A method for analyzing friction torque of rolling bearing seal ring

Abstract

The present invention relates to a bearing analysis method, and in particular to a rolling bearing sealing ring friction torque analysis method, the method comprising the following processes: using a model to simulate the actual posture of the bearing sealing ring; calculating the support force through finite element method; and calculating the bearing sealing ring friction torque through a formula. The bearing sealing ring friction torque finite element and theoretical method of the present invention is mainly used to accurately calculate the size of the sealing ring friction torque under the operating state of the bearing, and can comprehensively consider the influence of the sealing posture during and after the sealing ring assembly process on the friction torque and the sealing performance, and can be applicable to various types of bearings. The method is mainly used to calculate the operating friction torque of the bearing sealing ring, and provide guidance for the sealing ring design.

Description

Technical Field

[0001] The invention relates to a bearing analysis method, in particular to a rolling bearing sealing ring friction torque analysis method. Background Art

[0002] The friction torque of the bearing in the system needs to be comprehensively considered during operation. However, due to the specificity of the seal design and assembly process, the friction torque generated by the seal during operation is difficult to accurately consider.

[0003] However, the friction torque generated by the seal ring cannot be ignored and has a great impact on the entire system. Through in-depth analysis of the seal ring's force performance, its friction torque and behavior under specific assembly features and motion postures can be predicted, its performance indicators can be evaluated, and a theoretical basis can be provided for the structural optimization of the bearing seal ring and the motor torque configuration. Summary of the invention

[0004] In view of the above considerations for the friction torque of the bearing seal ring, the purpose of the present invention is to provide a method for analyzing the friction torque of the rolling bearing seal ring. The method comprehensively utilizes finite element theory and friction mechanics to solve the problem that the friction torque of the bearing seal ring is difficult to accurately analyze.

[0005] In order to achieve the above object, the technical solution adopted by the present invention is: a method for analyzing the friction torque of a rolling bearing seal ring, which is specifically as follows:

[0006] (1) Use the model to simulate the actual posture of the bearing seal ring;

[0007] The above model forms a sealing ring assembly structure by intercepting a part of the bearing area and changes the state of the sealing ring by controlling the inner ring of the bearing;

[0008] (2) Calculate the support force by finite element method;

[0009] (3) Calculate the friction torque of the bearing seal ring through the formula: friction torque of the seal ring = support force of each seal ring × number of seal rings × friction coefficient × friction radius × number of seal rings;

[0010] Furthermore, the friction radius is obtained by extracting the contact position coordinates of the finite element sealing ring and the inner ring and calculating the distance between the contact position coordinates and the inner ring rotation axis.

[0011] Furthermore, the augmented Lagrangian contact algorithm is used to perform static simulation calculations on the bearing. The contact stiffness is iterated at each step during the calculation process, and the results are post-processed after the calculation is completed. The normal pressure at the contact part is extracted by post-processing and substituted into the formula to obtain the friction torque.

[0012] Furthermore, the model of the sealing ring assembly structure includes: an outer ring, an inner ring and a sealing component; the sealing component is located between the inner diameter groove of the outer ring and the outer diameter of the inner ring, and the sealing component includes a sealing ring and a spring ring and a locking ring located on both sides of the sealing ring, the side of the sealing ring close to the end face of the bearing ring is the spring ring, and the side of the sealing ring away from the end face of the bearing ring is the locking ring; the lengths of the spring ring and the locking ring are both shorter than the length of the sealing ring; one end of the spring ring, the sealing ring and the locking ring close to the outer ring is arranged in the inner diameter groove of the outer ring, and the other end of the sealing ring faces the outer diameter of the inner ring; the outer diameter of the inner ring forms an upward sloped step structure from the inner ring end face to the center direction, and the sloped surface is the contact area between the sealing ring and the inner ring;

[0013] Furthermore, the outer ring and the inner ring are simplified local parts of the raceway and the oil groove. Considering that the friction of the sealing ring is only related to the contact part and the vicinity thereof, other irrelevant parts are simplified, that is, the raceway or the oil groove is simplified;

[0014] The above-mentioned partial area of ​​the bearing is an arbitrary arc intercepted from the bearing. Considering the symmetry of the bearing in the circumferential direction, any arc can be intercepted for calculation, and 1 / n can be intercepted for equivalent calculation.

[0015] Furthermore, the calculation method of this scheme takes into account the influence of the interaction between the length, stiffness, friction and supporting force of the spring ring and the sealing ring on the friction torque; for example, when the spring ring remains unchanged, the longer the sealing ring is, the softer the friction part is, the smaller the supporting force between the sealing ring and the inner ring is, and the smaller the friction torque is; when the sealing ring remains unchanged, the longer the spring ring is, the harder the friction part is, the greater the supporting force between the sealing ring and the inner ring is, and the greater the friction torque is.

[0016] Furthermore, considering that the seal ring deforms to produce a seal, in order to consider its installation process, the seal ring assembly structure simulates the operation of the seal ring's actual posture as follows:

[0017] The original state of the model before displacement: the inner diameter end of the sealing ring contacts the outer diameter of the inner ring; the inner ring is axially displaced away from the outer end face of the bearing until the slope surface of the inner ring is just out of contact with the sealing ring; then the inner ring is pushed back to its original position, at which time the sealing ring is deformed to simulate the actual posture of the sealing ring.

[0018] This solution calculates the support force through finite element method, and then calculates the friction torque of the bearing seal ring through a formula. It organically combines the most accurate parts of the finite element method and the formula method. Compared with using finite element calculation or formula calculation for the entire process, it effectively improves the accuracy of the calculation results.

[0019] The beneficial effects of the present invention are:

[0020] The method of combining finite element and theory of bearing sealing ring friction torque of the present invention is mainly used to accurately calculate the size of the sealing ring friction torque under the operating state of the bearing. It can comprehensively consider the influence of the sealing posture during and after the assembly of the sealing ring on the friction torque and sealing performance, and can be applicable to various types of bearings; this method is mainly used to calculate the operating friction torque of the bearing sealing ring to provide guidance for the design of the sealing ring. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Figure 1 This is a model original state diagram of the sealing ring assembly structure in the analysis method of the present invention.

[0022] Figure 2 It is the state diagram of the model displacement process.

[0023] Figure 3 Complete the displacement state diagram for the model.

[0024] Figure 4 This is the state diagram of the sealing ring after posture change (deformation).

[0025] Figure 5 for Figure 4 Stereoscopic diagram.

[0026] Figure 6 It is a schematic diagram showing the normal pressure at the contact point between the sealing ring and the inner ring.

[0027] Figure 7 This is a structural diagram of a rolling bearing according to the present invention.

[0028] Figure 8 The figure is a schematic diagram of the contact position coordinates between the sealing ring and the inner ring of the bearing sealing ring for the friction analysis and calculation of the finite element method of the present invention.

[0029] In the figure, 1, outer ring, 2, inner ring, 3, sealing ring, 4, spring ring, 5, locking ring, 6, contact area between sealing ring and inner ring;

[0030] 100. Inner ring position before displacement, 110. Inner ring position after displacement, 120. Contact position between the sealing ring and the inner ring after deformation, 130. Friction radius, 140. Inner ring rotation axis. DETAILED DESCRIPTION

[0031] In order to make the above-mentioned objects, features and advantages of the present invention more obvious and easy to understand, the specific embodiments of the present invention are described in detail below in conjunction with the accompanying drawings. In the following description, many specific details are set forth to facilitate a full understanding of the present invention. However, the present invention can be implemented in many other ways different from those described herein, and those skilled in the art can make similar improvements without violating the connotation of the present invention, so the present invention is not limited by the specific embodiments disclosed below.

[0032] like Figure 1-8 A method for analyzing the friction torque of a rolling bearing seal ring is shown in FIG. , and is as follows:

[0033] (1) Use the model to simulate the actual posture of the bearing seal ring;

[0034] The above model forms a sealing ring assembly structure by intercepting a part of the bearing area and changes the state of the sealing ring by controlling the inner ring of the bearing;

[0035] (2) Calculate the support force by finite element method;

[0036] (3) Calculate the friction torque of the bearing seal ring through the formula: friction torque of the seal ring = support force of each seal ring × number of seal rings × friction coefficient × friction radius × number of seal rings;

[0037] The friction radius is obtained by extracting the contact position coordinates of the finite element sealing ring and the inner ring and calculating the distance between the contact position coordinates and the inner ring rotation axis.

[0038] The model of the sealing ring assembly structure includes: an outer ring, an inner ring and a sealing component; the sealing component is located between the inner diameter groove of the outer ring and the outer diameter of the inner ring, and the sealing component includes a sealing ring and a spring ring and a locking ring located on both sides of the sealing ring, the side of the sealing ring close to the end face of the bearing ring is the spring ring, and the side of the sealing ring away from the end face of the bearing ring is the locking ring; the lengths of the spring ring and the locking ring are both shorter than the length of the sealing ring; the ends of the spring ring, the sealing ring and the locking ring close to the outer ring are all arranged in the inner diameter groove of the outer ring, and the other end of the sealing ring faces the outer diameter of the inner ring; the outer diameter of the inner ring forms an upward sloped step structure from the end face of the inner ring to the center direction, and the sloped surface is the contact area between the sealing ring and the inner ring;

[0039] Considering that the friction of the sealing ring is only related to its contact part and its vicinity, other irrelevant parts are simplified, that is, the raceway or oil groove is simplified.

[0040] Considering the symmetry of the bearing in the circumferential direction, any arc can be intercepted for calculation, and 1 / n can be intercepted for equivalent calculation.

[0041] The calculation method of this scheme takes into account the influence of the interaction between the length, stiffness, friction and supporting force of the spring ring and the sealing ring on the friction torque; for example, if the spring ring remains unchanged, the longer the sealing ring, the softer the friction part, the smaller the supporting force between the sealing ring and the inner ring, and the smaller the friction torque; if the sealing ring remains unchanged, the longer the spring ring, the harder the friction part, the greater the supporting force between the sealing ring and the inner ring, and the greater the friction torque.

[0042] Considering that the seal ring deforms to produce a seal, in order to consider its installation process, the original state of the model before displacement: the inner diameter end of the seal ring contacts the outer diameter of the inner ring, such as Figure 1 As shown in the figure, the inner ring is axially displaced away from the outer end face of the bearing. The displacement process is shown in the figure. Figure 2, move until the inner ring slope surface just does not touch the sealing ring, such as Figure 3 As shown; then push the inner ring back to its original position, and the sealing ring will deform. Figure 4 , 5 As shown, this simulates the actual posture of the sealing ring.

[0043] The augmented Lagrangian contact algorithm is used to carry out static simulation calculation of the bearing. The contact stiffness is iterated at each step during the calculation process, and the results are post-processed after the calculation is completed.

[0044] The normal pressure at the contact part is extracted by post-processing. The results are as follows Figure 6 Substituting into the formula, we get the friction torque, which is as follows:

[0045] Sealing ring friction torque = each sealing ring support force × number of sealing rings × friction coefficient × friction radius × number of sealing rings;

[0046] Taking bearing YSG105A06E as an example, the finite element boundary conditions are set to control the outer ring to be fixed, the sealing ring to be frictionally assembled with other parts, and the inner ring to be pushed from position 110 to position 100, so that the sealing ring is deformed and contacts the inner ring to form a contact position, and the normal pressure on the contact surface between the inner ring and the sealing ring is extracted, such as Figure 6 , the support force of each sealing ring is calculated to be 0.86233N. The sealing ring is cut into 12 parts in total, the friction coefficient is set to 0.04, the contact position coordinates of the finite element sealing ring and the inner ring are extracted, and the distance from the inner ring rotation axis is calculated to obtain the friction radius. The schematic diagram is shown in Figure 8 , the result is 6.18mm, there are 2 sealing rings, and the above data is substituted into the formula to get the result of 5.116N·mm;

[0047] In the above calculation process, the sealing ring support force and friction radius are calculated by finite element software known in the prior art. Specifically, the motion path and boundary conditions are set by the finite element software, and the software calculates the result of the motion, which needs no detailed description.

[0048] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0049] 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 at least one of the features. In the description of the present invention, the meaning of "plurality" is at least two, such as two, three, etc., unless otherwise clearly and specifically defined.

[0050] In the present invention, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", "fixed" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements, unless otherwise clearly defined. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0051] In the present invention, unless otherwise clearly specified and limited, a first feature being "above" or "below" a second feature may mean that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. Moreover, a first feature being "above", "above" or "above" a second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. A first feature being "below", "below" or "below" a second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.

[0052] It should be noted that when an element is referred to as being "fixed to" or "disposed on" another element, it may be directly on the other element or there may be a central element. When an element is considered to be "connected to" another element, it may be directly connected to the other element or there may be a central element at the same time. The terms "vertical", "horizontal", "upper", "lower", "left", "right" and similar expressions used herein are for illustrative purposes only and are not intended to be the only implementation method.

[0053] The above examples are only the best embodiments of the present invention. Obviously, the present invention is not limited to the above embodiments, and many variations are possible. All variations that can be directly derived or associated with the contents disclosed by a person skilled in the art should be considered as the protection scope of the present invention.

Claims

1. A method for analyzing the friction torque of a rolling bearing seal ring, characterized in that: The details are as follows: (1) Use the model to simulate the actual posture of the bearing seal ring The above model forms a sealing ring assembly structure by intercepting a part of the bearing area and changes the state of the sealing ring by controlling the inner ring of the bearing; (2) Calculate the support force by finite element method (3) The friction torque of the bearing seal ring is calculated by the formula: the friction torque of the seal ring = the support force of each seal ring × the number of cut parts of each seal ring × the friction coefficient × the friction radius × the number of seal rings; The model of the sealing ring assembly structure includes: an outer ring, an inner ring and a sealing component; the sealing component is located between the inner diameter groove of the outer ring and the outer diameter of the inner ring, and the sealing component includes a sealing ring and a spring ring and a locking ring located on both sides of the sealing ring, the side of the sealing ring close to the end face of the bearing ring is the spring ring, and the side of the sealing ring away from the end face of the bearing ring is the locking ring; the lengths of the spring ring and the locking ring are both shorter than the length of the sealing ring; the ends of the spring ring, the sealing ring and the locking ring close to the outer ring are all arranged in the inner diameter groove of the outer ring, and the other end of the sealing ring faces the outer diameter of the inner ring; the outer diameter of the inner ring forms an upward sloped step structure from the end face of the inner ring to the center direction, and the sloped surface is the contact area between the sealing ring and the inner ring; The bearing partial area is to intercept any arc of the bearing, consider the symmetry of the bearing circumferential direction, intercept any arc for calculation, and intercept 1 / n for equivalent calculation; The operation of the seal ring assembly structure to simulate the seal ring's actual posture is as follows: The original state of the model before displacement: the inner diameter end of the sealing ring contacts the outer diameter of the inner ring; the inner ring is axially displaced away from the outer end face of the bearing until the slope surface of the inner ring is just out of contact with the sealing ring; then the inner ring is pushed back to its original position, at which time the sealing ring is deformed to simulate the actual posture of the sealing ring.

2. A rolling bearing seal ring friction torque analysis method according to claim 1, characterized in that: The friction radius is obtained by extracting the contact position coordinates of the finite element sealing ring and the inner ring and calculating the distance between the contact position coordinates and the inner ring rotation axis.

3. A rolling bearing seal ring friction torque analysis method according to claim 1, characterized in that: The outer ring and the inner ring are local parts that simplify the positions of the raceways and oil grooves.

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