differential speed reducer is (45.9306 r/min-40 r/min) ÷ 2 is 2.9653r/min,

the transmission ratio i of the deflection direct-connection bevel gear differential speed reducer is 100 r/min/2.9653 r/min and is approximately equal to 34: 1.

According to the case, the transmission ratio of the mixed bevel gear differential speed reducer is large, the transmission ratio of the shifted mixed bevel gear differential speed reducer is small, the transmission ratio of the shifted direct-connected bevel gear differential speed reducer is between the mixed bevel gear differential speed reducer and the shifted mixed bevel gear differential speed reducer, and the function that the transmission ratio can be changed by only replacing part of parts of products with the same specification is achieved.

In the differential speed reducer with the directly-connected shifted bevel gears, due to the limitation of eight teeth of the outer gear teeth of the directly-connected shifted bevel gear 55, if the difference between the axis eccentric distance four of the directly-connected shifted bevel gear component on the contrast side and the meshing eccentric distance one of the mixed bevel gear component on the reference side is smaller than half of the modulus three, the eight outer gear teeth simultaneously adopt a height shifting method to make up the difference.