High-elastic coupling

Abstract

The invention discloses a high-elastic coupling, and relates to the technical field of couplings. The high-elastic coupling includes: a first hub having a first shaft hole into which a first connecting shaft is inserted; one side of the first radial variable cross-section elastic flange is connected with the first hub; one side of the annular cylinder is connected with the other side of the first radial variable cross-section elastic flange; the second hub is connected with the other side of the annular cylinder, the second hub is provided with a second shaft hole, and a second connecting shaft is inserted into the second shaft hole; when the high-elastic coupler works, the first radial variable cross-section elastic flange can deform after being stressed, and therefore centering error compensation is provided for the first connecting shaft and the second connecting shaft. The first radial variable cross-section elastic flange of the high-elastic coupling can deform after being stressed, so that centering error compensation is provided for the first connecting shaft and the second connecting shaft.

Description

Technical Field

[0001] The invention relates to the technical field of couplings, and in particular to a high-elastic coupling. Background Art

[0002] A coupling is a device used to connect rotating shafts. It can be divided into flexible couplings and rigid couplings according to whether it has the ability to compensate for the alignment error of the two connected shafts.

[0003] When traditional flexible couplings compensate for centering errors, there is usually a gap between the active and driven ends, resulting in low transmission accuracy at both ends. For example, traditional plum blossom or pin couplings are not allowed in some working conditions. For example, machine tools, which are called industrial mother machines, are used to process products. The connection between the motor and the tool spindle must use a zero-backlash coupling to ensure product accuracy. Therefore, in this case, it is not suitable to use existing flexible couplings.

[0004] Therefore, those skilled in the art provide a highly elastic coupling to solve the problems raised in the above background technology. Summary of the invention

[0005] The purpose of the present invention is to solve the shortcomings in the prior art and to propose a high elastic coupling.

[0006] To achieve the above object, the present invention provides the following technical solutions: A highly elastic coupling, comprising: A first hub, wherein the first hub has a first shaft hole, and a first connecting shaft is inserted into the first shaft hole; A first radial variable cross-section elastic flange, one side of which is connected to the first hub; an annular cylinder, one side of which is connected to the other side of the first radial variable-section elastic flange; a second hub, the second hub having a second shaft hole, the second connecting shaft being inserted into the second shaft hole; a second radial variable cross-section elastic flange, through which the annular cylinder is connected to the second hub; wherein when the highly elastic coupling is working, the first radial variable cross-section elastic flange can be deformed after being subjected to force, thereby providing centering error compensation for the first connecting shaft and the second connecting shaft; When the highly elastic coupling is working, the second radial variable-section elastic flange can be deformed after being subjected to force, thereby providing centering error compensation for the first connecting shaft and the second connecting shaft.

[0007] Optionally, the first radial variable cross-section elastic flange comprises: A first annular disk, wherein a first annular disk hole is provided in the middle of the first annular disk, and the first hub is connected to the first annular disk hole; A first annular tube connecting portion is provided at an end of the first annular disk away from the first annular disk hole; wherein the thickness of the end of the first annular disk close to the first annular disk hole gradually decreases toward the first annular tube connecting portion.

[0008] Optionally, the second radial variable cross-section elastic flange includes: A second annular disk, wherein a second annular disk hole is provided in the middle of the second annular disk, and the second hub is connected to the second annular disk hole; The second annular cylinder connecting portion is arranged at an end of the second annular disk away from the second annular disk hole; wherein the thickness of the end of the second annular disk close to the second annular disk hole gradually decreases toward the second annular cylinder connecting portion.

[0009] Optionally, the annular cylinder comprises: a first annular edge, one side of the first annular edge being connected to the first radial variable-section elastic flange; An intermediate connecting portion, one side of which is connected to the first annular edge; A second annular edge, one side of the second annular edge is connected to the other side of the middle connecting portion, and the other side of the second annular edge is connected to the second radial variable-section elastic flange.

[0010] Optionally, a plurality of axial strip holes are provided on the middle connecting portion, and each axial strip hole is arranged along the circumference of the middle connecting portion.

[0011] Optionally, a plurality of curved elastic members are provided on the intermediate connecting portion, and every two curved elastic members are connected by a connecting member.

[0012] Optionally, the stiffness of the first radial variable-section elastic flange is greater than that of the first radial variable-section flange.

[0013] Optionally, the first annular edge, the middle connecting portion and the second annular edge are integrally formed.

[0014] The present application also provides a design method of an annular tube in a highly elastic coupling, which is used for the highly elastic coupling as described above. The design method of the annular tube in the highly elastic coupling includes: Get the maximum torque information of the high elastic coupling; Obtain the allowable stress information of the annular cylinder; Obtaining expected torsion angle information; Get the length information of the annular tube; Get the shear modulus information of the material; Get the number of pre-opened axial strip holes; Establish a model to solve the width and thickness of the annular cylinder; According to the obtained maximum torque information of the highly elastic coupling, the allowable stress information of the annular cylinder, the expected torsion angle information, the length information of the annular cylinder and the shear modulus information of the material, the width information of the annular cylinder and the thickness information of the annular cylinder are obtained through the width and thickness solution model of the annular cylinder.

[0015] Optionally, the width and thickness solution model of the annular cylinder is: ; ; ; ; ; Wherein, T is the maximum torque of the high elastic coupling, G is the shear modulus of the material, L is the length of the annular tube, θ is the desired torsion angle, β is a dimensionless correction factor used to approximate the effect of the through hole groove on the polar moment of inertia, J is the polar moment of inertia of the annular tube, W is the width of the annular tube, t is the thickness of the annular tube, [σ] is the allowable stress of the annular tube, N is the number of pre-opened axial strip holes, L slot The opening length, W, of each pre-opened axial strip hole slot is the slot width of each through hole slot, k is the proportional coefficient, which is used to control the ratio of the total area of ​​the pre-opened axial strip holes to the outer surface area of ​​the annular tube, and α is the proportional coefficient, which represents the proportional relationship between the length of the through hole slot and the length of the annular tube.

[0016] The present invention has the following beneficial effects: The first radial variable-section elastic flange of the highly elastic coupling proposed in the present invention can be deformed after being subjected to force, thereby providing centering error compensation for the first connecting shaft and the second connecting shaft. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 This is a schematic diagram of the overall structure of a highly elastic coupling in the first embodiment of the present invention; Figure 2 It is a schematic diagram of the overall structure of a highly elastic coupling in the first embodiment of the present invention.

[0018] Legend: 1. First wheel hub; 11. First axial hole; 2. First radial variable cross-section elastic flange; 3. Annular cylinder; 4. Second wheel hub; 5. Second radial variable cross-section elastic flange; 21. First annular disk; 211. First annular disk hole; 22. First annular cylinder connecting part; 31. First annular edge; 32. Middle connecting part; 33. Second annular edge; 34. Axial strip hole; 35. Curved elastic member; 36. Connecting member. DETAILED DESCRIPTION

[0019] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments in the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention. In the description of this application, it should be noted that the terms used here are only for describing specific implementations, and are not intended to limit the exemplary implementations according to the present application. For ease of description, the sizes of the various parts shown in the drawings are not drawn according to the actual proportional relationship. The techniques, methods and devices known to ordinary technicians in the relevant fields may not be discussed in detail, but where appropriate, the techniques, methods and devices should be regarded as part of the authorization specification. In all examples shown and discussed here, any specific value should be interpreted as merely exemplary, not as a limitation. Therefore, other examples of the exemplary embodiments may have different values. It should be noted that similar reference numerals and letters represent similar items in the following drawings, so once an item is defined in one drawing, it does not need to be further discussed in subsequent drawings.

[0020] like Figure 1 The high elastic coupling shown comprises a first hub 1, a first radial variable cross-section elastic flange 2, an annular cylinder 3, a second hub 4 and a second radial variable cross-section elastic flange 5, wherein the first hub 1 has a first shaft hole 11, and the first connecting shaft is inserted into the first shaft hole 11; One side of the first radial variable-section elastic flange 2 is connected to the first hub 1; One side of the annular cylinder 3 is connected to the other side of the first radial variable-section elastic flange 2; The second hub 4 has a second axial hole, and the second connecting shaft is inserted into the second axial hole; The annular cylinder 3 is connected to the second hub 4 through the second radial variable cross-section elastic flange 5; wherein, when the high elastic coupling is working, the first radial variable cross-section elastic flange 2 can be deformed after being subjected to force, thereby providing centering error compensation for the first connecting shaft and the second connecting shaft; When the highly elastic coupling is working, the second radial variable-section elastic flange 5 can be deformed after being subjected to force, thereby providing centering error compensation for the first connecting shaft and the second connecting shaft.

[0021] The first radial variable-section elastic flange of the highly elastic coupling proposed in the present invention can be deformed after being subjected to force, thereby providing centering error compensation for the first connecting shaft and the second connecting shaft.

[0022] By providing the first radial variable-section elastic flange and the second radial variable-section elastic flange, better compensation for centering errors can be achieved.

[0023] In this embodiment, the first radial variable cross-section elastic flange includes a first annular disk 21 and a first annular cylinder connecting portion 22, wherein a first annular disk hole is provided in the middle of the first annular disk 21, and the first hub is connected to the first annular disk hole; The first annular tube connection portion 22 is disposed at an end of the first annular disk 21 away from the first annular disk hole; wherein the thickness of the end of the first annular disk close to the first annular disk hole gradually decreases toward the first annular tube connection portion.

[0024] In this embodiment, the second radial variable cross-section elastic flange includes a second annular disk and a second annular tube connecting portion, a second annular disk hole is arranged in the middle of the second annular disk, and the second hub is connected to the second annular disk hole; the second annular tube connecting portion is arranged at an end of the second annular disk away from the second annular disk hole; wherein the thickness of the end of the second annular disk close to the second annular disk hole gradually decreases toward the direction of the second annular tube connecting portion.

[0025] In this embodiment, the annular tube includes a first annular edge 31, an intermediate connecting portion 32 and a second annular edge 33. One side of the first annular edge 31 is connected to the first radial variable cross-section elastic flange; one side of the intermediate connecting portion is connected to the first annular edge 31; One side of the second annular edge 33 is connected to the other side of the middle connecting portion, and the other side of the second annular edge 33 is connected to the second radial variable-section elastic flange 5 .

[0026] See also Figure 1 In this embodiment, a plurality of axial strip holes 34 are provided on the middle connecting portion, and each axial strip hole is arranged along the circumference of the middle connecting portion.

[0027] In this embodiment, the annular tube is evenly provided with a plurality of axial strip holes, so that the annular tube is more likely to deform in the circumferential direction, so as to achieve the function of buffering and shock absorption.

[0028] See also Figure 2In this embodiment, a plurality of curved elastic members 35 are provided on the intermediate connecting portion, and every two curved elastic members are connected by a connecting member 36 .

[0029] By providing a curved elastic member, a better buffering effect can be achieved.

[0030] In this embodiment, the first radial variable cross-section elastic flange 2 has a greater rigidity than the second radial variable cross-section flange.

[0031] In this way, when torque is transmitted, the rated torque that can be transmitted by the first radial variable-section elastic flange 2 is greater than the rated torque that can be transmitted by the second radial variable-section elastic flange, and the error compensation capability of the second radial variable-section flange is greater than that of the first radial variable-section flange.

[0032] In this way, in actual work, you can choose which side to connect to the more important host according to the importance of the host. In this way, when abnormal working conditions occur (for example, overload or impact), the second radial variable cross-section flange can be broken preferentially at the weakest point to ensure the safety of the host. At the same time, when replacing spare parts, you only need to replace the second radial variable cross-section flange.

[0033] In this embodiment, the first annular edge, the middle connecting portion and the second annular edge are integrally formed.

[0034] In this embodiment, one axial side surface of the first radial variable-section flange is a plane, and the other axial side surface is a curved surface; One axial side surface of the second radial variable-section flange is a plane, and the other axial side surface is a curved surface.

[0035] In this embodiment, the first annular edge, the middle connecting portion and the second annular edge are integrally formed. It is understandable that in other embodiments, the middle connecting portion can also be connected to the first annular edge and the second annular edge in a detachable manner.

[0036] In this embodiment, the thickness of the second annular disk at any position r is obtained by the following formula:

[0037] in, : The thickness of the second annular disk at radius r; r: radius of the second annular disk; : The thickness of the second annular disk at its thinnest point; : The radius of the second annular disk at its thinnest point; c: profile index of the second annular disk; n: centrifugal force coefficient.

[0038] In this embodiment, the value of the profile index is between 0, 1, and 2. Specifically, if the curvature of both sides at any position r is 0, then the value is 0; if the curvature of one side is not 0, then the value is 1; if the curvature of both sides is not 0, then the value is 2.

[0039] In this embodiment, the centrifugal force coefficient is generally taken as 0.5~1.5. This type of coupling is generally used in high-speed, heavy-load and precision equipment, so the dynamic balance requirements of the product are very high. According to actual calculation and analysis, the influence of centrifugal force on flange thickness can be increased by 0.5~1.5 on the basic thickness, which can eliminate the influence of centrifugal force generated by residual imbalance on coupling strength.

[0040] Specifically, in this embodiment, when the working environment of the coupling is below 3000 revolutions, the correction coefficient is 0.15; when the working environment of the coupling is 3000-10000 revolutions, the correction coefficient is 0.16; when the working environment of the coupling is 10000-25000 revolutions, the correction coefficient is 0.18; when the working environment of the coupling is 25000-50000 revolutions, the correction coefficient is 0.2; when the working environment of the coupling is 50000-100000 revolutions, the correction coefficient is 0.22; when the working environment of the coupling is above 100000, the correction coefficient is 0.25.

[0041] By setting the centrifugal force coefficient, the bending and torsion combined characteristics of the product can be improved, making the toughness and rigidity more reasonably matched.

[0042] It is understandable that specific values ​​can be set as needed.

[0043] The present application also provides a design method of an annular tube in a highly elastic coupling, which is used for the highly elastic coupling as described above. The design method of the annular tube in the highly elastic coupling includes: Get the maximum torque information of the high elastic coupling; Obtain the allowable stress information of the annular cylinder; Obtaining expected torsion angle information; Get the length information of the annular tube; Get the shear modulus information of the material; Get the number of pre-opened axial strip holes; Establish a model to solve the width and thickness of the annular cylinder; According to the obtained maximum torque information of the highly elastic coupling, the allowable stress information of the annular cylinder, the expected torsion angle information, the length information of the annular cylinder and the shear modulus information of the material, the width information of the annular cylinder and the thickness information of the annular cylinder are obtained through the width and thickness solution model of the annular cylinder.

[0044] In this embodiment, the width and thickness solution model of the annular cylinder is: ; ; ; ; ; Wherein, T is the maximum torque of the high elastic coupling, G is the shear modulus of the material, L is the length of the annular tube, θ is the desired torsion angle, β is a dimensionless correction factor used to approximate the effect of the through hole groove on the polar moment of inertia, J is the polar moment of inertia of the annular tube, is the width of the annular tube, t is the thickness of the annular tube, [σ] is the allowable stress of the annular tube, N is the number of pre-opened axial strip holes, L slot The opening length for each number of pre-opened axial strip holes, is the slot width of each through hole slot, k is the proportional coefficient, which is used to control the ratio of the total area of ​​the pre-opened axial strip holes to the outer surface area of ​​the annular cylinder, and α is the proportional coefficient, which represents the proportional relationship between the length of the through hole slot and the length of the annular cylinder.

[0045] The present application is further described in detail below by way of examples. It should be understood that the examples do not constitute any limitation to the present application.

[0046] Assume that the maximum torque that the annular cylinder needs to withstand is , assuming that the allowable stress of the material is [σ] = 100MPa, assuming that the required torsion angle is a known condition, θ = 0.1rad, assuming that the length of the annular tube is L = 1m, assuming that the material is steel, then the shear modulus G ≈ 80GPa, assuming that the wall thickness t of the annular tube is equal to the width The proportional relationship is , assuming that the number of through-hole grooves N = 10, assuming α = 0.1 (assuming that the length of the through-hole groove is 10% of the length of the annular tube), assuming k = 0.5 (assuming that the total area of ​​the through-hole grooves occupies less than half of the outer surface area of ​​the annular tube), and the correction coefficient β = 0.8.

[0047] The specific technical steps for calculation through the above-mentioned simultaneous equations are as follows: ; ; ; ; The torque balance equation is simplified to: ; The allowable stress condition is simplified to: ; The geometric constraints of the through hole slot are simplified to: ; Solving this system of equations using numerical methods (such as iterative methods or optimization algorithms) eventually gives us the following values: ; ; ; .

[0048] In this embodiment, the correction coefficient β can be obtained by an experimental method, for example: Sample preparation: Annular cylinder samples with different numbers and sizes of through-hole slots were prepared.

[0049] Testing Torsional Stiffness: The torsional stiffness of these samples was tested experimentally.

[0050] Calculate the polar moment of inertia: Based on the test results and the torque balance equation, the actual polar moment of inertia can be deduced.

[0051] Determine the correction factor: The actual polar moment of inertia is compared with the theoretical polar moment of inertia without the through-hole slot to determine the correction factor β.

[0052] Finally, it should be noted that the above is only a preferred embodiment of the present invention and is not intended to limit the present invention. Although the present invention has been described in detail with reference to the aforementioned embodiments, it is still possible for those skilled in the art to modify the technical solutions described in the aforementioned embodiments or to make equivalent substitutions for some of the technical features therein. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present invention should be included in the protection scope of the present invention.

Claims

1. A highly elastic coupling, characterized in that: The highly elastic coupling comprises: A first wheel hub (1), the first wheel hub (1) having a first shaft hole (11), and a first connecting shaft inserted into the first shaft hole (11); a first radial variable cross-section elastic flange (2), one side of the first radial variable cross-section elastic flange (2) being connected to the first wheel hub (1); An annular cylinder (3), one side of the annular cylinder (3) being connected to the other side of the first radial variable-section elastic flange (2); A second wheel hub (4), the second wheel hub (4) having a second shaft hole, and a second connecting shaft inserted into the second shaft hole; a second radial variable cross-section elastic flange (5), the annular cylinder (3) being connected to the second hub (4) via the second radial variable cross-section elastic flange (5); wherein when the high elastic coupling is working, the first radial variable cross-section elastic flange (2) is deformable after being subjected to force, thereby providing centering error compensation for the first connecting shaft and the second connecting shaft; When the highly elastic coupling is working, the second radial variable cross-section elastic flange (5) can be deformed after being subjected to force, thereby providing centering error compensation for the first connecting shaft and the second connecting shaft.

2. The highly elastic coupling according to claim 1, characterized in that: The first radial variable cross-section elastic flange (2) comprises: a first annular disk (21), wherein a first annular disk hole (211) is provided in the middle of the first annular disk (21), and the first wheel hub (1) is connected to the first annular disk hole (211); A first annular cylinder connecting portion (22), the first annular cylinder connecting portion (22) being arranged at an end of the first annular disk (21) away from the first annular disk hole (211); wherein the thickness of an end of the first annular disk (21) close to the first annular disk hole (211) gradually decreases towards the first annular cylinder connecting portion (22).

3. The highly elastic coupling according to claim 2, characterized in that: The second radial variable cross-section elastic flange (5) comprises: A second annular disk, wherein a second annular disk hole is provided in the middle of the second annular disk, and the second wheel hub (4) is connected to the second annular disk hole; The second annular cylinder connecting portion is arranged at an end of the second annular disk away from the second annular disk hole; wherein the thickness of the end of the second annular disk close to the second annular disk hole gradually decreases toward the second annular cylinder connecting portion.

4. The highly elastic coupling according to any one of claims 2 to 3, characterized in that: The annular cylinder (3) comprises: a first annular edge (31), one side of the first annular edge (31) being connected to the first radial variable-section elastic flange (2); An intermediate connecting portion (32), one side of the intermediate connecting portion (32) being connected to the first annular edge (31); A second annular edge (33), one side of the second annular edge (33) is connected to the other side of the middle connecting portion (32), and the other side of the second annular edge (33) is connected to the second radial variable cross-section elastic flange (5).

5. The highly elastic coupling according to claim 4, characterized in that: A plurality of axial strip holes (34) are provided on the middle connecting portion, and each axial strip hole (34) is arranged along the circumference of the middle connecting portion (32).

6. The highly elastic coupling according to claim 5, characterized in that: A plurality of curved elastic members (35) are provided on the intermediate connecting portion, and every two curved elastic members (35) are connected via a connecting member (36).

7. The highly elastic coupling according to claim 5, characterized in that: The first annular edge (31), the middle connecting portion (32) and the second annular edge (33) are integrally formed.

8. A design method for an annular cylinder in a highly elastic coupling, used for the highly elastic coupling as claimed in any one of claims 1 to 5, characterized in that: The design method of the annular cylinder in the highly elastic coupling includes: Get the maximum torque information of the high elastic coupling; Obtaining allowable stress information of the annular cylinder (3); Obtaining expected torsion angle information; Obtaining length information of the annular cylinder (3); Get the shear modulus information of the material; Get the number of pre-opened axial strip holes; Establishing a width and thickness solution model of the annular cylinder (3); Based on the obtained maximum torque information of the highly elastic coupling, the allowable stress information of the annular cylinder (3), the expected torsion angle information, the length information of the annular cylinder (3) and the shear modulus information of the material, the width information of the annular cylinder (3) and the thickness information of the annular cylinder (3) are obtained through a width and thickness solution model of the annular cylinder (3).

9. The design method of the annular cylinder in the high elastic coupling according to claim 8, characterized in that: The width and thickness solution model of the annular cylinder (3) is: ； ； ； ； ; Wherein, T is the maximum torque of the high elastic coupling, G is the shear modulus of the material, L is the length of the annular tube, θ is the desired torsion angle, β is a dimensionless correction factor used to approximate the effect of the through hole groove on the polar moment of inertia, J is the polar moment of inertia of the annular tube, W is the width of the annular tube, t is the thickness of the annular tube, [σ] is the allowable stress of the annular tube, N is the number of pre-opened axial strip holes, L slot The opening length, W, of each pre-opened axial strip hole slot is the slot width of each through hole slot, k is the proportional coefficient, which is used to control the ratio of the total area of ​​the pre-opened axial strip holes to the outer surface area of ​​the annular cylinder, and α is the proportional coefficient, which represents the proportional relationship between the length of the through hole slot and the length of the annular cylinder.

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