A dresser structure and parameter design method for dressing a honing wheel

Abstract

This invention discloses a dresser structure and parameter design method for dressing honing wheels. It includes: Step 1: Determining the dresser gauge span M2 based on the parameters of the gear being processed; Step 2: Calculating the dresser wheel tip circle diameter da2; Step 3: Calculating the dresser wheel root circle diameter dg2; Step 4: Calculating the dresser wheel effective root circle diameter dnf2; Step 5: Calculating the dresser wheel effective tip circle diameter dna2; Step 6: Designing the dresser wheel structure for dressing honing wheels based on the parameters obtained in steps 1, 2, 3, 4, and 5. This invention improves the processing life of the dresser through enhanced dresser structure and parameter design.

Description

Technical Field

[0001] This invention belongs to the field of precision gear manufacturing technology, specifically relating to a dresser structure and parameter design method for dressing honing wheels. Background Technology

[0002] Due to the high-speed and high-torque performance requirements of motors, the precision requirements for gears in new energy vehicle reducers are becoming increasingly higher. The precision level reaches 5-6, the tooth profile and tooth direction shape error are required to be <1.5uM, and the drum shape error is required to be within ±2uM. Most gears even include special requirements such as tooth tip edge trimming and tooth root edge trimming. All of these are aimed at ensuring excellent NVH performance of the gears at high speeds.

[0003] To meet the stringent precision requirements of gears in new energy vehicle reducers, most mainstream gear processing techniques employ gear hobbing and grinding or gear hobbing and hobbing honing. Homing, due to its different surface texture compared to grinding, results in superior NVH performance in honed parts. Furthermore, with the development of new energy vehicles, shaft gears, due to their compact design, can only be processed using honing instead of grinding, leading to the increasingly widespread application of honed gears.

[0004] Because honing dressers use an internal meshing mechanism with the grinding wheel, the main motions during dressing include generating motion, radial feed motion, and axial feed motion. Therefore, the internal meshing and motion method result in a small structural size for the dressing wheel, with an outer diameter <90mm, a dressing wheel thickness <6mm, and a tooth tip circle thickness ≤0.5mm. This makes the dressing wheel prone to chipping. Furthermore, because the dressing wheel is small in size, there is less diamond coating, resulting in a smaller overall number of processed parts, a shorter dressing wheel life, and a higher unit cost. Summary of the Invention

[0005] The purpose of this invention is to overcome the shortcomings of the above-mentioned background technology and provide a dresser structure and parameter design method for dressing honing wheels.

[0006] The technical solution adopted in this invention is: a dresser structure for dressing honing wheels, comprising a base, a dressing wheel and a press-fit ring, wherein a protruding portion is provided in the middle of one side of the base, and the dressing wheel and the press-fit ring are disposed on the protruding portion from the inside to the outside.

[0007] The outer side of the press-fit ring is flush with the outer side of the protrusion.

[0008] A method for designing the structural parameters of a dresser for dressing honing wheels includes the following steps:

[0009] Step 1: Determine the dressing wheel gauge span M2 based on the parameters of the gear being machined;

[0010] Step 2: Calculate the tip circle diameter da2 of the dressing gear teeth;

[0011] Step 3: Calculate the root circle diameter dg2 of the dressing wheel;

[0012] Step 4: Calculate the effective root circle diameter dnf2 of the dressing wheel;

[0013] Step 5: Calculate the effective tip circle diameter dna2 of the dressing wheel;

[0014] Step Six: Based on the parameters obtained in Steps One, Two, Three, Four, and Five, design a dressing wheel for dressing the honing wheel.

[0015] The specific details for determining the dressing wheel gauge span M2 include:

[0016] 1) Given conditions: Normal module Mn1, number of teeth Z1, normal pressure angle an1, displacement coefficient Xn1, pitch circle helix angle Bf1, pitch circle end face pressure angle at1 of the gear being machined; Normal module Mn3, number of teeth Z3, normal pressure angle an3, displacement coefficient Xn3, pitch circle helix angle Bf3, pitch circle end face pressure angle at3 of the mating gear; Normal module Mn2, number of teeth Z2, normal pressure angle an2, pitch circle helix angle Bf2, pitch circle end face pressure angle at2 of the dressing gear;

[0017] From the gear meshing conditions, we know that: Mn1=Mn2=Mn3=Mn; Mt1=Mt2=Mt3=Mt; an1=an2=an3=an; at1=at2=at3=at; Bf1=Bf2=Bf3=Bf;

[0018] 2) Calculate the displacement coefficient Xn2 of the dressing wheel;

[0019] Xn2 = Xn1 - ζ, where the coefficient ζ is e / Mn and e is 0.14;

[0020] 3) Calculate the diameter dp of the measuring rod;

[0021] The diameter of the measuring rod is dp = df1 * (cosan * tg(an + 90° / Z1) - sinan), where df1 = Mt * Z1; where df1 is the pitch circle diameter of the gear being machined; and an is the normal pressure angle of the pitch circle.

[0022] 4) Determine the span M2 of the dressing wheel gauge bar;

[0023] Invax=2*Xn2 / (Z2*ctgan)+Invat+dp / (do2*cosB02)-90° / (2*Z2);

[0024] In the formula, Invax is the development angle on the involute line where the center of the gauge bar is located; ax is the pressure angle on the involute line where the center of the gauge bar is located; Invat is the development angle on the involute line where the pressure angle of the pitch circle is located; and at is the meshing pressure angle on the upper end face of the pitch circle.

[0025] The dressing wheel base circle diameter do2 = Mt * Z2 * cosat, and the dressing wheel base circle helix angle cosB02 = sinBf * cosan;

[0026] Base number of teeth M2 = (Mt*Z2*cosBf)*cos(90° / Z2) / cosax+dp;

[0027] Even-numbered teeth M2=(Mt*Z2*cosBf) / cosax+dp; where ax=tgax-Invax.

[0028] Calculating the tip circle diameter da2 of the dressing gear includes:

[0029] 1) Calculate the variation in center distance yt13 between the machined gear and the mating gear;

[0030] yt13==Mt*(Z1+Z3) / 2*((cosat / cosax1)-1);

[0031] In the formula, ax1 is the actual end face meshing pressure angle of the machined gear and the mating gear; at is the upper end face meshing pressure angle of the pitch circle.

[0032] 2) Calculate the change in center distance yt23 between the dressing wheel and the mating gear;

[0033] yt23=Mt*(Z2+Z3) / 2*((cosat / cosax2)-1);

[0034] In the formula, ax2 is the actual end face meshing pressure angle of the dressing wheel and the mating gear; at is the end face meshing pressure angle of the pitch circle.

[0035] 3) Calculate the tip circle diameter da2 of the dressing gear;

[0036] The dressing gear tooth tip circle diameter da2=Mt*Z2+2*((da1-df1) / (2*Mt)-ζ-yt13-yt23); where da1 is the tip circle diameter of the gear being machined; df1 is the pitch circle diameter of the gear being machined.

[0037] Calculating the root circle diameter dg2 of the dressing wheel includes:

[0038] The diameter of the root circle of the dressing gear is dg2 = (Z2 - 2*((df1-dg1) / (2*Mt)+ζ))Mt; where df1 is the pitch circle diameter of the gear being machined; and dg1 is the root circle diameter of the gear being machined.

[0039] The calculation of the effective tip circle diameter dnf2 of the dressing wheel includes:

[0040] The effective root circle diameter of the dressing wheel is dnf2 = 2 * SQRT((A23' * sin(RADIANS(αt)) - SQRT(ra3^2 - rb3^2))^2 + Mt * Z2 * cosat / 2^2); the actual center distance between the dressing wheel and the mating wheel is A23' = (df2 + df3) / 2 * (cosat / cosax2); where ra3 is the addendum circle radius of the mating gear; rb3 is the base circle radius of the mating gear; df2 is the pitch circle diameter of the dressing wheel; df3 is the pitch circle diameter of the mating wheel; at is the meshing pressure angle on the upper end face of the pitch circle; and ax2 is the actual end face meshing pressure angle between the dressing wheel and the mating gear.

[0041] The calculation of the effective tip circle diameter dna2 of the dressing wheel includes:

[0042] Effective tooth tip circle diameter dna2 = da2 - (da1 - dna1);

[0043] In the formula, da2 is the tip circle diameter of the dressing gear; da1 is the tip circle diameter of the gear being machined; and dna1 is the effective tip circle diameter of the gear being machined.

[0044] This invention relates to a dresser structure for dressing (cutting) honing wheels. Through structural and parameter design improvements, the dresser's service life is increased, unit cost is reduced, and the honing process is more widely applied in gear manufacturing. The dresser's external structure comprises three main components: a base, a dressing wheel, and a press-fit ring. Detailed parameter and tooth profile design were implemented for the key component, the dressing wheel. Attached Figure Description

[0045] Figure 1 This is a front view of the trimmer structure of the present invention;

[0046] Figure 2 This is a cross-sectional view of the trimmer structure of the present invention;

[0047] Figure 3 This is a cross-sectional view of the substrate of the present invention;

[0048] Figure 4 This is a cross-sectional view of the dressing wheel of the present invention;

[0049] Figure 5 This is a cross-sectional view of the press-fitting wheel of the present invention;

[0050] Figure 6 This is a diagram showing the tooth profile accuracy of the present invention;

[0051] Figure 7 This is a multi-segment line diagram of the tooth profile of the present invention. Detailed Implementation

[0052] The present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments to facilitate a clear understanding of the present invention, but these descriptions do not constitute a limitation on the present invention.

[0053] like Figure 1 , Figure 2 As shown, the dresser structure 100 for dressing honing wheels of the present invention consists of three parts: a base 101, a dressing wheel 102, and a press-fit ring 103. A raised portion 1011 is provided in the middle of one side of the base 100, and the dressing wheel 102 and the press-fit ring 103 are disposed on the raised portion 1011 from the inside out. The outer side of the press-fit ring 103 is flush with the outer side of the raised portion 1011.

[0054] In this embodiment, the dimensions of the substrate 101 are ( Figure 3 As shown: the outer diameter ΦD1 is infinitely close to the outer diameter of the dressing wheel to ensure the strength of the honing dresser teeth and to ensure that the dressing teeth are not easily chipped; the inner diameter ΦD2 is set according to the machine tool installation requirements, and the tolerance is controlled within 2μm; the material is alloy steel, and the core hardness is required to be 500HV and the surface hardness is required to be 850HV.

[0055] In this embodiment, the size of the dressing wheel 102 is ( Figure 4 (As shown): The outer diameter ΦD5 is designed. The inner hole ΦD4 of the dressing wheel matches the dimensions of the base 101, requiring a transition fit; the thickness of the dressing wheel is a key factor determining its service life. Theoretically, its thickness L is defined as 2MM < L < 4MM, which satisfies both the machining life design and the overall dimensions of the dressing wheel. The tooth thickness, addendum circle, dedendum circle, and effective dedendum circle of the dressing wheel are calculated based on the design. The dressing wheel is made of a special double-layer electroplated diamond material, with a diamond layer thickness of 2MM and a diamond adhesion layer thickness of 1MM. This is to ensure that the overall width of the contact area between the dresser and the part is less than 12MM, while simultaneously meeting the requirements for machining life and machining quality.

[0056] Press-fit ring 103 dimensions ( Figure 5 As shown): Its structural dimensions can ensure the strength of the dressing wheel, its outer diameter ΦD7 is infinitely close to the tooth root circle, the material is alloy steel, and the core hardness is guaranteed to be 500HV; the surface hardness is 860HV.

[0057] In this embodiment, the processing and assembly requirements for the dresser structure 100 are as follows: the base and dressing wheel are manufactured by gear hobbing, heat treatment, gear grinding, press bonding, micro-forming grinding, and electroplating. The inner diameter of the dressing wheel and the inner diameter of the press ring are adapted to the diameter of the base step. Before assembly, a special high-strength adhesive is applied to the mating surfaces to ensure that the three are firmly bonded together. After installation, the perpendicularity between the inner hole and the end face is required to be less than 2 μm.

[0058] The parameter design method for the dressing wheel 102 in the dressing device structure 100 of the present invention includes the following steps:

[0059] 1. Given conditions

[0060] The gear being machined has the following parameters: normal module Mn1, number of teeth Z1, normal pressure angle an1, displacement coefficient Xn1, pitch circle helix angle Bf1, and pitch circle end face pressure angle at1; the mating gear has the following parameters: normal module Mn3, number of teeth Z3, normal pressure angle an3, displacement coefficient Xn3, pitch circle helix angle Bf3, and pitch circle end face pressure angle at3; the dressing gear has the following parameters: normal module Mn2, number of teeth Z2, normal pressure angle an2, pitch circle helix angle Bf2, and pitch circle end face pressure angle at2.

[0061] From the gear meshing conditions, we know that: Mn1=Mn2=Mn3=Mn; Mt1=Mt2=Mt3=Mt; an1=an2=an3=an; at1=at2=at3=at; Bf1=Bf2=Bf3=Bf.

[0062] 2. Determine the span M2 of the dressing wheel gauge bar.

[0063] 2.1 Calculate the displacement coefficient Xn2 of the dressing wheel.

[0064] Since the dressing wheel and the gear being machined are meshed, theoretically their pitch circle (or other circle) tooth thicknesses are equal, i.e., their displacement coefficients are equal. However, the dressing wheel and the honing wheel mesh without backlash, and the honing wheel and the gear being machined also mesh without backlash. To ensure that the final machined gear maintains sufficient backlash, and simultaneously ensure that the honing wheel has sufficient clearance at the tooth root, the displacement coefficient Xn2 of the dressing wheel is generally taken to be less than the displacement coefficient Xn1 of the gear being machined. That is, the value of Xn2 of the dressing wheel is:

[0065] Xn2 = Xn1 - ζ, where the coefficient ζ is e / Mn and e is 0.14.

[0066] 2.2 Calculate the diameter dp of the measuring rod

[0067] The diameter of the measuring rod is dp = df1 * (cosan * tg(an + 90° / Z1) - sinan), where df1 = Mt * Z1; where df1 is the pitch circle diameter of the gear being machined; and an is the normal pressure angle of the pitch circle.

[0068] 2.3 Determine the span M2 of the dressing wheel gauge bar.

[0069] Invax=2*Xn2 / (Z2*ctgan)+Invat+dp / (do2*cosB02)-90° / (2*Z2);

[0070] In the formula, Invax is the development angle on the involute line where the center of the gauge bar is located; ax is the pressure angle on the involute line where the center of the gauge bar is located; Invat is the development angle on the involute line where the pressure angle of the pitch circle is located; and at is the meshing pressure angle of the upper end face of the pitch circle.

[0071] The dressing wheel base circle diameter do2 = Mt * Z2 * cosat, and the dressing wheel base circle helix angle cosB02 = sinBf * cosan;

[0072] Base number of teeth M2 = (Mt*Z2*cosBf)*cos(90° / Z2) / cosax+dp;

[0073] For even-numbered teeth, M2 = (Mt * Z2 * cosBf) / cosax + dp; by using ax = tgax - Invax, we can find ax and thus cosax.

[0074] 3. Calculate the addendum circle diameter da2 of the dressing gear.

[0075] 3.1 Calculate the variation in center distance yt13 between the machined gear and the mating gear.

[0076] Invax1=2*(Xn1+Xn3)tgan / (Z1+Z3)+Invat,

[0077] By using Invax1 = tgax1 - ax1, we can find ax1, and then find cosax1.

[0078] In the formula, ax1 is the actual end face meshing pressure angle of the machined gear and the mating gear; at is the upper end face meshing pressure angle of the pitch circle; Invax1 is the development angle of the involute line where the meshing point is located.

[0079] The theoretical center distance between the machined gear and the mating gear is A13 = (d1 + d3) / 2 = (Z1 + Z3) * Mt / 2;

[0080] In the formula, d1 is the pitch circle diameter of the gear being machined, and d3 is the pitch circle diameter of the mating gear;

[0081] The actual center distance between the machined gear and the mating gear is A13' = (d1 + d3) / 2 * (cosat / cosax1);

[0082] The variation in the center distance between the machined gear and the mating gear is yt13 = A13' - A13 = (Z1 + Z3) * Mt / 2 * (cosat / cosax1) - (Z1 + Z3) * Mt / 2;

[0083] yt13==Mt*(Z1+Z3) / 2*((cosat / cosax1)-1).

[0084] 3.2 Calculate the variation in center distance yt23 between the dressing wheel and the mating gear.

[0085] Invax2=2(Xn2+Xn3)*tgan / (Z2+Z3)+Invat,

[0086] Find ax² using Invax² = tgax² - ax, and then find cosax².

[0087] In the formula, ax2 is the actual end face meshing pressure angle of the dressing wheel and the mating gear; at is the upper end face meshing pressure angle of the pitch circle; Invax2 is the development angle on the involute line where the meshing point is located.

[0088] The theoretical center distance between the dressing wheel and the mating wheel is A23 = (df2 + df3) / 2 = (Z2 + Z3) * Mt / 2;

[0089] In the formula, df2 is the pitch circle diameter of the dressing wheel; df3 is the pitch circle diameter of the mating wheel;

[0090] The actual center distance between the dressing wheel and the mating wheel is A23' = (df2 + df3) / 2 * (cosat / cosax2);

[0091] Variation in center distance between dressing wheel and mating gear

[0092] yt23=A23-A23=(df2+df3) / 2*(cosat / cosax2)-(Z2+Z3)*Mt / 2=Mt*(Z2+Z3) / 2*(cosat / cosax2)-(Z2+Z3)*Mt / 2;

[0093] yt23=Mt*(Z2+Z3) / 2*((cosat / cosax2)-1).

[0094] 3.3 Calculate the total displacement coefficient of the machined part and the mating gears.

[0095] The total displacement coefficient of the machined part and the mating gear is ∑Xn13=Xn1+Xn3;

[0096] The total displacement coefficient of the dressing wheel and the mating gear is ∑Xn23=Xn2+Xn3.

[0097] 3.4 Calculate the total variation coefficient of the machined part and the mating gears.

[0098] The total variation coefficient of the machined part and the mating gear is k13 = ∑Xn13 - yt13;

[0099] The total variation coefficient of the dressing wheel and the paired gear is k23 = ∑Xn23 - yt23.

[0100] 3.5 Calculate the tooth tip height coefficient ha1* of the machined part.

[0101] ha1=(ha1*+Xn1–k13)*Mt, where ha1=(da1-df1) / 2; da1 is the addendum circle diameter of the gear being machined; df1 is the pitch circle diameter of the gear being machined;

[0102] The tooth tip height coefficient of the machined part is ha1*=(da1-df1) / (2*Mt)-Xn1+K13=(da1-df1) / (2*Mt)-Xn1+Xn2+Xn3-yt13=(da1-df1) / (2*Mt)-ζ+Xn3-yt13.

[0103] 3.6 Calculate the addendum ha2 of the dressing gear.

[0104] ha2=(ha2*+Xn2–k23)*Mt, where ha2*=ha1*, therefore

[0105] ha2=(da1-df1) / (2*Mt)-ζ+Xn3-yt13+Xn2-((Xn2+Xn3)-yt23));

[0106] The addendum of the dressing wheel is ha2 = (da1 - df1) / (2 * Mt) - ζ - yt13 - yt23.

[0107] 3.7 Calculate the addendum circle diameter da2 of the dressing gear teeth.

[0108] Dressing the tip circle diameter of the gear teeth: da2 = df2 + 2ha2 = Mt*Z2 + 2*ha2 = Mt*Z2 + 2*

[0109] ((da1-df1) / (2*Mt)-ζ-yt13-yt23).

[0110] 4. Find the diameter dg2 of the root circle of the dressed gear tooth.

[0111] 4.1 Calculate the clearance coefficient c1* of the workpiece.

[0112] The root height of the gear being machined is hf1 = (ha1* + c1* - Xn1)*Mt;

[0113] The root height of the gear being machined is hf1 = (df1 - dg1) / 2, where df1 is the pitch circle diameter of the gear being machined, and dg1 is the root circle diameter of the gear being machined.

[0114] The clearance coefficient of the workpiece is c1*=(df1-dg1) / (2*Mt)-ha1*+Xn1.

[0115] 4.2 Calculate the root height hf2 of the dressed gear teeth.

[0116] The root height of the dressed gear teeth is hf2 = (ha2* + c2* - Xn2)*Mt, ha1* = ha2*, c1* = c2*;

[0117] hf2=(ha1*+c1*-Xn2)Mt=((ha1*+(df1-dg1) / (2*Mt)-ha1*+Xn1-Xn1+

[0118] ζ)Mt;

[0119] Adjust the root height of the gear teeth hf2=((df1-dg1) / (2*Mt)+ζ)Mt;

[0120] The diameter of the tooth root circle of the dressing wheel is dg2 = df2 - 2hf2, df2 = MtZ2;

[0121] The diameter of the root circle of the dressing wheel tooth is dg2 = (Z2 - 2*((df1-dg1) / (2*Mt)+ζ))Mt.

[0122] 5. Calculate the effective root circle diameter of the dressing gear (dnf2).

[0123] 5.1 Determine the backlash-free meshing center distance A23' between the dressing wheel and the mating gear.

[0124] =(df2+df3) / 2*(cosat / cosax2);

[0125] In the formula, Invax2=2(Xn2+Xn3)tgan / (Z2+Z3)+Invat; by using Invax2=tgax2-ax2, we can find ax2, and then find cosax2;

[0126] 5.2 Calculate the effective root circle radius rnf2 of the dressing wheel.

[0127] The radius of the dressing wheel base circle is rb2 = Mt * Z2 * cosat / 2;

[0128] The effective root circle radius of the dressing wheel is rnf2=SQRT((A23')

[0129] *sin(RADIANS(αt))-SQRT(ra3^2-rb3^2))^2+Mt*Z2*cosat / 2^2);

[0130] In the formula, ra3 is the tip circle radius of the paired gear; rb3 is the base circle radius of the paired gear.

[0131] 5.3 Determine the effective root circle diameter dnf2 of the dressing wheel.

[0132] The effective root circle diameter of the dressing wheel is dnf2 = 2rnf2 = 2*SQRT((A23')

[0133] *sin(RADIANS(αt))-SQRT(ra3^2-rb3^2))^2+Mt*Z2*cosat / 2^2).

[0134] 6. Determine the effective tip circle diameter (dna2) of the dressed gear.

[0135] Effective tooth tip circle diameter dna2 = da2 - (da1 - dna1);

[0136] In the formula, da2 is the tip circle diameter of the dressing gear; da1 is the tip circle diameter of the gear being machined; and dna1 is the effective tip circle diameter of the gear being machined.

[0137] Tooth profile modification design of the dressing wheel in the dresser

[0138] The tooth profile is drawn using a multi-point simulation method to create the tooth profile modification diagram of the part, thereby generating the tool modification diagram. This solves the problem that general software is not easy to design complex multi-segment tooth profiles. For some gears with strict NVH requirements, the tooth profile adopts a multi-segment design, such as tooth tip edge modification, tooth root edge modification, and intermediate tooth profile modification requirements such as bulging amount and tooth profile. General design software is difficult to design complex multi-segment tooth profiles. The computer multi-point simulation method is used to draw the tooth profile diagram of the dressing wheel, which solves this technical problem. It can perfectly design any complex multi-segment tooth profile diagram, which is convenient for machine tool processing.

[0139] The contents not described in detail in this specification are existing technologies known to those skilled in the art.

Claims

1. A dressing device structure for dressing honing wheels, characterized in that: It includes a base, a dressing wheel and a press-fit ring, wherein a protruding part is provided in the middle of one side of the base, and the dressing wheel and the press-fit ring are disposed on the protruding part from the inside to the outside; The parameter design method for dressing the honing wheel dressing device structure includes the following steps: Step 1: Determine the dressing wheel gauge span M2 based on the parameters of the gear being machined; Step 2: Calculate the tip circle diameter da2 of the dressing gear teeth; Step 3: Calculate the root circle diameter dg2 of the dressing wheel; Step 4: Calculate the effective root circle diameter dnf2 of the dressing wheel; Step 5: Calculate the effective tip circle diameter dna2 of the dressing wheel; Step Six: Based on the parameters obtained in Steps One, Two, Three, Four, and Five, design a dressing wheel for dressing the honing wheel. The specific steps for determining the dressing wheel gauge span M2 include: 1) Given conditions: Normal module Mn1, number of teeth Z1, normal pressure angle an1, displacement coefficient Xn1, pitch circle helix angle Bf1, pitch circle end face pressure angle at1 of the gear being machined; Normal module Mn3, number of teeth Z3, normal pressure angle an3, displacement coefficient Xn3, pitch circle helix angle Bf3, pitch circle end face pressure angle at3 of the mating gear; Normal module Mn2, number of teeth Z2, normal pressure angle an2, pitch circle helix angle Bf2, pitch circle end face pressure angle at2 of the dressing gear; From the gear meshing conditions, we know that: Mn1=Mn2=Mn3=Mn; Mt1=Mt2=Mt3=Mt; an1=an2=an3=an; at1=at2=at3=at; Bf1=Bf2=Bf3=Bf; 2) Calculate the displacement coefficient Xn2 of the dressing wheel; Xn2 = Xn1 - ζ, where the coefficient ζ is e / Mn and e is 0.14; 3) Calculate the diameter dp of the measuring rod; The diameter of the measuring rod is dp = df1 * (cosan * tg(an + 90° / Z1) - sinan), where df1 = Mt * Z1; where df1 is the pitch circle diameter of the gear being machined; and an is the normal pressure angle of the pitch circle. 4) Determine the span M2 of the dressing wheel gauge bar; Invax=2*Xn2 / (Z2*ctgan)+Invat+dp / (do2*cosB02)-90° / (2*Z2); In the formula, Invax is the development angle on the involute line where the center of the gauge bar is located; ax is the pressure angle on the involute line where the center of the gauge bar is located; Invat is the development angle on the involute line where the pressure angle of the pitch circle is located; and at is the meshing pressure angle on the upper end face of the pitch circle. The dressing wheel base circle diameter do2 = Mt * Z2 * cosat, and the dressing wheel base circle helix angle cosB02 = sinBf * cosan; Odd-numbered teeth M2 = (Mt*Z2*cosBf)*cos(90° / Z2) / cosax+dp; Even-numbered teeth M2 = (Mt * Z2 * cosBf) / cosax + dp; where ax = tgax - Invax.

2. The dressing device structure for dressing honing wheels according to claim 1, characterized in that: The outer side of the press-fit ring is flush with the outer side of the protrusion.

3. The parameter design method for a dresser structure for dressing honing wheels according to claim 1, characterized in that: Calculating the tip circle diameter da2 of the dressing gear includes: 1) Calculate the variation in center distance yt13 between the machined gear and the mating gear; yt13==Mt*(Z1+Z3) / 2*((cosat / cosax1)-1); In the formula, ax1 is the actual end face meshing pressure angle of the machined gear and the mating gear; at is the end face meshing pressure angle of the pitch circle. 2) Calculate the change in center distance yt23 between the dressing wheel and the mating gear; yt23=Mt*(Z2+Z3) / 2*((cosat / cosax2)-1); In the formula, ax2 is the actual end face meshing pressure angle of the dressing wheel and the mating gear; at is the upper end face meshing pressure angle of the pitch circle. 3) Calculate the tip circle diameter da2 of the dressing gear; The dressing gear tooth tip circle diameter da2 = Mt*Z2 + 2*((da1-df1) / (2*Mt)-ζ-yt13-yt23; where da1 is the tip circle diameter of the gear being machined; df1 is the pitch circle diameter of the gear being machined.

4. The parameter design method for a dresser structure for dressing honing wheels according to claim 1, characterized in that: Calculating the root circle diameter dg2 of the dressing wheel includes: The diameter of the root circle of the dressing gear is dg2 = (Z2 - 2*((df1-dg1) / (2*Mt)+ζ))Mt; where df1 is the pitch circle diameter of the gear being machined; and dg1 is the root circle diameter of the gear being machined.

5. The parameter design method for a dresser structure for dressing honing wheels according to claim 1, characterized in that: The calculation of the effective tip circle diameter dnf2 of the dressing wheel includes: The effective root circle diameter of the dressing wheel is dnf2 = 2 * SQRT((A23' * sin(RADIANS(αt)) - SQRT(ra3^2 - rb3^2))^2 + Mt * Z2 * cosat / 2^2); the actual center distance between the dressing wheel and the mating wheel is A23' = (df2 + df3) / 2 * (cosat / cosax2); where ra3 is the addendum circle radius of the mating gear; rb3 is the base circle radius of the mating gear; df2 is the pitch circle diameter of the dressing wheel; df3 is the pitch circle diameter of the mating wheel; at is the meshing pressure angle on the upper end face of the pitch circle; and ax2 is the actual end face meshing pressure angle between the dressing wheel and the mating gear.

6. The parameter design method for a dresser structure for dressing honing wheels according to claim 1, characterized in that: The calculation of the effective tip circle diameter dna2 of the dressing wheel includes: Effective tooth tip circle diameter dna2 = da2 - (da1 - dna1); In the formula, da2 is the tip circle diameter of the dressing gear; da1 is the tip circle diameter of the gear being machined; and dna1 is the effective tip circle diameter of the gear being machined.

Images