Novel structure RV speed reducer
阅读说明：本技术 一种新型结构rv减速机 (Novel structure RV speed reducer ) 是由 顾京君 于 2020-07-24 设计创作，主要内容包括：本发明提供了一种新型结构RV减速机,涉及RV减速机技术领域,包括针齿壳、行星轮、偏心轴、输入轴、输出盘架、摆线轮,输出盘架包括输出轴盖和输出轴,行星轮安装在偏心轴上；行星轮与输入轴位于输出轴盖侧啮合,输出轴设置在输出轴盖另一侧；偏心轴圆周阵列设有三根,且每根偏心轴包括非凸轮轴和凸轮轴,凸轮轴直径为d3,非凸轮轴直径为d4；偏心轴轴心线与针齿壳轴线之间的距离为b且b＝8～123mm；减速机额定转矩为T,b×(d3)<Sup>2</Sup>＝(10～80)×T,b×(d4)<Sup>2</Sup>＝(6～40)×T；摆线轮上设有与凸轮轴一一对应的摆线轮轴承孔,摆线轮轴承孔直径为d1且d1＝(0.6～1.3)×b；针齿壳和摆线轮之间圆周阵列设有若干与其啮合的滚针,滚针中心圆直径为d2且d2＝(3～4)×b。本发明具有体积小、重量轻、减速比范围宽、大转矩等特点。(The invention provides an RV speed reducer with a novel structure, which relates to the technical field of RV speed reducers and comprises a pin gear shell, a planet wheel, an eccentric shaft, an input shaft, an output plate frame and a cycloid wheel, wherein the output plate frame comprises an output shaft cover and an output shaft; the planet gear is meshed with the input shaft at the side of the output shaft cover, and the output shaft is arranged at the other side of the output shaft cover; the eccentric shaft is circumferentially arrayed with threeEach eccentric shaft comprises a non-camshaft and a camshaft, the diameter of the camshaft is d3, and the diameter of the non-camshaft is d 4; the distance between the axial lead of the eccentric shaft and the axial lead of the pin gear shell is b, and b is 8-123 mm; rated torque of speed reducer T, b x (d3) 2 ＝(10～80)×T，b×(d4) 2 (6-40) x T; the cycloidal gear is provided with cycloidal gear bearing holes which correspond to the cam shaft one by one, the diameter of each cycloidal gear bearing hole is d1, and d1 is (0.6-1.3) x b; and a plurality of needle rollers meshed with the needle gear shell are arranged between the needle gear shell and the cycloid gear in a circumferential array, the diameter of a central circle of the needle rollers is d2, and d2 is (3-4) x b. The invention has the characteristics of small volume, light weight, wide reduction ratio range, large torque and the like.)
1. RV speed reducer with novel structureThe device comprises a needle gear shell (1), a planet wheel (4), an eccentric shaft (5), an input shaft (6), an output disc frame (7) and a cycloid wheel (3), wherein the output disc frame (7) comprises an output shaft cover (9) and an output shaft (8), and the planet wheel (4) is arranged on the eccentric shaft (5); the method is characterized in that: the planet gear (4) and the input shaft (6) are meshed at the side of the output shaft cover (9), and the output shaft (8) is arranged at the other side of the output shaft cover (9); the eccentric shafts (5) are circumferentially arrayed in three, each eccentric shaft (5) comprises a non-cam shaft (51) and a cam shaft (52) which are eccentric on the axis of the eccentric shaft, the diameter of each cam shaft (52) is d3, and the diameter of each non-cam shaft (51) is d 4; the distance between the axis of the eccentric shaft (5) and the axis of the needle gear shell (1) is b, and b is 8-123 mm; rated torque of the speed reducer is T, b x (d3)2＝(10～80)×T，b×(d4)2(6-40) x T; the cycloidal gear (3) is provided with cycloidal gear bearing holes (32) which correspond to cam shafts (52) on the eccentric shaft (5) one by one, the diameter of each cycloidal gear bearing hole (32) is d1, and d1 is (0.6-1.3) x b; a plurality of needle rollers (2) meshed with the needle gear shell (1) and the cycloid wheel (3) are arranged in a circumferential array mode, the diameter of a central circle of each needle roller (2) is d2, and d2 is (3-4) x b.
2. The RV reducer with the novel structure as claimed in claim 1, characterized in that: a cam needle roller and a retainer (10) which are connected with each other are arranged between the cycloid wheel bearing hole (32) and the camshaft (52) of the eccentric shaft (5), the load of the cam needle roller and the retainer (10) is Td, M retainer needle rollers (101) are arranged in the cam needle roller and the retainer (10), the diameter of the retainer needle roller (101) is Dwe, and the length of the retainer needle roller (101) is Lwe,and M is an integer;
3. The RV reducer with the novel structure as claimed in claim 2, characterized in that: the outer tooth number of the cycloid wheel (3) is Z1, the inner tooth number of the needle gear shell (1) is Z2, Z2 is Z1+1, and Z1 and Z2 are positive integers; the eccentricity of the non-camshaft (51) and the camshaft (52) on each eccentric shaft (5) on the axis of the eccentric shaft (5) is an eccentricity A, the short amplitude coefficient is Ki,wherein Ki is 0.45-0.85 and A is 0.33-3.88 mm.
4. The RV reducer with a novel structure as claimed in claim 3, characterized in that: the radial thickness of the pin gear shell (1) is P1, the inner tooth width of the pin gear shell (1) meshed with the cycloidal gear (3) is P2, the outer diameter of the pin gear shell (1) is c, wherein P1 is (0.13-0.28) x d2, c is d2+2P1, and P2 is 2G + (0.2-1).
5. The RV reducer with the novel structure as claimed in claim 4, characterized in that: three groups of tray frame table columns (71) are arranged on the output shaft (8) in a circumferential array, and the three groups of tray frame table columns (71) are connected with the output shaft cover (9) through N1 uniformly arranged table column bolts (72) and m taper pins (73); the column bolts (72) are Mj1 in specification, wherein j1 is the diameter of the column bolt (72), and the fastening force corresponding to each column bolt (72) with the specification of Mj1 is F1; the diameter of a pitch circle of N1 of the table column bolts (72) is D1, the fastening friction coefficient of the table column bolts (72) is mu and mu is 0.2, the torque transmitted by N1 of the table column bolts (72) is T1,
6. the RV reducer with the novel structure as claimed in claim 5, characterized in that: n4 pinion housing bolts (1101) are arranged on the pinion housing (1) in a circumferential array mode, and the axial direction of the pinion housing bolts (1101) is the same as the axial direction of the pinion housing (1); the gauge of the pin gear case bolt (1101) is Mj2, wherein j2 is the diameter of the pin gear case bolt (1101), and the corresponding fastening force of each pin gear case bolt (1101) with the gauge of Mj2 is F4; the diameter of a pitch circle of N4 of the pin gear shell bolts (1101) is D4, the fastening friction coefficient of the pin gear shell bolts (1101) is mu and mu is 0.2, the torque transmitted by N4 of the pin gear shell bolts (1101) is T4,
7. the RV reducer with the novel structure as claimed in claim 6, characterized in that: one side, far away from the output shaft cover (9), of the output shaft (8) is annularly provided with N5 output shaft mounting threaded holes (82) with the axial direction being the same as that of the needle gear shell (1), each output shaft mounting threaded hole (82) is internally provided with an output shaft bolt (83) with the specification of Mj3, wherein j3 is the diameter of the output shaft bolt (83), and the corresponding fastening force of each output shaft bolt (83) with the specification of Mj3 is F5; the diameter of a pitch circle of the N5 output shaft bolts (83) is D5, the fastening friction coefficient of the output shaft bolts (83) is mu and mu is 0.2, and the torque transmitted by the N5 output shaft bolts (83) isT5，Wherein D5 is (1.7-3.8) x b, N5 is an integer and
8. the RV reducer with the novel structure as claimed in claim 7, characterized in that: when the outer diameter c of the needle gear shell (1) is less than or equal to 130mm, a roller pin for non-cam and a retainer (12) are arranged between the output disc rack bearing hole (74) and the non-cam shaft (51) of the eccentric shaft (5), and a deep groove ball bearing (121) is arranged between the planet wheel (4) and the roller pin for non-cam and the retainer (12); when the outer diameter c of the needle gear shell (1) is larger than 130mm, a tapered roller bearing (13) is arranged between the output disc frame bearing hole (74) and the non-cam shaft (51) of the eccentric shaft (5).
9. The RV reducer with the novel structure as claimed in claim 8, characterized in that: the output disc frame (7) is provided with output disc frame bearing holes (74) which are in one-to-one correspondence with non-cam shafts (51) on the eccentric shaft (5) and an output disc frame center hole (75) which is positioned in the center of the output disc frame (7) and penetrates through the output disc frame, the diameter of each output disc frame bearing hole (74) is d5, the diameter of each output disc frame center hole (75) is a, the thinnest wall thickness between each output disc frame bearing hole (74) and the corresponding output disc frame center hole (75) is e, d5 is (0.65-1.3) x b, when the outer diameter c of the pin gear shell (1) is smaller than or equal to 130mm, d5-d4-d1+ d3 is larger than 0, and when the outer diameter c of the pin gear shell (1) is larger than 130mm, d5-d4-d1+ d3 is larger than; a is 2b-d5-2e, wherein e is more than or equal to 1.5 and a is more than 0.
10. The RV reducer of a new architecture according to any of claims 1-9, characterized in that: two angular contact ball bearings (11) are arranged between the outer wall of the output disc rack (7) and the inner wall of the pin gear shell (1), and the two cycloidal gears (3) are positioned between the two angular contact ball bearings (11); each angular contact ball bearing (11) comprises an inner ring channel (111), a steel ball (112), a bearing retainer (113) and a bearing outer ring (114), the steel ball (112) is mounted on the bearing retainer (113), the bearing outer ring (114) is mounted on the inner wall of the pin gear shell (1), and the inner ring channel (111) is arranged on the outer wall of the output disc rack (7) in a circular groove shape and is integrally formed with the output disc rack (7).
11. The RV reducer of a new architecture according to any of claims 1-9, characterized in that: be equipped with skeleton sealing washer oil blanket (14) between output shaft (8) outer wall and pin gear shell (1) hole, be equipped with on output shaft (8) the one end terminal surface of keeping away from output shaft lid (9) through hole (81) that link up with output plate rail dead eye (74), be equipped with cylindric oil blanket I (15) in through hole (81), be equipped with cylindric oil blanket II (16) in output plate rail centre bore (75) on output shaft (8).
Technical Field
The invention relates to the technical field of RV speed reducers, in particular to an RV speed reducer with a novel structure.
Background
The RV speed reducer is a novel speed reducer developed on the basis of cycloidal pin gear transmission, has the advantages of high rigidity, high precision, large torque, high transmission efficiency and the like, and has smaller volume and larger overload capacity compared with simple cycloidal pin gear planetary transmission.
The RV reducer comprises a middle-solid type RV reducer and a hollow type RV reducer, in the prior art, as shown in fig. 1 and fig. 2, the middle-solid type RV reducer comprises a pin gear housing 1, a
As shown in fig. 4, the hollow RV reducer includes a pin gear housing 1,
In summary, both the hollow RV reducer and the solid RV reducer in the prior art have problems of large volume, heavy weight, narrow reduction ratio range, inconvenient installation, and the like. The distance between the axis of the eccentric shaft and the axis of the pin gear shell is a main decisive factor of the external diameter of the speed reducer, the hollow RV speed reducer needs a larger central hole of the pin gear shell to install a through wire pipe for protecting a cable and assisting in sealing grease, the hollow RV speed reducer with a middle solid RV speed reducer and the hollow RV speed reducer with a slightly smaller structure are basically designed by two eccentric shafts and limited by processing capacity, precision, required torque capacity and the like, and the hollow type or the solid type can not make the volume of the speed reducer smaller on the premise of meeting certain torque capacity. Generally speaking, in the prior art, the distance between the axis of the eccentric shaft and the axis of the pin gear shell is normally between 22.5mm and 350mm, and can be designed to be more than 350mm but not less than 22.5mm according to requirements. Therefore, it is necessary to design a new structure RV reducer, which has the characteristics of small volume, light weight, compact structure, wide reduction ratio range, simple installation, large torque, etc.
Disclosure of Invention
The invention aims to provide an RV reducer with a novel structure, which has the characteristics of small volume, light weight, compact structure, wide reduction ratio range, simplicity in installation, large torque and the like.
The technical purpose of the invention is realized by the following technical scheme:
an RV reducer with a novel structure comprises a pin gear shell, a planet wheel, an eccentric shaft, an input shaft, an output disc frame and a cycloid wheel, wherein the output disc frame comprises an output shaft cover and an output shaft, and the planet wheel is arranged on the eccentric shaft; the planet gear is meshed with the input shaft at the side of the output shaft cover, and the output shaft is arranged at the other side of the output shaft cover; the eccentric shafts are circumferentially arrayed in three, each eccentric shaft comprises a non-cam shaft and a cam shaft which are eccentric on the axis of the eccentric shaft, the diameter of each cam shaft is d3, and the diameter of each non-cam shaft is
Through adopting above-mentioned technical scheme, distance b between eccentric shaft axial lead and the pin gear shell axis is the main decisive factor of speed reducer external diameter size, for guaranteeing the torque when reducing b, increases the quantity of eccentric shaft, sets up the eccentric shaft into three, reduces camshaft diameter d3 and non-camshaft diameter d4 on the eccentric shaft simultaneously, and then reaches and both reduces the speed reducer external diameter and guarantees great torque again. And selecting the required rated torque T and a proper b value, calculating the size values of other parts according to a formula, and repeatedly calculating in the calculation process, for example, returning to reselect the corresponding value or range if the calculation result is not accordant with the requirement. The RV reducer designed by the invention has small overall dimension, light weight and large torque, the overall dimension can be reduced by about 20% under the same torque, and the weight can be reduced by 35%. The planet gear is arranged on the side of the input shaft cover and is positioned on the same side with the input shaft, the output shaft cover is not a non-sealing surface but a motor mounting surface, when the motor mounting flange is fixed on the pin gear shell, the O-shaped ring and the framework sealing ring are used for oil sealing, the planet gear can be simultaneously sealed, the output end does not need to take corresponding sealing measures for sealing the planet gear, and the sealing requirement on the output end is simplified. In addition, the input shaft and the planet wheel are meshed at the same side, the axial length of the input shaft connected with the motor is short, the RV reducer with a compact axial direction can be obtained more easily, and the precision of a first-stage planet reducing mechanism formed by the input shaft and the planet wheel is effectively improved. Besides, the planet wheel sets up in output shaft cover one side and all unsettled with output shaft cover axial and radial, and the external diameter of planet wheel does not receive the output shaft restriction, and the input shaft external diameter is not restricted by the speed reducer body, makes the speed reducer speed reduction ratio scope of design wider like this.
Furthermore, a cam needle roller and a retainer which are connected with each other are arranged between the cycloid wheel bearing hole and the camshaft of the eccentric shaft, the load of the cam needle roller and the retainer is Td, M retainer needle rollers are arranged in the cam needle roller and the retainer, the diameter of the retainer needle roller is Dwe, the length of the retainer needle roller is Lwe,
By adopting the technical scheme, when the outer diameter of the cam shaft on the eccentric shaft is reduced, the bearing hole of the cycloid wheel is connected with the cam shaft on the eccentric shaft through the needle roller for the cam and the retainer, three needle rollers for the cam on each cycloid wheel and three retainers are arranged, when the pitch circle (the radius is b) of the eccentric shaft is reduced,the bearing capacity of the cam needle rollers and the retainer is improved by increasing the number of the cam needle rollers and the retainer and the axial length of the cam needle rollers and the retainer, which is determined by the length Lwe of the cam needle rollers and the retainer needle rollers on the retainer. Further, the outer diameter of the cycloid gear is reduced by reducing the diameter Dwe of the cam needle roller and the cage needle roller on the cage or by making the outer diameter smaller, and the outer diameter of the RV reducer is further reduced. Wherein, the formula for calculating the load Td of the needle roller and the retainer for the camFor the calculation formula of the bearing load in the prior art, fc is a coefficient specified according to the shape, machining precision and material of each part of the bearing, andin connection withThe values of (a) are selected accordingly. In addition, the meshing area between the outer teeth of the cycloid wheel and the inner teeth of the pin gear shell and the contact area between the cycloid wheel and the cam shaft on the eccentric shaft are increased by increasing the thickness G of the cycloid wheel, so that the cycloid wheel can bear large torque, and the aim of outputting the same torque is fulfilled.
Further, the outer tooth number of the cycloid wheel is Z1, the inner tooth number of the needle gear shell is Z2, Z2 is Z1+1, and Z1 and Z2 are positive integers; the eccentricity of the non-camshaft on each eccentric shaft and the camshaft on the axis of the eccentric shaft is an eccentricity A, the short amplitude coefficient is Ki,wherein Ki is 0.45-0.85 and A is 0.33-3.88 mm.
By adopting the technical scheme, the external tooth number Z1 of the cycloid wheel is determined, the internal tooth number of the pin gear shell is determined according to the Z2-Z1 +1, and the meshing between the external tooth of the cycloid wheel and the internal tooth of the pin gear shell is ensured. The reduction of the outer diameter of the pin gear shell can increase the short amplitude coefficient, and the reduction is needed to be properly reduced to avoid the influence of the short amplitude coefficient on the deceleration performanceEccentricity A, which is the eccentricity of the camshaft on the eccentric shaft and the amount of eccentricity of the camshaft on the axis of the eccentric shaft, according to the formula
Further, the radial thickness of the pin gear shell is P1, the inner tooth width of the pin gear shell meshed with the cycloid gear is P2, and the outer diameter of the pin gear shell is c, wherein P1 is (0.13-0.28).
By adopting the technical scheme, the radial thickness of the pin gear shell is properly reduced or maintained on the premise that the radial thickness P1 of the pin gear shell meets the requirement of large torque, and the outer diameter c of the pin gear shell is further reduced, so that the speed reducer with smaller volume and smaller pitch circle is obtained. On the premise of ensuring that the cycloidal gear is normally installed on the pin gear shell, the internal tooth width P2 of the pin gear shell is properly reduced, and the speed reducer with smaller volume is obtained.
Furthermore, three groups of disc rack table columns are arranged on the output shaft in a circumferential array, and the three groups of disc rack table columns are connected with the output shaft cover through N1 uniformly arranged table column bolts and m taper pins; the column bolts are Mj1 in specification, wherein j1 is the diameter of each column bolt, and the fastening force corresponding to each column bolt with the specification of Mj1 is F1; the distributed pitch circle diameter of N1 column bolts is D1, the fastening friction coefficient of the column bolts is mu, mu is 0.2, the torque transmitted by N1 column bolts is T1,wherein D1 is (2-2.8) x b and N1 is an integer; the diameter of the taper pin is D6, the distributed pitch circle diameter of m taper pins is D2, the shearing stress of each taper pin (73) is tau, the torque transmitted by m taper pins is T2,wherein D2 is (1.4-2.9) x b and m is an integer; the total torque transmitted by the N1 column bolts and the m taper pins is T3, T3 is T1+ T2 and
through adopting above-mentioned technical scheme, column bolt and taper pin connection plate rail column and output shaft lid realize becoming output plate rail wholly with output shaft lid and output shaft connection. The pitch circle diameters of the column bolts and the taper pins are reduced along with the reduction of the outer diameter of the speed reducer, and in order to bear the same torque, the number of the column bolts and the taper pins is increased, and the number of the tray frame columns is increased from two groups to three groups, so that the shearing capacity of the tray frame columns is increased. Selecting an appropriate number N1 of column bolts and an appropriate specification Mj1 according to the size of the speed reducer, determining the corresponding fastening force F1 of the column bolts when the strength grade is 11.9 according to the specification Mj1 of the column bolts, selecting an appropriate distributed pitch circle diameter D1 of the column bolts according to D1 ═ 2-2.8 x b, and then selecting an appropriate distributed pitch circle diameter D1 of the column bolts according to a formula
Furthermore, N4 pin gear shell bolts are arranged on the pin gear shell in a circumferential array mode, and the axial direction of the pin gear shell bolts is the same as the axial direction of the pin gear shell; the specification of the pin gear shell bolt is Mj2, wherein j2 is the diameter of the pin gear shell bolt, and the corresponding fastening force of each pin gear shell bolt with the specification of Mj2 is F4; the diameter of a pitch circle of N4 pin gear shell bolts is D4, the fastening friction coefficient of the pin gear shell bolts is mu and mu is 0.2, the torque transmitted by N4 pin gear shell bolts is T4,
through adopting above-mentioned technical scheme, the pinion housing bolt specification of installation reduces but quantity increase also can satisfy the distribution pitch circle of pinion housing bolt and reduce the moment of torsion unchangeable simultaneously on the pinion housing, reduces the aperture of pinion housing mounting hole on the pinion housing promptly and increases the quantity of pinion housing mounting hole, guarantees great moment of torsion simultaneously, and this is also a feasible factor that reduces speed reducer excircle size. Firstly, selecting proper specification Mj2 and number N4 of the pin gear shell bolts, then determining the corresponding fastening force F4 of the pin gear shell bolts with the strength grade of 11.9 according to the specification Mj2 of the pin gear shell bolts, selecting proper distribution pitch circle diameter D4 of the pin gear shell bolts according to D4-c-j 2- (2-10), and then selecting proper distribution pitch circle diameter D4 of the pin gear shell bolts according to a formula
Furthermore, one side of the output shaft, which is far away from the output shaft cover, is annularly provided with N5 output shaft mounting threaded holes, the axial direction of which is the same as the axial direction of the pin gear shell, each output shaft mounting threaded hole is internally provided with an output shaft bolt with the specification of Mj3, wherein j3 is the diameter of the output shaft bolt, and the corresponding fastening force of each output shaft bolt with the specification of Mj3 is F5; the distributed pitch circle diameter of N5 output shaft bolts is D5, the fastening friction coefficient of the output shaft bolts is mu, mu is 0.2, the torque transmitted by N5 output shaft bolts is T5,
through adopting above-mentioned technical scheme, the output shaft bolt plays and connects fixed action, and output shaft installation screw hole is used for installing the output shaft bolt, and when output shaft installation screw hole pitch circle reduced, but output shaft installation screw hole's quantity greatly increased, output shaft bolt quantity greatly increased promptly guarantees to transmit great moment of torsion. Similarly, selecting proper specification Mj3 and number N5 of output shaft bolts, determining fastening force F5 corresponding to the output shaft bolts when the strength grade is 11.9 according to the specification Mj3 of the output shaft bolts, selecting proper distributed pitch circle diameter D5 of the output shaft bolts according to D5 ═ 1.7-3.8 x b, and then selecting proper distributed pitch circle diameter D5 of the output shaft bolts according to a formulaAnd calculating the torque transmitted by N5 output shaft bolts, wherein mu is the friction coefficient when the pillar bolts are fastened in a surface grease-free state. According to
Further, when the outer diameter c of the pin gear shell is less than or equal to 130mm, a roller pin for non-cam and a retainer are arranged between the bearing hole of the output disc frame and a non-cam shaft of the eccentric shaft, and a deep groove ball bearing is arranged between the planet wheel and the roller pin for non-cam and the retainer; when the outer diameter c of the pin gear shell is larger than 130mm, a tapered roller bearing is arranged between the output disc frame bearing hole and the non-cam shaft of the eccentric shaft.
By adopting the technical scheme, the non-cam needle rollers and the retainer or the tapered roller bearing are arranged between the bearing hole of the output disc frame and the non-cam shaft of the eccentric shaft, and the number of the non-cam needle rollers and the retainer or the tapered roller bearing is also matched with that of the eccentric shaft to form three pairs, so that when the pitch circle of the eccentric shaft is reduced, the radial thickness of the non-cam needle rollers and the retainer or the tapered roller bearing is not changed, and larger torque can be transmitted. When the outer diameter c of the pin gear shell is larger than 130mm, the tapered roller bearing is arranged between the bearing hole of the output disc frame and the non-cam shaft of the eccentric shaft, the eccentric shaft can be limited on the output disc frame only by using the tapered roller bearing, the eccentric shaft is prevented from axially jumping or even separating from the output disc frame, and the structure of the speed reducer is effectively simplified. When the outer diameter c of the needle gear shell is less than or equal to 130mm, because the prior art can not manufacture smaller tapered roller bearings, a needle roller for non-cam and a retainer are arranged between a bearing hole of the output disk rack and a non-cam shaft of the eccentric shaft, a deep groove ball bearing is arranged between the planet wheel and the needle roller for non-cam and the retainer, the needle roller for non-cam and the retainer and the deep groove ball bearing are used for replacing the tapered roller bearing, the same effect as the tapered roller bearing is achieved, and the eccentric shaft is limited on the output disk rack.
Furthermore, the output disc frame is provided with output disc frame bearing holes which are in one-to-one correspondence with non-cam shafts on the eccentric shafts and an output disc frame center hole which is positioned in the center of the output disc frame and penetrates through the output disc frame, the diameter of each output disc frame bearing hole is d5, the diameter of each output disc frame center hole is a, the thinnest wall thickness between each output disc frame bearing hole and each output disc frame center hole is e, d5 is (0.65-1.3) x b, when the outer diameter c of the pin gear shell is less than or equal to 130mm, d5-d4-d1+ d3 is more than 0, and when the outer diameter c of the pin gear shell is more than 130mm, d5-d4-d1+ d3 is more than 6; a is 2b-d5-2e, wherein e is more than or equal to 1.5 and a is more than 0.
By adopting the technical scheme, the central hole of the output disc frame mainly reduces the weight of the speed reducer or uses an input shaft needing to be supported as a support hole, the smaller the diameter a of the central hole of the output disc frame is, the closer the diameter a is to the limit of small volume and large torque of the speed reducer, but the thinnest wall thickness e between the bearing hole of the output disc frame and the central hole of the output disc frame is ensured, so that the output disc frame can bear certain torque. Therefore, the diameter a of the central hole of the output disc frame is determined according to the d5 which is equal to (0.65-1.3) multiplied by b, the a which is equal to 2b-d5-2e, and the e which is equal to or more than 1.5, and the requirement that a is larger than 0 is met, the size of the speed reducer is reduced, and the speed reducer can meet the requirement of torque. When the outer diameter c of the pin gear shell is less than or equal to 130mm, d5-d4-d1+ d3 is more than 0, namely the space between the bearing hole of the output disc carrier and the non-camshaft is larger than the space between the bearing hole of the cycloid wheel and the camshaft, and the mounted non-cam roller pin and the mounted retainer as well as the cam roller pin and the cam retainer can meet the torque requirement of the speed reducer; when the outer diameter c of the needle gear shell is larger than 130mm, d5-d4-d1+ d3 is larger than 6, namely, the diameter and the number of the needle rollers in the outer ring and the inner ring of the tapered roller bearing can be larger or more than those of the needle rollers and the retainer for the cam under the condition that the outer ring and the inner ring of the tapered roller bearing have certain thicknesses, so that the torque requirement of the speed reducer is met.
Furthermore, two angular contact ball bearings are arranged between the outer wall of the output disc rack and the inner wall of the pin gear shell, and the two cycloidal gears are positioned between the two angular contact ball bearings; each angular contact ball bearing comprises an inner ring channel, a steel ball, a bearing retainer and a bearing outer ring, wherein the steel ball is arranged on the bearing retainer, the bearing outer ring is arranged on the inner wall of the pin gear shell, and the inner ring channel is arranged on the outer wall of the output plate rack in a circular groove shape and is integrally formed with the output plate rack.
By adopting the technical scheme, the outer diameter of the RV reducer is reduced, the angular contact ball bearing bears the moment and the thrust of the RV reducer, and the angular contact ball bearing is arranged to be composed of the inner ring channel, the steel ball, the bearing retainer and the bearing outer ring for obtaining the constant moment and thrust. The outer circular groove is arranged on the outer wall of the output disc frame and serves as an inner ring channel, so that the output disc frame body obtains higher rigidity, the diameter of a steel ball in the angular contact ball bearing is increased as much as possible, in addition, under the condition of enough space, a bearing retainer of the angular contact ball bearing is more compact, a bearing outer ring is arranged on the inner wall of the pin gear shell, the semi-open and semi-closed angular contact ball bearing is formed, and therefore higher torque and thrust are obtained.
Furthermore, a framework seal ring oil seal is arranged between the outer wall of the output shaft and the inner hole of the pin gear shell, a through hole communicated with a bearing hole of the output disc frame is formed in the end face, far away from the output shaft cover, of the output shaft, a cylindrical oil seal I is arranged in the through hole, and a cylindrical oil seal II is arranged in a central hole of the output disc frame on the output shaft.
By adopting the technical scheme, the output shaft is used as the output end of the RV speed reduction, the output end surface is in a full-sealed state and is provided with three oil seals, firstly, the framework sealing ring oil seal between the excircle of the output shaft and the inner hole of the pin gear shell, the framework sealing ring oil seal plays a role in dynamic sealing due to the relative motion of the output shaft and the pin gear shell, and the framework sealing ring oil seal has large axial space, so that the sealing under a more severe environment can be realized by increasing the quantity of the framework sealing ring oil seals or designing various sealing modes such as lip openings, and the like, the damage caused by the fact that external environment substances enter the RV speed reducer is prevented; the three through holes corresponding to the positions where the eccentric shafts are arranged on the output shaft are sealed by a cylindrical oil seal I, belonging to static seal; thirdly, the central hole of the output disk frame on the output shaft is sealed by a cylindrical oil seal II, and the output disk frame also belongs to static seal. One dynamic seal and two static seals realize the convenience of the output end in use, and complicated modes such as sealing glue are not needed for sealing.
In conclusion, the invention has the following beneficial effects:
1. the RV reducer has small overall dimension and large torque, and the overall dimension of the RV reducer can be reduced by about 20% under the same torque;
2. the RV reducer is light in weight and large in torque, and the weight of the RV reducer can be reduced by 35% under the same torque;
3. the number of the eccentric shafts is increased to three, the outer diameter d3 of the cam shaft on the eccentric shafts and the outer diameter d4 of the non-cam shaft are reduced, and the outer diameter of the RV reducer is reduced while large torque is kept;
4. the thickness G of the cycloidal gear is increased, the length of the roller pin and the thickness of the inner teeth of the pin gear shell are increased along with the thickness, the meshing area of the outer teeth of the cycloidal gear, the roller pin and the inner teeth of the pin gear shell is increased, and the external diameter of the RV speed machine is reduced while a larger torque is kept;
5. the number of the cam needle rollers and the retainer is increased to three, the length Lwe of the cam needle rollers and the retainer needle rollers in the retainer is increased, namely the axial length of the cam needle rollers and the retainer is increased, and as the thickness G of the cycloid wheel is increased and the number of the eccentric shafts is increased, the number of the cam needle rollers, the number of the retainer and the axial length between the eccentric shafts and the cycloid wheel are correspondingly increased, so that the load capacity of the cam needle rollers and the retainer is increased, the outer diameter of the RV reducer is reduced, and a larger torque is maintained;
6. the eccentricity A is reduced to obtain a proper short-amplitude coefficient Ki, high meshing efficiency is kept, meanwhile, large torque in the direction of the external tooth resultant force of the meshing cycloidal gear is obtained, meshing is stable and does not interfere, and the external diameter of the RV reducer is reduced while large torque is kept;
7. the smaller the diameter a of the central hole of the output disc frame is, the closer the diameter a is to the limit of the small volume and the large torque of the RV reducer;
8. the thickness G of the cycloid wheel is increased, the axial thickness of an external tooth meshing part of the pin gear shell is also increased, the radial thickness P1 is unchanged or properly reduced while the outer diameter c of the pin gear shell is reduced, and the outer diameter of the RV reducer is reduced while large torque is kept;
9. when the number of the eccentric shafts is increased, the number of the disc rack table posts on the output disc rack is increased, and the number of the table post bolts and the number of the taper pins on the disc rack table posts are correspondingly increased, so that the external diameter of the RV reducer is reduced while a larger torque is kept;
10. the aperture of the pin gear shell mounting holes on the pin gear shell is reduced and the number of the pin gear shell mounting holes is increased, so that the specification of the installed pin gear shell bolts is reduced and the number of the installed pin gear shell bolts is increased, the radial thickness P1 of the pin gear shell is reduced, and the external diameter of the RV reducer is reduced while larger torque is ensured;
11. when the number of the eccentric shafts is increased, the number of the non-cam needle rollers for supporting the output disc frame and the number of the retainer or the tapered roller bearing are also increased, so that the outer diameter of the RV reducer is reduced, and a larger torque is kept;
12. the outer circular groove is arranged on the outer wall of the output disc frame and serves as an inner ring channel of the angular contact ball bearing, so that the rigidity of the output disc frame is increased, the rigidity of the angular contact ball bearing is enhanced, the outer diameter of the output disc frame is reduced, the outer diameter of a steel ball of the angular contact ball bearing is larger, and the outer diameter of the RV reducer is reduced while larger torque and thrust are kept;
13. the output end face of the output shaft side is in a full-sealing state, and two static seals and one dynamic seal are arranged, wherein the axial space of the dynamic seal is large, the number of framework seal ring oil seals can be increased or sealing modes such as various lips are designed, the sealing performance is greatly increased, the sealing of the RV reducer in a severe environment is realized, the use is convenient, the complicated operations such as traditional glue sealing are not needed, and the sealing effectiveness is higher;
14. because the planet wheel and the output shaft are respectively arranged at two sides and do not influence each other, the output shaft can be easily used as an output end for output and can also be used as a fixed end for fixation;
15. the output shaft is used as an output end face, and the excircle of the output shaft and the central hole of the output plate frame can be used as positioning excircles or positioning holes, so that mounting and positioning diversity is realized;
16. the output shaft cover side is a non-sealing surface and is also a motor mounting surface, the motor mounting flange is fixed with the pin gear shell, the input shaft and the motor mounting flange are sealed through a motor mounting flange hole skeleton sealing ring oil seal, the motor only needs to be directly inserted into the input shaft and fixed to complete mounting, the motor is convenient and fast to mount, the length of the input shaft is short, the axial thickness of the motor in mounting is correspondingly reduced, the axial structure is compact, the gear meshing precision is high, and the noise is low;
17. the meshing tooth number range of the planetary gear and the input shaft is wide, the total reduction ratio range of the RV reducer is wide, and 5-250 total reduction ratios can be realized only by changing the tooth number relationship between the input shaft and the planetary gear; the number of the eccentric shafts is increased, the thickness of the planet wheels is increased, the diameter of the external spline of the eccentric shafts can be reduced, the planet wheels can obtain smaller or larger diameters, and the outer diameter of the gear on the input shaft is limited by the size of the center distance b of the speed reducer.
Drawings
FIG. 1 is a schematic diagram of a prior art deceleration configuration for a solid RV;
FIG. 2 is a schematic diagram of an output end structure of a solid RV reducer in the prior art;
FIG. 3 is a schematic view of a prior art mounting configuration for a solid RV deceleration;
FIG. 4 is a schematic diagram of a prior art hollow RV deceleration configuration;
FIG. 5 is a schematic view of a prior art mounting configuration for hollow RV deceleration;
fig. 6 is a schematic diagram of an overall structure of a RV reducer with a novel structure according to one to four embodiments;
fig. 7 is a schematic diagram of an input end structure of an RV reducer with a novel structure in one to twelve embodiments;
fig. 8 is a schematic structural diagram of an eccentric shaft of an RV reducer with a novel structure in one to twelve embodiments;
fig. 9 is a schematic structural view of an output plate frame of an RV reducer with a novel structure according to one to twelve embodiments;
fig. 10 is a schematic structural view of a cycloid wheel of an RV reducer having a novel structure in one to twelve embodiments;
fig. 11 is a schematic view of an installation structure of a RV reducer with a novel structure in the first to fourth embodiments;
fig. 12 is a schematic structural diagram of an output end of an RV reducer with a novel structure in one to twelve embodiments;
fig. 13 is a schematic view of an overall structure of an RV reducer having a novel structure according to a fifth embodiment to a twelfth embodiment;
fig. 14 is a schematic structural view of a needle roller and a cage for a cam of an RV reducer with a novel structure according to one to twelve embodiments;
fig. 15 is a sectional view of a cycloid wheel of a RV reducer of a novel structure in one to twelve embodiments;
fig. 16 is a sectional view of a pin gear housing of an RV reducer of a novel structure according to one to twelve embodiments;
fig. 17 is a front view of a pin gear housing of an RV reducer having a novel structure according to one to twelve embodiments.
In the figure, 1, a needle gear shell; 110. a needle gear housing mounting hole; 1101. a pin gear housing bolt; 1102. inner teeth of the pin gear shell; 2. rolling needles; 3. a cycloid wheel; 31. external teeth of the cycloid wheel; 32. a cycloid wheel bearing hole; 33. a center hole of the cycloid wheel; 34. a pillar hole; 4. a planet wheel; 5. an eccentric shaft; 51. a non-camshaft; 52. a camshaft; 6. an input shaft; 61. a duplicate gear; 7. an output tray frame; 71. a tray frame column; 72. a pillar bolt; 73. a taper pin; 74. an output tray bearing bore; 75. a central hole of the output tray frame; 8. an output shaft; 81. a through hole; 82. the output shaft is provided with a threaded hole; 83. an output shaft bolt; 9. an output shaft cover; 10. a needle roller for a cam and a retainer; 101. a cage needle roller; 11. angular contact ball bearings; 111. an inner race channel; 112. a steel ball; 113. a bearing retainer; 114. a bearing outer race; 12. a needle roller for non-cam and a cage; 121. a deep groove ball bearing; 13. a tapered roller bearing; 14. a framework seal ring oil seal; 15. a cylindrical oil seal I; 16. a cylindrical oil seal II; 17. installing a flange on the motor; 18. an input end skeleton sealing ring; 19. an O-shaped ring; 20. an output end flange; 21. an electric motor.
Detailed Description
The present invention will be described in further detail with reference to the following drawings and examples. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.
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