Hypoid gear design method

Abstract

A hypoid gear tooth surface design method, wherein normal lines and helical angles of two tooth surfaces are properly selected so as to position action limit curves (L3Acc) on the outer of the areas (R2t to R2h) where the tooth surfaces are formed, whereby undercut to a gear small end side can be prevented and, by setting the involute helicoids of two tooth surfaces on a pinion side to an equal lead, a pinion top land and a gear top land (z2h=0) can be made generally equal to each other in tooth lengthwise direction, such that sharpening of the top land can be prevented.

Description

TECHNICAL FIELD

The present invention relates to a hypoid gear tooth surface design method.

BACKGROUND ART

The applicant of the application concerned has proposed a method for uniformly describing a tooth surface of a pair of gears in Japanese Patent Laid-Open Publication No. Hei 9-53702. That is, a method for describing a tooth surface, which can uniformly be used in various situations including for a pair of parallel axes gears, which is the most widely used configuration, and a pair of gears whose axes do not intersect and are not parallel with each other (skew position), has been shown. Furthermore, it has been shown that, in power transmission gearing, it is necessary that the path of contact of the tooth surfaces should be a straight line in order to reduce a fluctuation of a load applied to bearings supporting shafts of gears. In addition, it has been clarified that a configuration wherein at least one tooth surface is an involute helicoid and the other tooth surface is a conjugate surface satisfies the condition that a path of contact of the tooth surfaces should be a straight line. In the case of parallel axes gears, such as spur gears, helical gears, this conclusion is identical with a conclusion of a conventional design method.

Furthermore, conventional gear design methods for non-parallel axes gears have been empirically obtained.

In the case of non-parallel axes gears, it has not yet been clarified that there actually exists a pair of gears wherein one gear has an involute helicoidal tooth surface and the other gear has a conjugate tooth surface for the involute helicoidal tooth surface and, further, an efficient method for obtaining such a pair of tooth surfaces was unknown.

DISCLOSURE OF INVENTION

An object of the present invention is to provide a method for designing a gear set, in particular a gear set comprising a pair of gears whose axes do not intersect and which are not parallel with each other.

The present invention provides a design method for a pair of gears whose axes do not intersect and are not parallel with each other, such as hypoid gears. Hereinafter, a small diameter gear in a pair of hypoid gears is referred to as a pinion and a large diameter gear is referred to as a large gear. In this specification, hypoid gears include a pair of gears in which a pinion is a cylindrical gear having its teeth formed on a cylinder and a large gear is a so-called face gear having teeth on a surface perpendicular to an axis of a disk.

Tooth surfaces of a hypoid gear can be described by a method disclosed in Japanese Patent Laid-Open Publication No. Hei 9-53702 described above.

First, let us consider (a) a stationary coordinate system in which one of three orthogonal coordinate axes coincides with a rotation axis of the gear and one of other two coordinate axes coincides with a common perpendicular for the rotation axis of the gear and the rotation axis of the mating gear to be engaged with the gear, (b) a rotary coordinate system in which one of three orthogonal coordinate axes coincides with the axis of the stationary coordinate system that coincides with the rotation axis of the gear, the rotary coordinate system rotates about the coincided axis together with the gear, and other two coordinate axes of three orthogonal coordinate axes coincide with other two coordinate axes of the stationary coordinate system respectively when the rotation angle of the gear is 0, and (c) a parameter coordinate system in which the stationary coordinate system is rotated about the rotation axis of the gear so that one of other two coordinate axes of the stationary coordinate system becomes parallel with the plane of action of the gear, respectively. Next, in the parameter coordinate system, a path of contact of a pair of tooth surfaces of the gear and the mating gear which are engaging with each other during the rotation of the gears and an inclination angle of the common normal which is a normal at each point of contact for the pair of tooth surfaces are described in terms of a first function, in which a rotation angle of the gear is used as a parameter. Furthermore, in the stationary coordinate system, the path of contact and the inclination angle of the common normal are described respectively in terms of a second function, in which a rotation angle of the gear is used as a parameter, based on the first function and the relationship between the relative positions of the stationary coordinate system and the parameter coordinate system. Furthermore, the path of contact and the inclination angle of the common normal in the stationary coordinate system are acquired, respectively, and in the rotary coordinate system, a tooth profile is obtained by describing the path of contact and the inclination angle of the common normal, respectively, in terms of a third function, in which a rotation angle of the gear is used as a parameter, based on the second function and the relationship between the relative positions of the rotary coordinate system and the stationary coordinate system.

From the obtained tooth profile, the surface of action for the pair of tooth surfaces is obtained. In a gear pair wherein a tooth surface of one gear (first gear) is an involute helicoid and the other gear (second gear) has a tooth surface conjugated with the tooth surface of the first gear, in the obtained surface of action, a zone where effective contact of a pair of tooth surfaces is realized (hereinafter, referred to as an effective surface of action) is limited to a part of the obtained surface of action. First, the effective surface of action must exist between action limit curves which are orthogonal projections of the axes of the two gears on the surface of action. Further, the effective surface of action must exist on the root side of a surface generated by the top of the gear, that is, a trajectory surface of the top of the gear due to the rotation of the gear. Therefore, the effective surface of action must exist between the line of intersection of the face surface formed by the rotation of the top of the gear and the surface of action (hereinafter, referred to as a tip line) and the action limit curves. Therefore, it is preferable that the area enclosed by the action limit curves and the tip line (that is, the effective surface of action) exists at least over the whole facewidth of the gear. When the effective surface of action exists on only a part of the facewidth, the residual facewidth is not useful as a gear, and such a design is nonsensical, or at least wasteful.

Furthermore, in order to actually form gear teeth, it is necessary that the teeth have necessary strength. Specifically, a required thickness must be given to a tooth surface of a drive side and a tooth surface of a coast side, and a root must be thicker than a top in a normal cross section profile of a tooth. In order to make the root sufficiently thick, it is necessary to properly select an intersection angle of the respective paths of contact for the tooth surface of the drive side and the tooth surface of the coast side. It is empirically appropriate that the intersection angle of the respective paths of contact for the tooth surface of the drive side and the tooth surface of the coast side is selected to be in the range from 38° to 40°, which corresponds to the vertex angle in conventional racks. Furthermore, it is empirically appropriate that the line of contact in the drive side is selected so as to nearly coincide with one of the limiting paths of contact (g_2z, g_t, g_1K) described below.

In order to generate the tooth described above on the first gear, it is necessary to acquire a profile of an equivalent rack. It can be considered that the equivalent rack is a generalized rack for involute spur gears.

Furthermore, when the tooth surface of the second gear is obtained using the determined path of contact and the face surface of the second gear is given, the tip lines for both normal and coast sides are obtained and the distance between both tip lines can be obtained; a small distance indicates that the face surface width of the second gear is narrow.

The effective surface of action is likely to be insufficient at a small end of a large gear, and the distance between both tip lines of the second gear (face surface width) is likely to be insufficient at a large end. When the effective surface of action is insufficient at a small end side, a design reference point is shifted toward the small end side of the gear, and acquisition of the tooth profile and the effective surface of action are carried out again. Further, when the distance between both tip lines is insufficient at the large end side, a design reference point is shifted toward the large end side of the large gear, and acquisition of the tooth profile and the effective surface of action is carried out. When the effective surface of action is insufficient at a small end side, and at the same time, the distance between both tip lines is insufficient at the large end side, the facewidth is reduced.

The above design processes can be executed using a computer by describing the processes by a predetermined computer program. Input means for receiving specifications of gears and selection of variables and output means for outputting design results or calculated results until a midterm stage of the design processes are connected to the computer.

BRIEF DESCRIPTION OF DRAWINGS

FIG. 1 is a schematic figure showing coordinate axes of respective coordinate systems, tooth surfaces of gears, tooth profiles, and a path of contact.

FIG. 2 is a figure for explaining relationships between respective coordinate systems.

FIG. 3 is a figure for explaining the obtaining of a path of contact and a tooth profile.

FIG. 4 is a figure showing a path of contact and a tooth profile.

FIG. 5 is a figure showing a concentrated load applied to a gear II and a relationship between the concentrated load and the bearing load.

FIG. 6 is a figure showing a path of contact in a case wherein fluctuations of the bearing load are zero.

FIG. 7 is a figure showing a relative rotation axis S and a coordinate system C_S severally for explaining a specific method for determining five variable values needed to be specified for obtaining a tooth profile from a path of contact (Hereinafter, referred to as a “variable determining method” simply).

FIG. 8 is a figure showing a relative velocity V_S at a point C_S for explaining the aforesaid variable determining method.

FIG. 9 is a figure showing a design reference point P₀, a relative velocity V_rs0 and a path of contact g₀ severally together with planes S_H, S_S, S_P and S_n for explaining the aforesaid variable determining method.

FIG. 10 is a figure showing a relationship between a relative velocity V_rs and the path of contact g₀ at a point P for explaining the aforesaid variable determining method.

FIG. 11 is a figure showing the relative velocity V_rs0 and the path of contact g₀ at the design reference point P₀ severally in the coordinate system C_s for explaining the aforesaid variable determining method.

FIG. 12 is a figure showing the design reference point P₀ and the path of contact g₀ severally in coordinate systems O₂, O_q2, O₁ and O_q1 for explaining the aforesaid variable determining method.

FIG. 13 is a figure showing a relationship among paths of contact g₀(ψ₀, φ_n0), g₀(φ₁₀, ψ_b10) and g₀(φ₂₀, ψ_b20) for explaining the aforesaid variable determining method.

FIG. 14 is a figure showing the path of contact g₀ and a tooth profile II severally in the coordinate systems O₂ and O_r2 for explaining the aforesaid variable determining method.

FIG. 15 is a figure showing the path of contact g₀ and a tooth profile I severally in the coordinate systems O₁ and O_r1 for explaining the aforesaid variable determining method.

FIG. 16 is a figure showing a plane of action G₂₀ for explaining a specific method for determining a tooth surface from a tooth profile (Hereinafter, referred to simply as a “tooth surface determining method”).

FIG. 17 is a figure showing an involute helicoid at a rotation angle θ₂ for explaining the aforesaid tooth surface determining method.

FIG. 18 is a figure showing a common normal n_m(P_m0 P_m) and a line of contact PP_m for explaining the aforesaid tooth surface determining method.

FIG. 19 is a figure showing a relationship among points Q_m0 (P_m0), Q_m (P_m), Q and P on the plane of action G₂₀ for explaining the aforesaid tooth surface determining method.

FIG. 20 is a figure showing a point P_m and the common normal n_m severally in the coordinate systems O₁ and O_q1 for explaining the aforesaid tooth surface determining method.

FIG. 21 is a figure showing a group of pairs of gears which has the same involute helicoids for one member for explaining the aforesaid tooth surface determining method.

FIG. 22 is a figure showing the specifications of a hypoid gear.

FIG. 23 is a figure showing relationships among planes S_H, S_P, S_n, S_t and W_N in a bevel gear and a hypoid gear.

FIG. 24 is a figure showing a design reference perpendicular C_n and a limiting path g_t of a hypoid gear.

FIG. 25 is a figure showing the plane S_n and an equivalent rack.

FIG. 26 is a figure showing relationships among paths of contact g_0D, g_0C, limiting paths g_2z, g_t and an equivalent rack.

FIG. 27 is an oblique perspective figure showing a surface of action.

FIG. 28 is a figure showing examples of an effective surface of action and an action limit curve of a hypoid gear, which is viewed to a negative direction along a z₁ axis in FIG. 27.

FIG. 29 is a figure showing the examples of the effective surface of action and the action limit curve of the hypoid gear, which is viewed to a negative direction along a v₁ axis in FIG. 27.

FIG. 30 is a figure showing the examples of the effective surface of action and the action limit curve of the hypoid gear, which is viewed to a negative direction along a u₁ axis in FIG. 27.

FIG. 31 is a figure showing the examples of the effective surface of action and the action limit curve of the hypoid gear, which corresponds to FIG. 28 and shows a surface of action in a case where the base cylinder is further reduced.

FIG. 32 is a figure showing the examples of the effective surface of action and the action limit curve of the hypoid gear, which corresponds to FIG. 29 and shows a surface of action in a case where the base cylinder is further reduced.

FIG. 33 is a figure showing the examples of the effective surface of action and the action limit curve of the hypoid gear, which corresponds to FIG. 30 and shows a surface of action in a case where the base cylinder is further reduced.

FIG. 34 is a figure showing a relationship of a point of contact P_wsCC of a tooth surface C_c at a rotation angle θ₁ (=0) to the design reference point P₀.

FIG. 35 is a figure showing an effective surface of action drawn by a pinion tooth surface D.

FIG. 36 is a figure showing a gear conjugate tooth surface D generated by the pinion tooth surface D shown in FIG. 35.

FIG. 37 is a figure showing an effective surface of action drawn by the pinion tooth surface C_c.

FIG. 38 is a figure showing a gear conjugate tooth surface C_c generated by the pinion tooth surface C_c shown in FIG. 37.

FIG. 39 is a figure showing a line of intersection of the conjugate gear tooth surfaces D, C_c and planes of rotation of gear (Z_2h=0, 3, 6).

FIG. 40 is a schematic block diagram of a system for supporting gear designing.

FIG. 41 is a flowchart showing of the gear designing process.

FIG. 42 is a plan view of a gear according to the invention, showing the base cylinder radii of the gear tooth surfaces.

BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, embodiments of the present invention are described in accordance with the attached drawings. First, the gear design method disclosed in Japanese Patent Laid-Open Publication No. Hei 9-53702 is described.

A. New Tooth Profile Theory

1. Tooth Profile in the New Tooth Profile Theory

FIG. 1 shows a state of tooth surfaces I, II contacting each other at point P_l. The tooth surfaces I, II rotate at angular velocities ω_1i, ω_2i (being vectors having normal directions shown in the figure), respectively, and respectively transmit certain input and output torque T₁, T₂ (having normal vectors in the same directions as those of the angular velocities ω_1i and ω_2i, respectively) at a certain instance. In the aforesaid contact state, the tooth surface II receives a normal force F_N2i of a concentrated load, and the tooth surface I receives a normal force F_N1i (=−F_N2i) as the reaction of the normal force F_N2i. If a common normal of the tooth surfaces I, II at the point of contact P_i is expressed by a unit vector n_i, the n_i, on the other hand, indicates a line of action (directed) of the normal force of the concentrated load.

If it is supposed that, when a pair of gears has rotated to a certain angular extent, the point of contact has moved to P_j and the angular velocities have changed to ω_1j, ω_2j, and further the normal forces of the concentrated load have changed to F_N1j, F_N2j, P_iP_j draws a path of contact such that common normals are n_i, n_j, respectively, at each point of contact. If the path of contact P_iP_j and the common normals n_i, n_j are transformed into a space rotating with each gear, the path of contact P_iP_j is defined as a space curve on which the tooth profiles I, II transmit quite the same motion as those of the tooth surfaces I, II, and the path of contact P_iP_j expresses a path of movement (tooth bearing) of the concentrated load on the tooth surface. The tooth profiles I, II are tooth profiles in the new tooth profile theory, and the tooth profiles I, II are space curves having a normal (or a microplane) at each point.

Consequently, when considering a contact state of the tooth surfaces I, II nearby a point of contact and mechanical motions of the pair of gears, it is sufficient to consider the tooth profiles I, II in place of the tooth surfaces I, II. Furthermore, if the Tooth profiles I, II are given, the tooth surfaces I, II transmitting quite the same mechanical motions may be a pair of curved surfaces including the tooth profiles I, II and not interfering with each other, with the pair of tooth surfaces being conjugate to each other being only one possible configuration.

As used herein, the concentrated load and its point of action refer to a resultant force of a distributed load (forming an osculating ellipse) of an arbitrary pair of tooth surfaces and its point of action. Consequently, the point of contact is the point of action of the concentrated load on the other hand, and the point of contact includes a deflection according to the concentrated load. Furthermore, because each of the pair of tooth surfaces is the same curved surface having one pitch of a phase difference from each other, the pair of tooth surfaces draws the same path of contact (including a deflection) in a static space according to its loaded state. In a case wherein a plurality of tooth surfaces are engaged with each other, concentrated loads borne by an adjoining pair of tooth surfaces at arbitrary rotation angles are in a row on the path of contact in the state of their phases being shifted from each other by pitches.

2. Basic Coordinate System

For an arbitrary point P on a path of contact P_iP_j, FIG. 2 shows the point P, normal forces F_N2, F_N1 of the concentrated loads at the point P, and a common normal n (a line of action of the concentrated load) at the point P by means of coordinate systems C₁, C₂ and coordinate systems C_q1, C_q2.

A shaft angle Σ, an offset E (≧0, a distance between a point C₁ and a point C₂), and the directions of angular velocities ω₁, ω₂ of two axes I, II are given. It is supposed that, when a common perpendicular of the two axes I, II is made to have a direction in which the direction of ω₂×ω₁, is positive to be a directed common perpendicular v_c, the intersection points of the two axes I, II and the common perpendicular v_c are designated by C₁, C₂ and a situation wherein the C₂ is on the C₁ with respect to the v_c axis will be considered in the following. A case wherein the C₂ is under the C₁ would be very similar.

Planes including the normal force F_N2 (common normal n) of the concentrated load and parallel to each of the gear axes I, II are defined as planes of action G₁, G₂. Consequently, the F_N2 (common normal n) exists on the line of intersection of the planes of action G₁, G₂. Cylinders being tangent to the planes of action G₁, G₂ and having axes being the axis of each gear are defined as base cylinders, and their radii are designated by reference marks R_b1, R_b2.

The coordinate systems C₂, C_q2 of a gear II are defined as follows. The origin of the coordinate system C₂ (u_2c, v_2c, z_2c) is set at C₂, its a_2c axis is set to extend into the ω₂ direction on a II axis, its V_2c axis is set as the common perpendicular v_c in the same direction as that of the common perpendicular v_c, and its u_2c axis is set to be perpendicular to both the axes to form a right-handed coordinate system. The coordinate system C_q2 (q₂, v_q2, z_2c) has the origin C₂ and the z_2c axis in common, and is a coordinate system formed by the rotation of the coordinate system C₂ around the z_2c axis as a rotation axis by χ₂ (the direction shown in the figure is positive) such that the plane v_2c (=0) is parallel to the plane of action G₂. Its u_2c axis becomes a q_2c axis, and its v_2c axis becomes a v_q2c axis.

The plane of action G₂ is expressed by v_q2c=−R_b2 by means of the coordinate system C_q2. To the coordinate system C₂, the inclination angle of the plane of action G₂ to the plane v_2c (=0) is the angle χ₂, and the plane of action G₂ is a plane tangent to the base cylinder (radius R_b2).

The relationships between the coordinate systems C₂ and C_q2 become as follows because the z_2c axis is in common.u_2c=q_2c cos χ₂−v_q2c sin χ₂ v_2c=q_2c sin χ₂+v_q2c cos χ₂

Because the plane of action G₂ meets v_q2c=−R_b2, the following expressions (1), are concluded if the plane of action G₂ is expressed by the radius R_b2 of the base cylinder.u_2c=q_2c cos χ₂+R_b2 sin χ₂ v_2c=q_2c sin χ₂−R_b2 cos χ₂ z_2c=z_2c  (1)

If the common normal n is defined to be on the plane of action G₂ and also defined such that the common normal n is directed in the direction in which the q_2c axis component is positive, an inclination angle of the common normal n from the q_2c axis can be expressed by ψ_b2 (the direction shown in the figure is positive). Accordingly, the inclination angle of the common normal n in the coordinate system C₂ is defined to be expressed by the form of n (φ₂, ψ_b2) by means of the inclination angles φ₂ (the complementary angle of the χ₂) of the plane of action G₂ to the directed common perpendicular v_c, and the ψ_b2.

Here, the positive direction of the normal force F_N2 of the concentrated load is the direction of then and the q_2c axis direction component, and the Z_2c axis direction component of the F_N2 are designated by F_q2, F_z2, respectively.

As for the gear I, coordinate systems C₁ (u_1C, v_1c, z_1c), C_q1 (q_1C, v_q1c, z_1c), a plane of action G₁, a radius R_b1 of the base cylinder, and the inclination angle n (φ₁, ψ_b1) of the common normal n can be similarly defined. Because the systems share a common z_1c axis, the relationship between the coordinate systems C₁ and C_q1 can also be expressed by the following expressions (2).u_1c=q_1c cos χ₁+R_b1 sin χ₁ v_1c=q_1c sin χ₁−R_b1 cos χ₁ z_1c=z_1c  (2)

The relationship between the coordinate systems C₁ and C₂ is expressed by the following expressions (3).u_1c=−u_2c cos Σ−z_2c sin Σv_1c=v_2c+E z_1c=u_2c sin Σ−z_2c cos Σ  (3)

The coordinate systems C₁ and C₂, and the coordinate systems C_q1 and C_q2, all defined above, are the basic coordinate systems of the new tooth profile theory proposed newly by the inventor of the present invention. The basic coordinate systems make it possible that the application scope of the present invention can be considered to include a hypoid gear and a bevel gear as well as cylindrical gears.

The relationship between inclination angles n(φ₁, φ_b1) and n(φ₂, φ_b2) of the common normal n can be obtained as follows because the n exists on the line of intersection of the planes of actions G₁, G₂. Each axis direction component of the coordinate system C₂ of the n can be expressed as follows.L_u2c=cos ψ_b2 sin φ₂ (L_u2c: the u_2c axis direction component of the n)L_v2c=cos ψ_b2 cos φ₂ (L_v2c: the v_2c axis direction component of the n)L_z2c=sin ψ_b2 (L_z2c: the z_2c axis direction component of the n)

Incidentally, the absolute value of the common normal n is 1.

If each axis direction component of the coordinate system C₁ is expressed by each axis direction component of the coordinate system C₂, it can be expressed as follows by means of the expressions (3).L_u1c=−L_u2c cos Σ−L_z2c sin Σ (L_u1c: the u_1c axis direction component of the n)L_v1c=L_v2c (L_v1c: the v_1c axis direction component of the n)L_z1c=L_u2c sin Σ−L_z2c cos Σ (L_z1c: the z_1c axis direction component of the n)

Consequently, the following expressions (4) and (5), can be obtained.

$\begin{array}{cc}\begin{array}{c}\tan {\phi }_1=L_{u1c}/L_{v1c}\\ =-\tan {\phi }_2\cos \Sigma -\tan {\psi }_{b2}\sin \Sigma /\cos {\phi }_2\end{array}& \left(4\right)\\ \begin{array}{c}\sin {\psi }_{b1}=L_{z1c}\\ =\cos {\psi }_{b2}\sin {\phi }_2\sin \Sigma -\sin {\psi }_{b2}\cos \Sigma \end{array}& \left(5\right)\end{array}$

Whereupon, the following expressions can be obtained.φ₁=π/2−χ₁ φ₂=π/2−χ₂ 3. Path of Contact and its Common Normal

FIG. 3 shows the relationships among the point P on a path of contact, the common normal n, and a tangential plane W (shown by a line of intersection w with the plane of action G₂), and a point of contact P_d, a common normal n_d, and a tangential plane W_d after the rotation of the former set by a minute angle Δθ₂ in the coordinate systems C₂ and C_q2. Here, the inclination angles of an arbitrary point of contact P and the common normal n at the point of contact P are expressed as follows by the coordinate system C₂ using the rotation angle θ₂ of the gear II as a parameter.P{u_2c(θ₂), v_2c(θ₂), z_2c(θ₂)}n{φ₂(θ₂), ψ_b2(θ₂)}

The positive direction of the rotation angle θ₂ is the direction shown in the figure. The, the following expression is realized.φ₂(θ₂)=π/2−χ₂(θ₂)

When the point P is expressed by means of the aforesaid expressions (1) by the use of the coordinate system C_q2, the point P can be expressed as follows.P{q_2c(θ₂), −R_b2(θ₂), z_2c(θ₂)}

Furthermore, if the inclination angle on the plane of action G₂ of a tangential line of a path of contact is designated by n_b2 (θ₂), the following expression (6) holds true.(dz_2c/dθ₂)/(dq_2c/dθ₂)=tan η_b2(θ₂)  (6)

If it is supposed that the gear II has rotated by the small angle Δθ₂, the point of contact P has changed to P_d, and the common normal n has changed to the n_d, P_d and n_d can be expressed as follows.P_d{q_2c(θ₂)+Δq_2c, −R_b2(θ₂)+ΔR_b2, z_2c(θ₂)+Δz_2c}n_d{π/2−χ₂(θ₂)−Δχ₂, ψ_b2(θ₂)+Δψ_b2}

It is supposed that a plane of action passing through the point P_d is designated by G_2d, and that, when the gear II has been rotated by Δχ₂ such that the G_2d has become parallel to the plane of action G₂, the plane of action G_2d has moved to G_2de and the point P_d has moved to P_de. Moreover, the orthogonal projection of the point P_de to the plane of action G₂ is designated by P_df. The line of intersection of the plane of action G_2d and the tangential plane W_d at the point P_d is designated by w_d, and the w_d is expressed by w_d′ passing at the point P_df by being projected on the plane of action G₂ as a result of the aforesaid movement. Furthermore, n_d is designated by n_d′. The intersection point of the w_d′ and a plane of rotation passing at the point P is designated by P_dg. The w_d′ is located at a position where the w_d′ has rotated to the w by Δθ₂−Δχ₂ on the plane of action G₂ as a result of the rotation by Δθ₂. Furthermore, the w_d′ inclines to the w by Δψ_b2 at the point P_df. Consequently, the amount of movement PP_dg of the w_d′ to the w in the q_2c axis direction can be expressed as follows.

$\begin{array}{c}{\mathrm{PP}}_{\mathrm{dg}}=\left\{R_{b2}\left({\theta }_2\right)-\Delta R_{b2}/2\right\}\left(\Delta {\theta }_2-\Delta {\chi }_2\right)+\Delta z_{2c}\Delta {\psi }_{b2}/{\cos }^2{\psi }_{b2}\left({\theta }_2\right)\\ =R_{b2}\left({\theta }_2\right)\left(\Delta {\theta }_2-\Delta {\chi }_2\right)\end{array}$

Consequently, a minute displacement Δz_2c on the plane of action G₂ caused by the minute angle Δθ₂ becomes as follows.Δz_2c[tan {ψ_b2(θ₂)+Δψ_b2}+1/tan {η_b2(θ₂)+Δη_b2}]=R_b2(θ₂)(Δθ₂−Δχ₂)

By the omission of second order minute amounts, the expression can be expressed as follows.Δz_2c=R_b2(θ₂)(Δθ₂−Δχ₂)/{tan ψ_b2(θ₂)+1/tan η_b2(θ₂)}

By the use of the aforesaid expression (6), Δq_2c can be expressed as follows.Δq_2c=R_b2(θ₂)(Δθ₂−Δχ₂)/{tan ψ_b2(θ₂) tan η_b2(θ₂)+1}

Because ΔR_b2, Δχ₂, Δψ_b2 and Δη_b2 are functions of θ₂, they can be expressed by the use of Δθ₂ formally as follows.ΔR_b2=(dR_b2/dθ₂)Δθ₂ Δη_b2=(dη_b2/dθ₂)Δθ₂ Δχ₂=(dχ₂/dθ₂)Δθ₂ Δψ_b2(dψ_b2/dθ₂)Δθ₂

By integration of the above expressions from 0 to θ₂, the following expressions (7) can be obtained.

$\begin{array}{cc}\begin{array}{c}{q}_{2c}\left({\theta }_2\right)=\int \left(R_{b2}\left({\theta }_2\right)\left(1-d{\chi }_2/d{\theta }_2\right)/\left\{\tan {\psi }_{b2}\left({\theta }_2\right)\tan {\eta }_{b2}\left({\theta }_2\right)+1\right\}\right)\\ d{\theta }_2+q_{2c}\left(0\right)\\ R_{b2}\left({\theta }_2\right)=\int \left(d{R}_{b2}/d{\theta }_2\right)d{\theta }_2+R_{b2}\left(0\right)\\ z_{2c}\left({\theta }_2\right)=\int \left[R_{b2}\left({\theta }_2\right)\left(1-d{\chi }_2/d{\theta }_2\right)/\left\{\tan {\psi }_{b2}\left({\theta }_2\right)+1/\tan {\eta }_{b2}\left({\theta }_2\right)\right\}\right]\\ d{\theta }_2+z_{2c}\left(0\right)\\ {\eta }_{b2}\left({\theta }_2\right)=\int \left(d{\eta }_{b2}/d{\theta }_2\right)d{\theta }_2+{\eta }_{b2}\left(0\right)\\ {\chi }_2\left({\theta }_2\right)=\int \left(d{\chi }_2/d{\theta }_2\right)d{\theta }_2+{\chi }_2\left(0\right)=\Pi /2-{\phi }_2\left({\theta }_2\right)\\ {\psi }_{b2}\left({\theta }_2\right)=\int \left(d{\psi }_{b2}/d{\theta }_2\right)d{\theta }_2+{\psi }_{b2}\left(0\right)\end{array}& \left(7\right)\end{array}$

The constants of integration indicate the coordinates of the point of contact P₀ at the time of the θ₂=0, the inclination angle of the common normal n₀ at the point of contact P₀, and the inclination angle of the tangential line of a path of contact on a plane of action. The expressions (7) are equations that express a path of contact and the common normal thereof by the coordinate system C_q2 and uses the θ₂ as a parameter. For the determination of the expressions (7), it is sufficient that the specifications at a design reference point P₀ (θ₂=0), i.e. the following ten variables in total, can be given.P₀{q_2c(0), −R_b2(0), z_2c(0)}η_b2(0)n₀{π/2−χ₂(0), ψ_b2(0)}dR_b2/dθ₂ dη_b2/dθ₂ dχ₂/dθ₂ dψ_b2/dθ₂

The expressions (7) are basic expressions of the new tooth profile theory for describing a tooth profile. Furthermore, the expressions (7) are a first function of the present invention.

If the point P is transformed to the coordinate system C₂ (u_2c, v_2c, z_2c), because z_2c is common, the following expressions (8) can be obtained from expressions (1).u_2c(θ₂)=q_2c(θ₂)cos χ₂(θ₂)+R_b2(θ₂)sin χ₂(θ₂)v_2c(θ₂)=q_2c(θ₂)sin χ₂(θ₂)−R_b2(θ₂)cos χ₂(θ₂)z_2c(θ₂)=z_2c(θ₂)  (8)

The expressions (8) are a second function of the present invention. By the use of the aforesaid expressions (2), (3), (4), and (5), the point of contact P and the inclination angle of the common normal n at the point of contact P can be expressed by the following expressions (9), by means of the coordinate systems C, and C_q1 by the use of the θ₂ as a parameter.P{u_1c(θ₂), v_1c(θ₂), z_1c(θ₂)}n{φ₁(θ₂), ψ_b1(θ₂)}P{q_1c(θ₂), −R_b1(θ₂), z_1c(θ₂)}  (9)4. Requirement for Contact and Rotation Angle θ₁ of Gear I

Because the common normal n of the point of contact P exists on the line of intersection of the planes G₁ and G₂, the requirements for contact can be expressed by the following expression (10).R_b1(θ₂)(dθ₁/dt)cos ψ_b1(θ₂)=R_b2(θ₂)(dθ₂/dt)cos ψ_b2(θ₂)  (10)

Consequently, the ratio of angular velocity i(θ₂) and the rotation angle θ₁ of the gear I can be expressed by the following expressions (11).

$\begin{array}{cc}\begin{array}{c}i\left({\theta }_2\right)=\left(d{\theta }_1/dt\right)/\left(d{\theta }_2/dt\right)\\ =R_{b2}\left({\theta }_2\right)\cos {\psi }_{b2}\left({\theta }_2\right)/\left\{R_{b1}\left({\theta }_2\right)\cos {\psi }_{b1}\left({\theta }_2\right)\right\}\\ {\theta }_1=\int i\left({\theta }_2\right)d{\theta }_2\text{(integrated from 0 to }{\theta }_2\text{)}\end{array}& \left(11\right)\end{array}$

It should be noted that it is assumed that θ₁=0 when θ₂=0.

5. Equations of Tooth Profile

5.1 Equations of Tooth Profile II

FIG. 4 shows point P in a coordinate system C_r2 (u_r2c, v_r2c, Z_r2c) rotating along with the gear II. The coordinate system C_r2 has an origin C₂ and z_2c axis in common with the coordinate system C₂ and rotates around the z_2c axis by the θ₂. The u_r2c axis coincides with the u_2c axis when θ₂=0. Because a path of contact and the common normal thereof are given by the above expressions (7), the point P(u_r2c, v_r2c, z_r2c) and the normal n(φ_r2, ψ_b2) at the point P, both being expressed in the coordinate system C_r2, can be expressed by the following expressions (12).χ_r2=χ₂(θ₂)−θ₂=π/2−φ₂(θ₂)−θ₂ φ_r2=φ₂(θ₂)+θ₂ u_r2c=q_2c(θ₂)cos χ_r2+R_b2(θ₂)sin χ_r2 v_r2c=q_2c(θ₂)sin χ_r2−R_b2(θ₂)cos χ_r2 z_r2c=z_2c(θ₂)  (12)

The expressions (12) is a third function of the present invention.

5.2 Equations of Tooth Profile I

If a coordinate system C_r1(u_r1c, v_r1c, z_r1c) rotating by the θ₁ to the coordinate system C₁ is similarly defined, the point P(u_r1c, v_r1c, z_r1c) and the normal n(φ_r1, ψ_b1) at the point P can be expressed by the following expressions (13), by means of the above expressions (9) and (11).χ_r1=χ₁(θ₂)−θ₁=π/2−φ₁(θ₂)−θ₁ φ_r1=φ₁(θ₂)+θ₁ u_r1c=q_1c(θ₂)cos χ_r1+Rb₁(θ₂)sin χ_r1 v_r1c=q_1c(θ₂)sin χ_r1−Rb₁(θ₂)cos χ_r1 z_r1c=Z_1c(θ₂)  (13)

The coordinate system C_r1 and the coordinate system C₁ coincide with each other when θ₁=0. The aforesaid expressions (12) and (13) generally express a tooth profile the ratio of angular velocity of which varies.

The three-dimensional tooth profile theory described above directly defines the basic specifications (paths of contacts) of a pair of gears in a static space determined by the two rotation axes and the angular velocities of the pair of gears without the medium of a pitch body of revolution (a pitch cylinder or a pitch cone). Consequently, according to the tooth profile theory, it becomes possible to solve the problems of tooth surfaces of all of the pairs of gears from cylindrical gears, the tooth surface of which is an involute helicoid or a curved surface approximate to the involute helicoid, to a hypoid gear, and the problems of the contact of the tooth surfaces using a common set of relatively simple expression through the use of unified concepts defined in the static space (such as a plane of action, a normal plane, a pressure angle, a helical angle and the like).

6. Motion of a Pair of Gears and Bearing Loads

6.1 Equations of Motion of Gears II and I and Bearing Loads

FIG. 5 shows relationships among the normal force F_N2 of the concentrated load of the gear II at the point of contact P shown in FIG. 2 and bearing loads B_z2, B_vq2f, B_vq2r, B_q2f, B_q2r by means of the coordinate system C_q2. Here, it is assumed that the lubrication of the tooth surfaces is sufficient and the frictional force component of the concentrated load is negligible. Furthermore, it is also assumed that the gear II is rigidly supported by bearings b_2a, b_2f and b_2r in both of its axis direction and its radius direction and the rigidity of the axis is sufficiently large. In the figure, “′” and “″” indicate the orthogonal projection of a point or a vector, respectively, to an object plane.

Because the gear II rotates around a fixed axle II by receiving the input (output) torque T₂ and the normal force F_N2 of a concentrated load from the gear I, an expression of the equations of motion of the gear II and the bearing load is concluded to the following expressions (15), from the balances of torque and forces related to each axis of the coordinate system C_q2.J₂(d²θ₂/dt²)=F_q2R_b2(θ₂)+T₂ B_z2=−F_z2=−F_q2 tan ψ_b2(θ₂)B_vq2rb₂₀=F_z2R_b2(θ₂)B_q2f+B_q2r=−F_q2 B_q2fb₂₀=−F_q2{z_2c(θ₂)−z_2cr}+F_q2q_2c(θ₂)tan ψ_b2(θ₂)B_vq2f+B_vq2r=0  (15)where

J₂: moment of inertia of gear II

θ₂: rotation angle of gear II

T₂: input (output) torque of gear II (constant)

F_q2, F_z2: q_2c and z_2c axis direction components of normal force F_2N

B_z2: z_2c axis direction load of bearing b_2a

B_{q2f, Bq2r}: q_2c axis direction load of bearings b_2f, b_2r

B_vq2f, B_vq2r: v_q2c axis direction load of bearings b_2f, b_2r

z_2cf, z_2cr: z_2c coordinates of point of action of load of bearings b_2f, b_2r

b₂₀: distance between bearings b_2f and b_2r (z_{2cf −z2cr}>0).

It should be noted that the positive directions of load directions are respective axis directions of the coordinate system C_q2. The situation of the gear I is the same.

6.2 Equations of Motion of a Pair of Gears

By setting of the equations of motion of the gears I and II and the aforesaid the requirement for contact (10) to be simultaneous equations, the equations of motion of a pair of gears are found as the following expressions (16).J₁(d²θ₁/dt²)=F_q1R_b1(θ₂)+T₁ J₂(d²θ₂/dt²)=F_q2R_b2(θ₂)+T₂ −F_q1/cos ψ_b1(θ₂)=F_q2/cos ψ_b2(θ₂)R_b1(θ₂)(dθ₁/d_t)cos ψ_b1(θ₂)=R_b2(θ₂)(dθ₂/dt)cos ψ_b2(θ₂)  (16)

Because a point of contact and the common normal thereof are given by the aforesaid expressions (7), the aforesaid expressions (16) are simultaneous equations including unknown quantities θ₁, θ₂, F_q1, F_q2, and the expressions (16) are basic expressions for describing motions of a pair of gears the tooth profiles of which are given. Incidentally, the expressions (16) can only be applied to an area in which a path of contact is continuous and differentiable. Accordingly, if an area includes a point at which a path of contact is nondifferentiable (such as a point where a number of engaging teeth changes), it is necessary to obtain expressions for describing the motion in the vicinity of the point. It is not generally possible to describe a steady motion of a pair of gears only by the aforesaid expressions (16).

7. Conditions for Making Fluctuations of Bearing Load Zero

Fluctuations of a load generated in the gear II because of the rotation of a pair of gears can be understood as fluctuations of the loads of the bearings b_2a, b_2f and b_2r to the stationary coordinate system C₂. Accordingly, if each bearing load expressed in the coordinate system C_q2 is transformed into an axis direction component in the coordinate system C₂, the result can be expressed by the following expressions (17).B_z2c=B_z2 (the Z_2c axis direction load of the bearing b_2a)B_u2cf=B_q2f cos χ₂−B_vq2f sin χ₂ (the u_2c axis direction load of the bearing b_2f)B_v2cf=B_q2f sin χ₂+B_vq2f cos χ₂ (the v_2c axis direction load of the bearing b_2f)B_u2cr=B_q2r cos χ₂−B_vq2r sin χ₂ (the u_2c axis direction load of the bearing b_2r)B_v2cr=B_q2r sin χ₂+B_vq2r cos χ₂ (the v_2c axis direction load of the bearing b_2r)  (17)

Fluctuation components of the bearing load can be expressed as follows by differentiation of the above expressions (17).

(a) Fluctuation Components of z_2c Axis Direction Load of Bearing b_2a ΔB_z2c=ΔB_z2=−ΔF_z2 ΔF_z2=ΔF_q2 tan ψ_2b+F_q2Δψb₂/cos²ψ_b2 ΔF_q2={Δ(J₂(d²θ₂/dt²))−F_q2ΔR_b2}/R_b2 (b) Fluctuation Components of u_2c and v_2c Axis Direction Loads of Bearing b_2f ΔB_u2cf=ΔB_q2f cos χ₂−B_q2f sin χ₂Δχ₂−ΔB_vq2f sin χ₂−B_vq2f cos χ₂Δχ₂ ΔB_v2cf=ΔB_q2f sin χ₂+B_q2f cos χ₂Δχ₂+ΔB_vq2f cos χ₂−B_vq2f sin χ₂Δχ₂ ΔB_q2f=−[ΔF_q2(z_2c−z_2cr−q_2c tan ψ_b2)+F_q2{Δz_2c−Δq_2c tan ψ_b2−q_2cΔψ_b2/cos²ψ_b2}]/b₂₀ ΔB_vq2f=−(ΔF_z2R_b2+F_z2ΔR_b2)/b₂₀ (c) Fluctuation Components of u_2c and v_2c Axis Direction Loads of Bearing b_2r ΔB_u2cr=ΔB_q2r cos χ₂−B_q2r sin χ₂Δχ₂−ΔB_vq2r sin χ₂−B_vq2r cos χ₂Δχ₂ ΔB_v2cr=ΔB_q2r sin χ₂+B_{q2r cos χ2}Δχ₂+ΔB_vq2r cos χ₂−B_vq2r sin χ₂Δχ₂ ΔB_q2r=−ΔF_q2−ΔB_q2f ΔB_vq2r=−ΔB_vq2f

The fluctuation components of the bearing load of the gear II at an arbitrary rotation angle θ₂ can be expressed as fluctuation components of the following six variables.

Δq_2c

ΔR_b2

Δz_2c

Δχ₂

Δψ_b2

Δ(d²θ₂/dt²)

When the gear II rotates under the condition such that input (output) torque is constant, at least the fluctuation components of the bearing load of the gear II should be zero so that the fluctuations of the bearing load of the gear II may be zero independent of rotation position. Consequently the following relationship holds true.ΔB_z2c=ΔB_u2cf=ΔB_v2cf=ΔB_u2cr=ΔB_v2cr=0

Consequently, the conditions that the fluctuations of the bearing load of the gear II become zero are arranged to the following five expressions (18).(1) Δχ₂=0(2) Δψ_b2=0(3) ΔR_b2(θ₂)=0(4) Δz_2c(θ₂)=Δq_2c(θ₂)tan ψ_b2(θ₂)(5) Δ(d²θ₂/dt²)=0  (18)

In the above, t designates a time hereupon.

Each item of the aforesaid (1)-(5) is described in order.

(1) Condition of Δχ₂(θ₂)=0

The inclination angle χ₂(θ₂) of the plane of action G₂ is constant (designated by χ₂₀). That is, the angle χ₂(θ₂) becomes as follows.

ti χ₂(θ₂)=χ₂(0)=χ₂₀=π/2−φ₂₀

(2) Condition of Δψ_b2(θ₂)=0

The inclination angle ψ_b2(θ₂) on the plane of action G₂ of the common normal of a point of contact is constant (ψ_b20). That is, the following expression is concluded.ψ_b2(θ₂)=ψ_b2(0)=ψ_b20 (3) Condition of ΔR_b2 (θ₂)=0

The base cylinder radius R_b2(θ₂) to which the common normal at a point of contact is tangent is constant (the constant value is designated by R_b20). That is, the following expression is obtained.R_b2(θ₂)=R_b2(0)=R_b20 (4) Condition of Δz_2c(θ₂)=Δq_2c(θ₂)tan ψ_b2(θ₂)

From ψ_b2 (θ₂)=ψ_b20 and expressions (7), the following expressions are obtained.Δz_2c=Δq_2c(θ₂)tan ψ_b20 η_b2(θ₂)=ψ_b20=η_b2(0)

That is, the inclination angle of a tangential line of a path of contact on the plane of action G₂ (q_2c−z_2c plane) should coincide with that of the common normal.

If the results of the conditions (1)-(4) are substituted in the above expressions (7) in order to express the expressions (7) in the coordinate system C₂, a path of contact and the inclination angle of the common normal of the path of contact are expressed by the following expressions.q_2c(θ₂)=R_b20θ₂ cos ²ψ_b20+q_2c(0)u_2c(θ₂)=q_2c(θ₂)cos χ₂₀+R_b20 sin χ₂₀ v_2c(θ₂)=q_2c(θ₂)sin χ₂₀−R_b20 cos χ₂₀ z_2c(θ₂)=R_b20θ₂ cos ψ_b20 sin ψ_b20+z_2c(0)n(φ₂₀=π/2−χ₂₀, ψ_b20)  (19)

The expressions (19) indicate that the path of contact is a straight line passing at a point P₀{q_2c(0), −R_b20, z_2c(0)} in the coordinate system C_q2 and coinciding with the common normal of the inclination angle n(φ₂₀=π/2−χ₂₀, ψ_b20) to the coordinate system C₂. Furthermore, by specifying five variables of R_b20, ψ_b20, q_2c(0), χ₂₀ and z_2c(0), the expressions (19) can specify a path of contact.

If the expressions (19) are transformed into the coordinate systems C₁, C_q1, the expressions (19) can be expressed as a straight line passing through the point P₀{q_1c(0), −R_b10, z_1c(0)} and having an inclination angle n(φ₁₀=π/2−χ₁₀, ψ_b10) to the coordinate system C₁ by means of the above expressions (9). Consequently, the ratio of angular velocity and the rotation angle of the gear I can be expressed as follows by the use of the expressions (11).i(θ₂)=(dθ₁/dt)/(dθ₂/dt)=R_b20 cos ψ_b20/(R_b10 cos ψ_b10)=i₀θ₁=i₀θ₂  (20)

The ratio of angular velocity is constant (designated by i₀)

(5) Condition of Δ(d²θ₂/dt²)=0

(d²θ₂/dt²) is constant. That is, it describes motion of uniform acceleration. Because the motion of a pair of gears being an object in the present case is supposed to be a steady motion such that inputs and outputs are constant, the motion is expressed by (d²θ₂/dt²)=0, and the expression means a motion of uniform rate. Moreover, because (dθ₁/dt) also becomes constant by means of the aforesaid expressions (20), (d²θ₁/dt²)=0 is also concluded as to the gear I. Consequently, by means of the expressions (16), the following expressions can be obtained.F_q2R_b20=−T₂ F_q1R_b10=−T₁

By the use of the aforesaid expressions (20) and a law of action and reaction the following expression is concluded.i₀=F_q2R_b2/(−F_q1R_b10)=−T₂/T₁

That is, the ratio of angular velocity i₀ of a pair of gears should be a given torque ratio (being constant owing to the supposition of the input and the output).

As for the fluctuations of a load to be produced in the gear I, a state wherein the fluctuation of a bearing load is zero is realized in accordance with the conditions of the aforesaid expressions (18) quite similarly to the gear II. Consequently, a path of contact and a common normal thereof should satisfy the following conditions in order to make fluctuations of a bearing load generated in a pair of gears zero under which input and output torques are constant.

• (a) When a point of contact is arbitrarily given in a static space (in the coordinate system C₂), a path of contact should be a straight line coinciding with the common normal of the point of contact and being fixed in the static space.
• (b) Furthermore, the ratio of angular velocity i₀ at the point of contact should be constant and coincide with a given torque ratio.

FIG. 6 shows relationships among a plane of action G₂₀ on which fluctuations of a bearing load are zero, a base cylinder (radius R_b20), a path of contact (common normal n) and the normal force F_N2 of the concentrated load in the coordinate systems C₂ and C_q2. If the path of contact is the same straight line in all of the surfaces of action (including a zone in which a plurality of contacts are included), the path of contact is continuous and differentiable in all of the zones. Consequently, a steady motion having no fluctuations of a bearing load can be realized.

8. Tooth Profile having no Fluctuations of Bearing Load

8.1 Tooth Profile II

If a coordinate system having the origin C₂ and the z_2c axis in common with the coordinate system C₂ and rotating around the z_2c axis by the θ₂ is set to the coordinate system C_r2(u_r2c, v_r2c, z_r2c), a tooth profile II having no fluctuation of its bearing load can be obtained in accordance with the following expressions (21) by transforming the aforesaid expressions (19) into the coordinate system C_r2.χ_r2=χ₂₀−θ₂=π/2−φ₂₀−θ₂ u_r2c=q_2c(θ₂)cos χ_r2+R_b20 sin χ_r2 v_r2c=q_2c(θ₂)sin χ_r2−R_b20 cos χ_r2 z_r2c=z_2c(θ₂)n(φ₂₀+θ₂,ψ_b20)  (21)

Here, the u_r2c axis is supposed to coincide with the r_2c axis when the rotation angle θ₂ is zero.

8.2 Tooth Profile I

Similarly, a coordinate system rotating around the Z_1c axis by the θ₁ is assumed to the coordinate system C_r1 (u_r1c, v_r1c, z_r1c) to the coordinate system C₁. If the aforesaid expressions (19) is transformed into the coordinate systems C₁, C_q1, the transformed expressions express a straight line passing at the point P₀{q_1c(0), −R_b10, z_1c(0)} and having the inclination angle n(φ₁₀=π/2−χ₁₀, ψ_b10) to the coordinate system C₁. Because an arbitrary point on the straight line is given by the aforesaid expressions (9), a tooth profile I having no fluctuations of bearing load can be obtained in accordance with the following expressions (22) by transforming the straight line into the coordinate system C_r1.χ_r1=χ₁₀−θ₁=π/2−φ₁₀−θ₁ u_r1c=q_1c(θ₂)cos χ_r1+R_b10 sin χ_r1 v_r1c=q_1c(θ₂)sin χ_r1−R_b10 cos χ_r1 z_r1c=Z_1c(θ₂)n(φ₁₀+θ_{1, ψb10})  (22)

Here, a u_r1c axis is supposed to coincide with a u_1c axis when the rotation angle θ₁ is zero.

Now, if q_1c(θ₂) and z_1C(θ₂) are substituted by q_1c(θ₁) and Z_1c(θ₁), respectively, again by the use of θ₁=i₀θ₂ and the θ₁ as a parameter, the following expressions (23) can be obtained.q_1c(θ₁)=R_b10θ₁ cos²ψ_b10+q_1c(0)z_1c(θ₁)=R_b10θ₁ cos ψ_b10 sin ψ_b10+z_1c(0)χ_r1=χ₁₀−θ₁=π/2−φ₁₀−θ₁ u_r1c=q_1c(θ₁)cos χ_r1+R_b10 sin χ_r1 v_r1c=q_1c(θ₁)sin χ_r1−R_b10 cos χ_r1 z_r1c=z_1c(θ₁)n(φ₁₀+θ₁, ψ_b10)  (23)

Practically the expressions (23) is easier to use than the expressions (22). The expressions (21), (23) show that the tooth profiles I, II are curves corresponding to the paths of contact on an involute helicoid. It is possible to use curved surfaces that include the tooth profiles I, II and do not interfere with each other as tooth surfaces. However, because the curved surfaces other than the involute helicoid or a tooth surface being an amended involute helicoid are difficult to realize the aforesaid path of contact and the common normal, those curved surfaces are not suitable for power transmission gearing.

A specific method for determining values to be substituted for the aforesaid five variables R_b20, ψ_b20, q_2c(0) χ₂₀, z_2c(0) for specifying the expressions (19) is described in detail.

9. A Pair of Gears Being Objects

A pair of gears being objects having no fluctuation of a bearing load is defined as follows as described above.

• (1) Positional relationships between two axes (a shaft angle Σ, an offset E) and angular velocities ω₁₀, ω₂₀ (assumed to be ω₁₀≧ω₂₀) are given, and a motion of a constant ratio of angular velocity (i₀) is transmitted. Both angular velocities ω₁₀, ω₂₀ are vectors.
• (2) A path of contact is given as a directed straight line g₀ coinciding with the common normal n at a point of contact and being fixed in a static space, and the planes of action of the pair of gears are designated by G₁₀, G₂₀. The g₀ is a unit vector indicating the direction of the path of contact and coincides with the n.
• (3) The coordinate systems C₁, C_q1, C₂, C_q2 are given, and the path of contact g₀ is given as follows by the coordinate systems C₂, C_q2, wherein, the g₀ can be expressed by the coordinate systems C₁, C_q1 and the rotation angle θ₁ of the gear I by replacing the suffix 2 with 1.q_2c(θ₂)=R_b20θ₂ cos² ψ_b20+q_2c(0)u_2c(θ₂)=q_2c(θ₂)cos χ₂₀+R_b20 sin χ₂₀ v_2c(θ₂)=q_2c(θ₂)sin χ₂₀−R_b20 cos χ₂₀ z_2c(θ₂)=R_b20θ₂ cos ψ_b20 sin ψ_b20+z_{hd 2c}(0)  (25)where

θ₂: a rotation angle of the gear II;

q_2c(0), z_2c(0): q_2c and z_2c coordinates of the point of contact when the θ₂ is zero;

χ₂₀: the inclination angle of the plane of action G₂₀ of the gear II;

ψ_b20: the inclination angle of the g₀ on the plane of action G₂₀; and

R_b20: the radius of a base cylinder being tangent with the plane of action G₂₀.

Consequently, it is necessary to select five suitable constants of q_2c(0), Z_2c(0), R_b20, χ₂₀, ψ_b20 in order that the pair of gears being objects transmits the motion of given ratio of angular velocity i₀.

10. Relative Rotation Axis and Coordinate System C_s

10.1 Relative Rotation Axis

FIG. 7 shows a relationship between a relative rotation axis and a coordinate system C_S. If a positional relationship between two axes I and II and their angular velocities ω₁₀, ω₂₀ are given, it is supposed that the intersection points of the common perpendicular v_c (the positive direction thereof is the direction of ω₂₀×ω₁₀) of the two axes with each of the axes I, II are designated by C₁, C₂, respectively, and the C₁ is located under the C₂ with respect to the v_c. If a relative angular velocity ω_r (vector) is supposed to be ω_r=ω₁₀−ω₂₀ and the axis thereof is assumed to be a relative rotation axis S, and then if a plane including the relative rotation axis S and being perpendicular to the common perpendicular v_c is assumed to be a plane S_H and the intersection point of the plane S_H with the common perpendicular v_c is designated by the C_s, the relative rotation axis S is a straight line passing at the C_s, and the position of the relative rotation axis S can be determined as follows.

If the orthogonal projections of the two axes I (ω₁₀), II (ω₂₀) to the plane S_H are designated by I_s (ω₁₀″), II_s (ω₂₀″), respectively, and an angle of the I_S to the II_S when the plane S_H is viewed from the positive direction of the common perpendicular V_c to the negative direction thereof is designated by Ω, the I_s is in a zone of 0≦Ω≦Π(the positive direction of the angle Ω is the counterclockwise direction) to the II_S in accordance with the definition of ω₂₀×ω₁₀. If an angle of the relative rotation axis S (ω_r) to the II_s on the plane S_H is designated by Ω_S (the positive direction of the angle Ω_S is the counterclockwise direction), the components of the ω₁₀ ″ and the ω₂₀″ that are orthogonal to the relative rotation axis on the plane S_H should be equal to each other in accordance with the definition of the relative rotation axis (ω_r=ω₁₀−ω₂₀). Consequently, the Ω_s satisfies the following expressions (26):sin Ω_S/sin(Ω_S−Ω)=ω₁₀/ω₂₀; orsin Γ_S/sin(Σ−Γ_S)=ω₁₀/ω₂₀  (26).wherein, Σ=π−Ω (shaft angle), Γ_s=π−Ω_s. The positive directions are shown in the figure.

The position of the C_s on the common perpendicular v_c can be obtained as follows. FIG. 8 shows a relative velocity V_s (vector) of the point C_s. In accordance with the aforesaid supposition, the C₁ is located under the position of the C₂ with respect to the common perpendicular v_c and ω₁₀≧ω₂₀. Consequently, the C_S is located under the C₂. If the peripheral velocities of the gears I, II at the point C_s are designated by V_s1, V_s2 (both being vectors), respectively, because the relative velocity V_s (=V_s1−V_s2) exists on the relative rotation axis S, the components of the V_s1, V_s2 (existing on the plane S_H ) orthogonal to the relative rotation axis should always be equal to each other. Consequently, the relative velocity V_s (=V_s1−V_s2) at the point C_s is like the shapes as shown in the same figure on the plane S_H according to the location (Γ_s) of the relative rotation axis S, and the distance C₂C_s between the C₂ and the C_s can be obtained by the following expression (27). That is,C₂C_s=E tan Γ_s/{ tan(Σ−Γ_s)+tan Γ_s}  (27).

The expression is effective within a range of 0≦Γ_s≦π, and the location of the C_s changes together with the Γ_s, and the location of the point C_s is located above the C₁ in case of 0≦Γ_s≦π/2, and the location of the point C_s is located under the C₁ in case of π/2≦Γ_s≦π.

10.2 Definition of Coordinate System C_s

Because the relative rotation axis S can be determined in a static space in accordance with the aforesaid expressions (26), (27), the coordinate system C_S is defined as shown in FIG. 7. The coordinate system C_S(u_c, v_c, z_c) is composed of C_s as its origin, the directed common perpendicular v_c as its v_c axis, the relative rotation axis S as its z_c axis (the positive direction thereof is the direction of ω_r), and its u_c axis taken to be perpendicular to both the axes as a right-handed coordinate system. Because it is supposed that a pair of gears being objects transmits a motion of a constant ratio of angular velocity, the coordinate system C_s becomes a coordinate system fixed in the static space. And the coordinate system C_s is a basic coordinate system in case of treating a pair of gears performing the transmission of the motion of constant ratio of angular velocity together with the previously defined coordinate systems C₁, C₂ and their derivative coordinate systems.

10.3 Relationship Among Coordinate Systems C_S, C₁, C₂

If the points C₁, C₂ are expressed to be C₁(0, v_cs1, 0), C₂(0, v_cs2, 0) by the use of the coordinate system C_s, v_cs1, v_cs2 are expressed by the following expressions (29).v_cs2=C_SC₂=E tan Γ_s/{ tan(Σ−Γ_s)+tan Γ_s}v_cs1=C_SC₁=V_cs2−E=−E tan(Σ−Γ_s)/{ tan(Σ−Γ_s)+tan Γ_s}  (29)

If it is noted that C₂ is always located above C_s with respect to the v_c axis, the relationships among the coordinate system C_s and the coordinate systems C₁, C₂ can be expressed as the following expressions (30), (31) by means of v_cs1, V_cs2, Σ and Γ_s.u_1c=u_c cos(Σ−Γ_s)+z_c sin(Σ−Γ_s)v_1c=v_c−v_cs1 z_1c=−u_c sin(Σ−Γ_s)+z_c cos(Σ−Γ_s)  (30)u_2c=−u_c cos Γ_s+z_c sin Γ_s v_2c=v_c−v_cs2 z_2c=−u_c sin Γ_s−z_c cos Γ_s  (31)The relationships among the coordinate system C_S and the coordinate systems C₁, C₂ is schematically shown in FIG. 9.11. Definition of Path of Contact g₀ by Coordinate System C_s 11.1 Relationship Between Relative Velocity and Path of Contact g₀

FIG. 10 shows a relationship between the given path of contact g₀ and a relative velocity V_rs (vector) at an arbitrary point P on the g₀. Incidentally, “′” and “″” in the figure indicate an orthogonal projection on the plane being an object of a point or a vector. If the position vector of the P from an arbitrary point on the relative rotation axis S is designated by r when a tooth surface contacts at the arbitrary point P on the path of contact g₀, the relative velocity V_rs at the point P can be expressed by the following expression (32).V_rs=ω_r×r+V_s  (32)whereω_r=ω₁₀−ω₂₀ ω_r=ω₂₀ sin Σ/sin(Σ−Γ_s)=ω₁₀ sin Σ/sin Γ_s V_s=ω₁₀×[C₁C_s]−ω₂₀×[C₂C_s]V_s=ω₂₀E sin Γ_s=ω₁₀E sin(Σ−Γ_s)

Here, [C₁C_s] indicates a vector having the C₁as its starting point and the C_s as its end point, and [C₂C_s] indicates a vector having the C₂ as its starting point and the C_s as its end point.

The relative velocity V_rs exists on a tangential plane of the surface of a cylinder having the relative rotation axis S as an axis, and an inclination angle ψ to the V_s on the tangential plane can be expressed by the following expression (33). Cos ψ=|V_s|/|V_rs| . . . (33)

Because the path of contact g₀ is also the common normal of a tooth surface at the point of contact, the g₀ is orthogonal to the relative velocity V_rs at the point P.V_rs·g₀=0

Consequently, the g₀ is a directed straight line on a plane N perpendicular to V_rs at the point P. If the line of intersection of the plane N and the plane S_H is designated by H_n, the H_n is normally a straight line intersecting with the relative rotation axis S, through and the g₀ necessarily passing through the H_n if an infinite intersection point is included. If the intersection point of the g₀ with the plane S_H is designated by P₀, then P₀ is located on the line of intersection H_n, and the g₀ and P₀ become as follows according to the kinds of pairs of gears.

(1) In Case of Cylindrical Gears of Bevel Gears (Σ=0, π or E =0)

Because V_s=0, the V_rs simply means a peripheral velocity around the relative rotation axis S. Consequently, the plane N includes the S axis. Hence, H_n coincides with the S, and the path of contact g₀ always passes through the relative rotation axis S. That is, the point P₀ is located on the relative rotation axis S. Consequently, as for these pairs of gears, the path of contact g₀ is an arbitrary directed straight line passing at the arbitrary point P₀ on the relative rotation axis.

(2) In Case of Gear other than Ones Described Above (Σ≠0, π or E≠0)

In the case of a hypoid gear, a crossed helical gear or a worm gear, if the point of contact P is selected at a certain position, the relative velocity V_rs, the plane N and the straight line H_n, all peculiar to the point P, are determined. The path of contact g₀ is a straight line passing at the arbitrary point P₀ on the H_n, and does not pass at the relative rotation axis S normally. Because the point P is arbitrary, g₀ is also an arbitrary directed straight line passing at the point P₀ on a plane perpendicular to the relative velocity V_rs0 at the intersection point P₀ with the plane S_H. That is, the aforesaid expression (32) can be expressed as follows.V_rs=V_rs0+ω_r×[P₀P]g₀

Here, [P₀P] indicates a vector having the P₀ as its starting point and the P as its end point. Consequently, if V_rs0·g₀=0, V_rs·g₀=0, and the arbitrary point P on the g₀ is a point of contact.

11.2 Selection of Design Reference Point

Among pairs of gears having two axes with known positional relationship and the angular velocities, pairs of gears with an identical path contacts g₀ have an identical tooth profile corresponding to g₀, with the only difference between them being which part of the tooth profile is used effectively. Consequently, in a design of a pair of gears, it is important at which position in a static space determined by the two axes the path of contact g₀ is disposed. Further, because a design reference point is only a point for defining the path of contact g₀ in the static space, it does not cause any essential difference at which position on the path of contact g₀ the design reference point is selected. When an arbitrary path of contact g₀ is given, the g₀ necessarily intersects with a plane S_H with the case where the intersection point is located at an infinite point. Accordingly, even when the intersection point is set as a design reference point, generality is not lost. In the present embodiment, it is designed to give the arbitrary point P₀ on the plane S_H (on a relative rotation axis in case of cylindrical gears and a bevel gear) as the design reference point.

FIG. 11 shows the design reference point P₀ and the path of contact g₀ by the use of the coordinate system C_s. When the design reference point expressed by means of the coordinate system C_s is designated by P₀(u_c0, v_c0, z_c0), each coordinate value can be expressed as follows.u_c0=O_sP₀ V_c0=0z_c0=C_SO_S

For cylindrical gears and a bevel gear, u_c0=0. Furthermore, the point O_s is the intersection point of a plane S_s, passing at the design reference point P₀ and being perpendicular to the relative rotation axis S. and the relative rotation axis S.

11.3 Definition of Inclination Angle of Path of Contact g₀

The relative velocity V_rs0 at the point P₀ is concluded as follows by the use of the aforesaid expression (32).V_rs0=ω_r×[u_c0]+V_s where, [u_c0] indicates a vector having the O_s as its starting point and the P₀ as its end point. If a plane (u_c=u_c0) being parallel to the relative rotation axis S and being perpendicular to the plane S_H at the point P₀ is designated by S_p. the V_rs0 is located on the plane S_p, and the inclination angle ψ₀ of the V_rs0 from the plane S_H (V_c=0) can be expressed by the following expression (34) by the use of the aforesaid expression (33).tan ψ₀=ω_ru_c0/V_s=u_c0 sin Σ/{E sin(Σ−Γ_s)sin Γ_s}  (34)

Incidentally, the ψ₀ is supposed to be positive when u_c0≧0, and the direction thereof is shown in FIG. 10.

If a plane passing at the point P₀ and being perpendicular to V_rs0 is designated by S_n, the plane S_n is a plane inclining to the plane S_s by the ω₀, and the path of contact g₀ is an arbitrary directed straight line passing at the point P₀ and located on the plane S_n. Consequently, the inclination angle of the g₀ in the coordinate system C_s can be defined with the inclination angle ψ₀ of the plane S_n from the plane S_s (or the v_c axis) and the inclination angle φ_n0 from the plane S_p on the plane S_n, and the defined inclination angle is designated by g₀ (ψ₀, φ_n0). The positive direction of the φ_n0 is the direction shown in FIG. 11.

11.4. Definition of g₀ by Coordinate System C_s

FIG. 9 shows relationships among the coordinate system C_s, the planes S_H, S_s, S_p and S_n, P₀ and g₀ (ψ₀, φ_n0). The plane S_H defined here corresponds to a pitch plane in case of cylindrical gears and an axis plane in case of a bevel gear according to the conventional theory. The plane S_s is a transverse plane, and the plane S_p corresponds to the axis plane of the cylindrical gears and the pitch plane of the bevel gear. Furthermore, it can be considered that the plane S_n is a normal plane expanded to a general gear, and that the φ_n0 and the ψ₀ also a normal pressure angle and a helical angle expanded to a general gear, respectively. By means of these planes, pressure angles and helical angles of ordinary pairs of gears can be expressed uniformly to static spaces as inclination angles to each plane of common normals (the g₀'s in this case) of points of contact. The planes S_n, φ_n0 defined here coincide with those of a bevel gear of the conventional theory, and differ for other gears because the conventional theory takes pitch planes of individual gears as standards, and then the standards change to a static space according to the kinds of gears. By the conventional theory, if a pitch body of revolution (a cylinder or a circular cone) is determined, it is sufficient to generate a mating surface by fixing an arbitrary curved surface to the pitch body of revolution as a tooth surface, and in the conventional theory conditions of the tooth surface (a path of contact and the normal thereof) are not limited except the limitations of manufacturing. Consequently, the conventional theory emphasizes the selection of P₀ (for discussions about pitch body of revolution), and there has been little discussion concerning design of go (i.e. a tooth surface realizing the g₀) beyond the existence of tooth surface. For making fluctuations of a bearing load zero in the design of a pair of gears, the design of the g₀ is more important than the selection of the P₀.

As for a pair of gears having the given shaft angle Σ thereof, the offset E thereof and the directions of angular velocities, the path of contact g₀ can generally be defined in the coordinate system C_s by means of five independent variables of the design reference point P₀ (u_c0, v_c0, z_c0) and the inclination angle g₀ (ψ₀, φ_n0). Because the ratio of angular velocity i₀ and v_c0=0 are given as conditions of designing in the present embodiment, there are three independent variables of the path of contact g₀. That is, the path of contact g₀ is determined in a static space by the selections of the independent variables of two of (the z_c0), the φ_n0 and the ψ₀ in case of cylindrical gears because the z_c0 has no substantial meaning, three of the z_c0, the φ_n0 and the ψ₀ in case of a bevel gear, or three of the z_c0, the φ_n0 and the ψ₀ (or the u_c0) in case of a hypoid gear, a worm gear or a crossed helical gear. When the point P₀ is given, the ψ₀ is determined at the same time and only the φ_n0 is a freely selectable variable in case of the hypoid gear and the worm gear. However, in case of the cylindrical gears and the bevel gear, because P₀ is selected on a relative rotation axis, both of ψ₀ and φ_n0 are freely selectable variables.

12. Transformation of Path of Contact g₀ to Coordinate Systems O₂, O₁

12.1 Definition of Coordinate Systems O₂, O_q2, O₁, O_q1

FIG. 12 shows the path of contact g₀ in coordinate systems O₂, O_q2, O₁, O_q1. The coordinate systems O₂(u₂, v₂, z₂) O_q2(q₂, v_q2, z₂) are coordinate systems having an origin at the intersection point O₂ of a plane of rotation Z₂₀ of the axis of the gear II passing at the design reference point P₀ with the axis of the gear II, and the coordinate systems O₂ and O_q2 are the coordinate systems C₂, C_q2 displaced by C₂O₂ in the z_2c axis direction in parallel. The coordinate systems O₁(u₁, v₁, z₁), O_q1(q₁, v_q1, z₁) are similarly coordinate systems having an origin being an intersection point O₁ of a plane of rotation Z₁₀ of the axis of the gear I passing at the point P₀ with the axis of the gear I, and the coordinate systems O₁ and O_q1 are the coordinate systems C₁ and C_q1 displaced by C₁O₁ in the Z_1c axis direction in parallel.

12.2 Transformation Expression of Coordinates of Path of Contact

The relationships among the coordinate systems C₂ and O₂, C_q2 and O_q2, and O₂ and O_q2 are as follows.

(1) Coordinate Systems C₂ and O₂ u₂=u_2c v₂=v_2c z₂=z_2cz_2c0 where z_2c0=C_sO_2s=−(u_c0 sin Γ_s+z_c0 cos Γ_s)(2) Coordinate Systems C_q2 and O_q2 q₂=q_2c v₂=v_q2c z₂=z_2c−z_2c0 where z_2c0=C_sO_2s=−(u_c0 sin Γ_s+z_c0 cos Γ_s).(3) Coordinate Systems O₂ and O_q2 (Z₂ are in Common)u₂=q₂ cos χ₂+R_b2 sin χ₂ v₂=q₂ sin χ₂−R_b2 cos χ₂ χ₂=π/2−φ₂

Quite similarly, the relationships among the coordinate systems C₁ and O₁, C_q1 and O_q1, and O₁ and O_q1 are as follows.

(4) Coordinate Systems C₁ and O₁ u₁=u_1c v₁=v_1c z₁=z_1c−z_1c0 where Z_1c0=C_sO_1s=−u_c0 sin(Σ−Γ_s)+z_c0 cos(Σ−Γ_s).(5) Coordinate Systems C_q1 and O_q1 q₁=q_1c v_q1=v_q1c z₁=z_1c−z_1c0 where z_1c0=C_sO_1s=−u_c0 sin(Σ−Γ_s)+z_c0 cos(Σ−Γ_s)(6) Coordinate Systems O₁ and O_q1 (z₁ is in Common)u₁=q₁ cos χ₁+R_b1 sin χ₁ v₁=q₁ sin χ₁−R_b1 cos χ₁ χ₁=π/2−φ_1, (7) Relationships Between Coordinate Systems O₁ and O₂ u₁=−u₂ cos Σ−(z₂+z_2c0)sin Σv₁=v₂+E z₁=u₂ sin Σ−(z₂+z_2c0)cos Σ−z_1c0 12.3 Transformation Expression of Inclination Angle of Path of Contact

If a plane including g₀ and parallel to the gear axis II is set as the plane of action G₂₀, the inclination angle of the g₀ on the coordinate system O₂ can be expressed as g₀(φ₂₀, ψ_b20) by means of the inclination angle φ₂₀ (the complementary angle of the χ₂₀) from the v₂ axis of the plane of action G₂₀ and the inclination angle ψ_b20 from the q₂ axis on the plane of action G₂₀. Quite similarly, the plane of action G₁₀ is defined, and the inclination angle of the g₀ can be expressed as g₀ (φ₁₀, ψ_b10) by means of the coordinate system O₁.

FIG. 13 shows relationships among g₀ (ψ₀, φ_n0), g₀(φ₁₀, ψ_b10) and g₀ (φ₂₀, ψ_b20). If it is assumed that a point of contact has moved from P₀ to P on the path of contact g₀ due to the rotation of the pair of gears and the displacement P₀P=L_g (positive when θ₂>0), each axis direction component of the coordinate system C_s can be expressed as follows.L_uc=−L_g sin φ_n0 (L_uc: the u_c direction component of the L_g)L_vc=L_g cos φ_n0 cos ψ₀ (L_vc: the v_c direction component of the L_g)L_zc=L_g cos φ_n0 sin ψ₀ (L_zc: the z_c direction component of the L_g)

Each axis direction component of the coordinate system O₂ can be expressed as follows by means of expressions (31) using each axis direction component of the coordinate system C_s.L_u2=−L_{uc 6} cos Γ_s+L_zc sin Γ_s (L_u2: the u₂ direction component of the L_g)L_v2=L_vc (L_v2: the v₂ direction component of the L_g)L_z2=−L_uc sin Γ_s−L_zc cos Γ_s (L_z2: the z₂ direction component of the L_g)

Consequently, the g₀(φ₂₀, ψ_b20) is concluded as follows.tan φ₂₀=L_u2/L_v2=tan φ_n0 cos Γ_s/cos ψ₀+tan ψ₀ sin Γ_s  (35)sin ψ_b20=L_z2/L_g=sin φ_n0 sin Γ_s−cos φ_n0 sin ψ₀ cos Γ_s  (36)

Quite similarly, the g₀ (φ₁₀, ψ_b10) is concluded as follows.tan φ₁₀=L_u1/L_{v1=−tan φn0} cos(Σ−rΓ_s)/cos ψ₀+tan ψ₀ sin(Σ−Γ_s)  (37)sin ψ_b10=L_z1/L_g=sin φ_n0 sin(Σ−Γ_s)+cos φ_n0 sin ψ₀ cos(Σ−Γ_s)  (38)

From the expressions (35), (36), (37), and (38), relationships among the g₀(ψ₀, φ_n0), the g₀(φ₁₀, ψ_b10) and the g₀ (φ₂₀, ψ_b20) are determined. Because the above expressions are relatively difficult to use for variables other than φ_n0 and ψ₀, relational expressions in the case where g₀(φ₁₀, ψ_b10) and g₀(φ₂₀, ψ_b20) are given are obtained here.

(1) Relational Expressions for Obtaining g₀(ψ₀, φ_n0) and g₀(φ₁₀, ψ_b10) from g₀(φ₂₀, ψ_b20)sin φ_n0=cos ψ_b20 sin φ₂₀ cos Γ_s+sin ψ_b20 sin Γ_s  (39)tan ψ₀=tan φ₂₀ sin Γ_s−tan ψ_b20 cos Γ_s/cos φ₂₀  (40)tan φ₁₀=tan φ₂₀ sin(Σ−π/2)−tan ψ_b20 cos(Σ−π/2)/cos φ₂₀  (41)sin ψ_b10 =cos ψ_b20 sin φ₂₀ cos(Σ−π/2)+sin ψ_b20 sin(Σ−π/2)  (42)(2) Relational Expressions for Obtaining g₀ (ψ₀, φ_n0) and g₀ (φ₂₀, ψ_b20) from g₀(φ₁₀, ψ_b10)sin φ_n0=−cos ψ_b10 sin φ₁₀ cos(Σ−Γ_s)+sin ψ_b10 sin(Σ−Γ_s)  (43)tan ψ₀=tan φ₁₀ sin(Σ−Γ_s)+tan ψ_b10 cos(Σ−Γ_s)/cos φ₁₀  (44)tan φ₂₀=tan φ₁₀ sin(Σ−π/2)+tan ψ_b10 cos(Σ−π/2)/cos φ₁₀  (45)sin ψ_b20=−cos ψ_b10 sin φ₁₀ cos(Σ−π/2)+sin ψ_b10 sin(Σ−π/2)  (46)12.4 Path of Contact g₀ Expressed by Coordinate System O₂

Next, the equation of a path of contact by the coordinate system O₂ is described. FIG. 14 shows the path of contact g₀ and the corresponding tooth profile II. It is supposed that the path of contact g₀ contacts at the design reference point P₀ when θ₂=0, and that the tangential plane at that time is designated by W₀ (expressed by a line of intersection with the plane of action in the same figure). It is also supposed that the point of contact has moved to the P and the tangential plane has moved to the W after the gear II has rotated by the θ₂.

(1) Design Reference Point P₀

A design reference point is given at P₀(u_c0, 0, z_c0) by the coordinate system C_s. Here, it is assumed that z_c0≧0 and u_c0=0 especially in case of cylindrical gears and a bevel gear. Consequently, if the design reference point expressed by the coordinate system O₂ is designated by P₀(u_2p0, −v_cs2, 0), u_2P0 can be expressed as follows by means of the expressions (31).u_2p0=O_2sP₀=−u_c0 cos Γ_s+z_c0 sin Γ_s  (47)

Because the g₀ (φ₂₀, ψ_b20) is given by the aforesaid expressions (35) and (36), if the P₀(u_2p0, −v_cs2, 0) is expressed by the P₀(q_2p0, −R_b20, 0) by transforming the P₀ (u_2p0, −v_cs2, 0) into the coordinate system O_q2, the q_2p0 and the R_b20 are as follows.q_2p0=u_2p0 cos χ₂₀−v_cs2 sin χ₂₀ R_b20=u_2p0 sin χ₂₀+v_cs2 cos χ₂₀ χ₂₀=π/2−φ₂₀  (48)(2) Equations of Path of Contact g₀

If the expressions (25) is transformed into the coordinate systems O₂ and O_q2 and the expressions (48) are substituted for the transformed expressions (25), the equations of the path of contact g₀ are concluded as follows by the coordinate system O₂ as the coordinates of the point of contact P at the rotation angle θ₂. When θ₂=0, the path of contact g₀ contacts at the design reference point P₀.q₂(θ₂)=R_b20θ₂ cos²ψ_b20+q_2p0 u₂(θ₂)=q₂(θ₂)cos χ₂₀+R_b20 sin χ₂₀ v₂(θ₂)=q₂(θ₂)sin χ₂₀−R_b20 cos χ₂₀ z₂(θ₂)=R_b20θ₂ cos ψ_b20 sin ψ_b20  (49)12.5 Path of Contact g₀ Expressed by Coordinate System O₁

FIG. 15 shows the path of contact g₀ and the corresponding tooth profile I. Because g₀ (φ₁₀, ψ_b10) is given by the aforesaid expressions (37) and (38), if the design reference point P₀(u_c0, 0, z_c0) is transformed into the coordinate systems O₁ and O_q1 to be expressed by P₀(u_1po, −v_cs1, 0) and p₀(q_1po, −R_b10, 0) quite similarly to the case of coordinate system O₂, u_1p0, q_1p0 and R_b10 are concluded as follows by means of the aforesaid expressions (30).u_1p0=O_1sP₀=u_c0 cos(Σ−Γ_s)+z_c0 sin(Σ−Γ_s)q_1p0=u_1p0 cos χ₁₀−v_cs1 sin χ₁₀ R_b10=u_1p sin χ₁₀+v_cs1 cos χ₁₀ χ₁₀=π/2−φ₁₀

Consequently, the equations of the path of contact g₀ are concluded as follows by expressing the aforesaid expressions (25) using the coordinate systems O₁ and O_q1 and θ₁.θ₁=i₀θ₂ (θ₁=0 when θ₂=0)q₁(θ₁)=R_b10θ₁ cos²ψ_b10+q_1p0 u₁(θ₁)=q₁(θ₁)cos χ₁₀+R_b10 sin χ₁₀ v₁(θ₁)=q₁(θ₁)sin χ₁₀−R_b10 cos χ₁₀ z₁(θ₁)=R_b10θ₁ cos ψ_b10 sin ψ_b10  (49-1)

Because the path of contact g₀ is given as a straight line fixed in static space and the ratio of angular velocity is constant, the equations of the path of contact can be expressed in the same form independently from the positional relationship of the two axes.

13. Equations of Tooth Profile

13.1 Equations of Tooth Profile II

FIG. 14 shows a tooth profile II using a coordinate system O_r2 (u_r2, V_r2, z_r2) rotating at the θ₂ together with the gear II. The coordinate system O_r2 has an origin O₂ and a z₂ axis in common with the coordinate system O₂, and coincide at the time of θ₂=0. Because the path of contact g₀ is given by the expressions (49), the equations of the tooth profile II expressed by the rotary coordinate system O_r2 are concluded as follows.χ_r2=χ₂₀−θ₂=π/2−φ₂₀−θ₂ u_r2=q₂(θ₂)cos χ_r2+R_b20 sin χ_r2 v_r2=q₂(θ₂)sin χ_r2−R_b20 cos χ_r2 z_r2=R_b20θ₂ cos ψ_b20 sin ψ_b20  (50)13.2 Equations of Tooth Profile I

FIG. 15 shows a tooth profile I in a coordinate system O_r1 (u_r1, v_r1, z_r1) rotating at θ₁ together with the gear I and the coordinate system O₁. The origin O₁ and the z₁ axis of coordinate system O_r1 are in common with those of the coordinate system O₁, with which it corresponds at the time of θ₁=0. Because the path of contact g₀ is given by the expressions (49-1), equations of the tooth profile I expressed by the rotary coordinate system O_r1 are concluded as follows.χ_r1=χ₁₀−θ₁=π/2−φ₁₀−θ₁ u_r1=q₁(θ₁)cos χ_r1−R_b10 sin χ_r1 v_r1=q₁(θ₁)sin χ_r1−R_b10 cos χ_r1 z_r1=R_b10θ₁ cos ψ_b10 sin ψ_b10  (53)

Next, a specific method for determining a tooth surface from a determined tooth profile is described in detail on the basis of the figures.

14. Definition of a Pair of Gears as Objects

It is supposed that an involute pair of gears being objects of the invention is defined as follows. If the tooth profiles corresponding to the path of contact g₀ are severally supposed to be the tooth profiles I, II, an involute helicoid including the tooth profile II is given as the tooth surface II, and a curved surface generated by the tooth surface II at the constant ratio of angular velocity i₀ is supposed to be the tooth surface I (consequently including the tooth profile I). If the tooth surfaces of the involute pair of gears defined in such a way are made to contact with each other along the tooth profiles I, II, fluctuations of a bearing load become zero. Consequently the involute pair of gears becomes the most advantageous pair of gears as a pair of gears for power transmission in view of the fluctuations of a load. Then, hereinafter, the relational expression of the involute pair of gears, i.e. equations of the involute helicoid, the surface of action thereof and the conjugate tooth surface I thereof, are described.

15. Equations of Involute Helicoid (Tooth Surface II)

15.1 Equations of Plane of Action G₂₀

FIG. 16 shows the plane of action G₂₀ (the inclination angle thereof: χ₂₀=π/2−φ₂₀) including the design reference point P₀ and the path of contact g₀, both being given by the aforesaid expressions (25) using the coordinate systems O₂, O_q2. The line of intersection of the tangential plane W₀ and the G₂₀ at the point P₀ is shown as a straight line w₀. It is assumed that the point of contact P₀ has moved to the P and the w₀ has moved to the w when the gear II has rotated by θ₂.

Because the tooth surface normal n of an arbitrary point on the w is located on the plane of action G₂₀ and the inclination angle ψ_b20 of the tooth surface normal n from the q₂ axis is constant in accordance with the definition of the involute helicoid, the w is a straight line passing at the point P on the g₀ and perpendicular to g₀. Consequently, the involute helicoid can be defined to be a trajectory surface drawn by the line of intersection w, moving on the G₂₀ in the q₂ axis direction by R_b20θ₂ in parallel together with the rotation of the gear II (rotation angle is θ₂), in a rotating space (the coordinate system O_r2) fixed to the gear II. Then, if an arbitrary point on the straight line w is designated by Q and the point Q is expressed by the coordinate system O_r2, the involute helicoid to be obtained can be expressed as a set of Q values.

If a directed straight line passing at the arbitrary point Q on the w and located on the plane of action G₂₀ perpendicular to w is designated by n (the positive direction thereof is the same as that of g₀) and the intersection point of n and w₀ is designated by Q₀, the point Q₀ (q₂₀, −R_b20, z₂₀) expressed by the coordinate system O_q2 can be determined as follows.q₂₀=q_2p0−z₂₀ tan ψ_b20

Consequently, if the point Q is expressed by the coordinate system O_q2, the Q(q₂, −R_b20, z₂) is expressed as follows.q₂(θ₂, z₂₀)=R_b20θ₂cos²ψ_b20+q₂₀=R_b20θ₂ cos²ψ_b20+q_2p0−z₂₀ tan ψ_b20 z₂(θ₂, z₂₀)=R_b20θ₂ cos ψ_b20 sin ψ_b20+z₂₀

Moreover, if the point Q is expressed by the coordinate system O₂, the Q(u₂, n₂, z₂) is found as follows.q₂(θ₂, z₂₀)=R_b20θ₂ cos²ψ_b20+q_2p0−z₂₀ tan ψ_b20 u₂(θ₂, z₂₀)=q₂(θ₂, z₂₀)cos χ₂₀+R_b20 sin χ₂₀ v₂(θ₂, z₂₀)=q₂(θ₂, z₂₀)sin χ₂₀−R_b20 cos χ₂₀ z₂(θ₂, z₂₀)=R_b20θ₂ cos ψ_b20 sin ψ_b20+z₂₀  (54)The expressions (54) is the equation of the plane of action G₂₀ that is expressed by the coordinate system O₂ by the use of the θ₂ and the z₂₀ as parameters. If the θ₂ is fixed, the line of intersection w of the tangential plane W and the plane of action G₂₀ is expressed, and if the z₂₀ is fixed, the directed straight line n on the plane of action is expressed. Because the path of contact g₀ is also a directed straight line n passing at the point P₀ the aforesaid expression (49) can be obtained by the setting of z₂₀=0.15.2 Equations of Involute Helicoid

If the straight line w in FIG. 16 is transformed into a coordinate system rotating together with the gear II, the locus of the straight line w draws an involute helicoid (the base cylinder radius thereof: R_b20, the helical angle thereof: ψ_b20). Accordingly, it is supposed that the locus of the straight line w is given as the tooth surface II. At this point, the directed straight line n at the point Q is the tooth surface normal n.

FIG. 17 shows an arbitrary point P_m on an involute helicoid (the tooth surface II) passing at the straight line w at the rotation angle θ₂ in the coordinate system O₂. If it is supposed that the w is at w_m when the tooth surface II has further rotated from the w by ξ₂, the intersection point Q_m of the w_m and the n can be expressed as follows.q_2m(θ₂, z₂₀, ξ₂)=q₂(θ₂, z₂₀)+R_b20ξ₂ cos²ψ_b20 z_2m(θ₂, z₂₀, ξ₂)=z₂(θ₂, z₂₀)+R_b20ξ₂ cos ψ_b20 sin ψ_b20

If a rotary coordinate system O_r2m is a coordinate system that coincides with the coordinate system O₂ when the rotation angle θ₂ and rotates by the ξ₂ around the z₂ axis, Q_m(u_r2m, v_r2m, z_r2m) can be expressed by the coordinate system O_r2m as follows.χ_r2m=χ₂₀−ξ₂=π/2−φ₂₀−ξ₂ u_r2m(θ₂, z₂₀, ξ₂)=q_2m(θ₂, z₂₀, ξ₂)cos χ_r2m+R_b20 sin χ_r2m v_r2m(θ₂, z₂₀, ξ₂)=q_2m(θ₂, z₂₀, ξ2)sin χ_r2m−R_b20 cos χ_r2m z_r2m(θ₂, z₂₀, ξ₀)=z₂(θ₂, z₂₀)+R_b20ξ₂ cos ψ_b20 sin ψ_b20

If the coordinate system O_r2m is rotated by the ξ₂ in the reverse direction of the θ₂ to be superposed on the coordinate system O₂, the Q_m moves to the P_m. Because the point Q_m on the coordinate system O_r2m is the point P_m on the coordinate system O₂ and both of points have the same coordinate values, the P_m(u_2m, v_2m, z_2m) becomes as follows if the point P_m is expressed by the coordinate system O₂.χ_2m=χ₂₀−ξ₂=π/2−φ₂₀−ξ₂ q_2m(θ₂, z₂₀, ξ₂)=q₂(θ₂, z₂₀)+R_b20ξ₂ cos²ψ_b20 u_2m(θ₂, z₂₀, ξ₂)=q_2m(θ₂, z₂₀, ξ₂)cos χ_2m+R_b20 sin χ_2m v_2m(θ₂, z₂₀, ξ₂)=q_2m(θ₂, z₂₀, ξ₂)sin χ_2m−R_b20 cos χ_2m z_2m(θ₂, z₂₀, ξ₂)=z₂(θ₂, z₂₀)+R_b20ξ₂ cos ψ_b20 sin ψ_b20  (55)

The expressions (55) are equations of the involute helicoid (the tooth surface II) passing at the point P on the path of contact g₀ at the arbitrary rotation angle θ₂ and using the z₂₀ and the ξ₂ as parameters by the coordinate system O₂. Supposing θ₂=0, the expressions (55) define the tooth surface II passing at the design reference point P₀. Moreover, supposing z₂₀=0, the expressions (55) become the expressions (50), i.e. the tooth profile II passing at the point P₀. Or, the expressions (55) can be considered as the equations of the point P_m on a plane G_2m, being the point Q_m on the plane of action G₂₀ rotated by the ξ₂ into the reverse direction of the θ₂, by the coordinate system O₂. When the involute helicoid passing at the point P is examined on the coordinate system O₂, the latter interpretation simplifies analysis.

16. Line of Contact and Surface of Action

When the tooth surface II is given by the expressions (55), the line of contact passing at the point P is a combination of the z₂₀ and the ξ₂, both satisfying the requirement for contact when the θ₂ is fixed. Consequently, the line of contact can be obtained as follows by the use of the ξ₂ as a parameter.

16.1 Common Normal n_m(P_m0P_m) of Point of Contact

FIG. 18 shows a line of contact PP_m and a common normal n_m(P_m0P_m) at the point of contact P_m. It is assumed that the gear II has rotated by the θ₂ and the point of contact is positioned at the point P on the path of contact g₀. The point of contact P_m other than the P is set on the tooth surface II, and the relative velocity of the point of contact P_m is designated by V_rsm, and the common normal of the point of contact P_m is designated by n_m(|n_m|=1). If the intersection point of the n_m with the plane S_H is designated by P_m0 and the relative velocity of the point P_m0 is designated by V_rsm0, because the P_m is a point of contact, the following relational expressions hold true.n_m·V_rsm=n_m·(V_rsm0+ω_r×[P_m0P_m]·n_m)=n_m·V_rsm0=0where [P_m0P_m] indicates vector having the P_m0 as its starting point and the P_m as its end point.

Because the relative velocity V_rsm0 is located on the plane S_pm passing at the P_m0 and being parallel to the plane S_p, an inclination angle on the plane S_pm to the plane S_H is designated by ψ_m0. If a plane passing at the point P_m0 and being perpendicular to the V_rsm0 is designated by S_nm, the plane S_nm includes the n_m(P_m0P_m). Consequently, the plane S_nm is a normal plane (the helical angle thereof: ψ_m0) at the point P_m. On the other hand, because the point of contact P_m and the common normal n_m thereof are located on the plane G_2m inclining by the ξ₂ from the plane of action G₂₀ passing at the P₀, the inclination angle of the n_m expressed by the coordinate system O₂ is given by n_m(φ₂₀+ξ₂, ψ_b20). Because the common normal n_m is located on the line of intersection of the plane S_nm and the G_2m, the helical angle ψ_m0 of the plane S_nm can be expressed as follows by the use of the transformation expression (40) of the inclination angle between the coordinate system C_s and the coordinate system O₂.tan ψ_m0=tan(φ₂₀+ξ₂)sin Γ_s−tan ψ_b20 cos Γ_s/cos(φ₂₀+ξ₂)

When the position of the point P_m0 is designated by P_m0(u_cm0, 0, z_cm0) using the coordinate system C_s, the following expressions (56) can be obtained from the relational expression (34) of the ψ_m0 and the u_cm0.u_cm0=O_mP_m0=E tan ψ_m0 sin(Σ−Γ_s)sin Γ_s/sin Σz_cm0=C_sO_m  (56)

If the point P_m0 is transformed from the coordinate system C_s to the coordinate system O₂ and is expressed by P_m0(u_2m0, −v_cs2, z_2m0), the point P_m0 can be expressed as follows,u_2m0=−u_cm0 cos Γ_s+z_cm0 sin Γ_s v_cs2=E tan Γ_s/{tan(Σ−Γ_s)+tan Γ_s}z_2m0=−u_cm0 sin Γ_s−z_cm0 cos Γ_s−z_2cs z_2c0=−u_c0 sin Γ_s−z_c0 cos Γ_s  (57)where the u_c0 and the z_c0 are the u_c and the z_c coordinate values of a design reference point P₀.

If the z_cm0 is eliminated from the expressions (57), the following expression can be obtained.u_2m0 cos Γ_s+(z_2m0+z_2cs)sin Γ_s=−u_cm0  (58)

The expression (58) indicates the locus P₀P_m0 of the common normal n_m of the point of contact on the plane S_H. Because P_m0 is an intersection point of the locus P₀P_m0 (the aforesaid expression (58)) and the line of intersection H_g2m of the plane of action G_2m and the plane S_H, P_m0 can be expressed as follows by the coordinate system O₂ by the use of ξ₂ as a parameter.u_2m0=R_b20/cos(φ₂₀+ξ₂)−v_cs2 tan(φ₂₀+ξ₂)v_cs2=E tan Γ_s/{tan(Σ−Γ_s)+tan Γ_s}z_2m0=−z_2c0−(u_2m0 cos Γ_s+u_cm0)/sin Γ_s  (59)

If the point P_m0 is expressed by P_m0 (q_2m0, −R_b20, z_2m0) by the use of the coordinate system O_q2, q_2m0 can be expressed as follows.q_2m0=u_2m0 cos χ_2m−vcs2sin χ_2m χ_2m=π/2−φ₂₀−ξ₂=χ₂₀−ξ₂

With these expressions, the common normal n_m can be expressed on the plane of action G_2m by the use of ξ₂ as a parameter as a directed straight line passing at the point P_m0 and having an inclination angle of n_m(φ₂₀+ξ₂, ψ_b20).

16.2 Equations of Line of Contact and Surface of Action

FIG. 19 shows relationships among points Q_mo(P_m0), Q_m(P_m), Q and the point P on the plane of action G₂₀. If the P_m0 and the P_m are expressed by a rotary coordinate system O_r2m, the plane of action G_2m rotates by the phase difference ξ₂ to be superposed on the plane of action G₂₀. The n_m moves to the n, and the P_m0 moves to the Q_m0, and the P_m moves to the Q_m. If the line of intersection of the tooth surface II and the plane of action G₂₀ is designated by w and the intersection point of w and n is designated by Q, the following relationship is concluded between the known points Q_mo(q_2m0, −R_b20, z_2m0) and P(q_2p, −R_b20, z_2p) and an unknown point Q{q₂(θ₂, ξ₂), −R_b20, z₂ (θ₂, ξ₂)} by means of the coordinate system O_q2.z_2m0=−{q₂(θ₂, ξ₂)−q_{2m0} tan ψb20}+{q_2p−q₂(θ₂, ξ₂)}/tan ψ_b20+z_2p

Consequently, the point Q can be expressed as follows by means of the coordinate system O_q2,q₂(θ₂, ξ₂)=(q_2m0 tan ψ_b20+q_2p/tan ψ_b20+z_2p−z_2m0)/(tan ψ_b20+1/tan ψ_b20)z₂(θ₂, ξ₂)=z_2p+{q_2p−q₂(θ₂, ξ₂)}/tan ψ_b20  (60)where q_2p=q_2p0+R_b20θ₂ cos² ψ_b20

z_2p=R_b20θ2 cos ψ_b20 sin ψ_b20.

The point Q_m can be expressed as follows by means of the coordinate system O_q2 by the use of the ξ₂ as a parameter.q_2m(θ₂, ξ₂)=q₂(θ₂, ξ₂)+R_b20ξ₂ cos²ψ_b20 z_2m(θ₂, ξ₂)=z₂(θ₂, ξ₂)+R_b20ξ₂ cos ψ_b20 sin ψ_b20

Consequently, if the point of contact P_m is expressed as P_m(u_2m, v_2m, z_2m) by the coordinate system O₂, each coordinate value is concluded as follows by means of the expressions (55) by the use of the ξ₂ as a parameter.χ_2m=χ₂₀−ξ₂=π/2−φ₂₀−ξ₂ q_2m(θ₂, ξ₂)=q_2m(θ₂, ξ₂)+R_b20ξ₂ cos²ψ_b20 u_2m(θ₂, ξ₂)=q_2m(θ₂, ξ₂)cos χ_2m+R_b20 sin χ_2m v_2m(θ₂, ξ₂)=q_2m(θ₂, ξ₂)sin χ_2m−R_b20 cos χ_2m z_2m(θ₂, ξ₂)=z₂(θ₂, ξ₂)+R_b20ξ₂ cos ψ_b20 sin ψ_b20  (61)

The expressions (61) are the equations of the line of contact (PP_m) at the arbitrary rotation angle θ₂ in the coordinate system O₂ using ξ₂ as a parameter. The parameter z₂₀ of the aforesaid expressions (55) is a function of ξ₂ from the requirement for contact. Consequently, by changing θ₂, the surface of action can be expressed as a set of lines of contact. Furthermore, when the aforesaid expressions (61) are the equations of the common normal n_m (P_m0P_m) using θ₂ at the arbitrary ξ₂ as a parameter, the expressions (61) can express the surface of action as a set of the common normals n_m by changing ξ₂. If an involute helicoid is used as the tooth surface II, the surface of action is a distorted curved surface drawn by the directed straight line (P_m0P_m) of the helical angle ψ_b20 on the plane of action by changing the inclination angle φ₂₀+ξ₂ of the directed straight line with the displacement of the gear II in the axis direction-

17. Equations of Tooth Surface I Generated by Tooth Surface II

FIG. 20 shows the point of contact P_m and the common normal n_m(P_m0P_m) in the coordinate systems O₁ and O_q1. When the point of contact P_m given by the aforesaid expressions (61) is expressed by the coordinate systems O₁, O_q1 to be transformed into the coordinate system O_r1, the transformed point of contact P_m expresses the tooth surface I. Because the point P_m is given as P_m(u_2m, v_2m, z_2m) by the aforesaid expressions (61), if the point P_m is expressed as P_m(u_1m, v_1m, z_1m) on the coordinate system O₁, each coordinate value can be expressed as follows by coordinate transformation expressions of the coordinate systems O₂ and O₁.u_1m=−u_2m cos Σ−(z_2m+z_2c0)sin Σv_1m=v_2m+E z_1m=u_2m sin Σ−(z_2m+z_2c0)cos Σ−z_1co z₁₀=−u_c0 sin(Σ−Γ_s)+z_c0 cos(Σ−Γ_s)

Because the inclination angle of the common normal n_m is given as n_m(φ₂₀+ξ₂, ψ_b20), the n_m(φ_1m, ψ_b1m) can be obtained as follows by means of the aforesaid expressions (41) and (42), which are transformation expressions of the inclination angles between the coordinate systems O₂ and O₁.tan_φ1m=tan(φ₂₀+ξ₂)sin(Σ−π/2)−tan ψ_b20 cos(τ−π/2)/cos(φ₂₀+ξ₂)sin ψ_b1m=cos ψ_b20 sin(φ₂₀+ξ₂)cos(Σ−π/2)+sin ψ_b20 sin(Σ−π/2)

If a plane of action including the common normal n_m is designated by G_1m and the point P_m is expressed as P_m(q_1m, −R_b1m, z_1m) in the coordinate system O_q1, the P_m can be expressed as follows by means of the expression (52), being the transformation expression between the coordinate systems O₁ and O_q1.q_1m=u_1m cos χ_1m+v_1m sin χ_1m R_b1m=u_1m sin χ_1m−v_1m cos χ_1m χ_1m=π/2−φ_1m

If the point P_m is transformed into the coordinate system O_r1, a conjugate tooth surface I can be expressed as follows.θ₁=i₀θ₂ (θ₁=0 when θ₂=0)χ_r1m=π/2−φ_1m−θ₁ u_r1m=q_1m cos φ_r1m+R_b1m sin χ_r1m v_r1m=q_1m sin χ_r1m−R_b1m cos χ_r1m z_r1m=z_1m  (62)18. Group of Pairs of Gears Having Same Involute Helicoid for One Member (Involute Gear Group)

Assuming that the axis of the gear II, the same involute helicoids (the base cylinder radius thereof; R_b20, the helical angle thereof:ψ_b20) as the tooth surface II and the point P₀ (at the radius R₂₀) on the tooth surface II are given, the point P₀ and the normal no thereof can be expressed as follows by means of the coordinate system O₂.

$P_0\left(u_{2p0},v_{2p0},0\right)$ $n_0\left({\phi }_{20},{\psi }_{b20}\right)$ ${\phi }_{20}+{\varepsilon }_{20}={\cos }^{-1}\left(R_{b20}/R_{20}\right)$ ${\varepsilon }_{20}={\tan }^{-1}\left(v_{2p0}/u_{2p0}\right)$ $R_{20}=\sqrt{\left(u_{2p0}^2+v_{2p0}^2\right)}$

Because P₀ is selected on the plane S_H and v_2p0=−v_cs2 in the present embodiment, E can be obtained by giving the shaft angle Σ and the ratio of angular velocity i₀ (or a shaft angle Γ_s of a relative rotation axis), and the relative rotation axis S and the mating gear axis I, i.e. a pair of gears, are determined.

FIG. 21 a conceptual drawing of an involute gear group in the case where the gear II is rotated and the point P₀ and the normal n₀ thereof are selected to be fixed at an appropriate position of the coordinate system O₂ to be a design reference point and a path of contact. Furthermore, in the figure, “S” designates a relative rotation axis of a helical gear and a worm gear (or a crossed helical gear), and “S_b” designates a relative rotation axis of a bevel gear, and “Shy” designates a relative rotation axis of a hypoid gear. The involute gear group changes as follows in accordance with the locations of the point P₀.

• (1) The involute gear group changes according to the values of the Σ when the P₀ is located on the v₂ axis.
• (a) When Σ=0 or π, the involute gear group becomes an external helical gear or an internal helical gear. In the case, Γ_s=0 or π is concluded, and the conjugate mating surface I also becomes an involute helicoid.
• (b) When Σ≢0, the involute gear group becomes a worm gear or a crossed helical gear. A worm gear having an involute helicoid for either a worm or a worm wheel has been put to practical use. Especially, a pair of gears employing an involute helicoid including the tooth profile I in its mating surface I is used as an involute crossed helical gear.
• (2) When the P₀ is located on the u₂ axis (P_0B), the involute gear group becomes a bevel gear. A bevel gear forming an involute helicoid including the tooth profile I on its mating surface also is put to practical use as a conical gear.
• (3) When the P₀ is located at a position other than the positions noted above (P_0H), the involute gear group becomes a hypoid gear and a profile shifted worm gear or a profile shifted crossed helical gear. If the P_0H is selected in a zone in which |εE₂₀| is relatively small (shown in the figure), the involute gear group is meant as a hypoid gear verging on a bevel gear. And if the |ε₂₀| is selected in the vicinity of π/2 (nearby the P₀), the involute gear group is meant as a profile shifted worm gear or a profile shifted crossed helical gear.B. Design of Hypoid Gear having Involute Helicoid as Pinion Tooth Surface

As has been described above, Japanese Patent Laid-Open Publication No. Hei 9-53702 proposes a method for describing a design method of gears uniformly from a gear having parallel two axes such as a spur gear, a helical gear or the like, which is the most popular gear type, to a hyperboloidal gear having two axes not intersecting with each other and not being parallel to each other such as a hypoid gear. However, in the hyperboloidal gear especially, there are often cases where sufficient surface of action cannot be obtained with some combinations of selected variables.

Hereinafter, a selection method of variables for forming effective surfaces of action of a hyperboloidal gear is described.

1. Design Method of Conventional Hyperboloidal Gear

Now, some of methods that have conventionally been used for the design of a hyperboloidal gear are simply described.

(1) Involute Face Gear

An involute face gear is a pair of gears having a pinion being an involute spur gear and a large gear forming a pinion tooth surface and a conjugate tooth surface thereof on a side face of a disk (a plane perpendicular to the axis of the disk). The involute face gear is conventionally well known, and can be designed and manufactured relatively easily to be used as a gear for light loads. Some of the involute face gears use a helical gear in place of the spur gear. However, the use of the helical gear makes the design and the manufacturing of the involute face gear difficult. Consequently, the involute face gear using the helical gear is less popular than that using the spur gear.

(2) Spiroid Gear

A reference pinion cone (or a reference pinion cylinder) is given. A tooth curve being tangent to a relative velocity on a curve (pitch contact locus) being tangent to the body of revolution of a mating gear being tangent to the reference pinion cone is set to be a pinion surface line. A pressure angle within a range from 10° to 30° on a plane including an axis as an empirical value for obtaining a gear effective tooth surface to form a pinion tooth surface, thereby realizing a mating gear. However, the pinion tooth surface is formed as a screw helicoid, unlike the involute hypoid gear of the present invention. If an involute tooth surface is employed in a pinion in the design method, there are cases where an effective tooth surface of a gear cannot be obtained to a gear having a small gear ratio, i.e. having a large-pinion diameter.

(3) Gleason Type Hypoid Gear

A Gleason type hypoid gear uses a conical surface, and both of its pinion and its gear form their teeth in a conical surface state. In the specification determining method of the expression, the helical angle ψ_0p (being different from the helical angle ψ₀ according to the present invention strictly) of its pinion is fixed at about 50°. A gear ratio, an offset, a gear width, all empirically effective nearby the fixed helical angle ψ_0p, are given as standards. Thereby, specifications are generated such that an almost constant asymmetric pressure angle (e.g. 14°-24°, or 10°-28°) may be effective. That is a method, so to speak, for determining a gear shape geometrically analogous to a reference gear shape. Accordingly, when designing a hypoid gear not conforming to the standard recommended by the Gleason method (for example, a face gear having a high offset and a small helical angle), because there are no empirical values, it is first necessary to establish a new standard.

2. Hypoid Gear being Object

When a static space is given by means of the shaft angle Σ and the offset E and a field of a relative velocity is given by means of the gear ratio i₀ according to the method disclosed in the noted Japanese Laid-Open Patent Publication, involute helicoidal tooth surfaces D and C can be determined when the design reference point P₀ (R₂₀, ψ₀) and two tooth surface normals g_0D(ψ₀, φ_n0D; C_s) and g_0C(ψ₀, φ_n0C; C_s) passing at the point P₀ are given. Hereupon, the tooth surfaces D and C are a drive side tooth surface and a coast side tooth surface of a pair of gears, and the g_0D and the g_0C are normals of respective tooth surfaces, i.e. paths of contact. Although the shaft angle Σ, the offset E, the gear ratio i₀, the radius R₂₀ or R₁₀ of a design reference point are given in the aforesaid design method of a face gear, relationships among a contact state of a tooth surface and three variables of ψ₀, φ_n0D and φ_n0C are not made to be clear. Consequently, the selection cannot be executed, and there are cases wherein an effective tooth surface cannot be obtained. If a case of shaft angle Σ=90° is exemplified, in at least one of the cases where the offset E is large (E/R₂₀>0.25), where the gear ratio is small (i₀=2.5-5), and where the helical angle ψ₀ is within a range of ψ₀=35°-70°, the top of the large end of the face width became sharpened and the undercut at the small end was formed improperly and no efficient tooth surfaces D and C can be formed.

In the present embodiment, as will be described in the following, a surface of action of a pair of gears a tooth surface of one of which is an involute helicoid is obtained. Using the obtained surface of action, a selection method of three variables of ψ₀, φ_n0D and φ_n0C the effective tooth surfaces of which exist in a surface of action given by a pinion and a gear, and the specifications of teeth having no sharpened top or undercut by means of an equivalent rack, which will be described later, are determined.

FIG. 22 and the following show size specifications of a hypoid gear.

shaft angle Σ                90°
gear ratio i0                4.1
instantaneous axis angle Γs  76.29°
offset Σ                     35 mm under the center
positions of axes I and II to instantaneous axis
vcs1                         −1.965 mm
vcs2                         33.035 mm
large end radius of gear R2h 95 mm
small end radius of gear R2t 67 mm

The coordinate systems C_s, C₁ and C₂ are determined based on the aforesaid specifications. The gear I is supposed to be a pinion, and the gear II is supposed to be a gear. In the following is described the process of determining an involute helicoid surface of a pinion for obtaining the effective gear tooth surfaces D and C in a zone enclosed by a given large end radius and a given small end radius of a gear on a disk in the case where the pinion is formed to be a cylinder shape and the involute helicoid is given to the pinion.

3. Equivalent Rack

In this paragraph is noted a rack (equivalent rack) moving on a plane formed by two paths of contact when the paths of contact g_0D and g_0C of the tooth surfaces D and C on the drive side and the coast side are given as the two directed straight lines intersecting at the design reference point. By use of the rack, teeth effective as the teeth of a gear can be formed in the vicinity of the design reference point. The descriptions concerning the equivalent rack in this paragraph can be applied not only to the hypoid gear but also to gears in the other expressions.

3.1 Path of Contact g₀, φ_n0D, φ_n0C

It is supposed that a path of contact to be an object is given as follows in accordance with the aforesaid Japanese Laid-Open Patent Publication.

• (1) Two axes I, II, their shaft angle Σ, an offset E (≧0) and a ratio of angular velocity (gear ratio) i₀ (≧1, constant) are given, and coordinate systems C₁, C₂ are defined by the use of the two axes and the common perpendicular, and a coordinate system C_s is defined by the use of a relative rotation axis S and the common perpendicular. Thereby, it is possible to transform coordinate values and inclination angles of directed straight lines between the coordinate systems with each other.
• (2) A path of contact g₀ having no fluctuations of a bearing load is given on the coordinate system C_s by a design reference point P₀(u_C0, v_C0, z_C0; C_S) and the inclination angle g₀(ψ₀, φ_n0; C_s) thereof, and coordinate systems C_q1, C_q2 are defined by the use of planes of action G₁₀, G₂₀ including the g₀.
• (3) If the intersection points of planes of rotation of the two axes I and II passing the design reference point P₀ with each gear axis are designated by O₁, O₂, the coordinate systems C₁, C_q1, C₂, C_q2 are moved in each gear axis direction in parallel until their origins become O₁, O₂, and thereby coordinate systems O₁, O_q1, O₂, O_q2 are defined. Consequently, arbitrary points P(q₂, −R_b2, z₂; O_q2) and P(u₂, v₂, z₂; O₂) on the g₀ by the coordinate systems O_q2, O₂ can be expressed as follows by means of the expressions (49),q₂(θ₂)=R_b20θ₂ cos²ψ_b20+q_2p0 R_b2(θ₂)=R_b20 z₂(θ₂)=R_b20θ₂ cos ψ_b20 sin ψ_b20 χ₂(θ₂)=χ₂₀=π/2−φ₂₀ u₂(θ₂)=q₂(θ₂)cos χ₂₀+R_b20 sin χ₂₀ v₂(θ₂)=q₂(θ₂)sin χ₂₀−R_b20 cos χ₂₀  (63)where θ₂: rotation angle of gear II

P(q₂, −R_b2, z₂; O_q2): the expression of the point P in the coordinate system C_q2

g₀(φ₂₀, ψ_b20; O₂): the expression of the inclination angle of g₀ in the coordinate system O₂.

• (4) If the point P and the inclination angles of the g₀ are transformed into the coordinate systems O₁ and O_q1, they can be expressed as follows.P{q₁(θ₁), −R_b10(θ₁), z₁(θ₁); O_q1}g₀(φ₁₀, ψ_b10; O₁)  (64)

Incidentally, θ₁=i₀θ₂.

• (5) When it can be assumed that the paths of contact on the drive side and the coast side intersect with each other at the point P₀ and further are given as two directed straight lines that do not generate any undercut and interference in the vicinity of the point P₀, as described above, the expressions of the paths of contact on the drive side and the coast side by the coordinate system C_s can be respectively designated by g_0D(ψ₀, φ_n0D; C_s) on the drive side and g_0C(ψ₀, φ_n0C; C_s) on the coast side.3.2 Definition of Limiting Path g_t (Case Where Plane S_n Does not Include Common Perpendicular)

FIG. 23 conceptually shows relationships among planes S_H, S_p and S_n of a hypoid gear and a plane S_t formed by velocities V₁₀, V₂₀ at the point P₀. Hereupon, the plane S_H is a V_c=0 plane in the coordinate system C_s, and the plane S_p is a u_c=u_c0 plane, and the plane S_n is a plane perpendicular to the relative velocity V_rs0 at the P₀.

Because the design reference point P₀ is located on the plane S_H, the relative velocity V_rs0 is located on the plane S_p. On the other hand, because the plane S_t also includes V_rs0, the plane S_t and the plane S_p intersect with each other with the relative velocity V_rs0 as a line of intersection. Furthermore, the plane S_t and the plane S_n cross with each other at right angles, and have a normal velocity V_gt0 on the plane S_t as the line of intersection g_t (positive in the direction of the V_gt0). That is, the plane S_t is a plane formed by the rotation of the plane S_p around V_rs0 as an axis on the plane S_n by φ_nt, and corresponds to the conventional pitch plane.

If the intersection points of the plane S_n with the gear axes I, II are designated by O_1n, O_2n, peripheral velocities V₁₀, V₂₀ of the point P₀ are expressed as follows.V₁₀=ω₁₀×[O_1nP₀]V₂₀=ω₂₀×[O_2nP₀]  (65)

Here, [AB] indicates a vector having a point A as its starting point and a point B as its end point. Because O_1nP₀ is located on the plane S_n, the O_1nP₀ is perpendicular to the relative velocity V_rs0, and is perpendicular to the V₁₀ owing to the aforesaid expression. Consequently, the O_1nP₀ is perpendicular to the plane S_t at the point P₀. Quite similarly, because O_2nP₀ is perpendicular to the V_rs0 and the V₂₀, the O_2nP₀ is perpendicular to plane S_t at the point P₀. In other words, the points O_1n, P₀ and O_2n are located on a straight line. Accordingly, the straight line is set to be a design criterion perpendicular C_n (positive in the direction from the O_1n to the O_2n). The C_n is the line of centres of a pair of gears passing at the point P₀. The relationship does not depend on the position of the point P₀.

Because an arbitrary plane including the relative velocity V_rso can be the tangential plane of a tooth surface passing at the point P₀, a tooth surface having a tangential plane W_N (perpendicular to the plane S_t) including the design criterion perpendicular C_n has the g_t as its path of contact (contact normal). Because, in an ordinary gear, the tangential plane of a tooth surface passing the point P₀ is appropriately inclined to the plane W_N formed by the V_rso and the C_n, the path of contact g₀ (contact normal) thereof is inclined on the plane S_n on the basis of the g_t. Accordingly, if g_t is a limiting path g_t, the inclination angle g_t(ψ₀, φ_nt; C_s) of the limiting path g_t can be obtained as follows.

FIG. 24 draws the design criterion perpendicular C_n on the plane S_n and the limiting path g_t perpendicular to the C_n. If the feet of perpendicular lines drawn from the points O_1n, O_2n to the plane S_p (perpendicular to the plane S_n) are designated by O_1np, O_2np, the φ_nt can be obtained as follows.

$\begin{array}{cc}\begin{array}{c}\tan {\phi }_{n1}=P_0{O}_{2\mathrm{np}}/O_{2\mathrm{np}}{O}_{2n}=O_{1\mathrm{np}}{P}_0/O_{1n}{O}_{1\mathrm{np}}\\ =v_{\mathrm{cs}2}/\left[\cos {\phi }_0\left\{\left(z_{\mathrm{c0}}+v_{\mathrm{cs}2}\tan {\psi }_0\right)\tan {\Gamma }_s-u_{s0}\right\}\right]\\ =-v_{\mathrm{cs}1}/\left[\cos {\phi }_0\left\{\left(z_{\mathrm{c0}}+v_{\mathrm{cs}1}\tan {\psi }_0\right)\tan \left(\Sigma -{\Gamma }_s\right)+u_{s0}\right\}\right]\end{array}& \left(66\right)\end{array}$

Here, each directed line segment has its positive direction being the positive direction of the each axis of the coordinate system C_s.

In a hypoid gear, v_cs2, v_cs1, u_c0, z_c0 can be expressed as follows by means of the coordinate systems O₁, O₂.v_cs2=E tan Γ_s/{tan Γ_s+tan(Σ−Γ_s)}u_c0=E sin(Σ−Γ_s)sin Γ_s tan ψ₀/sin Σz_c0=(u_2p0+u_c0 cos Γ_s)/sin Γ_s u_2p0=−v_cs2/tan ε₂₀ (ε₂₀≠0)v_cs1=−E tan(Σ−Γ_s)/{tan Γ_s+tan(Σ−Γ_s)}z_c0={u_1p0−u_c0 cos(Σ−Γ_s)}/sin(Σ−Γ_s)u_1p0=−v_cs1/tan₀(ε₁₀≠0)

If the u_c0, the z_c0, the v_cs1 and the v_cs2 are eliminated from the expressions (66) by the use of the above expressions and the eliminated expressions (66) is arranged, the changed expressions (66) become as follows.

$\begin{array}{c}\tan {\phi }_{\mathrm{nt}}=\cos {\Gamma }_s/\left(\cos {\psi }_0/\tan {\varepsilon }_{20}\sin {\Gamma }_s\sin {\psi }_0\right)\\ =\cos \left(\Sigma -{\Gamma }_s\right)/\left\{\cos {\psi }_0/\tan {\varepsilon }_{10}-\sin \left(\Sigma -{\Gamma }_s\right)\sin {\psi }_0\right\}\end{array}$

The limiting path g_t inclines by φ_nt to the plane S_p on the plane S_n. The φ_nt has its positive direction in the clockwise direction when it is viewed to the positive direction of the z_C axis.

3.3 Definition of Equivalent Rack

FIG. 25 shows an equivalent rack on the plane S_n shown from the positive direction of the relative velocity V_rs0. The following are shown: the peripheral velocities V₁₀, V₂₀ at the point P0, the relative velocity V_rs0 (=V_s10−V_s20), the normal velocity V_gt0 (in the direction of the limiting path g_t), the path of contact g_0D, g_0C on the plane S_n, and the tangential planes W_D, W_C (shown as lines of intersection W_sD, W_sC with the plane S_n in FIG. 25) of the tooth surfaces D, C having the g_0D, g_0C.

The peripheral velocities V₁₀, V₂₀ can be expressed as follows on the plane S_t.V₁₀=V_gt0+V_s10 V₂₀=V_gt0+V_s20

Because the tangential plane W_D has the relative velocity V_rs0 in common together with the plane S_t, the peripheral velocities V₁₀, V₂₀ can be expressed as follows,V₁₀=(V_g0D+V_WsD)+V_s10 V₂₀=(V_g0D+V_WsD)+V_s20 where

V_g0D: the normal velocity (in the g_0D direction) of tangential plane W_D

V_WsD: the velocity in the W_sD direction on the tangential plane W_D.

Consequently, the following relationships are always effective at the point P₀.V_gt0=V_g0D+V_WsD

The tangential plane W_C can also be expressed as follows quite similarly,V_gt0=V_g0C+V_WsC where

V_g0c: the normal velocity (in the g_0C direction) of the tangential plane W_C

V_WsC: the velocity of the W_sC direction of the tangential plane W_C.

Consequently, the normal velocities V_g0D, V_g0C can be obtained as follows as the g_0D, g_0C direction components of the V_gt0.V_g0D=V_gt0 cos(φ_{n0D −φnt})V_g0C=V_gt0 cos(φ_nt−φ_n0C)  (67)

On the other hand, the V_gt0, the V_g0D and the V_g0C can be expressed as follows,V_gt0=R_b2qt(dθ₂/dt)cos ψ_b2gt V_g0D=R_b20D(dθ₂/dt)cos ψ_b20D V_g0C=R_b20C(dθ₂/dt)cos ψ_b20C where

R_b2gt, R_b20D, R_b20C: the radii of the base cylinder of the gear II (large gear) of the g_t, the g_0D and the g_0C

ψ_b2gt, ψ_b20D, ψ_b20C: the inclination angles of the g_t, the g_0D and the g_0C on the plane of action of the gear II (large gear).

Because the g_t, the g_0D and the g_0C are straight lines fixed in static space, the normal velocities V_gt0, V_g0D, V_g0C are always constant. Consequently, the normal velocities V_g0D, V_g0C of the arbitrary points P_D, P_C on the g_0D and the g_0C can always be expressed by the expressions (67).

This fact means that the points of contact on the g_0D, g_0C owing to the rotation of a gear are expressed by the points of contact of a rack having the g_t as its reference line and the same paths of contact g_0D, g_0C (having the W_sD and the W_sC as its tooth profiles) and moving at V_gt0 in the direction of the g_t. If the rack is defined as an equivalent rack, the equivalent rack is a generalized rack of an involute spur gear. The problems of contact of all gears (from cylindrical gears to a hypoid gear) having paths of contact given to satisfy the conditions of having no fluctuations of a bearing load can be treated as the problem of the contact of the equivalent rack.

3.4 Specifications of Equivalent Rack

(1) Inclination Angles (Pressure Angles) of W_sD, W_sC to C_n

The W_sD and the W_sC are inclined by (φ_n0D−φ_nt) and (φ_nt−φ_n0C) to the C_n (perpendicular to the g_t), respectively. φ_n0D=φ_n0C=φ_nt indicates that the pressure angle of an equivalent rack is zero.

(2) Pitch p_gt

The limiting path g_t indicates the reference line of an equivalent rack, the reference pitch p_gt and the normal pitches p_n0D, p_n0c can be expressed as follows.p_gt=2πR_b2gt cos ψ_b2gt/N₂ (in the direction of the g_t)p_g0D=P_gt cos(φ_n0D−φ_nt)=2πR_b20D cos ψ_b20D/N₂ (in the direction of the g_0D)p_g0c=p_gt cos(φ_nt−φ_n0C)=2πR_b20C cos ψ_b20C/N₂ (in the direction of the g_0C)  (68)

Incidentally, N₂ is the number of teeth of the gear II.

(3) Working Depth h_k

In FIG. 25, if a position distant from the W_sD by a pitch (1 P_g0D) is designated by w_sDA and the intersection point of the W_sC with the W_sD and the W_sDA are designated by R_CD and R_CDA, a critical tooth depth h_cr (R_CDR_CDH), at which the top land of the equivalent rack is zero, can be expressed as follows with attention to the fact that the R_CDR_CDH crosses with the g_t at right angles.H_cr=R_CDR_CDH=p_g0D cos(φ_nt−φ_n0C)/sin(φ_n0D−φ_nt)

If the cutter top land on the equivalent rack is designated by t_cn and the clearance is designated by C_r, the working depth h_k (in the direction of the C_n) of the equivalent rack can be expressed as follows.h_k=h_cr−2t_cn/{tan(φ_n0D−φ_nt)+tan(φ_nt−φ_n0C)}−2C_r  (69)(4) Phase Angle of W_sC to Design Reference Point P₀ (W_sD)

In FIG. 25, Q_1n, Q_2n are set in the vicinity of the point P₀ on the C_n such that h_k=Q_1nQ_2n, and addendums A_d2, A_d1 are defined as follows.

P₀Q_2n=A_d2 (the addendum of the gear II)

P₀Q_1n=A_d1=h_k−A_d2 (the addendum of the gear I)

It should be noted that it is here assumed that the point Q_2n is selected in order that both of the paths of contact g_0D, g_0C may be included in an effective zone and the A_d2≧0 when the Q_2n is located on the O_1n side to the point P₀.

If the intersection point of the g_0C with the W_sC is designated by P_C, P₀P_C can be obtained as follows.P₀P_C=−{A_d2+(h_cr−h_k)/2} sin(φ_n0D−φ_n0C)/cos(φ_n0D−φ_nt)

Incidentally, the positive direction of the P₀P_C is the direction of g_0C.

Because the rotation angle θ₂ of the point P₀ is zero, the phase angle θ_2wsC of the point P_C becomes as follows,θ_2wsC=(P₀P_C/P_g0C)(2θ_2p)  (70)where the 2θ_2p is the angular pitch of the gear II. The W_sC is located at a position delayed by θ_2wsC to the W_sD. Thereby, the position of the W_sC to the point P₀ (W_sD) has been determined.

Because the phase angle of the W_sC to the W_sD is determined by the generalization of the concept of a tooth thickness in the conventional gear design (how to determine the tooth thickness of a rack on the g_t), the phase angle is determined by giving a working depth and an addendum in the present embodiment.

4. Action Limit Point

A tooth profile corresponding to an arbitrarily given path of contact exists mathematically. However, only one tooth profile can actually exist on one radius arc around a gear axis at one time. Consequently, a tooth profile continuing over both the sides of a contact point of a cylinder having the gear axis as its axis with a path of contact does not exist actually. Therefore, the contact point is the action limit point of the path of contact. Furthermore, this fact indicates that the action limit point is the foot of a perpendicular line drawn from the gear axis to the path of contact, i.e. the orthogonal projection of the gear axis.

If an intersection point of a path of contact with a cylinder (radius: R₂) having the gear axis as its axis is designated by P, the radius R₂ can be expressed as follows.R₂²=q₂²+R_b2²

If the point of contact P is a action limit point, the path of contact and the cylinder are tangent at the point P. Consequently, the following expression holds true.R₂(dR₂/dθ₂)=q₂(dq₂/dθ₂)+R_b2(dR_2b/dθ₂)=0

If the (dq₂/dθ₂) is eliminated by means of the expression (7), the result becomes as follows.q₂(1−dχ₂/dθ₂)/(tan ψ_b2 tan η_b2+1)+dR_b2/dθ₂=0

Hereupon, because the g_0D and the g_0C are supposed to be a straight line coinciding with a normal, dχ₂/dθ₂=0, dR_2b/dθ₂=0. The expression can then be simplified to q₂=0.

If the expression is solved for θ₂, an action limit point P_2k concerning the gear II can be obtained. An action limit point P_1k concerning the gear I can similarly be obtained by solving the equation q₁=0 after simplifying the following expression.q₁(1−dχ₁/dθ₁)/(tan ψ_b1 tan η_b1+1)+dR_b1/dθ₁=05. Selection of Design Reference Point P₀ and Inclination Angle ψ₀ of Plane S_n in Hypoid Gear

For a pair of gears having parallel gear axes, the shape of a surface of action is relatively simple, and there is no case where it becomes impossible to form any tooth surface according to the setting way of a design reference point P₀ as long as the design reference point P₀ is located within an ordinary range. Furthermore, even if no tooth surface can be formed by a given design reference point P₀, amendment of the design reference point P₀ remains relatively easy.

Because the surface of action of a hypoid gear is very complicated, as will be described later, it is difficult to determine how to alter the surface of action to form an effective tooth surface. Hereinafter, a method for designing a hypoid gear effectively, i.e. the selection method of specifications, is described.

FIG. 26 shows relationships among limiting paths g_2z, g_t, paths of contact g_0D, g_0C and their equivalent rack on the plane S_n. Hereupon, the limiting path g_2z is a line of intersection of the plane S_n with a right side plane Z₂₀ immediately below the gear axis, and the limiting path g_t is a line of intersection of the plane S_n with a plane S_t formed by the line velocities of the point P₀. The selection of the design reference point P₀ is the selection of a position in a static space where the shape of the equivalent rack is given. In the present embodiment, it is supposed that a pinion has a cylindrical shape and the shape of the teeth of the pinion is constant (only the phase angles thereof change) in the direction of the axis thereof. The shape of teeth of a gear changes from the small end thereof to the large end thereof. Then, the design reference point P₀ is selected at the center of the face width of the gear. That is, the radius R₂₀ of the design reference point P₀ to the gear axis becomes as follows.R₂₀=(R_2h+R_2t)/2  (71)

For forming an effective tooth surface with a given small end and a given large end of a large gear, there is a case where it is necessary to amend the shape of an equivalent rack or the position of the design reference point P₀. Consequently, the expression (71) can be considered to give a first rank approximation of the R₂₀.

Each ψ₀ being inclinations of the plane S_n perpendicular to the relative velocity at the design reference point P₀ is selected as follows. Because the line of intersection of the plane S_n with the plane of rotation Z₂₀ of the gear axis passing the point P₀ is the limiting path g_2z, the inclination angles g_2z(ψ₀, φ_n2z; C_s) and g_2z(φ_2z, 0; C₂) of the limiting path g_2z can be obtained from the following expressions.tan φ_n2z=sin ψ₀/tan Γ_s tan φ_2z=tan 104₀/sin Γ_s  (72)

Because the face and root surface of a large gear are formed as planes of rotation of gear in the present embodiment, the tangential planes of tooth surface of a large gear should be inclined mutually in the reverse directions to the plane of rotation of the large gear to each other in order that a tooth of the large gear may have an ordinary shape of a trapezoid. Consequently arbitrary paths of contact g_0D and g_0C should be located in the vicinity of the limiting path g_2z and should be inclined in the mutually reverse directions to the g_2z. Because the active limit radii (base circle radii) R_b20D, R_b20C of the paths of contact g_0D, g_0C on the gear side are near to the base cylinder radius R_b2z of the limiting path g_2z, the tooth surface of the gear should approximately satisfy the following relationships in order that the tooth surface may be effective at a radius equal to the small end radius R_2t of the gear or more.R_2t≧R_b2z=R₂₀ cos(φ_2z+ε₂₀)sin ε₂₀=−v_cs2/R₂₀  (73)

• • Incidentally, ε₂₀=0 in case of a bevel gear.

From the expressions (72), (73), the ψ₀ can be obtained. Because, if i₀ is large, φ_2z≈ψ₀ from the expressions (72) and the expressions (73) maybe replaced with the following expression.R_2t≧R₂₀ cos(φ_2z+ε₂₀)  (74)

From the R₂₀ and the ψ₀, the design reference point P₀ and the limiting paths g_2z, g_t are determined on the plane S_H by the coordinate system C_s as follows.

$P_0\left(u_{c0},0,z_{c0};C_s\right)$ $g_{2z}\left({\psi }_0,{\phi }_{n2z};C_s\right)$ $g_t\left({\psi }_0,{\phi }_{\mathrm{nt}};C_s\right)$ $u_{c0}=E\sin {\Gamma }_s\cos {\Gamma }_s\tan {\psi }_0$ $z_{c0}=\left\{\sqrt{\left(R_{20}^2-v_{\mathrm{cs}2}^2\right)}+u_{c0}\cos {\Gamma }_s\right\}/\sin {\Gamma }_s$ $\tan {\phi }_{n1}=\cos {\Gamma }_s/\left(-\cos {\psi }_0/\tan {\varepsilon }_{20}+\sin {\Gamma }_s\sin {\psi }_0\right)$

The R₂₀ and the ψ₀ determined as described above should be regarded as first rank approximates, and there are cases where the R₂₀ and the ψ₀ are adjusted according to the state of the tooth surface obtained as a result of the method described above. Furthermore, if needed values of an offset and a face width of a large gear are too large, there are cases wherein suitable R₂₀ and ψ₀ giving a satisfactory tooth surface do not exist.

If the coordinate systems O₁, O_q1, O₂, O_q2 are fixed, the design reference point P₀ and the inclination angles of the limiting paths g_2z, g_t can be expressed in each coordinate system.

6. Paths of Contact g_0D, g_0C

6.1 Domain of φ_n0D, φ_n0C on Plane S_n

It is preferable that the tangential planes W_sD and W_sC of a tooth surface of a gear are inclined to the plane of rotation of gear Z₂₀ in the mutual reverse directions in order that the teeth of the gear may have a necessary strength. Consequently, the paths of contact g_0D, g_0C should be selected to be inclined to the limiting path g_2z in the mutual reverse directions. That is, the inclinations of the paths of contact g_0D, g_0C are selected to satisfy the following expression.φ_n0C≦φ_n2z≦φ_n0D  (75)

Moreover, if it is supposed that the paths of contact g_0D, g_0C form an equivalent rack having a vertex angle of 38° on the plane S_n, the following expression is concluded.φ_n0D−φ_n0C=38°  (76)

The combinations of the φ_n0D and the φ_n0C can be expressed by the following three ways or nearby cases from the expressions (75) and (76).A. φ_n0C=φ_n2z, φ_n0D=φ_n2z+38°B. φ_n2z=φ_n0D, φ_n0C=φ_n2z−38°C. φ_n0C=φ_n2z−19°φ_n0D=φ_n2z+19°  (77)6.2 Surface of Action and Action Limit Curve of Involute Helicoid

FIGS. 27-30 show surfaces of action in a case where a pinion is given an involute helicoid (the base cylinder radius thereof: R_b12z, the plane of action helical angle thereof: ψ_b12z) the tooth surface normal of which is the limiting path g_2z. FIG. 27 is a sketch map for making the whole shape of a curved surface to be easy to understand. The expression of a surface of action is quite similar to that in the case where an involute helicoid is given to a large gear, the expression can be obtained by replacing the suffix 2 in the expressions (61) with 1.

A surface of action is expressed by paths of contact and lines of contact almost perpendicular to the paths of contact, and is composed of a curved surface (surface of action C) drawn by the movement of the path of contact from the g_2z (φ_12z=0) toward the z₁ (>0) direction while rotating in the φ₁ (>0) direction, and a curved surface (surface of action D) drawn by the movement of the path of contact toward the z₁ (>0) direction while rotating in the φ₁ (<0) direction. Only a tooth surface normal that satisfies the requirement for contact among the tooth surface normals of the involute helicoid becomes a contact normal. A tooth surface normal can be a contact normal at two positions of the both sides of the contact point to the base cylinder. Consequently, the curved surfaces shown in FIGS. 28-30 are drawn.

Loci of action limit curve (action limit point) of a pinion and a large gear of paths of contact are designated by L_1A (on a pinion base cylinder), L_2AD and L_2AC. Furthermore, orthogonal projections (action limit point on the gear axis side) to the surfaces of action of the large gear axis are designated by L_3AD and L_3AC which are the loci of the contact point of a cylinder having the large gear axis as its axis with an intersection line of the surface of action with a plane of rotation Z₂. Because the surface of action is determined by the involute helicoid given to the pinion side in the present embodiment, the orthogonal projection to the surface of action of the pinion axis (the action limit curve on the pinion side) is the L_1A. In cylindrical gears, the surface of action becomes a plane, such that consequently the orthogonal projection of the surface of action of a pinion axis and a large gear axis become a simple straight line. However, because the surfaces of action of hypoid gears are complicated curved surfaces as shown in the figures, the orthogonal projections of a pinion axis and a large gear axis do not become a straight line. And there are a plurality of the orthogonal projections for each the axes. Moreover, there is also a case where the orthogonal projections generate ramifications. A zone enclosed by a action limit curve nearest to the design reference point P₀ is a substantially usable tooth surface.

Moreover, the face surface of the gear is designated by Z_2h (=0) (the plane of rotation of the gear including g_2z). The large end of the large gear and the line of intersection of the small end cylinder with the surface of action are designated by R_2h, R_2t, respectively.

Because a surface of action including the limiting path g_2z and enclosed by the L_3AD and the L_3AC is limited to a narrow zone near to the P₀, there is no tooth surface that can substantially be used. Accordingly, an effective surface of action enclosed by the action limit curve, the face surface of the large gear, and large end and small end cylinders are as described in the following.

EFFECTIVE SURFACE OF ACTION C_eff: a zone (convexo-concave contact) enclosed by the action limit curve L_3AC on the surface of action C and the boundary lines of the gear Z_2h (=0) and R_2h.

EFFECTIVE SURFACE OF ACTION D_eff: a zone (convexo-convex contact) enclosed by boundary lines of the gear z_2h (=0), R_2h, R_2t on the surface of action D.

6.3 Selection of Paths of Contact g_0D, g_0C

(1) In Case of Expression (77)A

The case of the expression (77)A is one wherein the path of contact g_0C is taken as the g_2z, and, in the case the effective surface of action C_eff, is given by FIGS. 28-30. Because the boundary of the effective surface of action C_eff on the small end side of the large gear is determined by the action limit curve L_3AC, there is no tooth surface of the large gear on the small end side of the large gear from the L_3AC. Consequently, it is necessary to set the zones (R_2t-R_2h) of the gear to the larger end side in accordance with the effective surface of action C_eff again for realizing the tooth surface C as it is.

(2) In Case of Expression (77)B

The case of the expression (77)B is one wherein the path of contact g_0D is taken as the g_2z, and, in the case the effective surface of action D_eff, is also given by FIGS. 28-30. Because the lines of intersection z_2h (=0), R_2t, R_2h of the boundary surface of the large gear with the surface of action are located in the inner from the action limit curves L_1A, L_3AD, L_2AD, the combination of the expression (77)B can realize an effective tooth surface D in the inner of the zone (R_2t-R_2h) of the given large gear.

FIGS. 31-33 shows the effective surface of action C_eff of the tooth surface C (φ_n0C=φ_n2z−38°) at this time. Because the base cylinder radius R_b10C of the g_0C becomes small, the L_3AC moves to the inner of the large gear, and it is known that the L_3AC is pretty improved in comparison with the C_eff shown in FIGS. 28-30 when they are compared at the position of the point P₀. Consequently, it is shown that the tooth surface C can almost be realized in the zone of the large gear (R_2t-R_2h) by slightly altering g_0C.

(3) In Case of Expression (77)C

For ensuring the effective surface of action C_eff (convexo-concave contact) in the vicinity of the design reference point P₀, as described above, it is necessary to incline g_0C from g_2z as large as possible to make the radius of the base cylinder of a pinion small for locating the L_3AC on the small end side of the large gear (in the inner thereof if possible). On the other hand, to make the shape of the base cylinder small by inclining g_0D from g_2z by as much as possible results only in a decrease of the contact ratio, which is of little significance. In particular, if the tooth surface D is used on the drive side as in a hypoid gear for an automobile, it is rather advantageous to bring g_0D as close as possible to g_2z. For making both of the tooth surface D and the tooth surface C effective in the given large gear zone (R_2t-R_2h), the selection near to the expression (77)B (R_b10D>R_b10C) is advantageous in almost all cases.

In the pair of gears having an involute helicoid as the tooth surface of a pinion described above, it is necessary that the action limit curve (L_3AC in this case) on the convexo-concave contact side is brought to the inner from the small end of the large gear, which is a cause of employing unsymmetrical pressure angles (different base cylinders).

On the basis of the examination mentioned above, each of the inclination angles of the paths of contact g_{0D , g0C} is determined as follows.g_0D(ψ₀, φ_n0D=φ_n2z; C_s)g_0C(ψ₀, φ_n0C=φ_n2z−38°; C_s)  (78)

Here, it is practical to set the φ_n0D larger than the φ_2z a little for giving an allowance (Δφ_n).

7. Boundary Surfaces of Equivalent Rack and a Pair of Gears

7.1 Specifications of Equivalent Rack

FIG. 26 shows the shape of an equivalent rack on the plane S_n. If a design reference point P₀, a reference line (limiting path) g_t of the equivalent rack and paths of contact g_0D, g_0C are given, the specifications and a position of the equivalent rack to the design reference point P₀ can be obtained as follows.

(1) Normal Pitches p_g0D, p_g0C p_g0D=2πR_b10D cos ψ_b10D/N₁ (in the direction of g_0D)p_g0C=2πR_b10C cos ψ_b10C/N₁ (in the direction of g_0C)  (79)where

N₁: the number of teeth of the gear I.

(2) Working Depth h_k h_k=p_g0D cos(φ_nt−φ_n0C)/sin(φ_n0D−φ_n0C)−2t_cn/{tan(φ_n0D−φ_nt)+tan(φ_nt−φ_n0C)}  (80)where

t_cn: the cutter top land on the equivalent rack

c_r: clearance.

(3) Addendum A_d2 of Large GearP₀Q_2nA_d2=(u_1p0−R_b10D)sin(φ_n0D−φ_nt)/cos φ_10D/cos ψ_b10D P₀Q_1n=A_d1=h_k−A_d2  (81)(4) Phase Angle θ_2wsC of W_sC to Point P₀ (W_sD)θ_2wsC=−2θ_2p{A_d2+(h_cr−h_k)/2} sin(φ_n0D−φ_n0C)/cos(φ_n0D−φ_nt)/p_g0C  (82)where

2θ_2p: the angular pitch of the large gear.

7.2 Face Surface of Large Gear

Because the paths of contact g_0D, g_0C mutually incline in opposite directions to each other to the plane of rotation of large gear, it is advantageous for the face and root surfaces of a large gear to be planes of rotation of the large gear rather than to be a conical surface for realizing both of them reasonably. Accordingly, the plane of rotation of the gear passing the point Q_2n is supposed to be the face surface of gear as follows,face surface of gear z_2h=z_2Q2n  (83)where Q_2n (u_2Q2n, v_2Q2n, z_2Q2n; O₂).7.3 Pinion Face Cylinder

If a pinion face surface is supposed to be a cylinder passing the point Q_1n in accordance with the large gear face surface, the pinion face cylinder radius can be expressed as follows,R_1Q1n=√{square root over ((u_1Q1n²+v_1Q1n²))}  (84)where Q_1Q(u_1Q1n, v_1Q1n, z_1Q1n; O₂).7.4 Inner and Outer Ends of Pinion

The outer and the inner ends of a pinion are supposed to be planes of rotation of the pinion passing intersection points of a large end cylinder and a small end cylinder of the large gear with the axis of the pinion. Consequently, the outer and the inner ends of the pinion can be expressed as follows in the coordinate system O₁,pinion outer end z_1h=√{square root over ((R_2h²−E²))}−z_1c0 pinion inner end z_1t=√{square root over ((R_2t²−E⁷))}−z_1c0  (85)where

z_1c0: a transformation constant from the coordinate system C₁ to the O₁.

8. Modification of Pinion Involute Helicoid

The pinion involute helicoid determined as above has the following practical disadvantages in the case where the tooth surfaces D, C severally have leads different from each other. In the case where the face surface of pinion is a cylinder, for example, the pinion top land may not be constant, and it may be necessary to determine the location of the pinion in the axial direction and to manufacture tooth surfaces separately, and so forth. Accordingly, in the present embodiment, the pinion involute helicoid is somewhat modified as follows for making the leads of the tooth surfaces D and C equal. Various methods for making the leads of the tooth surfaces D and C equal can be considered. Hereupon, it is supposed that the tooth surface D is left to be the given original form, and that tooth surface C is changed to be a tooth surface C_c by the adjustment of only its helical angle ψ_b10C (with base cylinder radius R_b10C being left as it is).

(1) Helical Angle ψ_b10CC of Tooth Surface C_c

Because the lead of the tooth surface C_c is the same as that of the tooth surface D, the helical angle ψ_b10CC can be obtained from the following expression.tan ψ_b10CC=R_b10C tan ψ_b10D/R_b10D  (86)(2) Path of Contact g_0CC of Gear C_c

If the contact normal of a tooth surface C_c on the plane of action G_10C of the tooth surface C passing the design reference point P₀ is newly designated by a path of contact g_0CC, the inclination angle thereof can be expressed as follows.g_0CC(φ_10C, ψ_b10CC; O₁)  (87)

Consequently, the intersection point P_0CC(u_c0CC, 0, z_c0CC; C_s) thereof with the plane S_H expressed by the coordinate system C_s can be obtained from the following expressions.sin φ_n0CC=−cos ψ_10CC sin φ_10C sin ψ_b10CC cos Γ_s tan ψ_0CC=tan φ_10C cos Γ_s+tan ψ_b10CC sin Γ_s/cos φ_10C u_c0CC=E tan ψ_0CC cos Γ_s sin Γ_s z_c0CC=(u_1p0−u_c0CC sin Γ_s)/cos Γ_s  (88)

If the intersection point P_0CC is expressed by the coordinate systems O₁, O_q1, it can be expressed as follows.P_0CC(u_1p0, −V_cs1, z_1p0CC; O₁)P_0CC(q_1p0C, −R_b10C, z_1p0CC; O_q1)z_1p0CC=−u_c0CC cos Γ_s+z_c0CC sin Γ_s−z_1c0  (89)(3) Phase Angle of Tooth Surface C_c

FIG. 34 shows a relationship of a point of contact P_wsCC of a tooth surface C_c(g_0CC) at the rotation angle θ₁ (=0) to the design reference point P₀. When the rotation angle θ₁=0, the tooth surface C_c has rotated by a phase angle θ_1wsC to the point P₀ and intersects g_occ at P_wsCC, therefore the phase angle θ_1wsCC of the point P_wsCC to the point P_0CC can be obtained from the following expressions with respect to g_0CC,P_0CCP_wsCC=R_b10Cθ_1wsC cos ψ_b10CC−z_1p0CC sin ψ_b10CC θ_1wsCC=2θ_1p(P_0CP_wsCC)/P_g0CC P_g0CC=2πR_b10C cos ψ_b10CC/N₁  (90)where 2θ_1p: the angular pitch of the pinion.(4) Equation of Path of Contact g_0CC

The equations of the path of contact g_0CC to be determined finally by the modification described above can be expressed as follows in the coordinate systems O₁, O_q1.q₁(θ₁)=R_b10C(θ₁+θ_1wsCC)cos² ψ+q_b10CC χ₁(θ₁)=χ_10C=π/2−φ_10C u₁(θ₁)=q₁ cos χ_10C+R_b10C sin χ_10C v₁(θ₁)=q₁ sin χ_10C−R_b10C cos χ_10C z₁(θ₁)=R_b10C(θ₁+θ_1wsCC)cos ψ_b10CC sin ψ_b10CC+z_1p0CC  (91)

The normal n_0C of the tooth surface C_c passing the design reference point P₀ does not become a contact normal.

9. Conjugate Large Gear Tooth Surface and Top Land

9.1 Conjugate Large Gear Tooth Surface

FIG. 34 and FIG. 35 show an effective surface of action (FIG. 34) drawn by the pinion involute helicoidal tooth surface D determined in such a way as described above and a generated gear conjugate tooth surface D (FIG. 35). R.sub.1h designates the radius of the face cylinder of pinion. The path of contact on which the contact ratio of the tooth surface D becomes maximum is located on the large end side far from the g.sub.0D, and the value thereof is about 2.1. Consequently, the tooth bearing of the tooth surface D must be formed on the large end side along the path of contact on which the contact ratio becomes maximum.

Similarly, FIG. 36 and FIG. 37 show an effective surface of action (FIG. 36) drawn by the pinion tooth surface C_c and a generated gear conjugate tooth surface C_c (FIG. 37). It is known that the effective surface of action and the large gear conjugate tooth surface C_c are realized within the zone (R_2t-R_2h) of the large gear given by the selected pinion tooth surface C_c. The contact ratio along the path of contact is 0.9. Consequently, the tooth bearing of the tooth surface C_c cannot but be formed on the small end side for the use of the lengthwise engagement. In the tooth surface C_c, the conditions of the fluctuation of a bearing load being zero is not satisfied.

9.2 Large Gear Top Land

FIG. 38 shows a state of a tooth of a large gear viewed from the gear axis thereof, and draws lines of intersection of the aforesaid conjugate large gear tooth surfaces D, C_c with the planes of rotation of the large gear at Z_2h=0 (face surface), Z_2h=3, Z_2h=6. In the figure, the widths of two lines at each of Z_2h=0, 3, 6 are large gear thicknesses. The thickness at the face surface Z_2h=0 (hatched zone in the figure) is the large gear face surface. Here, the ending of the line of intersection with Z_2h=0 at the point P₀ means that the tooth surface at the face surface does not exist from that point because φ_n0D≈φ_n2z.

Furthermore, the fact that in the figure the lines of intersection of the aforesaid planes Z_2h=3, 6 with the tooth surface C_c do not extend to the left side of the action limit curve L_3Acc indicates that an undercut is occurred at the part. However, a tooth surface is realized in a large gear zone at the top part as it has been examined at paragraph 7.1.

Generally, a sharpened top is generated on the large end side of a large gear in a combination of a cylinder pinion and a disk gear. In the present embodiment, the top land becomes somewhat narrower to the large end, but a top land that is substantially allowable for practical use is realized. This fact is based on the following reason.

In the present embodiment, the paths of contact g_0D, g_0C are both located at the vicinity of the limiting path g_2z, and incline to the g_2z in the reverse directions mutually. Consequently, the base cylinder radii R_b20D, R_b20C of the g_0D and the g_0C on the gear side are near to the base cylinder radius R_b2z of the g_2z, and the difference between them is small. Then, by modification of the tooth surface C to the tooth surface C_c (point P_0C is changed to the point P_0CC), the difference becomes still smaller as a result.

If an arbitrary path of contact in a surface of action in the vicinity of the paths of contact g_0D, g_0C drawn by an involute helicoid of a pinion is designated by g_m, the inclination angle g_m of the arbitrary path of contact g_m can be expressed as follows by transforming the inclination angle g_m(φ_1m, ψ_b1m; O₁) given by the coordinate system O₁ to the inclination angle in the coordinate system O₂,tan_{100 2m}=tan ψ_b10/cos φ_1m sin ψ_b2m=−cos ψ_b10 sin φ_1m  (92)where Σ=π/2, ψ_b1m=ψ_b10 (constant).

As a design example, in a case wherein the i₀ is large and the ψ₀ is also large (60°), the ψ_b10 is large, and the changes of the inclination angle φ_2m of the path of contact is small as shown in FIGS. 28-30. Consequently, the changes of the ψ_b2m becomes further smaller from the expressions (92).

On the other hand, because the gear tooth surface is the conjugate tooth surface of an involute helicoid, the following relationship is concluded.R_b2m cos ψ_b2m=i₀R_b10 cos ψ_b10  (93)

If the changes of the ψ_2m are small, the changes of the R_b2m also becomes small from the expression (93). Consequently, the large gear tooth surfaces D, C_c can be considered as involute helicoids having base cylinders R_b20D and R_b20C whose cross sections of rotation are approximate involute curves. Because the difference between R_b20D and R_b20C is small, the two approximate involute curves are almost parallel with each other, and the top land of the large gear is almost constant from the small end to the large end.

By the selection of the design variables ψ₀, φ_n0D, φ_n0C as described above, the undercut at the small end and the sharpening of the top, which are defects of a conventional face gear, are overcome, and it becomes possible to design an involute hypoid gear for power transmission.

Furthermore, the following points are clear as the guidelines of design of a hypoid gear having an involute helicoidal tooth surface.

• (1) The radius R₂₀ of the design reference point P₀ is located at the center of the inner radius and the outer radius of the large gear, and the inclination angle ψ₀ of the plane S_n perpendicular to the relative velocity at the point P₀ is determined so as to substantially satisfy the following expressions.R₂₀=(R_2t+R_2h)/2ε₂₀=sin⁻¹(−v_cs2/R₂₀)ψ₀=±cos⁻¹(R_2t/R₂₀)−ε₂₀ where

for + of the double sign: ordinal hypoid gear (ψ₀≧−ε₂₀)

for − of the double sign: face gear (ψ₀<−ε₂₀).

By the ψ₀ determined in this manner, the radius of the action limit curve of each path of contact constituting a surface of action becomes smaller than the radius R_2t in the large gear. That is, the action limit curve can be located on the outer of the face width, and thereby the whole of the face width can be used for the engagement of the gear.

• (2) The line of intersection of the plane of rotation of large gear Z₂₀ passing the design reference point P₀ and the plane S_n is supposed to be a limiting path g_2z. The inclination angle of the limiting path g_2z on the plane S_n is designated by g_2z(ψ₀, φ_n2z; C_s). A normal (path of contact) g_0D of the tooth surface D passing the point P₀ is selected at a position near to the limiting path g_2z. That is, if the inclination angle of the g_{0D on the plane Sn} is designated by g_0D(ψ₀, φ_n0D; C_s), the φ_n0D is selected as follows.φ_n0D≈φ_n2z (φ_n0D>φ_n2z)

This condition meets the case where the contact of the tooth surface D at the point P₀ becomes a convexo-convex contact (ψ₀≧−ε₂₀) as the result of the selection of the ψ₀. On the other hand, in case of a convexo-concave contact (ψ₀<−ε₂₀), a normal of the tooth surface C on the opposite side is selected as described above.

• (3) If the inclination angle of the normal (path of contact) g_0C of the tooth surface C passing the point P₀ on the plane S_n is supposed to be designated by g_0C(ψ₀, φ_n0C; C_s), φ_n0C can be selected as follows.φ_n0C=φ_n0D−2φ_n0R

Here, the 2φ_n0R is the vertex angle of an equivalent rack, and is within a range of 30°-50°, being 38° or 40° ordinarily. By the selection of the φ_n0D, φ_n0C in such a way mentioned above, a wide effective surface of action can be formed in the vicinity of the design reference point P₀. In other words, the radius of the action limit curve being a boundary of the effective surface of action can be made to be smaller than the radius R_2t in the large gear.

• (4) The face surface of a gear (plane of rotation of the gear) is located on the outer of a base cylinder determined by the paths of contact g_0D, g_0C determined as described in (2), (3). By use of an equivalent rack having the line of intersection (limiting path g_t) of the plane S_n and the plane S_t formed by the peripheral velocities of the design reference point P₀ as its reference line and the g_0D and the g_0C as its tooth surface normal, a tooth depth having given top lands of a pinion and a large gear and the face surface (cylinder) of the pinion are determined. The face surface of the gear is selected to be on the outer of the base cylinder radii R_b10D, R_b10C of the pinion, that is, the radii between the center O of the gear and normals to points A and B, which points are respectively located on the intersection of the tooth surface D and Cc with a circle coaxial with the gear center O (FIG. 42).(5) An involute helicoid having tooth surface normals of the paths of contact g_0D, g_0C is given to the pinion side or the large gear side, and further a mating surface is generated. The values for g_0D or g_0C are modified such that the tooth surface D and the tooth surface C on the pinion side have almost the same leads and the base cylinder radii to which the g_0D and the g_0C on the large gear side are tangent are almost the same. By the modification of the tooth surfaces D, C of the pinion to have the same leads, the top land of the pinion becomes constant in the axis direction. Furthermore, by the modification of the base cylinder radii on the large gear side, the top land of the gear also becomes almost the same in the radius direction.

In the hypoid gear design described above, a computer support design system (CAD system) shown in FIG. 40 performs design support. The CAD system is provided with a computer 3 including a processor 1 and a memory 2, an input unit 4, an output unit 5 and an external memory 6. In the external memory 6, data are read from and written into a recording medium. A gear design program for implementing the gear design method mentioned above is recorded in the recording medium in advance. As the occasion demands, the program is read out from the recording medium to be executed by the computer 3.

The program, more concretely, executes operations in accordance with the design guides (1)-(5) of the hypoid gear described above. FIG. 41 shows the outline of the operation flow. At first, the radius R₂₀ of the design reference point P₀ and the inclination angle ψ₀ of the plane S_n are determined on the basis of requirement values of the design of a hypoid gear (S100). Next, the normal (path of contact) g_0D of the tooth surface D passing at the design reference point P₀ is determined from the limiting path g_2z (S102). Furthermore, the normal (path of contact) g_0C of the tooth surface C passing at the design reference point P₀ is determined (S104). Moreover, the face surface of the gear and the face surface of the pinion are determined on the basis of the paths of contact g_0D, g_0C (S106). One of either the pinion side or the large gear side of the involute helicoid having the paths of contact g_0D, g_0C c as its tooth surface normal is given, and the other side is then determined (S108). Whether the formed tooth surfaces C, D of the pinion have almost the same leads or not is then judged (S110). If the tooth surfaces C, D do not have almost the same leads, the system returns to the step S102 and obtains the path of contact again. Furthermore, whether the base cylinder radii contacting with the paths of contact g_0D, g_0C of the formed large gear are almost the same to each other or not is judged (S112). If the base cylinder radii are not almost the same to each other, the system returns to the step S102, and the paths of contact are obtained again.

Table 1 shows an example of calculated specifications of a hypoid gear. Table 1 refers to a hypoid gear such as that shown in FIG. 42, having a gear tooth coast surface Cc with a base cylinder radius R_b10C, and gear tooth drive surface D with a base cylinder radius R_b10D,

TABLE 1
CYLINDER RADIUS FOR DESIGNING LARGE GEAR R20	77
(mm)
INCLINATION ANGLE OF PLANE Sn ψ0 (°)	60
Designed value in coordinate system Cs
P0 (uc0, 0, zc0; Cs) (mm)	(13.96, 0,
	75.00)
SPECIFICATIONS OF EQUIVALENT RACK
g2z (ψ0, Φn2z; Cs) (°)	(60.0,
	11.93)
gt (ψ0, Φnt; Cs) (°)	(60.0,
	7.13)
g0D (ψ0, Φn0D; Cs) (°)	(60.0,
	13.93)
g0C (ψ0, Φn0C; Cs) (°)	(60.0,
	24.07)
GEAR ADDENDUM	Ad2 (mm)	0.0
NORMAL PITCH	Pg0D (mm)	9.599
	Pg0C (mm)	8.269
	Pgt (mm)	9.667
WORKING DEPTH	hk (mm)	3.818
where tn = 2 mm and CR = 2 mm are supposed
PHASE ANGLE OF TOOTH SURFACE C θ2wsC (°)	−3.13
SPECIFICATIONS OF TOOTH SURFACE Cc
P0CC (uc0CC, 0, zc0CC; Cs) (mm)	(15.35, 0,
	69.30)
g0CC (ψ0CC, Φn0CC; Cs) (°)	(62.30, 0,
	−21.60)
PHASE ANGLE OF TOOTH SURFACE Cc θ1wsCC (°)	6.37
SPECIFICATIONS OF PINION
RADIUS OF CYLINDER TO BE DESIGNED R10 (mm)	31.391
MAJOR DIAMETER R1h (mm)	35.18
MINOR DIAMETER R1t (mm)	29.39
TOOTH SURFACE WIDTH (mm)	28
LEAD (mm)	109.83
HELICAL ANGLE ON CYLINDER TO BE DESIGNED (°)	60.89
SPECIFICATIONS OF INVOLUTE HELICOID
	TOOTH SURFACE D	TOOTH SURFACE Cc
BASE CYLINDER	31.389	17.754
RADIUS (mm)
HELICAL ANGLE (°)	60.89	45.44
THICKNESS IN RIGHT ANGLE DIRECTION TO AXIS OF
CYLINDER
TO BE DESIGNED	12.685
TOP THICKNESS	6.556
MAXIMUM CONTACT RATIO ALONG PATH OF CONTACT
	2.10	0.88
TOTAL CONTACT	4.21	2.10
RATIO

Claims

1. A method for designing a hypoid gear consisting of a pair of gears including a pinion and a large gear, either of said gears being a first gear having an involute helicoid as a tooth surface, the other of said gears being a second gear having a tooth surface conjugate to the former tooth surface, said method comprising the steps of: assigning to said gears (a) a stationary coordinate system in which one of three mutually orthogonal coordinate axes coincides with a rotation axis of the gear and one of other two coordinate axes coincides with a common perpendicular for the rotation axis of the gear and a rotation axis of a mating gear to be engaged with the gear, (b) a rotary coordinate system in which one of three mutually orthogonal coordinate axes coincides with the axis of said stationary coordinate system that coincides with the rotation axis of the gear among the three coordinate axes of said stationary coordinate system, said rotary coordinate system rotating about the coincided coordinate axis together with the gear, the other two coordinate axes of the three orthogonal axes coinciding with the other two axes of said stationary coordinate system respectively when a rotation angle of the gear is zero, and (c) a parameter coordinate system in which said stationary coordinate system is rotated and transformed about the rotation axis of the gear so that one of the other two coordinate axes of said stationary coordinate system becomes parallel with the plane of action of the gear, respectively;describing a path of contact of a pair of tooth surfaces of the gear and the mating gear which engage with each other during the rotation of the gears and an inclination angle of a common normal which is a normal at each point of contact for the pair of tooth surfaces respectively in terms of a first function, in which a rotation angle of the gear is used as a parameter, in said parameter coordinate system;describing the path of contact and the inclination angle of the common normal respectively in terms of a second function, in which a rotation angle of the gear is used as a parameter, based on the first function and a relationship between relative positions of said stationary coordinate system and said parameter coordinate system, in said stationary coordinate system;acquiring the path of contact and the inclination angle of the common normal in the stationary coordinate system, respectively, and acquiring a tooth profile by describing the path of contact and the inclination angle of the common normal, respectively, in terms of a third function, in which the rotation angle of the gear is used as a parameter, based on the second function and the relationship between the relative positions of said rotary coordinate system and said stationary coordinate system, in said rotary coordinate system;acquiring a surface of action for the pair of tooth surfaces having the tooth profile;acquiring action limit curves which are orthogonal projections of axes of the two gears on the surface of action, and acquiring a tip line of the second gear in the surface of action, based on the tooth surface of the second gear, and further acquiring an effective surface of action existing between the action limit curves and the tip line; andjudging whether or not the effective surface of action exists over a whole face width of the gear.

2. A hypoid gear design method according to claim 1, said method further comprising the step of: acquiring an angle between paths of contact for the tooth surface of a drive side of the first gear and the tooth surface of a coast side of the first gear such that the teeth of the first gear have an appropriate strength.

3. A hypoid gear design method according to claim 2, said method further comprising the steps of: acquiring specifications of an equivalent rack including a tooth surface based on the path of contact of the respective tooth surfaces of the drive side and the coast side; and acquiring a distance of the respective tip lines of the tooth surface of the drive side and the tooth surface of the coast side of the second gear, based on the specifications of the equivalent rack, and judging whether the acquired distance is equal to or greater than a predetermined value.

4. A hypoid gear design method according to claim 3, wherein at the acquiring of the pair of tooth surfaces a design reference point is set near a center of the face width of the gear, and when the distance of the tip line is insufficient at a large end side, the design reference point is shifted toward the large end side of the face width of the gear, and the effective surface of action is acquired again.

5. A hypoid gear design method according to claim 3, wherein at the acquiring of the pair of tooth surfaces a design reference point is set near a center of the face width of the gear, and when the effective surface of action is insufficient at a small end side of the face width of the gear and the distance of the tip line is insufficient at a large end side, the face width of the gear is reduced.

6. A hypoid gear design method according to claim 1, wherein at the acquiring of the pair of tooth surfaces a design reference point is set near a center of the face width of the gear, and when the effective surface of action is insufficient at a small end side of the face width of the gear, the design reference point is shifted toward the small end side of the face width of the gear, and the effective surface of action is acquired again.

7. A program for executing a hypoid gear design method according to claim 1 with a computer.

8. A hypoid gear comprising: a first gear including an involute helicoid as a tooth surface; anda second gear which is one of a pair of gears including the first gear,wherein the second gear has a tooth surface conjugate to the first gear surface,wherein the tooth surface of the first gear and the tooth surface of the second gear define a line of contact, andwherein a radius of a base circle of the first gear differs between a drive side and a coast side, andwherein, when a helical angle Ψ0 is greater than or equal to −ε20, a pressure angle φn0D of a drive-side tooth surface and a pressure angle φn0C of a coast-side tooth surface are: φn0D=φn2z+Δφn, φn0C=φn0D−2φn0R,whereε20=sin−1(−vcs2/R20)Vcs2=E tan Γs/{ tan(Σ−Γs)+tan Γs}φn2z is an inclination angle of limit trajectory (φn2z=tan−1(sin Ψ0/tan Γs))2φn0R is a vertex angle of an equivalent rack and has a value of 30° to 50°, and Δφn=2° to 10°.

9. A hypoid gear according to claim 8, wherein leads of tooth surfaces on the drive side and the coast side of the gear provided with the involute helicoid are the same.

10. A hypoid gear according to claim 8, wherein a ratio of an offset E being the shortest distance between each axis of a pinion and a gear constituting said hypoid gear and a radius R20 at a design point of the gear (E/R20) is larger than 0.25.

11. A hypoid gear according to claim 8, a gear ratio i0 thereof is within a range of 2.5 to 5.

12. A hypoid gear according to claim 8, wherein a helical angle Ψ0 thereof is within a range of 35° to 70°.

13. A hypoid gear according to claim 8, wherein at least one of the tooth surface of the first gear and the tooth surface of the second gear is modified.

14. A hypoid gear according to claim 8, wherein the base circle radius corresponds to an action limit curve radius.

15. A hypoid gear comprising: a first gear including an involute helicoid as a tooth surface; anda second gear which is one of a pair of gears including the first gear,wherein the second gear has a tooth surface conjugate to the first gear surface,wherein the tooth surface of the first gear and the tooth surface of the second gear define a line of contact, andwherein a radius of a base circle of the first gear differs between a drive side and a coast side, andwherein, when a helical angle Ψ0 is less than −ε20, a pressure angle φn0D of a drive-side tooth surface and a pressure angle φn0C of a coast-side tooth surface are: φn0D=φn0C+2φn0R, φn0C=φn2z−δφn,whereε20=sin−1(−vcs2/R20)vcs2=E tan Γs/{tan(Σ−Γs}φn2z is an inclination angle of limit trajectory (φn2z=tan−1(sin Ψ0/tan Γs))2φn0R is a vertex angle of an equivalent rack and has a value of 39° to 50°, and Δφn=2° to 10°.

16. A hypoid gear according to claim 15, wherein leads of tooth surfaces on the drive side and the coast side of the gear provided with the involute helicoid are the same.

17. A hypoid gear according to claim 15, wherein a ratio of an offset E being the shortest distance between each axis of a pinion and a gear constituting said hypoid gear and a radius R20 at a design point of the gear (E/R20)is larger than 0.25.

18. A hypoid gear according to claim 15, a gear ratio i0 thereof is within a range of 2.5 to 5.

19. A hypoid gear according to claim 15, wherein a helical angle Ψ0 thereof is within a range of 35° to 70°.

20. A hypoid gear according to claim 15, wherein at least one of the tooth surface of the first gear and the tooth surface of the second gear is modified.

21. A hypoid gear according to claim 15, wherein the base circle radius corresponds to an action limit curve radius.

22. A hypoid gear comprising: a first gear including an involute helicoid as a tooth surface; anda second gear which is one of a pair of gears including the first gear,wherein the second gear has a tooth surface conjugate to the first gear surface,wherein the tooth surface of the first gear and the tooth surface of the second gear define a line of contact, andwherein a radius of a base circle of the first gear differs between a drive side and a coast side, andwherein, when a helical angle Ψ0 is greater than or equal to −ε20, a pressure angle φn0D of a drive-side tooth surface and a pressure angle φn0C of a coast-side tooth surface are: φn0D=φn2z+Δφn, φn0C=φn0D−2φn0R,whereε20=sin−1(−vcs2/R20)vcs2=E tan Γs/{tan(Σ−Γs)+tan Γs}φn2z is an inclination angle of limit trajectory (φn2z=tan−1(sin Ψ0/tan Γs))2φn0R is a vertex angle of an equivalent rack and has a value of 30° to 50°, and Δφn=0° to 4°.

23. The hypoid gear according to claim 22, wherein Δφn=0° to 2°.

24. A hypoid gear comprising: a first gear including an involute helicoid as a tooth surface; anda second gear which is one of a pair of gears including the first gear,wherein the second gear has a tooth surface conjugate to the first gear surface,wherein the tooth surface of the first gear and the tooth surface of the second gear define a line of contact, andwherein a radius of a base circle of the first gear differs between a drive side and a coast side, andwherein, when a helical angle Ψ0 is less than −ε20, a pressure angle φn0D of a drive-side tooth surface and a pressure angle φn0C of a coast-side tooth surface are: φn0D=φn0C+2φn0R, φn0C=φn2z−Δφn,whereε20=sin−1(−vcs2/R20)vcs2=E tan Γs/{tan(Σ−Γs)+tan Γs}φn2z is an inclination angle of limit trajectory (φn2z=tan−1(sin Ψ0/tan Γs))2φn0R is a vertex angle of an equivalent rack and has a value of 39° to 50°, and Δφn=0° to 4°.

25. The hypoid gear according to claim 24, wherein Δφn=0° to 2°.