CN114029560A - Cutter combination for machining cylindrical gear with variable hyperbolic arc tooth trace and machining method - Google Patents
Cutter combination for machining cylindrical gear with variable hyperbolic arc tooth trace and machining method Download PDFInfo
- Publication number
- CN114029560A CN114029560A CN202111472739.9A CN202111472739A CN114029560A CN 114029560 A CN114029560 A CN 114029560A CN 202111472739 A CN202111472739 A CN 202111472739A CN 114029560 A CN114029560 A CN 114029560A
- Authority
- CN
- China
- Prior art keywords
- blade
- tooth
- gear
- cutter
- double
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23F—MAKING GEARS OR TOOTHED RACKS
- B23F21/00—Tools specially adapted for use in machines for manufacturing gear teeth
- B23F21/005—Tools specially adapted for use in machines for manufacturing gear teeth with plural tools on a common axis
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23F—MAKING GEARS OR TOOTHED RACKS
- B23F23/00—Accessories or equipment combined with or arranged in, or specially designed to form part of, gear-cutting machines
- B23F23/12—Other devices, e.g. tool holders; Checking devices for controlling workpieces in machines for manufacturing gear teeth
- B23F23/1237—Tool holders
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P70/00—Climate change mitigation technologies in the production process for final industrial or consumer products
- Y02P70/10—Greenhouse gas [GHG] capture, material saving, heat recovery or other energy efficient measures, e.g. motor control, characterised by manufacturing processes, e.g. for rolling metal or metal working
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Gear Processing (AREA)
- Milling Processes (AREA)
Abstract
The invention discloses a cutter combination for processing a cylindrical gear with variable hyperbolic arc tooth lines and a processing method, and relates to the technical field of processing of circular arc tooth line gears. The gear convex surface and the gear concave surface of the gear can be cut simultaneously, the processing efficiency is improved, the redundancy of a high-grade numerical control machine tool can be effectively reduced by adopting the special processing cutter combination, the processing cost is greatly reduced, and the processing precision is improved.
Description
Technical Field
The invention relates to the technical field of circular arc tooth line gear machining, in particular to a cutter combination and a machining method for machining a cylindrical gear with hyperbolic-variable circular arc tooth lines.
Background
The cylindrical gear with variable hyperbolic arc tooth trace is a special form of circular arc tooth trace gear, the tooth trace of which is a circular arc trace on a plane developed along a certain generatrix of a cylindrical surface, the tooth thickness is narrowed from the middle to two ends, except for the involute of the middle section, all the other section tooth profiles are envelopes of hyperbolic families, and the gear is a novel gear pair capable of meeting the requirements of heavy load and high precision. The novel gear transmission has the advantages of good meshing performance, large coincidence coefficient, large bearing capacity, high transmission efficiency, no additional axial force, long service life, high stability, low noise and the like.
However, the novel gear is used as a basic part, and some problems exist in the process of adopting a high-grade numerical control machine tool: firstly, the economy is very poor, the processing cost is extremely high, and the method is one of the bottlenecks in large-scale industrial application of the basic parts; secondly, the function redundancy of the high-grade numerical control machine tool is large, and many functions are in a redundant state when basic parts are machined; in addition, in the case of the novel gear transmission, high-grade numerical control machine tool machining is typical approximate machining, and corresponding manufacturing is mainly carried out by interpolation, so that principle errors exist.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provides a cutter combination and a processing method for processing a cylindrical gear with a hyperbolic arc tooth trace, which can simultaneously cut a convex surface and a concave surface of a gear tooth, improve the processing efficiency, effectively reduce the redundancy of a high-grade numerical control machine tool by adopting the special processing cutter combination, greatly reduce the processing cost and improve the processing precision.
The purpose of the invention is realized by the following technical scheme: the utility model provides a processing becomes cutter combination of hyperbolic circular arc tooth line roller gear, includes the blade disc, the blade disc can rotate around self axis, the circumference array has a plurality of tooth groove cutter holder groups on the blade disc, tooth groove cutter holder group includes cutter holder seat and twolip blade, the tooth's socket has been seted up on the blade disc, cutter holder seat with the tooth's socket adaptation, twolip blade detachable installs on the cutter holder seat, the outer cutting edge of twolip blade is the forward taper, the contained angle between the inner and outer blade symmetry axis of outer cutting edge and twolip blade equals outer cutting edge with contained angle between the blade disc axis, the interior cutting edge of twolip blade is the back taper, the contained angle between interior cutting edge and twolip blade inner and outer blade symmetry axis equals interior cutting edge with contained angle between the blade disc axis.
Furthermore, the section of the double-edged blade along the axis direction of the mounting hole is rhombic, and the symmetrical axes of the inner edge and the outer edge of the double-edged blade are parallel to the rotating shaft of the cutter head.
Furthermore, a blade groove is formed in one side of the tool holder seat, one end of the symmetric axis of the inner and outer blades of the double-edged blade is matched in the blade groove, and the double-edged blade is connected with the tool holder seat through a blade fixing screw.
Further, the tooth socket tool holder group still includes blade side locking piece, be equipped with the wedge groove in the tooth's socket, the both sides of blade side locking piece are the wedge face, blade side locking piece adaptation is in the wedge inslot, a wedge face of blade side locking piece with twolip blade offsets, another wedge face of blade side locking piece with the inner wall in wedge groove offsets.
Further, be provided with cutter holder side locking piece in the wedge groove, the both sides of cutter holder side locking piece are the wedge face, a wedge face of cutter holder side locking piece with the toolholder seat offsets, another wedge face of cutter holder side locking piece with the inner wall in wedge groove offsets.
Furthermore, two positioning through holes are formed in the top of the tool holder seat in a penetrating manner, a first tool holder fixing screw and a second tool holder fixing screw are movably arranged in the two positioning through holes respectively in a penetrating manner, the first tool holder fixing screw is arranged close to the double-edge blade, the first tool holder fixing screw and the second tool holder fixing screw are both in threaded connection with the cutter head, a first threaded hole is formed in one end, close to the double-edge blade, of the tool holder seat, the first threaded hole is communicated with the positioning through hole close to the double-edge blade, a first tool holder fixing screw is adapted in the first threaded hole, a second threaded hole is formed in the other end of the tool holder seat, the second threaded hole is communicated with the other positioning through hole, and a second tool holder fixing screw is adapted in the second threaded hole.
Further, the tool holder side locking block is provided with a first locking screw in a matched mode, the first locking screw is in threaded connection with the cutter head, the bottom of the tool holder side locking block is provided with a first spring, the blade side locking block is provided with a second locking screw in a matched mode, the second locking screw is in threaded connection with the cutter head, and the bottom of the blade side locking block is provided with a second spring.
Furthermore, a lifting ring is arranged on the cutter head.
A method for machining the cylindrical gear with hyperbolic arc tooth trace includes such steps as installing the cutter head on the mainshaft of machine tool and rotating it around its axis, fixing the cutter holder group to the cutter head and rotating it with the cutter head, and rotating the blank to be machined around its axis at omega speed2And simultaneously, the gear blank to be processed performs horizontal feeding motion close to the cutter head, the speed of the horizontal feeding motion is V, so that the gear blank to be processed and the double-edge blade form compact generating motion, the outer cutting edge of the double-edge blade processes a gear concave surface, the inner cutting edge processes a gear convex surface, a pair of gear surfaces are processed, next pair of gear surfaces are processed by indexing until the whole gear is processed, and the relationship between the rotating speed of the gear blank to be processed and the feeding speed is as follows: v ═ ω2×R1Wherein R is1The gear pitch circle radius.
Further, the motion track of the contact point of the double-edged blade and the tooth blank to be processed in the fixed coordinate system is a contact line, and an equation (generating equation) of the contact line of the double-edged blade and the tooth blank to be processed is obtained as follows:
the coordinate systems are respectively: stationary coordinate system, i.e. fixed coordinate system O, of the double-edged blade (4)1-x1，y1，z1(coordinate basis i, j, k), static coordinate system O of the tooth blank to be machined2-x2，y2，z2(coordinate base i)2，j2，k2) Moving coordinate system O of the tooth blank to be processedd-xd，yd，zd(coordinate base i)d，jd，kd)；
The reference circle radius of the gear to be machined is R1The rotating angle of the dynamic coordinate of the tooth blank to be processed is psi;
the radius of the cutter head is R, theta is the rotation angle (DEG) of the double-edged blade from the middle section to the end surface of the tooth blank to be processed, and the rotation angle is the tooth profile position angle;
m is the module of the gear to be processed, alpha is the spread angle of the double-edged blade, namely the pressure angle of the gear tooth to be processed, the tooth width of the gear to be processed is B, and u is the direction from the generatrix of the cutter to the reference system x1Distance of axis, and is defined at z1The positive half shaft of the shaft is positive, and the negative half shaft is negative.
The invention has the beneficial effects that:
1. the meshing principle is adopted to carry out corresponding mathematical modeling and derivation, and the corresponding spatial relationship is adopted to carry out corresponding forming principle to carry out cutter combination design, so that interpolation manufacturing errors can be effectively avoided, the convex surface and the concave surface of the gear can be cut out simultaneously, and the machining efficiency is improved.
2. The special machining cutter combination can effectively reduce the redundancy of high-grade numerical control machine tools, greatly reduce the machining cost and improve the machining precision and the machining efficiency.
3. The limit of the nominal modulus of the processed gear is broken through, and the non-standard modulus can be specified according to actual needs for customized processing.
4. The cutter clamping seat does not need to be installed in a shifting mode, the position of the tooth socket cutter clamping group is finely adjusted through the first cutter clamping set screw and the second cutter clamping set screw, the radial position of the tooth socket cutter clamping group is fixed reliably and accurately, the center distance of the double-edged blade is adjusted, and the machining precision is improved.
5. The upper end and the lower end of the double-edged blade can be processed, and when the double-edged blade is abraded seriously, the double-edged blade can be rotated by 180 degrees and can be repositioned, installed and used, and the production cost can be greatly reduced.
Drawings
FIG. 1 is a schematic view of the overall structure of a cutter assembly for machining a cylindrical gear with hyperbolic-arc-shaped tooth trace according to the invention;
FIG. 2 is a first perspective view of a fluted cutter holder set in the cutter set for processing a cylindrical gear with a hyperbolic-arc-shaped tooth trace according to the present invention;
FIG. 3 is a second perspective view of a fluted cutter holder set in the cutter set for processing a cylindrical gear with hyperbolic-arc-shaped tooth trace according to the present invention;
FIG. 4 is a perspective view of a double-edged blade in a cutter assembly for machining a cylindrical gear with a hyperbolic-arc-shaped tooth trace according to the present invention;
FIG. 5 is a perspective view of a tool holder in a tool assembly for machining a cylindrical gear with hyperbolic-arc-shaped tooth trace according to the present invention;
FIG. 6 is a perspective view of a cutter head in the cutter assembly for processing a cylindrical gear with hyperbolic-arc-shaped tooth trace according to the present invention;
FIG. 7 is a perspective view of a clamp-side locking block in a cutter assembly for machining a cylindrical gear with hyperbolic-arc-shaped tooth trace according to the present invention;
FIG. 8 is a schematic view of the internal structure of a clamp-side locking block in a cutter assembly for machining a cylindrical gear with hyperbolic-arc-tooth-line-variable structure according to the present invention;
FIG. 9 is a perspective view of a blade-side locking block in the cutter assembly for machining a cylindrical gear with hyperbolic-arc-shaped tooth trace according to the present invention;
FIG. 10 is a schematic view of the internal structure of a blade-side locking block in the cutter assembly for processing a cylindrical gear with hyperbolic-arc-shaped tooth trace according to the present invention;
FIG. 11 is a schematic diagram of a cylindrical gear with hyperbolic arc tooth trace processed by a double-edged blade of a rotary cutter head;
FIG. 12 is a diagram of a reference coordinate system of the tool assembly and the gear to be machined;
in the figure, 1-cutter head, 2-tooth groove cutter holder group, 3-cutter holder seat, 4-double-edged blade, 5-tooth groove, 6-blade groove, 7-blade fixing screw, 8-blade side locking block, 9-wedge groove, 10-cutter holder side locking block, 11-first cutter clamping set screw, 12-positioning through hole, 13-first cutter holder fixing screw, 14-first threaded hole, 15-second threaded hole, 16-second cutter holder locking screw, 17-first locking screw, 18-first spring, 19-second locking screw, 20-second spring, 21-lifting ring, 22-second cutter holder fixing screw.
Detailed Description
The technical solutions of the present invention are further described in detail below with reference to the accompanying drawings, but the scope of the present invention is not limited to the following.
As shown in fig. 1 to 10, a cutter assembly for machining a cylindrical gear with a hyperbolic arc tooth trace comprises a cutter head 1, the cutter head 1 can rotate around a self axis, a plurality of tooth space cutter holder sets 2 are circumferentially arrayed on the cutter head 1, each tooth space cutter holder set 2 comprises a cutter holder seat 3 and a double-edged blade 4, a tooth space 5 is formed on the cutter head 1, each cutter holder seat 3 is matched with the tooth space 5, the double-edged blade 4 is detachably mounted on the cutter holder seat 3, referring to fig. 4, an outer cutting edge of the double-edged blade 4 is in a regular cone shape, an included angle between the outer cutting edge and a symmetrical axis between the inner cutting edge and the outer cutting edge of the double-edged blade 4 is equal to an included angle between the outer cutting edge and the axis of the cutter head 1, an inner cutting edge of the double-edged blade 4 is in a reverse cone shape, an included angle between the inner cutting edge and the symmetrical axis between the outer cutting edge and the symmetrical axis of the double-edged blade 4 is equal to an included angle between the inner cutting edge and the axis of the cutter head 1, the cutter holder sets 2 are driven by the cutter head 1 rotating around the self axis to machine teeth of a gear blank, the inner cutting edge and the outer cutting edge of the double-edge blade 4 work together to process a gear tooth on the gear blank, namely the outer cutting edge processes a gear tooth concave surface, the inner cutting edge processes a gear tooth convex surface, and the gear tooth convex surface and the gear tooth concave surface can be simultaneously cut, so that the processing efficiency is improved;
further, referring to fig. 4, the sectional shape of the double-edged blade 4 in the axial direction is a rhombus, and the double-edged blade has two axes, one of which is an axis of the mounting hole, and the other of which is a symmetry axis of the inner and outer edges, wherein the axis of the mounting hole is perpendicular to the symmetry axis of the inner and outer edges, the symmetry axis of the inner and outer edges of the double-edged blade 4 is parallel to the rotation axis of the cutter head 1, the double-edged blade 4 is of a symmetric structure, the distance from the symmetry axis of the inner and outer edges of the double-edged blade to the rotation axis of the cutter head 1 is a cutter radius R, and is also a nominal tooth line radius of the double-edged blade 4, a meshing principle is adopted to perform corresponding mathematical modeling and derivation, a corresponding spatial relationship is adopted to perform a cutter combination design according to a corresponding forming principle, so that an error of interpolation manufacturing can be effectively avoided, and a cylindrical gear with a variable hyperbolic arc tooth line can be accurately processed; a blade groove 6 is formed in one side of the tool holder seat 3, one end of the double-edged blade 4 along the external cutting edge symmetry axis is matched in the blade groove 6, the double-edged blade 4 is connected with the tool holder seat 3 through a blade fixing screw 7, namely the blade fixing screw 7 penetrates through a mounting hole of the double-edged blade 4 and is fixedly connected with the tool holder seat 3; the upper and lower ends of the double-edged blade 4 can be processed, when the double-edged blade 4 is worn seriously, the blade fixing screw 7 is screwed off, the double-edged blade 4 is detached from the tool holder seat 3, then the double-edged blade is rotated by 180 degrees, and the double-edged blade is fixed and installed on the tool holder seat 3 through the blade fixing screw 7 again for use, so that the production cost can be greatly reduced.
Further, as shown in fig. 1 and fig. 6 to fig. 10, the gullet tool holder set 2 further includes a blade side locking block 8, a wedge groove 9 is arranged in the gullet 5, both sides of the blade side locking block 8 are wedge surfaces, the blade side locking block 8 is adapted in the wedge groove 9, one wedge surface of the blade side locking block 8 abuts against the double-edged blade 4, the other wedge surface of the blade side locking block 8 abuts against the inner wall of the wedge groove 9, a tool holder side locking block 10 is arranged in the wedge groove 9, both sides of the tool holder side locking block 10 are wedge surfaces, one wedge surface of the tool holder side locking block 10 abuts against the tool holder base 3, and the other wedge surface of the tool holder side locking block 10 abuts against the inner wall of the wedge groove 9; the radial direction of the double-edged blade 4 is locked through the blade side locking block 8, and the radial direction of the tool holder seat 3 is locked through the tool holder side locking block 10, so that the installation stability of the tooth groove tool holder group is ensured; a first locking screw 17 is matched on the tool holder side locking block 10, the first locking screw 17 is in threaded connection with the cutter head 1, a first spring 18 is arranged at the bottom of the tool holder side locking block 10, a second locking screw 19 is matched on the blade side locking block 8, the second locking screw 19 is in threaded connection with the cutter head 1, and a second spring 20 is arranged at the bottom of the blade side locking block 8; the blade side locking block 8 and the tool holder side locking block 10 are both wedge-shaped blocks, the blade side locking block 8 and the tool holder side locking block 10 are pressed in the wedge-shaped groove 9 to enable the blade side locking block 8 and the tool holder side locking block 10 to generate radial pressure, the second spring 20 is in a compression state after the blade side locking block 8 is pressed, the blade side locking block 8 is enabled to receive axial pressure due to the reaction force of the second spring 20, the first spring 18 is in a compression state after the tool holder side locking block 10 is pressed, the tool holder side locking block 10 is enabled to receive axial pressure due to the reaction force of the first spring 18, the blade side locking block 8 and the tool holder side locking block 10 are further enabled to be locked by axial and radial partial pressure, the position precision of the tool holder tooth space group 2 is ensured, in order to ensure that the blade side locking block 8 and the tool holder side locking block 10 cannot fall off during gear processing, the second locking screw 19 is screwed in after the blade side locking block 8 is installed in place, after the tool holder side locking block 10 is installed in place, the first locking screw 17 is screwed in, so that the stability of installation of the tooth groove tool holder group 2 is ensured.
Further, as shown in fig. 2, 3 and 5, two positioning through holes 12 are formed through the top of the tool holder base 3, a first tool holder fixing screw 13 and a second tool holder fixing screw 22 are movably inserted into each of the two positioning through holes 12, the first tool holder fixing screw 13 and the second tool holder fixing screw 22 are both in threaded connection with the cutter head 1, the tool holder base 3 is mounted on the cutter head 1 through the first tool holder fixing screw 13 and the second tool holder fixing screw 22, the models of the first tool holder fixing screw 13 and the second tool holder fixing screw 22 are both M10X30, a first threaded hole 14 is formed at one end of the tool holder base 3 close to the double-edge blade 4, the first threaded hole 14 is communicated with the positioning through hole 12 close to the double-edge blade 4, the first tool holder fixing screw 11 is fittingly arranged in the first threaded hole 14, the model of the first tool holder fixing screw 11 is M8X20, a second threaded hole 15 is formed at the other end of the tool holder base 3, the second threaded hole 15 is communicated with another positioning through hole 12, a second cutter holder set screw 16 is adapted in the second threaded hole 15, the model of the second cutter holder set screw 16 is M8X8, the first cutter holder set screw 11 and the second cutter holder set screw 16 can finely adjust the position of the cutter holder seat 3 besides the function of fastening, specifically, after the first cutter holder set screw 11 is connected and screwed into the cutter holder seat 3, the tail end of the first cutter holder set screw 11 is used for supporting the first cutter holder set screw 13, after the second cutter holder set screw 16 is screwed into the cutter holder seat 3 when connected, the tail end of the second cutter holder set screw 16 is used for supporting the second cutter holder set screw 22, the magnitude of the fastening force can make the positions for fixing the first cutter holder set screw 13 and the second cutter holder set screw 22 slightly change along the radial direction, thereby realizing fine adjustment of the cutter holder seat 3, therefore, the radial position of the cutter holder seat is reliably and accurately fixed, adjusting the positions of the tool holder seats 3 in the rest tooth sockets 5 to ensure that the radial position error of each double-edged blade 4 on the circumference does not exceed 0.005 mm; the tool pan 1 is provided with a hanging ring 21, and the tool pan 1 is convenient to take through the hanging ring 21; if gears with different modules need to be machined, only the double-edge blade 4 and the tool holder seat 3 need to be replaced, the limitation of the nominal module of the machined gear is broken through, and the non-standard module can be appointed by actual needs to be customized and machined.
As shown in figures 11 and 12, the combination of the tools provides a processing method for processing a cylindrical gear with a hyperbolic-arc tooth trace, a cutter head 1 is arranged on a main shaft of a machine tool and rotates around an axis M-M of the cutter head, a tooth space cutter holder group 2 is fixed on the cutter head 1 and rotates with the cutter head 1, a tooth blank to be processed rotates around the axis of the cutter head, and the rotating speed of the tooth blank to be processed is omega2And meanwhile, the gear blank to be processed does horizontal feed motion close to the cutter head 1, the speed of the horizontal feed motion is V, so that the gear blank to be processed and the double-edge blade 4 form compact generating motion, the outer cutting edge of the double-edge blade 4 processes a gear concave surface in the processing process, the inner cutting edge processes a gear convex surface, a pair of gear surfaces are processed, the next pair of gear surfaces are processed by indexing, and the relationship between the rotating speed of the gear blank to be processed and the feed speed is as follows: v ═ ω2×R1Where R1 is the gear pitch radius.
The rated speeds of the gear blank to be processed and the double-edged blade 4 at the meshing point are respectively set as v1、v2The relative speed v of the tooth blank to be machined and the double-edged blade 4 at the point of engagement12According to the spatial meshing principle, the tooth blank workpiece to be machined and the double-edged blade 4 meet the following meshing condition in the machining process:
φ＝n1·v12＝n1·v1-n1·v2＝0
as shown in FIG. 12, assuming that the point M is an instantaneous contact point between the double-edged blade 4 and the tooth blank to be machined, the point M is located in the coordinate system O1-x1,y1,z1Middle, point O1、O2Vector to point M, point O1、O2The vectors in between are respectively:
O1M＝r1,O2M＝r2,O2O1＝ε
the relationship among the three is as follows:
r2＝ε+r1
wherein:
ε＝(R1ψ+R)i-R1k
then there are:
in the gear teeth machining process, the double-edged blade 4 only rotates around the axis of the rotary cutter head 1, the movement of the double-edged blade can be regarded as the spiral movement with the axis displacement being zero, and the double-edged blade has the characteristics of:
n1·v1＝0
further, the contact conditions during the processing can be simplified as follows:
φ＝n1·v2＝e1·v2＝0
speed v of the gear1Unfolding to obtain:
in the formula w1For the angular velocity of rotation of the cutter head 1, a vector v is obtained1And vector rdθParallel. In combination with the definition of normal vectors:
v1⊥n1(e1)。
and k2-j, and has:
v2＝w2k2×r2-w2R1i＝w2(k2×r2-R1i)
w2is angular velocity of rotation of the tooth blank
The above formulas are combined:
the formula shows that:
the motion track of the contact point of the double-edged blade 4 and the tooth blank to be processed in the fixed coordinate system is a contact line, and the equation (generating equation) of the contact line of the double-edged blade 4 and the tooth blank to be processed is obtained as follows:
the coordinate systems are respectively: stationary coordinate system, i.e. fixed coordinate system O, of double-edged blade 41-x1，y1，z1(coordinate basis i, j, k), static coordinate system O of the tooth blank to be machined2-x2，y2，z2(coordinate base i)2，j2，k2) Moving coordinate system O of the tooth blank to be processedd-xd，yd，zd(coordinate base i)d，jd，kd)。
The reference circle radius of the gear to be machined is R1The rotating angle of the dynamic coordinate of the tooth blank to be processed is psi;
the radius of the cutter head 1 is R, theta is the rotation angle (degree) of the double-edged blade 4 from the middle section to the end surface of the tooth blank to be processed, and the rotation angle is the tooth profile position angle.
m is the module of the gear to be processed, alpha is the pressure angle of the gear to be processed, namely the spread angle of the double-edged blade 4, and the tooth width of the gear to be processed is B. u is the direction of the tool along the generatrix to the reference frame x1Distance of axis, and is defined at z1The positive half shaft of the shaft is positive, and the negative half shaft is negative;
in the actual processing project, R, R1M, alpha are defined design parameters, theta and psiFor the surface parameters of the tooth surface of the gear tooth, the value ranges of the parameters theta and psi are determined, wherein theta influences the position of the point on the tooth surface in the tooth width direction, and psi determines the position of the point on the tooth surface in the tooth height direction.
For the variable hyperbolic arc-shaped tooth trace cylindrical gear, because the tooth profiles of all the sections are different and the curvature radius of any position in the tooth height direction of the same section is different, the ranges of the corresponding workpiece corners psi and theta are different, and the variable hyperbolic arc-shaped tooth trace cylindrical gear needs to be researched by combining the tooth profiles of all the sections.
The working principle of the rotary cutter head is known easily, the rotating angle of the cutter from the middle section of the gear tooth to two end faces is gradually increased, and the rotating angle theta of the cutter can be calculated by the following formula:
wherein b is the distance from each end section to the middle section, ReThe radius of curvature of the tooth profile in the tooth trace direction corresponding to any point. If b.ident.0 is present in the middle-section tooth profile, θ.ident.0 can be found by the formula. In the non-medium section tooth profile, b is not equal to 0, the curvature radius in the tooth trace direction at any point is different, and the ranges of psi and theta are determined according to the formula.
In fact, in the machining process, when the radius of the cutter head is increased, the change of the tooth profile of each section is gradually reduced, and the value range of the tooth profile psi and theta of each section is more and more close to the parameter range of the tooth profile of the middle section. In general, when the radius of the cutter head 1 is larger than the tooth width of the gear teeth, the parameter range of the tooth profile of the middle section can be used for replacing the parameter range of the whole tooth surface.
The value range of the section tooth profile line psi in the hypoid circular-arc tooth profile cylindrical gear can be expressed as follows:
when z is not less than (h a + c)*) When (1-cos alpha)
For the convex surface of the gear: alpha-beta-gamma1≤ψ≤α-β-γ2
Concave surface: beta-alpha + gamma2≤ψ≤β-α+γ1
When z < (h a + c)*) When (1-cos alpha)
Counter gear concave surface：β-α≤ψ≤γ1+β-α
Convex surface: alpha-beta-gamma1≤ψ≤α-β
Wherein:
the gear tooth crest coefficient is h x a, and the crest clearance coefficient is c*Z is the number of teeth of the gear to be machined, beta is a constant (related to the number of teeth of the gear workpiece)
Under the condition that the pressure angle and the tooth form coefficient are determined, the parameter psi of the section tooth profile line in the gear teeth of the cylindrical gear with the hyperbolic arc tooth profile line is only related to the tooth number of the gear workpiece to be processed. This will be described below by specific examples.
The number of teeth z of the processed gear is 49, the tooth width B is 90mm, the cutter radius R is 500mm, the crest height coefficient is 1, the tip clearance coefficient is 0.25, and the modulus is respectively m1 is 4 and m2 is 6. Then, according to the above calculation formula, the value ranges of both the two processed gears ψ are:
gear convex surface:
-0.1443≤ψ≤0.1910
concave surface of the gear:
-0.1910≤ψ≤0.1443
the cutter combination and the gear workpiece synchronously perform generating movement according to a preset tooth cutting speed until the current tooth socket is machined, wherein the current tooth socket comprises a convex surface of a previous tooth and a concave surface of a next tooth, after the previous tooth socket is machined, the cutter head 1 is separated from the machined gear, the indexing mechanism firstly returns to the indexing starting point, and then the indexing mechanism continues to index to the angle of the next tooth socket to be machined so as to avoid the generation of accumulated errors.
The foregoing is illustrative of the preferred embodiments of this invention, and it is to be understood that the invention is not limited to the precise form disclosed herein and that various other combinations, modifications, and environments may be resorted to, falling within the scope of the concept as disclosed herein, either as described above or as apparent to those skilled in the relevant art. And that modifications and variations may be effected by those skilled in the art without departing from the spirit and scope of the invention as defined by the appended claims.
Claims (10)
1. The utility model provides a processing becomes cutter combination of hyperbolic circular arc tooth line cylindrical gear, a serial communication port, including blade disc (1), blade disc (1) can rotate around self axis, the circumference array has a plurality of gullets cutter holder group (2) on blade disc (1), gullet cutter holder group (2) are including cutter holder seat (3) and twolip blade (4), tooth's socket (5) have been seted up on blade disc (1), cutter holder seat (3) with tooth's socket (5) adaptation, twolip blade (4) detachable install on cutter holder seat (3), the outer cutting edge of twolip blade (4) is positive cone, the contained angle between outer cutting edge and twolip blade (4) interior outer cutting edge axis equals outer cutting edge with the contained angle between blade disc (1) axis, the interior cutting edge of twolip blade (4) is the back taper, the contained angle between interior cutting edge and twolip blade (4) interior outer cutting edge equals interior inslot cutting edge with the contained angle between twolip blade axis The angle between the axes of the discs (1).
2. The cutter combination for processing the variable hyperbolic arc-tooth-line cylindrical gear according to claim 1, wherein the cross-sectional shape of the double-edged blade (4) along the axial direction of the self-mounting hole is a rhombus, and the symmetry axes of the inner edge and the outer edge of the double-edged blade (4) are parallel to the rotating shaft of the cutter head (1).
3. The cutter assembly for machining the cylindrical gear with the hyperbolic arc-shaped tooth trace according to claim 2, wherein a blade groove (6) is formed in one side of the cutter holder seat (3), one end of a symmetric axis of inner and outer edges of the double-edge blade (4) is matched in the blade groove (6), and the double-edge blade (4) is connected with the cutter holder seat (3) through a blade fixing screw (7).
4. The cutter assembly for machining the cylindrical gear with the hyperbolic-arc toothed line according to claim 3, wherein the tooth groove cutter clamp group (2) further comprises a blade side locking block (8), a wedge groove (9) is formed in the tooth groove (5), wedge surfaces are arranged on two sides of the blade side locking block (8), the blade side locking block (8) is matched in the wedge groove (9), one wedge surface of the blade side locking block (8) is abutted to the double-edge blade (4), and the other wedge surface of the blade side locking block (8) is abutted to the inner wall of the wedge groove (9).
5. The tool combination for machining the cylindrical gear with the hyperbolic-arc toothed line according to claim 4, wherein a tool holder side locking block (10) is arranged in the wedge-shaped groove (9), both sides of the tool holder side locking block (10) are wedge-shaped surfaces, one wedge-shaped surface of the tool holder side locking block (10) abuts against the tool holder seat (3), and the other wedge-shaped surface of the tool holder side locking block (10) abuts against the inner wall of the wedge-shaped groove (9).
6. The tool combination for machining the cylindrical gear with the hyperbolic-arc tooth trace as claimed in claim 1, wherein two positioning through holes (12) are formed through the top of the tool holder seat (3), a first tool holder fixing screw (13) and a second tool holder fixing screw (22) are movably arranged in the two positioning through holes (12) respectively, the first tool holder fixing screw (13) is arranged close to the double-edge tool piece (4), the first tool holder fixing screw (13) and the second tool holder fixing screw (22) are both in threaded connection with the cutter head (1), a first threaded hole (14) is formed in one end, close to the double-edge tool piece (4), of the tool holder seat (3), the first threaded hole (14) is communicated with the positioning through hole (12) close to the double-edge tool piece (4), and a first tool holder fixing screw (11) is adapted in the first threaded hole (14), the other end of the tool holder seat (3) is provided with a second threaded hole (15), the second threaded hole (15) is communicated with the other positioning through hole (12), and a second tool holder set screw (16) is matched in the second threaded hole (15).
7. The tool combination for machining the cylindrical gear with the hyperbolic-arc tooth trace according to claim 5, wherein a first locking screw (17) is adapted on the tool holder side locking block (10), the first locking screw (17) is in threaded connection with the cutter head (1), a first spring (18) is arranged at the bottom of the tool holder side locking block (10), a second locking screw (19) is adapted on the blade side locking block (8), the second locking screw (19) is in threaded connection with the cutter head (1), and a second spring (20) is arranged at the bottom of the blade side locking block (8).
8. The cutter combination for processing the cylindrical gear with the hyperbolic-arc toothed line according to claim 1, wherein a hanging ring (21) is arranged on the cutter head (1).
9. The method for processing the cylindrical gear with the variable hyperbolic arc tooth trace according to any one of claims 1-8, wherein the cutter head (1) is arranged on a main shaft of a machine tool and rotates around an axis M-M of the cutter head, the tooth groove cutter holder group (2) is fixed on the cutter head (1) and rotates with the cutter head (1), and a tooth blank to be processed rotates around an axis of the tooth blank to be processed, wherein the rotation speed of the tooth blank is omega2And simultaneously, the gear blank to be processed performs horizontal feeding motion close to the cutter head (1), the speed of the horizontal feeding motion is V, so that the gear blank to be processed and the double-edge blade (4) form tight generating motion, the outer cutting edge of the double-edge blade (4) processes a gear concave surface, the inner cutting edge processes a gear convex surface, a pair of gear surfaces needs to be subjected to indexing and then the next pair of gear surfaces is processed until the whole gear is processed, and the relationship between the rotating speed of the gear blank to be processed and the feeding speed is as follows: v ═ ω2×R1Wherein R is1The gear pitch circle radius.
10. The method for machining the cylindrical gear with the hyperbolic-arc toothed line according to claim 9, wherein a motion track of a contact point between the double-edged blade (4) and the tooth blank to be machined in a fixed coordinate system is a contact line, and an equation (generated motion equation) of the contact line between the double-edged blade (4) and the tooth blank to be machined is obtained as follows:
the coordinate systems are respectively: stationary coordinate system, i.e. fixed coordinate system O, of the double-edged blade (4)1-x1，y1，z1(coordinate basis i, j, k), static coordinate system O of the tooth blank to be machined2-x2，y2，z2(coordinate base i)2，j2，k2) Moving coordinate system O of the tooth blank to be processedd-xd，yd，zd(coordinate base i)d，jd，kd)；
The reference circle radius of the gear to be machined is R1The rotating angle of the dynamic coordinate of the tooth blank to be processed is psi;
the radius of the cutter head (1) is R, theta is the rotation angle (degree) of the double-edge blade (4) from the middle section to the end surface of the tooth blank to be processed, and the rotation angle is the tooth profile position angle;
m is the module of the gear to be processed, alpha is the spread angle of the double-edge blade (4), namely the pressure angle of the gear to be processed, the tooth width of the gear to be processed is B, and u is the direction from the generatrix of the cutter to the reference system x1Distance of axis, and is defined at z1The positive half shaft of the shaft is positive, and the negative half shaft is negative.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111472739.9A CN114029560B (en) | 2021-11-30 | 2021-11-30 | Cutter combination for machining cylindrical gear with hyperbolic circular arc toothed line and machining method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111472739.9A CN114029560B (en) | 2021-11-30 | 2021-11-30 | Cutter combination for machining cylindrical gear with hyperbolic circular arc toothed line and machining method |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114029560A true CN114029560A (en) | 2022-02-11 |
| CN114029560B CN114029560B (en) | 2023-07-14 |
Family
ID=80140016
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202111472739.9A Active CN114029560B (en) | 2021-11-30 | 2021-11-30 | Cutter combination for machining cylindrical gear with hyperbolic circular arc toothed line and machining method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN114029560B (en) |
Citations (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB659446A (en) * | 1949-03-17 | 1951-10-24 | Gleason Works | Cutters for and method of producing gears |
| US3662650A (en) * | 1970-02-16 | 1972-05-16 | Bird Island Inc | Gear making |
| SU524627A1 (en) * | 1975-01-23 | 1976-08-15 | Московский Автомобильный Завод Имени И.А.Лихачева | Cutter head |
| US20030044246A1 (en) * | 2001-09-06 | 2003-03-06 | Erickson Robert A. | Face hobbing cutter |
| US20040086350A1 (en) * | 2002-10-31 | 2004-05-06 | Yaxiong Zhang | Five-simultaneously-working-axis computerized numerical controlled tooth cutting machine tool for plane enveloping toroidal worms |
| CN101890540A (en) * | 2010-07-16 | 2010-11-24 | 扬州大学 | Method for processing curve-tooth cylindrical gear |
| CN103252538A (en) * | 2012-02-16 | 2013-08-21 | 山特维克知识产权股份有限公司 | Face hobbing milling cutter system and indexable milling blades used for same |
| CN103624310A (en) * | 2012-08-28 | 2014-03-12 | 株洲钻石切削刀具股份有限公司 | Cutting tool having fly-off prevention structure |
| CN106438920A (en) * | 2016-08-15 | 2017-02-22 | 四川大学 | Variable-double-curve circular-arc-tooth-trace cylindrical gear |
| CN206578343U (en) * | 2017-01-13 | 2017-10-24 | 浙江亚太机电股份有限公司 | A kind of adjustable indexable side and face milling cutter of cutter blade |
| CN107617795A (en) * | 2016-07-14 | 2018-01-23 | 方年学 | The processing method of curved tooth line gear |
| US20180056417A1 (en) * | 2016-08-23 | 2018-03-01 | Klingelnberg Ag | Method for machining the tooth flanks of face coupling workpieces in the semi-completing method |
| EP3666431A1 (en) * | 2017-08-07 | 2020-06-17 | Kitagawa Iron Works Co., Ltd | Chuck correction method |
| CN113182574A (en) * | 2021-05-17 | 2021-07-30 | 常熟万克精密工具有限公司 | Fine adjustment type cyclone milling cutter head |
-
2021
- 2021-11-30 CN CN202111472739.9A patent/CN114029560B/en active Active
Patent Citations (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB659446A (en) * | 1949-03-17 | 1951-10-24 | Gleason Works | Cutters for and method of producing gears |
| US3662650A (en) * | 1970-02-16 | 1972-05-16 | Bird Island Inc | Gear making |
| SU524627A1 (en) * | 1975-01-23 | 1976-08-15 | Московский Автомобильный Завод Имени И.А.Лихачева | Cutter head |
| US20030044246A1 (en) * | 2001-09-06 | 2003-03-06 | Erickson Robert A. | Face hobbing cutter |
| US20040086350A1 (en) * | 2002-10-31 | 2004-05-06 | Yaxiong Zhang | Five-simultaneously-working-axis computerized numerical controlled tooth cutting machine tool for plane enveloping toroidal worms |
| CN101890540A (en) * | 2010-07-16 | 2010-11-24 | 扬州大学 | Method for processing curve-tooth cylindrical gear |
| CN103252538A (en) * | 2012-02-16 | 2013-08-21 | 山特维克知识产权股份有限公司 | Face hobbing milling cutter system and indexable milling blades used for same |
| CN103624310A (en) * | 2012-08-28 | 2014-03-12 | 株洲钻石切削刀具股份有限公司 | Cutting tool having fly-off prevention structure |
| CN107617795A (en) * | 2016-07-14 | 2018-01-23 | 方年学 | The processing method of curved tooth line gear |
| CN106438920A (en) * | 2016-08-15 | 2017-02-22 | 四川大学 | Variable-double-curve circular-arc-tooth-trace cylindrical gear |
| US20180056417A1 (en) * | 2016-08-23 | 2018-03-01 | Klingelnberg Ag | Method for machining the tooth flanks of face coupling workpieces in the semi-completing method |
| CN206578343U (en) * | 2017-01-13 | 2017-10-24 | 浙江亚太机电股份有限公司 | A kind of adjustable indexable side and face milling cutter of cutter blade |
| EP3666431A1 (en) * | 2017-08-07 | 2020-06-17 | Kitagawa Iron Works Co., Ltd | Chuck correction method |
| CN113182574A (en) * | 2021-05-17 | 2021-07-30 | 常熟万克精密工具有限公司 | Fine adjustment type cyclone milling cutter head |
Non-Patent Citations (2)
| Title |
|---|
| 赵斐: "圆弧齿线圆柱齿轮全齿面数学模型及切齿条件分析", 《吉林大学学报(工学版)》 * |
| 赵斐: "旋转刀盘圆弧齿轮成形理论分析及数字化建模研究", 《四川大学学报(工程科学版)》 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN114029560B (en) | 2023-07-14 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP6022798B2 (en) | Milling tools and milling insert kits | |
| WO2022227815A1 (en) | Detachable multi-layer blade skiving cutter with staggered blades and assembly method | |
| US8882414B2 (en) | Method and system for milling a bevel gear tooth system in a continuous miling process | |
| US10016828B2 (en) | Cutting insert and milling tool | |
| CN109773279B (en) | Circular arc tooth line gear machining method | |
| CN111687496B (en) | Narrow clearance groove herringbone gear offset forming processing method | |
| CN203109371U (en) | Forming and generating gear milling machine | |
| CN108941785B (en) | Universal disc cutter composite milling process for large-modulus cylindrical outer gear | |
| CN112222538A (en) | Tooth pitch accumulated error compensation method for forming and milling tooth machining | |
| CN111715947A (en) | Method for forming linear contact gradually-reduced tooth arc tooth bevel gear pair | |
| CN206047261U (en) | The process equipment of curved tooth line gear | |
| Zhang et al. | Tooth surface geometry optimization of spiral bevel and hypoid gears generated by duplex helical method with circular profile blade | |
| CN114029560A (en) | Cutter combination for machining cylindrical gear with variable hyperbolic arc tooth trace and machining method | |
| CN109317764B (en) | Multi-tooth part machining method and multi-tooth part cutting tool | |
| CN112475945A (en) | Precise rotary worktable | |
| CN109434220B (en) | Arc bevel gear machining method | |
| CN208162786U (en) | A kind of asymmetric chamfered edge hobboing cutter | |
| CN211101962U (en) | Arc tooth bevel gear milling cutter | |
| CN107262752B (en) | Knife rest for automatic electrode grinding device | |
| CN105965106A (en) | Numerical control small-modulus straight bevel gear shaper | |
| CN115971552A (en) | Cutting tool with rolling device | |
| CN214212484U (en) | A cut tooth cutter for cycloid wheel processing | |
| CN115062429B (en) | Design method of finish turning roll slotting tool | |
| CN214023699U (en) | A whole double-end becomes grooved milling cutter for stainless steel processing | |
| CN212169119U (en) | Cutter with novel interface |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |