JP5276358B2 - Hypoid gear analysis system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an analysis system of a hypoid gear capable of easily adjusting data for providing a desired gear tooth contact state. <P>SOLUTION: A calculation section 6 sets a virtual gear 101iG obtained by adjusting design data of a gear 101G with adjustment dimensions when the relative position of a cutter head 230 to a pinion work 110P is set, calculates the virtual relative position of the cutter head 230 on the assumption that the gear tooth of the virtual work 110iG is formed according to data of the virtual gear 101iG and the set dimensions of the cutter head 230, adjusts the virtual relative position using a second adjustment dimension with reference to the pitch point P of the virtual gear 101iG, and calculates the relative position of the cutter head 230 when a pinion gear tooth 102P is generated in the pinion work 110P according to virtual assembling dimensions of the virtual gear 101iG and a pinion 101P and the adjusted virtual relative position. <P>COPYRIGHT: (C)2010,JPO&amp;INPIT

Description

  The present invention relates to a hypoid gear analysis system that analyzes a hypoid gear based on a relative relationship between a workpiece and a cutter head when processing the hypoid gear.

  Conventionally, as hypoid gears, hypoid gears with tooth surfaces processed on each gear (gear and pinion) by face mill type tooth surface processing that rotates the cutter head while the workpiece is fixed, and the workpiece and cutter head rotate simultaneously. Hypoid gears in which the tooth surfaces of each gear are processed by face hob type tooth surface processing are widely known.

  In recent years, with respect to hypoid gears that are processed with a face mill system, many studies have been conducted on a method for setting an appropriate control parameter for a processing machine, a method for analyzing a processed tooth surface, and the like.

  On the other hand, for hypoid gears that are machined using the face hob method, the most basic method for setting the relative position between each workpiece and the cutter head is fully established when setting various control parameters for the processing machine. The fact was not.

In response to this, for example, in Patent Document 1, control parameters for forming a gear with a processing machine are set based on the design specifications of the gear, while the gear design specifications include a tooth contact adjustment dimension (gear The virtual gear is set by reflecting the adjustment amount with respect to the pitch cone angle, the adjustment amount with respect to the torsion angle of the gear, and the ratio of the tooth contact width to the gear tooth width, and the relative position between the virtual gear work and the cutter head, and A technique for setting control parameters when generating a pinion with a processing machine based on an assembly dimension of a virtual gear and a pinion is disclosed. Furthermore, in the technique disclosed in Patent Document 1, a crowning correction amount or the like in the tooth trace direction can be set as the tooth contact adjustment dimension, and each set value on the processing machine can be set based on the crowning correction amount or the like. (For example, coordinate axes such as swivel angle and tilt angle on the processing machine) are finely adjusted.
JP 2007-185760 A

  However, in the technique disclosed in Patent Document 1 described above, each coordinate axis and the like on the processing machine to be adjusted has a small direct correspondence with the dimension of the hypoid gear, and therefore, based on the correction amount of these processing machine settings, It is difficult to imagine a change in the contact state of the tooth surface.

  In addition, fine adjustment of each coordinate axis on the processing machine results in indirectly changing the assembly dimensions of the virtual gear and the pinion (cutter head). As a result, the tooth height of the pinion to be created is reduced. There is a risk that a pinion with low utility will be processed, for example, the amount of cutting will be insufficient due to the change.

  For this reason, with the technique disclosed in Patent Document 1 described above, it is difficult to intuitively set the optimum tooth contact adjustment dimension, and this setting requires skill.

  The present invention has been made in view of the above circumstances, and an object thereof is to provide a hypoid gear analysis system capable of easily realizing specification adjustment for obtaining a desired tooth surface contact state.

In the hypoid gear analysis system according to one aspect of the present invention , the tooth surface of the first gear, which is one gear, is molded into the first workpiece by rotating the face hob type cutter head, and the other gear is used. And a hypoid gear analysis system in which a tooth surface of a second gear is created on a second workpiece, based on the design specifications of the first gear and the set dimensions of the cutter head. calculates the relative position of the cutter head relative to the workpiece, a first tooth surface calculation means for calculating the tooth surface of the first gear to be molded by the cutter head on the basis of the relative position, the generating process first tone adjusting that the second of said first of said design virtual gear design specifications that are set on the basis of the specifications of the gear as a virtual gear having a tooth surface conjugate tooth surface of the gear Dimensions and the design specifications and the setting dimensions and the pitch point or in the vicinity of the cutter head the virtual gear the slope of which is arranged for the virtual work of the virtual gear based on the cutter head of the virtual gear input means for inputting a second adjustment dimension adjustment as the reference points, of the virtual gear on the basis of the specifications and the second adjusting dimensions of the virtual gear and the set size of the cutter head Virtual relative position calculation means for calculating a virtual relative position of the cutter head with respect to the virtual workpiece when it is assumed that a tooth surface is formed on the virtual workpiece, specifications of the virtual gear , and design specifications of the second gear a virtual assembly dimension calculating means for calculating a virtual assembly dimension between the second gear and the virtual gear based on the bets, the second workpiece based on said virtual relative positions and said virtual assembly dimensions A second tooth surface calculating means for calculating a relative position of the cutter head and calculating a tooth surface of the second gear created by the cutter head based on the relative position; and the first tooth Tooth surface contact analyzing means for analyzing the contact state between the tooth surface of the first gear calculated by the surface calculating means and the tooth surface of the second gear calculated by the second tooth surface calculating means. It is a thing.

  According to the hypoid gear analysis system of the present invention, specification adjustment for obtaining a desired tooth surface contact state can be easily realized.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a perspective view of a hypoid gear, FIG. 2 is a perspective view showing an example of a face hob type cutter head, FIG. 3 is a schematic configuration diagram of a hypoid gear analysis system, and FIG. 4 is a hypoid gear. FIG. 5 is a flowchart showing a hypoid gear analysis routine, FIG. 6 is an explanatory diagram showing an example of an input screen, and FIG. 7 is a diagram showing the relative relationship between the cutter head and the gear work. FIG. 8 is an explanatory diagram showing the relative position of the cutter head relative to the pinion work calculated based on the relative position of the cutter head relative to the gear work and the assembly dimensions, and FIG. 9 is an example of the tilt adjustment axis of the cutter head. 10 to 18 are explanatory diagrams showing the relationship between the adjustment dimension and the change in ease-off. 9 through FIG. 23 is an explanatory view showing a display example of the adjustment dimension and the tooth surface contact analysis results, Figure 24 is a chart showing an example of the basic dimensions used in tooth surface contact analysis of FIGS. 19 to 23.

  In FIG. 1, reference numeral 100 denotes a hypoid gear. The hypoid gear 100 is, for example, one gear (hereinafter also referred to as a gear or a crown) 101G having a large diameter and the other gear (hereinafter also referred to as a pinion) having a small diameter. 101P meshes with each other. In the present embodiment, the tooth surfaces of the gear 101G and the pinion 101P are processed using, for example, a face hob type cutter head 230 shown in FIG. 2, and specifically, the tooth surfaces 102G (convex) of the gear 101G. The tooth surface 102Ga and the concave tooth surface 102Gb) are molded using the cutter head 230, and the tooth surface 102P (the convex tooth surface 102Pa and the concave tooth surface 102Pb) of the pinion 101P is formed using the cutter head 230. That is, in this embodiment, the gear 101G corresponds to the first gear, and the pinion 101P corresponds to the second gear.

  As shown in FIG. 2, in the present embodiment, the face hob type cutter head 230 has a disc-shaped cutter body 231. An attachment hole 232 for fixing the cutter head 230 to a processing machine (not shown) is provided at the center of the cutter body 231.

Further, one end surface of the cutter body 231 is configured as a surface (Cutter head Surface) 233 of cutter head 230, a point away set distance from the head surface 233 on the head axis Z _C direction, the reference point of the cutter head 230 (the origin O _C) is set as. Here, the axial distance from the head surface 233 of cutter head 230 to the origin O _C is one in which are unique to the cutter head 230, it is desirable to be set on the basis of the design specifications of the hypoid gear 100 In this embodiment, a value obtained by appropriately adding a clearance to the half value of the effective tooth height h of the hypoid gear 100 is set.

Further, a plurality of blades 240 including a concave tooth surface processing blade 240 o and a convex tooth surface processing blade 240 i are projected from the head surface 233. Here, each blade 240o, 240i is detachably inserted and fixed in a blade fixing hole (not shown) formed in the cutter body 231. At that time, each blade 240O, 240i, for example, an edge formed at the tip, the reference plane of the cutter head 230 (the origin _{O C} through the head surface 233 parallel to the plane; reference plane) to set the amount projected from the position Fixed to. As described above, in this embodiment the axial distance is set to half the effective tooth height h of the hypoid gear 100 from the head surface 233 of cutter head 230 to the origin O _C, the amount of protrusion is the hypoid gear 100 It is set to a value b (= (h / 2) + c: blade dedendum) obtained by adding the clearance c to the half value (h / 2) of the effective tooth height h.

  The analysis system 1 for analyzing the hypoid gear 100 processed by such a cutter head 230 inputs design specifications of the hypoid gear 100, set dimensions of the cutter head 230, tooth contact adjustment dimensions, and the like, as shown in FIG. An input unit 5 as an input means, a calculation unit 6 that performs various calculations such as contact analysis of the tooth surfaces 102G and 102P of the gear 101G and the pinion 101P processed by the cutter head 230, and these tooth surfaces, and a calculation unit 6 The storage unit 7 stores various programs to be executed, and appropriately stores input information from the input unit 5, and includes an output unit 8 that outputs calculation results and the like in the calculation unit 6. .

  The storage unit 7 of the analysis system 1 stores a program for analyzing the tooth surfaces processed on the workpieces 110G and 110P of the gear 101G and the pinion 101P using the cutter head 230 described above. By executing this program, the calculation unit 6 serves as first tooth surface calculation means, virtual relative position calculation means, virtual assembly dimension calculation means, second tooth surface calculation means, and tooth surface contact analysis means. Implement each function.

  In addition, the analysis system 1 of this embodiment is implement | achieved by the computer system 10 shown in FIG. 4, for example. The computer system 10 includes, for example, a computer main body 11, a keyboard 12, a display device 13, and a printer 14 that are connected via a cable 15 to constitute a main part. In the computer system 10, for example, various drive devices, a keyboard 12, and the like arranged in the computer main body 11 function as the input unit 5, and a CPU, ROM, RAM, and the like built in the computer main body 11 are arithmetic units. Function as. In addition, the display device 13, the printer 14, and the like function as the output unit 8 while functioning as a hard disk or the like built in the computer main body 11 or the storage unit 7.

  Next, the hypoid gear analysis processing executed by the calculation unit 6 will be described with reference to the flowchart of the hypoid gear analysis routine shown in FIG. When this routine starts, the calculation unit 6 first takes in various specifications such as the set dimensions of the cutter head 230, the design specifications of the hypoid gear 100, and the tooth contact adjustment dimensions in step S101. Specifically, for example, the calculation unit 6 displays an input screen of various specifications (see FIG. 6A) through the output unit 8 such as the display device 13, and the input of the keyboard 12 or the like is input on the input screen. The specifications entered through part 5 are read.

Here, in the present embodiment, the analysis system 1 includes the set dimensions of the cutter head 230 (and the blade 240) as, for example,
S _r : slot radius
S _o : slot offset
C _ht : cutter head thickness
λ _s : blade slot tilt angle
γ _s : blade side rake angle
b _fw : blade flat width
b _t : blade thickness
b _w: blade width
ν: Gear cutter lead angle r _C : Cutter radius N _B : The number of blade groups and the like are input.

In addition, the analysis system 1 includes, as design specifications of the hypoid gear 100 (gear 101G and pinion 101P),
ψ _G , ψ _P : Spiral angle
Γ _G , Γ _P : Cone angle
_RG , _RP : pitch point radius (P-point radius)
Etc. are input. These specifications are typical dimensions called three elements of so-called gear 101G and pinion 101P. The calculation unit 6 is based on these three elements as other design specifications of the gear 101G and the pinion 101P, for example,
Z _G , Z _P : Pitch point distance (P-point distance)
ε, η: Offset angle
Is uniquely calculated. Furthermore, the calculation part 6 is as an assembly specification based on the design specification of the gear 101G and the design specification of the pinion 101P, for example,
m: Gear ratio
Σ: Shaft angle
Ε: Offset amount
Is uniquely calculated.

Further, in the analysis system 1, as dimensions (first adjustment dimensions) for setting (adjusting) the specifications of the virtual gear (virtual gear) 101iG based on the design specifications of the gear 101G, for example,
Δψ _G : Twist angle adjustment dimension ΔΓ _G : Cone angle adjustment dimension ΔR _G : Pitch point radius adjustment dimension is input.

  Here, the virtual gear 101iG is a virtual gear set to adjust the arrangement of the cutter head 230 with respect to the pinion work 110P at the time of tooth surface generation, and its specifications are based on the three elements of the gear 101G. , Is set by reflecting each of the adjustment dimensions described above.

That is, the arrangement of the cutter head 230 when generating the pinion tooth surfaces 102Pa and 102Pb on the pinion work 110P is basically the arrangement of the cutter head 230 when forming the gear tooth surfaces 102Ga and 102Gb on the gear work 110G. And the assembly position of the gear 101G and the pinion 101P can be set. However, the pinion tooth surfaces 102Pa and 102Pb obtained by such an arrangement become conjugate tooth surfaces and “stickiness” with respect to the gear tooth surfaces 102Ga and 102Gb, so that it is not practical and requires some tooth surface adjustment. Therefore, in the present embodiment, as will be described later, the first adjustment dimensions (ΔΨ _G , ΔΓ _G , ΔR _G ) are reflected on the design specifications (ψ _G , Γ _G , R _G ) of the gear 101G. Based on the arrangement of the cutter head 230 with respect to the workpiece (virtual workpiece) 110iG and the assembly position of the virtual gear 101iG and the pinion 101P when the virtual gear 101iG is set and the tooth surface is assumed to be formed on the virtual gear 101iG. Thus, by setting the arrangement of the cutter head 230 with respect to the pinion work 110P, the tooth surface correction with respect to the pinion 101P is performed.

  Further, in order to perform further tooth surface correction on the pinion 101P through the virtual gear 101iG without changing the assembly state of the virtual gear 101iG and the pinion 101P, the analysis system 1 includes the second adjustment dimension in addition to the second adjustment dimension. The adjustment dimension is input. This second adjustment dimension directly determines the relative position (virtual relative position) of the cutter head 230 set with respect to the virtual workpiece 110iG when it is assumed that the tooth surface is formed on the virtual workpiece 110iG of the virtual gear 101iG. It is mainly composed of various dimensions for adjusting to the above.

In the present embodiment, as the second adjustment dimension, for example, a dimension (angle) for tilting the cutter head 230 around three axes with reference to the pitch point P (Ppoint) of the virtual gear 101iG is input. Specifically, for example, in the arrangement relationship between the virtual workpiece 110iG and the cutter head 230 at the time of tooth surface molding, the cutter head 230 is set around the α axis that passes through the pitch point P and is set in the generatrix direction of the pitch cone of the virtual gear. An angle θ _α for tilting is input as the second adjustment dimension. Further, a mu axis toward the origin O _C of the cutter head 230 from the pitch point P, and κ axis passing through the pitch point P on the tangent plane of the pitch cone perpendicular to the mu-axis and the virtual workpiece 110IG, mu axis and In an orthogonal coordinate system composed of ι axes orthogonal to the κ axis, angles θ _κ and θ _ι for tilting the cutter head 230 about the κ axis and about the ι axis are input as second adjustment dimensions. In FIG. 9, each axis (α axis, μ axis, κ axis, and ι axis) viewed from the virtual gear 101iG side is expressed on a pinion 101P that meshes with the virtual gear 101iG.

Further, as another adjustment dimension, for example, the dimensions for adjusting the cutter radius r _C (cutter radius correction amount) with [Delta] r _C is input, adjust the gear ratio m that is used as a parameter when the tooth surface generating process A correction amount (gear ratio correction amount) Δm, a blade pressure angle, and the like are input.

  When the process proceeds from step S101 to step S102, the calculation unit 6 calculates the relative position of the cutter head 230 with respect to the gear work 110G based on the design specifications of the gear 101G and the set dimensions of the cutter head 230, and based on this relative position. Then, the tooth surfaces 102Ga and 102Gb of the gear 101G formed by the cutter head 230 are calculated.

Here, in order to simplify the description, the origin O _C pitch point P of the gear 101G on the reference plane passing through the cutter head 230 is assumed to exist, to the setting dimensions of the design specifications and the cutter head 230 of the gear 101G Based on this, for example, the relationship shown in FIG. 7 can be derived as the relative position of the cutter head 230 with respect to the gear work 110G when the gear tooth surface 102G is molded. In other words, as the relative position of the cutter head 230 for Giyawaku 110G, reference plane of the cutter head 230 matches the tangent plane C of the pitch cone Giyawaku 110G, and the origin _{O C} of the cutter head 230, passes through the pitch point P from line of intersection between the tangent plane C perpendicular plane B to the gear axis Z _G, position rotated moved [psi _G -v along tangent plane C around the pitch point P is derived.

Based on such a relationship, the coordinates on the blade represented by the coordinate system X _C -Y _C -Z _C of the cutter head 230 are expressed by the determinant shown in the following formula (1) of the gear work 110G (gear 101G). The coordinate system can be converted to X _G -Y _G -Z _G. That is, if the matrix is expressed as [M],
[M] _GC = [M] _{RZ ((N B / N G} ) ω C) [M] _{TZ (Z P)} [M] _{TX (R} G)
[M] _RY (Γ _G −90 °) [M] _RZ (ψ _G −ν) [M] _TZ (d)
[M] _TY (r _C ) [M] _RZ (ω _C −90 °) (1)
In equation (1), [M] _GC is a matrix indicating the coordinates on the blade converted from the coordinate system of the cutter head 230 to the coordinate system of the gear work 110G. For example, [M] _RZ ((N _B / _NG ) ω _C ) represents the rotation (Rotate about Z) of (N _B / _NG ) ω _C around the Z axis, and [M] _TX (R _G ) Represents _RG movement (Translate along X) in the X-axis direction. Further, ω _C represents the rotation angle of the cutter head 230.

Since the gear tooth surface 102G is a molded tooth surface, the rotation angle ω _C of the cutter head 230 is changed in the equation (1), and the locus of the point on the blade of the cutter head 230 is expressed in the coordinate system of the gear work 110G. By tracing, it is possible to calculate the shape of the gear tooth surface 102G formed on the gear work 110G.

When the process proceeds from step S102 to step S103, the calculation unit 6 calculates the specifications of the virtual gear 101iG based on the design specifications of the gear 101G and the first adjustment dimension. That is, the calculation unit 6 reflects the first adjustment dimension on the three elements of the gear 101G, so that, for example, as the three elements of the virtual gear 101iG,
ψ _iG (= ψ _G + Δψ _G ): Spiral angle
Γ _iG (= Γ _G + ΔΓ _G ): Cone angle
R _iG (= R _G + ΔR _G : Pitch radius)
Based on these three factors, for example,
Z _iG : Pitch distance (P-point distance)
ε _i : Offset angle
Is uniquely calculated.

In step S104, the calculation unit 6 also performs adjustment based on the first adjustment dimension for the design specifications of the pinion 101P that meshes with the virtual gear 101iG.
Z _iP : P-point distance
η _i : Offset angle
Is calculated. Further, based on the specifications of the virtual gear 101iG and the design specifications of the pinion 101P, the calculation unit 6 can be used as these virtual assembly specifications (virtual assembly dimensions), for example:
m _i : Gear ratio
Σ _i : Shaft angle
Ε: Offset amount
Is calculated.

  When proceeding from step S103 to step S104, the calculation unit 6 determines the virtual of the cutter head 230 with respect to the virtual workpiece 110iG based on the specifications of the virtual gear 101iG, the second adjustment dimension, and the set dimension of the cutter head 230. The relative position (virtual relative position) is calculated.

Specifically, the arithmetic unit 6 firstly has the same relationship as shown in FIG. 7 as the relative position of the cutter head 230 with respect to the virtual workpiece 110iG based on the specifications of the virtual gear 101iG and the set dimensions of the cutter head 230. Derive relationships. Further, the calculation unit 6 determines the inclination of the cutter head 230 based on the angles θ _α , θ _κ , and θ _ι set as the second adjustment dimensions with respect to the pitch point P on the virtual work 110 iG. Adjust around (α, κ, and ι axes). Further, by adjusting in pitch point P relative to the cutter radius r _C based on the dimension [Delta] r _C, the origin O _C of the cutter head 230 is moved in the μ axially relative to the pitch point P.

Based on the virtual relative position of the cutter head 230 with respect to the virtual workpiece 110iG obtained by adding the second adjustment dimension in this way, the calculation unit 6 calculates the coordinates on the blade expressed in the coordinate system of the cutter head 230. The following equation (2) is set as a coordinate transformation equation for transforming to the coordinate system of the virtual work 110iG (virtual gear 101iG).
[M] _iGC = [M] _RZ ((N _B / N _iG ) ω _C ) [M] _TZ (Z _iP ) [M] _TX (R _iG )
[M] _RY (Γ _iG + θ _α −90 °) [M] _RZ (Ψ _iG −ν + θ _ι ) [M] _TZ (d _P )
[M] _TX (−θ _κ ) [M] _TY (r _C + Δr _C ) [M] _RZ (ω _C −90 °)
(2)
In equation (2), [M] _iGC is a matrix indicating the coordinates on the blade converted from the coordinate system of the cutter head 230 to the coordinate system of the virtual gearwork. When the adjustment dimensions θ _α , θ _κ , θ _ι , and Δr _C are zero, equation (2) is equal to equation (1), and [M] _iGC = [M] _GC .

When the process proceeds from step S104 to step S105, the calculation unit 6 determines the coordinates defined in the coordinate system of the virtual gear 101iG (virtual work 110iG) based on the virtual assembly dimensions of the virtual gear 101iG and the pinion 101P calculated in step S103. Is set to a coordinate conversion formula for converting into a coordinate in the coordinate system of the pinion 101P (pinion work 110P). In the present embodiment, this conversion formula is set in consideration of the gear ratio correction amount Δm and the change in the axial distance of the pitch point P of the pinion 101P, and specifically, for example, the following formula (3) Is set.
[M] _PIG = [M] _{TZ (Z} G _{-Z iG)} [M] _{RZ ((m i + Δm)} ω G -η i -180 °)
[M] _TY (−E _i ) [M] _RY (−Σ _i ) [M] _RZ (ε _i + ω _G ) (3)
Here, in equation (3), ω _G represents the rotation angle of the gear 101G (virtual gear 101iG).

  When the process proceeds from step S105 to step S106, the calculation unit 6 calculates the relative position of the cutter head 230 with respect to the pinion work 110P when the pinion tooth surface 102P is generated, and the cutter head 230 performs the generation process based on this relative position. The tooth surfaces 102Pa and 102Pb of the pinion 101P are calculated.

Here, the relative position of the cutter head 230 with respect to the pinion work 110P is the virtual relative position of the cutter head 230 with respect to the virtual work 110iG, and the virtual assembly dimensions of the virtual work 110iG (virtual gear 101iG) and the pinion work 110P (pinion 101P). (See FIG. 8). That is, the relative position of the cutter head 230 with respect to the pinion work 110P is the same as the pitch cone of the virtual work 110iG and the pitch cone of the pinion work 110P with respect to the orientation of the blade on the cutter head 230 arranged with respect to the virtual work 110iG. It is determined at a position where the tangent plane is reversed as a symmetry plane. Such a relationship can be expressed by, for example, the above-described equations (2) and (3). Specifically, the calculation unit 6 is represented by the coordinate system X _C -Y _C -Z _C of the cutter head 230. coordinates on the represented blades, as the determinant for transforming the coordinate system _{X P -Y} P -Z P pinions work 110P (gear 101G), calculating the following equation (4).
[M] _PC = [M] _PiG [M] _iGC (4)
In Equation (4), [M] _PC is a matrix indicating the coordinates on the blade converted from the coordinate system of the cutter head 230 to the coordinate system of the pinion work 110P.

Since the pinion tooth surface 102P is a generating tooth surface, in the equation (4), the rotation angle ω of the cutter head 230 and the rotation angle ω _G of the gear 101G are changed, and the cutter head 230 in the coordinate system of the pinion work 110P is changed. By following the locus of points on the blade, the shape of the pinion tooth surface 102P created on the pinion work 110 can be calculated.

  When the process proceeds from step S106 to step S107, the calculation unit 6 performs a tooth surface contact analysis on the meshing between the gear tooth surface 102G calculated in step S101 and the pinion tooth surface 102P calculated in step S106.

  That is, the calculation unit 6 arranges the gear 101G and the pinion 101P based on the assembly specifications (m, Σ, and Ε) calculated in step S101, and the above gear tooth surface 102G and the pinion tooth surface 102P on this arrangement. Tooth contact analysis is performed. And the calculating part 6 calculates an ease-off and a motion curve as information showing the contact state of the gear tooth surface 102G and the pinion tooth surface 102P, for example.

  When the process proceeds from step S107 to step S108, the calculation unit 6 displays the result of the tooth surface contact analysis performed in step S107, together with various adjustment dimensions, through the output unit 8 such as the display device 13. That is, for example, as shown in FIG. 19A to FIG. 23B, the calculation unit 6 includes a convex convex surface (Crown convex flank) 102Ga of the gear 101G and a concave concave surface (Pinion concave flank) 102Pb of the pinion. Tooth surface contact analysis result (Ease off and motion curve), and tooth surface contact analysis result (Ease off and motion) between the concave tooth surface 102Gb of the gear 101G and the pinion concave surface 102Pb (Pinion convex flank) 102Pa Curve) is displayed together with various adjustment dimensions, the outer shape of the hypoid gear 100, and the like.

  When the process proceeds from step S108 to step S109, the calculation unit 6 checks whether a change request from the user has been made.

  If it is determined in step S109 that a change request from the user has been made, the calculation unit 6 proceeds to step S110, and for example, an adjustment dimension input screen (see FIG. 10) through the output unit 8 such as the display device 13 or the like. 6 (b)) is displayed, and the tooth contact adjustment dimension input through the input unit 5 such as the keyboard 12 is read, and then the process returns to step S103.

  On the other hand, if it is determined in step S109 that a change request from the user has not been made, the arithmetic unit 6 proceeds to step S111 and checks whether or not the user has instructed the end of the analysis process.

  If it is determined in step S111 that the user has not given an end instruction, the calculation unit 6 returns to step S109.

  On the other hand, when it is determined in step S111 that the user has instructed termination, the calculation unit 6 directly exits the routine.

  Each cutter arrangement model for the gear work 110G and the pinion work 110P set by the above-described processing is converted into an arrangement (processing machine setting) on an actual processing machine, and the hypoid gear 100 (gear 101G and pinion 101P) is converted. Of course, gear cutting can be realized.

  Next, the relationship between each adjustment dimension adjusted by such an analyzer and the change in ease-off (change in ease-off maximum convex point position) obtained by this adjustment dimension will be described with reference to FIGS. 10 to 18. To do. 10 to 18, the left side shows the convex tooth surface 102Ga of the gear 101G, and the right side shows the concave tooth surface 102Gb of the gear 101G. In these tooth surfaces 102Ga and 102Gb, the left and right central sides are the toe side, and the lower side is the toe side. The root side. Moreover, the change when ± each adjustment dimension is shown is shown in the upper stage (a) and the lower stage (b), respectively.

FIG. 10 shows the effect when the angle θ _α around the α axis input as the second adjustment dimension is adjusted. This angle θ _α is a dimension for pitch cone adjustment, and if the angle θ _α is changed, if the most convex point position (tooth contact position) moves to the toe side on the convex tooth surface 102Ga of the gear 101G, The most convex point position moves to the toe side also on the concave tooth surface 102Gb side. That is, when correcting the cone angle at which the groove on the toe side becomes shallow, the groove width on the toe side is narrowed by the action of the blade pressure angle. Therefore, the most convex point position moves to the toe side.

Figure 11 shows the effect of adjusting the angle theta _kappa of kappa around an axis which is input as a second adjustment dimension. By adjusting the angle theta _kappa, most convex point position on the convex tooth surface 102Ga of the gear 101G is if moved to the tooth bottom side, on the concave tooth surface 102Gb Saitotsu point position is moved to the tooth tip side. Thus, it can be seen that the tooth surface 102P of the pinion 101P is a generating tooth surface, but the apparent pressure angle due to the inclination of the cutter head 230 is reflected in the change in tooth contact.

Figure 12 shows at the same time as the adjustment of the angle theta _kappa around kappa axis is inputted as a second adjusting dimensions, by changing the blade pressure angle, the effect of canceling the teeth per movement due to the inclination of the cutter head 230 . By such adjustment, it can be seen that crowning occurs on the convex tooth surface 102Ga and the concave tooth surface 102Gb. This is because when the cutter head 230 is rotated around the κ axis, the blade tip depth does not change much in the vicinity of the pitch point P, but becomes shallower at both ends of the tooth width, and the tooth pressure is reduced by the action of the blade pressure angle. This is because the width becomes narrower or deepens and spreads.

FIG. 13 shows the effect when the angle _θι around the ι axis that is input as the second adjustment dimension is adjusted. By adjusting the angle theta _iota, if the mobile lowest projected point position to the heel side on the convex tooth surface 102Ga of the gear 101G, than on the concave tooth surface 102Gb Saitotsu point position is moved to the toe side.

Although not shown, if the cutter radius correction amount Δr _C is adjusted, when the crowning in the tooth trace direction is increased on the convex tooth surface 102Ga side, the crowning in the tooth trace direction is reduced on the concave tooth surface 102Gb side.

Figure 14 shows the effect of adjusting the twist angle adjusting dimension [Delta] [phi] _G inputted as first adjustment dimension. By adjusting the twist angle adjusting size [Delta] [phi] _G, it can be seen that can change the crowning tooth depth direction of the concave tooth surface 102Gb side without much change teeth per convex tooth surface 102Ga side. In order to facilitate understanding of the effect of the adjustment dimensions on the three elements, in FIG. 14 (including FIGS. 15 and 16 described below), the cutter head 230 is arranged so that the ease-off maximum convex point is at the center of the tooth surface. This is a combination of changes in inclination and the like (second adjustment dimension).

Figure 15 shows the effect of adjusting the cone angle adjustment dimension [Delta] [gamma] _G inputted as first adjustment dimension. By adjusting the cone angle adjusting size [Delta] [gamma] _G, when the crowning tooth depth direction of convex tooth surface 102Ga side is increased, at the same time, it can be seen that the crowning of the tooth depth direction is larger in the concave tooth surface 102Gb side.

Figure 16 shows the effect of adjusting the pitch point radius adjustment dimension [Delta] R _G inputted as first adjustment dimension. By adjusting the pitch point radius adjustment dimension [Delta] R _G, it varies the crowning tooth depth direction as in the case of cone angle adjusting size [Delta] [gamma] _G, it can be seen that rotation of the principal axis direction occurs in conjunction.

  FIG. 17 shows the effect when the gear ratio correction amount Δm is adjusted. By adjusting the gear ratio correction amount Δm, when the most convex point position moves to the tooth tip side on the convex tooth surface 102Ga, the most convex point position also moves to the tooth tip side on the concave tooth surface 102Gb. I understand.

  Here, as described above, even if the three elements of the virtual gear 101iG are changed according to the first adjustment dimension, the three elements of the pinion 101P do not change, so that the tooth bottom and the tooth are between the gear 101G and the pinion 101P. Interference due to previous clearance changes does not occur.

  FIG. 18 shows the effect when the tooth contact movement is canceled by changing the blade pressure angle simultaneously with the adjustment of the gear ratio correction amount Δm. It can be seen that by such adjustment, the crowning on the convex tooth surface 102Ga side changes greatly compared to the concave tooth surface 102Gb side.

  From this relationship, the convex tooth surface 102Ga and the concave tooth surface 102Gb of the gear 101G are simultaneously molded by the cutter head 230, and the convex tooth surfaces 102Pa and 102Pb of the pinion 101P are simultaneously created by the cutter head 230. Also in the hypoid gear 100 of the form, it is possible to easily perform arbitrary tooth contact adjustment.

  For example, the movement of the most convex point position per tooth in the tooth height direction can be realized by adding the adjustments shown in FIGS. 11 and 17 to an appropriate size. In addition, for example, the movement of the most convex point position per tooth to an arbitrary position in the tooth width direction can be realized by adding the adjustments shown in FIGS. 10 and 13 to an appropriate size. .

Further, for example, when the crowning in the tooth height direction is arbitrarily adjusted, the adjustment shown in FIG. 14 in which the concave tooth surface 102Gb side greatly changes and the adjustment shown in FIG. 18 in which the convex tooth surface 102Ga side changes greatly are appropriately This can be realized by taking into account the adjustment shown in FIG. For example, when the crowning in the tooth trace direction is arbitrarily adjusted, the adjustment shown in FIG. 12 that changes in the same direction on the convex tooth surface 102Ga and the concave tooth surface 102Gb, and the adjustment of Δr _C that changes in the opposite direction, Can be realized by adding them in an appropriate size.

  Here, the relationship between each adjustment dimension and the tooth contact position shown in FIGS. 10 to 18 and the like can be appropriately displayed simultaneously with the adjustment dimension input screen in step S110 of the analysis routine described above.

  Next, based on the dimensions shown in FIG. 24, any one of the dimensions is changed, and each adjustment dimension is optimized using the analysis system 1 described above, with the goal of spherical ease-off in which the crown rotation angle transmission error is 40 μradians. FIG. 19 to FIG. 23 show the analysis results when it is realized.

  FIGS. 19A and 19B show an example when the cutter dimensions are changed. It was confirmed that even with such a change, the ease-off and motion curves can be substantially the same.

  FIGS. 20A and 20B show an example when the offset is changed. In this case, the twist angle and the diameter of the pinion 101P are larger when the offset is larger. Although the appearance shape of the pinion 101P is greatly different, it was confirmed that the same ease-off and motion curve can be obtained in any case.

  FIGS. 21A and 21B show an example when the shaft angle is changed. It was confirmed that even with such a change, the ease-off and motion curves can be substantially the same.

  FIGS. 22A and 22B show an example when the gear ratio is changed. If the gear ratio is small, the diameter of the pinion 101P is large and the cone angle of the gear 101G is small. It was confirmed that the same ease-off and motion curve can be obtained in both cases, although the shapes of the appearances are greatly different.

  FIGS. 23A and 23B show an example when the twist angle is changed. When the twist angle is small, the ease-off of slightly stronger crowning in the tooth height direction is achieved, but it has been confirmed that almost the target ease-off can be obtained in any case.

  According to such an embodiment, when setting the relative position of the cutter head 230 with respect to the pinion work 110P, the virtual gear 101iG obtained by adjusting the design specifications of the gear 101G with the first adjustment dimension is set, and the virtual gear 101iG is set. The virtual relative position of the cutter head 230 when the tooth surface is assumed to be formed on the virtual workpiece 110iG based on the specifications of the cutter head 230 and the set dimensions of the cutter head 230 is calculated, and the virtual relative position is calculated using the second adjustment dimension. Cutter for generating a pinion tooth surface 102P on the pinion work 110P based on the virtual assembly dimension of the virtual gear 101iG and the pinion 101P and the adjusted virtual relative position, with the position adjusted based on the pitch point P of the virtual gear 101iG By calculating the relative position of the head 230, a desired tooth surface contact state is obtained. It is possible to easily realize the original adjustment.

That is, the virtual relative position is calculated based on the specifications of the virtual gear 101iG and the set dimensions of the cutter head 230, and the second adjustment dimension (the cutter head) is calculated based on the virtual relative position with respect to the pitch point P of the virtual gear 101iG. ( Θα, θκ, θι, etc.) for adjusting the inclination of 230, the arrangement (virtual relative position) of the cutter head 230 can be adjusted while appropriately maintaining the cutting amount with respect to the virtual workpiece 110 iG. Based on the appropriately adjusted virtual relative position and the virtual assembly dimensions of the virtual gear 101iG and the pinion 101P, the relative position of the cutter head 230 with respect to the pinion work 110P is calculated to obtain the tooth height, etc. However, it is possible to achieve appropriate generation of the tooth surface.

  The second adjustment dimension is for adjusting the arrangement of the cutter head 230 on the basis of the pitch point P of the virtual gear 101iG (in other words, on the basis of the pitch point P of the pinion 101P). It is easy to intuitively understand changes in the tooth surface state, and it is possible to easily understand changes in the contact state of the tooth surface. Furthermore, if the adjustment direction of the second adjustment dimension, etc., is appropriately set by linking with the change direction of the ease-off maximum convex point position, etc., it is possible to understand the change in the tooth surface contact state more intuitively. It becomes.

  Note that the reference point of each of the above dimensions set as the second adjustment dimension is not limited to the pitch point P, and is a point in the vicinity of the pitch point P, particularly a point in the tooth height direction passing through the pitch point P. Can be suitably set.

Perspective view of hypoid gear A perspective view showing an example of a face hob type cutter head Schematic configuration diagram of hypoid gear analysis system Schematic configuration diagram showing an example of a computer system for realizing a hypoid gear analysis system Flow chart showing hypoid gear analysis routine Explanatory drawing showing an example of the input screen Explanatory drawing showing the relative position of the cutter head to the gear work Explanatory drawing which shows the relative position of the cutter head with respect to the pinion work calculated based on the relative position and assembly dimension of the cutter head with respect to the gear work Explanatory drawing showing an example of the tilt adjustment axis of the cutter head Explanatory drawing showing the relationship between adjustment dimensions and ease-off change Explanatory drawing showing the relationship between adjustment dimensions and ease-off change Explanatory drawing showing the relationship between adjustment dimensions and ease-off change Explanatory drawing showing the relationship between adjustment dimensions and ease-off change Explanatory drawing showing the relationship between adjustment dimensions and ease-off change Explanatory drawing showing the relationship between adjustment dimensions and ease-off change Explanatory drawing showing the relationship between adjustment dimensions and ease-off change Explanatory drawing showing the relationship between adjustment dimensions and ease-off change Explanatory drawing showing the relationship between adjustment dimensions and ease-off change Explanatory drawing which shows the example of a display of each adjustment dimension and tooth surface contact analysis result Explanatory drawing which shows the example of a display of each adjustment dimension and tooth surface contact analysis result Explanatory drawing which shows the example of a display of each adjustment dimension and tooth surface contact analysis result Explanatory drawing which shows the example of a display of each adjustment dimension and tooth surface contact analysis result Explanatory drawing which shows the example of a display of each adjustment dimension and tooth surface contact analysis result Chart showing examples of basic dimensions used in tooth surface contact analysis of FIGS. 19 to 23

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Analysis system 5 ... Input part (input means)
6... Calculation unit (first tooth surface calculation means, virtual relative position calculation means, virtual assembly dimension calculation means, second tooth surface calculation means, and tooth surface contact analysis means)
DESCRIPTION OF SYMBOLS 7 ... Memory | storage part 8 ... Output part 100 ... Hypoid gear 101G ... Gear 101P ... Pinion 101iG ... Virtual gear 102G ... Gear tooth surface 102Ga ... Convex tooth surface 102Gb ... Concave tooth surface 102P ... Pinion tooth surface 102Pa ... Convex tooth surface 102Pb ... Concave tooth Surface 110 ... Pinion work 110G ... Gear work 110P ... Pinion work 110iG ... Virtual work 230 ... Cutter head 231 ... Cutter body 232 ... Mounting hole 233 ... Head surface 240 ... Blade 240i ... Convex tooth surface processing blade 240o ... Concave tooth surface processing blade

Claims (1)

By rotating the face hob type cutter head, the tooth surface of the first gear, which is one gear, is molded into the first workpiece, and the tooth surface of the second gear, which is the other gear, is second. A hypoid gear analysis system created on the workpiece of
The relative position of the cutter head with respect to the first workpiece is calculated based on the design specifications of the first gear and the set dimensions of the cutter head, and the cutter head is molded based on the relative position. First tooth surface calculating means for calculating a tooth surface of the first gear;
A virtual gear having a tooth surface conjugate with the tooth surface of the second gear to be created is adjusted as a virtual gear design parameter set based on the design parameters of the first gear . 1, the inclination of the cutter head arranged with respect to the virtual workpiece of the virtual gear based on the design dimensions of the virtual gear and the set dimensions of the cutter head. or input means for inputting a second adjustment dimension adjustment as the reference point in the vicinity thereof
It is assumed that a tooth surface is formed on the virtual workpiece of the virtual gear based on the specifications of the virtual gear, the second adjustment dimension, and the setting dimension of the cutter head. Virtual relative position calculating means for calculating the relative position;
A virtual assembly dimension calculating means for calculating a virtual assembly dimension between the second gear and the virtual gear based the on the specifications of the virtual gear and the second gear of design specifications,
The relative position of the cutter head with respect to the second workpiece is calculated based on the virtual relative position and the virtual assembly dimension, and the teeth of the second gear that are created by the cutter head based on the relative position. Second tooth surface calculating means for calculating the surface;
Tooth surface contact analysis for analyzing the contact state between the tooth surface of the first gear calculated by the first tooth surface calculating means and the tooth surface of the second gear calculated by the second tooth surface calculating means. And a hypoid gear analysis system.