A high-speed high-load low-vibration multi-engagement-zone gear and a gear profile design method thereof

Abstract

The application discloses a high-speed high-load low-vibration multi-engagement-zone gear and a tooth profile design method thereof, wherein the high-speed high-load low-vibration multi-engagement-zone gear comprises a first gear and a second gear, a tooth profile curve of the first gear comprises a first tooth crest curve segment L3, a first involute curve segment L2 and a first tooth root curve segment L1, a tooth profile curve of the second gear comprises a second tooth crest curve segment L3', a second involute curve segment L2' and a second tooth root curve segment L1', and the first tooth crest curve segment L3 and the second tooth root curve segment L1' are continuously engaged, the first involute curve segment L2 and the second involute curve segment L2' are continuously engaged, and the first tooth root curve segment L1 and the second tooth crest curve segment L3' are continuously engaged during the engagement of the first gear and the second gear. The application can effectively bear higher load, improves the load bearing capacity and the end face coincidence degree of the gear pair, and can make the transmission process more stable and better adapt to high-speed working conditions.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of cylindrical gear transmission and processing application, and particularly relates to a high-speed high-load low-vibration multi-engagement-zone gear and a tooth profile design method thereof. BACKGROUND

[0002] For the research on involute cylindrical gears, domestic scholars have conducted a large number of theoretical and experimental researches for many years. Ordinary involute cylindrical gears are widely used in various mechanical transmission fields due to low manufacturing cost and high transmission efficiency. However, with the change of application scenarios and the increasing requirement of people on the working environment, the ordinary involute cylindrical gears are difficult to meet the application requirements, especially in the working conditions of high speed and high torque, the gear pair vibration is obvious, so the gear pair needs to have high precision, in addition, the gear pair needs to have strong load capacity in limited space, so there are high requirements on the manufacturing and theoretical design of the gear pair. SUMMARY

[0003] The present application provides a high-speed high-load low-vibration multi-engagement-zone gear and a tooth profile design method thereof.

[0004] To achieve the above-mentioned purpose, the technical scheme of the present application is as follows:

[0005] In one aspect, the present application provides a high-speed high-load low-vibration multi-engagement-zone gear, which comprises a first gear and a second gear, the first gear and the second gear form a gear pair, the tooth profile curve of the first gear comprises a first tooth crest curve segment L3, a first involute curve segment L2 and a first tooth root curve segment L1, the first involute curve segment L2 connects the first tooth crest curve segment L3 and the first tooth root curve segment L1.

[0006] The tooth profile curve of the second gear comprises a second tooth crest curve segment L3', a second involute curve segment L2' and a second tooth root curve segment L1', the second involute curve segment L2' connects the second tooth crest curve segment L3' and the second tooth root curve segment L1'.

[0007] During the meshing process of the first gear and the second gear, the first tooth crest curve segment L3 continuously meshes with the second tooth root curve segment L1', the first involute curve segment L2 continuously meshes with the second involute curve segment L2', and the first tooth root curve segment L1 continuously meshes with the second tooth crest curve segment L3'.

[0008] Further, the first tooth crest curve segment L3 on the first gear and the second tooth crest curve segment L3' on the second gear are both convex arc lines; the first tooth root curve segment L1 of the first gear and the second tooth root curve segment L1' of the second gear are both concave arc lines.

[0009] Further, two ends of the first involute curve segment L2 are tangent to the first addendum curve segment L3 and the first dedendum curve segment L1 respectively; two ends of the second involute curve segment L2' are tangent to the second addendum curve segment L3' and the second dedendum curve segment L1' respectively.

[0010] Further, the first addendum transition curve segment L4 not participating in meshing is connected between two first addendum curve segments L3 on the first gear in a tangent connection mode, and the second addendum transition curve segment L4' not participating in meshing is connected between two second addendum curve segments L3' on the second gear in a tangent connection mode.

[0011] Further, another aspect of the present application further provides a tooth profile design method of a high-speed high-load low-vibration multi-meshing area gear, comprising the following steps:

[0012] Step S1, selecting design parameters of the first gear and the second gear in a gear pair through bearing strength, and designing parameters of a first tool and a second tool for machining the first gear and the second gear respectively through the design parameters of the first gear and the second gear;

[0013] Step S2, obtaining a homogeneous coordinate equation of an arbitrary point M1 on the first tool in a first gear machining coordinate system and a homogeneous coordinate equation of an arbitrary point M2 on the second tool in a second gear machining coordinate system through the design parameters of the first gear and the second gear and the parameters of the first tool and the second tool;

[0014] Step S3, deducing tooth profile curve equations of the first gear and the second gear through coordinate equations of points on tooth profile curves of the first tool and the second tool.

[0015] Further, the design parameters in the step S1 at least include part or all of the following parameters: number of teeth, normal modulus, normal pressure angle, helix angle, modification coefficient, addendum coefficient, addendum clearance coefficient, dedendum corner radius.

[0016] Further, the step S2 specifically comprises the following steps:

[0017] Step S21, establishing a first gear machining coordinate system with an original point located on a first gear division circle according to a machining principle of the gear, in the first gear machining coordinate system, a Y1 axis is tangent to the first gear division circle and parallel to a center line of the first tool, an X1 axis is perpendicular to the Y1 axis and coincides with an axis center of the first gear division circle, a Z1 axis, the Y1 axis and the X1 axis are perpendicular to each other;

[0018] Step S22, a second gear machining coordinate system with the origin located on the second gear division circle is established according to the machining principle of the gear, in the second gear machining coordinate system, the Y2 axis is tangent to the second gear division circle and parallel to the center line of the second cutter, the X2 axis is perpendicular to the Y2 axis and coincides with the center of the second gear division circle, the Z2 axis, the Y2 axis and the X2 axis are perpendicular to each other;

[0019] Step S23, the homogeneous coordinate equation of any point M1 on the first cutter in the first gear machining coordinate system is obtained through the design parameters of the first gear and the parameters of the first cutter; then the homogeneous coordinate equation of any point M2 on the second cutter in the second gear machining coordinate system is obtained through the design parameters of the second gear and the parameters of the second cutter; the two homogeneous coordinate equations are the same, only the parameter values are different.

[0020] Further, the homogeneous coordinate equation of any point M1 on the first cutter in the first gear machining coordinate system specifically includes the coordinate equation of any point M1 on the first cutter in the straight line machining section, the coordinate equation of any point M1 on the first cutter in the nose radius section, and the coordinate equation of any point M1 on the first cutter in the root radius section, which are specifically as follows:

[0021] The coordinate equation of any point M1 on the first cutter in the straight line machining section is:

[0022]

[0023] The coordinate equation of any point M1 on the first cutter in the nose radius section is:

[0024]

[0025] The coordinate equation of any point M1 on the first cutter in the root radius section is:

[0026]

[0027] Wherein, represents the coordinate position vector of the tooth surface; represents the coordinate position vector of the tooth root; represents the coordinate position vector of the tooth tip; the upper indexes r and l of the left three parameters respectively represent the right and left sides of the first cutter, when r is taken, the + sign is taken as the upper part, when l is taken, the + sign is taken as the lower part, and γ is the motion parameter of any point M1 in the first cutter section root arc line part, when the upper index of the left three parameters is taken as r, -π / 2≤γ≤0, and when the upper index of the left three parameters is taken as l, 0≤γ≤π / 2; the subscripts mc, gc and dc of the left three parameters respectively represent the tooth surface, the tooth root and the tooth tip; n is the normal relative position coefficient of the first gear, m n is the normal relative modulus of the first gear, is the addendum coefficient of the first gear, t is the length of the linear part of the first tool rake section; u is the long-short axis ratio of the tool root ellipse; p is the first tool addendum arc radius; p' is the first tool root ellipse arc short axis radius, beta is the helix angle of the first gear, alpha n is the normal pressure angle of the first gear, alpha t is the first gear end face pressure angle, theta t represents the coordinate component of the coordinate vector in the Z-axis direction; theta m represents the maximum value of the first tool nose radius; t m represents the maximum value of the length of the linear part of the first tool rake section.

[0028] Further, the step S3 specifically comprises the following steps:

[0029] Step S31, according to the continuous engagement principle, there is a point M'1 on the first gear tooth profile curve corresponding to any point M1 on the first tool; there is a point M'2 on the second gear tooth profile curve corresponding to any point M2 on the second tool; the coordinate values of the first tool any point M1 and the second tool any point M2 are solved by using the two homogeneous coordinate equations obtained in S2;

[0030] Step S32, then the coordinate values of the first gear tooth profile M'1 point and the second gear tooth profile M'2 point are solved by homogeneous coordinate transformation and according to the coordinate values of the first tool any point M1 and the second tool any point M2;

[0031] Step S33, the steps S31 to S32 are cycled to obtain the coordinate values of multiple points on the first gear tooth profile and the coordinate values of multiple points on the second gear tooth profile, and finally the tooth profile curve of the first gear and the tooth profile curve of the second gear are derived according to the coordinate values of multiple points on the first gear tooth profile and the coordinate values of multiple points on the second gear tooth profile.

[0032] Further, the shape of the tip portion of the first tool and the second tool is a round angle, and the shape of the root portion of the first tool and the second tool is an elliptical arc.

[0033] The beneficial effects of the present application are:

[0034] 1, compared with the ordinary involute cylindrical gear, the gear pair addendum and the tooth root participate in meshing transmission, and can share a part of the transmission torque, under the premise of the same size, the tooth root stress concentration is small, and the bearing capacity is stronger than that of the ordinary involute gear;

[0035] 2、The invention, the tooth top and the tooth root of the gear pair (consisting of the first gear and the second gear) are continuously engaged, there is no engagement impact of the tooth top and the tooth root of the gear pair, compared with the conventional gear pair, the vibration generated by the engagement of the gear pair is effectively reduced, the vibration problem generated by the gear at the non-continuous engagement point is solved, the coincidence degree of the gear pair is increased to a certain extent, the transmission is more stable, and the gear pair has more excellent performance under high-speed working conditions.

[0036] 3、Under the same design space, the gear pair provided by the invention has stronger bearing capacity than the ordinary involute gear pair, and the design space can be reduced to a certain extent by applying the gear pair.

[0037] 4、During the engagement of the gear pair, the tooth top and the tooth root are engaged, the tooth root part and the tooth top part of the gear pair have a relatively high speed of movement, which is more conducive to the formation of the lubricating oil film at the tooth root, effectively reduces the wear of the gear pair, and improves the fatigue resistance of the tooth surface. BRIEF DESCRIPTION OF DRAWINGS

[0038] Figure 1 It is a high-speed high-bearing low-vibration multi-engagement area gear tooth profile schematic diagram.

[0039] Figure 2 It is a multi-engagement area gear engagement schematic diagram.

[0040] Figure 3 It is a multi-engagement area gear machining tool section view.

[0041] Figure 4 It is a multi-engagement area gear machining coordinate system schematic diagram. DETAILED DESCRIPTION

[0042] In order to facilitate the understanding of the present application, the present application will be described more fully below with reference to the accompanying drawings. The preferred embodiments of the present application are shown in the drawings. However, the present application can be realized in many other different forms, and is not limited to the embodiments described herein. On the contrary, the purpose of providing these embodiments is to make the disclosure of the present application more thorough and comprehensive.

[0043] It should be noted that when an element is referred to as being "fixed to" or "disposed on" another element, it can be directly on the other element or indirectly on the other element. When an element is referred to as being "connected to" another element, it can be directly connected to the other element or indirectly connected to the other element.

[0044] It should be understood that the terms "length", "width", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer" and the like, indicate directions or positions based on the directions or positions shown in the drawings, and are used only for the purpose of facilitating the description of the present application and simplifying the description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the present application.

[0045] In addition, the terms "first", "second" are only for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the technical features indicated. Therefore, the features defined as "first", "second" can explicitly or implicitly include one or more of the features. In the description of the present application, the meaning of "multiple" is two or more, unless otherwise specifically limited.

[0046] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which the present application belongs. The terms used in the specification of the present application are only for the purpose of describing specific embodiments and are not intended to limit the present application. The term "and / or" used herein includes any and all combinations of one or more of the related listed items.

[0047] It should also be noted that the same reference signs are used to represent the same components or the same parts in the embodiments of the present application. For the same parts in the embodiments of the present application, only one part or component may be labeled with a reference sign in the drawings, and it should be understood that the reference sign is also applicable to other identical parts or components.

[0048] As described in the background art, the ordinary involute cylindrical gear is already difficult to meet the requirements of high precision and high load capacity under high speed and high torque working conditions,

[0049] To solve the above problems, with reference to Figures 1-4 The present application provides a high-speed high-load low-vibration multi-engagement zone gear, which comprises a first gear and a second gear, the first gear and the second gear form a gear pair, the tooth profile curve of the first gear comprises a first addendum curve segment L3, a first involute curve segment L2 and a first dedendum curve segment L1, the first involute curve segment L2 connects the first addendum curve segment L3 and the first dedendum curve segment L1;

[0050] The tooth profile curve of the second gear comprises a second addendum curve segment L3', a second involute curve segment L2' and a second dedendum curve segment L1', the second involute curve segment L2' connects the second addendum curve segment L3' and the second dedendum curve segment L1';

[0051] Specifically, Figure 1 SAP in the figure represents an involute start circle; EAP represents an involute end circle; refer to Figure 2 , Figure 2 The dashed line H1 in the figure represents an effective addendum circle of the second gear; the dashed line H2 represents an involute start circle of the first gear or an involute end circle of the second gear; the dashed line H3 represents an involute end circle of the first gear or an involute start circle of the second gear; the dashed line H4 represents an effective addendum circle of the first gear;

[0052] The first tooth root curve segment L1 is located between the tooth root circle of the first gear and the dashed line H2; the first involute curve segment L2 and the second involute curve segment L2' are both located between the dashed line H2 and the dashed line H3; the first addendum curve segment L3 is located between the dashed line H3 and the dashed line H4; the second tooth root curve segment L1' is located between the tooth root circle of the second gear and the dashed line H3; the second addendum curve segment L3' is located between the dashed line H1 and the dashed line H2.

[0053] During the meshing of the first gear and the second gear, the first addendum curve segment L3 and the second tooth root curve segment L1' are continuously meshed, the first involute curve segment L2 and the second involute curve segment L2' are continuously meshed, and the first tooth root curve segment L1 and the second addendum curve segment L3' are continuously meshed.

[0054] In some embodiments, the first addendum curve segment L3 on the first gear and the second addendum curve segment L3' on the second gear are both convex arc lines; the first tooth root curve segment L1 of the first gear and the second tooth root curve segment L1' of the second gear are both concave arc lines.

[0055] In some embodiments, the two ends of the first involute curve segment L2 are tangent to the first addendum curve segment L3 and the first tooth root curve segment L1 respectively; the two ends of the second involute curve segment L2' are tangent to the second addendum curve segment L3' and the second tooth root curve segment L1' respectively.

[0056] In some embodiments, between the two first addendum curve segments L3 on the first gear, there is a first addendum transition curve segment L4 connected in a tangent connection manner and not participating in meshing; between the two second addendum curve segments L3' on the second gear, there is a second addendum transition curve segment L4' connected in a tangent connection manner and not participating in meshing.

[0057] Specifically, refer to Figure 2 The first addendum transition curve segment L4 is located between the dashed line H4 and the addendum circle of the first gear; the second addendum transition curve segment L4' is located between the dashed line H1 and the addendum circle of the second gear.

[0058] Refer to Figure 2In the meshing process, the tooth top part of the first gear first enters meshing with the tooth root part of the second gear, at this stage, the first tooth top curve segment L3 and the second tooth root curve segment L1' enter the meshing stage, with the continuous meshing of the first gear and the second gear, the tooth face part of the first gear starts to mesh with the tooth face part of the second gear, at this stage, the first involute curve segment L2 of the first gear and the second involute curve segment L2' of the second gear form a conventional involute gear meshing, with the continuous meshing of the first gear and the second gear, the tooth root part of the first gear meshes with the tooth top part of the second gear, at this stage, the first tooth root curve segment L1 of the first gear and the second tooth top curve segment L3' of the second gear enter the meshing stage, the gear in the application has multiple continuous meshing areas, theoretically, no meshing impact is generated, the meshing of the first gear and the second gear is more stable, the transmission is more stable, and the gear can be better applied to high-speed working conditions.

[0059] Another aspect of the application also provides a tooth profile design method of a high-speed high-load low-vibration multi-meshing area gear, comprising the following steps:

[0060] Step S1, selecting the design parameters of the first gear and the second gear in the gear pair through the bearing strength, and designing the parameters of the first cutter and the second cutter for machining the first gear and the second gear respectively through the design parameters of the first gear and the second gear;

[0061] Step S2, obtaining the homogeneous coordinate equation of any point M1 on the first cutter in the first gear machining coordinate system and the homogeneous coordinate equation of any point M2 on the second cutter in the second gear machining coordinate system through the design parameters of the first gear and the second gear and the parameters of the first cutter and the second cutter;

[0062] Step S3, deducing the tooth profile curve equation of the first gear and the second gear through the coordinate equations of the points on the tooth profile curves of the first cutter and the second cutter.

[0063] In some embodiments, the design parameters in step S1 include at least part or all of the following parameters: number of teeth, normal modulus, normal pressure angle, helix angle, modification coefficient, addendum coefficient, addendum clearance coefficient, and dedendum corner radius.

[0064] The following illustrates the design parameters by taking two paired helical cylindrical gears as an example, the design parameters of the two helical cylindrical gears are shown in Table 1, and the specific parameters are as follows:

[0065] Table 1, design parameter table of helical cylindrical gears;

[0066]

[0067] In addition, other parameters of the helical cylindrical gears can be calculated according to the design parameters of the helical cylindrical gears, and the specific parameters are as follows:

[0068] Face pressure angle: tan a t = tan a n / cos b→a t = 16.8815°;

[0069] Face module: m t = m n / cos b→m t = 1.804;

[0070] Base circle diameter: d b = z*m n / cos b→d b1 = 52.321, d b2 = 142.531

[0071] Tooth root formation circle development length:

[0072] C 01 = 2.267; C 02 = 6.009

[0073] Involute termination circle development length:

[0074] Tool cross-sectional straight line length: t = (C1-C0)tan a t

[0075] From the calculation results, C 11 -C 01 = C 12 -C 02 , that is, the length of the straight line part of the tool blade of the pair of gears is equal.

[0076] In some embodiments, the step S2 specifically comprises the following steps:

[0077] Step S21, establishing a first gear machining coordinate system with the origin located on the first gear division circle according to the machining principle of the gear, in the first gear machining coordinate system, the Y1 axis is tangent to the first gear division circle and parallel to the center line of the first tool, the X1 axis is perpendicular to the Y1 axis and coincides with the axis circle center of the first gear division circle, the Z1 axis, the Y1 axis and the X1 axis are perpendicular to each other;

[0078] Step S22, establishing a second gear machining coordinate system with the origin located on the second gear division circle according to the machining principle of the gear, in the second gear machining coordinate system, the Y2 axis is tangent to the second gear division circle and parallel to the center line of the second tool, the X2 axis is perpendicular to the Y2 axis and coincides with the axis circle center of the second gear division circle, the Z2 axis, the Y2 axis and the X2 axis are perpendicular to each other;

[0079] Step S23, obtaining the homogeneous coordinate equation of any point M1 on the first tool in the first gear machining coordinate system through the design parameters of the first gear and the parameters of the first tool; then obtaining the homogeneous coordinate equation of any point M2 on the second tool in the second gear machining coordinate system through the design parameters of the second gear and the parameters of the second tool; the two homogeneous coordinate equations are the same, only the parameter values are different.

[0080] In some embodiments, the homogeneous coordinate equation of any point M1 on the first tool in the first gear machining coordinate system specifically includes the coordinate equation of any point M1 on the first tool in the linear machining section, the coordinate equation of any point M1 on the first tool in the nose radius section, and the coordinate equation of any point M1 on the first tool in the root radius section, which are specifically as follows:

[0081] The coordinate equation of any point M1 on the first tool in the linear machining section is:

[0082]

[0083] The coordinate equation of any point M1 on the first tool in the nose radius section is:

[0084]

[0085] The coordinate equation of any point M1 on the first tool in the root radius section is:

[0086]

[0087] wherein, represents the coordinate position vector of the tooth surface; represents the coordinate position vector of the tooth root; represents the coordinate position vector of the tooth tip; the superscripts r and 1 of the left three parameters respectively represent the right and left sides of the first tool, when r is taken, the ± sign takes the upper part, when 1 is taken, the ± sign takes the lower part, and γ is the motion parameter of any point M1 in the root arc section of the first tool cross section, when the superscript of the left three parameters is taken as r, -π / 2≤γ≤0, and when the superscript of the left three parameters is taken as 1, 0≤γ≤π / 2; the subscripts mc, gc and dc of the left three parameters respectively represent the tooth surface, the tooth root and the tooth tip; x n is the normal relative displacement coefficient of the first gear, m n is the normal module of the first gear, is the addendum coefficient of the first gear, t is the length of the linear part of the first tool bevel section; u is the length-to-short-axis ratio of the root ellipse; ρ is the tooth tip circle radius of the first tool; ρ′ is the short-axis radius of the root ellipse arc of the first tool, β is the helix angle of the first gear, α n is the normal pressure angle of the first gear, α t is the end face pressure angle of the first gear, θ is the nose radius of the first tool, Z tdenotes the coordinate component of the coordinate vector in the direction of the Z-axis; θ m denotes the maximum value of the corner radius of the tip of the first cutter; t m denotes the maximum value of the length of the straight line portion of the chamfer section of the first cutter.

[0088] In some embodiments, the step S3 specifically comprises the following steps:

[0089] Step S31, according to the principle of continuous engagement, there is a point M'1 on the first gear tooth profile curve corresponding to any point M1 on the first cutter, and there is a point M'2 on the second gear tooth profile curve corresponding to any point M2 on the second cutter; the coordinate values of the first cutter point M1 and the second cutter point M2 are solved by using the two homogeneous coordinate equations obtained in S2;

[0090] Step S32, then the coordinate values of the point M'1 on the first gear tooth profile and the point M'2 on the second gear tooth profile are solved by homogeneous coordinate transformation and according to the coordinate values of the first cutter point M1 and the second cutter point M2;

[0091] Step S33, the steps S31 to S32 are repeated to obtain the coordinate values of multiple points on the first gear tooth profile and the coordinate values of multiple points on the second gear tooth profile, and finally the tooth profile curve of the first gear and the tooth profile curve of the second gear are derived according to the coordinate values of the multiple points on the first gear tooth profile and the coordinate values of the multiple points on the second gear tooth profile.

[0092] In some embodiments, the shape of the tip portion of the first cutter and the second cutter is a corner, and the shape of the root portion of the first cutter and the second cutter is an epitrochoid. In order to facilitate processing, the epitrochoid is generally replaced by an elliptical arc.

[0093] In some embodiments, the first cutter and the second cutter are standard rack cutters, which include two machining cutting edges symmetrically arranged on both sides of the standard rack cutter, and the machining cutting edge includes a root corner section, a straight machining section and a tip corner section connected in sequence, the root corner section and the tip corner section are used for machining the addendum curve section and the dedendum curve section of the gear respectively, and the straight machining section is used for machining the involute curve section of the gear, so as to ensure that the addendum of the first gear and the dedendum of the second gear, the involute tooth surface of the first gear and the involute tooth surface of the second gear, and the dedendum of the first gear and the addendum of the second gear can realize continuous engagement.

[0094] The above merely describes specific embodiments of the present application, but the protection scope of the present application is not limited thereto, any person skilled in the art can easily think of changes or replacements within the technical range disclosed by the present application, which should be covered within the protection scope of the present application. Furthermore, the technical solutions of each embodiment of the present application can be combined with each other, but it must be based on the realization of the ordinary skilled person in the art, when the combination of the technical solutions appears contradictory or unachievable, it should be considered that the combination of the technical solutions does not exist, and is not within the protection scope required by the present application. Therefore, the protection scope of the present application should be subject to the protection scope of the claims.

Claims

1. A high-speed, high-load-bearing, low-vibration multi-meshing-area gear, comprising a first gear and a second gear, characterized in that, The tooth profile curve of the first gear includes a first tooth tip curve segment L3, a first involute curve segment L2, and a first tooth root curve segment L1. The first involute curve segment L2 connects the first tooth tip curve segment L3 and the first tooth root curve segment L1. The tooth profile curve of the second gear includes a second tooth tip curve segment L3′, a second involute curve segment L2′, and a second tooth root curve segment L1′, wherein the second involute curve segment L2′ connects the second tooth tip curve segment L3′ and the second tooth root curve segment L1′. During the meshing process of the first gear and the second gear, the first tooth tip curve segment L3 meshes continuously with the second tooth root curve segment L1′, the first involute curve segment L2 meshes continuously with the second involute curve segment L2′, and the first tooth root curve segment L1 and the second tooth tip curve segment L3′ mesh continuously. The first gear has a first tooth tip transition curve segment L4 that does not participate in meshing, which is connected between the two first tooth tip curve segments L3 on the first gear by a tangential connection. The two second tooth tip curve segments L3′ on the second gear are connected in a tangential manner by a second tooth tip transition curve segment L4′ that does not participate in meshing.

2. The high-speed, high-load-bearing, low-vibration, multi-meshing-zone gear according to claim 1, characterized in that, The first tooth tip curve segment L3 on the first gear and the second tooth tip curve segment L3′ on the second gear are both convex arcs; the first tooth root curve segment L1 on the first gear and the second tooth root curve segment L1′ on the second gear are both concave arcs.

3. The high-speed, high-load-bearing, low-vibration, multi-meshing-zone gear according to claim 1, characterized in that, The two ends of the first involute curve segment L2 are tangent to the first tooth tip curve segment L3 and the first tooth root curve segment L1, respectively; the two ends of the second involute curve segment L2′ are tangent to the second tooth tip curve segment L3′ and the second tooth root curve segment L1′, respectively.

4. A tooth profile design method for a high-speed, high-load-bearing, low-vibration, multi-meshing-area gear as described in any one of claims 1 to 3, characterized in that, Includes the following steps: Step S1: Select the design parameters of the first gear and the second gear based on the load-bearing strength; and design the parameters of the first tool and the second tool for machining the first gear and the second gear respectively based on the design parameters of the first gear and the second gear. Step S2: Obtain the homogeneous coordinate equation of any point M1 on the first tool in the first gear machining coordinate system and the homogeneous coordinate equation of any point M2 on the second tool in the second gear machining coordinate system by using the design parameters of the first gear and the second gear and the parameters of the first tool and the second tool. Step S3: Using the coordinate equations of the points on the tooth profile curves of the first and second tools, derive the tooth profile curve equations of the first and second gears.

5. The tooth profile design method according to claim 4, characterized in that, The design parameters in S1 include at least some or all of the following parameters; Number of teeth, normal module, normal pressure angle, helix angle, displacement coefficient, addendum coefficient, clearance coefficient, and root fillet radius.

6. The tooth profile design method according to claim 4, characterized in that, Step S2 specifically includes the following steps: Step S21: Based on the gear machining principle, establish a first gear machining coordinate system with the origin located on the pitch circle of the first gear. In the first gear machining coordinate system, the Y1 axis is tangent to the pitch circle of the first gear and parallel to the center line of the first tool. The X1 axis is perpendicular to the Y1 axis and coincides with the center of the pitch circle of the first gear. The Z1 axis, Y1 axis and X1 axis are perpendicular to each other. Step S22: Based on the gear machining principle, establish a second gear machining coordinate system with the origin located on the pitch circle of the second gear. In the second gear machining coordinate system, the Y2 axis is tangent to the pitch circle of the second gear and parallel to the center line of the second tool. The X2 axis is perpendicular to the Y2 axis and coincides with the center of the pitch circle of the second gear. The Z2 axis, Y2 axis and X2 axis are perpendicular to each other. Step S23: Obtain the homogeneous coordinate equation of any point M1 on the first tool in the first gear machining coordinate system using the design parameters of the first gear and the parameters of the first tool; then obtain the homogeneous coordinate equation of any point M2 on the second tool in the second gear machining coordinate system using the design parameters of the second gear and the parameters of the second tool; the two homogeneous coordinate equations are the same, only the parameter values ​​are different.

7. The tooth profile design method according to claim 4 or 6, characterized in that, The homogeneous coordinate equation of any point M1 on the first cutting tool in the first gear machining coordinate system specifically includes the coordinate equation of any point M1 on the first cutting tool in the straight machining segment, the coordinate equation of any point M1 on the first cutting tool in the tool tip fillet segment, and the coordinate equation of any point M1 on the first cutting tool in the tool root fillet segment. The three coordinate equations are as follows: The coordinate equation of any point M1 on the first tool in the straight machining segment is as follows: The coordinate equation of any point M1 on the first cutting tool in the fillet segment of the cutting tip: The coordinate equation of any point M1 on the first cutting tool in the fillet segment of the tool root is as follows: in, Represents the coordinate position vector of the tooth surface; Represents the coordinate position vector of the tooth root; This represents the coordinate vector of the tooth tip; the superscripts r and l of the three parameters on the left represent the right and left sides of the first tool, respectively. When r is used, the upper part of the ± sign is used, and when l is used, the lower part of the ± sign is used. γ is the motion parameter of any point M1 on the root arc of the first tool section. When the superscript of the three parameters on the left is r, -π / 2≤γ≤0, and when l is used, 0≤γ≤π / 2; the subscripts mc, gc, and dc represent the tooth surface, tooth root, and tooth tip, respectively; x n Let m be the normal phase displacement coefficient of the first gear. n The normal phase module of the first gear is... α is the addendum coefficient of the first gear; t is the length of the straight section of the inclined plane of the first cutter; u is the ratio of the major and minor axes of the cutter root ellipse; ρ is the radius of the addendum arc of the first cutter; ρ′ is the minor axis radius of the arc of the root ellipse of the first cutter; β is the helix angle of the first gear; α n Let α be the normal pressure angle of the first gear. t Let θ be the pressure angle of the first gear end face, θ be the fillet radius of the first cutting tool, and Z be the radius of the first cutting tool tip. t θ represents the coordinate components of the coordinate vector along the Z-axis; m t represents the maximum value of the tip radius of the first cutting tool; m This represents the maximum length of the straight section of the first cutter's inclined plane.

8. The tooth profile design method according to claim 4, characterized in that, Step S3 specifically includes the following steps: Step S31: According to the principle of continuous meshing, there must be a point M′1 on the tooth profile curve of the first gear that corresponds to any point M1 on the first tool; there must be a point M′2 on the tooth profile curve of the second gear that corresponds to any point M2 on the second tool; use the two homogeneous coordinate equations obtained in S2 to solve for the coordinate values ​​of any point M1 on the first tool and any point M2 on the second tool respectively. Step S32: Then, through homogeneous coordinate transformation, and based on the coordinate values ​​of any point M1 of the first tool and any point M2 of the second tool, solve for the coordinate values ​​of point M′1 on the tooth profile of the first gear and the coordinate values ​​of point M′2 on the tooth profile of the second gear respectively. Step S33: Repeat steps S31 to S32 to obtain the coordinate values ​​of multiple points on the tooth profile of the first gear and multiple points on the tooth profile of the second gear. Finally, based on the coordinate values ​​of multiple points on the tooth profile of the first gear and multiple points on the tooth profile of the second gear, the tooth profile curves of the first gear and the second gear are derived respectively.

9. The tooth profile design method according to claim 8, characterized in that, The tips of the first and second cutting tools are rounded, and the roots of the first and second cutting tools are elliptical.

Images