Gear transmission installation registration method

Abstract

The invention belongs to the technical field of gear transmission, and discloses a gear transmission installation registration method, which comprises the steps of obtaining a scene to be registered and design parameters of a corresponding gear pair, the scene to be registered comprising a point contact spiral bevel gear pair registration scene and a point contact straight tooth-face gear transmission registration scene; selecting an intersection point of a pinion end face and a corresponding axis in a to-be-registered scene as an installation reference point, and calculating a theoretically correct meshing point according to design parameters of a gear pair and a preset backlash; and by taking a registration target that the gear pair is engaged at the theoretically correct engagement point and the actual backlash is equal to the preset backlash, adjusting the position of the intersection point of the end face of the bull gear and the corresponding axis on the axis, and completing registration of the scene to be registered. According to the technical scheme, the assembly precision and the service performance of a point contact spiral bevel gear pair and straight tooth-face gear transmission can be effectively improved.

Description

Technical Field

[0001] The invention belongs to the technical field of gear transmission, and in particular relates to a gear transmission installation and alignment method. Background Art

[0002] The side clearance of gear transmission is the gap reserved between non-working tooth surfaces when the gear pair is meshing in order to store lubricating oil, compensate for dimensional changes caused by temperature, elastic-plastic deformation, manufacturing errors and installation errors, and prevent gears from getting stuck. The designed side clearance of point contact gear transmission can only be obtained when the point contact gear transmission is installed to ensure theoretical correctness and the relative sliding speed of the two gear teeth is zero. At this time, the impact and noise of gear meshing are minimal, and the load-bearing capacity and service performance are optimal. When the actual meshing point deviates from the theoretical correct position, the actual side clearance will deviate from the design value, causing the impact and noise to increase, affecting its load-bearing capacity and service performance.

[0003] The contact modes of gear transmission include line contact and point contact. For line contact gear transmission, especially parallel axis contact gear pairs, one of the guarantee conditions for correct meshing transmission is to adjust the center distance during assembly so that the actual side clearance is equal to the designed side clearance, and the two gears are tangent on the pitch circle. For line contact non-parallel axis gear transmission, the correct installation position can be obtained by adjusting the axis angle of the two gears, selecting a position on the gear that is easy to detect, and examining whether the pitch circles are tangent. For point contact gear transmission, although its contact position is a contact ellipse of a certain size, the center of the contact ellipse varies due to the parameters, type, preset transmission error and processing quality of the gear, and will move within a certain range with the change of load, which makes it particularly difficult and important to determine the theoretical correct installation position of the point contact non-parallel axis gear pair. The repair method is generally used for adjustment on site, and there is a lack of unified standards.

[0004] In summary, the side clearance of gear transmission and its correct installation are of great significance to ensure the smooth, reliable and efficient operation of gear transmission. During the design and installation process, it is necessary to fully consider the influence of various factors and take corresponding measures to ensure the performance and life of gear transmission. Summary of the invention

[0005] The purpose of the present invention is to provide a gear transmission installation alignment method to solve the problems existing in the above-mentioned prior art.

[0006] To achieve the above object, the present invention provides a gear transmission installation alignment method, comprising:

[0007] Acquire a scene to be registered and design parameters of a corresponding gear pair, wherein the scene to be registered includes a point contact spiral bevel gear pair registration scene and a point contact spur-face gear transmission registration scene;

[0008] The intersection of the pinion end face and the corresponding axis in the scene to be registered is selected as the installation reference point, and the theoretical correct meshing point is calculated according to the design parameters of the gear pair and the preset backlash;

[0009] The alignment target is that the gear pair is meshed at the theoretically correct meshing point and the actual side clearance is equal to the preset side clearance. The position of the intersection of the end face of the large gear and the corresponding axis on the axis is adjusted to complete the alignment of the scene to be aligned.

[0010] Optionally, the registration process of the point contact spiral bevel gear pair registration scene specifically includes:

[0011] When transmission error is not considered: determine the pitch cone position according to the design parameters of the gear pair, calculate the theoretically correct meshing point position on the pitch cone according to the meshing principle of the spiral bevel gear, adjust the large gear position based on the calculated position and the alignment target, and complete the alignment;

[0012] When considering transmission error: use local conjugate method to design tooth surface, consider the symmetry of transmission error curve, calculate the coordinates of theoretically correct meshing point, adjust the position of large gear based on the calculated coordinates and alignment target, perform error compensation after position adjustment, and complete alignment.

[0013] Optionally, error compensation is performed after the position adjustment is completed, specifically including:

[0014] If there is an axial error, adjust the thickness of the mounting gasket according to the direction of the error;

[0015] If there is a pitch cone angle error, calculate the compensation amount of the installation gasket thickness based on the geometric relationship.

[0016] Optionally, the alignment process of the point contact spur-face gear transmission alignment scenario specifically includes:

[0017] Determine the indexing cylinder position of the spur gear;

[0018] Based on the meshing principle of spur-face gear transmission and the preset backlash calculation theory, the correct position of the meshing point on the dividing cylinder is determined, and the position of the face gear is adjusted in combination with the alignment target to complete the alignment.

[0019] Optionally, the installation reference is determined based on the condition that after the gears are installed, the relative sliding speed of the two gears at the theoretically correct meshing point is zero, and at this time the actual side clearance is equal to the preset side clearance.

[0020] Optionally, the actual backlash calculation process specifically includes:

[0021] Determine the end faces of the pinion and gear as the installation reference;

[0022] Considering the gear blank error and assembly error, establish the plane dimension chain;

[0023] Solve the plane dimension chain to determine the point in the gear pair where the relative speed is zero after actual assembly, analyze the change in the tooth side clearance at this point, and obtain the actual side clearance.

[0024] The technical effects of the present invention are:

[0025] The present invention calculates the theoretical reference point of the point contact gear pair according to the designed side clearance, maps it to the mounting end face of the gear as its mounting reference point, and provides a unified registration method for the assembly of the point contact gear pair. The registration method can also solve the assembly dimension chain to obtain its actual side clearance according to the actual error in the installation of the gear pair, and use it as a basis for analyzing the vibration and noise of the point contact gear pair, thereby further improving the assembly level and service performance of the point contact gear pair. Furthermore, the side clearance can be adjusted to ensure that the gear transmission will not be stuck due to deformation, impact, and excessive noise. This method can effectively improve the assembly accuracy and service performance of the point contact arc bevel gear pair and the spur-face gear transmission. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments will be 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.

[0027] The drawings constituting a part of the present application are used to provide a further understanding of the present application. The illustrative embodiments and descriptions of the present application are used to explain the present application and do not constitute an improper limitation on the present application. In the drawings:

[0028] Figure 1 It is a schematic diagram of the installation and registration of the spiral bevel gear when the transmission error is not considered in the embodiment of the present invention;

[0029] Figure 2 It is a schematic diagram of the installation and registration of the spiral bevel gear when the transmission error is considered in an embodiment of the present invention;

[0030] Figure 3 is a transmission error curve in an embodiment of the present invention;

[0031] Figure 4 is the theoretical correct meshing point on the large wheel axle cross section in the embodiment of the present invention;

[0032] Figure 5 is a transmission error curve in an embodiment of the present invention, wherein: Figure 5 (a) is a transmission error curve without considering symmetry in an embodiment of the present invention, Figure 5 (b) is a transmission error curve considering symmetry in an embodiment of the present invention.

[0033] Figure 6 Schematic diagram of the axial error of the small wheel in the embodiment of the present invention;

[0034] Figure 7 Schematic diagram of the axial error of the large wheel in an embodiment of the present invention;

[0035] Figure 8 Schematic diagram of the small wheel pitch cone angle error in an embodiment of the present invention;

[0036] Fig. 9 Schematic diagram of the large wheel pitch cone angle error in an embodiment of the present invention;

[0037] Fig.10 It is a schematic diagram of installation and registration of a point contact spur-face gear transmission in an embodiment of the present invention;

[0038] Fig.11 It is an implementation flow chart of an embodiment of the present invention. DETAILED DESCRIPTION

[0039] Various exemplary embodiments of the present invention will now be described in detail. This detailed description should not be considered as limiting the present invention, but should be understood as a more detailed description of certain aspects, features, and embodiments of the present invention.

[0040] It should be understood that the terms described in the present invention are only for describing special embodiments and are not intended to limit the present invention. In addition, for the numerical range in the present invention, it should be understood that each intermediate value between the upper and lower limits of the scope is also specifically disclosed. Each smaller range between the intermediate value in any stated value or stated range and any other stated value or intermediate value in the described range is also included in the present invention. The upper and lower limits of these smaller ranges can be independently included or excluded in the scope.

[0041] It will be apparent to those skilled in the art that various modifications and variations may be made to the specific embodiments of the present invention description without departing from the scope or spirit of the present invention. Other embodiments derived from the present invention description will be apparent to those skilled in the art. The present application description and examples are exemplary only.

[0042] The words “include,” “including,” “have,” “contain,” etc. used in this article are open-ended terms, meaning including but not limited to.

[0043] It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of the present application can be combined with each other. The present application will be described in detail below with reference to the accompanying drawings and in combination with the embodiments.

[0044] like Figure 1 - Fig.11 As shown, a gear transmission installation alignment method is provided in this embodiment, including: obtaining a scene to be aligned and design parameters of a corresponding gear pair, wherein the scene to be aligned includes a point contact arc bevel gear pair alignment scene and a point contact spur-face gear transmission alignment scene; selecting the intersection of the small gear end face and the corresponding axis in the scene to be aligned as the installation reference point, and calculating the theoretical correct meshing point according to the design parameters of the gear pair and the preset side clearance; taking the gear pair meshing at the theoretical correct meshing point and the actual side clearance being equal to the preset side clearance as the alignment target, adjusting the position of the intersection of the large gear end face and the corresponding axis on the axis, and completing the alignment of the scene to be aligned.

[0045] This embodiment uses point contact spiral bevel gear pairs and spur-face gear transmission as application cases, calculates the theoretical reference point of the point contact gear pair based on the designed side clearance, maps it to the mounting end face of the gear as its mounting reference point, and provides a unified registration method for the assembly of the point contact gear pair. The registration method can also solve the assembly dimension chain according to the actual error in the installation of the gear pair to obtain its actual side clearance, which is used as the basis for analyzing the vibration and noise of the point contact gear pair, further improving the assembly level and service performance of the point contact gear pair.

[0046] The point contact gear transmission installation alignment method of this embodiment refers to obtaining the designed side clearance D as a guide to make the point contact gear transmission mesh at the theoretical correct meshing point M corresponding to the designed side clearance. Specifically, it refers to the intersection point A of the pinion end face and its axis in the point contact gear transmission. p To locate the reference point, take the theoretical correct meshing point M as the alignment reference point, and adjust the intersection point B between the end face of the large gear and its axis. g The position on its axis ensures that the gear pair meshes at point M, so that the actual side clearance D' is equal to the designed side clearance D.

[0047] The installation datum of point contact gear transmission is determined by the fact that after the gears are installed, the relative sliding speed of the theoretical correct meshing point M when the two gears are meshing for transmission is zero, and the actual side clearance D' at this time is equal to the designed side clearance D.

[0048] There are two feasible alignment methods for point contact spiral bevel gear pairs guided by the designed backlash D: one is that when the transmission error is not considered, the theoretical correct meshing point M1 is on the pitch cone; the other is that when the transmission error is considered, the theoretical correct meshing point M2 is not on the pitch cone.

[0049] When the transmission error is not considered, the theoretical alignment reference point of the spiral bevel gear pair refers to the point where a pair of spiral bevel gears are tangent to each other on the pitch cone and their linear velocities are equal, such as Figure 1 shown.

[0050] When considering transmission error, the theoretical registration reference point of the spiral bevel gear pair refers to the reference point for the repair when the tooth surface is designed in a local conjugate manner. This point should be designed at the midpoint of the tooth surface on the pitch cone, but it has changed after considering the symmetry of the transmission error curve, such as Figure 2 shown.

[0051] The theoretical alignment reference point of the point contact spur gear-face gear transmission is the point on the spur gear indexing cylinder where the spur gear engages with the face gear, such as Fig.10 shown.

[0052] In engineering practice, the installation basis of point contact gear transmission is to select the end face A of the small gear and the end face B of the large gear, such as Figure 2 and Fig.10 As shown in the figure. Due to the error of the gear blank and the assembly error, the alignment reference point of the gear after actual assembly changes by ΔT. Assuming that the errors of the gear are ΔA and ΔB respectively, we can establish Figure 2 and Fig.10 The plane dimension chain shown in the figure can be solved to obtain the point where the relative speed is zero in the gear pair after actual assembly, which is used to solve and analyze the change in the tooth side clearance of the gear pair, and serves as the key parameter basis for the dynamic performance analysis of the gear transmission.

[0053] Specific application examples of this embodiment include:

[0054] Example 1: An example of the alignment method under the backlash guidance of the point contact spiral bevel gear pair design without considering the transmission error, including:

[0055] The designed backlash D is used as a guide to make the point contact gear transmission mesh at the theoretical correct meshing point M1 corresponding to the designed backlash. Specifically, it refers to the intersection point A of the pinion end face and its axis in the point contact gear transmission. p To locate the reference point, take the theoretical correct meshing point M1 as the alignment reference point, and adjust the intersection point B between the end face of the large gear and its axis. g The position on its axis ensures that the gear pair meshes at point M1, so that the actual side clearance D' is equal to the designed side clearance D.

[0056] Depend on Figure 1 The geometric relationship shown, the reference point A on the small wheel p and the reference point B on the large wheel g is the installation distance of the small and large wheels. The installation distance is the distance from the rear end face of the gear to the cone vertex, which is determined during design and is generally rounded up to an integer. δ1 and δ2 are the pitch cone angles of the small and large wheels respectively, and Σ is the shaft intersection angle.

[0057] According to the meshing principle of spiral bevel gears, the coordinate value of the theoretical correct meshing point M1 on the tooth surface can be calculated by formula (1).

[0058]

[0059] Among them, the first two equations in formula (1) are meshing equations, which are used to solve the meshing point trajectory, ψ1 and ψ2 are the rotation angles of the forming wheel, and θ p ,θ g is the cutting parameter of the tool, is the meshing angle of the large and small wheels; the last equation is the pitch cone equation, δ i is the pitch cone angle. The meshing point on the pitch cone can be expressed as the intersection of the meshing point trajectory on the shaft section and the pitch cone.

[0060] The coordinate value of the theoretical correct meshing point M1 in the X1O1Z1 coordinate system can be obtained by formula (2).

[0061]

[0062] Example 2: An example of the alignment method under the backlash guidance of the point contact spiral bevel gear pair design considering the transmission error, including:

[0063] Figure 2 This is a schematic diagram of the installation and registration of spiral bevel gears when transmission error is considered. Reference point A on the small wheel p and the reference point B on the large wheel g is the installation distance of the large and small wheels, which is determined during design and is generally rounded up to an integer. D' is the actual side clearance, D is the designed side clearance, M2″ is the actual meshing point, M2 is the theoretical correct meshing point, and ΔB is the axial installation error of the large wheel.

[0064] Figure 3 It is a schematic diagram of the transmission error curve. Generally, the pinion in the point contact spiral bevel gear pair is repaired after considering the transmission error.

[0065] Formula (3) is the most commonly used transmission error function, and the transmission error is represented by TE (Transmission Error).

[0066]

[0067] In the formula, Z1 and Z2 are the number of teeth of the small wheel and the large wheel respectively. is the initial meshing angle of the small wheel and the large wheel, is the actual meshing angle of the small wheel and the large wheel.

[0068] Figure 4 It is a schematic diagram of the theoretical correct meshing point on the large wheel axle section. O2 is the vertex of the pitch cone, R m is the midpoint cone distance, B is the tooth width, δ2 is the pitch cone angle, δ f2is the root cone angle, Δx and Δy are the changes in the tooth width and tooth height directions respectively. After considering the transmission error, the meshing point where the relative sliding speed is zero on the contact tooth surface of the point contact spiral bevel gear pair changes from the theoretical meshing point M2′ when the error is not considered to M2.

[0069] M2 is the theoretically correct meshing point selected, and its position can be expressed as

[0070]

[0071] According to the rotation and projection relationship, a nonlinear system of equations is constructed:

[0072]

[0073] where x2(ψ2,θ g ),y2(ψ2,θ g )、z2(ψ2,θ g ) are the three components of the gear tooth surface equation, ψ2 is the rotation angle of the forming wheel, θ g is the cutting parameter of the tool.

[0074] The theoretical correct meshing point on the large wheel tooth surface can be obtained by solving the equation group, and the theoretical correct meshing point of the small wheel can be obtained by solving the meshing equation in equation (5). The coordinate value of the theoretical correct meshing point M2 in the X2O2Z2 coordinate system can be calculated by equation (6).

[0075]

[0076] Figure 5 The transmission error curve is a pre-set second-order parabolic transmission error curve to absorb the linear transmission error caused by the installation error, thereby achieving the purpose of reducing noise and installation sensitivity. The symmetrical transmission error curve can avoid premature edge contact under loading conditions.

[0077] If there is an axial error and a pitch angle error between the large and small gears, the backlash will change. Axial errors are compensated in one direction, and angular errors are compensated in two directions. In order to ensure that the actual tooth side is equal to the designed backlash, compensation can be performed in the following way.

[0078] 1) If the pinion increases along the x-axis by ΔA and there is no pitch angle error, the thickness of the mounting washer at the large end of the pinion should be increased by ΔA, such as Figure 6 As shown;

[0079] 2) If the pinion is reduced by ΔA along the x-axis and there is no pitch angle error, the thickness of the mounting washer at the large end of the pinion should be reduced by ΔA, such as Figure 6 As shown;

[0080] 3) If the gear increases by ΔB along the x-axis and there is no pitch cone angle error, the thickness of the mounting washer at the large end of the gear should be increased by ΔB; vice versa, if Figure 7 As shown;

[0081] 4) If the pinion pitch angle error is Δδ p , there is no axial error. According to the geometric relationship shown in Figure (8), the compensation amount of the installation gasket thickness can be calculated by formula (8);

[0082] 5) If the pitch angle error of the large gear is Δδ g , there is no axial error. According to the geometric relationship shown in Figure (9), the compensation amount of the installation gasket thickness can be calculated by formula (10).

[0083] When the small wheel pitch angle increases, Δδ p is negative; when the cone angle decreases, Δδ p is positive. The position of M2″ can be expressed as

[0084]

[0085] Bidirectional compensation is performed for angular error. The compensation amount of the installation gasket thickness can be expressed as

[0086]

[0087] When the large pitch cone angle increases, Δδ g is positive; when the cone angle decreases, Δδ g is negative. The position of M2″ can be expressed as

[0088]

[0089] Bidirectional compensation is performed for angular error. The compensation amount of the installation gasket thickness can be expressed as

[0090]

[0091] Example 3: An example of the alignment method under the backlash guidance of the point contact spur-face gear transmission design, including:

[0092] Figure 5 The figure shows a schematic diagram of a point contact spur gear-face gear transmission. The axis of the spur gear as the driving wheel is the x-axis, and the axis intersects the installation reference plane of the spur gear at A. p Point; the axis of the face gear is the y-axis, and the axis intersects with the mounting reference plane of the face gear at B f point; the two axes intersect at the origin O. The tooth width of the spur gear is B p The outer diameter and inner diameter of the face gear are R of and R if . The thickness of the tooth blank of the face gear is R if, the tooth top height of the face gear is h af .

[0093] The theoretical correct meshing point M1 corresponding to the design backlash of the point contact spur gear-face gear transmission is located on the pitch circle of the spur gear. p To locate the reference point, take the theoretical correct meshing point M1 as the alignment reference point, and adjust the intersection point B between the end face of the face gear and its axis. g The position on its axis ensures that the gear pair meshes at point M1, so that the actual side clearance D' is equal to the designed side clearance D.

[0094] According to the meshing principle of spur gear transmission, the coordinate value of the theoretical correct meshing point M1 in the xOy coordinate system can be calculated by formula (11).

[0095]

[0096] Depend on Fig.10 The geometric relationship shown in the figure can be calculated by formula (12) to obtain the reference point A on the spur gear p Coordinate value in the xOy coordinate system.

[0097]

[0098] Formula (12) actually determines the origin of the xOy coordinate system relative to the reference point A on the spur gear. p The positional relationship of A in the known coordinate system p The position of the reference point B on the face gear can be calculated by formula (13): f Coordinate value in the xOy coordinate system.

[0099]

[0100] In summary, this embodiment proposes an installation alignment method for point contact arc bevel gear pairs and spur-face gear transmissions to ensure the design side clearance as the guide, including: the design side clearance of the point contact arc bevel gear pair and spur-face gear transmission is the side clearance when the point on the tooth surface where the relative sliding speed is zero corresponds to the installation theoretical reference point when the large and small gears are installed; the installation reference point of the point contact arc bevel gear pair and spur-face gear transmission is determined according to the installation theoretical reference point. A plane dimension chain is established when there are errors in the tooth blank or assembly, and the actual side clearance is calculated as a basis for adjusting the installation position. Furthermore, the side clearance can be adjusted to ensure that the gear transmission will not be stuck due to deformation, impact, and excessive noise. This method can effectively improve the assembly accuracy and service performance of point contact arc bevel gear pairs and spur-face gear transmissions.

[0101] The above is only a preferred specific implementation of the present application, but the protection scope of the present application is not limited thereto. Any changes or substitutions that can be easily thought of by a person skilled in the art within the technical scope disclosed in the present application should be included in the protection scope of the present application. Therefore, the protection scope of the present application should be based on the protection scope of the claims.

Claims

1. A gear transmission installation and alignment method, characterized in that: include: Acquire a scene to be registered and design parameters of a corresponding gear pair, wherein the scene to be registered includes a point contact spiral bevel gear pair registration scene and a point contact spur-face gear transmission registration scene; The intersection of the pinion end face and the corresponding axis in the scene to be registered is selected as the installation reference point, and the theoretical correct meshing point is calculated according to the design parameters of the gear pair and the preset backlash; The alignment target is that the gear pair is meshed at the theoretically correct meshing point and the actual side clearance is equal to the preset side clearance. The position of the intersection of the end face of the large gear and the corresponding axis on the axis is adjusted to complete the alignment of the scene to be aligned.

2. A gear transmission installation and alignment method according to claim 1, characterized in that: The registration process of the point contact spiral bevel gear pair registration scene specifically includes: When transmission error is not considered: determine the pitch cone position according to the design parameters of the gear pair, calculate the theoretically correct meshing point position on the pitch cone according to the meshing principle of the spiral bevel gear, adjust the large gear position based on the calculated position and the alignment target, and complete the alignment; When considering transmission error: use local conjugate method to design tooth surface, consider the symmetry of transmission error curve, calculate the coordinates of theoretically correct meshing point, adjust the position of large gear based on the calculated coordinates and alignment target, perform error compensation after position adjustment, and complete alignment.

3. A gear transmission installation and alignment method according to claim 2, characterized in that: After the position adjustment is completed, error compensation is performed, specifically including: If there is an axial error, adjust the thickness of the mounting gasket according to the direction of the error; If there is a pitch cone angle error, calculate the compensation amount of the installation gasket thickness based on the geometric relationship.

4. A gear transmission installation and alignment method according to claim 1, characterized in that: The registration process of the point contact spur-face gear transmission registration scenario specifically includes: Determine the indexing cylinder position of the spur gear; Based on the meshing principle of spur-face gear transmission and the preset backlash calculation theory, the correct position of the meshing point on the dividing cylinder is determined, and the position of the face gear is adjusted in combination with the alignment target to complete the alignment.

5. A gear transmission installation and alignment method according to claim 1, characterized in that: The determination of the installation reference is based on the condition that after the gears are installed, the relative sliding speed of the two gears at the theoretically correct meshing point is zero, and at this time the actual side clearance is equal to the preset side clearance.

6. A gear transmission installation and alignment method according to claim 1, characterized in that: The calculation process of the actual backlash specifically includes: Determine the end faces of the pinion and gear as the installation reference; Considering the gear blank error and assembly error, establish the plane dimension chain; Solve the plane dimension chain to determine the point in the gear pair where the relative speed is zero after actual assembly, analyze the change in the tooth side clearance at this point, and obtain the actual side clearance.

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