Gradual involute pattern plate horizontal measurement method, device and assembly method

Abstract

This invention belongs to the field of precision gear measurement technology, and relates to a horizontal measurement method, device, and assembly method for a large gear involute template. A V-shaped seat and a ball-end support are used to position the large gear involute template, and the deformation of the template caused by a loading block offsets the tooth profile deviation caused by gravity deformation, resulting in a final measurement of the total tooth profile deviation F on the measured tooth surface. ɑ With a precision of less than 0.05μm, this method is highly accurate, low-cost, and simple to operate. It can make the difference in tooth profile deviation caused by gravity deformation between horizontal and vertical measurements of large gear involute templates less than 0.05μm, ensuring consistency of involute tooth profile deviation under different measurement positions. This is beneficial for the traceability and comparison of involute values ​​and can be used for horizontal measurement of high-precision involute templates, showing good application prospects and promotion value.

Description

Technical Field

[0001] This invention belongs to the field of precision gear measurement technology, and relates to a horizontal measurement method, device and assembly method for a large gear involute template. Background Technology

[0002] The involute profile is currently the most widely used and technologically mature gear profile, and it is widely applied in various fields such as gear reduction / transmissions, gear cutting tools, high-end equipment, and industrial robots. High-precision gear involute templates are typically used as involute standards to transmit gear involute parameter values ​​and determine instrument reading errors.

[0003] Regarding large gear templates: The German Federal Institute of Physics and Technology has developed a sector-shaped large gear template with a tip circle diameter of 1000mm and a large gear ring standard template with a tip circle diameter of approximately 2000mm, with involute unfolded lengths of 120mm and 84mm respectively; Chinese invention patent CN202010124770.2 also discloses a large gear multi-parameter standard template with a diameter of 1m; invention patent CN202111007908.1 discloses an involute template for large gear measuring instruments, providing a mechanical structure of a dual-axis circular arc-shaped large-size involute template, simulating the involute through circular arc and error compensation. The aforementioned gear standard templates weigh between 0.5t and 2t. As standard instruments, gear standard templates need to be frequently transported between various metrology departments. The heavy weight of these gear standard templates causes inconvenience in operation and transportation, increasing the difficulty of traceability and value transfer of large gear involute values.

[0004] To facilitate operation and handling, lightweight involute templates for large gears have been developed. Invention patent CN202111128774.9 discloses a shaft-mounted involute template for large gears, which features a compact structure and light weight. When mounted on a turntable at a gear measuring center or coordinate measuring machine via a center or jaws for vertical measurement, the tooth profile deviation caused by gravity deformation is less than 0.05 μm. However, for horizontal measurement using a V-shaped support on a coordinate measuring machine without a turntable, the tooth profile deviation caused by gravity deformation and the difference between this deviation and the vertical measurement result will be greater than 1 μm. This is detrimental to the traceability and transfer of involute curve measurements. Summary of the Invention

[0005] To effectively solve the above-mentioned technical problems, the present invention proposes the following technical solution:

[0006] A horizontal measurement method for a large gear involute template includes the following steps:

[0007] S1: Place the large gear involute template horizontally on a V-shaped support and a ball-end support. The V-shaped support rests on the reference outer cylindrical surface of the large gear involute template, and the ball-end support rests on the root of the tooth surface to be measured. The line connecting the center of gravity of the large gear involute template and the support point of the ball-end support is perpendicular to the central axis of the reference outer cylindrical surface. On the large gear involute template, between the central axis of the reference outer cylindrical surface and the root of the tooth surface to be measured, apply a vertically downward force at a distance L from the central axis of the reference outer cylindrical surface of the large gear involute template. N The pseudo-loaded force F N ;

[0008] S2: Taking the minimization of the total deviation of the tooth profile of the measured tooth surface caused by the gravity deformation of the involute template of the large gear as the optimization objective, calculate the proposed loading force F. N The optimal solution is the loading force F and the proposed loading distance L. N The optimal solution is the loading distance L;

[0009] S3: Based on the actual structure of the large gear involute template, the supporting force at the ball joint support, and the loading force F and loading distance L, use finite element simulation to calculate the total profile deviation F of the large gear involute template after deformation. ɑ ;

[0010] S4: When the total deviation of the tooth profile F ɑ If the diameter is <0.05μm, a loading force F and a loading distance L are used to apply the load, and then the tooth surface to be measured is measured.

[0011] When the total deviation of the tooth profile F ɑ If the deviation is ≥0.05μm, the loading force F and loading distance L are adjusted; and based on the adjusted loading force F and loading distance L, the support force at the ball head support is recalculated. Then, step S3 is repeated to calculate the total tooth profile deviation F after the deformation of the large gear involute template using finite element simulation. ɑ until the total deviation F of the tooth profile ɑ If the diameter is less than 0.05 μm, a loading force F and a loading distance L are used to apply the load, and then the tooth surface to be measured is measured.

[0012] As a supplement to the technical solution, step S2 includes the following steps:

[0013] S2.1: Use the large gear involute template as the cantilever beam;

[0014] The V-shaped seat is used as a hinged support, and the support reaction force of the hinged support is F2;

[0015] The ball head support is used as a sliding support. The support reaction force of the sliding support is F4, and the lever arm length of the sliding support from the center axis of the reference outer cylindrical surface is l4.

[0016] Calculate the weight F1 of the large gear involute template at the hinge support extension section, the weight F3 of the section from the hinge support to the sliding support, the weight F5 of the sliding support extension section, and the lever arm lengths l1, l3, and l5 of the center of gravity of the hinge support extension section, the section from the hinge support to the sliding support, and the sliding support extension section to the center axis of the outer cylindrical surface of the large gear involute template reference; when L N When the value is greater than l3, forces F1 to F5 satisfy the following:

[0017]

[0018] The involute template for the large gear is located at F1~F2, F2~F3, and F3~F N F N The bending moments M1(x) to M5(x) of segments F4 and F4 to F5 satisfy:

[0019]

[0020] Where x is the lever arm length from the characteristic section of the cantilever beam to F1;

[0021] The involute template for the large gear is located at F1~F2, F2~F3, and F3~F N F N The turning angles θ1(x) to θ5(x) of segments ~F4 and F4~F5 satisfy:

[0022]

[0023] Among them, C1, D1, E1, F1, and G1 are undetermined constants;

[0024] The involute template for the large gear is located at F1~F2, F2~F3, and F3~F N F N The deflections w1(x) to w5(x) of segments ~F4 and F4~F5 satisfy:

[0025]

[0026] Among them, C2, D2, E2, F2, and G2 are constants to be determined;

[0027] The boundary conditions for rotation and deflection are satisfied as follows:

[0028]

[0029] When L≤l3

[0030] The involute template for the large gear is located at F1~F2 and F2~F N F N The bending moments M1(x) to M5(x) of segments ~F3, F3~F4, and F4~F5 satisfy:

[0031]

[0032] Where x is the lever arm length from the characteristic section of the cantilever beam to F1;

[0033] Large gear involute template F1~F2, F2~F N F N The turning angles θ1(x) to θ5(x) of segments ~F3, F3~F4, and F4~F5 satisfy:

[0034]

[0035] Among them, C1, D1, E1, F1, and G1 are undetermined constants;

[0036] The involute template for the large gear is located at F1~F2 and F2~F N F N The deflections w1(x) to w5(x) of segments ~F3, F3~F4, and F4~F5 satisfy:

[0037]

[0038] Among them, C2, D2, E2, F2, and G2 are constants to be determined;

[0039] The boundary conditions for rotation and deflection are satisfied as follows:

[0040]

[0041] Then, by combining equations (1) with equations (2) to (5) or equations (1) with equations (6) to (9), the deflection equation W5 of the tooth surface to be measured in the range of 0 to l4 can be obtained.

[0042] S2.2: Taking the minimum total deviation of the tooth profile of the test tooth surface caused by the gravity deformation of the large gear involute template as the optimization objective, the loading force F and loading distance L are calculated according to formula (10);

[0043]

[0044] Where, r root r is the radius of the tooth root circle. tip Let θ be the radius of the tooth tip circle. root Let θ be the development angle of the tooth surface to be measured at the tooth root. tip The angle of the tooth surface to be tested at the tooth tip is denoted as θ.

[0045] As a supplement to the technical solution, in step S3, the method of using finite element simulation is as follows:

[0046] A global gravitational acceleration is added to the involute template model of the large gear, a support force is added at the ball joint support, and a loading force F is added at the loading distance L; based on the simulation results, the total profile deviation F of the involute template after deformation is calculated. ɑ

[0047]

[0048] Where, θ i Let x be the development angle of the involute to be measured, (x) i y i ) represents the coordinates of the nodes of the involute element during finite element analysis, w i For finite element analysis, the involute at node (x) i y i Deformation at point f i Let the expansion angle be θ i Tooth profile deviation at that time.

[0049] As a supplement to the technical solution, the gravity of the section from the hinge support to the sliding support of the large gear involute template is F3, and the lever arm length from F3 to the center axis of the outer cylindrical surface of the large gear involute template is l3; in step S4, when the total deviation F of the tooth profile of the tooth surface to be measured after deformation... ɑ When the thickness is ≥0.05μm, the loading force F and loading distance L are adjusted as follows:

[0050] Based on the finite element simulation results of step S3, calculate the tooth profile deviation f at the root of the involute tooth after deformation. root and the profile deviation f at the tooth tip tip :

[0051]

[0052] Among them, (x r oot,y root ), (x tip ,y tip ) represents the coordinates of the involute tooth root and tooth tip during finite element analysis, w root w tip This refers to the deformation of the involute at the tooth root and tooth tip during finite element analysis.

[0053] When the tooth profile deviation at the root of the involute tooth after deformation is f root The tooth profile deviation f at the tooth tip is less than tip If so, increase the loading force F or make the loading force F closer to F3;

[0054] When the tooth profile deviation at the root of the involute tooth after deformation is f root Tooth profile deviation f greater than the tooth tip tip If so, reduce the loading force F or move the loading force F away from F3.

[0055] As a supplement to the technical solution, in step S4, when measuring the tooth surface to be measured, the large gear involute template is placed on the V-shaped seat and the ball head support seat. After the large gear involute template is installed, it should be left to stand for more than 12 hours to release the installation stress and balance the temperature inside the large gear involute template and the measuring chamber before measuring the tooth surface to be measured.

[0056] As a supplement to the technical solution, a loading force is applied to the large gear involute template by placing a loading block on the template. The weight of the loading block is equal to the loading force F. The optimal distance between the center of gravity of the loading block and the central axis of the outer cylindrical surface of the large gear involute template is the loading distance L.

[0057] The present invention also discloses a horizontal measuring device for a large gear involute template using the method of the above embodiments, comprising a large gear involute template, a V-shaped seat, a loading block, and a ball head support seat;

[0058] The large gear involute template includes a template strip support arm and a tooth surface to be measured. Multiple weight-reducing grooves are arranged along the length of the template strip support arm. A web is provided in the weight-reducing groove, and a weight-reducing hole is provided on the web. The end of the template strip support arm is the tooth surface to be measured.

[0059] The V-shaped seat is located below the large gear involute template and supports the reference outer cylindrical surface of the large gear involute template.

[0060] The ball head support is located below the involute template of the large gear and supports the template strip support arm at the root of the tooth surface to be tested.

[0061] The loading block is disposed within the weight-reducing groove of the large gear involute template. The loading block includes a positioning cylinder, a positioning block, and a loading cylinder. The positioning block is located between the positioning cylinder and the loading cylinder. The positioning cylinder has a cylindrical structure, and its diameter is 1 mm smaller than the diameter of the weight-reducing hole, while its height is greater than the thickness of the web. The loading block also includes a positioning block and a loading cylinder. The positioning block is disposed above the positioning cylinder, and the loading cylinder is disposed above the positioning cylinder. The radial dimension of the positioning block is greater than the diameter of the weight-reducing hole on the web of the loading block, thus supporting the loading cylinder.

[0062] The ball head support includes a supporting ball head, a supporting cylinder, and a supporting base.

[0063] The supporting cylinder is vertically mounted on the supporting base, and the supporting ball head is a hemispherical structure. The supporting ball head is located at the upper end of the supporting cylinder, and the diameter of the supporting ball head is the same as the diameter of the supporting cylinder.

[0064] The ball head support is located below the weight reduction groove on the template support arm that is closest to the tooth surface to be tested. The upper end of the ball head of the ball head support is used to support the web plate in the weight reduction groove. The distance between the outer circumferential surface of the support cylinder and the inner sidewall of the weight reduction groove located on the front side of the support cylinder and the inner sidewall located on the rear side of the support cylinder is less than 0.5mm.

[0065] The assembly method of the horizontal measuring device for the large gear involute template in the above embodiment is as follows:

[0066] Based on the loading force F and the loading distance L, the positioning cylinder of the loading block is placed in the weight-reducing hole on the web of the template support arm, where the distance between the center of the web and the center axis of the reference outer cylindrical surface is closest to the loading distance L. This ensures that the center of gravity of the loading block is located on the axis of the positioning cylinder, allowing the web to support the positioning block. The distance between the center of the weight-reducing hole on the web supporting the loading block and the center axis of the reference outer cylindrical surface of the large gear involute template is the final loading distance L. Z ;

[0067] Maintain loading distance L Z Without changing, the loading force F is adjusted again through steps S3 and S4 of the method described in claim 1; the weight of the loading block is set to be the same as the loading force F, and then the tooth surface to be measured is measured.

[0068] Beneficial Effects: This invention provides a horizontal measurement method for large gear involute templates. The method utilizes a V-shaped seat and a ball-end support to position the template, and the deformation of the template caused by the loading block offsets the tooth profile deviation caused by gravity deformation, ensuring that the total tooth profile deviation Fα of the measured tooth surface after deformation is less than 0.05μm. This method is highly accurate, low-cost, and simple to operate. It ensures that the difference in tooth profile deviation caused by gravity deformation during horizontal and vertical measurements of the large gear involute template is less than 0.05μm, maintaining consistency in involute tooth profile deviation under different measurement positions. This facilitates traceability and comparison of involute values ​​and can be used for horizontal measurement of high-precision large gear involute templates, demonstrating promising application prospects and widespread value. Attached Figure Description

[0069] Figure 1 This is a flowchart of a horizontal measurement method for a large gear involute template according to the present invention.

[0070] Figure 2 This is a schematic diagram of an involute template for a large gear according to the present invention.

[0071] Figure 3 This is a partial cross-sectional view of a large gear involute template according to the present invention.

[0072] Figure 4 This is a schematic diagram of force and lever arm on a large gear involute template according to the present invention.

[0073] Figure 5 This is a schematic diagram of the loading block structure of the present invention.

[0074] Figure 6 This is a schematic diagram of the ball head support structure of the present invention.

[0075] In the figure: 1. Large gear involute template; 1-1. Tooth surface to be measured; 1-2. Reference outer cylindrical surface; 1-3. Weight reduction hole; 1-4. Web plate; 1-5. Rib plate; 1-6. Weight reduction groove; 1-7. Template strip support arm; 2. V-shaped seat; 3. Loading block; 3-1. Positioning cylinder; 3-2. Positioning block; 3-3. Loading cylinder; 4. Ball head support seat; 4-1. Supporting ball head; 4-2. Supporting cylinder; 4-3. Support base. Detailed Implementation

[0076] In the description of this invention, it should be understood that the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0077] This embodiment provides a horizontal measurement method for a large gear involute template. The large gear involute template 1 is a Chinese invention patent for a shaft-mounted large gear involute template, patent number 202111128774.9.

[0078] Example 1:

[0079] The measurement method includes the following steps:

[0080] S1: Place the large gear involute template 1 horizontally on the V-shaped seat 2 and the ball head support 4. The V-shaped seat 2 supports the reference outer cylindrical surface 1-2 of the large gear involute template 1, and the ball head support 4 supports the root of the tooth surface 1-1 to be measured. The line connecting the center of gravity of the large gear involute template 1 and the support point of the ball head support 4 is perpendicular to the central axis of the reference outer cylindrical surface. On the large gear involute template 1, between the central axis of the reference outer cylindrical surface 1-2 and the root of the tooth surface 1-1 to be measured, apply a vertically downward force at a distance L from the central axis of the reference outer cylindrical surface of the large gear involute template. N The pseudo-loaded force F N ;

[0081] S2: Taking the minimization of the total deviation of the tooth profile of the tooth surface 1-1 under test caused by the gravity deformation of the involute template 1 of the large gear as the optimization objective, calculate the proposed loading force F. NThe optimal solution is the loading force F and the proposed loading distance L. N The optimal solution is the loading distance L; step S2 specifically includes the following steps:

[0082] S2.1: As Figures 2 to 4 As shown, the large gear involute template 1 is used as the cantilever beam;

[0083] V-shaped seat 2 is used as a hinge support, and the support reaction force of the hinge support is F2;

[0084] The ball head support is used as a sliding support. The support reaction force of the sliding support is F4, and the lever arm length of the support point of the sliding support from the center axis of the reference outer cylindrical surface is l4.

[0085] Calculate the weight F1 of the large gear involute template 1 at the hinge support extension section, the weight F3 of the section from the hinge support to the sliding support, and the weight F5 of the sliding support extension section, as well as the lever arm lengths l1, l3, and l5 of the center of gravity of the hinge support extension section, the section from the hinge support to the sliding support, and the sliding support extension section to the central axis of the reference outer cylindrical surface of the large gear involute template 1; forces F1 to F5 satisfy:

[0086]

[0087] When L N When >l3, the involute template 1 of the large gear is in the range of F1~F2, F2~F3, and F3~F N F N The bending moments M1(x) to M5(x) of segments F4 and F4 to F5 satisfy:

[0088]

[0089] Where x is the lever arm length from the characteristic section of the cantilever beam to F1;

[0090] Large gear involute template 1 in F1~F2, F2~F3, F3~F N F N The turning angles θ1(x) to θ5(x) of segments ~F4 and F4~F5 satisfy:

[0091]

[0092] Among them, C1, D1, E1, F1, and G1 are undetermined constants;

[0093] Large gear involute template 1 in F1~F2, F2~F3, F3~F N F N The deflections w1(x) to w5(x) of segments ~F4 and F4~F5 satisfy:

[0094]

[0095] Among them, C2, D2, E2, F2, and G2 are constants to be determined;

[0096] The boundary conditions for rotation and deflection are satisfied as follows:

[0097]

[0098] When L≤l3

[0099] Large gear involute template 1 in F1~F2, F2~F N F N The bending moments M1(x) to M5(x) of segments ~F3, F3~F4, and F4~F5 satisfy:

[0100]

[0101] Where x is the lever arm length from the characteristic section of the cantilever beam to F1;

[0102] Large gear involute template 1F1~F2, F2~F N F N The turning angles θ1(x) to θ5(x) of segments ~F3, F3~F4, and F4~F5 satisfy:

[0103]

[0104] Among them, C1, D1, E1, F1, and G1 are undetermined constants;

[0105] Large gear involute template 1 in F1~F2, F2~F N F N The deflections w1(x) to w5(x) of segments ~F3, F3~F4, and F4~F5 satisfy:

[0106]

[0107] Among them, C2, D2, E2, F2, and G2 are constants to be determined;

[0108] The boundary conditions for rotation and deflection are satisfied as follows:

[0109]

[0110] By combining equations (1) with equations (2) to (5) or equations (1) with equations (6) to (9), the deflection equation W5 of the tooth surface 1-1 to be measured in the range of 0 to l4 can be obtained, which includes C1, D1, E1, F1, G1, C2, D2, E2, F2, G2, and L.

[0111] S2.2: Taking the minimum total deviation of the tooth profile of the tooth surface 1-1 to be measured caused by the gravity deformation of the large gear involute template 1 as the optimization objective, the loading force F and loading distance L are calculated according to formula (10);

[0112]

[0113] Where, r root r is the radius of the tooth root circle. tip Let θ be the radius of the tooth tip circle. root Let θ be the development angle of the tooth surface 1-1 to be measured at the tooth root. tip Let be the unfolding angle of the tooth surface 1-1 to be measured at the tooth tip;

[0114] S3: Based on the actual structure of the large gear involute template 1, the supporting force at the ball joint support, and the loading force F and loading distance L, use finite element simulation to calculate the total deviation F of the tooth profile after deformation of the large gear involute template 1. ɑ The method using finite element simulation is as follows:

[0115] A global gravitational acceleration is added to the involute template 1 model of the large gear; a support force is added at the ball joint support 4; and a loading force F is added at the loading distance L. Based on the simulation results, the total tooth profile deviation F after deformation of the involute template 1 of the large gear is calculated. ɑ

[0116]

[0117] Where, θ i Let x be the development angle of the involute to be measured, (x) i y i ) represents the coordinates of the nodes of the involute element during finite element analysis, w i For finite element analysis, the involute at node (x) i y i Deformation at point f i Let the expansion angle be θ i Tooth profile deviation at that time.

[0118] S4: When the total deviation of the tooth profile F ɑ If the diameter is <0.05μm, a loading force F and a loading distance L are used to apply the load, and then the tooth surface to be measured is measured.

[0119] When the total deviation of the tooth profile F ɑ If the deviation is ≥0.05μm, the loading force F and loading distance L are adjusted; and based on the adjusted loading force F and loading distance L, the support force at the ball head support is recalculated. Then, step S3 is repeated to calculate the total tooth profile deviation F after the deformation of the large gear involute template 1 using finite element simulation. ɑ until the total deviation F of the tooth profile ɑIf the diameter is less than 0.05 μm, a loading force F and a loading distance L are used to apply the load, and then the tooth surface to be measured is measured.

[0120] When the total deviation F of the tooth profile of the tooth surface 1-1 under deformation is... ɑ When the thickness is ≥0.05μm, the loading force F and loading distance L are adjusted as follows:

[0121] Based on the finite element simulation results of step S3, calculate the tooth profile deviation f at the root of the involute tooth after deformation. root and the profile deviation f at the tooth tip tip :

[0122]

[0123] Among them, (x root ,y root ), (x tip ,y tip ) represents the coordinates of the involute tooth root and tooth tip during finite element analysis, w root w tip This refers to the deformation of the involute at the tooth root and tooth tip during finite element analysis.

[0124] When the tooth profile deviation at the root of the involute tooth after deformation is f root The tooth profile deviation f at the tooth tip is less than tip If so, increase the loading force F or make the loading force F closer to F3;

[0125] When the tooth profile deviation at the root of the involute tooth after deformation is f root Tooth profile deviation f greater than the tooth tip tip If so, reduce the loading force F or move the loading force F away from F3.

[0126] When measuring the tooth surface to be measured, place the large gear involute template 1 on the V-shaped seat 2 and the ball head support seat. After the large gear involute template 1 is installed, it should be left to stand for more than 12 hours to release the installation stress and balance the temperature inside the large gear involute template 1 and the measuring chamber. Then, measure the tooth surface 1-1 to be measured.

[0127] Example 2:

[0128] In the above embodiment, in order to apply a loading force F to the large gear involute template 1 at a position L away from the center axis of the reference outer cylindrical surface under ideal conditions, the deformation of the large gear involute template 1 caused by the loading force F is used to offset the tooth profile deviation caused by the gravity deformation of the large gear involute template 1 itself.

[0129] In actual operation, multiple weight-reducing grooves 1-6 are arranged along the length of the template support arm 1-7 on the large gear involute template 1. Each weight-reducing groove 1-6 contains a web 1-4, and the web 1-4 has weight-reducing holes 1-3. For ease of operation, a loading block 3 is placed on the large gear involute template 1. The weight of the loading block 3 is equal to the loading force F, and the center of gravity of the loading block 3 is a loading distance L from the center axis of the outer cylindrical surface of the large gear involute template reference.

[0130] This invention also discloses a horizontal measuring device for a large gear involute template using the method described in Embodiment 1, such as... Figure 2 , Figure 5 , Figure 6 As shown, it includes a large gear involute template 1, a V-shaped seat 2, a loading block 3, and a ball head support 4;

[0131] The large gear involute template 1 includes a mandrel, a template support arm 1-7, and a tooth surface 1-1 to be measured. The mandrel serves as the machining and measurement reference axis for the large gear involute template and is located at one end of the template support arm 1-7. In Embodiment 1, the central axis of the reference outer cylindrical surface is the axis of the mandrel, and the reference outer cylindrical surface 1-2 is the outer circumferential surface of the mandrel. Multiple weight-reducing grooves 1-6 are arranged along the length of the template support arm 1-7. A web 1-4 is provided within each weight-reducing groove 1-6, and weight-reducing holes 1-3 are provided on the web 1-4. The end of the template support arm 1-7 furthest from the mandrel is the tooth surface 1-1 to be measured.

[0132] The V-shaped seat 2 is located below the large gear involute template 1 and supports the reference outer cylindrical surface 1-2 of the mandrel of the large gear involute template 1.

[0133] The ball head support 4 is located below the large gear involute template 1 and supports the root of the tooth surface 1-1 to be tested. The ball head support 4 is located at the template strip support arm 1-7 at the root of the tooth surface 1-1 to be tested.

[0134] The loading block 3 is disposed within the weight-reducing groove 1-6 of the large gear involute template 1. The loading block 3 includes a positioning cylinder 3-1, a positioning block 3-2, and a loading cylinder 3-3. The positioning block 3-2 is located between the positioning cylinder 3-1 and the loading cylinder 3-3. The positioning cylinder 3-1 is a cylindrical structure. The diameter of the positioning cylinder 3-1 is 1 mm smaller than the diameter of the weight-reducing hole 1-3 on the web 1-4, and its height is greater than the thickness of the web 1-4. The positioning block 3-2 is disposed above the positioning cylinder 3-1, and the loading cylinder 3-3 is disposed above the positioning cylinder 3-1. The radial dimension of the positioning block 3-2 is greater than the diameter of the weight-reducing hole 1-3 on the web 1-4 that supports the loading block 3, thus serving to support the loading cylinder 3-3.

[0135] The ball head support 4 includes a supporting ball head 4-1, a supporting cylinder 4-2, and a supporting base 4-3.

[0136] The supporting cylinder 4-2 is vertically mounted on the supporting base 4-3, and the supporting ball head 4-1 is located at the upper end of the supporting cylinder 4-2. The supporting ball head 4-1 has a hemispherical structure, and the diameter of the supporting ball head 4-1 is the same as the diameter of the supporting cylinder 4-2.

[0137] The ball head support 4 is located below the weight reduction groove 1-6 on the template support arm 1-7, which is closest to the tooth surface 1-1 to be tested. The upper end of the supporting ball head 4-1 of the ball head support 4 is used to support the web plate 1-4 in the weight reduction groove 1-6. In order to improve the support accuracy of the ball head support 4, the distance between the outer peripheral surface of the supporting cylinder 4-2 and the inner sidewall of the weight reduction groove 1-6 located on the front side of the supporting cylinder 4-2 and the inner sidewall located on the rear side of the supporting cylinder 4-2 is less than 0.5mm.

[0138] Based on the above-mentioned horizontal measuring device for the large gear involute template, its assembly method is as follows: According to the loading force F and loading distance L obtained in step S3 or S4 of Embodiment 1, the positioning cylinder 3-1 of the loading block 3 is placed in the weight reduction hole 1-3 on the web 1-4 of the template strip support arm 1-7, where the distance between the center of the web 1-4 and the center axis of the reference outer cylindrical surface is closest to the loading distance L. This makes the center of gravity of the loading block 3 located on the axis of the positioning cylinder 3-1, so that the web 1-4 bears the positioning block 3-2. At this time, the loading distance L of the loading block changes, and the distance between the center of the weight reduction hole 1-3 on the web 1-4 bearing the loading block 3 and the center axis of the reference outer cylindrical surface of the large gear involute template is the final loading distance L. Z .

[0139] Maintain loading distance L Z Without changing, the loading force F is adjusted again through steps S3 and S4 of the method described in Example 1; the weight of the loading block 3 is set to be the same as the loading force F, and then the tooth surface to be measured is measured.

[0140] Example 3:

[0141] This embodiment discloses a method for horizontally measuring a large gear involute template, using a coupling assembly template disclosed in invention patent CN202111128774.9 as an example. The steps are as follows:

[0142] S1: Two V-shaped supports 2 are used to support the two reference outer cylindrical surfaces 1-2 of the large gear involute template 1. The thickness of the V-shaped supports 2 is 10mm less than the height of the reference outer cylindrical surfaces 1-2, so that the reference outer cylindrical surfaces 1-2 have enough space to calibrate the installation position of the large gear involute template 1. The V-shaped supports 2 are made of marble. A ball head support 4 is set below the weight reduction groove 1-6 on the template support arm 1-7, which is closest to the tooth surface 1-1 to be measured. The distance between the outer circumference of the supporting cylinder 4-2 of the ball head support 4 and the inner sidewall of the weight reduction groove 1-6 located on the front side and the inner sidewall of the supporting cylinder 4-2 located on the rear side of the supporting cylinder 4-2 is less than 0.5mm to ensure the positioning accuracy of the ball head. The lever arm length l4 from the support point of the supporting ball head 4-1 on the template support arm 1-7 to the center axis of the reference outer cylindrical surface of the large gear involute template 1 is 380mm. In this example, the diameter of the ball supporting the ball head 4-1 and the outer diameter of the supporting cylinder 4-2 are both 17.5 mm; the outer diameter of the supporting base 4-3 is 60 mm to ensure the stability of the support; the material of the ball head support 4 is 40Cr; a loading block 3, made of 40Cr, is placed on the large gear involute template 1.

[0143] S2: Taking the minimum total deviation of the tooth profile of the tooth surface 1-1 to be measured caused by the gravity deformation of the large gear involute template 1 as the optimization objective, the optimal solution of the gravity of the loading block 3 is calculated as the loading force F and the optimal solution of the lever arm of the loading block 3 at the setting position of the large gear involute template 1 from the center axis of the outer cylindrical surface of the reference loading distance is the loading distance L.

[0144] S2.1: Using the large gear involute template 1 as the overhanging beam, the V-shaped seat 2 as the hinge support with a support reaction force F2, and the ball head support 4 as the sliding support, the weight of the large gear involute template 1 at the hinge support overhang is F1 = 116 N, the weight of the section from the hinge support to the sliding support is F3 = 72.3 N, and the weight of the section from the hinge support to the sliding support is F5 = 7 N. The lever arm lengths from the center of gravity of each section to the central axis of the reference outer cylindrical surface of the large gear involute template 1 are l1 = 75.45 mm, l3 = 80 mm, and l5 = 424 mm, respectively. Located between the central axis of the reference outer cylindrical surface and the root of the tooth surface 1-1 to be measured, a vertically downward force L is to be applied at a distance L from the central axis of the reference outer cylindrical surface of the large gear involute template. N The pseudo-loaded force F N Calculate the proposed loading force F N The optimal solution is the loading force F and the proposed loading distance L. N The optimal solution is the loading distance L.

[0145] Forces F1 to F5 satisfy:

[0146]

[0147] When L NWhen >l3, the involute template 1 of the large gear is in the range of F1~F2, F2~F3, and F3~F N F N The bending moments M1(x) to M5(x) of segments F4 and F4 to F5 satisfy:

[0148]

[0149] Where x is the lever arm length from the characteristic section of the cantilever beam to F1;

[0150] Large gear involute template 1 in F1~F2, F2~F3, F3~F N F N The turning angles θ1(x) to θ5(x) of segments ~F4 and F4~F5 satisfy:

[0151]

[0152] Among them, C1, D1, E1, F1, and G1 are undetermined constants;

[0153] Large gear involute template 1 in F1~F2, F2~F3, F3~F N F N The deflections w1(x) to w5(x) of segments ~F4 and F4~F5 satisfy:

[0154]

[0155] Among them, C2, D2, E2, F2, and G2 are constants to be determined;

[0156] The boundary conditions for rotation and deflection are satisfied as follows:

[0157]

[0158] When L≤l3

[0159] Large gear involute template 1 in F1~F2, F2~F N F N The bending moments M1(x) to M5(x) of segments ~F3, F3~F4, and F4~F5 satisfy:

[0160]

[0161] Where x is the lever arm length from the characteristic section of the cantilever beam to F1;

[0162] Large gear involute template 1F1~F2, F2~F N F N The turning angles θ1(x) to θ5(x) of segments ~F3, F3~F4, and F4~F5 satisfy:

[0163]

[0164] Among them, C1, D1, E1, F1, and G1 are undetermined constants;

[0165] Large gear involute template 1 in F1~F2, F2~F N F N The deflections w1(x) to w5(x) of segments ~F3, F3~F4, and F4~F5 satisfy:

[0166]

[0167] Among them, C2, D2, E2, F2, and G2 are constants to be determined;

[0168] The boundary conditions for rotation and deflection are satisfied as follows:

[0169]

[0170] Then, by combining equations (1) with equations (2) to (5) or equations (1) with equations (6) to (9), the deflection equation W5 of the tooth surface to be measured (1-1) in the range of 0 to l4 can be obtained;

[0171] S2.2: The optimization equations for the loading force F and the loading distance L are:

[0172]

[0173] Where, r root r is the radius of the tooth root circle. tip Let θ be the radius of the tooth tip circle. root Let θ be the development angle of the tooth surface 1-1 to be measured at the tooth root. tip Let be the unfolding angle of the tooth surface 1-1 to be measured at the tooth tip;

[0174] S3: Through calculation, the minimum value of f(F, L) is obtained near the loading force F = 27N and the loading distance L = 241mm. Based on the specific structure of the large gear involute template 1, in this example, the loading block 3 is placed on the web plate 1-4 inside the weight reduction groove 1-6 in the middle of the large gear involute template 1. The outer diameter of the positioning cylinder 3-1 is 1mm smaller than the inner diameter of the weight reduction hole 1-3 at that location, and the height of the positioning cylinder 3-1 should be greater than the thickness of the web plate 1-4. In this example, the outer diameter of the positioning cylinder 3-1 is 39mm and the height is 20mm. The lower end face of the positioning block 3-2 contacts the web plate 1-4 to perform loading. The length, width, and height of the positioning block 3-2 are adjusted to avoid interference between the loading block 3 and the large gear involute template 1. In this example, the length × width × height of the positioning block 3-2 is 40 × 40 × 25mm.

[0175] S5: Based on the actual structure of the large gear involute template, the support force at the ball head support, and the loading force F and loading distance L, finite element simulation is used. The support force and loading force are adjusted according to the simulation results to ensure that the total deviation F of the tooth profile 1-1 on the deformed tooth surface is achieved. α <0.05μm, total profile deviation F α satisfy:

[0176]

[0177] Where, θ i Let x be the development angle of the involute to be measured, (x) i y i ) represents the coordinates of the nodes of the involute element during finite element analysis, w i For finite element analysis, the involute at node (x) i y i Deformation at point f i Let the expansion angle be θ i Tooth profile deviation at that time.

[0178] The weight of loading block 3 can be adjusted by adjusting the outer diameter and height of loading cylinder 3-3. When the weight of loading block 3 is 32N, the total tooth profile deviation F α At its minimum, Fα = 0.03 μm, and the outer diameter and height of the loaded cylinder 3-3 are 100 mm and 45 mm, respectively;

[0179] S6: When measuring the involute template 1 of the large gear horizontally, first place two V-shaped seats 2 and ball head support seats 4 on the platform in approximate positions, and then place the involute template 1 of the large gear on the V-shaped seats 2 and ball head support seats 4. Then adjust the positions of the V-shaped seats 2 and ball head support seats 4.

[0180] Move the V-block 2 closer to the large gear involute template 1. Except for the reference cylindrical surface 1-2, the V-block 2 should not contact any other position of the large gear involute template 1. Adjust the position of the V-block 2 visually so that the distance from the mid-section of the tooth surface 1-1 to be measured to the V-block 2 is basically the same.

[0181] The ball head support 4 is gently pushed forward against the inner wall of the weight reduction groove 1-6, and the left and right positions of the ball head support 4 are adjusted visually so that the central axis of the ball head support 4 is aligned with the middle section of the tooth surface 1-1 to be tested.

[0182] Then, the loading block 3 is placed on the large gear involute template 1, that is, the positioning cylinder 3-1 is placed in the weight reduction hole 1-3, and the lower end face of the positioning block 3-2 contacts the web plate 1-4; then, it is left to stand for more than 12 hours at a temperature of 20℃ in the measuring chamber to release the installation stress and balance the temperature inside the large gear involute template 1 and the measuring chamber, and then the tooth surface 1-1 to be measured is measured.

[0183] The above description is merely a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any equivalent substitutions or modifications made by those skilled in the art within the scope of the technology disclosed in the present invention, based on the technical solution and inventive concept of the present invention, should be covered within the scope of protection of the present invention.

Claims

1. A horizontal measurement method for a large gear involute template, characterized in that, The horizontal measurement method of the large gear involute template is implemented based on the horizontal measurement device of the large gear involute template, which includes a large gear involute template (1), a V-shaped seat (2), a loading block (3), and a ball head support seat (4). The large gear involute template (1) includes a template strip support arm (1-7) and a tooth surface to be measured (1-1). The template strip support arm (1-7) has multiple weight-reducing grooves (1-6) arranged along its length. A web plate (1-4) is provided in the weight-reducing groove (1-6), and a weight-reducing hole (1-3) is provided on the web plate (1-4). The end of the template strip support arm (1-7) is the tooth surface to be measured (1-1). The V-shaped seat (2) is located below the large gear involute template (1) and is supported on the reference outer cylindrical surface (1-2) of the large gear involute template (1). The ball head support (4) is located below the large gear involute template (1) and is supported by the template strip support arm (1-7) at the root of the tooth surface to be tested (1-1). The loading block (3) is disposed in the weight reduction groove (1-6) of the large gear involute template (1). The loading block (3) includes a positioning cylinder (3-1), a positioning block (3-2), and a loading cylinder (3-3). The positioning block (3-2) is located between the positioning cylinder (3-1) and the loading cylinder (3-3). The positioning cylinder (3-1) is a cylindrical structure. The diameter of the positioning cylinder (3-1) is 1 mm smaller than the diameter of the weight reduction hole (1-3) and its height is greater than the thickness of the web plate (1-4). The radial dimension of the positioning block (3-2) is greater than the diameter of the weight reduction hole (1-3) on the web plate (1-4) that supports the loading block (3), thus supporting the loading cylinder (3-3). By placing a loading block (3) on the large gear involute template (1), a loading force is applied to the large gear involute template (1). The weight of the loading block (3) is equal to the loading force F. The center of gravity of the loading block (3) is a loading distance L from the center axis of the outer cylindrical surface of the large gear involute template reference. The ball head support (4) includes a supporting ball head (4-1), a supporting cylinder (4-2), and a supporting base (4-3). The supporting cylinder (4-2) is vertically mounted on the supporting base (4-3). The supporting ball head (4-1) is a hemispherical structure. The supporting ball head (4-1) is located at the upper end of the supporting cylinder (4-2), and the diameter of the supporting ball head (4-1) is the same as the diameter of the supporting cylinder (4-2). The ball head support (4) is located below the weight reduction groove (1-6) on the template support arm (1-7) that is closest to the tooth surface (1-1) to be tested. The upper end of the support ball head (4-1) of the ball head support (4) is used to support the web plate (1-4) in the weight reduction groove (1-6). The distance between the outer circumferential surface of the support cylinder (4-2) and the inner sidewall of the weight reduction groove (1-6) located in front of the support cylinder (4-2) and the inner sidewall located in the rear of the support cylinder (4-2) is less than 0.5 mm. The horizontal measurement method for the involute template of a large gear includes the following steps: S1: Place the large gear involute template (1) horizontally on the V-shaped seat (2) and the ball head support (4), wherein the V-shaped seat (2) is supported on the reference outer cylindrical surface (1-2) of the large gear involute template (1), and the ball head support (4) is supported on the root of the tooth surface (1-1) to be measured. The line connecting the center of gravity of the large gear involute template (1) and the support point of the ball head support (4) is perpendicular to the central axis of the reference outer cylindrical surface (1-2). On the large gear involute template (1), between the central axis of the reference outer cylindrical surface and the root of the tooth surface (1-1) to be measured, a vertically downward load is to be applied at a distance L from the central axis of the reference outer cylindrical surface of the large gear involute template. N The pseudo-loaded force F N ; S2: Taking the minimization of the total deviation of the tooth profile of the tooth surface (1-1) to be measured caused by the gravity deformation of the involute template (1) of the large gear as the optimization objective, the proposed loading force F is calculated. N The optimal solution is the loading force F and the proposed loading distance L. N The optimal solution is the loading distance L; S3: Based on the actual structure of the large gear involute template (1), the supporting force at the ball head support, and the loading force F and loading distance L, the total deviation F of the tooth profile after deformation of the large gear involute template (1) is calculated using finite element simulation. ɑ ; S4: When the total deviation of the tooth profile F ɑ If the diameter is <0.05μm, a loading force F and a loading distance L are used to apply the load, and then the tooth surface to be measured is measured. When the total deviation of the tooth profile F ɑ If the diameter is ≥0.05μm, the loading force F and loading distance L are adjusted; and based on the adjusted loading force F and loading distance L, the support force at the ball head support is recalculated, and step S3 is repeated to calculate the total deviation F of the tooth profile of the large gear involute template (1) after deformation using finite element simulation. ɑ until the total deviation F of the tooth profile ɑ If the diameter is less than 0.05 μm, a loading force F and a loading distance L are used to apply the load, and then the tooth surface to be measured is measured.

2. The horizontal measurement method for a large gear involute template according to claim 1, characterized in that, Step S2 includes the following steps: S2.1: Use the large gear involute template (1) as the overhang beam; The V-shaped seat (2) is used as a hinge support, and the support reaction force of the hinge support is F2; The ball head support is used as a sliding support. The support reaction force of the sliding support is F4, and the lever arm length of the support point of the sliding support from the center axis of the reference outer cylindrical surface is l4. Calculate the gravity F1 of the large gear involute template (1) at the hinge support extension section, the gravity F3 of the hinge support to sliding support section, the gravity F5 of the sliding support extension section, and the lever arm lengths l1, l3, l5 of the center of gravity of the hinge support extension section, the hinge support to sliding support section, and the sliding support extension section to the central axis of the reference outer cylindrical surface of the large gear involute template (1); forces F1~F5 satisfy: When L N When >l3, the involute template (1) of the large gear is in F1~F2, F2~F3, F3~F N F N The bending moments M1(x)~M5(x) of segments ~F4 and F4~F5 satisfy: Where x is the lever arm length from the characteristic section of the cantilever beam to F1; Large gear involute template (1) in F1~F2, F2~F3, F3~F N F N The turning angles θ1(x) and θ5(x) of segments ~F4 and F4~F5 satisfy: Among them, C1, D1, E1, F1, and G1 are undetermined constants; Large gear involute template (1) in F1~F2, F2~F3, F3~F N F N The deflections w1(x)~w5(x) of segments ~F4 and F4~F5 satisfy: Among them, C2, D2, E2, F2, and G2 are constants to be determined; The boundary conditions for rotation and deflection are satisfied as follows: When L≤l3 Large gear involute template (1) in F1~F2, F2~F N F N The bending moments M1(x)~M5(x) of segments ~F3, F3~F4, and F4~F5 satisfy: Where x is the lever arm length from the characteristic section of the cantilever beam to F1; Large gear involute template (1) F1~F2, F2~F N F N The turning angles θ1(x) to θ5(x) of segments ~F3, F3~F4, and F4~F5 satisfy: Among them, C1, D1, E1, F1, and G1 are undetermined constants; Large gear involute template (1) in F1~F2, F2~F N F N The deflections w1(x)~w5(x) of segments ~F3, F3~F4, and F4~F5 satisfy: Among them, C2, D2, E2, F2, and G2 are constants to be determined; The boundary conditions for rotation and deflection are satisfied as follows: Then, by combining equations (1) with equations (2) to (5) or equations (1) with equations (6) to (9), the deflection equation W5 of the tooth surface (1-1) to be measured in the range of 0 to l4 can be obtained; S2.2: Taking the minimum total deviation of the tooth profile of the tooth surface (1-1) to be measured caused by the gravity deformation of the large gear involute template (1) as the optimization objective, the loading force F and loading distance L are calculated according to formula (10); Where, r root r is the radius of the tooth root circle. tip Let θ be the radius of the tooth tip circle. root Let θ be the development angle of the tooth surface (1-1) at the root. tip The spread angle of the tooth surface (1-1) to be tested is at the tooth tip.

3. The horizontal measurement method for a large gear involute template according to claim 1, characterized in that, In step S3, the method of using finite element simulation is as follows: Add global gravitational acceleration to the involute template (1) model of the large gear, add support force at the ball head support (4), and add loading force F at the loading distance L; calculate the total tooth profile deviation F after deformation of the involute template (1) of the large gear based on the simulation results. ɑ Where, θ i Let x be the development angle of the involute to be measured, (x) i y i ) represents the coordinates of the nodes of the involute element during finite element analysis, w i For finite element analysis, the involute at node (x) i y i Deformation at point f i Let the expansion angle be θ i Tooth profile deviation at that time.

4. The horizontal measurement method for a large gear involute template according to claim 2, characterized in that, In step S4, when the total deviation F of the tooth profile of the tooth surface (1-1) to be measured after deformation... ɑ When the thickness is ≥0.05μm, the loading force F and loading distance L are adjusted as follows: Based on the finite element simulation results of step S3, calculate the tooth profile deviation f at the root of the involute tooth after deformation. root and the profile deviation f at the tooth tip tip : Among them, (x root , y root ), (x tip , y tip ) represents the coordinates of the involute tooth root and tooth tip during finite element analysis, w root w tip This refers to the deformation of the involute at the tooth root and tooth tip during finite element analysis. When the tooth profile deviation at the root of the involute tooth after deformation is f root The tooth profile deviation f at the tooth tip is less than tip If so, increase the loading force F or make the loading force F closer to F3; When the tooth profile deviation at the root of the involute tooth after deformation is f root Tooth profile deviation f greater than the tooth tip tip If so, reduce the loading force F or move the loading force F away from F3.

5. The horizontal measurement method for a large gear involute template according to claim 1, characterized in that, In step S4, when measuring the tooth surface to be measured, the large gear involute template (1) is placed on the V-shaped seat (2) and the ball head support seat (4). After the large gear involute template (1) is installed, it should be left to stand for more than 12 hours to release the installation stress and balance the temperature inside the large gear involute template (1) and the measuring chamber. Then the tooth surface (1-1) to be measured is measured.

6. The horizontal measurement method for a large gear involute template according to claim 1, characterized in that, The assembly method of the horizontal measuring device for the involute template of a large gear is as follows: Based on the loading force F and the loading distance L, the positioning cylinder (3-1) of the loading block (3) is placed in the weight reduction hole (1-3) on the web plate (1-4) of the template support arm (1-7), where the distance between the center of the web plate (1-4) and the center axis of the reference outer cylindrical surface is closest to the loading distance L. This makes the center of gravity of the loading block (3) located on the axis of the positioning cylinder (3-1), and the web plate (1-4) bears the positioning block (3-2). The distance between the center of the weight reduction hole (1-3) on the web plate (1-4) bearing the loading block (3) and the center axis of the reference outer cylindrical surface of the large gear involute template is the final loading distance L. Z ; Maintain loading distance L Z The loading force F is adjusted again through steps S3 and S4 of the method described in claim 1; the weight of the loading block (3) is set to be the same as the loading force F, and then the tooth surface to be measured is measured.

Images