Cycloidal gears

Claim 2

A planetary gear comprising at least one planet wheel moved with the aid of an eccentric and at least one concentric wheel, said wheels engaging by means of a closed cam plate cycloid constructed on one wheel and a ring of rollers constructed on the other wheel, and the tangency points of the rollers with the cam plate cycloid describing points of a reference cycloid whereby both cycloids can be mathematically expressed as follows: x = r·cos α ± e·cos(β ± α) ∓ q·cos(γ ± α) y = r·sin α + e·sin(β ± α) - q·sin(γ ± α) where: x, y = abscissa and ordinate of the plane of said cycloids; r = sum of the radii of a circle rolling without sliding on the outer circumference of a fixed base circle; α = angle subtended between said abscissa and a line passing through the center of said cycloids, through a point of tangency of said rolling circle and fixed base circle, and through the center of said rolling circle; e = eccentricity of the gear arrangement; β = rolling angle; q = equidistant spacing; γ = transmission angle; and wherein the value of the parameter q for the cam plate cycloid is larger than for the reference cycloid, and the value of the parameter r in the case of the construction of the cam plate cycloid as an epicycloid is larger, and in the case of the construction of the cam plate cycloid as a hypocycloid is smaller than for the reference cycloid.

Claim 3

A planetary gear as claimed in claim 1, wherein the cam plate cycloid has a larger value for the parameter e than the reference cycloid.

Claim 4

A planetary gear as claimed in claim 2, wherein the difference of the values for the parameters r to the difference of the values for the parameters q for the reference and cam plate cycloids is as √(1+m 2 )-1 to 1-√(1-m 2 ), where: m = the shortening ratio of the cycloids.

Claim 5

A planetary gear as claimed in claim 3, wherein a rotation reversal tolerance δ is minimized in accordance with the following equation: δ = (1 ± 1/z) · (arc cos (-m) - arc cos (-m.sub.1)), where: m is the shortening ratio of the reference cycloid and m 1 of the shortening ratio of the cam plate cycloid.

Claim 6

A planetary gear as claimed in claim 4, wherein the shortening ratio m and the equidistant q are chosen to give the smallest possible contact pressure.

Claim 7

A planetary gear as claimed in any of claim 4, wherein the equidistant q is approximately the same size as the smallest radius of curvature occurring in proximity to the point of inflection of the cam flank of the reference cycloid.

Claim 8

A planetary gear arrangement comprising: at least one planet wheel, eccentric means for moving said planet wheel, at least one further wheel concentrically mounted with respect to said planet wheel means for engaging said at least one planet wheel and said at least one further wheel including a closed cycloid cam means provided on one of said planet wheel and said further wheel and roller means provided on the other of said planet wheel and said cam means defining contact points describing points of a reference cycloid, wherein both the reference cycloid and cycloid cam means are mathematically expressed in the following terms: x = r·cos α + e · cos (β + α) - q · cos (γ+α), y = 4· sin α + e· sin (β + α) - q · sin (γ+α), where: x, y = abscissa and ordinate of the plane of said cycloids; r = sum of the radii of a circle rolling without sliding on the outer circumference of a fixed base circle; α = angle subtended between said abscissa and a line passing through the center of said cycloids, through a point of tangency of said rolling circle and fixed base circle, and through the center of said rolling circle; e = eccentricity of the gear arrangement; β = rolling angle; q = equidistant spacing; γ = transmission angle; and wherein the value of the parameter q for said cam means is larger than the value q for said reference cycloid, said cam means being constructed as an epicycloid cam plate with the value of the parameter r being larger than the value of the parameter r for the reference cycloid.

Claim 9

A planetary gear arrangement comprising: at least one planet wheel, eccentric means for moving said planet wheel, at least one further wheel concentrically mounted with respect to said planet wheel means for engaging said at least one planet wheel and said at least one further wheel including a closed cycloid cam means provided on one of said planet wheel and said further wheel and roller means provided on the other of said planet wheel and said cam means defining contact points describing points of a reference cycloid, wherein both the reference cycloid and cycloid cam means are mathematically expressed in the following terms: x = r·cos α + e · cos (β + α) - q · cos (γ+α), y = 4· sin α + e· sin (β + α) - q · sin (γ+α), where: x, y = abscissa and ordinate of the plane of said cycloids; r = sum of the radii of a circle rolling without sliding on the outer circumference of a fixed base circle; α = angle subtended between said abscissa and a line passing through the center of said cycloids, through a point of tangency of said rolling circle and fixed base circle, and through the center of said rolling circle; e = eccentricity of the gear arrangement; β = rolling angle; q = equidistant spacing; γ = transmission angle; and wherein the value of the parameter q for said cam means is larger than the value q for said reference cycloid, said cam means being constructed as an epicycloid cam plate with the value of the parameter r being larger than the value of the parameter r for the reference cycloid.

Claim 10

An arrangement according to claim 7, wherein said epicycloid cam plate has a large value for the parameter e than the reference cycloid.

Claim 11

An arrangement according to claim 8, wherein the difference between the values for the parameter r to the difference between the values for the parameter between the values for the parameters q for the reference and said epicycloid cam plate is: √(1+m.sup.2) -1 to 1 -√(1-m.sup.2), where: m = shortening ratio of the cycloids.

Claim 12

An arrangement according to claim 9, wherein a rotation reversal tolerance angle δ of the gear arrangement is minimized in accordance with the following: δ = (1+1/z) - (arc cos (-M)- arc cos (-M.sub.1)) where: z = ratio of the radius of the fixed base circle to the radius of the rolling circle, m = shortening ratio of the reference cycloid, m 1 ' shortening ratio of the epicycloid cam plate.

Claim 13

An arrangement according to claim 10, wherein the shortening ratio m and the constant equidistant spacing q are selected to provide the smallest contact pressure between said roller means and said epicycloid cam plate.

Claim 14

An arrangement according to claim 11, wherein the reference cycloid includes cam flank means, and wherein the equidistant spacing q is substantially of the same size as the smallest radius of curvature occurring proximate to a point of inflection of said cam flank means of the reference cycloid.

Claim 15

A planetary gear arrangement comprising: at least one planet wheel, eccentric means for moving said planet wheel, at least one further wheel concerntrically mounted with respect to said planet wheel means for engaging said at least one planet wheel and said at least one further wheel including a closed cycloid cam means provided on one of said planet wheel and said further wheel and roller means provided on the other side of said planet wheel and said cam means defining contact points describing points of a reference cycloid, wherein both the reference cycloid and cycloid cam means are mathematically expressed in the following terms: x = r · cos α - e · cos (β - α) + q · cos (γ-α), y =r · sin α + e · sin (β - α) - q · sin (γ-α), where: x, y = abscissa and ordinate of the plane of said cycloids; r = sum of the radii of a circle rolling without sliding on the outer circumference of a fixed base circle; α = angle subtended between said abscissa and a line passing through the center of said cycloids, through a point of tangency of said rolling circle and fixed base circle, and through the center of said rolling circle; e = eccentricity of the gear arrangement; β = rolling angle; q = equidistant spacing; γ = transmission angle; and wherein the value of the parameter q for said cam means is larger than the value q for said reference cycloid, said cam means being constructed as a hypocycloid cam plate with the value of the parameter r being smaller than the value of the parameter r for the reference cycloid.

Claim 16

A planetary gear arrangement comprising: at least one planet wheel, eccentric means for moving said planet wheel, at least one further wheel concerntrically mounted with respect to said planet wheel means for engaging said at least one planet wheel and said at least one further wheel including a closed cycloid cam means provided on one of said planet wheel and said further wheel and roller means provided on the other side of said planet wheel and said cam means defining contact points describing points of a reference cycloid, wherein both the reference cycloid and cycloid cam means are mathematically expressed in the following terms: x = r · cos α - e · cos (β - α) + q · cos (γ-α), y =r · sin α + e · sin (β - α) - q · sin (γ-α), where: x, y = abscissa and ordinate of the plane of said cycloids; r = sum of the radii of a circle rolling without sliding on the outer circumference of a fixed base circle; α = angle subtended between said abscissa and a line passing through the center of said cycloids, through a point of tangency of said rolling circle and fixed base circle, and through the center of said rolling circle; e = eccentricity of the gear arrangement; β = rolling angle; q = equidistant spacing; γ = transmission angle; and wherein the value of the parameter q for said cam means is larger than the value q for said reference cycloid, said cam means being constructed as a hypocycloid cam plate with the value of the parameter r being smaller than the value of the parameter r for the reference cycloid.

Claim 17

An arrangement according to claim 13, wherein said hypocycloid cam has a larger value for the parameter e than the reference cycloid.

Claim 18

An arrangement according to claim 14, wherein the difference between the values for the parameter r to the difference between the values for the parameter between the values for the parameters q for the reference and said hypocycloid cam plate is: √(1+m.sup.2) -1 to 1- √(1-m.sup.2), where: m = shortening ratio of the cycloids.

Claim 19

An arrangement according to claim 15, wherein a rotation reversal tolerance angle δ of the gear arrangement is minimized in accordance with the following: δ = (1+1/z) - (arc cos (-M)-arc cos (-M.sub.1)), where: z = ratio of the radius of the fixed base circle to the radius of the rolling circle, m = shortening ratio of the reference cycloid, m 1 = shortening ratio of the hypocycloid cam plate.

Claim 20

An arrangement according to claim 16, wherein the shortening ratio m and the constant equidistant spacing q are selected to provide the smallest contact pressure between said roller means and said epicycloid cam plate.

Claim 21

A planetary gear arrangement comprising: at least one planet wheel, eccentric means for moving said planet wheel, at least one further wheel concentrically mounted with respect to said planet wheel, means for engaging said at least one planet wheel including a closed cycloid cam means provided on one of said planet wheel and said further wheel and roller means provided on the other of said planet wheel and said further wheel, said roller means and said cam engaging at contact points describing points of reference cycloid, wherein distance values Δμ occurring between said roller means and said contact points on said cam means and the reference cycloid, respectively, are defined as follows: Δμ = (Δq - Δr · cosγ/sinγ), where: Δq = difference of values of an equidistant spacing of the cam means and reference cycloid, Δr = difference of values of the sum of the radii of a circle rolling without sliding on the outer circumference of a fixed base circle respectively defining the cam means and the reference cycloid, and γ = the transmission angle.

Claim 22

A planetary gear arrangement comprising: at least one planet wheel, eccentric means for moving said planet wheel, at least one further wheel concentrically mounted with respect to said planet wheel, means for engaging said at least one planet wheel including a closed cycloid cam means provided on one of said planet wheel and said further wheel and roller means provided on the other of said planet wheel and said further wheel, said roller means and said cam engaging at contact points describing points of reference cycloid, wherein distance values Δμ occurring between said roller means and said contact points on said cam means and the reference cycloid, respectively, are defined as follows: Δμ = (Δq - Δr · cosγ/sinγ), where: Δq = difference of values of an equidistant spacing of the cam means and reference cycloid, Δr = difference of values of the sum of the radii of a circle rolling without sliding on the outer circumference of a fixed base circle respectively defining the cam means and the reference cycloid, and γ = the transmission angle.