# Geometric and Meshing Properties of Conjugate Curves for Gear Transmission

Authors: Dong Liang; Bingkui Chen; Yane Gao; Shuai Peng; Siling Qin
Journal: Mathematical Problems in Engineering
 (2014)

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## Abstract

Conjugate curves have been put forward previously by authors for gear transmission. Compared with traditional conjugate surfaces, the conjugate curves have more flexibility and diversity in aspects of gear design and generation. To further extend its application in power transmission, the geometric and meshing properties of conjugate curves are discussed in this paper. Firstly, general principle descriptions of conjugate curves for arbitrary axial position are introduced. Secondly, geometric analysis of conjugate curves is carried out based on differential geometry including tangent and normal in arbitrary contact direction, characteristic point, and curvature relationships. Then, meshing properties of conjugate curves are further revealed. According to a given plane or spatial curve, the uniqueness of conjugated curve under different contact angle conditions is discussed. Meshing commonality of conjugate curves is also demonstrated in terms of a class of spiral curves contacting in the given direction for various gear axes. Finally, a conclusive summary of this study is given.


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## Body

## 1. Introduction

The theory of plane or space curves and surfaces in the three-dimensional Euclidean space forms the basis for development of differential geometry [1, 2]. And its application in gear transmission, namely, the geometry theory of conjugate surfaces, has been widely applied to conventional gear drive [3–5]. Working performance of conjugate surfaces affects greatly the overall power and motion properties of gear drive. The mathematical principle, geometrical design, and characteristic analysis about conjugate surfaces were developed by many scholars.Litvin et al. [6] proposed systematic methodology to study mathematical model of conjugate surfaces and analyzed the geometrical and meshing characteristics based on differential geometry. Chen [7] investigated surface geometry of spatial gear pairs and discussed general property from the practical point of view. Li [8] described spatial geometry modeling of conjugate surfaces. The specific application in engineering was also introduced. Di Puccio et al. [9] put forward a rather general formulation for generation and curvature analysis of conjugate surfaces via the alternative formulation of the theory of gearing. In [10], Wu and Luo studied a geometric theory of conjugate tooth surfaces and derived curvatures equations in terms of the limit functions of the first kind and considering the mating surfaces subjected to relative screw motion with constant translational and rotational velocities. Ito and Takahashi [11] analyzed curvatures in hypoid gears starting from a classical differential geometry point of view, but then introducing kinematic relationships. By employing the theory of screws, Dooner [12] provided the third law of gearing and formulated the limiting relationship between the radii of curvature of conjugate surfaces, which is valid only for the reference pitch surfaces. Duan et al. [13] presented the conjugate principle and basic characteristic of Bertrand conjugate surfaces. And Chen et al. [14] researched the geometric properties of moulding conjugate surfaces.However, in some cases, the higher overload requirements are difficult to meet in existing conjugate surfaces. The convex-to-convex tooth profile is more common in contact pattern and it has low contact strength. In additional, there is larger sliding between general tooth surfaces which leads to the low transmission efficiency. Many studies have been carried out to develop various concepts, design, and analysis approaches toward these problems [15–21]. Generally speaking, the surface and curve are both common elements in nature. Compared with general surfaces, the contact between curves has more flexibility and diversity. The related investigations on conjugate curves have been carried out by the authors, and basic meshing principle and theoretical applications for gear transmission have been studied [22–25]. To further reveal general property of conjugate curves and extend the application in gear transmission, the geometric and meshing properties of conjugate curves are discussed in this paper.The remainder of this paper is organized into four sections. In the following section, the principle descriptions of conjugate curves for arbitrary axial position are introduced. Based on differential geometry, geometric analysis of conjugate curves is carried out including tangent and normal in arbitrary contact direction, characteristic point, and curvature relationships in the next section. The subsequent section reveals meshing properties of conjugate curves: the uniqueness of conjugated curves and meshing commonality of conjugate curves. And a conclusive summary of this study is given in the last section.


## 2. Principle Descriptions of Conjugate Curves for Arbitrary Axial Position

Conjugate curves are described as two smooth curves that always keep continuous and tangent contact with each other in given contact direction under motion law. Particularly, the principle of conjugate curves was proposed only for parallel-axes gears in [22] and its procedure graph is displayed in Figure 1. However, for arbitrary axial position, the principle descriptions of conjugate curves are studied.Figure 1
Principle procedure graph of conjugate curves.As shown in Figure2, S(O-x,y,z) and Sp(Op-xp,yp,zp) are the fixed coordinate systems. Conjugate curves Γ1 and Γ2 are defined using coordinate systems S1(O1-x1,y1,z1) and S2(O2-x2,y2,z2) which are connected to pinion 1 and gear 2, respectively. Point P is the contact point.Figure 2
Coordinate systems for arbitrary axial position.The transformation matrix from coordinate systemsS1 to S2 can be expressed as(1)M21=cos⁡ϕ1cos⁡ϕ2-sinϕ1sinϕ2cos⁡Σ-sinϕ1cos⁡ϕ2-cos⁡ϕ1sinϕ2cos⁡Σ-sinϕ2sinΣ-acos⁡ϕ2cos⁡ϕ1sinϕ2+sinϕ1cos⁡ϕ2cos⁡Σ-sinϕ1sinϕ2+cos⁡ϕ1cos⁡ϕ2cos⁡Σcos⁡ϕ2sinΣ-asinϕ2-sinϕ1sinΣ-cos⁡ϕ1sinΣcos⁡Σ00001,where ϕ1 and ϕ2 are the angular displacements of pinion 1 and gear 2, respectively. a is center distance and Σ is angle between the axes of mating gears.The parallel axis, intersecting axis, and crossed axis gear transmission can be realized separately by adjusting the center distancea and angle Σ. Consider that the general curve Γ1 is represented in parametric form as
(2)Γ1:r1=x1θi1+y1θj1+z1θk1,
where θ is curve parameter. i1, j1, and k1 are the unit vectors of coordinate system S1.The relative velocity of pointP(1) of pinion 1 with respect to point P(2) of gear 2 is calculated as
(3)υ1(12)=-y11+i21cos⁡Σ-z1i21cos⁡ϕ1sinΣhhh-ai21sinϕ1cos⁡Σi1+x11+i21cos⁡Σ+z1i21sinϕ1sinΣhhhhh-ai21cos⁡ϕ1cos⁡Σj1+i21sinΣx1cos⁡ϕ1-y1sinϕ1-ak1,
where i21 is the transmission ratio and there exists ϕ2=i21ϕ1.Based on the curve trihedron established in [22], the normal vector to contact point in arbitrary direction of contact angle is expressed as
(4)nn=(t1nβx1+t2nγx1)i1+(t1nβy1+t2nγy1)j1+t1nβz1+t2nγz1k1,
where t1 and t2 are the coefficients indicating the projection of contact angle α0 on the direction of principal normal and binormal vectors, respectively.Moreover, meshing equation along given contact direction is derived as(5)Ucos⁡ϕ1-Vsinϕ1=W,
where
(6)U=i21sinΣnnz1x1-nnx1z1-i21cos⁡Σnny1a;V=-i21sinΣnny1z1-nnz1y1+i21cos⁡Σnnx1a;W=1+i21cos⁡Σnnx1y1-nny1x1+nnz1ai21sinΣ.Using transformation relationr2=M21r1 and meshing equation simultaneously, according to original curve Γ1, the equation of conjugated curve Γ2 is derived as (7). r2 is position vector of point P in S2. Considering transformation matrix from S1 to S, the equation of line of action can also be obtained.The comparison analysis of general principles of conjugate surfaces and conjugate curves is introduced. As the existing theoretical basis of gear geometry, the conjugate surfaces are widely used in the design and generation of tooth surfaces of gears. Usually, as shown in Figure3, conjugated surface 2 can be obtained based on original surface 1 and the given motion law. Then the mating tooth surfaces of gear are generated [3].Figure 3
Theory of conjugate surfaces.However, the conjugate curves are described as two smooth curves that always keep continuous and tangent contact with each other in the given contact direction under motion law. Conjugated curve 2 can be derived according to original curve 1, designated contact direction, and given motion law. Then, the tubular meshing tooth surfaces inheriting meshing characteristics of the conjugate curves are generated based on equidistant-enveloping method [22, 23]. The generated tooth profiles specially can be diversity if choosing the different equidistant orientation and position. The theory of conjugate curves is simply represented in Figure 4 and three different contact models of tooth profiles are also displayed in Figure 5:
(7)x2=x1cos⁡ϕ1cos⁡i21ϕ1-sinϕ1sini21ϕ1cos⁡Σ+y1-sinϕ1cos⁡i21ϕ1-cos⁡ϕ1sini21ϕ1cos⁡Σ-z1sini21ϕ1sinΣ-acos⁡i21ϕ1,y2=x1cos⁡ϕ1sini21ϕ1+sinϕ1cos⁡i21ϕ1cos⁡Σ+y1-sinϕ1sini21ϕ1+cos⁡ϕ1cos⁡i21ϕ1cos⁡Σ+z1cos⁡i21ϕ1sinΣ-asini21ϕ1,z2=-x1sinϕ1sinΣ-y1cos⁡ϕ1sinΣ+z1cos⁡Σ,Ucos⁡ϕ1-Vsinϕ1=W.Figure 4
Theory of conjugate curves.Three different contact models of gear: (a) convex-convex contact; (b) convex-plane contact; (c) convex-concave contact.
(a)
(b)
(c)According to the aforementioned descriptions, the following analysis conclusions can be got as follows:(1)
The contact element is surface for the theory of conjugate surfaces, while curve is the contact element for the theory of conjugate curves.(2)
The tooth surfaces of conjugate-surface gear are generated based on the surface. But the tooth surfaces of conjugate-curve gear are developed by means of the spatial curve. The relation between the curve and surface is revealed.(3)
Conjugated surface 2 is unique for original surface 1 and the meshing pair of conjugate surfaces is also unique. However, conjugated curve 2 is unique in the arbitrary designated contact direction for original curve 1 and the mating conjugate curves are diversity if choosing the various contact direction.(4)
The carrier and form of curves are varied compared to that of surface. The ideal conjugate curves can be obtained according to the selection of original curve and determination of contact direction. The different meshing tooth surfaces containing the characteristics of conjugate curves can be generated.


## 3. Geometric Characteristic Analysis of Conjugate Curves

### 3.1. Tangent and Normal to Conjugate Curves in Arbitrary Contact Direction

The concept of a tangent to the conjugate curves at contact point is similar to that of general curve based on the so-called limiting positions of rays [3]. Consider a set of rays that are drawn through a curve point M and its neighboring points Mi (i=1,2,…,n). As points Mi approach point M, all rays come to some limit position. In the case shown in Figure 6, there are two limiting rays with coinciding lines of action. These two rays form the tangent to the curve at point M and it is identified as a regular point of the curve. A tangent T exists only at a regular point of a curve. A curve point where the tangent T does not exist or is equal to zero is identified as a singular point.Figure 6
Illustration of rays and tangent.Then tangentT is determined and it has
(8)T:rθ=x′θi1+y′θj1+z′θk1.For conjugate curvesΓ1 and Γ2, the tangents T1 and T2 are expressed by r1θ, r2θ, respectively.The normalnn to conjugate curves at contact point in arbitrary direction of contact angle is perpendicular to the tangent to the mating curves. There is an infinite number of normals n belonging to normal plane at contact point M. For instance, vector nn is one of the set of curve normals in Figure 7. Three orthogonal vectors can be determined: the tangent vector α, principal normal β, and binormal γ.Figure 7
Normal to conjugate curves in arbitrary contact direction.The principal normal vectorβ and binormal γ can be calculated, respectively, as
(9)β=xθθ(yθ2+zθ2)-xθ(yθyθθ+zθzθθ)xθ2+yθ2+zθ22i1β=+yθθ(xθ2+zθ2)-yθ(xθxθθ+zθzθθ)xθ2+yθ2+zθ22j1β=+zθθxθ2+yθ2-zθxθxθθ+yθyθθxθ2+yθ2+zθ22k1,γ=yθzθθ-zθyθθxθ2+yθ2+zθ23/2i1-xθzθθ-zθxθθxθ2+yθ2+zθ23/2j1γ=+xθyθθ-yθxθθxθ2+yθ2+zθ23/2k1.The normal vector to contact point in arbitrary direction of contact angle can be represented as a linear combination of principal normal and binormal vectors, and it hasnn=t1β+t2γ. Here, contact angle α0 is defined as the angle between arbitrary normal vector nn and binormal vector γ.


### 3.2. Characteristic Point

Given the curveΓ1, adding a motion parameter λ, the family of curves {Γi} is obtained [2]. The enveloping curve Γ2 can be generated as depicted in Figure 8 if satisfying the following conditions: (1) curve Γ1 is smooth and regular curve. (2) At every instant t, Γ1 and Γ2 touch each other in contact point M. (3) Each point of curve Γ2 is also a contact point at a unique instant t. Obviously, it is the set of different contact points. (4) The relation between curves Γ1 and Γ2 can be rendered quite symmetrical, and each may be said to be conjugated for the other if their domains are suitably restricted.Figure 8
Envelope of a family of curves in given contact direction.According to (2), family of curves {Γi} can be expressed as
(10)Γi:r1=r1θ,λ.
And if the enveloping curve exists, it has
(11)r1¯=r1¯θλ,λ=r1¯λ.For arbitrary curve in family of curves{Γi}, its tangent vector is written as
(12)r1θ=∂r1∂θ.The calculation for enveloping curve is(13)r1¯=∂r1∂θdθdλ+∂r1∂λ=r1θdθdλ+r1λ.There is common tangent between both curves at contact point so that it hasr1θ∥r1¯. Then
(14)r1θ×r1¯=0.Substituting (12) and (13) into (14) yields the result as
(15)r1θ×r1¯=r1θ×∂r1∂θdθdλ+∂r1∂λ=r1θ×r1λ=0;
that is,
(16)r1θ×r1λ=i1j1k1∂x1∂θ∂y1∂θ∂z1∂θ∂x1∂λ∂y1∂λ∂z1∂λ=0.So the mathematical formula of enveloping curve of family of curves{Γi} is derived as
(17)r1=r1θ,λ,r1θ×r1λ=Φ(θ,λ)=0.Compared with the solution of conjugated curve in Section2, (17) has the same meaning with (7). Usually, each family of surfaces and its enveloping surface are not generally tangent at one point, but along a curve which is called the characteristic line on the surface. Actually it is also the contact curve for both surfaces proposed above. The enveloping surface could be used as the set of family of single parameter characteristic lines [3]. Similarly, each family of curves and its enveloping curve are tangent with point contact and the set of contact points which are called characteristic points finally forms the target curve.According to aforementioned discussion, we can get such following conditions.(1) The necessary and sufficient conditions for contact between arbitrary curve of family of curves{Γi} and its enveloping curve are
(18)Φ(θ,λ)=r1θ×r1λ=0
and the generation formula of enveloping curve is
(19)r1=r1θ,λ,r1θ×r1λ=Φ(θ,λ)=0.(2) The characteristic point which is also the conjugate contact point with generated enveloping curve exists on each curve of family of curves{Γi}. It has
(20)r1=r1θ,λ0,r1θ×r1λ0=Φ(θ,λ0)=0,
where λ0 is the constant.


### 3.3. Curvature Relationships

It is well known that the curvature is of great importance indicator for evaluating geometric characteristic of curve, and it reflects the bending degree at one point of curve. As the parameter of arc length,s is introduced to the derivation of curve curvature. As shown in Figure 9, M0 is arbitrary given point of curve Γ and M1 is its neighboring curve point. The correspondence parameters of arc length are s0 and s0+Δs, respectively. Δφ is angle formed by the tangents taken at the given and neighboring curve points. Δs is arc length between the neighboring points. Then the change rate of tangents when point M0 turns the arc length Δs can be described as the curvature of curve Γ at this point.Figure 9
Curve curvature analysis.The curvatureκ0 of a spatial curve is determined as
(21)κ0=lim⁡Δs→0ΔφΔs,
where the subscript “0” in κ0 indicates that the curvature is considered for a small piece of the curve located in the osculating plane. Based on differential geometry, the curvature κ0 can be calculated with formula κ0=rs×rss.To derive equations for determination of the curve curvatureκ0 and curve torsion τ, the parameter s of arc length and curve parameter θ are considered to be related by function s(θ). Based on (2), the curve to be discussed can be represented as r1(s(θ)). Differentiation of this vector function yields
(22)r1θ=rsdsdθ.
Here ds/dθ=r1θ because rs=1. Moreover, it has
(23)r1θθ=rssdsdθ2+rsd2sdθ2,r1θθθ=rsssdsdθ3+3rssdsdθd2sdθ2+rsd3sdθ3.Substituting (22) and (23) into the expression of curvature κ0, we obtain the simplified result
(24)rs×rss=r1θ×r1θθds/dθ3=r1θ×r1θθr1θ3,κ0=r1θ×r1θθr1θ3=x1θy1θθ-x1θθy1θ2+x1θz1θθ-x1θθz1θ2WW+y1θz1θθ-y1θθz1θ21/2×x1θ2+y1θ2+z1θ23/2-1.For the analysis of torsion of curve, the formulaτ=(rs,rss,rsss)/κ02 yields
(25)τ=(r1θ×r1θθ)·r1θθθr1θ×r1θθ2.


## 3.1. Tangent and Normal to Conjugate Curves in Arbitrary Contact Direction

The concept of a tangent to the conjugate curves at contact point is similar to that of general curve based on the so-called limiting positions of rays [3]. Consider a set of rays that are drawn through a curve point M and its neighboring points Mi (i=1,2,…,n). As points Mi approach point M, all rays come to some limit position. In the case shown in Figure 6, there are two limiting rays with coinciding lines of action. These two rays form the tangent to the curve at point M and it is identified as a regular point of the curve. A tangent T exists only at a regular point of a curve. A curve point where the tangent T does not exist or is equal to zero is identified as a singular point.Figure 6
Illustration of rays and tangent.Then tangentT is determined and it has
(8)T:rθ=x′θi1+y′θj1+z′θk1.For conjugate curvesΓ1 and Γ2, the tangents T1 and T2 are expressed by r1θ, r2θ, respectively.The normalnn to conjugate curves at contact point in arbitrary direction of contact angle is perpendicular to the tangent to the mating curves. There is an infinite number of normals n belonging to normal plane at contact point M. For instance, vector nn is one of the set of curve normals in Figure 7. Three orthogonal vectors can be determined: the tangent vector α, principal normal β, and binormal γ.Figure 7
Normal to conjugate curves in arbitrary contact direction.The principal normal vectorβ and binormal γ can be calculated, respectively, as
(9)β=xθθ(yθ2+zθ2)-xθ(yθyθθ+zθzθθ)xθ2+yθ2+zθ22i1β=+yθθ(xθ2+zθ2)-yθ(xθxθθ+zθzθθ)xθ2+yθ2+zθ22j1β=+zθθxθ2+yθ2-zθxθxθθ+yθyθθxθ2+yθ2+zθ22k1,γ=yθzθθ-zθyθθxθ2+yθ2+zθ23/2i1-xθzθθ-zθxθθxθ2+yθ2+zθ23/2j1γ=+xθyθθ-yθxθθxθ2+yθ2+zθ23/2k1.The normal vector to contact point in arbitrary direction of contact angle can be represented as a linear combination of principal normal and binormal vectors, and it hasnn=t1β+t2γ. Here, contact angle α0 is defined as the angle between arbitrary normal vector nn and binormal vector γ.


## 3.2. Characteristic Point

Given the curveΓ1, adding a motion parameter λ, the family of curves {Γi} is obtained [2]. The enveloping curve Γ2 can be generated as depicted in Figure 8 if satisfying the following conditions: (1) curve Γ1 is smooth and regular curve. (2) At every instant t, Γ1 and Γ2 touch each other in contact point M. (3) Each point of curve Γ2 is also a contact point at a unique instant t. Obviously, it is the set of different contact points. (4) The relation between curves Γ1 and Γ2 can be rendered quite symmetrical, and each may be said to be conjugated for the other if their domains are suitably restricted.Figure 8
Envelope of a family of curves in given contact direction.According to (2), family of curves {Γi} can be expressed as
(10)Γi:r1=r1θ,λ.
And if the enveloping curve exists, it has
(11)r1¯=r1¯θλ,λ=r1¯λ.For arbitrary curve in family of curves{Γi}, its tangent vector is written as
(12)r1θ=∂r1∂θ.The calculation for enveloping curve is(13)r1¯=∂r1∂θdθdλ+∂r1∂λ=r1θdθdλ+r1λ.There is common tangent between both curves at contact point so that it hasr1θ∥r1¯. Then
(14)r1θ×r1¯=0.Substituting (12) and (13) into (14) yields the result as
(15)r1θ×r1¯=r1θ×∂r1∂θdθdλ+∂r1∂λ=r1θ×r1λ=0;
that is,
(16)r1θ×r1λ=i1j1k1∂x1∂θ∂y1∂θ∂z1∂θ∂x1∂λ∂y1∂λ∂z1∂λ=0.So the mathematical formula of enveloping curve of family of curves{Γi} is derived as
(17)r1=r1θ,λ,r1θ×r1λ=Φ(θ,λ)=0.Compared with the solution of conjugated curve in Section2, (17) has the same meaning with (7). Usually, each family of surfaces and its enveloping surface are not generally tangent at one point, but along a curve which is called the characteristic line on the surface. Actually it is also the contact curve for both surfaces proposed above. The enveloping surface could be used as the set of family of single parameter characteristic lines [3]. Similarly, each family of curves and its enveloping curve are tangent with point contact and the set of contact points which are called characteristic points finally forms the target curve.According to aforementioned discussion, we can get such following conditions.(1) The necessary and sufficient conditions for contact between arbitrary curve of family of curves{Γi} and its enveloping curve are
(18)Φ(θ,λ)=r1θ×r1λ=0
and the generation formula of enveloping curve is
(19)r1=r1θ,λ,r1θ×r1λ=Φ(θ,λ)=0.(2) The characteristic point which is also the conjugate contact point with generated enveloping curve exists on each curve of family of curves{Γi}. It has
(20)r1=r1θ,λ0,r1θ×r1λ0=Φ(θ,λ0)=0,
where λ0 is the constant.


## 3.3. Curvature Relationships

It is well known that the curvature is of great importance indicator for evaluating geometric characteristic of curve, and it reflects the bending degree at one point of curve. As the parameter of arc length,s is introduced to the derivation of curve curvature. As shown in Figure 9, M0 is arbitrary given point of curve Γ and M1 is its neighboring curve point. The correspondence parameters of arc length are s0 and s0+Δs, respectively. Δφ is angle formed by the tangents taken at the given and neighboring curve points. Δs is arc length between the neighboring points. Then the change rate of tangents when point M0 turns the arc length Δs can be described as the curvature of curve Γ at this point.Figure 9
Curve curvature analysis.The curvatureκ0 of a spatial curve is determined as
(21)κ0=lim⁡Δs→0ΔφΔs,
where the subscript “0” in κ0 indicates that the curvature is considered for a small piece of the curve located in the osculating plane. Based on differential geometry, the curvature κ0 can be calculated with formula κ0=rs×rss.To derive equations for determination of the curve curvatureκ0 and curve torsion τ, the parameter s of arc length and curve parameter θ are considered to be related by function s(θ). Based on (2), the curve to be discussed can be represented as r1(s(θ)). Differentiation of this vector function yields
(22)r1θ=rsdsdθ.
Here ds/dθ=r1θ because rs=1. Moreover, it has
(23)r1θθ=rssdsdθ2+rsd2sdθ2,r1θθθ=rsssdsdθ3+3rssdsdθd2sdθ2+rsd3sdθ3.Substituting (22) and (23) into the expression of curvature κ0, we obtain the simplified result
(24)rs×rss=r1θ×r1θθds/dθ3=r1θ×r1θθr1θ3,κ0=r1θ×r1θθr1θ3=x1θy1θθ-x1θθy1θ2+x1θz1θθ-x1θθz1θ2WW+y1θz1θθ-y1θθz1θ21/2×x1θ2+y1θ2+z1θ23/2-1.For the analysis of torsion of curve, the formulaτ=(rs,rss,rsss)/κ02 yields
(25)τ=(r1θ×r1θθ)·r1θθθr1θ×r1θθ2.


## 4. Meshing Characteristics of Conjugate Curves

### 4.1. Uniqueness of Conjugated Curve

The conjugated curve is generated in terms of the meshing equation and transformation matrixes among different coordinate systems, according to a given original curve. The normal vectornn to conjugate curves at contact point in arbitrary direction of contact angle can be determined in the previous study. Particularly, from the expression of normal vector nn, we can identify that coefficients t1 and t2 indicate the projection of contact angle α0 on the direction of principal normal and binormal vectors, respectively.Given the different coefficientst1 and t2, if the original curve is determined, the corresponding conjugated curve can be represented in various results. Then the further study on the relationship between obtained conjugated curves is carried out. Given the contact angles α1, α2 (where α2=α1+Δα) in Figure 10, respectively, based on principle descriptions of conjugate curves in Section 2, the conjugated curves Γ2i (i=1,2) which are separately related to given conditions are expressed as
(26)x2(i)=x1cos⁡ϕ1icos⁡i21ϕ1i-sinϕ1isini21ϕ1icos⁡Σy2(i)=+y1-sinϕ1icos⁡i21ϕ1iy2(i)=+hhiy1-cos⁡ϕ1isini21ϕ1icos⁡Σy2(i)=-z1sini21ϕ1isinΣ-acos⁡i21ϕ1i,y2(i)=x1cos⁡ϕ1isini21ϕ1i+sinϕ1icos⁡i21ϕ1icos⁡Σy2(i)=+y1-sinϕ1isini21ϕ1iy2(i)=+iy1+cos⁡ϕ1icos⁡i21ϕ1icos⁡Σy2(i)=+z1cos⁡i21ϕ1isinΣ-asini21ϕ1i,z2(i)=-x1sinϕ1isinΣ-y1cos⁡ϕ1isinΣ+z1cos⁡Σ,ϕ1(i)=arcsinW(i)U(i)2+V(i)2-arctanViUi.Figure 10
Two conjugated curves for different contact anglesα1, α2.Considering that conjugated curveΓ21 rotates about central contact point M with angle Δα, it has this expression after the coordinate transformation as
(27)x2(1)′=x2(1)cos⁡Δα+y2(1)sinΔα,y2(1)′=-x21sinΔα+y21cos⁡Δα,z2(1)′=z2(1).Substituting (26) into (27), the derived result is written as
(28)x2(1)′=x1A1+y1B1-z1C1cos⁡Δα+x1A2+y1B2+z1C2sinΔα-acos⁡Δα-i21ϕ11,y2(1)′=-x1A1-y1B1+z1C1sinΔα-x1A2-y1B2-z1C2cos⁡Δα-asinΔα-i21ϕ11,z2(1)′=-x1sinϕ11sinΣ-y1cos⁡ϕ11sinΣ+z1cos⁡Σ,
where
(29)A1=cos⁡ϕ11cos⁡i21ϕ11-sinϕ11sini21ϕ11cos⁡Σ;A2=cos⁡ϕ11sini21ϕ11+sinϕ11cos⁡i21ϕ11cos⁡Σ;B1=-sinϕ11cos⁡i21ϕ11-cos⁡ϕ11sini21ϕ11cos⁡Σ;B2=-sinϕ11sini21ϕ11+cos⁡ϕ11cos⁡i21ϕ11cos⁡Σ;C1=sin(i21ϕ1(1))sinΣ;C2=cos⁡(i21ϕ1(1))sinΣ.A comparison about the expressions ofΓ22 and Γ21′ between (26) and (28) is worked. It can be concluded from the simplified results that the two conjugated curves Γ21 and Γ22 are the same and unique curves, while the difference is that Γ22 is the rotational curve of Γ21 about contact point M under given angle Δα. For verifying above conclusion, the mathematical example for parallel axis gearing based on cylindrical spiral curve is introduced and its parametric form is represented as
(30)r1=Rcos⁡θi1+Rsinθj1+pθk1,
where R is the radius of pitch circle, θ is spiral curve parameter, and p is helix parameter. Through the aforementioned principle of conjugate curves, the equation of conjugated curve is derived as
(31)x2=R-acos⁡i21θ,y2=-R-asini21θ,z2=pθ.A simplified meshing model of conjugate curves along various contact angles for gear drive is developed by means of Matlab software, as displayed in Figure11, according to the designated parameters shown in Table 1.Table 1
Design parameters for conjugate curves.
Parameters
Values
Radius of pitch circleR/mm
24
Tooth number of pinion 1Z1
6
Tooth number of gear 2Z2
30
Transmission ratioi21
5
Modulemn/mm
4
Helix parameterp
28.6478
Central distancea/mm
144
Tooth widthB/mm
50
Parameter of spiral curveθ/rad
0~1.0472
Parametert1
−0.5
Parametert2
−0.866Uniqueness of conjugated curve at any contact position: (a) beginning position; (b) middle position; (c) end position.
(a)
(b)
(c)From Figure11, the generated conjugated curves are different if the selected contact angles are various. When the gear pair rotates with fixed angular velocity, the movement of conjugate curves with 20 degrees rotation, 30 degrees rotation, and 40 degrees rotation can be described, respectively. The engagement point is still fixed on the common point during the whole meshing. Throughout this process, contact point changes gradually in the axial direction, and the line of action is always a straight line which is parallel with gear axes. The characteristics of conjugate curves provide more flexibility for the design of gear transmission. We can choose the optimized design result which is suitable for practical application in terms of appropriate parameters.


### 4.2. Meshing Commonality of Conjugate Curves

To analyze intrinsic nature of conjugate curves, a class of spiral curves contacting in the given direction for various gear axes is discussed.


#### 4.2.1. Gear Pair with Parallel Axis

Assuming that parametersa≠0 and Σ=0, the gear pair with parallel axis can be obtained, as displayed in Figure 12. A calculation procedure of designated spiral curve expressed in (30) for general cylindrical gears is carried out and the conjugated curve is derived as (31).Conjugate spiral curves for parallel axis gear drive.
(a)
(b)Here(32)R1=R-a;θ1=i21θ.
Then (31) can be written as
(33)x2=R1cos⁡θ1,y2=-R1sinθ1,z2=pθ.It is consistent with general form of cylindrical spiral curve in parallel axis gear drive.


#### 4.2.2. Gear Pair with Intersecting Axis

Assuming that parametersa=0 and Σ≠0, the gear pair with intersecting axis can be obtained, as shown in Figure 13. The selected conical spiral curve for bevel gears is expressed in coordinate system S1, and its parametric form is represented as
(34)r1=R1f-cθcos⁡θi1+R1f-cθsinθj1+pθk1,
where R1f is the radius of pitch circle and θ and p are also the spiral curve and helix parameters, respectively. It has the correlation c=ptanδ; δ is the conical angle.Conjugate spiral curves for intersecting axis gear drive.
(a)
(b)Through a series of calculation on the basis of principle of conjugate curves, its conjugated curve is expressed as(35)x2=x1cos⁡ϕ1cos⁡i21ϕ1-sinϕ1sini21ϕ1cos⁡Σ+y1-sinϕ1cos⁡i21ϕ1-cos⁡ϕ1sini21ϕ1cos⁡Σ-z1sini21ϕ1sinΣ,y2=x1cos⁡ϕ1sini21ϕ1+sinϕ1cos⁡i21ϕ1cos⁡Σ+y1-sinϕ1sini21ϕ1+cos⁡ϕ1cos⁡i21ϕ1cos⁡Σ+z1cos⁡i21ϕ1sinΣ,z2=-x1cos⁡ϕ1sinΣ-y1sinϕ1sinΣ+z1cos⁡Σ,Ucos⁡ϕ1-Vsinϕ1=W.Furthermore, substituting (34) into (35), the simplified result with parameter θ is represented as
(36)x2=R1f-c+pθcos⁡i21θ+2θ+Σ,y2=R1f-c+pθsini21θ+2θ+Σ,z2=-csinΣ+pcos⁡Σθ-R1fsinΣ.
Here
(37)c1=c+p;θ2=i21θ+2θ+Σ;p1=-csinΣ+pcos⁡Σ.
Then (36) can be written as
(38)x2=R1f-c1θcos⁡θ2,y2=R1f-c1θsinθ2,z2=p1θ-R1fsinΣ.Conjugated curve attached to gear 2 is got according to above derivation. Obviously, it is also a conical spiral curve in form.


#### 4.2.3. Gear Pair with Crossed Axis

Assuming that parametersa≠0 and Σ≠0, it gets the gear pair with crossed axis which is depicted in Figure 14. The general spiral curve selected for worm gear drive is given and it has the same expression with (30). Based on the principle of conjugate curves, its conjugated curve is derived as
(39)x2=p2sin2Σ+R-a2cos⁡i21θ+arctanR-apsinΣ,y2=p2sin2Σ+R-a2sini21θ+arctanR-apsinΣ,z2=pθcos⁡Σ.
Here
(40)R2=p2sin2Σ+R-a2;θ3=i21θ+arctanR-apsinΣ.
Then (39) can be written as
(41)x2=R2cos⁡θ3,y2=R2sinθ3,z2=pθcos⁡Σ.Conjugate spiral curves for crossed axis gear drive.
(a)
(b)It also represents the similar relationship with given original curve in form.From what are discussed above, we can conclude that the conjugated curves corresponding to the given spiral curves for various gear axes are still the spiral curves. It can be written as the same expression form with the given conditions. It is called meshing commonality of conjugate curves. Moreover, based on the principle of conjugate curves, for any chosen contact curve, the corresponding same type of conjugated curve in the direction of arbitrary contact angle can be identified. Freedom of selecting contact curve suggests the possibility of optimal conjugation design.According to the aforementioned research, it offers a versatile way for high-performance profile design: (1) few teeth number and large module may be obtained without tooth undercutting. The problems of limited installation space and lightweight design can be solved. (2) Three different contact models of tooth profiles can be established based on the proposed study. Particularly, the special meshing of generated convex and concave tooth profiles makes relative radius of curvature of the contact point longer and increases the contact strength. The load capacity and useful life has been evidently improved. (3) The tooth surfaces mesh in point contact along the conjugate curves and contain the transmission properties of conjugate curves. Due to the selection and generation processes, the approximate pure rolling contact between mating tooth surfaces maybe occurs. The transmission efficiency will be improved.The further studies on strength property, manufacturing key technology, and performance experiment of conjugate-curve gear drive will be carried out. And the excellent transmission performance of gearing is expected to be obtained on the basis of theoretical and experimental investigations.


## 4.1. Uniqueness of Conjugated Curve

The conjugated curve is generated in terms of the meshing equation and transformation matrixes among different coordinate systems, according to a given original curve. The normal vectornn to conjugate curves at contact point in arbitrary direction of contact angle can be determined in the previous study. Particularly, from the expression of normal vector nn, we can identify that coefficients t1 and t2 indicate the projection of contact angle α0 on the direction of principal normal and binormal vectors, respectively.Given the different coefficientst1 and t2, if the original curve is determined, the corresponding conjugated curve can be represented in various results. Then the further study on the relationship between obtained conjugated curves is carried out. Given the contact angles α1, α2 (where α2=α1+Δα) in Figure 10, respectively, based on principle descriptions of conjugate curves in Section 2, the conjugated curves Γ2i (i=1,2) which are separately related to given conditions are expressed as
(26)x2(i)=x1cos⁡ϕ1icos⁡i21ϕ1i-sinϕ1isini21ϕ1icos⁡Σy2(i)=+y1-sinϕ1icos⁡i21ϕ1iy2(i)=+hhiy1-cos⁡ϕ1isini21ϕ1icos⁡Σy2(i)=-z1sini21ϕ1isinΣ-acos⁡i21ϕ1i,y2(i)=x1cos⁡ϕ1isini21ϕ1i+sinϕ1icos⁡i21ϕ1icos⁡Σy2(i)=+y1-sinϕ1isini21ϕ1iy2(i)=+iy1+cos⁡ϕ1icos⁡i21ϕ1icos⁡Σy2(i)=+z1cos⁡i21ϕ1isinΣ-asini21ϕ1i,z2(i)=-x1sinϕ1isinΣ-y1cos⁡ϕ1isinΣ+z1cos⁡Σ,ϕ1(i)=arcsinW(i)U(i)2+V(i)2-arctanViUi.Figure 10
Two conjugated curves for different contact anglesα1, α2.Considering that conjugated curveΓ21 rotates about central contact point M with angle Δα, it has this expression after the coordinate transformation as
(27)x2(1)′=x2(1)cos⁡Δα+y2(1)sinΔα,y2(1)′=-x21sinΔα+y21cos⁡Δα,z2(1)′=z2(1).Substituting (26) into (27), the derived result is written as
(28)x2(1)′=x1A1+y1B1-z1C1cos⁡Δα+x1A2+y1B2+z1C2sinΔα-acos⁡Δα-i21ϕ11,y2(1)′=-x1A1-y1B1+z1C1sinΔα-x1A2-y1B2-z1C2cos⁡Δα-asinΔα-i21ϕ11,z2(1)′=-x1sinϕ11sinΣ-y1cos⁡ϕ11sinΣ+z1cos⁡Σ,
where
(29)A1=cos⁡ϕ11cos⁡i21ϕ11-sinϕ11sini21ϕ11cos⁡Σ;A2=cos⁡ϕ11sini21ϕ11+sinϕ11cos⁡i21ϕ11cos⁡Σ;B1=-sinϕ11cos⁡i21ϕ11-cos⁡ϕ11sini21ϕ11cos⁡Σ;B2=-sinϕ11sini21ϕ11+cos⁡ϕ11cos⁡i21ϕ11cos⁡Σ;C1=sin(i21ϕ1(1))sinΣ;C2=cos⁡(i21ϕ1(1))sinΣ.A comparison about the expressions ofΓ22 and Γ21′ between (26) and (28) is worked. It can be concluded from the simplified results that the two conjugated curves Γ21 and Γ22 are the same and unique curves, while the difference is that Γ22 is the rotational curve of Γ21 about contact point M under given angle Δα. For verifying above conclusion, the mathematical example for parallel axis gearing based on cylindrical spiral curve is introduced and its parametric form is represented as
(30)r1=Rcos⁡θi1+Rsinθj1+pθk1,
where R is the radius of pitch circle, θ is spiral curve parameter, and p is helix parameter. Through the aforementioned principle of conjugate curves, the equation of conjugated curve is derived as
(31)x2=R-acos⁡i21θ,y2=-R-asini21θ,z2=pθ.A simplified meshing model of conjugate curves along various contact angles for gear drive is developed by means of Matlab software, as displayed in Figure11, according to the designated parameters shown in Table 1.Table 1
Design parameters for conjugate curves.
Parameters
Values
Radius of pitch circleR/mm
24
Tooth number of pinion 1Z1
6
Tooth number of gear 2Z2
30
Transmission ratioi21
5
Modulemn/mm
4
Helix parameterp
28.6478
Central distancea/mm
144
Tooth widthB/mm
50
Parameter of spiral curveθ/rad
0~1.0472
Parametert1
−0.5
Parametert2
−0.866Uniqueness of conjugated curve at any contact position: (a) beginning position; (b) middle position; (c) end position.
(a)
(b)
(c)From Figure11, the generated conjugated curves are different if the selected contact angles are various. When the gear pair rotates with fixed angular velocity, the movement of conjugate curves with 20 degrees rotation, 30 degrees rotation, and 40 degrees rotation can be described, respectively. The engagement point is still fixed on the common point during the whole meshing. Throughout this process, contact point changes gradually in the axial direction, and the line of action is always a straight line which is parallel with gear axes. The characteristics of conjugate curves provide more flexibility for the design of gear transmission. We can choose the optimized design result which is suitable for practical application in terms of appropriate parameters.


## 4.2. Meshing Commonality of Conjugate Curves

To analyze intrinsic nature of conjugate curves, a class of spiral curves contacting in the given direction for various gear axes is discussed.


### 4.2.1. Gear Pair with Parallel Axis

Assuming that parametersa≠0 and Σ=0, the gear pair with parallel axis can be obtained, as displayed in Figure 12. A calculation procedure of designated spiral curve expressed in (30) for general cylindrical gears is carried out and the conjugated curve is derived as (31).Conjugate spiral curves for parallel axis gear drive.
(a)
(b)Here(32)R1=R-a;θ1=i21θ.
Then (31) can be written as
(33)x2=R1cos⁡θ1,y2=-R1sinθ1,z2=pθ.It is consistent with general form of cylindrical spiral curve in parallel axis gear drive.


### 4.2.2. Gear Pair with Intersecting Axis

Assuming that parametersa=0 and Σ≠0, the gear pair with intersecting axis can be obtained, as shown in Figure 13. The selected conical spiral curve for bevel gears is expressed in coordinate system S1, and its parametric form is represented as
(34)r1=R1f-cθcos⁡θi1+R1f-cθsinθj1+pθk1,
where R1f is the radius of pitch circle and θ and p are also the spiral curve and helix parameters, respectively. It has the correlation c=ptanδ; δ is the conical angle.Conjugate spiral curves for intersecting axis gear drive.
(a)
(b)Through a series of calculation on the basis of principle of conjugate curves, its conjugated curve is expressed as(35)x2=x1cos⁡ϕ1cos⁡i21ϕ1-sinϕ1sini21ϕ1cos⁡Σ+y1-sinϕ1cos⁡i21ϕ1-cos⁡ϕ1sini21ϕ1cos⁡Σ-z1sini21ϕ1sinΣ,y2=x1cos⁡ϕ1sini21ϕ1+sinϕ1cos⁡i21ϕ1cos⁡Σ+y1-sinϕ1sini21ϕ1+cos⁡ϕ1cos⁡i21ϕ1cos⁡Σ+z1cos⁡i21ϕ1sinΣ,z2=-x1cos⁡ϕ1sinΣ-y1sinϕ1sinΣ+z1cos⁡Σ,Ucos⁡ϕ1-Vsinϕ1=W.Furthermore, substituting (34) into (35), the simplified result with parameter θ is represented as
(36)x2=R1f-c+pθcos⁡i21θ+2θ+Σ,y2=R1f-c+pθsini21θ+2θ+Σ,z2=-csinΣ+pcos⁡Σθ-R1fsinΣ.
Here
(37)c1=c+p;θ2=i21θ+2θ+Σ;p1=-csinΣ+pcos⁡Σ.
Then (36) can be written as
(38)x2=R1f-c1θcos⁡θ2,y2=R1f-c1θsinθ2,z2=p1θ-R1fsinΣ.Conjugated curve attached to gear 2 is got according to above derivation. Obviously, it is also a conical spiral curve in form.


### 4.2.3. Gear Pair with Crossed Axis

Assuming that parametersa≠0 and Σ≠0, it gets the gear pair with crossed axis which is depicted in Figure 14. The general spiral curve selected for worm gear drive is given and it has the same expression with (30). Based on the principle of conjugate curves, its conjugated curve is derived as
(39)x2=p2sin2Σ+R-a2cos⁡i21θ+arctanR-apsinΣ,y2=p2sin2Σ+R-a2sini21θ+arctanR-apsinΣ,z2=pθcos⁡Σ.
Here
(40)R2=p2sin2Σ+R-a2;θ3=i21θ+arctanR-apsinΣ.
Then (39) can be written as
(41)x2=R2cos⁡θ3,y2=R2sinθ3,z2=pθcos⁡Σ.Conjugate spiral curves for crossed axis gear drive.
(a)
(b)It also represents the similar relationship with given original curve in form.From what are discussed above, we can conclude that the conjugated curves corresponding to the given spiral curves for various gear axes are still the spiral curves. It can be written as the same expression form with the given conditions. It is called meshing commonality of conjugate curves. Moreover, based on the principle of conjugate curves, for any chosen contact curve, the corresponding same type of conjugated curve in the direction of arbitrary contact angle can be identified. Freedom of selecting contact curve suggests the possibility of optimal conjugation design.According to the aforementioned research, it offers a versatile way for high-performance profile design: (1) few teeth number and large module may be obtained without tooth undercutting. The problems of limited installation space and lightweight design can be solved. (2) Three different contact models of tooth profiles can be established based on the proposed study. Particularly, the special meshing of generated convex and concave tooth profiles makes relative radius of curvature of the contact point longer and increases the contact strength. The load capacity and useful life has been evidently improved. (3) The tooth surfaces mesh in point contact along the conjugate curves and contain the transmission properties of conjugate curves. Due to the selection and generation processes, the approximate pure rolling contact between mating tooth surfaces maybe occurs. The transmission efficiency will be improved.The further studies on strength property, manufacturing key technology, and performance experiment of conjugate-curve gear drive will be carried out. And the excellent transmission performance of gearing is expected to be obtained on the basis of theoretical and experimental investigations.


## 4.2.1. Gear Pair with Parallel Axis

Assuming that parametersa≠0 and Σ=0, the gear pair with parallel axis can be obtained, as displayed in Figure 12. A calculation procedure of designated spiral curve expressed in (30) for general cylindrical gears is carried out and the conjugated curve is derived as (31).Conjugate spiral curves for parallel axis gear drive.
(a)
(b)Here(32)R1=R-a;θ1=i21θ.
Then (31) can be written as
(33)x2=R1cos⁡θ1,y2=-R1sinθ1,z2=pθ.It is consistent with general form of cylindrical spiral curve in parallel axis gear drive.


## 4.2.2. Gear Pair with Intersecting Axis

Assuming that parametersa=0 and Σ≠0, the gear pair with intersecting axis can be obtained, as shown in Figure 13. The selected conical spiral curve for bevel gears is expressed in coordinate system S1, and its parametric form is represented as
(34)r1=R1f-cθcos⁡θi1+R1f-cθsinθj1+pθk1,
where R1f is the radius of pitch circle and θ and p are also the spiral curve and helix parameters, respectively. It has the correlation c=ptanδ; δ is the conical angle.Conjugate spiral curves for intersecting axis gear drive.
(a)
(b)Through a series of calculation on the basis of principle of conjugate curves, its conjugated curve is expressed as(35)x2=x1cos⁡ϕ1cos⁡i21ϕ1-sinϕ1sini21ϕ1cos⁡Σ+y1-sinϕ1cos⁡i21ϕ1-cos⁡ϕ1sini21ϕ1cos⁡Σ-z1sini21ϕ1sinΣ,y2=x1cos⁡ϕ1sini21ϕ1+sinϕ1cos⁡i21ϕ1cos⁡Σ+y1-sinϕ1sini21ϕ1+cos⁡ϕ1cos⁡i21ϕ1cos⁡Σ+z1cos⁡i21ϕ1sinΣ,z2=-x1cos⁡ϕ1sinΣ-y1sinϕ1sinΣ+z1cos⁡Σ,Ucos⁡ϕ1-Vsinϕ1=W.Furthermore, substituting (34) into (35), the simplified result with parameter θ is represented as
(36)x2=R1f-c+pθcos⁡i21θ+2θ+Σ,y2=R1f-c+pθsini21θ+2θ+Σ,z2=-csinΣ+pcos⁡Σθ-R1fsinΣ.
Here
(37)c1=c+p;θ2=i21θ+2θ+Σ;p1=-csinΣ+pcos⁡Σ.
Then (36) can be written as
(38)x2=R1f-c1θcos⁡θ2,y2=R1f-c1θsinθ2,z2=p1θ-R1fsinΣ.Conjugated curve attached to gear 2 is got according to above derivation. Obviously, it is also a conical spiral curve in form.


## 4.2.3. Gear Pair with Crossed Axis

Assuming that parametersa≠0 and Σ≠0, it gets the gear pair with crossed axis which is depicted in Figure 14. The general spiral curve selected for worm gear drive is given and it has the same expression with (30). Based on the principle of conjugate curves, its conjugated curve is derived as
(39)x2=p2sin2Σ+R-a2cos⁡i21θ+arctanR-apsinΣ,y2=p2sin2Σ+R-a2sini21θ+arctanR-apsinΣ,z2=pθcos⁡Σ.
Here
(40)R2=p2sin2Σ+R-a2;θ3=i21θ+arctanR-apsinΣ.
Then (39) can be written as
(41)x2=R2cos⁡θ3,y2=R2sinθ3,z2=pθcos⁡Σ.Conjugate spiral curves for crossed axis gear drive.
(a)
(b)It also represents the similar relationship with given original curve in form.From what are discussed above, we can conclude that the conjugated curves corresponding to the given spiral curves for various gear axes are still the spiral curves. It can be written as the same expression form with the given conditions. It is called meshing commonality of conjugate curves. Moreover, based on the principle of conjugate curves, for any chosen contact curve, the corresponding same type of conjugated curve in the direction of arbitrary contact angle can be identified. Freedom of selecting contact curve suggests the possibility of optimal conjugation design.According to the aforementioned research, it offers a versatile way for high-performance profile design: (1) few teeth number and large module may be obtained without tooth undercutting. The problems of limited installation space and lightweight design can be solved. (2) Three different contact models of tooth profiles can be established based on the proposed study. Particularly, the special meshing of generated convex and concave tooth profiles makes relative radius of curvature of the contact point longer and increases the contact strength. The load capacity and useful life has been evidently improved. (3) The tooth surfaces mesh in point contact along the conjugate curves and contain the transmission properties of conjugate curves. Due to the selection and generation processes, the approximate pure rolling contact between mating tooth surfaces maybe occurs. The transmission efficiency will be improved.The further studies on strength property, manufacturing key technology, and performance experiment of conjugate-curve gear drive will be carried out. And the excellent transmission performance of gearing is expected to be obtained on the basis of theoretical and experimental investigations.


## 5. Conclusions

(1)
The principle descriptions of conjugate curves for arbitrary axial position are introduced. With the aid of given plane or space curve, generation principle and mathematical model of conjugated curve are developed. It can be applied to parallel axis, intersecting axis, and crossed axis gear drive, respectively.
(2)
Based on differential geometry, geometric characteristic analysis of conjugate curves is carried out. The tangent and normal to conjugate curves in arbitrary contact direction are discussed and general calculation methods are provided. The enveloping condition of family of conjugate curves with single parameter is analyzed and characteristic point is determined. Curvature and torsion relationships of conjugate curves are also derived.
(3)
Meshing properties of conjugate curves are further revealed. According to a given plane or spatial curve, the variation law of meshing function is analyzed. The uniqueness of conjugated curves is discussed. The conjugated curves are always the same and unique curves for any given curve under different contact angles, while the difference is that there exists the rotational angle relationship with contact pointM among generated curves.
(4)
Meshing commonality of conjugate curves is demonstrated in terms of a class of spiral curves contacting in the given direction for various gear axes. For any chosen contact curve under various gear axes, the conjugated curve has the same type and it can be written as the same expression form.
(5)
The proposed theory lays the foundation for design of new types of gear drive. The further study on conjugate curves and applications in gear transmission will be carried out. Excellent transmission performance of gearing is expected to be obtained.



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*Source: 484802-2014-12-07.xml*