JPS5846260A - Gear arrangement - Google Patents

Abstract

PURPOSE:To make it possible to make the distance between axles to coincide with the distance between intermeshing centers and to adjust the quantity of backlash by constructing the gear arrangement so that the variation rate of the quantity of displacement between teeth of a gear of a frustum of a cone becomes constant, and deviating gears in axial direction. CONSTITUTION:Involute plain gears 1 and 2 formed into the shape of a frustrum of a cone are positive shift gears in each of which the quantities of shifts differ between the small-diameter side end and the large diameter side end, and the variation rate m.DELTAs/b of the quantities of shifts between the teeth widths becomes constant. By setting the variation rate m.DELTAx/b at a constant value, the distance (a) between intermeshing centers of both gears 1 and 2 becomes constant at an arbitray position between the teeth widths (b). The distance (a) of the intermeshing centers is a function of only an intermeshing pressure angle alpha0, If the shifting positions of both gears 1 and 2 are set so that the sum (X1X X2) of the shift coefficients of both gears 1 and 2 becomes constant, the intermeshing pressure angle alpha0 becomes constant and the distance (a) of the intermeshing centers becomes constant.

Description

[Detailed description of the invention] TECHNICAL FIELD The present invention relates to improvements in gear devices.

Conventionally, the meshing center distance of a gear device is calculated from the module, number of teeth, tool pressure angle, and square meshing angle of the meshing gears. It is impossible to match them due to manufacturing reasons.

However, when the gear device is ≦2, the amount of backlash is determined by the distance between the shafts (==), and the amount of pub crush is determined by the size of the gear device. It is very important to set the crash.As mentioned above (= gear mechanism ("
Although it is essential to adjust the distance between the shafts of the gears, such adjustment requires a considerable amount of time and effort, such as modifying the components of the gear device and selecting spacers.

The present invention has been made in view of the conventional circumstances, and its purpose is to slightly shift the gears in the axial direction, so that the distance between the shafts is matched to the meshing center distance C, and the amount of backlash is reduced. Providing a gear system that can be easily adjusted (two).

An example of the embodiment of the present invention will be described with reference to FIG. 1. The gear device of the present invention is constituted by a spur gear (1) formed in a truncated conical shape.

The gears (1) and (2) are both normal gears with different rotational positions at the small diameter end and the large diameter end, and the face width (b)
They are formed so that the rate of change in the amount of dislocations between them is constant.

That is, in the figure, 1·ΔI indicates the change in the amount of dislocation of the gears (1) and (2), and if the rate of change is expressed as m·mu x/b, then m
-Ax, 15 is assumed to be constant.

Also, by keeping m・Todoroki x/b constant, the meshing center distance (a) of both gears (1) and (2) becomes constant at any position between the face width (-).This meshing center distance ( ~ is 2nd gear: Number of teeth of gear U) Z3: Number of teeth of gear (2) m: Module (■) of gears (1) and C) a: Distance between meshing centers of gears (1) and (2) ( Ill) α: Tool pressure angle (dog,) of gears (1) and (2) α0: Meshing pressure angle (dog, ) of gears (1) and (2) equals 2aosα.

becomes. (In formula 11, module (ml), number of teeth of gear (1) (Zyu), number of teeth of gear (2) (zl), tool pressure (
α) is a constant determined by the design of the gear, but the meshing pressure angle (0°) is a variable that changes depending on the meshing state C of gears (1) and (21), so the meshing center short path 1al is the meshing pressure angle It becomes a function of only (α.).

The following 6 two-mesh pressure angle (α.) is X: Shift coefficient of gear (1) x 3: Shift coefficient of gear (2) f: Packlash pupil (III) So, I□+”m”2am- α 1rrV (ni) = Thin α −...
(2) 2□ +2°. Above (in formula 21, tool pressure angle -, module (
-1 Number of teeth of gear (1) ■, ), Number of teeth of gear (2) (2,
) is a constant determined by the design of the gear, and the amount of backlash (f) can also be considered a constant since the optimum value is indicated based on the purpose and accuracy of the gear device. That is, the above c
2) Equation is the sum of the shift coefficients of gears (1) and (2), 0□10M,
) is the only function. From the above, gears (1), (2) (:
, the sum of the shift coefficients of gears (11, (21)
, ) is constant C2 (=, both gears (1), (21
If the amount of dislocation is set, the meshing pressure angle (α) becomes constant.

As mentioned above, since it is a function only of the meshing center distance (-meshing pressure angle opening), gears (1) and (2)
By setting the sum of the dislocation coefficients (x, +x,) to be constant, the meshing center distance (&) is therefore constant.

The sum of the shift coefficients (X□+x,) of gear (11, (2)) is m
-x: Amount of dislocation of gear (1) (M)m-I engineering. Minimum shift amount of two gears α) (■)m”Xs:
Gear (2) (D dislocation amount (wm) m'
so: Minimum amount of dislocation of gear (III) m・Δ
X: Change in dislocation amount between face width (b) (IIB) h:
Axial distance from the small diameter end of gear α)
(■) Mix, = m@x1゜+ −・m・ΔI−x
,=x,. Sanskrit・Δx-=・・・・-(3)m@Xll
=m”X,.+ll118X-b “m” x・°・
xl = x80+ x-r 11m ・ΔN----・
−(4), and from the sum of each side of equations (3) and (4), I
□＋】Vertical, =X yo◎＋ Imaro. ＋ΔI・・・・・・
... (5) In the above equation (5), the shift coefficient (X, ) of the small end diameter of gear (1) is the shift coefficient (X, ) of the small end diameter of gear (1). : It is a constant determined by the change rate type of dislocation amount between face width (b)・Δx/
b is constant C: formed, module (m), tooth width (
Since b) is a constant, the shift coefficient (ΔX) that indicates the change in shift amount between the tooth width (b1) is naturally a constant. From the above, the sum of the shift coefficients of gears (1) and (2) (xl+x, ) becomes constant, and the meshing center distance (a) is determined by the meshing tooth width (
An arbitrary position c2 between b1 becomes constant.

Next, the second embodiment is shown in FIG. It is.

That is, when each of the gears (3) and (4) is moved two degrees in the axial direction, C is set so that the gear (3) meshes within a face width of 1 lb4).
Second, the transmission strength is increased. Then, the rate of change in the amount of dislocation between the face width (b, ) of gear (3) m・ΔI3/′bI and the rate of change in the amount of dislocation between the face width (b4) of gear (4) m・muxa/
By keeping b4 constant, the rate of change in the amount of dislocation between the meshing tooth widths can be made constant (:), and the meshing center distance (a) Y can be made constant.

Claims (1)

[Claims] A gear device comprising a gear in which the change rate of the amount of displacement between the tooth widths of the shifted gear is constant.