CN212318679U - Inner gearing RV reduction gear for precision control - Google Patents
Inner gearing RV reduction gear for precision control Download PDFInfo
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- CN212318679U CN212318679U CN202021544246.2U CN202021544246U CN212318679U CN 212318679 U CN212318679 U CN 212318679U CN 202021544246 U CN202021544246 U CN 202021544246U CN 212318679 U CN212318679 U CN 212318679U
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Abstract
The utility model discloses an inner gearing RV reduction gear for precision control relates to robot reduction gear technical field, include hypocycloid ring gear and arrange two-stage speed reduction part wherein in: the first-stage speed reduction part comprises an input shaft, a sun gear and a planet gear; second stage of speed reductionThe parts comprise 2-3 eccentric shafts, a cycloidal gear and a planetary plate which are uniformly distributed, and after the cycloidal gear is trimmed, the side clearance between hypocycloid teeth and two sides of cycloidal tooth grooves is 0.1 lambda1≤Δc＜0.7λ1，λ1The theoretical radial thermal expansion of the cycloid wheel is the theoretical radial thermal expansion of the cycloid wheel when doing work under rated torque. The shape modification of the cycloid wheel of the utility model satisfies the relational expression of the side clearance delta c and the thermal expansion amount of the cycloid wheel, thereby having good dynamic characteristic, less heat generation and less abrasion; the conventional manufacturing precision and the cost are low; interchangeable with existing RV reducers.
Description
Technical Field
The utility model relates to a reduction gear technical field of robot especially relates to an inner gearing RV reduction gear for precision control that dynamic characteristic is good.
Background
The robot is a pearl on the top of the crown in the manufacturing industry and is an important mark for measuring the level of national technological innovation and high-end manufacturing industry. The RV reducer is one of the most core components of the robot and is the only component which is not truly localized.
The side clearance technology after the existing cycloidal gear of the RV reducer is trimmed has two types. One is patent CN 110966357A, CN 111059225A, CN 110985611A, CN 110985610 a, etc., because the side gap is set based on the calculation parameter of the theoretical thermal expansion amount, the thermal expansion coefficient α t =1.379 · 10-5(1/. degree. C.) from research on the thermal expansion coefficient of precision parts and the precise thermal expansion coefficient of materials, page 95 (Miao En Ming, university of Hefei, 2004.09), the actual thermal expansion of the solid round bar-shaped structural bearing steel material was measured. The actual cycloid wheel structure is a porous disc-shaped structure, and is far from the solid round bar-shaped structure of a theoretical actual sample. According to the solid Physics introduction (Girtell C [ Mei ]]Beijing: scientific press, 1979) that the thermal deformation is closely related to the form factor. Meanwhile, through the actual measurement and comparative study on the thermal expansion of the cycloidal bearing steel material with the existing structure and different structures, the thermal expansion coefficient of the porous disc-shaped structure bearing steel material is proved to be greatly different from that of the solid circular rod-shaped structure bearing steel material. Therefore, the prior art is difficult to be implemented to meet the design requirement.
The other is that, CN 108869644A, CN 106641110 a and other patents do not make any quantitative setting for specifically defining the range of the side clearance of the cycloid gear, and only if the side clearance is too small, the principle description will be given that the side clearance will cause heat generation due to wear, poor dynamic performance, shortened life and the like when expanding under temperature rise, and such principle knowledge is well known to those skilled in the art.
SUMMERY OF THE UTILITY MODEL
The utility model aims at providing a correct cycloidal gear is repaiied shape back side direction clearance deltac and the relational expression of thermal expansion volume lambda for there are defects such as easily generating heat, easy wearing and tearing, precision retentivity are poor among the solution prior art, provide an inner gearing RV reduction gear for the precision control that dynamic characteristic is good.
In order to solve the technical problem, the utility model discloses a technical scheme be:
the inner gearing RV reducer for the precision control comprises a hypocycloid gear ring and two-stage reduction parts arranged in the hypocycloid gear ring: the first-stage speed reduction part comprises an input shaft, a sun gear and a planet gear; the second-stage speed reduction part comprises 2-3 eccentric shafts, cycloidal gears and planetary disks which are uniformly distributed, wherein the planetary disks comprise a left planetary disk and a right planetary disk, the extension end of an eccentric shaft is connected with a planetary wheel, eccentric shaft bearings for supporting the cycloidal gears are arranged on two eccentric sections of the eccentric shaft, the shaft extensions on two sides of the eccentric section of the eccentric shaft are respectively supported in peripheral holes of the left planetary disk and the right planetary disk by conical roller bearings, the left planetary disk and the right planetary disk are respectively supported in inner holes on two sides of an inner cycloidal gear ring by main bearings, the input shaft is respectively supported in central holes of the left planetary disk and the right planetary disk by an input shaft bearing, flanges uniformly distributed on the left planetary disk penetrate through corresponding through holes of the cycloidal gears to be connected with the right planetary disk by screws and positioning pins into a rigid body, the cycloidal gears comprise a left cycloidal gear and a right cycloidal gear and adopt 'equidistant-displacement' shape modification, the modification enables a lateral clearance delta c and a radial clearance to be formed between the hypocycloid teeth and the cycloidal tooth grooves,
(1) when lambda 1 is the theoretical radial thermal expansion amount of the cycloid wheel when the speed reducer does work:
the range of the lateral clearance delta c between the hypocycloid tooth and the single side of the cycloid tooth slot is as follows: Δ c is more than or equal to 0.1 λ 1 and less than 0.7 λ 1;
(2) when lambda 2 is the actual radial thermal expansion amount of the cycloid wheel when the speed reducer does work:
a lateral clearance delta c = (0.1-5) lambda 2 between the hypocycloid teeth and the single side of the cycloidal tooth slot;
(3) when lambda is the actual lateral thermal expansion amount of the cycloid wheel when the speed reducer does work:
and a lateral clearance delta c = (0.1-5) lambda between the hypocycloid teeth and the single side of the cycloidal tooth slot.
In a preferred embodiment of the present invention, the lateral clearance Δ c = (0.2-0.6) λ 1 between the hypocycloidal tooth and the single side of the cycloidal tooth slot.
In a preferred embodiment of the present invention, the lateral clearance Δ c = (0.1-4) λ 2 between the hypocycloidal tooth and the single side of the cycloidal tooth slot.
In a preferred embodiment of the present invention, the lateral clearance Δ c = (0.2-3) λ 2 between the hypocycloidal tooth and the single side of the cycloidal tooth slot.
In a preferred embodiment of the present invention, the lateral clearance Δ c = λ 2 between the hypocycloidal tooth and the single side of the cycloidal tooth slot.
In a preferred embodiment of the present invention, the range of the lateral clearance between the hypocycloid tooth and the single side of the cycloidal tooth slot is: Δ c is more than or equal to 0.1 λ 2 and less than 0.7 λ 2.
In a preferred embodiment of the present invention, the lateral clearance Δ c = (0.2-0.6) λ 2 between the hypocycloidal tooth and the single side of the cycloidal tooth slot.
In a preferred embodiment of the present invention, the lateral clearance Δ c = (0.1-4) λ is between the hypocycloidal tooth and the single side of the cycloidal tooth slot.
In a preferred embodiment of the present invention, the lateral clearance Δ c = (0.2-3) λ is between the hypocycloidal tooth and the single side of the cycloidal tooth slot.
In a preferred embodiment of the present invention, the lateral clearance Δ c = λ between the hypocycloidal tooth and the single side of the cycloidal tooth slot.
In a preferred embodiment of the present invention, the range of the lateral clearance between the hypocycloid tooth and the single side of the cycloidal tooth slot is: delta c is more than or equal to 0.1 lambda and less than 0.7 lambda.
In a preferred embodiment of the present invention, the lateral clearance Δ c = (0.2-0.6) λ is between the hypocycloidal tooth and the single side of the cycloidal tooth slot.
In a preferred embodiment of the present invention, the through hole has a fan-like structure, or expansion reducing holes are formed on both sides of the through hole, and the expansion reducing holes have a circular or polygonal shape or a special shape.
In a preferred embodiment of the present invention, the theoretical radial thermal expansion amount λ 1= (d0 Δ t) α t1 of the cycloid wheel, the actual radial thermal expansion amount λ 2= (d0 Δ t) α t2 of the cycloid wheel, the actual lateral thermal expansion amount λ = (d0 Δ t) α t of the cycloid wheel, wherein α t, α t1, α t2 are the actual lateral thermal expansion coefficient, the theoretical radial thermal expansion coefficient, the actual radial thermal expansion coefficient of the bearing steel of the cycloid wheel, Δ t is the temperature rise of the cycloid wheel, d0 is the average diameter of the addendum circle and the dedendum circle, α t1=1.38 · 10-5(1/° c), temperature rise Δ t =45 ℃, λ 1= (d0 Δ t) α t =0.00062d 0.
The utility model has the advantages that:
(1) the side clearance delta c generated by the 'equidistance-displacement' shape modification is closely related to the thermal expansion amount of the cycloid wheel, so the cycloid wheel has good dynamic characteristic and is not overheated when the cycloid wheel operates and does work under rated load;
(2) the utility model adopts conventional manufacturing precision, simple process and low cost;
(3) the utility model discloses overall dimension is the same with RV reduction gear commonly used, can exchange with it.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the description of the embodiments are briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained without inventive work, wherein:
fig. 1 is a schematic structural cross-sectional view of a preferred embodiment of an inner gearing RV reducer for precision control according to the present invention;
fig. 2 is a schematic structural view of an embodiment of a cycloid wheel in an inner gearing RV reducer for precision control according to the present invention;
fig. 3 is a schematic structural view of another embodiment of a cycloid wheel in an inner gearing RV reducer for precision control according to the present invention;
in the figure: 1. the planetary gear set comprises a hypocycloid gear ring, 2 degrees of main bearings, 3 degrees of left cycloidal gears, 4 degrees of planet gears, 5 degrees of right cycloidal gears, 6 degrees of eccentric shafts, 7 degrees of tapered roller bearings, 8 degrees of eccentric shaft bearings, 9 degrees of input shafts, 10 degrees of input shaft bearings, 11 degrees of flanges, 12 degrees of right side planetary discs, 13 degrees of left side planetary discs, 14 degrees of sun gears, 15 degrees of through holes, 16 degrees of expansion reducing holes.
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely below, and it should be apparent that the described embodiments are only some embodiments of the present invention, but not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative efforts belong to the protection scope of the present invention.
Referring to fig. 1-3, an embodiment of the present invention includes:
an inner gearing RV reduction gear for precision control, which comprises a hypocycloid gear ring and two-stage reduction parts arranged in the hypocycloid gear ring:
the first stage comprises an input shaft, a sun gear and a planet gear;
the second level includes the eccentric shaft of equipartition, cycloid wheel, bearing and planetary plate, wherein: the cycloidal gear comprises a left cycloidal gear and a right cycloidal gear, the planetary plate comprises a left planetary plate and a right planetary plate, the extension end of an eccentric shaft is connected with a planetary gear, eccentric shaft bearings used for supporting the cycloidal gear are arranged on two eccentric sections of the eccentric shaft, the shaft extensions on the two sides of the eccentric section of the eccentric shaft are respectively supported in peripheral holes of the left planetary plate and the right planetary plate by tapered roller bearings, the left planetary plate and the right planetary plate are respectively supported on the two sides of an inner cycloidal gear ring by main bearings, an input shaft is respectively supported in central holes of the left planetary plate and the right planetary plate by input shaft bearings, and a flange on the left planetary plate passes through a corresponding through hole of the cycloidal gear to; the cycloidal gears comprise a left cycloidal gear and a right cycloidal gear, and are modified by adopting an equal distance-displacement mode, so that a lateral gap delta c and a radial gap are formed between hypocycloid teeth and cycloidal tooth grooves, wherein the positive equal distance-positive displacement mode is preferentially adopted during modification, and the negative equal distance-negative displacement mode can be selected for modification.
When lambda 1 is the theoretical radial thermal expansion amount of the cycloid wheel when the speed reducer does work:
the range of the lateral clearance Δ c is: Δ c is more than or equal to 0.1 λ 1 and less than 0.7 λ 1.
The shape of the through hole on the cycloid wheel can be a fan-like structure, or expansion reducing holes are formed in two sides of the through hole, and the shape of the expansion reducing holes can be circular, polygonal or special-shaped.
According to the discovery that thermal deformation and form factors are inseparable in a thermal expansion research theory, the actual measurement and comparison research on the thermal expansion coefficients of the bearing steel materials of the cycloidal gears with different structures finds that the thermal expansion coefficients of the bearing steel materials of the cycloidal gears with different structures are different, and particularly the structural change of the through holes of the cycloidal gears or the structural change around the through holes has influence on the thermal expansion of the cycloidal gears. Therefore, the cycloid wheel structure is reasonably arranged, particularly the through hole or the structure around the through hole is reasonably arranged, so that the thermal expansion of the cycloid wheel is minimum, and the precision design of the speed reducer is facilitated. Through the comparison research of the thermal expansion of a large number of cycloidal gears with different structures, on the premise of ensuring the rigidity of the cycloidal gear, the through holes of the cycloidal gear are designed into fan-like shapes from the existing circular or fan-shaped structures, namely the through holes are expanded to the two sides of the fan-shaped structures to form the fan-like shapes; or the two sides of the through hole are provided with expansion reducing holes, and the shape of the expansion reducing holes is a circular or polygonal or special-shaped structure.
Therefore, the temperature of the molten metal is controlled,
(1) when lambda 2 is the actual radial thermal expansion amount of the cycloid wheel when the speed reducer does work:
a lateral clearance delta c = (0.1-5) lambda 2 between the hypocycloid teeth and the single side of the cycloidal tooth slot;
(2) when lambda is the actual lateral thermal expansion amount of the cycloid wheel when the speed reducer does work:
and a lateral clearance delta c = (0.1-5) lambda between the hypocycloid teeth and the single side of the cycloidal tooth slot.
The actual radial thermal expansion amount of the cycloid wheel can be obtained by actually measuring the thermal expansion amount, or can be obtained by calculation after actually measuring the thermal expansion coefficient, namely lambda 2= (d0 delta t) alpha t2, or can be obtained by calculation and derivation of the actual lateral thermal expansion amount; the actual lateral thermal expansion of the cycloid gear can be obtained by actually measuring the thermal expansion, or can be obtained by calculation after actually measuring the thermal expansion coefficient, namely lambda = (d0 delta t) alpha t, or can be obtained by calculation and derivation through the actual radial thermal expansion; wherein alpha t and alpha t2 are thermal expansion coefficients of the bearing steel of the cycloidal gear, delta t is the temperature rise of the cycloidal gear, and d0 is the average diameter of the addendum circle and the dedendum circle of the cycloidal gear.
According to the quasi-resonance approximation theory of the solid physics introduction (Kittall C [ Mei ], Beijing: scientific Press, 1979), the mechanism of thermal expansion is that a solid is composed of tiny crystals, the crystals are formed by arranging atoms at certain positions in space, the atoms have potential energy and kinetic energy, when the atoms are in equilibrium, the sum of the kinetic energy and the potential energy is minimum, the kinetic energy of the atoms is increased along with the increase of temperature, so that the displacement among the atoms is increased, the potential energy is increased, the macroscopic expression is the occurrence of thermal expansion, and the thermal expansion can be regarded as that the object is subjected to uniform outward expansion force. The amount of thermal expansion is closely related to the shape of the object.
According to the research of 'research on influence of shape parameters on thermal expansion of parts' (Miaoming, Fuyitai, applied science bulletin, 2003.06), the thermal deformation is found to be inseparable with the shape factor; the calculation of the thermal expansion coefficient generally includes a simple calculation method, a statistical calculation method, a ruley hessian formula and the like, and the methods all have certain limitations, so that the calculated thermal expansion coefficient value is greatly different from an actual measured value, the currently used thermal expansion coefficient is still an actual measured value using a round rod with a certain size, and the measured value of the thermal expansion coefficient inevitably contains the influence of a shape factor.
According to the search on page 95 (Miao En Ming, Hei Fu university, 2004.09) of research on the thermal expansion coefficient of precision parts and materials, the thermal expansion coefficient of the bearing steel is alpha t = 1.38.10-5(1/. degree. C.), is a measured value of a solid round bar structure bearing steel material with a certain size.
According to ZhongThe linear expansion coefficients and the density tables (tables 12.2-4) of the conventional materials in the State mechanical design dictionary (volume 1), the linear expansion coefficient alphat tables (tables 1-1-12) of the materials in the mechanical design Manual (volume 1), and the linear expansion coefficient tables (tables 1-1-12) of the conventional materials in the modern mechanical design Manual (volume 1) are searched, and the linear expansion coefficients alphat = 1.12.10 when the chromium steel is referred to at 20-100 DEG C-5Coefficient of thermal expansion α t =1.38 · 10 for bearing steel only-581.12% of (1/. degree. C.).
According to the national standard GB/T36491-. The specific value of the temperature rise of the cycloid gear can be calculated by the temperature difference between the shell of the speed reducer and the environment and the temperature difference between the shell and the cycloid gear, and can also be directly taken as 45 ℃. When the temperature rise of the cycloid wheel is 45 ℃, the thermal expansion amount of the cycloid wheel is relatively high because the speed reducer generally works in a room temperature environment.
The actual structure of the cycloid wheel is a porous disc-shaped structure, and is far from the solid round bar-shaped structure of a theoretical actual measurement sample. The actual coefficient of thermal expansion of the bearing steel material of the cycloid wheel will be lower than the theoretical coefficient of thermal expansion of the bearing steel material.
By applying a related thermal expansion research theory and through the actual measurement research on the thermal expansion coefficients of the cycloidal bearing steel materials with the existing structures and different structures, the actual thermal expansion coefficients of the cycloidal bearing steel materials with the existing structures and different structures are also proved to be lower than the thermal expansion coefficient of the theoretical bearing steel materials.
In summary, the theoretical thermal expansion amount, the thermal expansion coefficient and the temperature rise of the cycloid wheel are all larger than the actual thermal expansion amount, the thermal expansion coefficient and the temperature rise, so as to obtain the correct lateral clearance, the actual thermal expansion amount, or the data of the thermal expansion coefficient and the temperature rise of the cycloid wheel can be measured by various existing means, and the actual thermal expansion amount is multiplied by a certain coefficient to be adjusted, so as to obtain the parameter of the actually required lateral clearance Δ c.
Although the amount of thermal expansion, the coefficient of thermal expansion, the temperature, and the multiplied coefficient may be different from the present patent, the value of the final lateral clearance Δ c is within the claims of the present patent and is included in the scope of the present patent. In a similar way, this patent is because of having set for actual side direction thermal expansion volume value interval, if extend theoretical side direction thermal expansion volume from theoretical radial thermal expansion volume and have had no practicality, has been covered by the practicality of actual side direction thermal expansion volume, can also directly derive theoretical side direction thermal expansion volume from theoretical radial thermal expansion volume simultaneously, so the value of theoretical side direction thermal expansion volume has been included in the patent protection scope of the utility model.
In part of the prior art, due to the reasons of large values of theoretical thermal expansion coefficient, temperature rise and adjustment coefficient and the like, the lateral clearance delta c is over-large, so that the precision is poor.
In part of the prior art, the lateral clearance delta c is too small, so that the cycloidal gear and the hypocycloid gear ring are in interference friction, and the problem of poor dynamic performance is inevitable. To further illustrate the problem, the national 863 program of RV reducers, which is jointly attacked by a famous expert at university of large-scale transportation and a research institute of middle-sized villa weir machine, is taken as an example, and published parameters in 2017 and 9 months are as follows: rz =77, e =1.50, Za =39, K1=0.7792, Δ Rz = -0.027, Δ Rz = -0.047, return difference 0.29'.
When the return difference = 0.29' is constant, it is calculated that:
lateral gap ac =0.003 (mm).
And the theoretical radial thermal expansion amount λ 1= (d0 Δ t) α t =0.00062d0 (mm) =0.09548 (mm) of the cycloid wheel, when the temperature rise Δ t =45 ℃, in the formula: bearing steel GCr15 thermal expansion coefficient alpha t =1.38 · 10-5(1/° C), d0 is the average diameter of the tip circle and the root circle of the cycloidal gear.
And further calculating to obtain that the actual radial thermal expansion amount lambda 2 of the cycloid wheel is smaller than the theoretical radial thermal expansion amount lambda 1, namely lambda 2 is smaller than lambda 1.
And further calculating to obtain that the actual radial thermal expansion amount lambda 2 of the cycloid wheel is smaller than the actual lateral thermal expansion amount lambda, namely lambda 2 is smaller than lambda, wherein lambda is the actual lateral thermal expansion amount of the cycloid wheel when the speed reducer works under rated torque.
And simultaneously, obtaining that the actual lateral thermal expansion amount lambda of the cycloid wheel is smaller than the theoretical radial thermal expansion amount lambda 1, namely lambda is smaller than lambda 1.
Therefore, the lateral clearance delta C is less than the set 0.1 lambda 2, less than the set 0.1 lambda 1, less than the actual radial thermal expansion lambda 2, less than the actual lateral thermal expansion lambda, less than the theoretical radial thermal expansion lambda 1, namely, delta C is less than 0.1 lambda 2 and less than 0.1 lambda 1 and less than lambda 2 and less than lambda 1.
From this, it is found that the lateral clearance Δ C of this item is smaller than the actual lateral thermal expansion amount λ, i.e., Δ C < λ, and Δ C = (0.1 to 5) λ, 0.1 λ 1 ≦ Δ C < 0.7 λ 1, and Δ C = (0.1 to 5) λ 2 are not satisfied. Therefore, the problem that the dynamic performances such as heating, abrasion, precision reduction and the like are poor inevitably occurs due to interference friction between the cycloid wheel and the hypocycloid gear ring.
The effect of the reducer in use at different side clearances is shown in the following table,
from the above table, it can be seen that:
the first expression is as follows: when the lateral clearance delta c meets the condition that delta c is more than or equal to 0.1 lambda 1 and less than 0.7 lambda 1, the standard is reached;
performing two steps: when the lateral clearance delta c = (0.1-5) lambda 2, the standard is reached;
the third expression is that: when the lateral clearance delta c = (0.7-5) lambda 1, delta c is less than 0.1 lambda 1, and delta c is more than 5 lambda 1, the standard is not reached;
the expression is four: when the lateral clearance delta c is less than 0.1 lambda 2 and the delta c is more than 5 lambda 2, the standard is not reached;
and (5) performing the following steps: under the condition of reaching the standard, the temperature rise is lower than 45 ℃.
Therefore, to sum up, the above table can more intuitively display the technical effects achieved by the improvement point of the present application from the perspective of actual detection, that is:
(1) when the theoretical radial thermal expansion amount lambda 1 is adopted, the lateral clearance needs to meet the condition that delta c is more than or equal to 0.1 lambda 1 and less than 0.7 lambda 1, so that the heating condition caused by abrasion can be effectively reduced, and meanwhile, the precision of the speed reducer can be maintained at a higher level;
(2) when the radial thermal expansion amount lambda 2 is obtained through actual measurement, the measured radial thermal expansion amount is generally smaller than the theoretical radial thermal expansion amount, so that the requirements of reducing temperature rise, reducing abrasion, prolonging service life and maintaining high precision can be met only when the lateral clearance meets the requirement that delta c = (0.1-5) lambda 2.
(3) When the lateral thermal expansion amount lambda is obtained through actual measurement, the lateral clearance can meet the requirements of reducing temperature rise, reducing abrasion, prolonging service life and maintaining high precision only if the lateral clearance meets delta c = (0.1-5) lambda because the actual measurement lateral thermal expansion amount is generally smaller than the theoretical radial thermal expansion amount.
Similarly, through theoretical calculation and actual measurement and research of the thermal expansion coefficients of cycloidal gears with different structures, it is deduced that the lateral clearance delta c between the hypocycloid teeth and the single side of the cycloidal tooth groove needs to satisfy the formula that delta c is more than or equal to 0.1 lambda 1 and less than 0.7 lambda 1, and the theoretical calculation and the actual measurement results are met through actual operation tests.
Furthermore, the through hole is of a fan-like structure, or expansion reducing holes are formed in two sides of the through hole, the expansion reducing holes are of a circular or polygonal or special-shaped structure, and corresponding to various RV reducer models, the lateral clearance delta c between the hypocycloid teeth and one side of the cycloidal tooth socket is = (0.2-0.6) lambda 1.
Furthermore, the through hole is of a fan-like structure, or expansion reducing holes are formed in two sides of the through hole, the expansion reducing holes are of a circular or polygonal or special-shaped structure, and corresponding to various RV reducer models, the lateral clearance delta c between the hypocycloid teeth and one side of the cycloidal tooth socket is not less than (0.1-4) lambda 2.
Furthermore, the through hole is of a fan-like structure, or expansion reducing holes are formed in two sides of the through hole, the expansion reducing holes are of a circular or polygonal or special-shaped structure, and corresponding to various RV reducer models, the lateral clearance delta c between the hypocycloid teeth and one side of the cycloidal tooth socket is not less than (0.2-3) lambda 2.
Furthermore, the through hole is in a fan-like structure, or expansion reducing holes are formed in two sides of the through hole, the expansion reducing holes are in a circular or polygonal or special-shaped structure, and corresponding to various RV reducer models, the lateral clearance delta c = lambda 2 between the hypocycloid teeth and one side of the cycloidal tooth socket is obtained.
Furthermore, the shape of the through hole is a fan-like structure, or expansion reducing holes are formed in two sides of the through hole, the expansion reducing holes are in a circular or polygonal or special-shaped structure, and the range of the lateral clearance between the hypocycloid teeth and one side of the cycloid tooth space is as follows corresponding to various RV reducer models: Δ c is more than or equal to 0.1 λ 2 and less than 0.7 λ 2.
Furthermore, the through hole is in a fan-like structure, or expansion reducing holes are formed in two sides of the through hole, the expansion reducing holes are in a circular or polygonal or special-shaped structure, and corresponding to various RV reducer models, the lateral clearance delta c between the hypocycloid teeth and one side of the cycloidal tooth socket is not less than (0.2-0.6) lambda 2.
Furthermore, the through hole is of a fan-like structure, or expansion reducing holes are formed in two sides of the through hole, the expansion reducing holes are of a circular or polygonal or special-shaped structure, and corresponding to various RV reducer models, the lateral clearance delta c between the hypocycloid teeth and one side of the cycloidal tooth socket is not less than (0.1-4) lambda.
Furthermore, the through hole is of a fan-like structure, or expansion reducing holes are formed in two sides of the through hole, the expansion reducing holes are of a circular or polygonal or special-shaped structure, and corresponding to various RV reducer models, the lateral clearance delta c between the hypocycloid teeth and one side of the cycloidal tooth socket is not less than (0.2-3) lambda.
Furthermore, the through hole is in a fan-like structure, or expansion reducing holes are formed in two sides of the through hole, the expansion reducing holes are in a circular or polygonal or special-shaped structure, and corresponding to various RV reducer models, the lateral clearance delta c = lambda between the hypocycloid teeth and one side of the cycloidal tooth socket is larger than the lateral clearance delta c = lambda.
Furthermore, the shape of the through hole is a fan-like structure, or expansion reducing holes are formed in two sides of the through hole, the expansion reducing holes are in a circular or polygonal or special-shaped structure, and the range of the lateral clearance between the hypocycloid teeth and one side of the cycloid tooth space is as follows corresponding to various RV reducer models: delta c is more than or equal to 0.1 lambda and less than 0.7 lambda.
Furthermore, the through hole is in a fan-like structure, or expansion reducing holes are formed in two sides of the through hole, the expansion reducing holes are in a circular or polygonal or special-shaped structure, and corresponding to various RV reducer models, the lateral clearance delta c between the hypocycloid teeth and one side of the cycloidal tooth socket is not less than (0.2-0.6) lambda.
Detailed description of the preferred embodiment
The utility model provides an inner gearing RV reduction gear for precision control, its structure includes hypocycloid ring gear 1 and arranges the two-stage speed reduction part in it: the first-stage speed reduction part comprises an input shaft 9, a sun gear 14 and a planet gear 4; the second-stage speed reduction component comprises 2-3 eccentric shafts 6, cycloidal gears and planetary discs which are uniformly distributed, each cycloidal gear comprises a left cycloidal gear 3 and a right cycloidal gear 5, each planetary disc comprises a left planetary disc 13 and a right planetary disc 12, the shaft extension ends of the eccentric shafts 6 are connected with planetary wheels 14, eccentric shaft bearings 8 used for supporting the cycloidal gears are arranged on two eccentric sections of the eccentric shafts 6, the shaft extensions on two sides of the eccentric sections of the eccentric shafts are respectively supported in peripheral holes of the left planetary disc 13 and the right planetary disc 12 through conical roller bearings 7, the left planetary disc 13 and the right planetary disc 12 are respectively supported in inner holes on two sides of the hypocycloid gear ring 1 through main bearings 2, the input shaft 9 is respectively supported in central holes of the left planetary disc 13 and the right planetary disc 12 through input shaft bearings 10, flanges 11 uniformly distributed on the left planetary disc 13 penetrate through corresponding 3 through holes 15 of the cycloidal gears and are connected with the right planetary disc 12 through bolts and positioning pins to form a rigid body, the shape of 3 through holes 15 is fan-shaped structure, the cycloid wheel adopts "equidistance-displacement" modification, and the modification makes the hypocycloid tooth and the cycloid wheel tooth's socket form lateral clearance delta c and radial clearance, the lateral clearance delta c = lambda of hypocycloid tooth and cycloid wheel tooth's socket unilateral, in the formula: and lambda is the actual lateral thermal expansion amount of the cycloid wheel when the speed reducer does work under the rated torque.
Meanwhile, the size of the lateral clearance delta c is related to factors such as the adjacent distance machining precision of the hypocycloid gear ring, the diameter machining precision of the hypocycloid gear ring, the tooth pitch deviation of the cycloid wheel, the deviation generated by assembly and the like, and is related to the size of the model of the RV reducer, interference friction is generated when the lateral clearance delta c is too small, and vibration is easily generated when the input rotating speed is too high.
Therefore, the lateral clearance delta c in the embodiment is equal to the actual lateral thermal expansion, namely, delta c = lambda, so that good gear meshing is realized, and interference friction is avoided; meanwhile, the requirement on the processing precision is greatly reduced, so that the investment, production and management costs of enterprises are greatly reduced.
The utility model provides an inner gearing RV reduction gear for precision control compares with prior art and has following advantage:
(1) the utility model discloses a side clearance delta c that "equidistance-displacement" modification produced is closely correlated with cycloid wheel thermal expansion volume, therefore has good dynamic characteristic, does not overheat when the operation does work under rated load.
(2) The utility model discloses use conventional manufacturing accuracy, simple process, it is with low costs.
(3) The utility model discloses overall dimension is the same with RV reduction gear commonly used, can exchange with it.
The above only is the embodiment of the present invention, not limiting the patent scope of the present invention, all of which utilize the equivalent structure or equivalent flow transformation made by the content of the specification of the present invention, or directly or indirectly applied to other related technical fields, all included in the same way in the patent protection scope of the present invention.
Claims (12)
1. An inner gearing RV reduction gear for precision control, includes hypocycloid ring gear and arranges the two-stage reduction part in it: the first-stage speed reduction part comprises an input shaft, a sun gear and a planet gear; the second-stage speed reduction part comprises 2-3 eccentric shafts, cycloidal gears and planetary disks which are uniformly distributed, wherein the planetary disks comprise a left planetary disk and a right planetary disk, the extension end of an eccentric shaft is connected with a planetary wheel, eccentric shaft bearings for supporting the cycloidal gears are arranged on two eccentric sections of the eccentric shaft, the shaft extensions at two sides of the eccentric section of the eccentric shaft are respectively supported in peripheral holes of the left planetary disk and the right planetary disk by conical roller shafts, the left planetary disk and the right planetary disk are respectively supported in inner holes at two sides of an inner cycloidal gear ring by main bearings, the input shaft is respectively supported in central holes of the left planetary disk and the right planetary disk by an input shaft bearing, flanges uniformly distributed on the left planetary disk penetrate through corresponding through holes of the cycloidal gears to be connected with the right planetary disk by screws and positioning pins into a rigid body, the cycloidal gears comprise a left cycloidal gear and a right cycloidal gear and adopt 'equidistant-displacement' shape modification, so that a lateral clearance delta c and a radial clearance are formed between the hypocycloid teeth and the cycloidal tooth grooves, and the device is characterized in that:
(1) when lambda 1 is the theoretical radial thermal expansion amount of the cycloid wheel when the speed reducer does work:
the range of the lateral clearance delta c between the hypocycloid tooth and the single side of the cycloid tooth slot is as follows: Δ c is more than or equal to 0.1 λ 1 and less than 0.7 λ 1;
(2) when lambda 2 is the actual radial thermal expansion amount of the cycloid wheel when the speed reducer does work:
the range of the lateral clearance delta c between the hypocycloid tooth and the single side of the cycloid tooth slot is as follows: Δ c = (0.1 to 5) λ 2;
(3) when lambda is the actual lateral thermal expansion amount of the cycloid wheel when the speed reducer does work:
the range of the lateral clearance delta c between the hypocycloid tooth and the single side of the cycloid tooth slot is as follows: Δ c = (0.1 to 5) λ.
2. An inside gearing RV reducer for precision control according to claim 1, characterized in that: and a lateral clearance delta c = (0.2-0.6) lambda 1 between the hypocycloid teeth and the single side of the cycloidal tooth slot.
3. An inside gearing RV reducer for precision control according to claim 1, characterized in that: and a lateral clearance delta c = (0.1-4) lambda 2 between the hypocycloid teeth and the single side of the cycloidal tooth slot.
4. An inside gearing RV reducer for precision control according to claim 3, characterized in that: and a lateral clearance delta c = (0.2-3) lambda 2 between the hypocycloid teeth and the single side of the cycloidal tooth slot.
5. An inside gearing RV reducer for precision control according to claim 4, characterized in that: and the lateral clearance delta c = lambda 2 between the hypocycloid tooth and the single side of the cycloidal tooth slot.
6. An inside gearing RV reducer for precision control according to claim 1, characterized in that: the range of the lateral clearance between the hypocycloid tooth and the single side of the cycloid tooth slot is as follows: Δ c is more than or equal to 0.1 λ 2 and less than 0.7 λ 2.
7. An inside gearing RV reducer for precision control according to claim 1, characterized in that: and a lateral clearance delta c = (0.1-4) lambda between the hypocycloid teeth and the single side of the cycloidal tooth slot.
8. An inside gearing RV reducer for precision control according to claim 7, characterized in that: and a lateral clearance delta c = (0.2-3) lambda between the hypocycloid teeth and the single side of the cycloidal tooth slot.
9. An inside gearing RV reducer for precision control according to claim 8, characterized in that: and the lateral clearance delta c = lambda between the hypocycloid tooth and the single side of the cycloidal tooth slot.
10. An inside gearing RV reducer for precision control according to claim 1, characterized in that: the range of the lateral clearance between the hypocycloid tooth and the single side of the cycloid tooth slot is as follows: delta c is more than or equal to 0.1 lambda and less than 0.7 lambda.
11. An inside gearing RV reducer for precision control according to any of claims 1 to 10, characterized in that: the through hole is of a fan-like structure, or expansion reducing holes are formed in the two sides of the through hole and are circular, polygonal or special-shaped.
12. An inside gearing RV reducer for precision control according to any of claims 1 to 10, characterized in that: theoretical radial thermal expansion amount lambda 1= (d0 delta t) alpha t1 of the cycloid wheel, actual radial thermal expansion amount lambda 2= (d0 delta t) alpha t2 of the cycloid wheel, actual lateral thermal expansion amount lambda = (d0 delta t) alpha t of the cycloid wheel, wherein alpha t1 is theoretical radial thermal expansion coefficient of the cycloid bearing steel, alpha t2 is actual radial thermal expansion coefficient of the cycloid bearing steel, alpha t is actual lateral thermal expansion coefficient of the cycloid bearing steel, delta t is temperature rise of the cycloid wheel,d0 is the average diameter of the tip circle and the root circle of the cycloidal gear, and alpha t1= (1.378-1.382) · 10-5(1/° c), temperature rise Δ t =45 ℃, λ 1= (d0 Δ t) α t1= 0.00062d 0.
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| CN202021544246.2U CN212318679U (en) | 2020-07-30 | 2020-07-30 | Inner gearing RV reduction gear for precision control |
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