CN109352092B - Design method of powerful gear cutter - Google Patents
Design method of powerful gear cutter Download PDFInfo
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- CN109352092B CN109352092B CN201811514697.9A CN201811514697A CN109352092B CN 109352092 B CN109352092 B CN 109352092B CN 201811514697 A CN201811514697 A CN 201811514697A CN 109352092 B CN109352092 B CN 109352092B
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- 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
- B23F21/04—Planing or slotting tools
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Abstract
The invention discloses a design method of a strong gear cutter, which utilizes the shaft intersection angle between the axis of the strong gear cutter and the axis of a processed gear when strong gear cutting is carried out, namely the meshing principle that a pair of staggered shaft cylindrical gears are meshed without clearance is formed between the strong gear cutter and the processed gear, namely the pitch circle pitch is equal to the relation between the pitch circle tooth thickness of the processed gear and the pitch circle tooth thickness of the strong gear cutter, and calculates and obtains the end face pitch circle pressure angle of the strong gear cutter and the end face pitch circle pressure angle of the processed gear, thus combining other known parameters, the design of the strong gear cutter can be realized; when the gear is machined by the strong gear cutting knife designed by the method, compared with the common gear slotting knife, the machining efficiency can be improved by 4-8 times, the tooth surface roughness Rz is improved by 2-3 grades, and the machining precision of the gear reaches ISO7 grade.
Description
Technical Field
The invention belongs to the technical field of tools specially used for gear and tooth processing equipment, and particularly relates to a design method of a powerful gear cutter.
Background
In the traditional gear production industries of automobiles, motorcycles, aviation, aerospace, military machinery and the like, gear shaping processing is an indispensable processing link, and the gear shaping processing can be suitable for processing gears such as inner ring teeth, outer ring teeth, inner and outer step teeth and the like. The conventional gear shaping processing is adopted, so that the tooth surface precision and the surface roughness are low, and the efficiency is lower. Therefore, a brand-new high-efficiency cylindrical gear cutting method, namely a powerful gear scraping method, is produced.
The powerful gear scraping processing adopts a cutting mode of integrating rolling and gear shaping to process the cylindrical gear with the inner tooth and the outer tooth, in the gear cutting processing process, a gear cutting tool is equivalent to a hob and a gear shaping tool, the cutting mode is that a workpiece and the tool rotate continuously, and the gear rolling and the gear shaping movement are combined to cut the gear. When strong gear scraping is carried out, the cutter has an intersecting angle relative to the workpiece, and rotates around the axis of the cutter and the workpiece respectively to form generating motion, and meanwhile, the cutter is fed along the axial direction of the workpiece to cut out the full length of the workpiece. The shape of the cutter is very similar to that of a pinion cutter. When the workpiece is straight teeth, the cutter is bevel teeth; when the workpiece is a skewed tooth, the tool is typically formed as a straight tooth. When processing involute tooth form, no matter the cutter is straight tooth or inclined tooth, the tooth form in the end section is involute. The theoretical cutting edge shape of the tool should be made to the line of contact on the tool tooth flank when the tool is engaged with a workpiece. Therefore, when the cutter is straight, the cutting edge is involute on the end plane of the cutter; when the tool is a bevel tooth, its cutting edge is the intersection line of the involute helicoid and hyperboloid of revolution. In machining gears, the cutting edge of the tool is at the contact line location during engagement and is sharpened to its front face when the tool is dull.
The existing powerful gear scraping knife is generally calculated by adopting an approach algorithm, and the tooth profile structure of the powerful gear scraping knife has larger errors, so that the tooth profile precision of the gear produced by adopting the powerful gear scraping knife cannot meet the requirement. The chinese patent application with publication number CN105397203A discloses a helical tooth scraping tool for machining a numerical control strong scraping tooth, which discloses a design method of the helical tooth scraping tool, but the design method still belongs to an approach algorithm, and the tooth profile precision of the designed helical tooth scraping tool is poor, which cannot meet the requirement of the machining precision of a gear.
Disclosure of Invention
In view of the above, the present invention provides a design method for a strong cutter, which adopts a generating method to improve the design precision.
In order to achieve the purpose, the invention provides the following technical scheme:
a design method of a strong gear cutter is characterized in that when strong gear cutting is carried out, an axis intersection angle is formed between the axis of the strong gear cutter and the axis of a gear to be processed, namely, a pair of staggered shaft cylindrical gears are meshed between the strong gear cutter and the gear to be processed without clearance, and according to the meshing principle, the method comprises the following steps:
Pjn＝Sjn1+Sjno
wherein, PjnIs pitch circle pitch; sjn1For the gear to be machinedThe pitch circle tooth thickness of (2); sjnoThe pitch circle tooth thickness of the strong gear cutter; m is a modulus; alpha is alphafnIs a reference circle pressure angle; alpha is alphajnIs a pitch circle pressure angle;
Sfn1the normal tooth thickness of the gear to be processed; z1The number of teeth of the processed gear; alpha is alphafs1The end face of the gear to be processed is divided into a circle pressure angle; alpha is alphajs1The pitch circle pressure angle is the end face pitch circle pressure angle of the gear to be processed; beta is ab1The base circle helix angle of the gear to be processed; beta is aj1Is the pitch circle helical angle of the gear to be processed; dj1The pitch circle diameter of the gear to be processed; and d isj1＝db1/cosαfs1，db1Is the base circle diameter of the gear to be processed;
Sfnothe normal tooth thickness of the strong gear cutter; zoThe number of teeth of the powerful gear cutter is shown; alpha is alphafsoThe end face of the powerful gear cutter is provided with a reference circle pressure angle; alpha is alphajsoThe pressure angle is the pitch circle pressure angle of the end surface of the strong gear cutter; beta is aboThe base circle helix angle of the strong gear cutter; beta is ajoIs the pitch circle helical angle of the powerful gear cutter; djoThe pitch circle diameter of the powerful gear cutter; and d isjo＝dbo/cosαfso，dboThe diameter of the base circle of the powerful gear cutter;
the normal engagement angle of a pair of staggered shaft cylindrical gears formed between the powerful gear cutting knife and the processed gear is equal, and then:
sinαjn＝sinαjs1cosβb1＝sinαjsocosβbo
namely:
this gives:
this equation is converted to an identity:
wherein F is a constant and:
it is known that f (α)js1) In which only the pitch circle pressure angle alpha of the end face of the gear to be machinedjs1For unknown parameters, a Newton iteration method is adopted to carry out pitch circle pressure angle alpha on the end face of the gear to be machinedjs1And solving to obtain:
wherein, f' (α)js1(n)) Is f (alpha)js1(n)) N is a positive integer greater than or equal to 0;
according to the calculated pitch circle pressure angle alpha of the end surface of the machined gearjs1Further obtain the end surface pitch circle pressure angle alpha of the strong gear cutterjsoComprises the following steps:
further, the outer diameter of the powerful cutter is: deo＝2Ao1-dil
The root diameter of the powerful gear cutting knife is as follows: dio＝2Ao1-del-05m
Wherein d isilThe root diameter of the gear to be processed; delThe outer diameter of the gear to be processed;
Ao1is the meshing center distance between the powerful gear cutting knife and the gear to be processed, and Ao1＝rj1+rjo；
rj1Is the pitch circle radius of the gear to be machined, and
rjothe pitch circle radius of the strong gear cutter; and is
Further, the measurement stopping circle radius of the powerful gear cutter is as follows:
wherein R is1oThe arc radius of the tooth top side of the strong gear cutter is the transition circle radius of the two sides of the tooth top of the strong gear cutter; r iseo＝deo/2；rboIs the base radius of the strong gear cutter, and rbo＝dbo/2。
Further, the length of the meshing line between the powerful gear cutter and the gear to be machined is as follows:
wherein r isb1Is the base radius of the gear to be machined, and rb1＝db1/2。
Further, the measurement of the starting radius of the strong cutter:
wherein r ise1Is the radius of the addendum circle of the gear to be machined.
Further, after the normal front angle and the normal back angle are injected, the shaping design method of the powerful cutter comprises the following steps:
axial relief angle of the power cutter:
wherein alpha isenoThe normal tooth top back angle of the powerful gear cutter is adopted; beta is afoThe pitch circle helix angle of the powerful gear cutter;
pitch circle side relief angle of the power cutter:
wherein, γenoThe normal front angle of the strong cutter is the normal front angle of the strong cutter;
acute edge helix angle of the power cutter: beta is afro＝βfo+βco
Sharp edge pressure angle of the power cutter:
sharp edge base circle diameter of the strong gear cutter:
sharp edge base radius of the strong gear cutter: r isbro＝dbro/2
The final measurement of the expansion length of the sharp edge of the powerful gear cutter is as follows:
wherein r isbroThe radius of a sharp edge base circle of the powerful gear cutter;
the sharp edge of the strong gear cutter is used for measuring the unfolding length:
the blunt helix angle of the power cutter: beta is afdo＝βfo-βco
Blunt pressure angle of the power slotting cutter:
base circle diameter of blunt edge of the powerful slotting cutter:
base radius of blunt edge of the powerful slotting cutter: r isbdo＝dbdo/2
Blunt of powerful slotting cutterEdge final measurement of the deployment length:
the extended length of the blunt edge of the powerful slotting cutter is measured:
the tooth thickness of the powerful slotting cutter measures the chord tooth thickness included angle:
wherein alpha isdcloThe end face pressure angle of the measurement circle of the chord tooth height and the chord tooth thickness of the powerful slotting cutter is measured;
dclothe diameter of the circle for measuring the chordal height and the chordal thickness of the powerful slotting cutter, and dclo＝(deo-dio)/2
Measurement chordal tooth height of the powerful slotting cutter: h isclo＝reo-rclocosθ
rcloThe radius of the measuring circle of the chord tooth height and the chord tooth thickness of the powerful slotting cutter; and r isclo＝dclo/2；
Measurement of the chordal tooth thickness of the powerful slotting cutter: sclo＝dclosinθcosβfo。
The invention has the beneficial effects that:
the design method of the strong gear cutter starts from the meshing relation between the strong gear cutter and a gear to be processed, and calculates and obtains an end face pitch circle pressure angle of the strong gear cutter and an end face pitch circle pressure angle of the gear to be processed by utilizing the relation that the pitch circle pitch is equal to the pitch circle tooth thickness of the gear to be processed and the pitch circle tooth thickness of the strong gear cutter, so that the design of the strong gear cutter can be realized by combining other known parameters; when the gear is machined by the strong gear cutting knife designed by the method, compared with the common gear slotting knife, the machining efficiency can be improved by 4-8 times, the tooth surface roughness Rz is improved by 2-3 grades, and the machining precision of the gear reaches ISO7 grade.
The invention discloses a design method of a strong gear cutter, which utilizes the meshing principle that a pair of staggered shaft cylindrical gears are formed between the axial line of the strong gear cutter and the axial line of a processed gear without clearance meshing when strong gear cutting is carried out, realizes the normal tooth profile design and the end face tooth profile design of the strong gear cutter, realizes the correction design of the normal tooth profile of the strong gear cutter after a normal front angle and a normal rear angle are injected, finally solves the difficult problem of theoretical design by verifying a structure diagram, a meshing diagram, a generating diagram, a meshing tooth profile diagram, a normal measurement tooth profile diagram of the strong gear cutter and the like, overcomes the technical problem that the strong gear scraper can only be designed by adopting an approach algorithm in the prior art, achieves the expected effect through multiple actual processing tests, improves the geometric precision of a tooth surface, the surface roughness and the production efficiency, the cost is reduced and the user can confirm the cost.
Drawings
In order to make the object, technical scheme and beneficial effect of the invention more clear, the invention provides the following drawings for explanation:
FIG. 1 is a schematic structural view of a strong cutter designed by the method of the present invention, specifically, the strong cutter is a helical tooth;
FIG. 2 is a reference diagram of the use state of the helical tooth strong gear cutter when the excircle gear is machined;
FIG. 3 is a diagram showing the engagement relationship between the strong cutter and the external gear;
FIG. 4 is a schematic view of the normal tooth form structure of the strong cutter;
FIG. 5 is a generating diagram of the strong gear-cutting tool for machining a cylindrical gear;
FIG. 6 is a top view of FIG. 5;
FIG. 7 is a schematic structural view of a strong cutter designed by the method of the present invention, specifically, the strong cutter is straight teeth;
fig. 8 is a reference view showing a state of use when the straight-tooth strong-cutting-tooth cutter is used for machining an inner circular gear.
Detailed Description
The present invention is further described with reference to the following drawings and specific examples so that those skilled in the art can better understand the present invention and can practice the present invention, but the examples are not intended to limit the present invention.
In the method for designing a strong gear cutter according to the present embodiment, when performing strong gear cutting, an axis intersection angle is formed between the axis of the strong gear cutter and the axis of the gear to be processed, that is, a pair of staggered-axis cylindrical gears is formed between the strong gear cutter and the gear to be processed without a gap, and according to the meshing principle, the method includes:
Pjn＝Sjn1+Sjno
wherein, PjnIs pitch circle pitch; sjn1The pitch circle tooth thickness of the gear to be processed; sjnoThe pitch circle tooth thickness of the strong gear cutter; m is a modulus; alpha is alphafnIs a reference circle pressure angle; alpha is alphajnIs a pitch circle pressure angle;
Sfn1the normal tooth thickness of the gear to be processed; z1The number of teeth of the processed gear; alpha is alphafs1The end face of the gear to be processed is divided into a circle pressure angle; alpha is alphajs1The pitch circle pressure angle is the end face pitch circle pressure angle of the gear to be processed; beta is ab1The base circle helix angle of the gear to be processed; beta is aj1Is the pitch circle helical angle of the gear to be processed; dj1The pitch circle diameter of the gear to be processed; and d isj1＝db1/cosαfs1，db1Is the base circle diameter of the gear to be processed;
Sfnothe normal tooth thickness of the strong gear cutter; zoThe number of teeth of the powerful gear cutter is shown; alpha is alphafsoThe end face of the powerful gear cutter is provided with a reference circle pressure angle;αjsothe pressure angle is the pitch circle pressure angle of the end surface of the strong gear cutter; beta is aboThe base circle helix angle of the strong gear cutter; beta is ajoIs the pitch circle helical angle of the powerful gear cutter; djoThe pitch circle diameter of the powerful gear cutter; and d isjo＝dbo/cosαfso，dboThe diameter of the base circle of the powerful gear cutter;
the normal engagement angle of a pair of staggered shaft cylindrical gears formed between the powerful gear cutting knife and the processed gear is equal, and then:
sinαjn＝sinαjs1cosβb1＝sinαjsocosβbo
namely:
this gives:
this equation is converted to an identity:
wherein F is a constant and:
it is known that f (α)js1) In which only the pitch circle pressure angle alpha of the end face of the gear to be machinedjs1For unknown parameters, a Newton iteration method is adopted to carry out pitch circle pressure angle alpha on the end face of the gear to be machinedjs1And solving to obtain:
wherein, f' (α)js1(n)) Is f (alpha)js1(n)) N is a positive integer greater than or equal to 0;
according toThe calculated pitch circle pressure angle alpha of the end surface of the gear to be processedjs1Further obtain the end surface pitch circle pressure angle alpha of the strong gear cutterjsoComprises the following steps:
further, the outer diameter of the powerful cutter is: deo＝2Ao1-dil
The root diameter of the powerful gear cutting knife is as follows: dio＝2Ao1-del-05m
Wherein d isilThe root diameter of the gear to be processed; delThe outer diameter of the gear to be processed;
Ao1is the meshing center distance between the powerful gear cutting knife and the gear to be processed, and Ao1＝rj1+rjo；
rj1Is the pitch circle radius of the gear to be machined, and
rjothe pitch circle radius of the strong gear cutter; and is
Further, the measurement stopping circle radius of the powerful gear cutter is as follows:
wherein R is1oThe arc radius of the tooth top side of the strong gear cutter is the transition circle radius of the two sides of the tooth top of the strong gear cutter; r iseo＝deo/2；rboIs the base radius of the strong gear cutter, and rbo＝dbo/2。
Further, the length of the meshing line between the powerful gear cutter and the gear to be machined is as follows:
wherein r isb1Is the base radius of the gear to be machined, and rb1＝db1/2。
Further, the measurement of the starting radius of the strong cutter:
wherein r ise1Is the radius of the addendum circle of the gear to be machined.
Further, after the normal front angle and the normal back angle are injected, the shaping design method of the powerful cutter comprises the following steps:
axial relief angle of the power cutter:
wherein alpha isenoThe normal tooth top back angle of the powerful gear cutter is adopted; beta is afoThe pitch circle helix angle of the powerful gear cutter;
pitch circle side relief angle of the power cutter:
wherein, γenoThe normal front angle of the strong cutter is the normal front angle of the strong cutter;
acute edge helix angle of the power cutter: beta is afro＝βfo+βco
Sharp edge pressure angle of the power cutter:
sharp edge base circle diameter of the strong gear cutter:
sharp edge base radius of the strong gear cutter: r isbro＝dbro/2
Sharp edge of strong gear cutterFinal measurement of deployment length:
wherein r isbroThe radius of a sharp edge base circle of the powerful gear cutter;
the sharp edge of the strong gear cutter is used for measuring the unfolding length:
the blunt helix angle of the power cutter: beta is afdo＝βfo-βco
Blunt pressure angle of the power slotting cutter:
base circle diameter of blunt edge of the powerful slotting cutter:
base radius of blunt edge of the powerful slotting cutter: r isbdo＝dbdo/2
The final measurement of the unfolding length of the blunt edge of the powerful slotting cutter is as follows:
the extended length of the blunt edge of the powerful slotting cutter is measured:
the tooth thickness of the powerful slotting cutter measures the chord tooth thickness included angle:
wherein alpha isdcloThe end face pressure angle of the measurement circle of the chord tooth height and the chord tooth thickness of the powerful slotting cutter is measured;
dclothe diameter of the circle for measuring the chordal height and the chordal thickness of the powerful slotting cutter, and dclo＝(deo-dio)/2
Measurement chordal tooth height of the powerful slotting cutter: h isclo＝reo-rclocosθ
rcloThe radius of the measuring circle of the chord tooth height and the chord tooth thickness of the powerful slotting cutter; and r isclo＝dclo/2；
Measurement of the chordal tooth thickness of the powerful slotting cutter: sclo＝dclosinθcosβfo。
The design process of this embodiment will be described with reference to specific examples.
Parameters of the gear to be processed are as follows: modulus m is 1.6, pressure angle α is 20 °, number of teeth Z148, the helix angle beta is 0 DEG, and the weighing distance M of the gear tooth thickness is measureddp/dp82.735/2.75, normal tooth thickness Sfn13.419, outside diameter deRoot diameter d 80.25i＝76.234。
Basic parameters of the powerful serrated knife are as follows: modulus m is 1.6, pressure angle α is 20 °, number of teeth Zo64, helix angle betaLo20 DEG, normal rake angle gammaeno5 DEG, normal tooth crest clearance angle alphaeno6 DEG normal tooth thickness Sfno2.694, radius of addendum side arc R1o＝0.3。
Then:
using a newton iterative algorithm, we obtain: alpha is alphajs1＝22°05′38″
dj1＝db1/cosαfs1＝77.887796618；
djo＝dbo/cosαfso＝110.724712371；
Ao1＝rj1+rjo＝94.306254955
deo＝2Ao1-dil＝112.378508991；reo＝deo/2＝56.189254495
dio＝2Ao1-del-05m＝107.562508997
And (3) after the normal front angle and the normal rear angle are injected, the trimming design of the normal tooth form of the powerful gear cutter is as follows:
βfro＝βfo+βco＝22°12′40″
rbro＝dbro/2＝50.649863964
βfdo＝βfo-βco＝17°47′20″
rbdo＝dbdo/2＝50.838986509
the chord tooth height and the chord tooth thickness of the powerful slotting cutter are measured by the following circle diameters: dclo＝(deo-dio)/2＝109.970508991
hclo＝reo-rclocosθ＝1.218100523
Sclo＝dclosinθcosβfo＝2.3407707235。
The design method of the strong gear cutter of the embodiment starts from the meshing relationship between the strong gear cutter and the gear to be processed, and calculates the end face pitch circle pressure angle of the strong gear cutter and the end face pitch circle pressure angle of the gear to be processed by utilizing the relationship that the pitch circle pitch is equal to the pitch circle tooth thickness of the gear to be processed and the pitch circle tooth thickness of the strong gear cutter, so that the design of the strong gear cutter can be realized by combining other known parameters; and when the gear is machined by adopting the strong gear cutting knife designed by the method of the embodiment, compared with the common pinion cutter, the machining efficiency can be improved by 4-8 times, the tooth surface roughness Rz is improved by 2-3 grades, and the machining precision of the gear reaches ISO7 grade.
The design method of the strong gear cutter of the embodiment utilizes the meshing principle that a pair of staggered shaft cylindrical gears are formed between the axial line of the strong gear cutter and the axial line of the processed gear without clearance meshing when strong gear cutting is carried out, realizes the normal tooth profile design and the end face tooth profile design of the strong gear cutter, realizes the correction design of the normal tooth profile of the strong gear cutter after the normal front angle and the normal rear angle are injected, finally solves the difficult problem of theoretical design by verifying a structure diagram, a meshing diagram, a generating diagram, a meshing tooth profile diagram, a normal measurement tooth profile diagram of the strong gear cutter and the like, overcomes the technical problem that the strong gear scraper can only be designed by adopting an approach algorithm in the prior art, achieves the expected effect through multiple actual processing tests, improves the geometric precision, the surface roughness and the production efficiency of the tooth surface, the cost is reduced and the user can confirm the cost.
The above-mentioned embodiments are merely preferred embodiments for fully illustrating the present invention, and the scope of the present invention is not limited thereto. The equivalent substitution or change made by the technical personnel in the technical field on the basis of the invention is all within the protection scope of the invention. The protection scope of the invention is subject to the claims.
Claims (6)
1. A design method of a powerful gear cutter is characterized by comprising the following steps: when strong gear cutting is carried out, an axis crossing angle is formed between the axis of a strong gear cutting knife and the axis of a gear to be processed, namely, a pair of staggered shaft cylindrical gears are meshed without clearance between the strong gear cutting knife and the gear to be processed, and according to the meshing principle, the gear cutting machine comprises:
Pjn＝Sjn1+Sjno
wherein, PjnIs pitch circle pitch; sjn1The pitch circle tooth thickness of the gear to be processed; sjnoThe pitch circle tooth thickness of the strong gear cutter; m is a modulus; alpha is alphafnIs a reference circle pressure angle; alpha is alphajnIs a pitch circle pressure angle;
Sfn1the normal tooth thickness of the gear to be processed; z1The number of teeth of the processed gear; alpha is alphafs1The end face of the gear to be processed is divided into a circle pressure angle; alpha is alphajs1The pitch circle pressure angle is the end face pitch circle pressure angle of the gear to be processed; beta is ab1The base circle helix angle of the gear to be processed; beta is aj1Is the pitch circle helical angle of the gear to be processed; dj1The pitch circle diameter of the gear to be processed; and d isj1＝db1/cosαfs1，db1Is the base circle diameter of the gear to be processed;
Sfnothe normal tooth thickness of the strong gear cutter; zoThe number of teeth of the powerful gear cutter is shown; alpha is alphafsoThe end face of the powerful gear cutter is provided with a reference circle pressure angle; alpha is alphajsoThe pressure angle is the pitch circle pressure angle of the end surface of the strong gear cutter; beta is aboThe base circle helix angle of the strong gear cutter; beta is ajoIs the pitch circle helical angle of the powerful gear cutter; djoThe pitch circle diameter of the powerful gear cutter; and d isjo＝dbo/cosαfso，dboThe diameter of the base circle of the powerful gear cutter;
the normal engagement angle of a pair of staggered shaft cylindrical gears formed between the powerful gear cutting knife and the processed gear is equal, and then:
sinαjn＝sinαjs1cosβb1＝sinαjsocosβbo
namely:
this gives:
this equation is converted to an identity:
wherein F is a constant and:
it is known that f (α)js1) In which only the pitch circle pressure angle alpha of the end face of the gear to be machinedjs1For unknown parameters, a Newton iteration method is adopted to carry out pitch circle pressure angle alpha on the end face of the gear to be machinedjs1And solving to obtain:
wherein, f' (α)js1(n)) Is f (alpha)js1(n)) N is a positive integer greater than or equal to 0;
according to the calculated pitch circle pressure angle alpha of the end surface of the machined gearjs1Further obtain the end surface pitch circle pressure angle alpha of the strong gear cutterjsoComprises the following steps:
2. the power cutter designing method according to claim 1, characterized in that:
the outer diameter of the powerful gear cutter is as follows: deo＝2Ao1-dil
The root diameter of the powerful gear cutting knife is as follows: dio＝2Ao1-del-05m
Wherein d isilThe root diameter of the gear to be processed; delThe outer diameter of the gear to be processed;
Ao1is the meshing center distance between the powerful gear cutting knife and the gear to be processed, and Ao1＝rj1+rjo；
rj1Is the pitch circle radius of the gear to be machined, and
rjothe pitch circle radius of the strong gear cutter; and is
3. The power cutter designing method according to claim 2, characterized in that: the measurement stopping circle radius of the powerful gear cutter is as follows:
wherein R is1oThe arc radius of the tooth top side of the strong gear cutter is the transition circle radius of the two sides of the tooth top of the strong gear cutter; r iseo＝deo/2；rboIs the base radius of the strong gear cutter, and rbo＝dbo/2。
4. A power cutter design method according to claim 3, characterized in that: length of meshing line between the strong gear cutter and the gear to be processed:
wherein r isb1Is the base radius of the gear to be machined, and rb1＝db1/2。
5. The power cutter design method according to claim 4, characterized in that: measurement of initial circle radius of the power cutter:
wherein r ise1Is the radius of the addendum circle of the gear to be machined.
6. A power cutter design method according to any one of claims 1 to 5, characterized in that: after the normal front angle and the normal back angle are injected, the shaping design method of the powerful gear cutting knife comprises the following steps:
axial relief angle of the power cutter:
wherein alpha isenoThe normal tooth top back angle of the powerful gear cutter is adopted; beta is afoThe pitch circle helix angle of the powerful gear cutter;
pitch circle side relief angle of the power cutter:
wherein, γenoThe normal front angle of the strong cutter is the normal front angle of the strong cutter;
acute edge helix angle of the power cutter: beta is afro＝βfo+βco
Sharp edge pressure angle of the power cutter:
sharp edge base circle diameter of the strong gear cutter:
sharp edge base radius of the strong gear cutter: r isbro＝dbro/2
The final measurement of the expansion length of the sharp edge of the powerful gear cutter is as follows:
the sharp edge of the strong gear cutter is used for measuring the unfolding length:
the blunt helix angle of the power cutter: beta is afdo＝βfo-βco
Blunt pressure angle of the power slotting cutter:
base circle diameter of blunt edge of the powerful slotting cutter:
base radius of blunt edge of the powerful slotting cutter: r isbdo＝dbdo/2
The final measurement of the unfolding length of the blunt edge of the powerful slotting cutter is as follows:
the extended length of the blunt edge of the powerful slotting cutter is measured:
the tooth thickness of the powerful slotting cutter measures the chord tooth thickness included angle:
wherein alpha isdcloThe end face pressure angle of the measurement circle of the chord tooth height and the chord tooth thickness of the powerful slotting cutter is measured;
dclothe diameter of the circle for measuring the chordal height and the chordal thickness of the powerful slotting cutter, and dclo＝(deo-dio)/2
Measurement chordal tooth height of the powerful slotting cutter: h isclo＝reo-rclocosθ
rcloThe radius of the measuring circle of the chord tooth height and the chord tooth thickness of the powerful slotting cutter; and r isclo＝dclo/2；
Measurement of the chordal tooth thickness of the powerful slotting cutter: sclo＝dclosinθcosβfo。
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