High-speed high-bearing low-vibration multi-meshing-area gear and tooth profile design method thereof

Abstract

The invention discloses a high-speed, high-load and low-vibration multi-meshing-area gear and a tooth profile design method thereof, the high-speed, high-load and low-vibration multi-meshing-area gear comprises a first gear and a second gear, and a tooth profile curve of the first gear comprises a first tooth crest curve section L3, a first involute curve section L2 and a first tooth root curve section L1; the tooth profile curve of the second gear comprises a second tooth crest curve section L3 ', a second involute curve section L2' and a second tooth root curve section L1 '; and in the meshing process of the first gear and the second gear, the first tooth crest curve section L3 is continuously meshed with the second tooth root curve section L1 ', the first involute curve section L2 is continuously meshed with the second involute curve section L2', and the first tooth root curve section L1 is continuously meshed with the second tooth crest curve section L3 '. The gear pair can effectively bear higher loads, the bearing capacity and the end face contact ratio of the gear pair are improved, the transmission process can be more stable, and the gear pair can better adapt to the high-speed working condition.

Description

Technical Field

[0001] The invention relates to the technical field of cylindrical gear transmission and processing application, and in particular to a high-speed, high-load, low-vibration, multi-meshing-area gear and a tooth profile design method thereof. Background Art

[0002] Domestic scholars have conducted a lot of theoretical and experimental research on involute cylindrical gears over the years. Ordinary involute cylindrical gear transmission is widely used in various mechanical transmission fields due to its low manufacturing cost and high transmission efficiency. However, with the changes in application scenarios and people's increasingly higher requirements for the working environment, ordinary involute cylindrical gears have become more difficult to meet application requirements, especially under high speed and high torque conditions, the vibration of the gear pair is more obvious, so this requires the gear pair to have high precision. In addition, in a limited space, the gear pair is also required to have a strong load-bearing capacity, so there are extremely high requirements in the manufacturing and processing and theoretical design stages of the gear pair. Summary of the invention

[0003] The purpose of the present invention is to provide a high-speed, high-load, low-vibration, multi-meshing-area gear and a tooth profile design method thereof.

[0004] To achieve the above object, the technical solution of the present invention is achieved as follows:

[0005] On one hand, the present invention provides a high-speed, high-load, low-vibration, multi-meshing-area gear, comprising a first gear and a second gear, the first gear and the second gear forming a gear pair, the tooth profile curve of the first gear comprising a first tooth top curve segment L3, a first involute curve segment L2 and a first tooth root curve segment L1, the first involute curve segment L2 connecting the first tooth top curve segment L3 and the first tooth root curve segment L1;

[0006] The tooth profile curve of the second gear includes a second tooth top curve segment L3′, a second involute curve segment L2′ and a second tooth root curve segment L1′, and the second involute curve segment L2′ connects the second tooth top 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 top curve segment L3 is continuously meshed with the second tooth root curve segment L1′, the first involute curve segment L2 is continuously meshed with the second involute curve segment L2′, and the first tooth root curve segment L1 and the second tooth top curve segment L3′ are continuously meshed.

[0008] Furthermore, the first tooth top curve segment L3 on the first gear and the second tooth top curve segment L3′ on the second gear are both convex arcs; 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 arcs.

[0009] Furthermore, two ends of the first involute curve segment L2 are tangent to the first tooth top curve segment L3 and the first tooth root curve segment L1 respectively; two ends of the second involute curve segment L2′ are tangent to the second tooth top curve segment L3′ and the second tooth root curve segment L1′ respectively.

[0010] Furthermore, the two first tooth top curve segments L3 on the first gear are connected tangentially with a first tooth top transition curve segment L4 that does not participate in meshing, and the two second tooth top curve segments L3′ on the second gear are connected tangentially with a second tooth top transition curve segment L4′ that does not participate in meshing.

[0011] Furthermore, another aspect of the present invention provides a tooth profile design method for a high-speed, high-load, low-vibration, multi-meshing-zone gear, comprising the following steps:

[0012] Step S1, selecting design parameters of a first gear and a second gear in a gear pair according to the bearing strength, and designing parameters of a first tool and a second tool for machining the first gear and the second gear respectively according to 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 the first gear machining coordinate system and a homogeneous coordinate equation of an arbitrary point M2 on the second tool in the second gear machining coordinate system through design parameters of the first gear and the second gear and parameters of the first tool and the second tool;

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

[0015] Furthermore, the design parameters in step S1 include at least part or all of the following parameters: number of teeth, normal module, normal pressure angle, helix angle, displacement coefficient, tooth top height coefficient, top clearance coefficient, and tooth root fillet radius.

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

[0017] Step S21, according to the gear processing principle, a first gear processing coordinate system with its origin located on the first gear pitch circle is established, in which the Y1 axis is tangent to the first gear pitch 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 center of the first gear pitch circle, and the Z1 axis, the Y1 axis and the X1 axis are perpendicular to each other;

[0018] Step S22, according to the gear processing principle, a second gear processing coordinate system with its origin located on the second gear pitch circle is established, in which the Y2 axis is tangent to the second gear pitch 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 center of the second gear pitch circle, and the Z2 axis, the Y2 axis and the X2 axis are perpendicular to each other;

[0019] Step S23, obtain the homogeneous coordinate equation of any point M1 on the first tool in the first gear processing coordinate system through 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 processing 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 except that the parameter values ​​are inconsistent.

[0020] Further, the homogeneous coordinate equation of any point M1 on the first tool in the first gear processing coordinate system specifically includes the coordinate equation of any point M1 on the first tool in the straight line processing segment, the coordinate equation of any point M1 on the first tool in the tool tip fillet segment, and the coordinate equation of any point M1 on the first tool in the tool root fillet segment. The three coordinate equations are specifically as follows:

[0021] The coordinate equation of any point M1 on the first tool in the straight line machining segment:

[0022]

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

[0024]

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

[0026]

[0027] in, Represents the tooth surface coordinate position vector; represents the tooth root coordinate position vector; Represents the tooth top coordinate position vector; 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 taken, the ± sign takes the upper part, and when l is taken, the ± sign takes the lower part. γ is the motion parameter of any point M1 in the arc part of the root of the first tool section. When the superscripts of the three parameters on the left are taken as r, -π / 2≤γ≤0, and when l is taken, 0≤γ≤π / 2; the subscripts mc, gc and dc of the three parameters on the left represent the tooth surface, tooth root and tooth top respectively; x n is the normal phase modification coefficient of the first gear, m n is the normal modulus of the first gear, is the tooth top height coefficient of the first gear, t is the length of the straight part of the first tool slope segment; u is the major-minor axis ratio of the tool root ellipse; ρ is the radius of the first tool tooth top arc; ρ′ is the minor axis radius of the first tool tooth root ellipse arc, β is the helix angle of the first gear, α n is the normal pressure angle of the first gear, α t is the pressure angle of the first gear end face, θ is the tool tip radius of the first tool, Z t Represents the coordinate component of the coordinate vector in the Z-axis direction; θ m Indicates the maximum value of the tool tip radius of the first tool; t m Indicates the maximum value of the length of the straight portion of the first tool slope segment.

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

[0029] 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 corresponding to any point M1 on the first tool; there must be a point M′2 on the tooth profile curve of the second gear corresponding to any point M2 on the second tool; the coordinate values ​​of any point M1 of the first tool and any point M2 of the second tool are solved by using the two homogeneous coordinate equations obtained in S2;

[0030] Step S32, then by homogeneous coordinate transformation, and according to the coordinate value of the arbitrary point M1 of the first tool and the coordinate value of the arbitrary point M2 of the second tool, respectively solve the coordinate value of the point M'1 on the first gear tooth profile and the coordinate value of the point M'2 on the second gear tooth profile;

[0031] Step S33, looping step S31 to step S32, obtaining 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 deriving the tooth profile curve of the first gear and the tooth profile curve of the second gear respectively 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] Furthermore, the tip portions of the first tool and the second tool are in the shape of rounded corners, and the root portions of the first tool and the second tool are in the shape of an elliptical arc.

[0033] Beneficial effects of the present invention:

[0034] 1. Compared with ordinary involute cylindrical gears, the tooth top and tooth root of the gear pair of the present invention participate in meshing transmission, which can share part of the transmission torque. Under the premise of the same size, the stress concentration of the tooth root is small, and its load-bearing capacity is stronger than that of ordinary involute gears;

[0035] 2. The meshing of the tooth top and the tooth root of the gear pair (composed of the first gear and the second gear) in the present invention is continuous meshing, and there is no meshing impact between the tooth top and the tooth root of the gear pair. Compared with the conventional gear pair, the vibration generated by the meshing of the gear pair is effectively reduced, and the vibration problem generated by the gear at the discontinuous meshing point is solved. The overlap of the gear pair is increased to a certain extent, making the transmission more stable and having better performance under high-speed conditions;

[0036] 3. Under the same design space, the gear pair provided by the present invention has a stronger load-bearing capacity than the ordinary involute gear pair. The application of this gear pair can reduce the design space to a certain extent.

[0037] 4. During the meshing process of the gear pair of the present invention, the tooth top and the tooth root mesh, and the tooth root and the tooth top of the gear pair have a higher relative movement speed, which is more conducive to the formation of lubricating oil film at the tooth root, effectively reducing the wear of the gear pair and improving the fatigue resistance of the tooth surface. BRIEF DESCRIPTION OF THE DRAWINGS

[0038] Figure 1 It is a schematic diagram of the gear tooth profile of high-speed, high-load, low-vibration and multi-meshing areas;

[0039] Figure 2 It is a schematic diagram of meshing of a gear pair with multiple meshing zones;

[0040] Figure 3 This is a cross-sectional view of a tool for machining gears with multiple meshing zones;

[0041] Figure 4 Schematic diagram of the machining coordinate system for multi-meshing zone gears. DETAILED DESCRIPTION

[0042] In order to facilitate the understanding of the present invention, the present invention will be described more fully below with reference to the relevant drawings. Preferred embodiments of the present invention are provided in the drawings. However, the present invention can be implemented 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 understanding of the disclosure of the present invention 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 orientation or position relationship indicated by terms such as "length", "width", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside" and "outside" are based on the orientation or position relationship shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operate in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0045] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, the meaning of "plurality" is two or more, unless otherwise clearly and specifically defined.

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

[0047] It should also be noted that, in the embodiments of the present application, the same figure mark is used to represent the same component or the same part. For the same parts in the embodiments of the present application, the figure may only mark one of the parts or components as an example. It should be understood that the figure mark also applies to other identical parts or components.

[0048] As described in the background technology, ordinary involute cylindrical gears have difficulty meeting the requirements of high precision and high load capacity under high speed and high torque conditions.

[0049] To solve the above problems, refer to Figure 1 to Figure 4 The present application provides a high-speed, high-load, low-vibration, multi-meshing-area gear, comprising a first gear and a second gear, the first gear and the second gear forming a gear pair, the tooth profile curve of the first gear comprising a first tooth top curve segment L3, a first involute curve segment L2 and a first tooth root curve segment L1, the first involute curve segment L2 connecting the first tooth top curve segment L3 and the first tooth root curve segment L1;

[0050] The tooth profile curve of the second gear includes a second tooth top curve segment L3′, a second involute curve segment L2′ and a second tooth root curve segment L1′, and the second involute curve segment L2′ connects the second tooth top curve segment L3′ and the second tooth root curve segment L1′;

[0051] Specifically, Figure 1 SAP in the figure indicates the starting circle of the involute; EAP indicates the ending circle of the involute; Figure 2 , Figure 2 The dotted line H1 is the effective addendum circle of the second gear; the dotted line H2 is the involute starting circle of the first gear or the involute ending circle of the second gear; the dotted line H3 is the involute ending circle of the first gear or the involute starting circle of the second gear; the dotted line H4 is the 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 dotted line H2; the first involute curve segment L2 and the second involute curve segment L2' are both located between the dotted line H2 and the dotted line H3; the first tooth top curve segment L3 is located between the dotted line H3 and the dotted line H4; the second tooth root curve segment L1' is located between the tooth root circle of the second gear and the dotted line H3; the second tooth top curve segment L3' is located between the dotted line H1 and the dotted line H2;

[0053] During the meshing process of the first gear and the second gear, the first tooth top 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 meshes continuously with the second tooth top curve segment L3'.

[0054] In some embodiments, the first tooth top curve segment L3 on the first gear and the second tooth top curve segment L3' on the second gear are both convex arcs; 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 arcs.

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

[0056] In some embodiments, the two first tooth top curve segments L3 on the first gear are connected tangentially with a first tooth top transition curve segment L4 that does not participate in meshing, and the two second tooth top curve segments L3′ on the second gear are connected tangentially with a second tooth top transition curve segment L4′ that does not participate in meshing.

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

[0058] Reference Figure 2During the meshing process, the tooth top portion of the first gear and the tooth root portion of the second gear first enter into meshing. At this stage, the first tooth top curve segment L3 and the second tooth root curve segment L1′ enter into the meshing stage. As the gear meshing continues, the tooth surface portion of the first gear and the tooth surface portion of the second gear begin to enter into meshing. 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. As the meshing of the first gear and the second gear continues, the tooth root portion of the first gear and the tooth top portion of the second gear enter into meshing. 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 into the meshing stage. The gear in the present invention has multiple continuous meshing areas, and theoretically no meshing impact is generated, so that the meshing of the first gear and the second gear is more stable, the transmission is smoother, and it can be better applied to high-speed conditions.

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

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

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

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

[0063] In some embodiments, the design parameters in step S1 include at least some or all of the following parameters: number of teeth, normal module, normal pressure angle, helix angle, displacement coefficient, tooth top height coefficient, top clearance coefficient, and tooth root fillet radius.

[0064] The following is an example of design parameters. Taking two paired helical cylindrical gears as an example, the design parameters of the two helical cylindrical gears are shown in Table 1, as follows:

[0065] Table 1. Design parameters of helical cylindrical gears;

[0066]

[0067] In addition, other parameters of the helical cylindrical gear can be calculated based on the above design parameters of the helical cylindrical gear, as follows:

[0068] End face pressure angle: tanα t =tanα n / cosβ→α t =16.8815°;

[0069] End face modulus: m t =m n / cosβ→m t =1.804;

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

[0071] Tooth root circle extension:

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

[0073] The length of the involute end circle:

[0074] Tool section straight line length: t = (C1-C0)tanα t

[0075] From the calculation results, we can see that C 11 -C 01 =C 12 -C 02 , that is, the lengths of the straight sections of the cutting tool surfaces for the pair of gears are equal.

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

[0077] Step S21, according to the gear processing principle, a first gear processing coordinate system with its origin located on the first gear pitch circle is established, in which the Y1 axis is tangent to the first gear pitch 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 center of the first gear pitch circle, and the Z1 axis, the Y1 axis and the X1 axis are perpendicular to each other;

[0078] Step S22, according to the gear processing principle, a second gear processing coordinate system with its origin located on the second gear pitch circle is established, in which the Y2 axis is tangent to the second gear pitch 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 center of the second gear pitch circle, and the Z2 axis, the Y2 axis and the X2 axis are perpendicular to each other;

[0079] Step S23, obtain the homogeneous coordinate equation of any point M1 on the first tool in the first gear processing coordinate system through 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 processing 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 except that the parameter values ​​are inconsistent.

[0080] In some embodiments, the homogeneous coordinate equation of any point M1 on the first tool in the first gear processing coordinate system specifically includes the coordinate equation of any point M1 on the first tool in the straight line processing segment, the coordinate equation of any point M1 on the first tool in the tool tip fillet segment, and the coordinate equation of any point M1 on the first tool in the tool root fillet segment. The three coordinate equations are specifically as follows:

[0081] The coordinate equation of any point M1 on the first tool in the straight line machining segment:

[0082]

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

[0084]

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

[0086]

[0087] in, represents the tooth surface coordinate position vector; represents the tooth root coordinate position vector; Represents the tooth top coordinate position vector; the superscripts r and 1 of the three parameters on the left represent the right and left sides of the first tool respectively. When r is taken, the ± sign takes the upper part, and when 1 is taken, the ± sign takes the lower part. γ is the motion parameter of any point M1 in the arc part of the root of the first tool section. When the superscripts of the three parameters on the left are r, -π / 2≤γ≤0, and when 1 is taken, 0≤γ≤π / 2; the subscripts mc, gc and dc of the three parameters on the left represent the tooth surface, tooth root and tooth top respectively; x n is the normal phase modification coefficient of the first gear, m n is the normal modulus of the first gear, is the tooth top height coefficient of the first gear, t is the length of the straight part of the first tool slope segment; u is the major-minor axis ratio of the tool root ellipse; ρ is the radius of the first tool tooth top arc; ρ′ is the minor axis radius of the first tool tooth root ellipse arc, β is the helix angle of the first gear, α n is the normal pressure angle of the first gear, α t is the pressure angle of the first gear end face, θ is the tool tip radius of the first tool, Z tRepresents the coordinate component of the coordinate vector in the Z-axis direction; θ m Indicates the maximum value of the tool tip radius of the first tool; t m Indicates the maximum value of the length of the straight portion of the first tool slope segment.

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

[0089] 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 corresponding to any point M1 on the first tool; there must be a point M′2 on the tooth profile curve of the second gear corresponding to any point M2 on the second tool; the coordinate values ​​of any point M1 of the first tool and any point M2 of the second tool are solved by using the two homogeneous coordinate equations obtained in S2;

[0090] Step S32, then by homogeneous coordinate transformation, and according to the coordinate value of the arbitrary point M1 of the first tool and the coordinate value of the arbitrary point M2 of the second tool, respectively solve the coordinate value of the point M'1 on the first gear tooth profile and the coordinate value of the point M'2 on the second gear tooth profile;

[0091] Step S33, looping step S31 to step S32, obtaining 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 deriving the tooth profile curve of the first gear and the tooth profile curve of the second gear respectively 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.

[0092] In some embodiments, the tip of the first tool and the second tool is rounded, and the root of the first tool and the second tool is an epicycloid. For ease of processing, the epicycloid is generally replaced by an elliptical arc.

[0093] In some embodiments, the first tool and the second tool are both standard rack tools, and the standard rack tool includes two machining blades symmetrically arranged on both sides of the standard rack tool, and the machining blades include a root fillet section, a straight processing section and a tip fillet section connected in sequence, the root fillet section and the tip fillet section are respectively used to machine the tooth top curve section and the tooth root curve section of the gear, and the straight processing section is used to machine the involute curve section of the gear, ensuring that the machined first gear tooth top and second gear tooth root, the first gear involute tooth surface and the second gear involute tooth surface, and the first gear tooth root and the second gear tooth top can achieve continuous meshing.

[0094] The above is only a specific embodiment of the present invention, but the protection scope of the present invention is not limited thereto. Any technician familiar with the technical field can easily think of changes or substitutions within the technical scope disclosed by the present invention, which should be covered within the protection scope of the present invention. In addition, the technical solutions between the various embodiments of the present invention can be combined with each other, but it must be based on the ability of ordinary technicians in the field to implement. When the combination of technical solutions is contradictory or cannot be implemented, it should be considered that such a combination of technical solutions does not exist and is not within the protection scope of the present invention. Therefore, the protection scope of the present invention shall be based on the protection scope of the claims.

Claims

1. A high-speed, high-load, low-vibration, multi-meshing gear, comprising a first gear and a second gear, characterized in that: The tooth profile curve of the first gear includes a first tooth top curve segment L3, a first involute curve segment L2 and a first tooth root curve segment L1, wherein the first involute curve segment L2 connects the first tooth top curve segment L3 and the first tooth root curve segment L1; The tooth profile curve of the second gear includes a second tooth top 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 top 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 top curve segment L3 is continuously meshed with the second tooth root curve segment L1′, the first involute curve segment L2 is continuously meshed with the second involute curve segment L2′, and the first tooth root curve segment L1 and the second tooth top curve segment L3′ are continuously meshed.

2. The high-speed, high-load, low-vibration, multi-meshing-area gear according to claim 1, characterized in that: The first tooth top curve segment L3 on the first gear and the second tooth top curve segment L3′ on the second gear are both convex arcs; 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 arcs.

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

4. The high-speed, high-load, low-vibration, multi-meshing-area gear according to claim 1, characterized in that: The two first tooth top curve segments L3 on the first gear are connected by a first tooth top transition curve segment L4 which does not participate in meshing in a tangential connection manner; The two second tooth top curve segments L3 ′ on the second gear are connected tangentially to each other by a second tooth top transition curve segment L4 ′ which does not participate in meshing.

5. A tooth profile design method for a high-speed, high-load, low-vibration, multi-meshing-zone gear according to any one of claims 1 to 4, characterized in that: The steps include: Step S1, selecting design parameters of the first gear and the second gear according to the bearing strength; and designing parameters of a first tool and a second tool for machining the first gear and the second gear respectively according to the design parameters of the first gear and the second gear; Step S2, obtaining a homogeneous coordinate equation of an arbitrary point M1 on the first tool in the first gear machining coordinate system and a homogeneous coordinate equation of an arbitrary point M2 on the second tool in the second gear machining coordinate system through design parameters of the first gear and the second gear and parameters of the first tool and the second tool; Step S3, deriving the tooth profile curve equations of the first gear and the second gear through the coordinate equations of the points on the tooth profile curves of the first tool and the second tool.

6. The tooth profile design method according to claim 5, characterized in that: The design parameters in S1 include at least part or all of the following parameters: Number of teeth, normal module, normal pressure angle, helix angle, displacement coefficient, tooth top height coefficient, top clearance coefficient, tooth root fillet radius.

7. The tooth profile design method according to claim 5, characterized in that: Step S2 specifically includes the following steps: Step S21, according to the gear processing principle, a first gear processing coordinate system with its origin located on the first gear pitch circle is established, in which the Y1 axis is tangent to the first gear pitch 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 center of the first gear pitch circle, and the Z1 axis, the Y1 axis and the X1 axis are perpendicular to each other; Step S22, according to the gear processing principle, a second gear processing coordinate system with its origin located on the second gear pitch circle is established, in which the Y2 axis is tangent to the second gear pitch 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 center of the second gear pitch circle, and the Z2 axis, the Y2 axis and the 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 processing coordinate system through 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 processing 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 except that the parameter values ​​are inconsistent.

8. The tooth profile design method according to claim 5 or 7, characterized in that: The homogeneous coordinate equation of any point M1 on the first tool in the first gear processing coordinate system specifically includes the coordinate equation of any point M1 on the first tool in the straight line processing segment, the coordinate equation of any point M1 on the first tool in the tool tip fillet segment, and the coordinate equation of any point M1 on the first tool in the tool root fillet segment. The three coordinate equations are specifically as follows: The coordinate equation of any point M1 on the first tool in the straight line machining segment: The coordinate equation of any point M1 on the first tool in the tool tip radius section is: The coordinate equation of any point M1 on the first tool in the tool root fillet section is: in, represents the tooth surface coordinate position vector; represents the tooth root coordinate position vector; Represents the tooth top coordinate position vector; 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 taken, the ± sign takes the upper part, and when l is taken, the ± sign takes the lower part. γ is the motion parameter of any point M1 in the arc part of the root of the first tool section. When the superscripts of the three parameters on the left are r, -π / 2≤γ≤0, and when 1 is taken, 0≤γ≤π / 2; the subscripts mc, gc and dc of the three parameters on the left represent the tooth surface, tooth root and tooth top respectively; x n is the normal phase modification coefficient of the first gear, m n is the normal modulus of the first gear, is the tooth top height coefficient of the first gear, t is the length of the straight part of the first tool bevel segment; u is the major-minor axis ratio of the tool root ellipse; ρ is the radius of the first tool tooth top arc; ρ′ is the minor axis radius of the first tool tooth root ellipse arc, β is the helix angle of the first gear, α n is the normal pressure angle of the first gear, α t is the pressure angle of the first gear end face, θ is the tool tip radius of the first tool, Z t Represents the coordinate component of the coordinate vector in the Z-axis direction; θ m Indicates the maximum value of the tool tip radius of the first tool; t m Indicates the maximum value of the length of the straight portion of the first tool slope segment.

9. The tooth profile design method according to claim 5, 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 corresponding to any point M1 on the first tool; there must be a point M′2 on the tooth profile curve of the second gear corresponding to any point M2 on the second tool; the coordinate values ​​of any point M1 of the first tool and any point M2 of the second tool are solved by using the two homogeneous coordinate equations obtained in S2; Step S32, then by homogeneous coordinate transformation, and according to the coordinate value of the arbitrary point M1 of the first tool and the coordinate value of the arbitrary point M2 of the second tool, respectively solve the coordinate value of the point M'1 on the first gear tooth profile and the coordinate value of the point M'2 on the second gear tooth profile; Step S33, looping step S31 to step S32, obtaining 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 deriving the tooth profile curve of the first gear and the tooth profile curve of the second gear respectively 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.

10. The tooth profile design method according to any one of claims 5 to 9, characterized in that: The tip of the first tool and the second tool has a rounded shape, and the root of the first tool and the second tool has an elliptical arc shape.

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