Design method for large gear ring deformation detection and small gear matching

Abstract

The invention relates to the technical field of gear deformation detection and matched gear design, in particular to a method for large gear ring deformation detection and matched pinion design. The method comprises the following steps: S1, arranging a strain measurement sensor, and detecting the deformation at the tooth root of a gear tooth of a large gear ring by using the strain measurement sensor; s2, calculating the torsion angle of the gear teeth of the large gear ring on the end face according to the deformation amount; the tooth groove width increment of the gear teeth of the large gear ring on the end face is obtained according to the torsion angle; s3, calculating the pressure angle and modulus of the large gear ring after deformation by using the torsion angle of the gear teeth of the large gear ring on the end surface and the tooth space width increment; s4, calculating the pressure angle and modulus of the paired pinion according to the pressure angle and modulus of the deformed large gear ring; the paired pinion is designed based on the pressure angle and modulus of the paired pinion. According to the invention, the deformation of the large gear ring can be detected, and then the paired pinion is designed, so that the engineering design requirements are met.

Description

Technical Field

[0001] The invention relates to the technical field of gear deformation detection and paired gear design, and in particular to a method for large gear ring deformation detection and paired pinion design. Background Art

[0002] Since large gear rings may be affected by various external factors during production and use, such as heavy load, high-speed rotation, temperature changes, etc., they may deform, thus affecting the meshing accuracy and transmission efficiency of the gears. In recent years, with the rapid development of industrial technology, the performance requirements for gears have also been continuously improved. The bending fatigue resistance, meshing accuracy, wear resistance, etc. of gears have become important criteria for measuring their quality. Among them, large gear rings are widely used in mining machinery and heavy machinery. Due to the large size and mass of large gear rings themselves, large gear rings will deform at the meshing position with the matching pinion under non-operating conditions just by the influence of gravity, thus affecting the meshing transmission conditions of the two, resulting in large transmission errors and unstable transmission motion, which is difficult to meet the actual engineering design needs.

[0003] In the prior art, there is a method for detecting the tooth profile of a super-large bearing gear ring using a projection measuring instrument. This method uses a super-hard gypsum for demoulding to make a plaster model of the gear ring, and then uses a projection measuring instrument to detect and analyze the plaster model to obtain the tooth profile parameters of the gear ring. Although this method can improve the detection accuracy to a certain extent, it still has problems such as complex operation and long detection cycle.

[0004] At the same time, there have been some new attempts and explorations in gear design. For example, by optimizing the gear modification design, the stress distribution of hardened gears can be improved, the life of the gears can be increased, and the vibration and noise of the gearbox can be reduced. However, these methods still need to rely on a lot of experimental verification and experience accumulation, and are difficult to be directly applied to the design of matching pinions for large gear rings. Summary of the invention

[0005] In order to solve the above technical problems, the purpose of the present invention is to provide a method for large gear ring deformation detection and matching pinion design, and the technical solution adopted is as follows:

[0006] An embodiment of the present invention provides a method for large gear ring deformation detection and matching pinion design:

[0007] Step S1, setting a strain measurement sensor, and using the strain measurement sensor to detect the deformation at the root of the large ring gear teeth;

[0008] Step S2, calculating the torsion angle of the large ring gear teeth on the end surface according to the deformation; obtaining the tooth gap width increment of the large ring gear teeth on the end surface according to the torsion angle;

[0009] Step S3, calculating the pressure angle and modulus of the large gear ring after deformation using the torsion angle of the large gear ring teeth on the end surface and the tooth gap width increment;

[0010] Step S4, calculating the pressure angle and module of the mating pinion according to the pressure angle and module of the large gear ring after deformation; and designing the mating pinion based on the pressure angle and module of the mating pinion.

[0011] Preferably, a strain measurement sensor is provided, and the strain measurement sensor is used to detect the deformation at the root of the gear ring teeth, including:

[0012] The strain measurement sensors include a first strain measurement sensor and a second strain measurement sensor; the first strain measurement sensor and the second strain measurement sensor are arranged at the tooth root position between the theoretical meshing gear teeth at two end surfaces of the large gear ring.

[0013] Preferably, the calculation formula for the torsion angle of the large ring gear teeth on the end face is:

[0014]

[0015] in, represents the torsion angle of the large gear ring teeth on the end face; δ1 and δ2 represent the deformation at the root of the large gear ring teeth measured by the first strain measurement sensor and the second strain measurement sensor respectively; R represents the distance between the strain measurement sensor 1 and the center of the large gear; d represents the distance between the first strain measurement sensor and the second strain measurement sensor.

[0016] Preferably, obtaining the tooth width increment of the large ring gear teeth on the end surface according to the torsion angle includes:

[0017] The tooth width increment of the large ring gear teeth on the end face is the product of the pitch circle radius of the large ring gear and the torsion angle of the large ring gear teeth on the end face.

[0018] Preferably, the pressure angle and modulus of the large gear ring after deformation include:

[0019] The pressure angle after the deformation of the large gear ring includes the end surface pressure angle after the deformation of the large gear ring and the normal pressure angle of the large gear ring after the deformation of the large gear ring;

[0020] The modulus of the large gear ring after deformation includes the normal modulus of the large gear ring after deformation and the end face modulus of the large gear ring.

[0021] Preferably, the calculation formula of the end face pressure angle of the large gear ring after deformation is:

[0022]

[0023] Among them, α t1 Indicates the end face pressure angle of the large gear ring after deformation; α t It represents the end face pressure angle of the large gear ring before deformation; R0 represents the pitch circle radius of the large gear ring; Indicates the torsion angle of the gear ring teeth on the end face; Δs n represents the increment of the tooth width of the gear ring on the end face; θ represents the angle of the tooth profile involute at the pitch circle before the gear ring is deformed; r b Indicates the base circle radius of the large ring gear.

[0024] Preferably, the calculation formula of the normal pressure angle of the large gear ring after deformation is:

[0025] α n1 =arctan(tanα t1 cosβ),

[0026] Among them, α n1 represents the normal pressure angle of the gear ring after deformation; α t1 It represents the end face pressure angle of the large gear ring after deformation; β represents the helix angle of the large gear ring.

[0027] Preferably, the calculation formula for the normal modulus of the large gear ring after deformation is:

[0028]

[0029] Among them, m n1 ′ represents the normal modulus of the large gear ring after deformation; m n1 It represents the normal module of the big gear ring before deformation; R0 represents the pitch circle radius of the big gear ring; It represents the torsion angle of the gear teeth on the end face of the gear ring; β represents the helix angle of the gear ring; π represents the circumference of a circle.

[0030] Preferably, the calculation formula for the end face modulus of the large gear ring after deformation is:

[0031]

[0032] Among them, m t1 ′ represents the end face modulus of the large gear ring after deformation; m n1 ′ represents the normal module of the large gear ring after deformation; β represents the helix angle of the large gear ring.

[0033] Preferably, the pressure angle and the module of the paired pinion are calculated according to the pressure angle and the module of the large gear ring after deformation, including:

[0034] The end face pressure angle and normal pressure angle of the mating pinion are respectively equal to the end face pressure angle of the large gear ring after deformation and the normal pressure angle of the large gear ring after deformation;

[0035] The end face modulus and normal modulus of the mating pinion are respectively equal to the end face modulus and normal modulus of the large ring gear after the large ring gear is deformed.

[0036] The embodiments of the present invention have at least the following beneficial effects: the present invention can detect the deformation at the root of the large gear ring teeth by setting a strain measurement sensor. Compared with the existing detection method, it not only ensures the accuracy of detection, but also improves the efficiency of detection; further, the torsion angle and tooth width increment of a single tooth of the corresponding large gear ring on the end face are calculated according to the deformation of the teeth of the large gear ring, and the module and pressure angle of the deformed large gear ring are calculated based on the change of relevant parameters of the large gear ring, and then the module and pressure angle of the mating pinion are inversely calculated according to the module and pressure angle of the deformed large gear ring; it can ensure that after the large gear ring is affected by its own gravity and its theoretical meshing position has been deformed under non-operating conditions, it still has a good meshing state with the mating pinion designed by using the present method, thereby meeting the engineering design requirements well. BRIEF DESCRIPTION OF THE DRAWINGS

[0037] In order to more clearly illustrate the technical solutions and advantages in the embodiments of the present invention or the prior art, the drawings required for use in the embodiments or the prior art descriptions are briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0038] Figure 1 It is a method flow chart of a method for large gear ring deformation detection and matching pinion design method provided by an embodiment of the present application;

[0039] Figure 2 It is a schematic diagram of large gear ring gear tooth deformation detection for large gear ring deformation detection and matching pinion design method provided in an embodiment of the present application;

[0040] Figure 3 It is a schematic diagram of the involute position of a large gear ring tooth before and after deformation for a large gear ring deformation detection and matching pinion design method provided by an embodiment of the present application;

[0041] Figure 4 It is a schematic diagram of the relationship between the pressure angle of a large ring gear after deformation and the pitch circle radius, base circle radius, and span angle for large ring gear deformation detection and matching pinion design method provided in an embodiment of the present application.

[0042] In order to better illustrate the present embodiment, some parts of the drawings may be omitted, enlarged or reduced, and do not represent the size of the actual product. In addition, the drawings are only used for illustrative purposes and should not be construed as limitations on the present application. DETAILED DESCRIPTION

[0043] In order to further explain the technical means and effects adopted by the present invention to achieve the predetermined invention purpose, the following is a detailed description of the specific implementation method, structure, features and effects of a large gear ring deformation detection and matching pinion design method proposed by the present invention in combination with the accompanying drawings and preferred embodiments. In the following description, different "one embodiment" or "another embodiment" does not necessarily refer to the same embodiment. In addition, specific features, structures, or characteristics in one or more embodiments may be combined in any suitable form.

[0044] Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs.

[0045] A specific solution for large gear ring deformation detection and matching pinion design method provided by the present invention is described in detail below with reference to the accompanying drawings.

[0046] Example:

[0047] The main application scenarios of the present invention are: In modern industrial manufacturing, gear transmission devices play a vital role. As basic parts for transmitting motion and power, gears are widely used in various mechanical systems. Especially large ring gears, which are usually used in heavy machinery and equipment, such as wind turbines, ships, large engineering machinery, etc., and their performance directly affects the stability and reliability of the entire system. Therefore, there is an urgent need for an efficient and practical large ring gear deformation detection device and a matching pinion design method to achieve rapid and accurate detection of large ring gear deformation, as well as precise design of matching pinions, thereby improving the accuracy and efficiency of gear transmission and meeting the high requirements of modern industry for gear performance.

[0048] See also Figure 1 , which shows a flow chart of a method for large gear ring deformation detection and matching pinion design provided by an embodiment of the present invention, the method comprising the following steps:

[0049] Step S1, setting a strain measurement sensor, and using the strain measurement sensor to detect the deformation at the root of the large ring gear teeth;

[0050] Step S2, calculating the torsion angle of the large ring gear teeth on the end surface according to the deformation; obtaining the tooth gap width increment of the large ring gear teeth on the end surface according to the torsion angle;

[0051] Step S3, calculating the pressure angle and modulus of the large gear ring after deformation using the torsion angle of the large gear ring teeth on the end surface and the tooth gap width increment;

[0052] Step S4, calculating the pressure angle and module of the mating pinion according to the pressure angle and module of the large gear ring after deformation; and designing the mating pinion based on the pressure angle and module of the mating pinion.

[0053] Specifically, in step S1, a strain measurement sensor is provided, and the strain measurement sensor is used to detect the deformation at the root of the gear teeth of the large ring gear.

[0054] For large gear rings whose gear end faces are perpendicular to the ground when not in operation, most of these large gear rings are thin-walled gear rings. Therefore, when these gear rings mesh with their matching pinions, the influence of their own gravity will cause gear tooth deformation at the meshing position.

[0055] Therefore, it is necessary to detect the deformation of the teeth of the large gear on the two end faces of the theoretical meshing position between the large gear ring and the matching pinion, and arrange two devices for measuring strain at the root positions between the theoretical meshing teeth on the two end faces of the large gear ring, respectively, to measure the deformation of the gear ring of the large gear, wherein the device for measuring strain is a strain measurement sensor.

[0056] like Figure 2 As shown, in the present invention, the first strain measurement sensor and the second strain measurement sensor are respectively arranged at the tooth root positions between the theoretical meshing gear teeth at the two end surfaces of the large gear ring, and the first strain measurement sensor and the second strain measurement sensor correspond to Figure 2 The strain measurement sensor 1 and the strain measurement sensor 2 in the embodiment of the present invention are as follows: the deformation at the root of the gear ring gear measured by the first strain measurement sensor and the second strain measurement sensor is δ i In the embodiment of the present invention, the value of i is 1 and 2, δ1 and δ2 respectively represent the deformation at the root of the large ring gear teeth measured by the first strain measurement sensor and the second strain measurement sensor respectively.

[0057] At this point, the strain measurement sensor can be used to detect the deformation at the root of the large ring gear teeth. Compared with the method of using a projection measuring instrument to detect the tooth shape of an extra-large bearing ring gear and the method of using manual detection, the detection method in the present invention not only ensures the accuracy of the detection but also takes into account the efficiency of the detection.

[0058] Step S2, calculating the torsion angle of the large ring gear teeth on the end surface according to the deformation; and obtaining the tooth gap width increment of the large ring gear teeth on the end surface according to the torsion angle.

[0059] Further, such as Figure 2As shown, the distance between the first strain measurement sensor and the second strain measurement sensor is obtained, which is recorded as d, and the distance between the strain measurement sensor 1 and the center of the large gear is obtained, which is recorded as R. Then, the deformation δ1 and δ2 at the root of the large gear ring tooth measured by the first strain measurement sensor and the second strain measurement sensor can be combined to calculate the torsion angle of the gear tooth on the end face, which is Figure 3 The deflection angle between involute 1 and involute 2 shown in the figure is the torsion angle of the gear teeth on the end face. Specifically, the calculation formula for the torsion angle of the gear ring gear teeth on the end face is:

[0060]

[0061] in, represents the torsion angle of the large gear ring teeth on the end face; δ1 and δ2 represent the deformation at the root of the large gear ring teeth measured by the first strain measurement sensor and the second strain measurement sensor respectively; R represents the distance between the strain measurement sensor 1 and the center of the large gear; d represents the distance between the first strain measurement sensor and the second strain measurement sensor.

[0062] like Figure 2 As shown in the figure, the end face pitch of the large gear ring before the gear teeth are deformed is p t , the end face tooth thickness is s t , the end face tooth width is e. The end face tooth pitch is p t Equal to the end face tooth thickness s t The sum of the end face tooth width e.

[0063] Due to the deformation of the gear teeth of the large ring gear, the gear teeth will have a torsion angle Although the gear torsion angle does not affect the end face tooth thickness s of the large gear ring t , but it will affect the tooth width e on the end face, that is, as the torsion angle of the gear increases, the tooth width on the end face of the large gear ring will also increase accordingly. The increment of the tooth width on the end face of the gear after deformation is as follows: Figure 3 shown

[0064] Specifically, the tooth width increment is the product of the pitch circle radius of the large gear ring and the torsion angle of the large gear ring teeth on the end face. The calculation formula for the tooth width increment of the large gear ring teeth on the end face is:

[0065]

[0066] Where, Δs n It indicates the increment of the tooth width of the gear ring teeth on the end face; R0 indicates the pitch circle radius of the gear ring; Indicates the torsion angle of the large ring gear teeth on the end face.

[0067] Thus, the torsion angle of the large ring gear teeth on the end face and the tooth width increment of the large ring gear teeth on the end face can be obtained, and then the following analysis can be carried out.

[0068] Step S3, calculating the pressure angle and modulus of the large gear ring after deformation using the torsion angle of the large gear ring teeth on the end surface and the tooth width increment.

[0069] The torsion angle of the gear ring teeth on the end face and the tooth width increment have been calculated. Figure 4 As shown in the figure, after the large ring gear teeth are deformed, Q1 shifts to the position of Q2, and θ is Figure 3 The angle of involute 1 at Q1 is θ1. Figure 3 The angle of the involute 2 at Q2 is shown, and the base circle radius of the large gear ring before and after deformation is r b and r b1 , the end face pressure angle of the large gear ring before deformation is α t , the end face pressure angle of the deformed large gear ring is α t1 The change in the end face pressure angle is the difference between the end face pressure angles before and after the deformation of the gear ring gear, that is, Δα = α t1 -α t .

[0070] By Figure 4 The basic parameters and geometric relationship of the large gear ring before and after deformation are shown in the figure, and then the calculation formula of Δα is deduced as Δα=∠Q1AQ2-∠Q1OQ2. Figure 4 As shown, there is a certain relationship between ∠Q1AQ2 and ∠Q1OQ2, so the relationship between ∠Q1AQ2 and ∠Q1OQ2 is: in,

[0071]

[0072] By combining the above formulas, the calculation formula for the change in the pressure angle of the rear end of the large gear ring deformation is:

[0073]

[0074] Among them, Δα represents the change value of the pressure angle of the rear end of the large gear ring after deformation; R0 represents the pitch circle radius of the large gear ring; Indicates the torsion angle of the gear ring teeth on the end face; Δs n represents the tooth width increment of the gear ring gear on the end face; θ represents the angle of the involute; r b Indicates the base circle radius of the large gear ring. The pressure angle after the large gear ring is deformed includes the end face pressure angle after the large gear ring is deformed and the normal pressure angle of the large gear ring after the large gear ring is deformed.

[0075] Furthermore, the change value Δα of the end face pressure angle of the large gear ring after deformation is compared with the end face pressure angle α before deformation of the large gear ring. t By adding them together, we can get the end face pressure angle α of the large gear ring after deformation. t1 , the specific calculation formula is:

[0076]

[0077] Among them, α t1 Indicates the end face pressure angle of the large gear ring after deformation; α t It represents the end face pressure angle of the large gear ring before deformation; R0 represents the pitch circle radius of the large gear ring; Indicates the torsion angle of the gear ring teeth on the end face; Δs n represents the increment of the tooth width of the gear ring on the end face; θ represents the angle of the tooth profile involute at the pitch circle before the gear ring is deformed; r b Indicates the base circle radius of the large gear ring. The calculation formula of θ is θ = tanα t -α t .

[0078] Next, in order to make the subsequent small gear match the large gear, it is also necessary to calculate the normal pressure angle of the large gear ring after deformation. The specific calculation formula is:

[0079] α n1 =arctan(tanα t1 cosβ),

[0080] Among them, α n1 represents the normal pressure angle of the gear ring after deformation; α t1 It represents the end face pressure angle of the large gear ring after deformation; β represents the helix angle of the large gear ring.

[0081] The modulus of the large gear ring after deformation includes the normal modulus and end modulus of the large gear ring after deformation. After the large gear ring is deformed, the tooth width of the rear end increases, and the corresponding end pitch also increases, that is, the end pitch p of the gear. t Related to the gear module, the end face pitch p t If the gear modulus changes, the gear modulus will also change, so the end face pitch can be used to calculate the normal modulus of the deformed ring gear. The calculation formula for the normal modulus of the ring gear after deformation is:

[0082]

[0083] Among them, m n1 ′ represents the normal modulus of the large gear ring after deformation; m n1 It represents the normal module of the big gear ring before deformation; R0 represents the pitch circle radius of the big gear ring; It represents the torsion angle of the gear teeth on the end face of the gear ring; β represents the helix angle of the gear ring; π represents the circumference of a circle. Therefore, m n1 The calculation formula of ′ can also be expressed as

[0084] The calculation formula for the end face modulus of the large gear ring after deformation is:

[0085]

[0086] Among them, m t1 ′ represents the end face modulus of the large gear ring after deformation; m n1 ′ represents the normal module of the large gear ring after deformation; β represents the helix angle of the large gear ring.

[0087] Thus, the end face pressure angle α of the large gear ring after deformation is obtained. t1 、The normal pressure angle α of the large gear ring after deformation n1 、The normal modulus of the large gear ring after deformation m n1 ′ and the end face modulus m of the large gear ring after deformation t1 ′.

[0088] Step S4, calculating the pressure angle and module of the mating pinion according to the pressure angle and module of the large gear ring after deformation; and designing the mating pinion based on the pressure angle and module of the mating pinion.

[0089] Among them, the pressure angle after the deformation of the large gear ring includes the end surface pressure angle after the deformation of the large gear ring and the normal pressure angle of the large gear ring after the deformation of the large gear ring, which are α t1 and α n1 The modulus of the large gear ring after deformation includes the normal modulus of the large gear ring after deformation and the end modulus of the large gear ring, which are m n1 ′ and m t1 ′.

[0090] In order to form better meshing conditions between the large ring gear and the mating pinion, the pressure angle and module of the mating pinion should be equal.

[0091] Therefore, the end face pressure angle and normal pressure angle of the matching pinion are equal to the end face pressure angle of the large gear ring after deformation and the normal pressure angle of the large gear ring after deformation, respectively. The calculation formulas for the end face pressure angle and normal pressure angle of the matching pinion are:

[0092] α t2 =α t1 ;

[0093] α n2 =αn1 ;

[0094] Among them, α t1 is the end face pressure angle of the large gear ring after deformation; α t2 Represents the end face pressure angle of the pinion; α n1 is the normal pressure angle of the gear ring after deformation; α n2 represents the normal pressure angle of the pinion.

[0095] The end modulus and normal modulus of the mating pinion are respectively equal to the end modulus and normal modulus of the large ring gear after the large ring gear is deformed. The calculation formulas for the end modulus and normal modulus of the mating pinion are:

[0096] m n2 =m n1 ′;

[0097] m t2 =m t1 ′;

[0098] Among them, m n1 ′ is the normal modulus of the large gear ring after deformation, m n2 Indicates the normal module of the mating pinion; m t1 ′ is the end face modulus of the large gear ring after deformation; m t2 Indicates the end module of the mating pinion.

[0099] Thus, the end face pressure angle and normal pressure angle of the mating pinion, the end face module and normal module of the mating pinion can be obtained, and the mating pinion can be designed based on this.

[0100] It should be noted that the sequence of the above embodiments of the present invention is only for description and does not represent the advantages and disadvantages of the embodiments. The above is a description of a specific embodiment of this specification. In addition, the processes depicted in the accompanying drawings do not necessarily require the specific order or continuous order shown to achieve the desired results. In some embodiments, multitasking and parallel processing are also possible or may be advantageous.

[0101] The various embodiments in this specification are described in a progressive manner, and the same or similar parts between the various embodiments can be referenced to each other, and each embodiment focuses on the differences from other embodiments.

[0102] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. A method for large gear ring deformation detection and matching pinion design, characterized in that: The method includes: Step S1, setting a strain measurement sensor, and using the strain measurement sensor to detect the deformation at the root of the large ring gear teeth; Step S2, calculating the torsion angle of the large ring gear teeth on the end surface according to the deformation; obtaining the tooth gap width increment of the large ring gear teeth on the end surface according to the torsion angle; Step S3, calculating the pressure angle and modulus of the large gear ring after deformation using the torsion angle of the large gear ring teeth on the end surface and the tooth gap width increment; Step S4, calculating the pressure angle and module of the mating pinion according to the pressure angle and module of the large gear ring after deformation; and designing the mating pinion based on the pressure angle and module of the mating pinion.

2. A method for large gear ring deformation detection and matching pinion design according to claim 1, characterized in that: The method of setting a strain measurement sensor and using the strain measurement sensor to detect the deformation at the root of the gear teeth of the large ring gear comprises: The strain measurement sensors include a first strain measurement sensor and a second strain measurement sensor; the first strain measurement sensor and the second strain measurement sensor are arranged at the tooth root position between the theoretical meshing gear teeth at two end surfaces of the large gear ring.

3. A method for large gear ring deformation detection and matching pinion design according to claim 1, characterized in that: The calculation formula of the torsion angle of the large gear ring teeth on the end surface is: in, represents the torsion angle of the large gear ring teeth on the end face; δ1 and δ2 represent the deformation at the root of the large gear ring teeth measured by the first strain measurement sensor and the second strain measurement sensor respectively; R represents the distance between the strain measurement sensor 1 and the center of the large gear; d represents the distance between the first strain measurement sensor and the second strain measurement sensor.

4. A method for large gear ring deformation detection and matching pinion design according to claim 1, characterized in that: The step of obtaining the tooth width increment of the large ring gear teeth on the end surface according to the torsion angle comprises: The tooth width increment of the large ring gear teeth on the end face is the product of the pitch circle radius of the large ring gear and the torsion angle of the large ring gear teeth on the end face.

5. A method for large gear ring deformation detection and matching pinion design according to claim 1, characterized in that: The pressure angle and modulus of the large gear ring after deformation include: The pressure angle after the deformation of the large gear ring includes the end surface pressure angle after the deformation of the large gear ring and the normal pressure angle of the large gear ring after the deformation of the large gear ring; The modulus of the large gear ring after deformation includes the normal modulus of the large gear ring after deformation and the end face modulus of the large gear ring.

6. A method for large gear ring deformation detection and matching pinion design according to claim 5, characterized in that: The calculation formula of the end face pressure angle of the large gear ring after deformation is: Among them, α t1 Indicates the end face pressure angle of the large gear ring after deformation; α t It represents the end face pressure angle of the large gear ring before deformation; R0 represents the pitch circle radius of the large gear ring; Indicates the torsion angle of the gear ring teeth on the end face; Δs n represents the increment of the tooth width of the gear ring on the end face; θ represents the angle of the tooth profile involute at the pitch circle before the gear ring is deformed; r b Indicates the base circle radius of the large ring gear.

7. A method for large gear ring deformation detection and matching pinion design according to claim 1, characterized in that: The calculation formula of the normal pressure angle of the large gear ring after the large gear ring is deformed is: a n1 =arctan(tan α t1 cosβ), Among them, α n1 represents the normal pressure angle of the gear ring after deformation; α t1 It represents the end face pressure angle of the large gear ring after deformation; β represents the helix angle of the large gear ring.

8. A method for large gear ring deformation detection and matching pinion design according to claim 1, characterized in that: The calculation formula of the normal modulus of the large gear ring after the large gear ring is deformed is: Among them, m n1 ′ represents the normal modulus of the large gear ring after deformation; m n1 It represents the normal module of the big gear ring before deformation; R0 represents the pitch circle radius of the big gear ring; It represents the torsion angle of the gear teeth on the end face of the gear ring; β represents the helix angle of the gear ring; π represents the circumference of a circle.

9. A method for large gear ring deformation detection and matching pinion design according to claim 1, characterized in that: The calculation formula of the end face modulus of the large gear ring after the large gear ring is deformed is: Among them, m t1 ′ represents the end face modulus of the large gear ring after deformation; m n1 ′ represents the normal module of the large gear ring after deformation; β represents the helix angle of the large gear ring.

10. A method for large gear ring deformation detection and matching pinion design according to claim 1, characterized in that: The method of calculating the pressure angle and module of the paired pinion according to the pressure angle and module of the deformed large gear ring includes: The end face pressure angle and normal pressure angle of the mating pinion are respectively equal to the end face pressure angle of the large gear ring after deformation and the normal pressure angle of the large gear ring after deformation; The end face modulus and normal modulus of the mating pinion are respectively equal to the end face modulus and normal modulus of the large ring gear after the large ring gear is deformed.

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