Novel single-row self-aligning roller bearing

Abstract

The utility model provides a novel single-row self-aligning roller bearing. The self-aligning roller bearing comprises an inner ring, an outer ring, a retainer and a plurality of drum-shaped rollers, wherein the retainer and the drum-shaped rollers are arranged between the inner ring and the outer ring, and the retainer is an inner ring guide type retainer or an outer ring guide type retainer or a composite guide retainer for simultaneously guiding the inner ring and the outer ring; the inner ring surfaces of the two side rings of the inner ring guide retainer are cylindrical surfaces, protrude towards the axial lead direction of the side rings, and form inner guide surfaces matched with the inner ring flanges; the outer ring surfaces of two side rings of the outer ring guide retainer are spherical surfaces, the spherical surfaces of the two side rings are located on the same spherical surface, the sphere center of the spherical surfaces of the two side rings is the same as the sphere center of the outer ring raceway, and the spherical surfaces of the two side rings form an outer guide surface matched with the outer ring raceway. According to the utility model, the limit rotating speed and the impact load resistance of the bearing are greatly improved, the service life of the bearing is prolonged, and the application scene of the bearing is greatly expanded.

Description

Technical Field

[0001] This utility model relates to the field of bearings, specifically a novel single-row self-aligning roller bearing. Background Technology

[0002] Rolling bearings generally consist of four parts: an outer ring, an inner ring, rolling elements, and a cage. Based on the shape of the rolling elements, they are generally divided into two types: ball bearings and roller bearings. Roller bearings can be further subdivided into cylindrical roller bearings, tapered roller bearings, and spherical roller bearings (where the generatrix of the roller's outer diameter surface is an arc). Spherical roller bearings, because their outer ring raceway (inner surface of the outer ring) is spherical with its center coinciding with the center of the entire bearing, allow the inner ring to rotate in any direction relative to the outer ring, using the bearing's center point as a reference. This self-aligning function is why spherical roller bearings are also called self-aligning roller bearings. The spherical rollers inside a self-aligning roller bearing are arranged sequentially between the outer and inner ring raceways, with their axes parallel to the bearing's axis. Based on the number of rows of rolling elements, self-aligning roller bearings are generally divided into double-row self-aligning roller bearings and single-row self-aligning roller bearings. A single-row self-aligning roller bearing is a bearing with only one row of drum-shaped rollers inside. This utility model mainly relates to a single-row self-aligning roller bearing.

[0003] The bearing cage in a bearing is used to evenly isolate the rolling elements and maintain their correct posture and position. It is a crucial component for ensuring the normal operation of the bearing. During operation, the bearing needs to guide the cage to ensure its relative stability as it rotates along the bearing axis, preventing excessive vibration and positional deviation. There are generally two types of cage guidance: one is rolling element guidance, characterized by large radial clearances between the inner and outer diameters of the cage and the inner and outer rings of the bearing. During operation, they do not contact each other; instead, the rolling elements guide the cage's trajectory. The other type is ring guidance. The structure is further divided into: (1) outer ring guide (abbreviated as outer guide), the characteristic of this structure is that the gap between the outer diameter of the cage and the inner diameter of the outer ring is very small. During operation, the two are in contact with each other, and the outer ring guides the running trajectory of the cage. These two circumferential surfaces with very small gaps are called the outer guide surface of the cage and the outer ring guide surface, respectively; (2) inner ring guide (abbreviated as inner guide), the characteristic of this structure is that the gap between the inner diameter of the cage and the outer diameter of the inner ring is very small. During operation, the two are in contact with each other, and the inner ring guides the running trajectory of the cage. These two circumferential surfaces with very small gaps are called the inner guide surface of the cage and the inner ring guide surface, respectively.

[0004] In bearing applications, matching the appropriate guiding method according to different working conditions is crucial to maximizing bearing performance. However, in the current bearing industry, due to factors such as different design concepts and varying processing capabilities, the design structures of cage guiding methods vary greatly. Even within the same type of bearing and the same type of guiding method, there are various different design structures, and some types of bearings even lack corresponding guiding method designs. A typical example is the single-row self-aligning roller bearing. Because the rollers of a single-row self-aligning roller bearing are single-row drum-shaped rollers, the structure is quite special. For ease of processing and assembly, the cage guiding method of single-row self-aligning roller bearings in the current bearing industry is all rolling element guiding, and there are no cases of inner and outer ring guiding.

[0005] Roller element guidance, due to its advantages in ease of machining and lubrication, is widely used in ordinary, low-speed bearing applications. However, in high-speed, high-vibration environments, the high-speed rotation and intense vibration of the bearing cause both the rolling elements and the cage to generate high-frequency vibrations. These high-frequency vibrations can transmit and superimpose, resulting in even more intense vibrations. This intense vibration can lead to increased bearing temperature and premature damage to the rolling elements and cage. If ring guidance is used, the cage is constrained by the rings' running trajectory, thus transmitting the high-frequency vibrations from the rolling elements and the cage itself to the bearing rings. The bearing rings absorb these high-frequency vibrations, preventing vibration superposition and maintaining the working stability of the rolling elements and cage. This significantly reduces damage to the bearing. External guidance, in particular, offers superior performance in such high-speed, high-vibration conditions.

[0006] The lack of inner and outer ring guidance design for single-row self-aligning roller bearings undoubtedly limits their application range. As industrial applications increasingly demand high-speed, high-load, and strong-vibration conditions, it is essential to design a cage with a suitable ring guidance structure for single-row self-aligning roller bearings.

[0007] Patent announcements CN206246535U and CN201606409U each disclose a cage for an externally guided single-row cylindrical roller bearing. These patents are all designed for single-row cylindrical roller bearings. Although single-row cylindrical roller bearings and single-row self-aligning roller bearings appear somewhat similar, their structures and operating conditions differ significantly. First, the raceways and rolling element surfaces of a single-row cylindrical roller bearing are cylindrical, while those of a single-row self-aligning roller bearing are spherical. Second, in a single-row cylindrical roller bearing, the raceways rotate along the bearing axis, and the inner and outer rings cannot rotate relative to each other. In contrast, with a self-aligning roller bearing, in addition to the raceways rotating along the bearing axis, the inner and outer rings can rotate relative to each other around the bearing's center point. Similarly, the outer guide cages of single-row cylindrical roller bearings and single-row self-aligning roller bearings may look somewhat similar, but they are not interchangeable. This is because the guide surface of the outer guide cage of a single-row cylindrical roller bearing is cylindrical. This cylindrical guide surface cannot match the spherical surface of the outer ring raceway of a self-aligning roller bearing, and therefore cannot play a guiding role. Thus, it cannot be used on single-row self-aligning roller bearings. Utility Model Content

[0008] To address the shortcomings of existing technologies, this invention provides a novel single-row self-aligning roller bearing. The bearing employs a ring-guided cage structure, which serves both external and internal guiding functions, significantly improving the limiting speed and impact load resistance of the single-row self-aligning roller bearing. This greatly expands the application range of the single-row self-aligning roller bearing, especially in high-speed vibration applications, where its advantages are even more pronounced.

[0009] To solve the above-mentioned technical problems, this utility model provides a novel single-row self-aligning roller bearing, including an outer ring, an inner ring, a cage disposed between the outer ring and the inner ring, and multiple drum-shaped rollers. The outer ring has an inner spherical raceway on its inner circumferential surface, and the inner ring has an inner spherical raceway corresponding to and cooperating with the inner spherical raceway, and annular inner ring flanges on both sides. The inner spherical raceway and the inner spherical raceway match the outer diameter surface of the drum-shaped rollers. The cage is an annular frame with pockets. A crossbeam is provided between two adjacent pockets, and side rings are provided on both axial sides of the pockets. Multiple drum-shaped rollers are respectively installed in corresponding pockets and are located between the outer ring raceway and the inner ring raceway. The cage is characterized by being an inner ring-guided cage, an outer ring-guided cage, or a composite guided cage that guides both the inner and outer rings simultaneously.

[0010] When the retainer is an inner ring guide retainer, the inner ring surfaces of the two side rings of the retainer are cylindrical surfaces, and the inner ring surfaces of the two side rings protrude toward the axis of the side ring, forming an inner guide surface that cooperates with the inner ring flange.

[0011] When the cage is an outer ring guided cage, the outer ring surfaces of the two side rings of the cage are spherical surfaces, and the two spherical surfaces of the two side rings are on the same spherical surface. The center of the sphere of the two side rings is the same as the center of the sphere of the outer ring raceway. The spherical surfaces of the two side rings form an outer guide surface that cooperates with the outer ring raceway. Cutting surfaces are provided on the outer guide surfaces of the two side rings of the cage. Two cutting surfaces are symmetrically provided on each side ring. The positions of the cutting surfaces on the two side rings correspond to each other. The four cutting surfaces are on the same cylindrical surface, and the diameter of the cylindrical profile section formed by the extension of the four cutting surfaces is smaller than the diameter of the end face of the outer ring raceway.

[0012] When the cage is a composite guide cage with simultaneous inner and outer ring guidance, the inner ring surfaces of the two side rings of the cage are cylindrical surfaces, and the inner ring surfaces of the two side rings protrude towards the axis of the side ring, forming an inner guide surface that cooperates with the inner ring flange; the outer ring surfaces of the two side rings of the cage are spherical surfaces, and the two spherical surfaces of the two side rings are on the same spherical surface, the center of the two spherical surfaces of the two side rings is the same as the center of the outer ring raceway, and the spherical surfaces of the two side rings form an outer guide surface that cooperates with the outer ring raceway; and cutting surfaces are respectively provided on the outer guide surfaces of the two side rings of the cage, with two cutting surfaces symmetrically provided on each side ring, the positions of the cutting surfaces on the two side rings corresponding to each other, the four cutting surfaces on the same cylindrical surface, and the diameter of the cylindrical profile section formed by the extension of the four cutting surfaces is smaller than the diameter of the end face of the outer ring raceway.

[0013] The preferred technical solution of this utility model is as follows: On the opposite sides of the two rings, and symmetrically provided at the position corresponding to the center of each pocket, the axis of the boss coincides with the axis of the drum-shaped roller; after the drum-shaped roller is installed into the pocket, an assembly gap is formed between the two end faces of the drum-shaped roller and the inner end face of the pocket.

[0014] The preferred technical solution of this utility model is as follows: when the retainer is an inner ring guide retainer, multiple inner ring grooves are evenly distributed on the inner ring surface of the two side rings; when the retainer is an outer ring guide retainer, multiple outer ring grooves are evenly distributed on the outer ring surface of the two side rings; when the retainer is a composite guide retainer that guides both inner and outer rings simultaneously, multiple inner ring grooves are evenly distributed on the inner ring surface of the two side rings, and multiple outer ring grooves are evenly distributed on the outer ring surface of the two side rings.

[0015] The preferred technical solution of this utility model is as follows: When the cage is an outer ring guided cage or a composite guided cage with both inner and outer rings guided simultaneously, the cylindrical surface formed by the extended contours of the four cut surfaces on the outer guide surface has a cross-sectional diameter slightly smaller than the diameter of the outer ring raceway end face. The difference is between 0.001 and 0.02 times the diameter of the outer ring raceway end face. Because the outer diameter surfaces of the two side rings of the cage are spherical, the inner diameter of the side rings must be larger than the outer diameter. Since the diameter of the outer ring raceway end face is basically the same as the diameter of the outer side ring of the cage, the inner diameter of the cage side ring is larger than the diameter of the outer ring raceway end face, which prevents the cage from being installed in the outer ring raceway. To address this issue, this invention involves cutting away portions of the cage's outer diameter surface at symmetrical locations along a direction perpendicular to the cage's radial direction, forming four cut surfaces. The combined profile of these four cut surfaces is equivalent to a cylindrical surface with a diameter slightly smaller than the diameter of the outer raceway end face. The difference between the diameter of the outer raceway end face and this profile is set between 0.001 and 0.02 times the diameter of the outer raceway end face. This allows the cage to be inserted into the outer raceway in a position perpendicular to the outer raceway end face. By cutting the cage in this manner, it is possible to ensure that the cage can be installed into the outer raceway while minimizing the amount of reduction on the cage's side rings, thereby minimizing the impact on the cage's strength caused by the cutting.

[0016] The preferred technical solution of this utility model is as follows: the outer ring is a short cylindrical shape, its outer ring surface is cylindrical, and its two end faces are flat. The inner spherical outer ring raceway on its inner surface is an inner spherical ring with the geometric center of the outer ring as its center. The inner ring is also a short cylindrical shape, its inner ring surface is cylindrical, and its two end faces are flat. The inner spherical inner ring raceway on the outer surface of the inner ring is an inwardly concave ring with the same generatrix curvature as the outer ring raceway. Two inner ring flanges are symmetrically provided on both sides of the inner ring raceway.

[0017] A further technical solution of this utility model: the drum-shaped roller is a cylindrical object with an arc-shaped outer diameter surface and two flat ends.

[0018] The preferred technical solution of this utility model is as follows: the retainer is a cylindrical structure composed of two side rings and multiple crossbeams connected between the side rings, and a pocket is formed between two adjacent crossbeams to accommodate drum-shaped rollers.

[0019] The preferred technical solution of this utility model is as follows: the area of ​​the boss end face is 0.05 to 0.5 times the area of ​​the drum-shaped roller end face, and the protrusion height of the boss is 0.005 to 0.05 times the radius of the rotation circle of the roller axis of the drum-shaped roller.

[0020] There are two advantages to setting up such a boss. First, because self-aligning roller bearings generally allow for an angular deflection of up to 3°, meaning there will be an axial offset distance between the rolling elements and the outer ring raceway within a 3° range, the boss height is determined by using the radius of the roller axis's revolution circle as a reference. This height-restricted boss allows for a certain clearance between the roller end face and the inner surface of the cage side ring, preventing the running trajectory of the cage's outer guide surface on the outer ring raceway from intersecting with the running trajectory of the rollers on the outer ring raceway when the inner and outer rings rotate under unstable slight deflection. This ensures that both the rolling elements and the cage maintain good working conditions. Second, setting up a boss reduces the contact area between the roller end face and the cage side ring, significantly reducing the heat generated during friction between the two surfaces, thus reducing the heat source during bearing operation.

[0021] The preferred technical solution of this utility model is as follows: the number of inner ring grooves and outer ring grooves is four or more each; the total length of the opening arc of all inner ring grooves is 20% to 65% of the circumference of the inner diameter of the side ring, and the depth of the inner ring groove does not exceed the circumference of the axis of rotation of the drum-shaped roller; the total length of the opening arc of the outer ring groove is 20% to 65% of the circumference of the outer diameter of the side ring, and the depth of the outer ring groove does not exceed the circumference of the axis of rotation of the roller. The inner and outer ring grooves of the cage facilitate the flow of lubricant, thereby reducing friction on the guide surface. The number of these grooves should be moderate; too many will affect the strength and wear resistance of the cage, while too few will not achieve the purpose of friction reduction. This utility model limits the number of grooves to four or more, the total length of the opening arc of all grooves is between 20% and 65% of the circumference of the guide surface of the side ring of the cage, and the depth of the groove does not exceed the circumference of the axis of rotation of the roller.

[0022] The preferred technical solution of this utility model is as follows: When the cage is guided on the outer ring, the outer diameter surfaces of the two side rings serve as the outer guiding surfaces of the cage. If the generatrices of the surfaces of the two side rings are extended towards each other, they will form a spherical outer guiding surface profile when combined. The outer ring raceway area corresponding to the outer guiding surface of the cage is the guiding surface of the outer ring. The center of the spherical outer guiding surface of the cage is the same as the center of the outer ring raceway, and an outer guiding gap is provided between the spherical outer guiding surface of the cage and the guiding surface formed by the outer ring raceway. The value of the outer guiding gap is 1.2 to 12 times the upper limit of the radial clearance design of the bearing. Designing the outer guiding surface of the cage as a spherical surface with the same curvature as the outer ring raceway allows the two guiding surfaces to fit together well. This design ensures smoother operation of the contact surfaces, minimizing wear. The spherical guide surface allows for both radial and axial positioning, a capability not found in other cages. This structure significantly increases the stability of the cage during operation, greatly benefiting bearing performance. When the cage guides the inner ring, the inner ring surface of the side rings is cylindrical, and the inner ring surfaces of the two side rings form the inner guide surface of the cage. The outer diameter of the two inner ring flanges serves as the inner ring guide surface. The inner guide surface of the cage is larger than the inner ring guide surface, forming an inner guide gap. The value of this inner guide gap ranges from 1 to 10 times the upper limit of the bearing's radial clearance design.

[0023] In this invention, the radial clearance of the bearing is a proprietary technical parameter representing the relative radial displacement between the inner and outer rings. Using the radial clearance as a reference for determining the bearing guide surface clearance is both informative and practical. However, the specific value of the clearance between the guide surfaces requires consideration of various factors, primarily the bearing operating temperature, the ratio of the thermal expansion coefficients of the cage material to the ring and rolling element materials, and machining accuracy deviations. This is because there are many materials used to manufacture cages, including non-ferrous metals and non-metallic materials. The coefficient of thermal expansion of metallic materials differs greatly from that of steel used in bearing rings and rolling elements. In particular, the coefficient of thermal expansion of some non-metallic materials is several times greater than that of steel. Therefore, this invention sets the range of the outer guide surface clearance to be within 1.2 to 12 times the upper limit of the bearing's radial clearance design. The inner guide surface clearance also faces this problem, but its working condition is slightly different from that of the outer guide. The variation of its guide surface clearance during operation is smaller than that of the outer guide. Therefore, this invention sets the range of the inner guide surface clearance to be within 1 to 10 times the upper limit of the bearing's radial clearance design.

[0024] The composite guide cage with inner and outer rings in this invention not only extends the service life of the cage but also expands the application scenarios of the bearing. For example, the outer guide method is more suitable when the outer ring does not rotate and the inner ring rotates, while the inner guide method is more suitable when the outer ring rotates and the inner ring does not rotate. This composite guide method allows one bearing to be used for both working conditions. Furthermore, if the bearing operates in an unstable posture, the cage may become misaligned. In such cases, this composite guide method will complement each other and work together, resulting in a more stable and effective guide than a single guide.

[0025] The cage in this invention can be processed in sections and disassembled, and then assembled into the bearing by welding, riveting, splicing and other methods.

[0026] The beneficial effects of this utility model are:

[0027] (1) This utility model designs the cage guidance method of the single-row self-aligning roller bearing as inner ring guidance, outer ring guidance, or a combination of inner and outer ring guidance, which greatly improves the limiting speed and impact load resistance of this type of bearing, extends the service life of the bearing, and greatly expands the application scenarios of this type of bearing.

[0028] (2) The present invention designs the outer guide surface of the cage as a spherical surface that matches the raceway of the outer ring. By reasonably reducing the outer diameter of the cage, the cage with the spherical outer surface can be installed in the raceway of the outer ring with the same ball diameter. This realizes the reasonable application of the outer guide method in single-row self-aligning roller bearings and significantly improves the performance of the bearing. This spherical guide surface can both radially and axially position the cage. This ability to position in two directions at the same time is not available in other cages. This structure greatly increases the stability of the cage working state and is extremely beneficial to improving the working performance of the bearing.

[0029] (3) By setting a boss at the center of the inner side of each of the two side rings of the cage pocket, the present invention allows the roller end face and the inner side of the cage side ring to have a certain assembly gap. This leaves a certain gap between the contact surface of the rolling element and the outer ring raceway and the contact surface of the outer guide surface of the cage and the outer ring raceway. In this way, when the inner and outer rings of the bearing are in an unstable deflection operation state, the two contact surfaces do not cross and overlap, ensuring the good working state of the rolling element and the cage. In addition, this boss design can also reduce the contact area between the roller end face and the cage side ring, greatly reducing the heat generated when the two surfaces rub against each other, thereby improving the working performance of the bearing and extending its service life. Attached Figure Description

[0030] Figure 1 This is a schematic diagram of the structure of a single-row self-aligning roller bearing with composite inner and outer ring guidance according to this utility model.

[0031] Figure 2 This is a schematic diagram of the outer ring structure in this utility model;

[0032] Figure 3 This is a longitudinal cross-sectional view of the outer ring in this utility model;

[0033] Figure 4 This is a schematic diagram of the inner ring structure in this utility model;

[0034] Figure 5 This is a longitudinal cross-sectional view of the inner ring in this utility model;

[0035] Figure 6 This is a schematic diagram of the roller structure in this utility model;

[0036] Figure 7 This is a schematic diagram of the assembly section of a single-row self-aligning roller bearing guided by the outer ring in this utility model;

[0037] Figure 8 This is a three-dimensional structural diagram of the cage guided by the outer ring in this utility model;

[0038] Figure 9 This is a schematic diagram of the outer ring guided cage in this utility model;

[0039] Figure 10 This is a side view of the outer ring guided cage in this utility model;

[0040] Figure 11 This is a top view of the outer ring guided cage in this utility model;

[0041] Figure 12 This is a schematic diagram of the assembly section of the single-row self-aligning roller bearing guided by the inner ring in this utility model;

[0042] Figure 13 This is a three-dimensional structural diagram of the inner ring guided cage in this utility model;

[0043] Figure 14 This is a schematic diagram of the inner ring guided cage in this utility model;

[0044] Figure 15 This is a side view of the inner ring guided cage in this utility model;

[0045] Figure 16 This is a top view of the inner ring guided cage in this utility model;

[0046] Figure 17 This is a schematic diagram of the assembly section of a single-row self-aligning roller bearing with composite inner and outer ring guidance in this utility model;

[0047] Figure 18 This is a schematic diagram of the three-dimensional structure of the cage with composite inner and outer ring guidance in this utility model;

[0048] Figure 19 This is a schematic diagram of the cage with composite inner and outer ring guidance in this utility model;

[0049] Figure 20 This is a side view of the retainer with composite inner and outer ring guidance in this utility model;

[0050] Figure 21 This is a top view of the cage with composite inner and outer ring guidance in this utility model;

[0051] Figure 22 This is a schematic diagram of the gap between the guide surfaces in this utility model.

[0052] In the diagram: 1—outer ring, 100—outer ring raceway, 2—inner ring, 200—inner ring raceway, 201—inner ring flange, 3—cage, 300—pocket, 301—crossbeam, 302—side ring, 303—inner guide surface, 304—outer guide surface, 305—cutting surface, 4—drum roller, 400—roller axis rotation circle, 401—roller axis, 5—boss, 6—inner ring groove, 7—outer ring groove, 8—outer guide clearance, 9—inner guide clearance, 10—assembly clearance. Detailed Implementation

[0053] The present invention will be further described below with reference to the accompanying drawings and embodiments. Figures 1 to 22 All accompanying drawings are simplified versions of embodiments and are intended solely for the purpose of clearly and concisely illustrating the embodiments of this utility model. The technical solutions shown in the drawings below are specific solutions of embodiments of this utility model and are not intended to limit the scope of the claimed utility model. All other embodiments obtained by those skilled in the art based on the embodiments of this utility model without inventive effort are within the scope of protection of this utility model.

[0054] In the description of this utility model, it should be understood that the terms "upper", "lower", "inner", "outer", "left", "right", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, or the orientation or positional relationship that the utility model product is usually placed in during use, or the orientation or positional relationship that is commonly understood by those skilled in the art. They are only used to facilitate the description of this utility model and to simplify the description, and are not intended to indicate or imply that the device or component referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0055] In the description of this utility model, it should also be noted that, unless otherwise explicitly specified and limited, terms such as "set" and "connection" should be interpreted broadly. For example, "connection" 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 a connection within two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0056] This utility model provides a novel single-row self-aligning roller bearing, such as... Figures 1 to 22 As shown, the device includes an outer ring 1, an inner ring 2, a cage 3 disposed between the outer ring 1 and the inner ring 2, and multiple drum-shaped rollers 4. An inner spherical outer ring raceway 100 is provided on the inner circumferential surface of the outer ring 1. An inner spherical inner ring raceway 200, corresponding to the inner spherical outer ring raceway 100, and inner ring flanges 201 located on both sides are provided on the outer circumferential surface of the inner ring 2. The outer ring raceway 100 and the inner ring raceway 200 conform to the outer diameter surface of the drum-shaped rollers 4. The cage 3 is an annular frame with pockets 300. A crossbeam 301 is provided between two adjacent pockets 300. Side rings 302 are provided on both axial sides of the pockets 300. Multiple drum-shaped rollers 4 are respectively installed in the corresponding pockets 300 and are located between the outer ring raceway 100 and the inner ring raceway 200. Figure 2 and Figure 3 As shown, the outer ring 1 is a short cylindrical shape, with its outer ring surface being cylindrical and its two end faces being flat. The outer ring raceway 100 on its inner surface is an inner spherical ring with the geometric center of the outer ring as its center; as... Figure 4 and Figure 5 As shown, the inner ring 2 is also a short cylindrical shape, with its inner ring surface being cylindrical and its two end faces being flat. Two inner ring flanges 201 are symmetrically arranged on both sides of the inner ring raceway 200. The inner guide surface 303 of the cage 3 operates under the guidance of the outer ring surface of the inner ring flanges 201. The inner ring raceway 200 is an inwardly concave ring, and the curvature of its concavity is the same as that of the outer ring raceway 100. Figure 6 As shown, the drum-shaped roller 4 is a cylindrical object with an arc-shaped outer diameter surface. The arc of its outer diameter surface generatrix is ​​the same as the arc of the outer ring raceway 100, and its two end faces are flat.

[0057] The embodiments of this utility model provide three different guiding methods, and three different retainers are provided for each of the three different guiding methods, including an inner ring guiding retainer, an outer ring guiding retainer, and a composite guiding retainer that guides both the inner and outer rings simultaneously; in the three different embodiments, such as Figures 7 to 22As shown, the retainer 3 is a cylindrical structure composed of two side rings 302 and multiple crossbeams 301 connected between the side rings 302. A pocket 300 for mounting the drum-shaped roller 4 is formed between two adjacent crossbeams 301, and a boss 5 is symmetrically provided at the center of each pocket 300. The axis of the boss 5 coincides with the axis of the drum-shaped roller 4. After the drum-shaped roller 4 is installed into the pocket 300, an assembly gap 10 is formed between the two end faces of the drum-shaped roller 4 and the inner end face of the pocket 300. The end face area of ​​the boss 5 is 0.05 to 0.5 times the end face area of ​​the drum-shaped roller 4, and the protrusion height of the boss 5 is 0.005 to 0.05 times the radius of the rotation circle 400 of the roller axis of the drum-shaped roller 4. Because self-aligning roller bearings generally allow for angular deflection within 3°, meaning there can be an axial offset between the rolling elements and the outer ring raceway within a 3° range, the boss height is determined using the radius of the roller axis's revolution circle as a reference. This height-restricted boss 5 allows for a certain assembly clearance 10 between the roller end face and the inner side of the cage side ring. This prevents the running trajectory of the outer guide surface 304 of the cage 3 on the outer ring raceway 100 from intersecting with the running trajectory of the roller on the outer ring raceway 100 when the inner and outer rings rotate under unstable slight deflection. This ensures that both the rolling elements and the cage maintain good working conditions. Furthermore, the boss 5 reduces the contact area between the roller end face and the side ring of the cage 3, significantly reducing the heat generated during friction between the two surfaces and thus minimizing the heat source during bearing operation.

[0058] In this embodiment, the entire bearing consists of an outer ring 1, a cage 3, and an inner ring 2 assembled together in sequence, while the drum-shaped rollers 4 are respectively installed in the pockets 300 of the cage 3. These four parts together form a bearing assembly.

[0059] The cage structure of this utility model will be further described below with reference to specific embodiments and accompanying drawings;

[0060] The novel single-row self-aligning roller bearing provided in Embodiment 1 has a cage 3 that is an outer ring guided cage, such as... Figures 7 to 11 As shown, the outer ring surfaces of the two side rings 302 of the cage are spherical surfaces, and the two spherical surfaces of the two side rings 302 are located on the same spherical surface. The center of the spherical surface of the two side rings 302 and the center of the outer raceway 100 are the same center. The spherical surfaces of the two side rings 302 and the outer raceway 100 are in close contact with a small gap to form an outer guide surface 304 that cooperates with the outer raceway 100.

[0061] Multiple outer ring grooves 7 are evenly distributed on the outer ring surface of the two side rings 302 to facilitate the flow of lubricant and reduce friction on the guide surface. Furthermore, cutting surfaces 305 are respectively provided on the outer guide surfaces 304 of the two side rings 302 of the cage 3. Two cutting surfaces are symmetrically arranged on each side ring 302, and the positions of the cutting surfaces on the two side rings 302 correspond to each other. The extended contours of the four cutting surfaces form a converging cylindrical surface. The cross-sectional diameter of this cylindrical surface is smaller than the diameter of the end face of the outer ring raceway 100, and the difference is between 0.001 and 0.02 times the diameter of the end face of the outer ring raceway 100. The bearing assembly in Embodiment 1 is as follows... Figure 7 As shown, after assembly, the outer diameter surfaces of the two side rings 302 serve as the outer guide surfaces of the cage 3. The generatrices of the surfaces of the two side rings 302 extend towards each other, and their combined contours form a spherical outer guide surface. The area of ​​the outer ring raceway 100 corresponding to the outer guide surface of the cage is the guide surface of the outer ring 1. The center of the spherical outer guide surface of the cage 3 is the same as the center of the outer ring raceway 100. During bearing rotation, the spherical outer guide surface of the cage 3 and the guide surface formed by the outer ring raceway 100 come into contact with each other and are guided.

[0062] Example 2 provides a novel single-row self-aligning roller bearing, in which the bearing is as follows: Figures 12 to 16 As shown, the retainer 3 is an inner ring guide retainer. The inner ring surfaces of the two side rings 302 of the retainer 3 are cylindrical surfaces that protrude towards the axis of the side rings and fit closely with a small gap to the outer diameter surface of the inner ring retainer 201, forming an inner guide surface 303 that cooperates with the inner ring retainer 201. Multiple inner ring grooves 6 are evenly distributed on the inner ring surfaces of the two side rings 302, which facilitates the flow of lubricant and reduces friction on the guide surface; the bearing assembly in Embodiment 2 is as follows... Figure 12 As shown, the inner ring surface of the side ring 302 of the cage is a cylindrical surface, and the inner ring surfaces of the two side rings 302 are the inner guide surfaces of the cage. The outer ring surfaces of the two inner ring flanges 201 of the inner ring 2 are the guide surfaces of the inner ring. When the bearing rotates, the inner guide surface of the cage 3 and the guide surface formed by the outer ring surfaces of the two inner ring flanges 201 of the inner ring 2 come into contact with each other and are guided.

[0063] Example 3 provides a novel single-row self-aligning roller bearing, such as... Figures 17 to 22When the cage 3 is a composite guide cage that guides both inner and outer rings simultaneously, the inner ring surfaces of the two side rings 302 of the cage 3 are cylindrical surfaces that protrude towards the axis of the side rings and fit with a small gap against the outer diameter surface of the inner ring flange 201, forming an inner guide surface 303 that cooperates with the inner ring flange 201; the outer ring surfaces of the two side rings 302 are spherical surfaces, and the two spherical surfaces of the two side rings are on the same spherical surface. The center of the spherical surface of the two side rings 302 and the center of the outer ring raceway are the same spherical center. The spherical surfaces of the two side rings 302 fit with the outer ring raceway 100 with a small gap, forming an inner guide surface 303 that cooperates with the outer ring flange 201. The outer guide surfaces 304 of the raceways 100 are mutually cooperating. Multiple inner ring grooves 6 are evenly distributed on the inner ring surfaces of the two side rings 302, and multiple outer ring grooves 7 are evenly distributed on the outer ring surfaces of the two side rings 302. This facilitates the flow of lubricant and reduces friction on the guide surfaces. Furthermore, cutting surfaces 305 are provided on the outer guide surfaces 304 of the side rings 302 of the cage 3. Each side ring has two symmetrically arranged cutting surfaces, and the positions of the cutting surfaces between two side rings correspond to each other. The extended contours of the four cutting surfaces form a converging cylindrical surface, the cross-sectional diameter of which is smaller than the diameter of the end face of the outer ring raceway 100 of the outer ring 1. Embodiment 3 combines the inner guide of Embodiment 1 and the outer guide of Embodiment 2. The cage assembly is as follows: Figure 17 As shown, after assembly, when the bearing rotates, the spherical outer guide surface of the cage 3 contacts and is guided by the guide surface formed by the outer ring raceway 100, and the inner guide surface of the cage 3 contacts and is guided by the guide surface formed by the outer ring surfaces of the two inner ring flanges 201 of the inner ring 2.

[0064] In the outer ring guide cage of Embodiment 1 and the composite guide cage with simultaneous inner and outer ring guidance in Embodiment 3, such as Figure 22 As shown, an outer guide gap 8 is provided between the spherical outer guide surface of the cage 3 and the guide surface formed by the outer ring raceway 100. The value of the outer guide gap 8 is 1.2 to 12 times the upper limit of the radial clearance design of the bearing. In the above two embodiments, the outer guide surface 304 of the cage 3 is designed as a spherical surface with the same curvature as the outer ring raceway 100. This allows the two guide surfaces to fit together well, making the contact surfaces work more smoothly and minimizing wear. At the same time, this spherical guide surface can be used for both radial and axial positioning, providing positioning in both directions simultaneously. This structure greatly increases the stability of the cage's working state and is extremely beneficial to improving the bearing's performance.

[0065] In Embodiments 2 and 3, when the cage 3 is guided by the inner ring, the inner ring surface of the side ring 302 is a cylindrical surface, and the inner ring surfaces of the two side rings 302 are the inner guide surfaces of the cage. The outer ring surfaces of the two inner ring flanges 201 of the inner ring 2 are the guide surfaces of the inner ring. The inner guide surface of the cage 3 has a larger diameter than the guide surface of the inner ring 2, and an inner guide gap 9 is formed between them. The value range of the inner guide gap 9 is 1 to 10 times the upper limit of the radial clearance design of the bearing.

[0066] The outer guide gap 8 and inner guide gap 9 in this embodiment are set primarily to account for thermal expansion of the cage 3 due to temperature increases or machining accuracy deviations during bearing operation, which could lead to seizing between the two guide surfaces. Setting the outer guide gap 8 and inner guide gap 9 solves this problem, allowing the two guide surfaces to fit together well without seizing. Since there are many materials used to make the cage, including non-ferrous metals and non-metallic materials, the coefficients of thermal expansion of these materials differ significantly from the steel used for bearing rings and rolling elements. In particular, the coefficient of thermal expansion of some non-metallic materials is several times greater than that of steel. Therefore, this invention sets the value of the outer guide gap 8 within 1.2 to 12 times the upper limit of the bearing's radial clearance design. The working state of the inner guide gap is slightly different from that of the outer guide gap, and its variation during operation is smaller. Therefore, its value range is 1 to 10 times the upper limit of the bearing's radial clearance design.

[0067] In Examples 1 and 3, the diameter of the cylindrical profile section formed by the four cutting surfaces 305 is slightly smaller than the diameter of the end face of the outer raceway 100. The difference is set between 0.001 and 0.02 times the diameter of the end face of the outer raceway 100. Specifically, this is because the outer diameter surfaces of the two side rings 302 of the cage 3 are spherical. The diameter of the inner ring surface of the side ring 302 near the crossbeam 301 is larger than the diameter of the outer ring surface away from the crossbeam 301. The diameter of the end face of the outer raceway 100 is basically the same as the diameter of the outer ring surface of the side ring 302 of the cage 3. Thus, the diameter of the inner ring surface of the side ring 302 of the cage 3 is larger than the diameter of the end face of the outer raceway 100, which makes it impossible for the cage 3 to be installed in the outer raceway 100. In both Embodiment 1 and Embodiment 3, to achieve external guidance of the cage, a portion is cut off at symmetrical positions on the outer surface of the cage in a direction perpendicular to the radial direction of the cage, forming four cutting surfaces. The cylindrical surfaces formed by the extended contours of these four cutting surfaces 305 have a cross-sectional diameter slightly smaller than the diameter of the end face of the outer raceway 100. The difference is set between 0.001 and 0.02 times the diameter of the end face of the outer raceway 100. In this way, the cage 3 can be inserted into the outer raceway 100 in an attitude perpendicular to the end face of the outer raceway. This ensures that the cage 3 can be installed into the outer raceway 100 while minimizing the amount of reduction of the side ring of the cage 3, thereby minimizing the impact on the strength of the cage caused by the reduction.

[0068] In the above embodiments, the number of inner ring grooves 6 and outer ring grooves 7 are each more than four; the total length of the groove opening arc of all inner ring grooves 6 is 20% to 65% of the inner diameter circumference of the side ring 302, and the depth of the inner ring groove 6 does not exceed the rotation circle 400 of the axis of the drum roller 4; the total length of the groove opening arc of the outer ring groove 7 is 20% to 65% of the outer diameter circumference of the side ring 302, and the depth of the outer ring groove 7 does not exceed the rotation circle 400 of the axis of the roller. The number and depth of the grooves do not affect the strength and wear resistance of the cage, and can achieve the purpose of friction reduction.

[0069] The following is a detailed description of the assembly process using Embodiment 3. In Embodiment 3, the retainer 3 is a composite inner and outer guide retainer, and its assembly is as follows: Figure 17As shown, first, the cage 3 is inserted into the outer ring raceway 100 with the cut surface 305 perpendicular to the end face of the outer ring 1. After the center points of the two parts coincide, the cage 3 is flipped to the horizontal position of the outer ring 1. Then, the inner ring 2 is fitted parallel to the center position of the cage 3. Then, the inner ring 2 and the cage 3 are flipped together to the position perpendicular to the outer ring 1. At this time, while rotating the cage 3 along the axis of the cage 3, the drum-shaped rollers 4 are inserted one by one into the pockets 300 of the cage 3 until all the drum-shaped rollers 4 are inserted. Then, the assembly composed of the inner ring 2, the cage 3, and the drum-shaped rollers 4 is flipped to the horizontal position of the outer ring 1. At this point, the bearing assembly is completed.

[0070] The following is an implementation explanation of the clearance value between the outer guide surfaces of the cage 3 of the standard-designed 22318 / C3 bearing: According to the national standard GB / T273.3, the 22318 self-aligning roller bearing has an outer diameter of 190mm, an inner diameter of 90mm, and a width of 64mm. Based on the bearing's external dimensions, referring to the national standard GB / T4604.1, the radial clearance value range for the C3 group is 0.10~0.135mm. Therefore, the upper limit of its radial clearance is 0.135mm. If we do not consider the influence of different materials and machining accuracy deviations, the optimal clearance value between the guide surfaces of the bearing cage is twice the upper limit of the radial clearance. Based on this, without considering different materials and machining accuracy deviations, the clearance value between the outer guide surfaces of this bearing is: h1=2×0.135=0.27mm.

[0071] The above description is merely one embodiment of this utility model, and while it is quite specific and detailed, it should not be construed as limiting the scope of this utility model. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of this utility model, and these all fall within the protection scope of this utility model. Therefore, the protection scope of this utility model should be determined by the appended claims.

Claims

1. A novel single-row self-aligning roller bearing, comprising an outer ring (1), an inner ring (2), a cage (3) disposed between the outer ring (1) and the inner ring (2), and a plurality of drum-shaped rollers (4). An inner spherical outer ring raceway (100) is provided on the inner circumferential surface of the outer ring (1), and an inner spherical inner ring raceway (200) corresponding to and cooperating with the inner spherical outer ring raceway (100) and inner ring flanges (201) located on both sides are provided on the outer circumferential surface of the inner ring (2). The outer ring raceway (100), inner ring raceway (200), inner ring raceway (200), inner ring raceway (200), inner ring raceway (201 ... The outer diameter surfaces of the raceway (200), the drum rollers (4), and the inner diameter surfaces have the same curvature of their generatrices; the cage (3) is an annular frame with pockets (300) on it, a crossbeam (301) between two adjacent pockets (300), and side rings (302) on both sides of the axial direction of the pockets (300). Multiple drum rollers (4) are respectively installed in the corresponding pockets (300) and located between the outer raceway (100) and the inner raceway (200). Its characteristic is that: The cage (3) is an inner ring guided cage, or an outer ring guided cage, or a composite guided cage that guides both the inner and outer rings simultaneously; When the retainer (3) is an inner ring guide retainer, the inner ring surface of the two side rings (302) of the retainer is a cylindrical surface, and the inner ring surface of the two side rings (302) protrudes towards the axis of the side ring (302) and forms an inner guide surface (303) that cooperates with the inner ring flange (201). When the cage (3) is an outer ring guide cage, the outer ring surface of the two side rings (302) of the cage is a spherical surface, and the two spherical surfaces of the two side rings are on the same spherical surface. The center of the two side rings is the same as the center of the outer ring raceway (100). The spherical surfaces of the two side rings (302) form an outer guide surface (304) that cooperates with the outer ring raceway (100). Cutting surfaces (305) are respectively provided on the outer guide surfaces (304) of the two side rings (302) of the cage (3). Two cutting surfaces are symmetrically provided on each side ring (302). The positions of the cutting surfaces on the two side rings (302) correspond to each other. The four cutting surfaces (305) are on the same cylindrical surface, and the diameter of the cylindrical profile section formed by the extension of the four cutting surfaces (305) is smaller than the diameter of the end face of the outer ring raceway (100). When the cage (3) is a composite guide cage that guides both the inner and outer rings simultaneously, the inner ring surfaces of the two side rings (302) of the cage are cylindrical surfaces, and the inner ring surfaces of the two side rings (302) protrude towards the axis of the side ring (302), forming an inner guide surface (303) that cooperates with the inner ring flange (201); the outer ring surfaces of the two side rings (302) of the cage are spherical surfaces, and the two spherical surfaces of the two side rings are on the same spherical surface, and the center of the two spherical surfaces of the two side rings is the same as the center of the outer ring raceway (100). The spherical surface of the ring (302) forms an outer guide surface (304) that cooperates with the outer raceway (100); and cutting surfaces (305) are respectively provided on the outer guide surfaces (304) of the two side rings (302) of the cage (3). Two cutting surfaces are symmetrically provided on each side ring (302), and the positions of the cutting surfaces on the two side rings (302) correspond to each other. The four cutting surfaces (305) are on the same cylindrical surface, and the diameter of the cylindrical profile section formed by the extension of the four cutting surfaces (305) is smaller than the diameter of the end face of the outer raceway (100).

2. The novel single-row self-aligning roller bearing according to claim 1, characterized in that: On the opposite sides of the two rings (302), and symmetrically provided at the center of each pocket (300), the axis of the boss (5) coincides with the axis of the drum roller (4); after the drum roller (4) is installed into the pocket (300), an assembly gap (10) is formed between the two end faces of the drum roller (4) and the inner end face of the pocket (300).

3. A novel single-row self-aligning roller bearing according to claim 1 or 2, characterized in that: When the retainer (3) is an inner ring guide retainer, multiple inner ring grooves (6) are evenly distributed on the inner ring surface of the two side rings (302); when the retainer (3) is an outer ring guide retainer, multiple outer ring grooves (7) are evenly distributed on the outer ring surface of the two side rings (302); when the retainer (3) is a composite guide retainer that guides both inner and outer rings simultaneously, multiple inner ring grooves (6) are evenly distributed on the inner ring surface of the two side rings (302), and multiple outer ring grooves (7) are evenly distributed on the outer ring surface of the two side rings (302).

4. A novel single-row self-aligning roller bearing according to claim 1 or 2, characterized in that: When the cage (3) is an outer ring guide cage or a composite guide cage that guides both the inner and outer rings, the diameter of the cylindrical cross-section formed by the extended contours of the four cut surfaces on the outer guide surface (304) is smaller than the diameter of the end face of the outer ring raceway (100), and the difference is between 0.001 and 0.02 times the diameter of the end face of the outer ring raceway (100).

5. A novel single-row self-aligning roller bearing according to claim 1 or 2, characterized in that: The outer ring (1) is a short cylindrical shape with a cylindrical outer surface and flat ends on both sides. The inner spherical outer ring raceway (100) on its inner surface is an inner spherical ring with the geometric center of the outer ring as its center. The inner ring (2) is also a short cylindrical shape with a cylindrical inner surface and flat ends on both sides. The inner ring raceway (200) on the outer surface of the inner ring (2) is an inwardly concave ring with the same generatrix curvature as the outer ring raceway (100). Two inner ring flanges (201) are symmetrically provided on both sides of the inner ring raceway (200).

6. A novel single-row self-aligning roller bearing according to claim 1 or 2, characterized in that: The drum-shaped roller (4) is a cylindrical object with an arc-shaped outer diameter surface and two flat ends.

7. A novel single-row self-aligning roller bearing according to claim 1 or 2, characterized in that: The retainer (3) is a cylindrical structure consisting of two side rings (302) and multiple crossbeams (301) connected between the side rings (302), with pockets (300) formed between two adjacent crossbeams (301) for placing drum-shaped rollers (4).

8. A novel single-row self-aligning roller bearing according to claim 1 or 2, characterized in that: When the cage (3) is guided on the outer ring, the outer diameter surfaces of the two side rings (302) serve as the outer guide surfaces of the cage (3). The generatrices of the surfaces of the two side rings (302) extend towards each other and combine to form a spherical outer guide surface profile. The area of ​​the outer ring raceway (100) corresponding to the outer guide surface (304) of the cage is the guide surface of the outer ring (1). The center of the spherical outer guide surface of the cage (3) is the same as the center of the spherical raceway (100) of the outer ring, and an outer guide gap (8) is provided between the spherical outer guide surface of the cage (3) and the guide surface formed by the outer ring raceway (100). The value of the guide clearance (8) is 1.2 to 12 times the upper limit of the radial clearance design of the bearing. When the cage (3) is guided by the inner ring, the inner ring surface of the side ring (302) is a cylindrical surface, and the inner ring surfaces of the two side rings (302) are the inner guide surfaces (303) of the cage. The outer diameter of the two inner ring flanges (201) of the inner ring (2) is used as the guide surface of the inner ring. The inner guide surface of the cage (3) is larger than the guide surface of the inner ring (2), and an inner guide clearance (9) is formed between them. The value of the inner guide clearance (9) is 1 to 10 times the upper limit of the radial clearance design of the bearing.

9. A novel single-row self-aligning roller bearing according to claim 2, characterized in that: The end face area of ​​the boss (5) is 0.05 to 0.5 times the end face area of ​​the drum roller (4), and the protrusion height of the boss (5) is 0.005 to 0.05 times the radius of the rotation circle (400) of the roller axis of the drum roller (4).

10. A novel single-row self-aligning roller bearing according to claim 3, characterized in that: The number of inner ring grooves (6) and outer ring grooves (7) is more than 4 each; the total length of the groove opening arc of all inner ring grooves (6) is 20% to 65% of the inner diameter circumference of the side ring (302), and the depth of the inner ring grooves (6) does not exceed the axial rotation circle (400) of the drum roller (4); the total length of the groove opening arc of the outer ring grooves (7) is 20% to 65% of the outer diameter circumference of the side ring (302), and the depth of the outer ring grooves (7) does not exceed the axial rotation circle (400) of the roller.

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