CN111895045A

CN111895045A - Novel structure RV speed reducer

Info

Publication number: CN111895045A
Application number: CN202010724501.XA
Authority: CN
Inventors: 顾京君
Original assignee: Nantong Zhenkang Welding Electromachinery Co ltd; NANTONG ZHENKANG MACHINERY CO Ltd
Current assignee: Nantong Zhenkang Welding Electromachinery Co ltd; NANTONG ZHENKANG MACHINERY CO Ltd
Priority date: 2020-07-24
Filing date: 2020-07-24
Publication date: 2020-11-06
Anticipated expiration: 2040-07-24
Also published as: CN111895045B

Abstract

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.

Description

Novel structure RV speed reducer

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 needle roller 2, a cycloid wheel 3, a planet wheel 4, an eccentric shaft 5, an input shaft 6, an output disc rack 7, an output shaft 8, an output shaft cover 9 and the like, the planet wheel 4 is installed on the eccentric shaft 5, the output shaft 8 and the planet wheel 4 are located on the same side, the planet wheel 4 is concavely arranged on the output shaft 8, and the input shaft 6 is arranged on the opposite side of the output shaft 8. The medium-solid RV reducer is large in size and heavy in weight, and because the planet wheel 4 is concavely arranged on the output shaft 8, the reduction ratio range is limited by the size of the outer circle of the output shaft 8 and the size of a mounting hole on the output shaft 8; because the input shaft 6 penetrates through the speed reducer body, the length of the input shaft 6 is required to be longer, and the gear outer diameter of the input shaft 6 is limited by the central hole 75 of the output disc frame, the reduction ratio range is narrow, and the gear meshing precision is poor; in addition, the reducer planet wheels 4 and the eccentric shafts 5 are only provided with two groups, so that the capacity of the eccentric shafts 5 for transmitting torque on the same pitch circle is reduced. As shown in fig. 3, when the medium-sized RV reducer is installed, an output end flange 20 needs to be fixed on an output end, a motor installation flange 17 is installed on an input end, a planet wheel 4 on an output end surface of an output shaft side is concave to an output shaft 8, and the whole plane needs to be sealed by adopting sealing glue, a skeleton sealing ring oil seal 14, an input end skeleton sealing ring 18 and other sealing modes, so that the installation is complicated.

As shown in fig. 4, the hollow RV reducer includes a pin gear housing 1, needle rollers 2, a cycloid gear 3, planet wheels 4, an eccentric shaft 5, a duplicate gear 61, an input shaft 6, an output disc rack 7, an output shaft 8, an output shaft cover 9, etc., the planet wheels 4 are mounted on the eccentric shaft 5, the input shaft 6 and the planet wheels 4 are located on the same side and connected through the duplicate gear 61, and the output shaft 8 is disposed on the opposite side of the input shaft 6. The hollow type RV speed reducer input is duplicate gear 61 structure, and the reduction ratio is generally great, and the reduction ratio scope is narrow, because the centre bore of speed reducer installation output shaft 8 is too big and input shaft 6 eccentric mounting outwards, leads to the speed reducer bulky and weight heavy. As shown in fig. 5, when the hollow RV reducer is installed, the output end and the input end are simultaneously sealed, and the sealing is basically performed by using an input end skeleton sealing ring 18 or an O-ring 19, when the motor mounting flange 17 is installed at the input end, the motor mounting flange 17 is complicated to manufacture and install due to the structure of the input end; in addition, the hollow RV reducer has a large cavity space and is filled with a large amount of grease, which results in high manufacturing and use costs of the hollow RV reducer.

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 d 4; the distance between the axial lead of the eccentric shaft and the axial lead of the needle gear shell is b, and the 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 is provided with cycloidal gear bearing holes which correspond to cam shafts on the eccentric 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 mode, the diameter of a central circle of the needle rollers is d2, and d2 is (3-4) x b.

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,

and M is an integer;

where bm is 1.1 and fc is and

the coefficients of interest; the thickness G of the cycloid wheel is (0.8-1.8) multiplied by 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 cam

For 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, and

in connection with

The 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

And Ki is 0.45 ~ 0.85, A is 0.3 ~ 3.88mm, selects suitable short width coefficient, calculates the eccentricity A, when obtaining big torque cycloid wheel external tooth, guarantees that the meshing efficiency between cycloid wheel external tooth and kingpin and the pin tooth shell internal tooth is high and do not take place to interfere.

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). times.d 2, c is d2+2P1, and P2 is 2G + (0.2-1).

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

And calculating the torque transmitted by N1 column bolts, wherein mu is the friction coefficient when the column bolts are fastened in a surface grease-free state. Selecting proper taper pins according to taper pin materials, hardness and the like, selecting proper taper pin diameters D6, the number m and the shear stress tau, selecting proper taper pin distribution pitch circle diameters D2 according to a formula D2 ═ 1.4-2.9 x b, and then selecting proper taper pins according to a formula

Determining the torque transmitted by the m taper pins, and finally passing T3-T1 + T2

And judging whether the calculation of the T1 and the T2 can enable the total torque T3 to meet the judgment condition, if not, adjusting the selection of the data related to the table stud, and if not, adjusting the selection of the data related to the taper pin until the total torque T3 meets the judgment condition. The number and the specification of the column bolts and the taper pins are determined to ensure the column boltsThe bolt and taper pin can meet the torque requirement when connecting the tray frame column and the output shaft cover.

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,

wherein D4 is c-j2- (2-10), N4 is an integer and

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

The torque transmitted by N4 pin-shell bolts is calculated, wherein mu is the friction coefficient when the pillar bolt is fastened under the condition of no grease on the surface. According to

And judging whether the torque of the pin gear shell bolt meets the condition, and if not, adjusting and selecting the related data of the pin gear shell bolt until the torque T4 meets the condition.

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,

wherein D5 is (1.7-3.8) x b, N5 is an integer and

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 formula

And 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

And judging whether the torque of the output shaft bolt meets the condition, and if not, adjusting and selecting the relevant data of the output shaft bolt until the torque T5 meets the condition.

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.

The first embodiment is as follows:

the utility model provides a novel structure RV speed reducer, as shown in figure 6, the essential element includes the pin gear shell 1, the planet wheel 4, eccentric shaft 5, input shaft 6, output plate rail 7, two cycloidal gears 3 etc, two cycloidal gears 3 and output plate rail 7 are installed in the pin gear shell 1, output plate rail 7 is including the output shaft lid 9 and the output shaft 8 that are located 1 axial both sides of pin gear shell respectively, and two cycloidal gears 3 are located between output shaft lid 9 and the output shaft 8, be equipped with a plurality of kingpins 2 rather than the meshing between every cycloidal gear 3's cycloidal gear external tooth 31 and the pin gear shell internal tooth 1102. As shown in fig. 7 and 8, the eccentric shafts 5 are axially arranged along the pin gear housing 1 and circumferentially arrayed in three, each eccentric shaft 5 includes a non-cam shaft 51 and a cam shaft 52 which are eccentric on the axis thereof, as shown in fig. 6, 9 and 10, the output shaft cover 9 and the output shaft 8 are respectively provided with an output disc frame bearing hole 74 which is matched with the non-cam shaft 51 of the eccentric shaft 5, two cycloidal gears 3 are respectively provided with a cycloidal gear bearing hole 32 which is matched with the cam shaft 52 of the eccentric shaft 5, and a needle roller for connecting the cycloidal gear bearing hole 32 and the cam shaft 52 of the eccentric shaft 5 and a retainer 10 are arranged between the cycloidal gear bearing hole 32 and the cam shaft 52 of the eccentric shaft 5.

As shown in fig. 6 and 7, the planetary gear 4 and the input shaft 6 are engaged on the output shaft cover 9 side, that is, the planetary gear 4 and the input shaft 6 are on the opposite side of the output shaft 8, and the planetary gear 4 and the input shaft 6 constitute a first-stage planetary reduction mechanism. The planet wheels 4 are mounted on an eccentric shaft 5, fixed circumferentially in a splined manner, axially in an axial circlip or the like, as in the prior art and not shown in the figures. The planet wheels 4 are arranged on the side of the output shaft cover 9 and are suspended with the output shaft cover 9 in the axial direction and the radial direction, so that the planet wheels 4 can obtain larger outer diameter. And the internal splines of the planet wheels 4 are meshed with the external splines of the eccentric shafts 5, and due to the increase of the number of the eccentric shafts 5 and the thickness of the planet wheels 4, the external splines of the eccentric shafts 5 can obtain smaller external diameter, so that the planet wheels 4 can obtain smaller diameter. The size of the outer diameter of the input shaft 6 is not limited by the speed reducer body, so that the speed reducer can obtain a speed reducer ratio in a wider range from an extremely-small speed reduction ratio to an extremely-large speed reducer.

As shown in fig. 6 and 11, the output shaft cover 9 is not only a non-sealing surface but also a mounting surface of the motor 21, when the motor mounting flange 17 is fixed on the pin gear housing 1, the sealing is realized by the O-ring 19 and the skeleton seal ring oil seal 14, the sealing of the planet wheel 4 can be realized at the same time, and the output end does not need to take corresponding sealing measures for sealing the planet wheel 4, thereby simplifying the sealing requirement of the output end. In addition, because the input shaft 6 and the planet wheel 4 are meshed at the same side, the axial length of the connection between the input shaft 6 and the motor 21 is short, an RV reducer with a compact axial direction can be obtained more easily, and the precision of a first-stage planetary reduction mechanism formed by the input shaft 6 and the planet wheel 4 is effectively improved.

As shown in fig. 9 and 10, the pin gear housing 1 serves as a fixed end of the RV reducer, the output plate rack 7 serves as an output end of the RV reducer, and the output plate rack 7 is formed by fixedly combining an output shaft cover 9 and an output shaft 8 through a taper pin 73 and a pillar bolt 72. A tray column 71 is arranged on the output shaft 8, column holes 34 corresponding to the tray column 71 one by one are arranged on each cycloidal gear 3, the tray column 71 penetrates through the corresponding column holes 34 and then is connected with the output shaft cover 9 through a column bolt 72 and a taper pin 73, connection between the output shaft cover 9 and the output shaft 8 is achieved, and the taper pin 73 mainly plays a role in positioning and transmits partial torque. Because the pitch circles of the taper pins 73 and the column bolts 72 on the output tray frame 7 are reduced along with the reduction of the outer diameter of the RV reducer, in order to bear the same torque, the tray frame columns 71 are correspondingly added into three groups in a circumferential array, so that the shearing capacity of the tray frame columns 71 is increased, and the number of the column bolts 72 and the taper pins 73 is increased.

As shown in fig. 10, wherein the cross-sectional area of the tray column 71 is limited by the size of the column hole 34 on the cycloid wheel 3, and the size of the column hole 34 is limited by the size of the cycloid wheel bearing hole 32, the cycloid wheel center hole 33, and the cycloid wheel outer teeth 31; and the minimum wall thickness between the pillar hole 34 and the center hole 33 of the cycloid wheel is L1, the minimum wall thickness between the pillar hole 34 and the bearing hole 32 of the cycloid wheel is L2, and the minimum wall thickness between the pillar hole 34 and the tooth root of the outer tooth 31 of the cycloid wheel is L3, so that L1, L2 and L3 are all larger than 2mm, and meanwhile, the sectional area of the disc frame pillar 71 is far larger than that of the non-cam shaft 51 on the eccentric shaft 5, so that the bearing torque requirement is met.

As shown in fig. 6, angular contact ball bearings 11 for bearing the torque and thrust of the RV reducer are provided between the outer wall of the output shaft cover 9 and the outer wall of the output shaft 8 and the inner wall of the pin gear housing 1, and the two cycloidal gears 3 are located 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, wherein 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 housing 1, 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, thus the semi-open and semi-closed angular contact ball bearing 11 is formed, not only the output disc rack 7 body is enabled to obtain higher rigidity, but also the diameter of the steel ball 112 in the angular contact ball bearing 11 is enabled to be increased as much as possible, thus higher load capacity can be obtained, and the bearing retainer 113 of the angular contact ball bearing 11 is more compact in enough.

As shown in fig. 6 and 12, the output shaft 8 is used as an output end of the RV reducer, the output end face is in a fully sealed state and is provided with three oil seals, firstly, the skeleton sealing ring oil seal 14 between the outer circle of the output shaft 8 and the inner hole of the pin gear shell 1, because the output shaft 8 and the pin gear shell 1 move relatively, the skeleton sealing ring oil seal 14 plays a role in dynamic sealing, and the axial space of the skeleton sealing ring oil seal 14 is large, sealing under a more severe environment can be realized by increasing the number of the skeleton sealing ring oil seals 14 or designing various sealing modes such as lip openings, and the like, damage caused by the fact that external environment substances enter the RV reducer is prevented, and grease in the inner cavity of; the position of the output shaft 8 corresponding to the eccentric shaft 5 is provided with three through holes 81, and the three through holes 81 are sealed by a cylindrical oil seal I15 and belong to static seal; thirdly, the central hole 75 of the output disc frame on the output shaft 8 is sealed by a cylindrical oil seal II 16, and 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.

As shown in fig. 6 and 13, in addition to this, the non-cam needle rollers and the cage 12 or the tapered roller bearings 13 are provided between the output carrier bearing hole 74 and the non-camshaft 51 of the eccentric shaft 5, and the number of the non-cam needle rollers and the cage 12 or the tapered roller bearings 13 is also set to three pairs in accordance with the number of the eccentric shaft 5, so that while the pitch circle of the eccentric shaft 5 is reduced, a large torque can be transmitted without changing the radial thickness of the non-cam needle rollers and the cage 12 or the tapered roller bearings 13. When the outer diameter c of the pin gear housing 1 is larger than 130mm, the tapered roller bearing 13 is arranged between the output disk rack bearing hole 74 and the non-cam shaft 51 of the eccentric shaft 5, the eccentric shaft 5 can be limited on the output disk rack 7 only by using the tapered roller bearing 13, and the eccentric shaft 5 is prevented from axially shifting and even being separated from the output disk rack 7. When the outer diameter c of the needle housing 1 is not more than 130mm, since the conventional technique cannot manufacture a smaller tapered roller bearing 13, a non-cam needle roller and a retainer 12 are provided between the output carrier bearing hole 74 and the non-camshaft 51 of the eccentric shaft 5, a deep groove ball bearing 121 is provided between the planet wheel 4 and the non-cam needle roller and the retainer 12, and the non-cam needle roller and the retainer 12 and the deep groove ball bearing 121 are used instead of the tapered roller bearing 13.

As shown in fig. 7, the distance between the axial line of the eccentric shaft 5 and the axial line of the pin gear housing 1 is the center distance b, and b is the main determining factor of the outer diameter of the speed reducer, i.e. the outer diameter c of the pin gear housing 1, so that b is reduced, the number of the eccentric shafts 5 is increased to three to ensure the torque, and the diameters of the camshaft 52 and the non-camshaft 51 on the eccentric shafts 5 are reduced, thereby achieving the purposes of reducing the outer diameter of the speed reducer and ensuring the larger torque. In addition, in order to ensure that the structure of each part of the speed reducer can meet the torque requirement while reducing the outer diameter of the speed reducer, the size, the number and the like of each part of the structure of the speed reducer are designed and calculated.

As shown in fig. 8, the camshaft 52 on the eccentric shaft 5 has a diameter d3, the non-camshaft 51 has a diameter d4, the cycloid wheel bearing hole 32 on each cycloid wheel 3 has a diameter d1, the central circle diameter of the needle rollers 2 between the cycloid wheel outer teeth 31 and the needle housing inner teeth 1102 is d2, and the rated torque of the reduction gear is T. Wherein, b is 8 to 123mm, b is x (d3)²＝(10～80)×T，b×(d4)²The required rated torque T and an appropriate value of b are selected first, and the size values of other parts are calculated according to a formula, wherein the required rated torque T and the appropriate value of b are selected to be (6-40) x T, d1 is (0.6-1.3) x b, and d2 is (3-4) x b.

As shown in fig. 6, the diameter d3 of the cam shaft 52 on the eccentric shaft 5 is reduced, the cycloid wheel bearing hole 32 and the cam shaft 52 on the eccentric shaft 5 are connected to the cage 10 via the cam needle rollers, three cam needle rollers and three cages 10 are provided for each cycloid wheel 3, and the bearing capacity of the cam needle rollers and the cages 10 is improved by increasing the number and axial length of the cam needle rollers and the cages 10 while the pitch circle (radius b) of the eccentric shaft 5 is reduced. As shown in fig. 14, the axial length of the cam needle roller and the cage 10 is determined by the length Lwe of the cam needle roller and the cage needle roller 101 on the cage 10. Further, the outer diameter of the cycloid gear 3 is reduced by reducing the diameter Dwe of the cage cam needle roller and the cage needle roller 101 on the cage 10 or smaller, and the outer diameter of the RV reducer is further reduced. Wherein the load between the needle roller for cam and the cage 10 isTd, M cage needles 101 are provided in the cam needle roller and the cage 10, the diameter of the cage needle 101 is Dwe, the length of the cage needle 101 is Lwe,

and M is an integer;

where fc is a coefficient specified in accordance with the shape, machining accuracy and material of each member of the bearing, and

in connection with

The calculation result of (b) is directly selected, bm is a rated coefficient according to conventional materials and processing amount, and bm is 1.1.

As shown in fig. 8 and 10, the cam shafts 52 on the three eccentric shafts 5 drive the cycloid wheel 3 to perform eccentric motion, and the eccentric distance is the eccentricity a of the eccentric shafts 5, that is, the eccentric amount of the non-cam shaft 51 and the cam shaft 52 on the axis of the eccentric shafts 5 on each eccentric shaft 5. Since the outer diameter of the cycloid gear 3 and the distance b between the axial line of the eccentric shaft 5 and the axial line of the pin gear housing 1 are reduced, as shown in fig. 15, in order to output the same torque, it is necessary to increase the thickness G of the cycloid gear 3 to increase the meshing area between the outer teeth 31 of the cycloid gear and the inner teeth 1102 of the pin gear housing and the contact area between the cycloid gear 3 and the camshaft 52 on the eccentric shaft 5, so that the cycloid gear 3 can bear a large torque and output the same torque. Wherein the thickness G of the cycloid wheel 3 is (0.8 to 1.8) × Lwe.

As shown in fig. 15 and 16, the decrease in the outer diameter of the cycloid gear 3 increases the short amplitude coefficient Ki, and in order to obtain an appropriate short amplitude coefficient Ki, it is necessary to appropriately decrease the eccentricity a to obtain the large-torque cycloid gear outer teeth 31 and to ensure that the cycloid gear outer teeth 31 mesh with the needle rollers 2 and the pin gear housing inner teeth 1102 with high efficiency and that no interference occurs when meshing with each other. Firstly, determining the outer tooth number Z1 of the cycloidal gear 3, and determining the inner tooth number Z2 of the needle gear housing 1 according to Z2 ═ Z1+1, wherein Z1 and Z2 are positive integers; root of herbaceous plantAccording to

And Ki is 0.45-0.85, A is 0.33-3.88 mm, and the eccentricity A is determined by selecting proper Ki. Of course, in other embodiments, the number of internal teeth Z2 of the pin gear housing 1 can also be calculated according to the formula

But this results in a reduction of T by around 20%.

As shown in fig. 16, while the outer diameter c of the pin gear housing 1 is reduced, the radial thickness P1 of the pin gear housing 1 can be properly reduced or maintained on the premise of ensuring that a large torque is satisfied, and the outer diameter c of the pin gear housing 1 is further reduced, so as to obtain a speed reducer with a smaller volume and a smaller pitch circle; on the premise of ensuring that the cycloidal gear 3 is normally installed on the pin gear shell 1, the width P2 of the inner teeth of the pin gear shell 1 is properly reduced, and the speed reducer with smaller volume is obtained. Wherein, P1 is (0.13-0.28). times.d 2, c is d2+2P1, and P2 is 2G + (0.2-1).

As shown in fig. 9, the diameter of the output tray bearing hole 74 is d5 and the diameter of the output tray center hole 75 is a. The output disk frame center hole 75 mainly reduces the weight of the speed reducer or is used as a support hole for the input shaft 6 to be supported, the smaller the diameter a of the output disk frame center hole 75 is, the closer the diameter a is to the limit of the small volume and the large torque of the speed reducer, but the thinnest wall thickness e between the output disk frame bearing hole 74 and the output disk frame center hole 75 is ensured, so that the output disk frame 7 can bear a certain torque. Therefore, the diameter a of the central hole 75 of the output disc frame is determined according to d5 (0.65-1.3) x b, a 2b-d5-2e and e is more than or equal to 1.5, a is more than 0, and when the outer diameter c of the pin gear shell 1 is less than or equal to 130mm, d5-d4-d1+ d3 is more than 0, namely the space between the bearing hole 74 of the output disc frame and the non-camshaft 51 is larger than the space between the bearing hole 32 of the cycloid wheel and the camshaft 52, so that the mounted non-cam roller and the cage 12 as well as the cam roller and the cage 10 can meet the torque requirement of the speed reducer; when the outer diameter c of the gear case 1 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 13 can be larger or more than those of the needle rollers for the cam and the retainer 10 under the condition that the outer ring and the inner ring have certain thicknesses, so that the torque requirement of the speed reducer is met.

As shown in fig. 7 and 9, the three sets of tray columns 71 and the output shaft cover 9 are connected by N1 column bolts 72 and m taper pins 73 which are uniformly arranged, the specification of the column bolts 72 is Mj1, 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 distributed pitch circle diameter of the N1 table stud bolts 72 is D1, the fastening friction coefficient of the table stud bolts 72 is μ and μ is 0.2, the torque transmitted by the N1 table stud bolts 72 is T1,

wherein D1 is (2-2.8) x b and N1 is an integer; the diameter of the taper pin 73 is D6, the distributed pitch circle diameter of the m taper pins 73 is D2, the shearing stress of the taper pins 73 is tau, which is determined according to the selection of taper pin materials, hardness and the like, the torque transmitted by the m taper pins 73 is T2,

wherein D2 is (1.4-2.9) x b and m is an integer; the total torque transmitted by the N1 table studs 72 and the m taper pins 73 is T3, T3 is T1+ T2 and

selecting proper quantity N1 of the pillar bolts 72 and proper specification Mj1 according to the size of the speed reducer, wherein j1 takes the values of national or international standards and 1.6, 2, 2.5, 3, 4, 5, 6, 8, 10, 12, 14, 16, 18, 20, 22 and the like, and the values of j2 and j3 are the same; determining the fastening force F1 corresponding to the column bolt 72 with the strength grade of 11.9 according to the specification Mj1 of the column bolt 72, selecting the proper distributed pitch circle diameter D1 of the column bolt 72 according to the D1 which is (2-2.8) x b, and then according to the formula

The torque transmitted by the N1 table studs 72 is calculated, where μ is the coefficient of friction when the table studs 72 are tightened in a surface greaseless state. Then, the diameter D6, the number m and the shear stress τ of the taper pin 73 are selected, and the taper pin 73 is selected according to the formula D2 ═ 1.4-2.9 x bThe diameter D2 of the pitch circle according to the formula

The torque transmitted by the m taper pins 73 is determined, finally T3 is T1+ T2

Whether the calculation of T1 and T2 can make the total torque T3 satisfy the judgment condition is judged, if not, the selection of the data related to the table stud 72 is adjusted, if not, the selection of the data related to the taper pin 73 is adjusted until the total torque T3 satisfies the judgment condition. The number and the specification of the column bolts 72 and the taper pins 73 are determined, so that the column bolts 72 and the taper pins 73 can meet the torque requirement when the tray frame columns 71 and the output shaft cover 9 are connected.

As shown in fig. 7 and 17, the reduction of the diameter of the pin gear housing mounting holes 110 on the pin gear housing 1 but the increase of the number can also satisfy the reduction of the pitch circle of the pin gear housing mounting holes 110 but the unchanged torque, which is also a feasible factor for reducing the size of the outer circle of the reducer. The number and size of the pin housing bolts 1101 mounted in the pin housing mounting holes 110 need to be determined to ensure the torque they carry. The pin gear shell 1 is circumferentially provided with N4 pin gear shell bolts 1101 with the axial direction the same as that of the pin gear shell 1, the specification of the pin gear shell bolts 1101 is Mj2, wherein j2 is the diameter of the pin gear shell bolts 1101, and the fastening force corresponding to each pin gear shell bolt 1101 with the specification of Mj2 is F4; the distributed pitch circle diameter of N4 pin housing bolts 1101 is D4, the fastening friction coefficient of pin housing bolts 1101 is μ and μ is 0.2, the torque transmitted by N4 pin housing bolts 1101 is T4,

wherein D4 is c-j2- (2-10), N4 is an integer and

as shown in FIG. 12, the output shaft 8 may be provided with an output shaft mounting threaded hole 82 for mounting an output shaft screw, except for two static seals of the cylindrical oil seal I15 and the cylindrical oil seal II 16The number of the bolts 83, the output shaft mounting threaded holes 82 can be greatly increased while the pitch circle of the output shaft mounting threaded holes 82 is reduced. Similarly, the number N5 and the specification Mj3 of the output shaft bolts 83 mounted in the output shaft mounting threaded holes 82 need to be determined to ensure the torque carried by the output shaft bolts. The specification of the N5 output shaft bolts 83 is Mj3, wherein j3 is the diameter of the output shaft bolt 83, and the fastening force corresponding to each output shaft bolt 83 with the specification of Mj3 is F5; the pitch circle diameter of N5 output shaft bolts 83 is D5, the fastening friction coefficient of the output shaft bolts 83 is μ and μ is 0.2, the torque transmitted by N5 output shaft bolts 83 is T5,

wherein D5 is (1.7-3.8) x b, N5 is an integer and

firstly, selecting proper specification Mj2 and number N4 of the pin gear shell bolts 1101, then determining fastening force F4 corresponding to the pin gear shell bolts 1101 with the strength grade of 11.9 according to specification Mj2 of the pin gear shell bolts 1101, selecting proper distributed pitch circle diameter D4 of the pin gear shell bolts 1101 according to D4-c-j 2- (2-10), and then selecting proper distributed pitch circle diameter D4 according to a formula

The torque transmitted by N4 pin-shell bolts 1101 was calculated, where μ is the coefficient of friction when fastening stud bolt 72 in a surface greaseless state. According to

Whether the torque of the pin housing bolt 1101 meets the condition is judged, and if not, the relevant data of the pin housing bolt 1101 is adjusted and selected until the torque T4 meets the condition. The number and size of the output shaft bolts 83 are determined similarly.

In this embodiment, the values and the calculation results mentioned above are as follows, and the calculation results both retain two digits after the decimal point (some formulas in the first to twelfth embodiments automatically call the parameter to retain the value of the multi-digit decimal when calling the parameter in the actual calculation):

1. firstly, selecting a proper rated torque T value and a proper center distance b value, wherein T is 12Nm, and b is 8 mm;

2. according to formula b x (d3)²(10 ~ 80) x T and b x (d4)²Calculating the diameter d3 of the camshaft 52 and the diameter d4 of the non-camshaft 51 respectively as (6-40) multiplied by T; selection of b × (d3)²10T, i.e. 8 × (d3)²When d3 is calculated to be 3.87mm, b x (d4) is selected as 10 × 12²6T, i.e. 8 × (d4)²D4 is calculated to be 3.00mm at 6 × 12;

3. calculating the diameter d1 of the cycloid wheel bearing hole 32 and the diameter d2 of the central circle of the needle roller 2 according to the formulas d1 (0.6-1.3) x b and d2 (3-4) x b respectively; d 1-0.6 × b-0.6 × 8, i.e., d 1-4.80 mm, d 2-4 × b-4 × 8, i.e., d 2-32.00 mm;

4. according to the formula

Calculating the diameter Dwe of the cam needle roller and the cage needle roller 101 on the cage 10, the number M of the cage needle rollers 101, the length Lwe of the cage needle rollers 101 and the like;

calculating Dwe-0.46 mm;

calculating M-15;

so fc is selected to be 85.3 and Td is selected to be 100 × T, i.e.

Lwe mm is calculated as 5.62 mm;

5. calculating the thickness G of the pin gear shell 1 according to the formula G ═ 0.8-1.8 x Lwe; selecting 0.8 × Lwe, namely 0.8 × 5.62, and calculating 4.50 mm;

6. selecting the cycloid gear outer teeth number Z1 equal to 21The number of teeth Z2 in the gear shell is Z1+1 is 22, an appropriate short amplitude coefficient Ki is selected, and the formula is shown

Calculating an eccentricity A; the short amplitude coefficient Ki is 0.45,

calculating A to be 0.33 mm;

7. calculating the radial thickness P1 of the needle gear case 1, the internal tooth width P2 of the needle gear case 1 and the external diameter c of the needle gear case 1 according to P1 (0.13-0.28) x d2, c (d 2+2P 1) and P2 (2G + (0.2-1); selecting P1-0.18 × d2, i.e. P1-0.18 × 32.00, and calculating P1-5.76 mm; selecting P2-2G +0.2, i.e. P2-2 x 4.50+0.2, and calculating P2-9.20 mm; c is 32.00+2 × 5.76, i.e., c is 43.52 mm;

8. c is less than or equal to 130mm, so that according to the formula d5 ═ 0.65-1.3 × b and d5-d4-d1+ d3 > 0, a ═ 2b-d5-2e, wherein e is greater than or equal to 1.5 and a > 0, the diameter d5 of the output tray bearing hole 74 and the diameter a of the output tray center hole 75 are calculated; d5 is selected to be 0.65 × b, namely d5 is 0.65 × 8, d5 is calculated to be 5.20mm, and d5-d4-d1+ d3 is 5.20-3.00-4.80+3.87 is calculated to be 1.27, so that d5-d4-d1+ d3 is more than 0; selecting e as 1.5, i.e. a as 2 × 8-5.20-2 × 1.5, and calculating a as 7.80 mm;

9. selecting and determining the specifications and the number of the column bolts 72 and the taper pins 73, and calculating whether the torque is qualified; selecting the number N1 of the column bolts 72 as N1-6, the specification Mj1 of the column bolts 72 as M3, the fastening force F1 of the corresponding column bolts 72 as F1-3166N, and selecting D1-2 × b-2 × 8 according to the formula D1 of the distributed pitch circle diameter of the column bolts 72 (2-2.8) × b, that is, D1-16.00 mm; according to the formula

The torque T1 transmitted by the table stud 72 is calculated,

namely, T1 is 30.39N; selecting the number m of taper pins 73 to be 3, the diameter D6 of the taper pins 73 to be 3mm, the shearing stress tau of the taper pins 73 to be 196N/mm, and selecting the number m of the taper pins 73 to be (1.4-2.9) x b according to the distribution pitch circle diameter formula D2 of the taper pins 73D2 ═ 1.4 × b ═ 1.4 × 8, i.e., D2 ═ 11.20 mm; according to the formula

The torque T2 transmitted by the taper pin 73 is calculated,

namely, T2 is 23.28 Nm; the total torque T3 is T3 ═ T1+ T2 and

satisfies the conditions

10. Selecting and determining the number and specification of the pin gear housing bolts 1101, and calculating whether the torque of the pin gear housing bolts 1101 is qualified; selecting N4 of the pin-tooth shell bolts 1101 as N4-6, selecting M3 of the specifications Mj2 of the pin-tooth shell bolts 1101, namely j2-3, selecting D4-c-j 2-2-43.52-3-2 of the specifications D4-38.52 mm according to a distributed pitch circle diameter formula D4-c-j 2- (2-10) of the pin-tooth shell bolts 1101, wherein the specifications Mj2 of the pin-tooth shell bolts 1101 are M3, namely j2-3, and the fastening force F4 of the corresponding pin-tooth shell bolts 1101 is F4-3166N; according to the formula

The torque T4 transmitted by the pin housing bolt 1101 is calculated,

i.e., 73.17Nm for T4; and is

Satisfies the conditions

11. Selecting and determining the number and specification of the output shaft bolts 83, and calculating whether the torque of the output shaft bolts 83 is qualified; the number N5 of output shaft bolts 83 is selected to be N5-6, the specification Mj3 of output shaft bolts 83 is selected to be M4, the corresponding fastening force F5 of output shaft bolts 83 is selected to be F5-5580N, and the formula D5 of the pitch circle diameter of output shaft bolts 83 is selected to be (1).7-3.8). times.b, selecting D5-3 × b-3 × 8, namely D5-24.00 mm; according to the formula

The torque T5 transmitted by the output shaft bolt 83 is calculated,

namely T5-80.35 Nm; and is

Satisfies the conditions

In summary, the RV reducer designed in this embodiment has the following relevant dimensions:

the rated torque T is 12Nm, the center distance b is 8mm, the diameter d3 of the camshaft 52 is 3.87mm, the diameter d4 of the non-camshaft 51 is 3.00mm, the diameter d1 of the cycloid wheel bearing hole 32 is 4.80mm, and the diameter d2 of the center circle of the needle roller 2 is 32.00 mm; the diameter Dwe of the cam needle roller and the cage needle roller 101 on the cage 10 is 0.46mm, the number M of the cage needle rollers 101 is 15, and the length Lwe of the cage needle rollers 101 is 5.62 mm; the thickness G of the pin gear shell 1 is 4.50mm, the outer tooth number Z1 of the cycloid gear is 21, the inner tooth number Z2 of the pin gear shell is 22, the short amplitude coefficient Ki is 0.45, and the eccentricity A is 0.33 mm; the diameter d5 of the bearing hole 74 of the output disk frame is 5.20mm, and the diameter a of the central hole 75 of the output disk frame is 7.80 mm; the radial thickness P1 of the pin gear shell 1 is 5.76mm, the inner tooth width P2 of the pin gear shell is 9.20mm, and the outer diameter c of the pin gear shell 1 is 43.52 mm; the number N1 of the column bolts 72 is 6, the specification Mj1 of the column bolts 72 is M3, the diameter D1 of the distributed pitch circle of the column bolts 72 is 16.00mm, and the torque T1 transmitted by the column bolts 72 is 30.39N; the number m of the taper pins 73 is 3, the diameter D6 of the taper pins 73 is 3mm, the shear stress tau of the taper pins 73 is 196N/mm, the distributed pitch circle diameter D2 of the taper pins 73 is 11.20mm, and the torque T2 transmitted by the taper pins 73 is 23.28 Nm; the number N4 of the pin housing bolts 1101 is 6, the specification Mj2 of the pin housing bolts 1101 is M3, the diameter D4 of the pitch circle of the pin housing bolts 1101 is 38.52mm, and the torque T4 transmitted by the pin housing bolts 1101 is 73.17 Nm; the number N5 of the output shaft bolts 83 is 6, the specification Mj3 of the output shaft bolts 83 is M4, the distributed pitch circle diameter D5 of the output shaft bolts 83 is 24.00mm, and the torque T5 transmitted by the output shaft bolts 83 is 80.35 Nm.

In the present embodiment, since the outer diameter c of the pinion housing 1 is 43.52mm, that is, c is not more than 130mm, as shown in fig. 6, a needle roller for non-cam and a cage 12 are provided between the output carrier bearing hole 74 and the non-cam shaft 51 of the eccentric shaft 5, and a deep groove ball bearing 121 is provided between the planet wheel 4 and the needle roller for non-cam and the cage 12.

Example two:

the structure of the RV reducer with the novel structure of the second to twelfth embodiments is basically the same as that of the RV reducer with the novel structure of the first embodiment, and the design concept is also the same, except that the sizes of the parts of the RV reducer are different, that is, the values and calculation results are different. In the second embodiment, the values and calculation results related to the RV reducer with the novel structure are as follows, and the calculation results all retain two digits after the decimal point:

1. firstly, selecting a proper rated torque T value and a proper center distance b value, wherein T is 38Nm, and b is 13.75 mm;

2. according to formula b x (d3)²(10 ~ 80) x T and b x (d4)²Calculating the diameter d3 of the camshaft 52 and the diameter d4 of the non-camshaft 51 respectively as (6-40) multiplied by T; selection of b × (d3)²28T, i.e. 13.75 × (d3)²When the measured value is 28X 38, d 3mm is calculated to be 8.80mm, b X (d4) is selected²12T, i.e. 13.75 × (d4)²12 × 38, and d4 is calculated to be 5.76 mm;

3. calculating the diameter d1 of the cycloid wheel bearing hole 32 and the diameter d2 of the central circle of the needle roller 2 according to the formulas d1 (0.6-1.3) x b and d2 (3-4) x b respectively; d 1-0.93 × b-0.93 × 13.75, i.e., d 1-12.79 mm, d 2-3.5 × b-3.5 × 13.75, i.e., d 2-48.13 mm;

4. according to the formula

The diameter Dwe of the cage needle roller 101 on the cam needle roller and cage 10, the number M of the cage needle rollers 101, and the cage needle roller 1 are calculatedLength Lwe of 01, etc.;

calculating Dwe-2.00 mm;

calculating M to be 10;

so fc is chosen to be 88.80 and Td is chosen to be 80T, i.e.

Lwe mm is calculated to be 3.48 mm;

5. calculating the thickness G of the pin gear shell 1 according to the formula G ═ 0.8-1.8 x Lwe; selecting 1.4 × Lwe, namely 1.4 × 3.48, and calculating 4.87 mm;

6. the outer tooth number Z1 of the cycloid gear is 27, the inner tooth number Z2 of the pin gear shell is Z1+1 is 28, a proper short amplitude coefficient Ki is selected, and the formula is used

Calculating an eccentricity A; the short amplitude coefficient Ki is selected to be 0.69,

calculating A to be 0.59 mm;

7. calculating the radial thickness P1 of the needle gear case 1, the internal tooth width P2 of the needle gear case 1 and the external diameter c of the needle gear case 1 according to P1 (0.13-0.28) x d2, c (d 2+2P 1) and P2 (2G + (0.2-1); selecting P1-0.15 × d2, i.e. P1-0.15 × 48.13, and calculating P1-7.22 mm; selecting P2-2G +0.55, i.e. P2-2 × 4.87+0.55, and calculating P2-10.28 mm; c is 48.13+2 × 7.22, i.e., c is 62.56 mm;

8. c is less than or equal to 130mm, so that according to the formula d5 ═ 0.65-1.3 × b and d5-d4-d1+ d3 > 0, a ═ 2b-d5-2e, wherein e is greater than or equal to 1.5 and a > 0, the diameter d5 of the output tray bearing hole 74 and the diameter a of the output tray center hole 75 are calculated; selecting d 5-0.87 × b, i.e. d 5-0.87 × 13.75, calculating d 5-11.96 mm, and d5-d4-d1+ d 3-11.96-5.76-12.79 + 8.80-2.21, satisfying d5-d4-d1+ d3 > 0; selecting e-2, i.e. a-2 × 13.75-11.96-2 × 2, and calculating a-11.54 mm;

9. selecting and determining the specifications and the number of the column bolts 72 and the taper pins 73, and calculating whether the torque is qualified; selecting the number N1 of the column bolts 72 as N1-6, the specification Mj1 of the column bolts 72 as M4, the fastening force F1 of the corresponding column bolts 72 as F1-5580N, and selecting D1-2.8 × b-2.8 × 13.75 according to the formula D1 of the distributed pitch circle diameter of the column bolts 72, namely selecting D1-38.50 mm; according to the formula

The torque T1 transmitted by the table stud 72 is calculated,

namely, T1 is 128.90N; selecting the number m of taper pins 73 to be 3, the diameter D6 of the taper pins 73 to be 3mm, the shear stress tau of the taper pins 73 to be 196N/mm, and selecting D2 to be 2 x b to be 2 x 13.75 according to the distribution pitch circle diameter formula D2 of the taper pins 73 to be (1.4-2.9) x b, namely D2 to be 27.50 mm; according to the formula

The torque T2 transmitted by the taper pin 73 is calculated,

i.e., T2 ═ 57.15 Nm; the total torque T3 is T3 ═ T1+ T2 and

satisfies the conditions

10. Selecting and determining the number and specification of the pin gear housing bolts 1101, and calculating whether the torque of the pin gear housing bolts 1101 is qualified; selecting N4 as N4-9, M4 as specification Mj2 of the pin-shell bolts 1101, namely j2-4, and F4 as corresponding fastening force F4-5580N, and selecting D4-c-j 2-3-62.56-4-3, namely D4-55.56 mm according to a distributed pitch circle diameter formula D4-c-j 2- (2-10) of the pin-shell bolts 1101; according to the formula

The torque T4 transmitted by the pin housing bolt 1101 is calculated,

namely T4-279.03 Nm; and is

Satisfies the conditions

11. Selecting and determining the number and specification of the output shaft bolts 83, and calculating whether the torque of the output shaft bolts 83 is qualified; selecting N5 as N5 as 6, Mj3 as output shaft bolts 83 specification as M5, F5 as F5 as F9310N, and selecting D5 as 3.5 × b as 3.5 × 13.75 according to the formula D5 (1.7-3.8) × b of the distribution pitch diameter of the output shaft bolts 83, namely D5 as 48.13 mm; according to the formula

The torque T5 transmitted by the output shaft bolt 83 is calculated,

namely T5-268.83 Nm; and is

Satisfies the conditions

the rated torque T is 38Nm, the center distance b is 13.75mm, the diameter d3 of the camshaft 52 is 8.80mm, the diameter d4 of the non-camshaft 51 is 5.76mm, the diameter d1 of the cycloid wheel bearing hole 32 is 12.79mm, and the diameter d2 of the center circle of the needle roller 2 is 48.13 mm; the diameter Dwe of the cam needle roller and the retainer needle roller 101 on the retainer 10 is 2.00mm, the number M of the retainer needle rollers 101 is 10, and the length Lwe of the retainer needle rollers 101 is 3.48 mm; the thickness G of the pin gear shell 1 is 4.87mm, the outer tooth number Z1 of the cycloid gear is 27, the inner tooth number Z2 of the pin gear shell is 28, the short amplitude coefficient Ki is 0.69, and the eccentricity A is 0.59 mm; the diameter d5 of the bearing hole 74 of the output tray is 11.96mm, and the diameter a of the central hole 75 of the output tray is 11.54 mm; the radial thickness P1 of the pin gear shell 1 is 7.22mm, the inner tooth width P2 of the pin gear shell is 10.28mm, and the outer diameter c of the pin gear shell 1 is 62.56 mm; the number N1 of the column bolts 72 is 6, the specification Mj1 of the column bolts 72 is M4, the diameter D1 of the distributed pitch circle of the column bolts 72 is 38.50mm, and the torque T1 transmitted by the column bolts 72 is 128.90N; the number m of the taper pins 73 is 3, the diameter D6 of the taper pins 73 is 3mm, the shear stress tau of the taper pins 73 is 196N/mm, the distributed pitch circle diameter D2 of the taper pins 73 is 27.50mm, and the torque T2 transmitted by the taper pins 73 is 57.15 Nm; the number N4 of the pin gear housing bolts 1101 is 9, the specification Mj2 of the pin gear housing bolts 1101 is M4, the diameter D4 of the pitch circle of the pin gear housing bolts 1101 is 55.56mm, and the torque T4 transmitted by the pin gear housing bolts 1101 is 279.03 Nm; the number N5 of the output shaft bolts 83 is 6, the specification Mj3 of the output shaft bolts 83 is M5, the distributed pitch circle diameter D5 of the output shaft bolts 83 is 48.13mm, and the torque T5 transmitted by the output shaft bolts 83 is 268.83 Nm.

Similarly, since the outer diameter c of the pinion housing 1 is 52.56mm, i.e., c is 130mm or less in the present embodiment, as shown in fig. 6, a needle roller for non-cam and a cage 12 are provided between the output carrier bearing hole 74 and the non-camshaft 51 of the eccentric shaft 5, and a deep groove ball bearing 121 is provided between the planet gears 4 and the needle roller for non-cam and the cage 12.

Example three:

in the third embodiment, the values and calculation results related to the RV reducer with the novel structure are as follows, and the calculation results all retain two digits after the decimal point:

1. firstly, selecting a proper rated torque T value and a proper center distance b value, wherein T is 58Nm, and b is 18 mm;

2. according to formula b x (d3)²(10 ~ 80) x T and b x (d4)²Calculating the diameter d3 of the camshaft 52 and the diameter d4 of the non-camshaft 51 respectively as (6-40) multiplied by T; selection of b × (d3)²31T, i.e. 18 × (d3)²31X 58, d3 is calculated to be 9.99mm, b X (d4)²15T, i.e. 18 × (d4)²15 × 58, d4 is calculated to be 6.95 mm;

3. calculating the diameter d1 of the cycloid wheel bearing hole 32 and the diameter d2 of the central circle of the needle roller 2 according to the formulas d1 (0.6-1.3) x b and d2 (3-4) x b respectively; d 1-0.83 × b-0.83 × 18, i.e., d 1-14.94 mm, d 2-3.78 × b-3.78 × 18, i.e., d 2-68.04 mm;

4. according to the formula

calculating Dwe-2.47 mm;

calculating M to 9;

so fc is chosen to be 88.70 and Td is chosen to be 86T, i.e.

Lwe mm is calculated as 5.42 mm;

5. calculating the thickness G of the pin gear shell 1 according to the formula G ═ 0.8-1.8 x Lwe; selecting 1.05 × Lwe, namely 1.05 × 5.42, and calculating 5.69 mm;

6. selecting the outer tooth number Z1 of the cycloid gear to be 31, the inner tooth number Z2 of the pin gear shell to be Z1+1 to be 32, selecting a proper short amplitude coefficient Ki and according to a formula

Calculating an eccentricity A; the short amplitude coefficient Ki is 0.75,

calculating A to be 0.80 mm;

7. calculating the radial thickness P1 of the needle gear case 1, the internal tooth width P2 of the needle gear case 1 and the external diameter c of the needle gear case 1 according to P1 (0.13-0.28) x d2, c (d 2+2P 1) and P2 (2G + (0.2-1); selecting P1-0.13 × d2, namely P1-0.13 × 68.04, and calculating P1-8.85 mm; selecting P2-2G +0.6, i.e. P2-2 × 5.69+0.6, and calculating P2-11.97 mm; c is 68.04+2 × 8.85, i.e., c is 85.73 mm;

8. c is less than or equal to 130mm, so that according to the formula d5 ═ 0.65-1.3 × b and d5-d4-d1+ d3 > 0, a ═ 2b-d5-2e, wherein e is greater than or equal to 1.5 and a > 0, the diameter d5 of the output tray bearing hole 74 and the diameter a of the output tray center hole 75 are calculated; d5 is selected to be 0.83 × b, namely d5 is 0.83 × 18, d5 is calculated to be 14.94mm, and d5-d4-d1+ d3 is calculated to be 14.94-6.95-14.94+9.99 is calculated to be 3.04, so that d5-d4-d1+ d3 is more than 0; selecting e-2.5, i.e. a-2 × 18-14.94-2 × 2.5, and calculating a-16.06 mm;

9. selecting and determining the specifications and the number of the column bolts 72 and the taper pins 73, and calculating whether the torque is qualified; selecting the number N1 of the column bolts 72 as N1-6, the specification Mj1 of the column bolts 72 as M5, the fastening force F1 of the corresponding column bolts 72 as F1-9310N, and selecting D1-2.45 × b-2.45 × 18, namely D1-44.10 mm according to the formula D1 of the distributed pitch circle diameter of the column bolts 72 as (2-2.8) × b; according to the formula

The torque T1 transmitted by the table stud 72 is calculated,

namely, T1 is 246.34N; selecting the number m of taper pins 73 to be 3, the diameter D6 of the taper pins 73 to be 5mm, the shear stress tau of the taper pins 73 to be 196N/mm, and selecting the D2 to be 1.9 x b to be 1.9 x 18 according to the distribution pitch circle diameter formula D2 of the taper pins 73 to be (1.4-2.9) x b, namely D2 to be 34.20 mm; according to the formula

The torque T2 transmitted by the taper pin 73 is calculated,

namely T2-197.43 Nm; the total torque T3 is T3 ═ T1+ T2 and

satisfies the conditions

10. Selecting and determining the number and specification of the pin gear housing bolts 1101, and calculating whether the torque of the pin gear housing bolts 1101 is qualified; selecting N4 as N4-12, M4 as specification Mj2 of the pin-shell bolts 1101, namely j2-4, and F4 as corresponding fastening force F4-5580N of the pin-shell bolts 1101, and selecting D4-c-j 2-3-85.73-4-3, namely D4-78.73 mm according to a distributed pitch circle diameter formula D4-c-j 2- (2-10) of the pin-shell bolts 1101; according to the formula

The torque T4 transmitted by the pin housing bolt 1101 is calculated,

namely T4-527.18 Nm; and is

Satisfies the conditions

11. Selecting and determining the number and specification of the output shaft bolts 83, and calculating whether the torque of the output shaft bolts 83 is qualified; selecting N5 as N5 as 9, Mj3 as output shaft bolts 83 specification as M6, F5 as F5 as 13180N, and selecting D5 as 1.7 × b as 1.7 × 18 according to the formula D5 (1.7-3.8) × b of the distribution pitch circle diameter of the output shaft bolts 83, namely D5 as 30.60 mm; according to the formula

The torque T5 transmitted by the output shaft bolt 83 is calculated,

namely T5-362.98 Nm; and is

Satisfies the conditions

the rated torque T is 58Nm, the center distance b is 18mm, the diameter d3 of the camshaft 52 is 9.99mm, the diameter d4 of the non-camshaft 51 is 6.95mm, the diameter d1 of the cycloid wheel bearing hole 32 is 14.94mm, and the diameter d2 of the center circle of the needle roller 2 is 68.04 mm; the diameter Dwe of the cam needle roller and the retainer needle roller 101 on the retainer 10 is 2.47mm, the number M of the retainer needle rollers 101 is 9, and the length Lwe of the retainer needle rollers 101 is 5.42 mm; the thickness G of the pin gear shell 1 is 5.69mm, the external tooth number Z1 of the cycloid gear is 31, the internal tooth number Z2 of the pin gear shell is 32, the short amplitude coefficient Ki is 0.75, and the eccentricity A is 0.80 mm; the diameter d5 of the bearing hole 74 of the output tray is 14.94mm, and the diameter a of the central hole 75 of the output tray is 16.06 mm; the radial thickness P1 of the pin gear shell 1 is 8.85mm, the inner tooth width P2 of the pin gear shell 1 is 11.97mm, and the outer diameter c of the pin gear shell 1 is 85.73 mm; the number N1 of the column bolts 72 is 6, the specification Mj1 of the column bolts 72 is M5, the diameter D1 of the distributed pitch circle of the column bolts 72 is 44.10mm, and the torque T1 transmitted by the column bolts 72 is 246.34N; the number m of the taper pins 73 is 3, the diameter D6 of the taper pins 73 is 5mm, the shear stress tau of the taper pins 73 is 196N/mm, the distributed pitch circle diameter D2 of the taper pins 73 is 34.20mm, and the torque T2 transmitted by the taper pins 73 is 197.43 Nm; the number N4 of the pin gear housing bolts 1101 is 12, the specification Mj2 of the pin gear housing bolts 1101 is M4, the diameter D4 of the pitch circle of the pin gear housing bolts 1101 is 78.73mm, and the torque T4 transmitted by the pin gear housing bolts 1101 is 527.18 Nm; the number N5 of the output shaft bolts 83 is 9, the specification Mj3 of the output shaft bolts 83 is M6, the distributed pitch circle diameter D5 of the output shaft bolts 83 is 30.60mm, and the torque T5 transmitted by the output shaft bolts 83 is 362.98 Nm.

Similarly, in the present embodiment, since the outer diameter c of the pinion housing 1 is 85.73mm, that is, c is not more than 130mm, as shown in fig. 6, a needle roller for non-cam and a cage 12 are provided between the output carrier bearing hole 74 and the non-cam shaft 51 of the eccentric shaft 5, and a deep groove ball bearing 121 is provided between the planet wheel 4 and the needle roller for non-cam and the cage 12.

Example four:

in the fourth embodiment, the values and calculation results related to the RV reducer with the novel structure are as follows, and the calculation results all retain two digits after the decimal point:

1. firstly, selecting a proper rated torque T value and a proper center distance b value, wherein T is 245Nm, and b is 24.5 mm;

2. according to formula b x (d3)²(10 ~ 80) x T and b x (d4)²Calculating the diameter d3 of the camshaft 52 and the diameter d4 of the non-camshaft 51 respectively as (6-40) multiplied by T; selection of b × (d3)²32.5T, i.e. 24.5 × (d3)²32.5X 245, calculate d3 ═ 18.03mm, select b × (d4)²10T, i.e. 24.5 × (d4)²D4 is calculated to be 10.00mm when being 10 × 245;

3. calculating the diameter d1 of the cycloid wheel bearing hole 32 and the diameter d2 of the central circle of the needle roller 2 according to the formulas d1 (0.6-1.3) x b and d2 (3-4) x b respectively; d 1-0.98 × b-0.98 × 24.5, i.e., d 1-24.01 mm, d 2-3.7 × b-3.7 × 24.5, i.e., d 2-90.65 mm;

4. according to the formula

calculating Dwe-2.99 mm;

calculating M-16;

therefore, fc is 87.70 and Td is 50.5T, i.e.

Calculating Lwe-7.80 mm;

5. calculating the thickness G of the pin gear shell 1 according to the formula G ═ 0.8-1.8 x Lwe; selecting 1.4 × Lwe, namely 1.4 × 7.80, and calculating 10.92 mm;

6. the outer tooth number Z1 of the cycloid gear is 39, the inner tooth number Z2 of the pin gear shell is Z1+1 is 40, a proper short amplitude coefficient Ki is selected, and the formula is used

Calculating an eccentricity A; the short amplitude coefficient Ki is 0.8,

calculating A to be 0.91 mm;

7. calculating the radial thickness P1 of the needle gear case 1, the internal tooth width P2 of the needle gear case 1 and the external diameter c of the needle gear case 1 according to P1 (0.13-0.28) x d2, c (d 2+2P 1) and P2 (2G + (0.2-1); selecting P1-0.19 × d2, i.e. P1-0.19 × 90.65, and calculating P1-17.22 mm; selecting P2-2G +0.55, i.e. P2-2 x 10.92+0.55, and calculating P2-22.39 mm; c is 90.65+2 × 17.22, i.e., c is 125.10 mm;

8. c is less than or equal to 130mm, so that according to the formula d5 ═ 0.65-1.3 × b and d5-d4-d1+ d3 > 0, a ═ 2b-d5-2e, wherein e is greater than or equal to 1.5 and a > 0, the diameter d5 of the output tray bearing hole 74 and the diameter a of the output tray center hole 75 are calculated; selecting d 5-0.92 × b, i.e. d 5-0.92 × 24.5, calculating d 5-22.54 mm, and d5-d4-d1+ d 3-22.54-10.00-24.01 + 18.03-6.56, satisfying d5-d4-d1+ d3 > 0; selecting e-2, namely a-2 × 24.5-22.54-2 × 2, and calculating a-22.46 mm;

9. selecting and determining the specifications and the number of the column bolts 72 and the taper pins 73, and calculating whether the torque is qualified; selecting the number N1 of the column bolts 72 as N1-6, the specification Mj1 of the column bolts 72 as M6, the fastening force F1 of the corresponding column bolts 72 as F1-13180N, and selecting D1-2.5 × b-2.5 × 24.5, namely D1-61.25 mm according to the formula D1 of the distributed pitch circle diameter of the column bolts 72 as (2-2.8) × b; according to the formula

The torque T1 transmitted by the table stud 72 is calculated,

namely, T1 is 484.37N; selecting the number m of taper pins 73 to be 3, the diameter D6 of the taper pins 73 to be 6mm, the shear stress tau of the taper pins 73 to be 196N/mm, and selecting the D2 to be 2.3 x b to be 2.3 x 24.5 according to the distribution pitch circle diameter formula D2 of the taper pins 73 to be (1.4-2.9) x b, namely D2 to be 56.35 mm; according to the formula

The torque T2 transmitted by the taper pin 73 is calculated,

namely T2-486.42 Nm; the total torque T3 is T3 ═ T1+ T2 and

satisfies the conditions

10. Selecting and determining the number and specification of the pin gear housing bolts 1101, and calculating whether the torque of the pin gear housing bolts 1101 is qualified; selecting N4 as N4 as 16, selecting Mj2 as M5, namely j2 as 5, selecting D4 as c-j2-4 as 125.10-5-4, namely D4 as 116.10mm according to a distributed pitch circle diameter formula D4 as c-j2- (2-10) of the pin-shell bolts 1101, wherein the specification Mj2 of the pin-shell bolts 1101 is M5, namely j2 as 5, and the corresponding fastening force F4 of the pin-shell bolts 1101 is F4 as 9310N; according to the formula

The torque T4 transmitted by the pin housing bolt 1101 is calculated,

namely T4-1729.38 Nm; and is

Satisfies the conditions

11. The number and specification of the output shaft bolts 83 are selectively determined and countedCalculating whether the torque of the output shaft bolt 83 is qualified; selecting N5 as N5 as 9, Mj3 as output shaft bolts 83 specification as M8, F5 as F5 as F23960N, and selecting D5 as 3.8 × b as 3.8 × 24.5 according to the formula D5 (1.7-3.8) × b of the distribution pitch diameter of the output shaft bolts 83, namely D5 as 93.10 mm; according to the formula

The torque T5 transmitted by the output shaft bolt 83 is calculated,

namely T5-2007.61 Nm; and is

Satisfies the conditions

the rated torque T is 245Nm, the center distance b is 24.5mm, the diameter d3 of the camshaft 52 is 18.03mm, the diameter d4 of the non-camshaft 51 is 10.00mm, the diameter d1 of the cycloid wheel bearing hole 32 is 24.01mm, and the diameter d2 of the center circle of the needle roller 2 is 90.65 mm; the diameter Dwe of the cam needle roller and the retainer needle roller 101 on the retainer 10 is 2.99mm, the number M of the retainer needle rollers 101 is 16, and the length Lwe of the retainer needle rollers 101 is 7.80 mm; the thickness G of the pin gear shell 1 is 10.92mm, the outer tooth number Z1 of the cycloid gear is 39, the inner tooth number Z2 of the pin gear shell is 40, the short amplitude coefficient Ki is 0.8, and the eccentricity A is 0.91 mm; the diameter d5 of the bearing hole 74 of the output tray is 22.54mm, and the diameter a of the central hole 75 of the output tray is 22.46 mm; the radial thickness P1 of the pin gear shell 1 is 17.22mm, the inner tooth width P2 of the pin gear shell is 22.39mm, and the outer diameter c of the pin gear shell 1 is 125.10 mm; the number N1 of the column bolts 72 is 6, the specification Mj1 of the column bolts 72 is M6, the diameter D1 of the distributed pitch circle of the column bolts 72 is 61.25mm, and the torque T1 transmitted by the column bolts 72 is 484.37N; the number m of taper pins 73 is 3, the diameter D6 of the taper pins 73 is 6mm, the shear stress tau of the taper pins 73 is 196N/mm, the distributed pitch circle diameter D2 of the taper pins 73 is 56.35mm, and the torque T2 transmitted by the taper pins 73 is 468.42 Nm; the number N4 of the pin housing bolts 1101 is 16, the specification Mj2 of the pin housing bolts 1101 is M5, the diameter D4 of the pitch circle of the pin housing bolts 1101 is 116.10mm, and the torque T4 transmitted by the pin housing bolts 1101 is 1729.38 Nm; the number N5 of the output shaft bolts 83 is 9, the specification Mj3 of the output shaft bolts 83 is M8, the distributed pitch circle diameter D5 of the output shaft bolts 83 is 93.10mm, and the torque T5 transmitted by the output shaft bolts 83 is 2007.61 Nm.

Similarly, since the outer diameter c of the pinion housing 1 is 125.10mm, i.e., c is 130mm or less in the present embodiment, as shown in fig. 6, a needle roller for non-cam and a cage 12 are provided between the output carrier bearing hole 74 and the non-camshaft 51 of the eccentric shaft 5, and a deep groove ball bearing 121 is provided between the planet gears 4 and the needle roller for non-cam and the cage 12.

Example five:

in the fifth embodiment, values and calculation results related to the RV reducer with the novel structure are as follows, and the calculation results all retain two digits after the decimal point:

1. firstly, selecting a proper rated torque T value and a proper center distance b value, wherein T is 412Nm, and b is 32.5 mm;

2. according to formula b x (d3)²(10 ~ 80) x T and b x (d4)²Calculating the diameter d3 of the camshaft 52 and the diameter d4 of the non-camshaft 51 respectively as (6-40) multiplied by T; selection of b × (d3)²34T, i.e. 32.5 × (d3)²34X 412, d3 is calculated to be 20.76mm, b X (d4)²12T, i.e. 32.5 × (d4)²12 × 412, calculating d 4-12.33 mm;

3. calculating the diameter d1 of the cycloid wheel bearing hole 32 and the diameter d2 of the central circle of the needle roller 2 according to the formulas d1 (0.6-1.3) x b and d2 (3-4) x b respectively; d 1-0.86 × b-0.86 × 32.5, i.e., d 1-27.95 mm, d 2-3.6 × b-3.6 × 32.5, i.e., d 2-117.00 mm;

4. according to the formula

Calculating the diameter Dwe of the cam needle roller and the cage needle roller 101 on the cage 10, the number M of the cage needle rollers 101, and the holdingLength Lwe of cage needle roller 101, etc.;

dwe mm is calculated to be 3.59 mm;

calculating M-14;

so fc is chosen to be 88.10 and Td is chosen to be 40T, i.e.

Calculating Lwe-9.90 mm;

5. calculating the thickness G of the pin gear shell 1 according to the formula G ═ 0.8-1.8 x Lwe; selecting 1.25 × Lwe, namely 1.25 × 9.90, and calculating 12.37 mm;

Calculating an eccentricity A; the short amplitude coefficient Ki is 0.75,

calculating A to be 1.10 mm;

7. calculating the radial thickness P1 of the needle gear case 1, the internal tooth width P2 of the needle gear case 1 and the external diameter c of the needle gear case 1 according to P1 (0.13-0.28) x d2, c (d 2+2P 1) and P2 (2G + (0.2-1); selecting P1-0.2 × d2, i.e. P1-0.2 × 117.00, and calculating P1-23.40 mm; selecting P2-2G +0.6, i.e. P2-2 × 12.37+0.6, and calculating P2-25.34 mm; c is 117.00+2 × 23.40, i.e., c is 163.80 mm;

8. since c > 130mm, the diameter d5 of the output tray bearing hole 74 and the diameter a of the output tray center hole 75 are calculated according to the formula d5 ═ 0.65-1.3 × b and d5-d4-d1+ d3 > 6, a ═ 2b-d5-2e, where e ≧ 1.5 and a > 0; d5 is selected to be 0.82 x b, namely d5 is 0.82 x 32.5, d5 is calculated to be 26.65mm, and d5-d4-d1+ d3 is 26.65-12.33-27.95+20.76 is calculated to be 7.13, so that d5-d4-d1+ d3 > 6 is satisfied; selecting e-4.5, namely a-2 × 32.5-26.65-2 × 4.5, and calculating a-29.35 mm;

9. selecting and determining the specifications and the number of the column bolts 72 and the taper pins 73, and calculating whether the torque is qualified; selecting the number N1 of the column bolts 72 as N1-6, the specification Mj1 of the column bolts 72 as M8, the fastening force F1 of the corresponding column bolts 72 as F1-23960N, and selecting D1-2.35 × b-2.35 × 32.5 according to the formula D1 of the distributed pitch circle diameter of the column bolts 72 as (2-2.8) × b, namely selecting D1-76.38 mm; according to the formula

The torque T1 transmitted by the table stud 72 is calculated,

namely, T1 is 1097.97N; selecting the number m of taper pins 73 to be 3, the diameter D6 of the taper pins 73 to be 6mm, the shear stress tau of the taper pins 73 to be 196N/mm, and selecting D2 to be 2 x b to be 2 x 32.5 according to the distribution pitch circle diameter formula D2 of the taper pins 73 to be (1.4-2.9) x b, namely D2 to be 65.00 mm; according to the formula

The torque T2 transmitted by the taper pin 73 is calculated,

namely T2-540.32 Nm; the total torque T3 is T3 ═ T1+ T2 and

satisfies the conditions

10. Selecting and determining the number and specification of the pin gear housing bolts 1101, and calculating whether the torque of the pin gear housing bolts 1101 is qualified; selecting N4 as N4 as 16, selecting Mj2 as M6, namely j2 as 6, selecting D4 as c-j2-4 as 163.80-6-4, namely D4 as 153.80mm according to a distributed pitch circle diameter formula D4 as c-j2- (2-10), and selecting F4 as F4 as 13180N; according to the formula

The torque T4 transmitted by the pin housing bolt 1101 is calculated,

namely T4-3243.33 Nm; and is

Satisfies the conditions

11. Selecting and determining the number and specification of the output shaft bolts 83, and calculating whether the torque of the output shaft bolts 83 is qualified; selecting N5 as N5 as 9, Mj3 as output shaft bolts 83 specification as M8, F5 as F5 as F23960N, and selecting D5 as 3.6 × b as 3.6 × 32.5 according to the formula D5 (1.7-3.8) × b of the distribution pitch diameter of the output shaft bolts 83, namely D5 as 117.00 mm; according to the formula

The torque T5 transmitted by the output shaft bolt 83 is calculated,

namely T5-2522.99 Nm; and is

Satisfies the conditions

the rated torque T is 412Nm, the center distance b is 32.5mm, the diameter d3 of the camshaft 52 is 20.76mm, the diameter d4 of the non-camshaft 51 is 12.33mm, the diameter d1 of the cycloid wheel bearing hole 32 is 27.95mm, and the diameter d2 of the center circle of the needle roller 2 is 117.00 mm; the diameter Dwe of the cam needle roller and the retainer needle roller 101 on the retainer 10 is 3.59mm, the number M of the retainer needle rollers 101 is 14, and the length Lwe of the retainer needle rollers 101 is 9.90 mm; the thickness G of the pin gear shell 1 is 12.37mm, the outer tooth number Z1 of the cycloid gear is 39, the inner tooth number Z2 of the pin gear shell is 40, the short amplitude coefficient Ki is 0.75, and the eccentricity A is 1.10 mm; the diameter d5 of the bearing hole 74 of the output tray is 26.65mm, and the diameter a of the central hole 75 of the output tray is 29.35 mm; the radial thickness P1 of the pin gear shell 1 is 23.40mm, the inner tooth width P2 of the pin gear shell is 25.34mm, and the outer diameter c of the pin gear shell 1 is 163.80 mm; the number N1 of the column bolts 72 is 6, the specification Mj1 of the column bolts 72 is M8, the diameter D1 of the distributed pitch circle of the column bolts 72 is 76.38mm, and the torque T1 transmitted by the column bolts 72 is 1097.97N; the number m of the taper pins 73 is 3, the diameter D6 of the taper pins 73 is 6mm, the shear stress tau of the taper pins 73 is 196N/mm, the distributed pitch circle diameter D2 of the taper pins 73 is 65.00mm, and the torque T2 transmitted by the taper pins 73 is 540.32 Nm; the number N4 of the pin housing bolts 1101 is 16, the specification Mj2 of the pin housing bolts 1101 is M6, the diameter D4 of the pitch circle of the pin housing bolts 1101 is 153.80mm, and the torque T4 transmitted by the pin housing bolts 1101 is 3243.33 Nm; the number N5 of the output shaft bolts 83 is 9, the specification Mj3 of the output shaft bolts 83 is M8, the distributed pitch circle diameter D5 of the output shaft bolts 83 is 117mm, and the torque T5 transmitted by the output shaft bolts 83 is 2522.99 Nm.

Different from the first to fourth embodiments, in the present embodiment, the outer diameter c of the gear housing 1 is 163.80mm, that is, the diameter c is larger than 130mm, so as shown in fig. 13, a tapered roller bearing 13 is disposed between the output disc carrier bearing hole 74 and the non-cam shaft 51 of the eccentric shaft 5, so as to limit the eccentric shaft 5 on the output disc carrier 7, and prevent the eccentric shaft 5 from moving axially and even separating from the output disc carrier 7.

Example six:

in the sixth embodiment, values and calculation results related to the RV reducer with the novel structure are as follows, and the calculation results all retain two digits after the decimal point:

1. firstly, selecting a proper rated torque T value and a proper center distance b value, wherein T is 1000Nm, and b is 40 mm;

2. according to formula b x (d3)²(10 ~ 80) x T and b x (d4)²Calculating the diameter d3 of the camshaft 52 and the diameter d4 of the non-camshaft 51 respectively as (6-40) multiplied by T; selection of b × (d3)²29T, i.e. 40 × (d3)²When the measured value is 29X 1000, d 3mm is 26.93mm, b X (d4) is selected²14T, i.e40×(d4)²14 × 1000, calculating d 4-18.71 mm;

3. calculating the diameter d1 of the cycloid wheel bearing hole 32 and the diameter d2 of the central circle of the needle roller 2 according to the formulas d1 (0.6-1.3) x b and d2 (3-4) x b respectively; d 1-0.92 × b-0.92 × 40, i.e., d 1-36.80 mm, d 2-3.56 × b-3.56 × 40, i.e., d 2-142.40 mm;

4. according to the formula

calculating Dwe-4.94 mm;

calculating M-16;

so fc is chosen to be 88.10 and Td is chosen to be 23T, i.e.

Calculating Lwe-8.61 mm;

5. calculating the thickness G of the pin gear shell 1 according to the formula G ═ 0.8-1.8 x Lwe; selecting 1.24 × Lwe, namely 1.24 × 8.61, and calculating 10.68 mm;

Calculating an eccentricity A; the short amplitude coefficient Ki is 0.8,

computingThe A is 1.42 mm;

7. calculating the radial thickness P1 of the needle gear case 1, the internal tooth width P2 of the needle gear case 1 and the external diameter c of the needle gear case 1 according to P1 (0.13-0.28) x d2, c (d 2+2P 1) and P2 (2G + (0.2-1); selecting P1-0.21 × d2, i.e. P1-0.21 × 142.40, and calculating P1-29.90 mm; selecting P2-2G +0.6, i.e. P2-2 × 10.68+0.6, and calculating P2-21.96 mm; c is 142.40+2 × 29.90, i.e., c is 202.21 mm;

8. since c > 130mm, the diameter d5 of the output tray bearing hole 74 and the diameter a of the output tray center hole 75 are calculated according to the formula d5 ═ 0.65-1.3 × b and d5-d4-d1+ d3 > 6, a ═ 2b-d5-2e, where e ≧ 1.5 and a > 0; d5 is selected to be 0.9 × b, namely d5 is 0.9 × 40, d5 is calculated to be 36.00mm, and d5-d4-d1+ d3 is 36.00-18.71-36.80+26.93 is calculated to be 7.42, so that d5-d4-d1+ d3 is more than 6; selecting e-6, i.e. a-2 × 40-36.00-2 × 6, and calculating a-32.00 mm;

9. selecting and determining the specifications and the number of the column bolts 72 and the taper pins 73, and calculating whether the torque is qualified; selecting the number N1 of the column bolts 72 as N1-9, the specification Mj1 of the column bolts 72 as M10, the fastening force F1 of the corresponding column bolts 72 as F1-38080N, and selecting D1-2.7 × b-2.7 × 40, namely D1-108.00 mm according to the distribution pitch circle diameter formula D1 of the column bolts 72 as (2-2.8) × b; according to the formula

The torque T1 transmitted by the table stud 72 is calculated,

namely, T1 is 3701.38N; selecting the number m of taper pins 73 to be 3, the diameter D6 of the taper pins 73 to be 6mm, the shear stress tau of the taper pins 73 to be 196N/mm, and selecting the D2 to be 2.2 x b to be 2.2 x 40 according to the distribution pitch circle diameter formula D2 of the taper pins 73 to be (1.4-2.9) x b, namely D2 to be 88.00 mm; according to the formula

The torque T2 transmitted by the taper pin 73 is calculated,

namely T2-731.51 Nm; total torqueT3 is T3 ═ T1+ T2 and

satisfies the conditions

10. Selecting and determining the number and specification of the pin gear housing bolts 1101, and calculating whether the torque of the pin gear housing bolts 1101 is qualified; selecting N4 as N4 as 16, selecting M8 as the specification of the pin-shell bolt 1101, namely j2 as 8, selecting D4 as c-j2-5 as 202.21-8-5 as D4 as 189.21mm according to a distributed pitch circle diameter formula D4 as c-j2- (2-10) of the pin-shell bolt 1101, wherein the specification Mj2 of the pin-shell bolt 1101 is M8, namely j2 as 8, and the corresponding fastening force F4 of the pin-shell bolt 1101 is F4 as 23960N; according to the formula

The torque T4 transmitted by the pin housing bolt 1101 is calculated,

namely T4-7253.48 Nm; and is

Satisfies the conditions

11. Selecting and determining the number and specification of the output shaft bolts 83, and calculating whether the torque of the output shaft bolts 83 is qualified; selecting N5 as N5 as 12, Mj3 as output shaft bolts 83 specification as M10, F5 as F5 as 38080N, and selecting D5 as 3.3 × b as 3.3 × 40 according to the formula D5 as (1.7-3.8) × b of the distribution pitch diameter of the output shaft bolts 83, namely D5 as 132.00 mm; according to the formula

The torque T5 transmitted by the output shaft bolt 83 is calculated,

namely T5-6031.87 Nm; and is

Satisfies the conditions

the rated torque T is 1000Nm, the center distance b is 40mm, the diameter d3 of the camshaft 52 is 26.93mm, the diameter d4 of the non-camshaft 51 is 18.71mm, the diameter d1 of the cycloid wheel bearing hole 32 is 36.80mm, and the diameter d2 of the center circle of the needle roller 2 is 142.40 mm; the diameter Dwe of the cam needle roller and the retainer needle roller 101 on the retainer 10 is 4.94mm, the number M of the retainer needle rollers 101 is 16, and the length Lwe of the retainer needle rollers 101 is 8.61 mm; the thickness G of the pin gear shell 1 is 10.68mm, the external tooth number Z1 of the cycloid gear is 39, the internal tooth number Z2 of the pin gear shell is 40, the short amplitude coefficient Ki is 0.8, and the eccentricity A is 1.42 mm; the diameter d5 of the bearing hole 74 of the output disk frame is 36.00mm, and the diameter a of the central hole 75 of the output disk frame is 32.00 mm; the radial thickness P1 of the pin gear shell 1 is 29.90mm, the inner tooth width P2 of the pin gear shell is 21.96mm, and the outer diameter c of the pin gear shell 1 is 202.21 mm; the number N1 of the column bolts 72 is 9, the specification Mj1 of the column bolts 72 is M10, the diameter D1 of the distributed pitch circle of the column bolts 72 is 108.00mm, and the torque T1 transmitted by the column bolts 72 is 3701.38N; the number m of taper pins 73 is 3, the diameter D6 of the taper pins 73 is 6mm, the shear stress tau of the taper pins 73 is 196N/mm, the distributed pitch circle diameter D2 of the taper pins 73 is 88.00mm, and the torque T2 transmitted by the taper pins 73 is 731.51 Nm; the number N4 of the pin housing bolts 1101 is 16, the specification Mj2 of the pin housing bolts 1101 is M8, the diameter D4 of the pitch circle of the pin housing bolts 1101 is 189.21mm, and the torque T4 transmitted by the pin housing bolts 1101 is 7253.48 Nm; the number N5 of the output shaft bolts 83 is 12, the specification Mj3 of the output shaft bolts 83 is M10, the distributed pitch circle diameter D5 of the output shaft bolts 83 is 132.00mm, and the torque T5 transmitted by the output shaft bolts 83 is 6031.87 Nm.

Similarly, in the present embodiment, the outer diameter c of the needle housing 1 is 202.21mm, i.e., the diameter c is larger than 130mm, so as shown in fig. 13, a tapered roller bearing 13 is disposed between the output disc carrier bearing hole 74 and the non-cam shaft 51 of the eccentric shaft 5, and the eccentric shaft 5 is limited on the output disc carrier 7, thereby preventing the eccentric shaft 5 from moving axially and even separating from the output disc carrier 7.

Example seven:

in the seventh embodiment, values and calculation results related to the RV reducer with the novel structure are as follows, and the calculation results all retain two digits after the decimal point:

1. firstly, selecting a proper rated torque T value and a proper center distance b value, wherein T is 1960Nm, and b is 50 mm;

2. according to formula b x (d3)²(10 ~ 80) x T and b x (d4)²Calculating the diameter d3 of the camshaft 52 and the diameter d4 of the non-camshaft 51 respectively as (6-40) multiplied by T; selection of b × (d3)²28T, i.e. 50 × (d3)²28X 1960, d3 is calculated to 33.13mm, b (d4)²16T, i.e. 50 × (d4)²16 × 1960, and d4 is calculated to be 25.04 mm;

3. calculating the diameter d1 of the cycloid wheel bearing hole 32 and the diameter d2 of the central circle of the needle roller 2 according to the formulas d1 (0.6-1.3) x b and d2 (3-4) x b respectively; d 1-1.3 × b-1.3 × 50, i.e., d 1-65.00 mm, d 2-4 × b-4 × 50, i.e., d 2-200.00 mm;

4. according to the formula

calculating Dwe-15.93 mm;

calculating M to 8;

so fc is chosen to be 82.20 and Td is chosen to be 25T, i.e.

Lwe mm is calculated as 9.63 mm;

5. calculating the thickness G of the pin gear shell 1 according to the formula G ═ 0.8-1.8 x Lwe; selecting 1.3 × Lwe, namely 1.3 × 9.63, and calculating 12.53 mm;

Calculating an eccentricity A; the short amplitude coefficient Ki is selected to be 0.78,

calculating A to be 1.95 mm;

7. calculating the radial thickness P1, the inner tooth width P2 and the outer diameter c of the needle tooth shell 1 according to the P1 (0.13-0.28) x d2, c (d 2+2P 1) and P2 (2G + (0.2-1); selecting P1-0.22 × d2, i.e. P1-0.22 × 200.00, and calculating P1-44.00 mm; selecting P2-2G +0.55, i.e. P2-2 × 12.53+0.55, and calculating P2-25.60 mm; c is 200.00+2 × 44.00, i.e., c is 288.00 mm;

8. since c > 130mm, the diameter d5 of the output tray bearing hole 74 and the diameter a of the output tray center hole 75 are calculated according to the formula d5 ═ 0.65-1.3 × b and d5-d4-d1+ d3 > 6, a ═ 2b-d5-2e, where e ≧ 1.5 and a > 0; d5 is selected to be 1.3 × b, that is, d5 is 1.3 × 50, d5 is calculated to be 65.00mm, and d5-d4-d1+ d3 is 65.00-25.04-65.00+33.13 is calculated to be 8.09, so that d5-d4-d1+ d3 is more than 6; selecting e-4, i.e. a-2 × 50-65.00-2 × 4, and calculating a-27.00 mm;

9. selecting and determining the specifications and the number of the column bolts 72 and the taper pins 73, and calculating whether the torque is qualified; selecting the number N1 of the column bolts 72 as N1-6, the specification Mj1 of the column bolts 72 as M16, the fastening force F1 of the corresponding column bolts 72 as F1-103410N, and selecting D1-2.5 × b-2.5 × 50 according to the distribution pitch circle diameter formula D1 of the column bolts 72 as (2-2.8) × b, that is, D1-125.00 mm; according to the formula

Calculating the torque transmitted by the table stud 72The moment T1 of the force of gravity,

namely, T1 is 7755.75N; selecting the number m of taper pins 73 to be 3, the diameter D6 of the taper pins 73 to be 8mm, the shear stress tau of the taper pins 73 to be 196N/mm, and selecting the D2 to be 2.7 x b to be 2.7 x 50 according to the distribution pitch circle diameter formula D2 of the taper pins 73 to be (1.4-2.9) x b, namely D2 to be 135.00 mm; according to the formula

The torque T2 transmitted by the taper pin 73 is calculated,

namely T2-1995.04 Nm; the total torque T3 is T3 ═ T1+ T2 and

satisfies the conditions

10. Selecting and determining the number and specification of the pin gear housing bolts 1101, and calculating whether the torque of the pin gear housing bolts 1101 is qualified; selecting N4 as N4 as 16, selecting M10 as specification Mj2 of the pin housing bolts 1101, namely j2 as 10, selecting D4 as c-j2-5 as 288.00-10-5 as D4 as 273.00mm according to a formula D4 as distributed pitch circle diameter of the pin housing bolts 1101, c-j2- (2-10), and selecting F4 as 38080N; according to the formula

The torque T4 transmitted by the pin housing bolt 1101 is calculated,

namely T4-16633.34 Nm; and is

Satisfies the conditions

11. Selecting and determining the number and specification of the output shaft bolts 83, and calculating whether the torque of the output shaft bolts 83 is qualified; selecting N5 as N5 as 18, Mj3 as the specification of the output shaft bolts 83 as M10, F5 as F5 as F38080N, and selecting D5 as 3.5 × b as 3.5 × 50, namely D5 as 175.00mm according to a distribution pitch circle diameter formula D5 of the output shaft bolts 83 (1.7-3.8) × b; according to the formula

The torque T5 transmitted by the output shaft bolt 83 is calculated,

namely T5-11995.20 Nm; and is

Satisfies the conditions

the rated torque T is 1960Nm, the center distance b is 50mm, the diameter d3 of the camshaft 52 is 33.13mm, the diameter d4 of the non-camshaft 51 is 25.04mm, the diameter d1 of the cycloid wheel bearing hole 32 is 65.00mm, and the diameter d2 of the center circle of the needle roller 2 is 200.00 mm; the diameter Dwe of the cam needle roller and the retainer needle roller 101 on the retainer 10 is 15.93mm, the number M of the retainer needle rollers 101 is 8, and the length Lwe of the retainer needle rollers 101 is 9.63 mm; the thickness G of the pin gear shell 1 is 12.53mm, the outer tooth number Z1 of the cycloid gear is 39, the inner tooth number Z2 of the pin gear shell is 40, the short amplitude coefficient Ki is 0.78, and the eccentricity A is 1.95 mm; the diameter d5 of the bearing hole 74 of the output disk frame is 65.00mm, and the diameter a of the central hole 75 of the output disk frame is 27.00 mm; the radial thickness P1 of the pin gear shell 1 is 44.00mm, the inner tooth width P2 of the pin gear shell is 25.60mm, and the outer diameter c of the pin gear shell 1 is 288.00 mm; the number N1 of the column bolts 72 is 6, the specification Mj1 of the column bolts 72 is M16, the diameter D1 of the distributed pitch circle of the column bolts 72 is 125.00mm, and the torque T1 transmitted by the column bolts 72 is 7755.75N; the number m of the taper pins 73 is 3, the diameter D6 of the taper pins 73 is 8mm, the shear stress tau of the taper pins 73 is 196N/mm, the distributed pitch circle diameter D2 of the taper pins 73 is 135.00mm, and the torque T2 transmitted by the taper pins 73 is 1995.04 Nm; the number N4 of the pin housing bolts 1101 is 16, the specification Mj2 of the pin housing bolts 1101 is M10, the diameter D4 of the pitch circle of the pin housing bolts 1101 is 273.00mm, and the torque T4 transmitted by the pin housing bolts 1101 is 16633.34 Nm; the number N5 of output shaft bolts 83 is 18, the specification Mj3 of the output shaft bolts 83 is M10, the distributed pitch circle diameter D5 of the output shaft bolts 83 is 175.00mm, and the torque T5 transmitted by the output shaft bolts 83 is 11995.20 Nm.

Similarly, in the present embodiment, the outer diameter c of the needle housing 1 is 288.00mm, i.e., the diameter c is larger than 130mm, so as shown in fig. 13, a tapered roller bearing 13 is disposed between the output disc carrier bearing hole 74 and the non-cam shaft 51 of the eccentric shaft 5, and the eccentric shaft 5 is limited on the output disc carrier 7, thereby preventing the eccentric shaft 5 from moving axially and even separating from the output disc carrier 7.

Example eight:

the values and calculation results related to the novel-structure RV reducer in the eighth embodiment are as follows, and the calculation results retain two digits after the decimal point:

1. firstly, selecting a proper rated torque T value and a proper center distance b value, wherein T is 3136Nm, and b is 56 mm;

2. according to formula b x (d3)²(10 ~ 80) x T and b x (d4)²Calculating the diameter d3 of the camshaft 52 and the diameter d4 of the non-camshaft 51 respectively as (6-40) multiplied by T; selection of b × (d3)²26T, i.e. 56 × (d3)²When the measured value is 26X 3136, d3 is 38.16mm, b is selected (d4)²15T, i.e. 56 × (d4)²15 × 3136, and d4 is calculated to be 28.98 mm;

3. calculating the diameter d1 of the cycloid wheel bearing hole 32 and the diameter d2 of the central circle of the needle roller 2 according to the formulas d1 (0.6-1.3) x b and d2 (3-4) x b respectively; d 1-1.23 × b-1.23 × 56, i.e., d 1-68.88 mm, d 2-3.8 × b-3.8 × 56, i.e., d 2-212.80 mm;

4. according to the formula

ComputingThe diameter Dwe of the cage needle roller 101 on the cam needle roller and cage 10, the number M of the cage needle rollers 101, the length Lwe of the cage needle rollers 101, and the like;

calculating Dwe-15.36 mm;

calculating M to 9;

so fc is chosen to be 84.50 and Td is chosen to be 23T, i.e.

Calculating Lwe-14.36 mm;

5. calculating the thickness G of the pin gear shell 1 according to the formula G ═ 0.8-1.8 x Lwe; selecting 1.25 × Lwe, namely 1.25 × 14.36, and calculating 17.95 mm;

Calculating an eccentricity A; the short amplitude coefficient Ki is selected to be 0.79,

calculating A to be 2.10 mm;

7. calculating the radial thickness P1 of the needle gear case 1, the internal tooth width P2 of the needle gear case 1 and the external diameter c of the needle gear case 1 according to P1 (0.13-0.28) x d2, c (d 2+2P 1) and P2 (2G + (0.2-1); selecting P1-0.23 × d2, namely P1-0.23 × 212.80, and calculating P1-48.94 mm; selecting P2-2G +0.7, i.e. P2-2 × 17.95+0.7, and calculating P2-36.60 mm; c is 212.80+2 × 48.94, i.e., c is 310.69 mm;

8. since c > 130mm, the diameter d5 of the output tray bearing hole 74 and the diameter a of the output tray center hole 75 are calculated according to the formula d5 ═ 0.65-1.3 × b and d5-d4-d1+ d3 > 6, a ═ 2b-d5-2e, where e ≧ 1.5 and a > 0; d5 is selected to be 1.26 × b, namely d5 is 1.26 × 56, d5 is calculated to be 70.56mm, and d5-d4-d1+ d3 is 70.56-28.98-68.88+38.16 is 10.85, so that d5-d4-d1+ d3 is more than 6; selecting e-4.5, i.e. a-2 × 56-70.56-2 × 4.5, and calculating a-32.44 mm;

9. selecting and determining the specifications and the number of the column bolts 72 and the taper pins 73, and calculating whether the torque is qualified; selecting the number N1 of the column bolts 72 as N1-9, the specification Mj1 of the column bolts 72 as M18, the fastening force F1 of the corresponding column bolts 72 as F1-125000N, and selecting D1-2.35 × b-2.35 × 56 according to the distribution pitch circle diameter formula D1 of the column bolts 72 (2-2.8) × b, namely D1-131.60 mm; according to the formula

The torque T1 transmitted by the table stud 72 is calculated,

namely, T1 is 14805.00N; selecting the number m of taper pins 73 to be 3, the diameter D6 of the taper pins 73 to be 8mm, the shear stress tau of the taper pins 73 to be 196N/mm, and selecting D2 to be 2 x b to be 2 x 56 according to the distribution pitch circle diameter formula D2 of the taper pins 73 to be (1.4-2.9) x b, namely D2 to 112.00 mm; according to the formula

The torque T2 transmitted by the taper pin 73 is calculated,

namely T2-1655.14 Nm; the total torque T3 is T3 ═ T1+ T2 and

satisfies the conditions

10. Selecting and determining the number and specification of the pin gear housing bolts 1101, and calculating whether the torque of the pin gear housing bolts 1101 is qualified; the number N4 of the pin housing bolts 1101 was selected to be N4-20, the gauge Mj2 of the pin housing bolts 1101 was M10, i.e. j2-10, and the corresponding fastening force F4 of the pin housing bolts 1101 was selected to be F4-38080N, according to the pin housing bolts 1101, selecting D4 as a distributed pitch circle diameter formula D4 c-j2- (2-10), namely D4 as 294.69mm, wherein c-j2-6 is 310.69-10-6; according to the formula

The torque T4 transmitted by the pin housing bolt 1101 is calculated,

namely T4-22443.44 Nm; and is

Satisfies the conditions

11. Selecting and determining the number and specification of the output shaft bolts 83, and calculating whether the torque of the output shaft bolts 83 is qualified; selecting N5 as N5 as 21, Mj3 as M12, and F5 fastening force F5 as F5 as 55360N, and selecting D5 as 3.3 × b as 3.3 × 56, that is, D5 as 184.80mm, according to the formula D5 of the distribution pitch circle diameter of the output shaft bolt 83 (1.7-3.8) × b; according to the formula

The torque T5 transmitted by the output shaft bolt 83 is calculated,

namely T5-21484.11 Nm; and is

Satisfies the conditions

the rated torque T is 3136Nm, the center distance b is 56mm, the diameter d3 of the cam shaft 52 is 38.16mm, the diameter d4 of the non-cam shaft 51 is 28.98mm, the diameter d1 of the cycloid wheel bearing hole 32 is 68.88mm, and the diameter d2 of the center circle of the needle roller 2 is 212.80 mm; the diameter Dwe of the cam needle roller and the retainer needle roller 101 on the retainer 10 is 15.36mm, the number M of the retainer needle rollers 101 is 9, and the length Lwe of the retainer needle rollers 101 is 14.36 mm; the thickness G of the pin gear shell 1 is 17.95mm, the external tooth number Z1 of the cycloid gear is 39, the internal tooth number Z2 of the pin gear shell is 40, the short amplitude coefficient Ki is 0.79, and the eccentricity A is 2.10 mm; the diameter d5 of the bearing hole 74 of the output disk frame is 70.56mm, and the diameter a of the central hole 75 of the output disk frame is 32.44 mm; the radial thickness P1 of the pin gear shell 1 is 48.94mm, the inner tooth width P2 of the pin gear shell is 36.60mm, and the outer diameter c of the pin gear shell 1 is 310.69 mm; the number N1 of the column bolts 72 is 9, the specification Mj1 of the column bolts 72 is M18, the diameter D1 of the distributed pitch circle of the column bolts 72 is 131.60mm, and the torque T1 transmitted by the column bolts 72 is 14805.00N; the number m of taper pins 73 is 3, the diameter D6 of the taper pins 73 is 8mm, the shear stress tau of the taper pins 73 is 196N/mm, the distributed pitch circle diameter D2 of the taper pins 73 is 112.00mm, and the torque T2 transmitted by the taper pins 73 is 1655.14 Nm; the number N4 of the pin housing bolts 1101 is 20, the specification Mj2 of the pin housing bolts 1101 is M10, the diameter D4 of the pitch circle of the pin housing bolts 1101 is 294.69mm, and the torque T4 transmitted by the pin housing bolts 1101 is 22443.44 Nm; the number N5 of the output shaft bolts 83 is 21, the specification Mj3 of the output shaft bolts 83 is M12, the distributed pitch circle diameter D5 of the output shaft bolts 83 is 184.80mm, and the torque T5 transmitted by the output shaft bolts 83 is 21484.11 Nm.

Similarly, in the present embodiment, the outer diameter c of the needle housing 1 is 310.69mm, i.e., the diameter c is larger than 130mm, so as shown in fig. 13, a tapered roller bearing 13 is disposed between the output disc carrier bearing hole 74 and the non-cam shaft 51 of the eccentric shaft 5, and the eccentric shaft 5 is limited on the output disc carrier 7, thereby preventing the eccentric shaft 5 from moving axially and even separating from the output disc carrier 7.

Example nine:

in the ninth embodiment, values and calculation results related to the RV reducer with the novel structure are as follows, and the calculation results both retain two digits after the decimal point:

1. firstly, selecting a proper rated torque T value and a proper center distance b value, wherein T is 4410Nm, and b is 60 mm;

2. according to formula b x (d3)²(10 ~ 80) x T and b x (d4)²Calculating the diameter d3 of the camshaft 52 and the diameter d4 of the non-camshaft 51 respectively as (6-40) multiplied by T; selection of b × (d3)²24T, i.e. 60 × (d)3)²When the measured value is 24X 4410, d3 is calculated to be 42.00mm, and b (d4) is selected²13T, i.e. 60 × (d4)²D4 is calculated to be 30.91mm when 13 × 4410 is obtained;

3. calculating the diameter d1 of the cycloid wheel bearing hole 32 and the diameter d2 of the central circle of the needle roller 2 according to the formulas d1 (0.6-1.3) x b and d2 (3-4) x b respectively; d1 ═ 1.2 × b ═ 1.2 × 60, i.e., d1 ═ 72.00mm, d2 ═ 3.8 × b ═ 3.8 × 60, i.e., d2 ═ 228.00 mm;

4. according to the formula

calculating Dwe-15.00 mm;

calculating M to be 10;

so fc is selected to be 86.40 and Td is selected to be 19T, i.e.

Calculating Lwe-15.78 mm;

5. calculating the thickness G of the pin gear shell 1 according to the formula G ═ 0.8-1.8 x Lwe; selecting 1.2 × Lwe, namely 1.2 × 15.78, and calculating 18.94 mm;

Calculating an eccentricity A; the short amplitude coefficient Ki is 0.81,

calculating A to be 2.31 mm;

7. calculating the radial thickness P1 of the needle gear case 1, the internal tooth width P2 of the needle gear case 1 and the external diameter c of the needle gear case 1 according to P1 (0.13-0.28) x d2, c (d 2+2P 1) and P2 (2G + (0.2-1); selecting P1-0.23 × d2, namely P1-0.23 × 228.00, and calculating P1-52.44 mm; selecting P2-2G +0.55, i.e. P2-2 × 18.94+0.55, and calculating P2-38.43 mm; c is 228.00+2 × 52.44, i.e., c is 332.88 mm;

8. since c > 130mm, the diameter d5 of the output tray bearing hole 74 and the diameter a of the output tray center hole 75 are calculated according to the formula d5 ═ 0.65-1.3 × b and d5-d4-d1+ d3 > 6, a ═ 2b-d5-2e, where e ≧ 1.5 and a > 0; d5 is selected to be 1.22 × b, namely d5 is 1.22 × 60, d5 is calculated to be 73.20mm, and d5-d4-d1+ d3 is 73.20-30.91-72.00+42.00 is calculated to be 12.29, so that d5-d4-d1+ d3 is more than 6; selecting e-5, i.e. a-2 × 60-73.20-2 × 5, and calculating a-36.80 mm;

9. selecting and determining the specifications and the number of the column bolts 72 and the taper pins 73, and calculating whether the torque is qualified; selecting the number N1 of the column bolts 72 as N1-6, the specification Mj1 of the column bolts 72 as M20, the fastening force F1 of the corresponding column bolts 72 as F1-162500N, and selecting D1-2.6 × b-2.6 × 60, namely D1-156.00 mm according to the distribution pitch circle diameter formula D1 of the column bolts 72 as (2-2.8) × b; according to the formula

The torque T1 transmitted by the table stud 72 is calculated,

namely, T1 is 15210.00N; selecting the number m of taper pins 73 to be 3, the diameter D6 of the taper pins 73 to be 10mm, the shear stress tau of the taper pins 73 to be 196N/mm, and selecting D2 to be 2 x b to be 2 x 60 according to the distribution pitch circle diameter formula D2 of the taper pins 73 to be (1.4-2.9) x b, namely D2 to be 120.00 mm; according to the formula

The torque T2 transmitted by the taper pin 73 is calculated,

namely T2-2770.88 Nm; the total torque T3 is T3 ═ T1+ T2 and

satisfies the conditions

10. Selecting and determining the number and specification of the pin gear housing bolts 1101, and calculating whether the torque of the pin gear housing bolts 1101 is qualified; selecting N4 of the pin-tooth shell bolts 1101 as N4-20, selecting M12 of specifications Mj2 of the pin-tooth shell bolts 1101, namely j 2-12, selecting D4-c-j 2-7-332.88-12-7, namely D4-313.88 mm according to a distributed pitch circle diameter formula D4-c-j 2- (2-10) of the pin-tooth shell bolts 1101, wherein the corresponding fastening force F4 of the pin-tooth shell bolts 1101 is F4-55360N; according to the formula

The torque T4 transmitted by the pin housing bolt 1101 is calculated,

namely T4-34752.79 Nm; and is

Satisfies the conditions

11. Selecting and determining the number and specification of the output shaft bolts 83, and calculating whether the torque of the output shaft bolts 83 is qualified; selecting N5 as N5 as 15, Mj3 as M16, F5 fastening force F5 as F5 as 103410N, and selecting D5 as 3.4 × b as 3.4 × 60 according to a distribution pitch circle diameter formula D5 of the output shaft bolts 83 (1.7-3.8) × b, namely D5 as 204.00 mm; according to the formula

The torque T5 transmitted by the output shaft bolt 83 is calculated,

namely T5-31643.46 Nm; and is

Satisfies the conditions

the rated torque T is 4410Nm, the center distance b is 60mm, the diameter d3 of the camshaft 52 is 42.00mm, the diameter d4 of the non-camshaft 51 is 30.91mm, the diameter d1 of the cycloid wheel bearing hole 32 is 72.00mm, and the diameter d2 of the center circle of the needle roller 2 is 228.00 mm; the diameter Dwe of the cam needle roller and the retainer needle roller 101 on the retainer 10 is 15.00mm, the number M of the retainer needle rollers 101 is 10, and the length Lwe of the retainer needle rollers 101 is 15.78 mm; the thickness G of the pin gear shell 1 is 18.94mm, the outer tooth number Z1 of the cycloid gear is 39, the inner tooth number Z2 of the pin gear shell is 40, the short amplitude coefficient Ki is 0.81, and the eccentricity A is 2.31 mm; the diameter d5 of the bearing hole 74 of the output disk frame is 73.20mm, and the diameter a of the central hole 75 of the output disk frame is 36.80 mm; the radial thickness P1 of the pin gear shell 1 is 52.44mm, the inner tooth width P2 of the pin gear shell is 38.43mm, and the outer diameter c of the pin gear shell 1 is 332.88 mm; the number N1 of the column bolts 72 is 6, the specification Mj1 of the column bolts 72 is M20, the diameter D1 of the distributed pitch circle of the column bolts 72 is 156.00mm, and the torque T1 transmitted by the column bolts 72 is 15210.00N; the number m of the taper pins 73 is 3, the diameter D6 of the taper pins 73 is 10mm, the shear stress tau of the taper pins 73 is 196N/mm, the distributed pitch circle diameter D2 of the taper pins 73 is 120.00mm, and the torque T2 transmitted by the taper pins 73 is 2770.88 Nm; the number N4 of the pin housing bolts 1101 is 20, the specification Mj2 of the pin housing bolts 1101 is M12, the diameter D4 of the pitch circle of the pin housing bolts 1101 is 313.88mm, and the torque T4 transmitted by the pin housing bolts 1101 is 34752.79 Nm; the number N5 of the output shaft bolts 83 is 15, the specification Mj3 of the output shaft bolts 83 is M16, the distributed pitch circle diameter D5 of the output shaft bolts 83 is 204.00mm, and the torque T5 transmitted by the output shaft bolts 83 is 31643.46 Nm.

Similarly, in the present embodiment, the outer diameter c of the needle housing 1 is 332.88mm, i.e., the diameter c is larger than 130mm, so as shown in fig. 13, a tapered roller bearing 13 is disposed between the output disc carrier bearing hole 74 and the non-cam shaft 51 of the eccentric shaft 5, and the eccentric shaft 5 is limited on the output disc carrier 7, thereby preventing the eccentric shaft 5 from moving axially and even separating from the output disc carrier 7.

Example ten:

in the tenth embodiment, values and calculation results related to the RV reducer with the novel structure are as follows, and the calculation results all retain two digits after the decimal point:

1. firstly, selecting a proper rated torque T value and a proper center distance b value, wherein T is 4900Nm, and b is 63 mm;

2. according to formula b x (d3)²(10 ~ 80) x T and b x (d4)²Calculating the diameter d3 of the camshaft 52 and the diameter d4 of the non-camshaft 51 respectively as (6-40) multiplied by T; selection of b × (d3)²26T, i.e. 63 × (d3)²26X 4900, 44.97mm (d3) and b (d4) are selected²13.5T, i.e. 63 × (d4)²D4 is calculated to be 32.40mm when the thickness is 13.5 multiplied by 4900;

3. calculating the diameter d1 of the cycloid wheel bearing hole 32 and the diameter d2 of the central circle of the needle roller 2 according to the formulas d1 (0.6-1.3) x b and d2 (3-4) x b respectively; d 1-1.25 × b-1.25 × 63, i.e., d 1-78.75 mm, d 2-3.4 × b-3.4 × 63, i.e., d 2-214.20 mm;

4. according to the formula

calculating Dwe-16.89 mm;

calculating M to 9;

so select fc85.80, Td 17T, i.e.

Calculating Lwe-14.86 mm;

5. calculating the thickness G of the pin gear shell 1 according to the formula G ═ 0.8-1.8 x Lwe; selecting 1.1 × Lwe, namely 1.1 × 14.86, and calculating 16.34 mm;

Calculating an eccentricity A; the short amplitude coefficient Ki is selected to be 0.82,

calculating A to be 2.20 mm;

7. calculating the radial thickness P1 of the needle gear case 1, the internal tooth width P2 of the needle gear case 1 and the external diameter c of the needle gear case 1 according to P1 (0.13-0.28) x d2, c (d 2+2P 1) and P2 (2G + (0.2-1); selecting P1-0.25 × d2, namely P1-0.25 × 214.20, and calculating P1-53.55 mm; selecting P2-2G +0.7, i.e. P2-2 × 16.34+0.7, and calculating P2-33.39 mm; c is 214.20+2 × 53.55, i.e., c is 321.30 mm;

8. since c > 130mm, the diameter d5 of the output tray bearing hole 74 and the diameter a of the output tray center hole 75 are calculated according to the formula d5 ═ 0.65-1.3 × b and d5-d4-d1+ d3 > 6, a ═ 2b-d5-2e, where e ≧ 1.5 and a > 0; d5 is selected to be 1.3 × b, namely d5 is 1.3 × 63, d5 is calculated to be 81.90mm, and d5-d4-d1+ d3 is 81.90-32.40-78.75+44.97 is calculated to be 15.72, so that d5-d4-d1+ d3 is more than 6; selecting e-6, i.e. a-2 × 63-81.90-2 × 6, and calculating a-32.10 mm;

9. selecting and determining the specifications and the number of the column bolts 72 and the taper pins 73, and calculating whether the torque is qualified; selecting the number N1 of the column bolts 72 as N1-6, the specification Mj1 of the column bolts 72 as M20, the fastening force F1 of the corresponding column bolts 72 as F1-162500N, and selecting D1-2.6 × b-2.6 × 63, namely D1-163.80 mm according to the distribution pitch circle diameter formula D1 of the column bolts 72 as (2-2.8) × b; according to the formula

The torque T1 transmitted by the table stud 72 is calculated,

namely, T1 is 15970.50N; selecting the number m of taper pins 73 to be 3, the diameter D6 of the taper pins 73 to be 12mm, the shear stress tau of the taper pins 73 to be 196N/mm, and selecting the D2 to be 2.2 x b to be 2.2 x 63 according to the distribution pitch circle diameter formula D2 of the taper pins 73 to be (1.4-2.9) x b, namely D2 to be 138.60 mm; according to the formula

The torque T2 transmitted by the taper pin 73 is calculated,

namely T2-4608.54 Nm; the total torque T3 is T3 ═ T1+ T2 and

satisfies the conditions

10. Selecting and determining the number and specification of the pin gear housing bolts 1101, and calculating whether the torque of the pin gear housing bolts 1101 is qualified; selecting N4 as N4 as 22, M12 as Mj2 as specification of the pin-shell bolt 1101, namely j2 as 12, and F4 as fastening force F4 as 55360N, and selecting D4 as c-j2-7 as 321.30-12-7 as D4 as 302.30mm according to a distributed pitch circle diameter formula D4 as c-j2- (2-10) of the pin-shell bolt 1101; according to the formula

The torque T4 transmitted by the pin housing bolt 1101 is calculated,

namely T4-36817.72 Nm; and is

Satisfies the conditions

11. Selecting and determining the number and specification of the output shaft bolts 83, and calculating whether the torque of the output shaft bolts 83 is qualified; selecting N5 as N5 as 21, Mj3 as output shaft bolts 83 specification as M16, selecting F5 as F5 as 103410N, and selecting D5 as 2.4 × b as 2.4 × 63 according to the formula D5 of the distribution pitch circle diameter of the output shaft bolts 83 (1.7-3.8) × b, namely D5 as 151.20 mm; according to the formula

The torque T5 transmitted by the output shaft bolt 83 is calculated,

namely T5-32834.74 Nm; and is

Satisfies the conditions

the rated torque T is 4900Nm, the center distance b is 63mm, the diameter d3 of the camshaft 52 is 44.97mm, the diameter d4 of the non-camshaft 51 is 32.40mm, the diameter d1 of the cycloid wheel bearing hole 32 is 78.75mm, and the diameter d2 of the center circle of the needle roller 2 is 214.20 mm; the diameter Dwe of the cam needle roller and the retainer needle roller 101 on the retainer 10 is 16.89mm, the number M of the retainer needle rollers 101 is 9, and the length Lwe of the retainer needle rollers 101 is 14.86 mm; the thickness G of the pin gear shell 1 is 16.34mm, the outer tooth number Z1 of the cycloid gear is 39, the inner tooth number Z2 of the pin gear shell is 40, the short amplitude coefficient Ki is 0.82, and the eccentricity A is 2.20 mm; the diameter d5 of the bearing hole 74 of the output tray is 81.90mm, and the diameter a of the central hole 75 of the output tray is 32.10 mm; the radial thickness P1 of the pin gear shell 1 is 53.55mm, the inner tooth width P2 of the pin gear shell is 33.39mm, and the outer diameter c of the pin gear shell 1 is 321.30 mm; the number N1 of the column bolts 72 is 6, the specification Mj1 of the column bolts 72 is M20, the diameter D1 of the distributed pitch circle of the column bolts 72 is 163.80mm, and the torque T1 transmitted by the column bolts 72 is 15970.50N; the number m of taper pins 73 is 3, the diameter D6 of the taper pins 73 is 12mm, the shear stress tau of the taper pins 73 is 196N/mm, the distributed pitch circle diameter D2 of the taper pins 73 is 138.60mm, and the torque T2 transmitted by the taper pins 73 is 4608.54 Nm; the number N4 of the pin housing bolts 1101 is 22, the specification Mj2 of the pin housing bolts 1101 is M12, the diameter D4 of the pitch circle of the pin housing bolts 1101 is 302.30mm, and the torque T4 transmitted by the pin housing bolts 1101 is 36817.72 Nm; the number N5 of the output shaft bolts 83 is 21, the specification Mj3 of the output shaft bolts 83 is M16, the distributed pitch circle diameter D5 of the output shaft bolts 83 is 151.20mm, and the torque T5 transmitted by the output shaft bolts 83 is 32834.74 Nm.

Similarly, in the present embodiment, the outer diameter c of the needle housing 1 is 321.30mm, i.e., the diameter c is larger than 130mm, so as shown in fig. 13, a tapered roller bearing 13 is disposed between the output disc carrier bearing hole 74 and the non-cam shaft 51 of the eccentric shaft 5, and the eccentric shaft 5 is limited on the output disc carrier 7, thereby preventing the eccentric shaft 5 from moving axially and even separating from the output disc carrier 7.

Example eleven:

in the eleventh embodiment, values and calculation results related to the RV reducer with the novel structure are as follows, and the calculation results all retain two digits after the decimal point:

1. firstly, selecting a proper rated torque T value and a proper center distance b value, wherein T is 7000Nm, and b is 79 mm;

2. according to formula b x (d3)²(10 ~ 80) x T and b x (d4)²Calculating the diameter d3 of the camshaft 52 and the diameter d4 of the non-camshaft 51 respectively as (6-40) multiplied by T; selection of b × (d3)²40T, 79 × (d3)²40X 7000, d3 is calculated to 59.53mm, b X (d4) is selected²20T, 79 × (d4)²20 × 7000, d4 is calculated to 42.10 mm;

3. calculating the diameter d1 of the cycloid wheel bearing hole 32 and the diameter d2 of the central circle of the needle roller 2 according to the formulas d1 (0.6-1.3) x b and d2 (3-4) x b respectively; d 1-1.1 × b-1.1 × 79, i.e., d 1-86.90 mm, d 2-3.5 × b-3.5 × 79, i.e., d 2-276.50 mm;

4. according to the formula

calculating Dwe-13.68 mm;

calculating M to be 11;

so fc is chosen to be 88.70 and Td is chosen to be 13T, i.e.

Calculating Lwe-17.58 mm;

5. calculating the thickness G of the pin gear shell 1 according to the formula G ═ 0.8-1.8 x Lwe; selecting 1.05 × Lwe, namely 1.05 × 17.58, and calculating 18.45 mm;

Calculating an eccentricity A; the short amplitude coefficient Ki is 0.85,

calculating A to be 2.94 mm;

7. calculating the radial thickness P1 of the needle gear case 1, the internal tooth width P2 of the needle gear case 1 and the external diameter c of the needle gear case 1 according to P1 (0.13-0.28) x d2, c (d 2+2P 1) and P2 (2G + (0.2-1); selecting P1-0.21 × d2, namely P1-0.21 × 276.50, and calculating P1-58.07 mm; selecting P2-2G +0.8, i.e. P2-2 × 18.45+0.8, and calculating P2-37.71 mm; c is 276.50+2 × 58.07, i.e., c is 392.63 mm;

8. since c > 130mm, the diameter d5 of the output tray bearing hole 74 and the diameter a of the output tray center hole 75 are calculated according to the formula d5 ═ 0.65-1.3 × b and d5-d4-d1+ d3 > 6, a ═ 2b-d5-2e, where e ≧ 1.5 and a > 0; d5 is selected to be 1.12 × b, namely d5 is selected to be 1.12 × 79, d5 is calculated to be 88.48mm, and d5-d4-d1+ d3 is 88.48-42.10-86.90+59.53 is calculated to be 19.02, so that d5-d4-d1+ d3 is more than 6; selecting e-8, namely a-2 × 79-88.48-2 × 8, and calculating a-53.52 mm;

9. selecting and determining the specifications and the number of the column bolts 72 and the taper pins 73, and calculating whether the torque is qualified; selecting the number N1 of the table bolts 72 as N1-9, the specification Mj1 of the table bolts 72 as M20, the fastening force F1 of the corresponding table bolts 72 as F1-162500N, and selecting D1-2.45 × b-2.45 × 79, namely D1-193.55 mm according to the distribution pitch circle diameter formula D1 of the table bolts 72 as (2-2.8) × b; according to the formula

The torque T1 transmitted by the table stud 72 is calculated,

namely, T1 is 28306.69N; selecting the number m of taper pins 73 to be 3, the diameter D6 of the taper pins 73 to be 12mm, the shear stress tau of the taper pins 73 to be 196N/mm, and selecting the D2 to be 2.6 x b to be 2.6 x 79 according to the distribution pitch circle diameter formula D2 of the taper pins 73 to be (1.4-2.9) x b, namely selecting the D2 to be 205.40 mm; according to the formula

The torque T2 transmitted by the taper pin 73 is calculated,

namely T2-6829.68 Nm; the total torque T3 is T3 ═ T1+ T2 and

satisfies the conditions

10. Selecting and determining the number and specification of the pin gear housing bolts 1101, and calculating whether the torque of the pin gear housing bolts 1101 is qualified; the number N4 of the pin gear housing bolts 1101 is selected to beN4 is 24, the gauge Mj2 of the pin-shell bolt 1101 is M12, i.e., j2 is 12, the corresponding fastening force F4 of the pin-shell bolt 1101 is F4 is 55360N, and D4 is c-j2-8 is 392.63-12-8, i.e., D4 is 372.63mm, according to the distribution pitch circle diameter formula D4 is c-j2- (2-10) of the pin-shell bolt 1101; according to the formula

The torque T4 transmitted by the pin housing bolt 1101 is calculated,

namely T4-49509.11 Nm; and is

Satisfies the conditions

11. Selecting and determining the number and specification of the output shaft bolts 83, and calculating whether the torque of the output shaft bolts 83 is qualified; selecting N5 as N5 as 18, Mj3 as the specification of the output shaft bolts 83 as M16, F5 as F5 as F103410N, and selecting D5 as 3 × b as 3 × 79, namely D5 as 237.00mm according to a distribution pitch circle diameter formula D5 of the output shaft bolts 83 (1.7-3.8) × b; according to the formula

The torque T5 transmitted by the output shaft bolt 83 is calculated,

namely T5-44114.71 Nm; and is

Satisfies the conditions

the rated torque T is 7000Nm, the center distance b is 79mm, the diameter d3 of the camshaft 52 is 59.53mm, the diameter d4 of the non-camshaft 51 is 42.10mm, the diameter d1 of the cycloid wheel bearing hole 32 is 86.90mm, and the diameter d2 of the center circle of the needle roller 2 is 276.50 mm; the diameter Dwe of the cam needle roller and the retainer needle roller 101 on the retainer 10 is 13.68mm, the number M of the retainer needle rollers 101 is 11, and the length Lwe of the retainer needle rollers 101 is 17.58 mm; the thickness G of the pin gear shell 1 is 18.45mm, the external tooth number Z1 of the cycloid gear is 39, the internal tooth number Z2 of the pin gear shell is 40, the short amplitude coefficient Ki is 0.85, and the eccentricity A is 2.94 mm; the diameter d5 of the bearing hole 74 of the output tray is 88.48mm, and the diameter a of the central hole 75 of the output tray is 53.52 mm; the radial thickness P1 of the pin gear shell 1 is 58.07mm, the inner tooth width P2 of the pin gear shell is 37.71mm, and the outer diameter c of the pin gear shell 1 is 392.63 mm; the number N1 of the column bolts 72 is 9, the specification Mj1 of the column bolts 72 is M20, the diameter D1 of the distributed pitch circle of the column bolts 72 is 193.55mm, and the torque T1 transmitted by the column bolts 72 is 28306.69N; the number m of the taper pins 73 is 3, the diameter D6 of the taper pins 73 is 12mm, the shear stress tau of the taper pins 73 is 196N/mm, the distributed pitch circle diameter D2 of the taper pins 73 is 205.40mm, and the torque T2 transmitted by the taper pins 73 is 6829.68 Nm; the number N4 of the pin housing bolts 1101 is 24, the specification Mj2 of the pin housing bolts 1101 is M12, the diameter D4 of the pitch circle of the pin housing bolts 1101 is 372.63mm, and the torque T4 transmitted by the pin housing bolts 1101 is 49509.11 Nm; the number N5 of the output shaft bolts 83 is 18, the specification Mj3 of the output shaft bolts 83 is M16, the distributed pitch circle diameter D5 of the output shaft bolts 83 is 237.00mm, and the torque T5 transmitted by the output shaft bolts 83 is 44114.71 Nm.

Similarly, in the present embodiment, the outer diameter c of the needle housing 1 is 392.63mm, i.e., the diameter c is larger than 130mm, so as shown in fig. 13, a tapered roller bearing 13 is disposed between the output disc carrier bearing hole 74 and the non-cam shaft 51 of the eccentric shaft 5, and the eccentric shaft 5 is limited on the output disc carrier 7, thereby preventing the eccentric shaft 5 from moving axially and even separating from the output disc carrier 7.

Example twelve:

in the twelfth embodiment, the values and calculation results related to the RV reducer with the novel structure are as follows, and the calculation results all retain two digits after the decimal point:

1. firstly, selecting a proper rated torque T value and a proper center distance b value, wherein T is 12000Nm, and b is 123 mm;

2. according to formula b x (d3)²(10 ~ 80) x T and b x (d4)²Calculating the diameter d3 of the camshaft 52 and the diameter d4 of the non-camshaft 51 respectively as (6-40) multiplied by T; selection of b × (d3)²80T, i.e. 123 × (d3)²80X 12000, d3 is calculated to 88.35mm, b X (d4)²40T, i.e. 123 × (d4)²D4 is calculated to be 62.47mm when the thickness is 40 multiplied by 12000;

3. calculating the diameter d1 of the cycloid wheel bearing hole 32 and the diameter d2 of the central circle of the needle roller 2 according to the formulas d1 (0.6-1.3) x b and d2 (3-4) x b respectively; d 1-1.1 × b-1.1 × 123, i.e., d 1-135.30 mm, d 2-3 × b-3 × 123, i.e., d 2-369.00 mm;

4. according to the formula

calculating Dwe-23.48 mm;

calculating M-14;

so fc is chosen to be 88.50 and Td is chosen to be 20T, i.e.

Calculating Lwe-23.07 mm;

5. calculating the thickness G of the pin gear shell 1 according to the formula G ═ 0.8-1.8 x Lwe; selecting 1.8 × Lwe, namely 1.8 × 23.07, and calculating 41.53 mm;

Calculating an eccentricity A; the short amplitude coefficient Ki is 0.842,

calculating A to be 3.88 mm;

7. calculating the radial thickness P1 of the needle gear case 1, the internal tooth width P2 of the needle gear case 1 and the external diameter c of the needle gear case 1 according to P1 (0.13-0.28) x d2, c (d 2+2P 1) and P2 (2G + (0.2-1); selecting P1-0.28 × d2, namely P1-0.28 × 369.00, and calculating P1-103.32 mm; selecting P2-2G +1, namely P2-2 × 41.53+1, and calculating P2-84.05 mm; c is 369.00+2 × 103.32, i.e., c is 575.64 mm;

8. since c > 130mm, the diameter d5 of the output tray bearing hole 74 and the diameter a of the output tray center hole 75 are calculated according to the formula d5 ═ 0.65-1.3 × b and d5-d4-d1+ d3 > 6, a ═ 2b-d5-2e, where e ≧ 1.5 and a > 0; d5 is selected to be 1.1 × b, namely d5 is selected to be 1.1 × 123, d5 is calculated to be 135.30mm, and d5-d4-d1+ d3 is 135.30-62.47-135.30+88.35 is calculated to be 25.88, so that d5-d4-d1+ d3 > 6 is satisfied; selecting e-8, namely a-2 × 123-135.30-2 × 8, and calculating a-94.70 mm;

9. selecting and determining the specifications and the number of the column bolts 72 and the taper pins 73, and calculating whether the torque is qualified; selecting the number N1 of the column bolts 72 as N1-12, the specification Mj1 of the column bolts 72 as M20, the fastening force F1 of the corresponding column bolts 72 as F1-162500N, and selecting D1-2.6 × b-2.6 × 123, namely D1-319.80 mm according to the distribution pitch circle diameter formula D1 of the column bolts 72 as (2-2.8) × b; according to the formula

The torque T1 transmitted by the table stud 72 is calculated,

namely, T1 is 62361.00N; selecting the number m of taper pins 73 to be 3, the diameter D6 of the taper pins 73 to be 16mm, the shear stress tau of the taper pins 73 to be 196N/mm, and selecting the D2 to be 2.9 x b to be 2.9 x 123 according to the distribution pitch circle diameter formula D2 of the taper pins 73 to be (1.4-2.9) x b, namely D2 to be 356.70 mm; according to the formula

The torque T2 transmitted by the taper pin 73 is calculated,

namely T2-21085.32 Nm; the total torque T3 is T3 ═ T1+ T2 and

satisfies the conditions

10. Selecting and determining the number and specification of the pin gear housing bolts 1101, and calculating whether the torque of the pin gear housing bolts 1101 is qualified; selecting N4 of the pin-tooth shell bolts 1101 as N4-32, selecting M12 of specifications Mj2 of the pin-tooth shell bolts 1101, namely j 2-12, selecting D4-c-j 2-10-575.64-12-10, namely D4-553.64 mm according to a distributed pitch circle diameter formula D4-c-j 2- (2-10) of the pin-tooth shell bolts 1101, wherein the corresponding fastening force F4 of the pin-tooth shell bolts 1101 is F4-55360N; according to the formula

The torque T4 transmitted by the pin housing bolt 1101 is calculated,

namely T4-98078.43 Nm; and is

Satisfies the conditions

11. Selecting and determining the number and specification of the output shaft bolts 83, and calculating whether the torque of the output shaft bolts 83 is qualified; selecting N5 as N5 as 21, Mj3 as output shaft bolts 83 specification as M16, selecting F5 as F5 as 103410N, and selecting D5 as 2.8 × b as 2.8 × 123 according to the formula D5 of the distribution pitch circle diameter of the output shaft bolts 83 (1.7-3.8) × b, namely D5 as 344.40 mm; according to the formula

The torque T5 transmitted by the output shaft bolt 83 is calculated,

namely T5-74790.25 Nm; and is

Satisfies the conditions

the rated torque T is 12000Nm, the center distance b is 123mm, the diameter d3 of the cam shaft 52 is 88.35mm, the diameter d4 of the non-cam shaft 51 is 62.47mm, the diameter d1 of the cycloid wheel bearing hole 32 is 135.30mm, and the diameter d2 of the center circle of the needle roller 2 is 369.00 mm; the diameter Dwe of the cam needle roller and the retainer needle roller 101 on the retainer 10 is 23.48mm, the number M of the retainer needle rollers 101 is 14, and the length Lwe of the retainer needle rollers 101 is 23.07 mm; the thickness G of the pin gear shell 1 is 41.53mm, the external tooth number Z1 of the cycloid gear is 39, the internal tooth number Z2 of the pin gear shell is 40, the short amplitude coefficient Ki is 0.842, and the eccentricity A is 3.88 mm; the diameter d5 of the bearing hole 74 of the output tray is 135.30mm, and the diameter a of the central hole 75 of the output tray is 94.70 mm; the radial thickness P1 of the pin gear shell 1 is 103.32mm, the inner tooth width P2 of the pin gear shell is 84.05mm, and the outer diameter c of the pin gear shell 1 is 575.64 mm; the number N1 of the column bolts 72 is 12, the specification Mj1 of the column bolts 72 is M20, the diameter D1 of the distributed pitch circle of the column bolts 72 is 319.80mm, and the torque T1 transmitted by the column bolts 72 is 62361.00N; the number m of taper pins 73 is 3, the diameter D6 of the taper pins 73 is 16mm, the shear stress tau of the taper pins 73 is 196N/mm, the distributed pitch circle diameter D2 of the taper pins 73 is 356.70mm, and the torque T2 transmitted by the taper pins 73 is 21085.32 Nm; the number N4 of the pin housing bolts 1101 is 32, the specification Mj2 of the pin housing bolts 1101 is M12, the diameter D4 of the pitch circle of the pin housing bolts 1101 is 553.64mm, and the torque T4 transmitted by the pin housing bolts 1101 is 98078.43 Nm; the number N5 of the output shaft bolts 83 is 21, the specification Mj3 of the output shaft bolts 83 is M16, the distributed pitch circle diameter D5 of the output shaft bolts 83 is 344.40mm, and the torque T5 transmitted by the output shaft bolts 83 is 74790.25 Nm.

Similarly, in the present embodiment, the outer diameter c of the pinion housing 1 is 575.64mm, that is, the diameter c is larger than 130mm, so as shown in fig. 13, a tapered roller bearing 13 is provided between the output carrier bearing hole 74 and the non-camshaft 51 of the eccentric shaft 5, and the eccentric shaft 5 is defined on the output carrier 7.

The table i schematically compares the center distance b of the RV reducer and the outer diameter c of the pin gear housing 1 in the twelve embodiments of the present invention with the center distance b1 and the outer diameter c1 of the RV reducer and the pin gear housing in the prior art under the same torque.

Table one:

as can be seen from the comparison in table one, the design scheme provided in example eight has a more significant effect than that of the other embodiments, and on the premise of satisfying the same torque, the center distance b of the RV reduction and the outer diameter c of the pin gear housing 1 in example eight are greatly reduced compared with those in the prior art, so that the volume and weight of the RV reducer are greatly reduced. Meanwhile, the RV reducer designed in the first embodiment, the second embodiment and the twelfth embodiment meets the rated torque requirement which is not met temporarily in the RV reducer in the prior art.

While the foregoing description shows and describes the preferred embodiments of the present invention, it is to be understood that the invention is not limited to the forms disclosed herein, but is not to be construed as excluding other embodiments and is capable of use in various other combinations, modifications, and environments and is capable of changes within the scope of the inventive concept as described herein, commensurate with the above teachings, or the skill or knowledge of the relevant art. And that modifications and variations may be effected by those skilled in the art without departing from the spirit and scope of the invention as defined by the appended claims.

Claims

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;

where bm is 1.1 and fc is and

in connection withA coefficient; the thickness G of the cycloid wheel (3) is (0.8-1.8) multiplied by Lwe.

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,

wherein D1 is (2-2.8) x b and N1 is an integer; the diameter of the taper pin (73) is D6, the distributed pitch circle diameter of m taper pins (73) is D2, the shearing stress of each taper pin (73) is tau, the torque transmitted by m taper pins (73) 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 (72) and the m taper pins (73) is T3, T3 is T1+ T2 and

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,

wherein D4 is c-j2- (2-10), N4 is an integer and

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).