JPS62277218A - Continuously variable adjustment helical guide mechanism for gear shaper - Google Patents

Abstract

PURPOSE:To shorten preparation time for machining by adjusting helical angles continuously variably through a combined reciprocal rotary motion of a main shaft by combining a motion along a lead of a 1st helical ridge with a motion along a lead of a 2nd helical ridge. CONSTITUTION:A main shaft 11 performs reciprocal rotary motion along a lead of a 1st helical ridge 15a as a 1st crank shaft 25 rotates. At this time, if a 1st female part 16 is relatively moved by rotating a 2nd crank shaft 43, the main shaft 11 performs a combined rotation in which the reciprocal rotary motion along the lead of the 1st helical ridge 15a is combine with a reciprocal rotary motion along a lead of a 2nd helical ridge 17a. In the case helical angles are to be changed, the diameters of the 1st and the 2nd crank shafts 25 and 43 are adjusted to change relative quantities of movements of the 1st female part 16 and a male part 15. With the above arrangent, design of a helical gear becomes less restricted and a machining preparation time can be shortened.

Description

[Detailed description of the invention] 3 Detailed explanation of the invention <Industrial application field> The present invention relates to a helical guide mechanism for a gear shaper.

<Conventional technology> When processing a helical gear with a gear shaper,
The gear cutting tool (cutter) must be moved axially and rotated at the same time to provide helical interlocking to the cutter. Conventionally, the helical motion of the cutter is controlled by a helical guide mechanism. FIG. 9 shows a longitudinal sectional view of a conventional helical guide mechanism. As shown in FIG. 9, the main shaft 2 on which the cutter 1 is attached is guided by a hydrostatic bearing 3 so that it can freely reciprocate in the axial direction and freely rotate, and is driven by a crank mechanism. It is designed so that it can be moved back and forth in the axial direction. A male helical guide 6, as shown in perspective in FIG.
The main shaft 2 rotates as it moves in the axial direction. 7 The flange 7 is driven to rotate synchronously with the helical gear, which is a workpiece, during gear cutting by a worm wheel 9 and a worm (not shown).

Figures 11 and 12 are explanatory diagrams showing the relationship between the specifications of the cutter and the leads of the helical guide.
Pitch circle diameter d of helical guide glue L and cutter 1
There is the following relationship with cp.

Lt breath nφ=π・d ・・・・・・・・・+11 Here, φ is the helix angle of the cutter 1, m is the tooth normal module of the cutter 1, and 2 is the number of teeth of the cutter 1.

Therefore, for one helical guide, the helix angle that can be machined is limited to d, when p = a certain range and Z satisfies the condition that Z is an integer.For this reason, the cutter can be used with the same lead. The helical angle of the helical gear to be machined cannot be changed arbitrarily as it is limited by the specifications.

<Problems to be solved by the invention> As described above, in the conventional helical guide mechanism, the helical guide has a fixed helical angle, and the cutter 1 that can be used for it is limited to specific gear specifications. In addition, when changing the helical angle of the helical gear being machined, there is the problem that the male type 6 and female type 8 of the helical guide must be replaced with ones that have a corresponding helical angle. Ta. Therefore, this becomes a constraint on gear design, and if this constraint is not taken into account, a problem arises in that the machining setup change time becomes extremely long. Further, in the crank system having the connecting rod 4, a complete single string motion is not performed, so it is difficult to synchronize the rotational movement of the main shaft 2 and the axial movement. For this reason, if a gear is machined in this state, the tooth surface will look like it has been hit, making it impossible to machine a practical gear, and there is also a high possibility that an abnormal load will be applied to the tool during machining, resulting in damage to the tool.

The present invention was made in view of the above situation, and is a stepless gear shaper that can adjust the helical angle steplessly and accurately regardless of the moving speed of the main shaft! By providing 81 J-aligned helical guide structures, it is possible to process multiple 1111M helical gears with different helical ranges without setup changes, reducing constraints on the design of helical gears and shortening the setup change time for machining, increasing production efficiency. The purpose is to improve.

Means for Solving the Problems> The structure of the present invention to achieve the above object includes a main shaft that is capable of reciprocating in the axial direction and rotatable around the axis, and a shaft that is connected or integrated with the main shaft and that can be rotated freely. a male shape in which a first helical convex portion having a lead and direction corresponding to the corner is formed; a first helical concave portion on the inner circumference that fits into the first helical convex portion of the male shape; A driving device having a first female shape in which a second helical convex portion having a lead and a direction that is the same as or different from the helical convex portion is formed, and a second helical concave portion that fits into a second helical convex portion of the first female shape. a second female type that is rotated, and a first crank mechanism that reciprocates the male type together with the main shaft in the axial direction by rotation of a first crankshaft;
a second crank mechanism that provides the first female type with a relative reciprocating motion synchronized with the male type with a phase of 0 degrees or 180 degrees by rotation of a second crankshaft that rotates in synchronization with the first crankshaft; It is characterized by being equipped.

Function: The rotation of the first crankshaft of the first crank mechanism causes the main shaft to reciprocate in the axial direction, thereby reciprocating the main shaft along the lead of the first helical convex portion where the male and first female shapes are fitted. The main shaft performs a reciprocating rotational movement, and at this time, when the first female shape is moved relative to the axial direction in synchronization with the movement of the main shaft by the rotation of the second crankshaft of the second crank mechanism, the main shaft moves into the first helical convex The reciprocating rotational motion along the lead of the second helical convex portion is combined with the reciprocating rotational motion along the lead of the second helical convex portion to rotate.

By synchronizing the rotation of the first crankshaft and the second crankshaft, obtain the relative movement of the first female type and male type that follows the movement speed of the main shaft, and obtain the rotation of the main shaft according to the movement speed. If the helical angle is changed, adjust the crank diameters of the first and second crankshafts to change the amount of relative movement between the first female type and male type.

<Embodiment> FIG. 1 shows a vertical cross section of a stepless adjustment helical guide mechanism of a gear shaper according to an embodiment of the present invention, FIG. 2 shows a view taken along the line ■-■ in FIG. 1, and FIG. 1 is a perspective view of the drive mechanism, and FIG. 5 is a graph showing the relationship between crank diameter and torsion angle.

A cutter 12 is attached to the lower end of the main shaft 11.
is slidably guided in the axial direction and in the direction of rotational force by a bearing 14 fitted to the cutter head 13. A male shape 15 having a first helical convex portion 15a having a lead and direction corresponding to a desired helix angle is fitted into the upper part of the main shaft 11. A first female shape 16 is disposed on the outer periphery of the male shape 15, and a first helical convex portion 15a of the male shape 15 is fitted into a first helical recess 16a provided on the inner circumference of the first female shape 16. There is. A second helical convex portion 16b is provided on the outer periphery of the first female shape 16, and a second female shape 17 is provided on the outer periphery of the first female shape 16. The second helical convex portion 16b is not provided on the inner periphery of the second female shape 17.
It is fitted in a. The second female shape 17 is driven to rotate in synchronization with the helical gear, which is a workpiece, during gear cutting 9 by a worm wheel 18 and a worm (not shown).

A housing 19 is fitted into the upper part of the male type 15, and a spherical bearing 21, which is not attached to one end of the feed screw 20, is provided in the housing 19 so as to be rotatable and swingable. The other end of the feed screw 20 is screwed into a female thread of a block 22, and a rod 24 rotatably supported by a gear box 23 is attached to the block 22.

The threaded portion of the feed screw 20 and the female screw is fixed during operation by a clamp device (not shown), and the screw portion of the feed screw 20. block 2
2. The integral rod 24 is supported at both ends by a spherical bearing 21 and a gear box 23.

The first crankshaft 25 for the male type 15 is a gear box 23
A bracket 26 is provided on the end surface of the first crankshaft 25 so as to be slidable in the axial direction.

A seven flange 27 is attached to the bracket 26, and a disc 28 is rotatably supported between the bracket 26 and the flange 27. Three roller followers 30 are supported on the disk 28 via bins 29, and the main shaft 1 is supported on the block 22.
A yoke 31 is provided in a direction perpendicular to the axis of the roller 1, and three roller followers 30 are fitted into the yoke 31.

A flange 32 is attached to the end of the first crankshaft 25, and a feed screw 33 is rotatably supported on the flange 32.

A gear 34 is attached to the tip of the feed screw 33, and the feed screw 33 is fixed in the axial direction by a nut 35. The bracket 26 is provided with a female thread 36, and the female thread 36 is screwed into the feed screw 33.

A cylinder 3 having a disk portion 37 formed at the upper end of the first female shape 16
8 is provided, and a roller follower 39 is fitted into the disk portion 37 of the cylinder 38. Roller follower 39 is bin 4o
The slider 41 is supported by a linear guide 42 so as to be freely slidable.

The second crankshaft 43 of the first female type 16 is rotatably supported by the gear box 23 coaxially and symmetrically with the first crankshaft 25.

Like the first crankshaft 25, the second crankshaft 43 has three roller followers 44, a pin 45, a disc 46, a flange 47, a bracket 48, a female screw 49, a feed screw 50,
A flange 51, a nut 52, and a gear 70 are attached.

The three roller followers 44 are fitted into a yoke 53 extending in a direction perpendicular to the sliding direction of the slider 41.

As shown in FIG. 4, the first crankshaft 25 and the second crankshaft 43 have a phase of 0 degrees or 180
connected by degrees.

The rotational movement of the first crankshaft 25 is caused by the first crankshaft 25,
The first crank mechanism, which is a Scotch choke mechanism, is composed of a bracket 26, a flange 27, a roller follower 30, and a yoke 31. is converted into a reciprocating motion of a single chord (sine) motion in the axial direction of the main shaft 11. At this time, in the first female type 16 as well, the rotational movement of the second crankshaft 43 is converted into a single chord (sine) movement in the axial direction via the yoke 53, the slider 41, and the three roller followers 44 by the Scotch coke mechanism. (It is converted into a y motion and reciprocates. Therefore, in addition to the reciprocating motion in the axial direction, the main shaft 11 rotates the male shape 15 with respect to the first female shape 16 according to the relative movement stroke between the male shape 15 and the first female shape 16. , and the rotation of the first female shape 16 relative to the second female shape 17 is added, and the space between the first female shape 16 and the second female shape 17 is 1-0-.
Is it constant (the ratio of axial speed and rotational speed due to screw motion is constant) determined by the rip width ratio? IJ order.

(By driving the fiIII 34, the feed screw 33 is rotated to slide the bracket 26 via the female thread 36, and the crank diameter R1 on the male type 15 side determines the stroke of the deformed main shaft 11. teeth J170
When is driven, the bracket 48 is similarly slid to change the crank diameter R2 on the first female 16 side and adjust the stroke of the first female 16 appropriately.

Due to the relative movement of the male type 15 and the first female type 16, the main shaft 1
FIG. 5 shows the state in which the rotation angle α of 1 changes. If the sign of α is positive, it represents clockwise rotation when viewed from above, and if it is negative, it represents counterclockwise rotation. Here, the right lead is used for the first helical protrusion 15a of the male type 15, and the left lead is used for the second helical protrusion 16a of the first female type 16, and the leads have the same size.

For example, when the first female type 16 is in a stationary state, the main shaft 1
1 performs a right-handed twisting motion on the first helical convex portion 16a of the male shape 15, and when the first female shape 16 moves at the same speed as the male shape 15 with a phase of 0 degrees, it moves along the second helical convex portion 16b. Perform a left-handed twisting exercise. In addition, the first female type 16
If it moves at half the speed of the male type 15 with a phase of 0 degrees, the main shaft 11
The rotational motion in both directions cancels each other out, resulting in motion only in the axial direction. In addition, the first female type 16 and the male type 15 are in phase 180.
When the main shaft 11 moves in the axial direction in degrees, the first helical convex 11I5
15 Perform a right-handed movement smaller than the lead of a.

Adjust the crank radius R1 and R2 appropriately! 4, the first female type 16 relative to the male type 15 has a speed ratio of 0 to 1.2 at a phase of 0 degrees, and a speed ratio of 0 to 2.2 at a phase of 180 degrees.
Since it can be changed up to 0, it is possible to select an arbitrary lead (size direction).

The phase between the male type 15 and the first female type 16 can be adjusted to 0 degrees or 18 degrees by using an NC device without using a gear train, or by setting the crank radii R1 and R2 in the same or opposite directions.
It can also be adjusted to 0 degrees. In addition, the speed ratio of the male type 15 and the first female type 16 can be changed by changing the angle θ of the yoke 31°53.
This can also be done by changing the shape of the circle.

As shown in FIG. 4, the gear 34 is driven by the servo motor 54 through the gears 55, 56, 57 and 58, and the gear 61. Similarly, the gear 70 is driven by the servo motor 54 through the gears 55, 56 and the gear 59. , 60 and a gear 62. Gear 61 and gear 34 and tooth lX62 and gear 70
The gears 61 and 62 mesh only when adjusting the strokes of the male type 15 and the first female type 16.
is moved in the axial direction by a hydraulic cylinder (not shown) to disengage the mesh. The mechanism for raising and lowering the position of the main shaft 11 drives gears 63 and 64 to adjust the position of the main shaft 11, but the explanation thereof is omitted.

Next, the principle of synchronous driving of the male type 15 and the first female type 16 will be explained with reference to FIGS. 6.7 and 8.

The helix angle of the male shape 15 is the same as that of the male shape 15 and the first female shape 16.
Twist by the amount of lead corresponding to the relative movement of. If the displacement yh of the male shape 15 and the first female shape 16 is the same and there is no relative slip, no torsional movement will occur in the male shape 15.

Therefore, if the torsional rotation angle of the male shape 15 caused by the relative interlocking of the male shape 15 and the first female shape 16 is α, then a = −□ (S±S) tanθd, /;
I O Also, if the torsional rotation angle of the male type 15 due to the interlocking of the first female type 16 is β, then β=□・5−tanθ d /2 ° ・ =□・5−tanθ ・・−・(2) d . .

The torsional rotation angle γ of the male shape 15 (that is, the main shaft 11) when viewed from the main body side (upper part) of the cutter head 13 provided with the male shape 15 and the first female shape 16 is expressed by the following equation.

γ=a+β (3) (1) In the center of the equation, the minus sign represents the following.

+: The vertical movements of the male type 15 and the first female type 16 are in opposite phases.

1: The vertical movements of the male type 15 and the first female type 16 are in the same phase.

In other words, (S2±80) is the male type 15 and the first female type 16
represents the relative slip of 1.

In addition, No. 6. ? , 8 and (11 (with the code in formula 21, S
, is the amount of axial movement of the male type 15, So is the amount of axial movement of the first female type 16, dl is the effective diameter of the male type 15, d, l are the effective diameters of the first female type 16, θ, is the lead angle of male type 15, θ. is the lead angle of the first female type 16, and θ is the composite lead angle of the male type 15.

Male type 1 due to relative interlocking of male type 15 and first female type 16
In order to process a helical gear using the synthetic torsional interlocking of the male type 15, the vertical interlocking and rotational interlocking of the male type 15 must be constant even at any stroke position. That is, at this time, the apparent advance angle θ of the synthesized male shape 15 and first female shape 16 is θ; (torque n-'K (5)).

θ=jan-' = tan-” (□(α+β)) S.

Since θ is a constant, it is sufficient if the angle is constant at −8° because θ is constant. If the upper and lower wJ mechanisms of the male type 15 and the first and female types 16 perform sinusoidal motion like a Scotchoke mechanism, the axial movement of the male type 15 and first female type 16 at the Kuralev rotation angle ω( The quantity is expressed by the following formula.

S,, = R, (1-cosωt) - (7) S,
,=R. (1-cos ω t ) --(8
) However, R1 is the crank radius of the male type 15, and Ro is the crank radius of the first female type 16.

Therefore, Tona'J, (expressed as 6 + 2) Since the composite torsion angle θ is also constant regardless of the crank rotation angle ω, the male type 1
The vertical movement and rotational movement of 5 remain constant at any stroke position. As a result, highly accurate helical gears can be machined.

By the way, when the male type 15 and the first female type 16 are driven by a crank system with a connecting rod, the length of the connecting rod is 11 crank radius/l ^
Then, S,,=Rjl-cosωt)+1' (1
("Co n'ut) - side So, = R0 (1-cos
ωt)+1(1-1-1"sin"eat) ・-(
■11 Therefore, S,,l, R,, (1-cosωt)+f' (1-
1-A'sin"ut), that is, l(1-1-A"s
im'; t) becomes a factor in the variation of the helix angle, and the male shape 1
The composite helix angle θ of No. 5 varies depending on the rotation angle of the crank, making it impossible to accurately machine a gear having a constant helix angle. In the case of Scotchoke@horizontal as in this embodiment, (field (11) equation) (where there is no stove top, (ko!) = 0, and θ is constant as expressed by equation (9).

According to the i structure described above, the male type 15 and the first female type 16
By arbitrarily setting the amount of relative displacement rjJ and the speed, it is possible to obtain an arbitrary helical angle. In addition, since a Scotchoke type mechanism is used as the vertical drive mechanism for the male type 15 and the first female type 16, the ratio of the amount of movement of the male type 15 and the first female type 16 to the crank rotation angle is always constant, and the The vertical movement and rotational movement of the shape 15 are constant at any stroke position. Therefore, highly accurate helical gears can be machined.

<Effects of the Invention> The gear shaver of the present invention has a stepless i! The J-aligned helical guide mechanism can adjust the helical angle steplessly and accurately to 1lsJl regardless of the movement speed of the spindle, so multiple countersunk helical gears with different helical angles can be processed without changing setups. It becomes possible. As a result, restrictions on the design of helical gears are reduced, machining setup changes and time are shortened, and production efficiency can be improved.

[Brief explanation of the drawing]

FIG. 1 is a vertical cross-sectional view of a stepless adjustment helical guide mechanism of a gear shaper according to an embodiment of the present invention, FIG. 2 is a view taken along arrows II-]Ii in FIG. 1, and FIG. Figure 4 is a conceptual perspective view of the drive mechanism, Figure 5 is a graph showing the relationship between crank diameter and torsion angle, and Figure 6 is a graph showing the torsion angle of the male type. Figure 7 is a conceptual diagram to explain the helix angle of the first female type, Figure 8 is a conceptual diagram to explain the composite helix angle of the male type, and Figure 9 is a longitudinal cross section of the conventional helical guide mechanism. 10 is a perspective view of the male type of the helical guide, FIG. 11 is an explanatory diagram showing the relationship between the specifications of the cutter and the lead of the helical guide, and FIG. 12 is a perspective view of the male type of the helical guide.
1 is a view from P in FIG. 1. In the drawing, 11 is a main shaft, 15 is a male type, 15a is a first helical convex part, 16 is a first female type, 16a is a first helical concave part, 17 is a second female type, 17a is a second helical concave part 1 25 is a first crankshaft, and 43 is a second crankshaft. Patent applicant: Mitsubishi Heavy Industries, Ltd.

Claims (1)

[Claims] A main shaft that can reciprocate in the axial direction and rotate around the axis,
a male shape in which a first helical convex portion is connected or integrated with the main shaft and has a lead and direction corresponding to an arbitrary twist angle, and a first helical concave portion that fits into the first helical convex portion of the male shape; a first female shape having an inner periphery and a second helical protrusion having the same or different lead and direction as the first helical protrusion on the outer periphery; and a second helical protrusion of the first female shape. a second female type that has a second helical recess that fits together and is driven and rotated, a first crank mechanism that reciprocates the male type in the axial direction together with the main shaft by rotation of the first crankshaft, and the male type. and a second crank mechanism that provides a relative reciprocating motion synchronized with the phase of 0 degrees or 180 degrees between the first female type and the second crank mechanism by rotation of a second crankshaft that rotates in synchronization with the first crankshaft. Step adjustment helical guide mechanism.