Cylindrical roller bearing with disc type retainer

Abstract

The utility model relates to a cylindrical roller bearing with a disc-type retainer, which belongs to the technical field of bearing assembly and manufacture and comprises an inner ring, an outer ring, rollers and the disc-type retainer, the inner ring and the outer ring are coaxially arranged, and the disc-type retainer and the plurality of rollers are arranged between the inner ring and the outer ring; the outer ring is formed by combining two annular split half outer rings, a retainer limiting groove used for positioning the disc type retainer is formed in the middle of the inner diameter face of the outer ring, the retainer limiting groove is formed between the two split half outer rings, and the outer edge of the disc type retainer is assembled in the retainer limiting groove. Flanges are arranged on the two sides of the inner diameter face of the outer ring, and the rollers are axially limited through the flanges. The limitation on the retainer is reduced through the split bearing outer ring, and the split outer ring is combined with the disc type retainer, so that the assembly space of the retainer is effectively controlled, the bearing has the advantages of high bearing capacity, long service life and high reliability, the performance of the gear box is improved, and meanwhile, the loss caused by fault shutdown is avoided.

Description

Technical Field

[0001] The utility model relates to a disc-type retainer cylindrical roller bearing, belonging to the technical field of bearing assembly and manufacturing. Background Art

[0002] With the continuous development of equipment technology, the performance requirements for industrial gearboxes are becoming increasingly higher, especially in the petrochemical industry. The performance of existing cylindrical roller bearings is increasingly unable to meet the growing production capacity needs, and abnormal production stoppages can cause significant economic losses. Therefore, bearings with high load capacity, long life, and high reliability are required. Conventional cylindrical roller bearing cages occupy a large space, reducing the bearing's load capacity. Although full-complement cylindrical roller bearings have a significant improvement in load capacity, they are not suitable for high-speed operating conditions and are prone to seizure. Utility Model Content

[0003] In view of the defects of the above-mentioned prior art, the purpose of the present invention is to provide a disc-type cage cylindrical roller bearing by comprehensively considering the bearing's load, speed and other working conditions, which can meet the high performance and high reliability requirements of large industrial gearboxes.

[0004] To achieve the above-mentioned purpose, the technical solution adopted by the present invention is as follows: a disc-type cage cylindrical roller bearing, comprising an inner ring, an outer ring, rollers and a disc-type cage, the inner ring and the outer ring being coaxially arranged, the disc-type cage and a plurality of rollers being arranged between the inner ring and the outer ring; the outer ring is formed by a combination of two annular split half outer rings, a cage limiting groove for positioning the disc-type cage is provided in the middle of the inner diameter surface of the outer ring, the cage limiting groove is formed between the two split half outer rings, the outer edge of the disc-type cage is assembled in the cage limiting groove, and outer ring ribs are provided on both sides of the inner diameter surface of the outer ring, and the rollers are axially limited by the outer ring ribs.

[0005] Furthermore, an outer V-shaped groove is provided in the middle of the outer diameter surface of the outer ring, and the outer V-shaped groove is arranged in a circle along the ring; an inner V-shaped groove is provided on the outer diameter surface of the retaining frame limiting groove, and the inner V-shaped groove is arranged in a circle along the ring; the outer V-shaped groove is symmetrically arranged along the axial center line of the outer ring, and the bottom of the outer V-shaped groove is located on the axial center line of the outer ring; the inner V-shaped groove is symmetrically arranged along the axial center line of the outer ring, and the bottom of the inner V-shaped groove is located on the axial center line of the outer ring.

[0006] Furthermore, the two split half outer rings are formed by splitting the integral outer ring along the outer V-shaped groove and the inner V-shaped groove.

[0007] Furthermore, a V-shaped separation groove is provided in the middle of the outer diameter surface of the outer ring, and the separation groove is arranged in a circle along the ring. The outer V-shaped groove is provided at the bottom of the separation groove, and the groove mouth of the outer V-shaped groove continues at the bottom of the separation groove; the groove edge inclination angles of the outer V-shaped groove and the inner V-shaped groove are consistent with the machining tool angle, and the groove edge inclination angle of the separation groove is 120°; the distance between the groove bottom of the outer V-shaped groove and the groove bottom of the inner V-shaped groove is 1~1.5mm.

[0008] Furthermore, each split half outer ring is provided with a plurality of semicircular clamping grooves on the outer diameter surface, and the plurality of semicircular clamping grooves are evenly arranged along the outer diameter surface of the split half outer ring. The clamping grooves on the two split half outer rings are symmetrically arranged along the outer ring split surface, and are paired and combined to form a complete annular clamping groove. An annular clamping ring is embedded in each annular clamping groove, and the two split half outer rings are locked by multiple clamping rings.

[0009] Furthermore, the inner diameter of the clamping ring is interference fit with the clamping groove.

[0010] Furthermore, the radial angle between the outer ring rib and the outer ring is 15'-20', the roller end face is set as a spherical base surface, a roller cavity is set in the center of the end face, and the outer ring rib is in contact with the roller spherical base surface for limiting position.

[0011] Furthermore, the two end faces of the outer edge of the disc retainer correspond to the side walls of the retainer limiting groove, and an axial gap between the disc retainer and the outer ring is formed between the two end faces of the outer edge of the disc retainer and the side walls of the retainer limiting groove; the outer diameter surface of the disc retainer corresponds to the bottom of the retainer limiting groove, and a radial gap between the disc retainer and the outer ring is formed between the outer diameter surface of the disc retainer and the bottom of the retainer limiting groove.

[0012] Furthermore, the radial gap is larger than the axial gap.

[0013] Furthermore, the disc-type retainer includes an annular body, which is an integrally formed disc, and the outer edge of the annular body of the disc-type retainer is assembled in the retainer limiting groove of the outer ring; a number of retainer beams extending toward the center direction of the disc-type retainer are formed along the circumferential inner diameter of the annular body, and the number of retainer beams are evenly arranged in the annular body.

[0014] Furthermore, pockets of the disc-type cage are formed between every two adjacent cage beams. The pockets are semi-open, and the center diameter of the circle where the pockets are located matches the roller diameter.

[0015] Furthermore, each pocket is formed by two adjacent side walls of the retaining frame beam to form a contact surface that cooperates with the outer surface of the roller, that is, the inner wall surface of the pocket.

[0016] Furthermore, the disc-type retainer holds the roller in the radial direction of the roller and is located in the middle of the entire axial length of the roller.

[0017] Furthermore, the end portion of the cage beam extending toward the center of the disc cage is the free end of the cage beam; and a locking opening of the pocket is formed between the free ends of every two adjacent cage beams.

[0018] Furthermore, the outer edge of the disc retainer is evenly provided with a plurality of oil holes along the circumferential direction, and the plurality of oil holes include radial lubricating oil holes and axial lubricating oil holes of the same number and corresponding to each other; the plurality of axial lubricating oil holes are all provided on the outer edge of the disc retainer corresponding to the position of the retainer beam and pass through the end faces of both sides of the disc retainer, and the plurality of radial lubricating oil holes are all provided from the outer diameter surface of the disc retainer perpendicular to the axial lubricating oil holes and are connected with the axial lubricating oil holes.

[0019] The assembly method of the above-mentioned disc-type cage cylindrical roller bearing is as follows: the outer ring is integrally machined and formed, and corresponding outer V-grooves and inner V-grooves are machined on the inner diameter surface and outer diameter surface of the integral outer ring. The integral outer ring is split along the outer V-grooves and inner V-grooves to form two annular split half outer rings. When assembling the bearing, the roller is first installed in the disc-type cage, and then the disc-type cage with the roller is installed in the cage limit groove between the two split half outer rings, and then the two split half outer rings are locked by multiple clamping rings; after the outer component is assembled, the inner ring is finally installed into the bearing from one side.

[0020] The beneficial effects of the present invention are as follows: the present invention reduces the restrictions on the cage structure through the split bearing outer ring structure, and the split outer ring is combined with the disc cage to effectively control the assembly space of the cage, so that the disc cage cylindrical roller bearing has the advantages of high load capacity, long life and high reliability, thereby improving the performance of the gear box and avoiding losses caused by fault shutdown. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Figure 1 This is a schematic structural diagram of a disc-type cage cylindrical roller bearing according to the present invention;

[0022] Figure 2 Schematic diagram of the bearing outer ring structure;

[0023] Figure 3 This is an enlarged view of the outer ring V-groove structure;

[0024] Figure 4 This is an enlarged view of the outer ring rib structure;

[0025] Figure 5 Schematic diagram of the bearing roller structure;

[0026] Figure 6 This is a schematic diagram of the clamping ring assembly;

[0027] Figure 7 This is the exploded view of the clamping ring and clamping groove separated;

[0028] Figure 8 Schematic diagram of the bearing disc cage structure;

[0029] Figure 9 for Figure 8 Front cross-sectional view of

[0030] Figure 10 Schematic diagram of the structure for installing rollers in disc cages;

[0031] Figure 11 for Figure 9 AA section view;

[0032] Figure 12 for Figure 11 Enlarge the C point and assemble it with the bearing outer ring;

[0033] Figure 13 for Figure 9 A magnified view of point B and the structure of the assembly state with the roller;

[0034] In the picture:

[0035] 100, inner circle,

[0036] 200, outer ring, 210, first split half outer ring, 220, second split half outer ring, 230, retainer limit groove, 240, outer ring rib, 250, outer V-groove, 260, inner V-groove, 270, separation groove, 280, clamping groove;

[0037] 300, roller, 310, spherical base surface, 320, roller cavity;

[0038] 400, disc cage, 410, cage beam, 411, free end of cage beam, 420, pocket, 421, inner wall surface of pocket, 430, locking mouth, 440, radial lubricating oil hole, 450, axial lubricating oil hole;

[0039] 500, clamping ring;

[0040] 600, axial clearance;

[0041] 700. Radial clearance. DETAILED DESCRIPTION

[0042] To make the above-mentioned objects, features, and advantages of the present invention more clearly understood, the following detailed description of specific embodiments of the present invention is provided in conjunction with the accompanying drawings. The following description sets forth many specific details to facilitate a full understanding of the present invention. However, the present invention can be implemented in many other ways than those described herein, and those skilled in the art may make similar modifications without departing from the scope of the present invention. Therefore, the present invention is not limited to the specific embodiments disclosed below.

[0043] See attached Figure 1-12 , a disc-type cage cylindrical roller bearing includes an inner ring 100, an outer ring 200, rollers 300 and a disc-type cage 400. The inner ring 100 and the outer ring 200 are coaxially arranged, and a plurality of rollers 300 and a disc-type cage 400 are arranged between the inner ring and the outer ring; the outer ring 200 is formed by combining two annular split half outer rings 210 and 220, and a cage limiting groove 230 for positioning the disc-type cage is provided in the middle of the inner diameter surface of the outer ring. The cage limiting groove 230 is formed between the two split half outer rings, and the outer edge of the disc-type cage 400 is assembled in the cage limiting groove 230, and outer ring ribs 240 are provided on both sides of the inner diameter surface of the outer ring, and the rollers are axially limited by the outer ring ribs 240. The two split half outer rings are correspondingly provided with clamping grooves 280 on the outer diameter surfaces. Clamping rings 500 are embedded in the clamping grooves 280 . The two split half outer rings 210 and 220 are locked by multiple clamping rings 500 .

[0044] Furthermore, each split outer ring half is provided with a plurality of semi-circular clamping grooves on its outer diameter surface. These semi-circular clamping grooves are evenly arranged around the outer diameter surface of the split outer ring half. The clamping grooves on the two split outer ring half are symmetrically arranged along the outer ring split plane, and are paired together to form a complete annular clamping groove. An annular clamping ring is embedded in each annular clamping groove, and the two split outer ring half are locked together by the multiple clamping rings. The inner diameter of the clamping ring is an interference fit with the clamping groove.

[0045] Specifically, in this embodiment, the number of clamping rings is 13 and they are evenly distributed along the circumference of the outer ring.

[0046] Furthermore, an outer V-groove 250 is provided in the middle of the outer diameter surface of the outer ring, and is arranged along a circle. An inner V-groove 260 is provided on the outer diameter surface of the retainer retaining groove 230, and is arranged along a circle. The outer V-grooves 250 are symmetrically arranged along the axial centerline of the outer ring, with their bottoms located on the axial centerline of the outer ring. The inner V-grooves 260 are symmetrically arranged along the axial centerline of the outer ring, with their bottoms located on the axial centerline of the outer ring. The two split outer ring halves are formed by splitting the outer ring along the outer and inner V-grooves.

[0047] Based on the above technical solution, inner V-grooves 260 and outer V-grooves 250 are designed on the inner and outer surfaces of the outer ring, allowing the bearing outer ring to be split along the opening direction of the inner and outer V-grooves 260. This makes the splitting process safer and more reliable, and reduces component waste. After the outer ring is split and assembled, the split surfaces of the two split outer ring halves can correspond to each other, achieving a better assembly effect than split outer ring halves that are separately processed and then paired.

[0048] like Figure 2 As shown, the outer ring of the bearing is designed as an integral structure. After the ring is processed as a whole, the outer ring is split into two halves through the inner V-groove 260 and the outer V-groove 250. When assembling the bearing, the roller 300 is first installed in the disc retainer 400, and then the disc retainer 400 is installed in the retainer limit groove 230 between the two split outer ring halves. Finally, the two split outer ring halves are locked by multiple clamping rings 500.

[0049] Furthermore, a V-shaped separation groove 270 is provided in the middle of the outer diameter surface of the outer ring, and the separation groove 270 is arranged in a circle along the ring. The outer V-groove 250 is provided at the bottom of the separation groove, and the groove mouth of the outer V-groove 250 continues at the bottom of the separation groove 270; the groove edge inclination angles of the outer V-groove 250 and the inner V-groove 260 are consistent with the machining tool angle, and the groove edge inclination angle of the separation groove 270 is 120°; the distance S between the groove bottom of the outer V-groove 250 and the groove bottom of the inner V-groove 260 is 1~1.5mm.

[0050] Based on the above technical solution, the inner diameter of the bearing outer ring and the outer diameter of the retaining groove are both designed with V-shaped grooves, such as Figure 3 As shown, the V-groove angle is α, which generally corresponds to the machining tool angle. The upper separation groove angle is β, which is set at 120°. The distance S between the bottoms of the inner and outer V-grooves is controlled between 1 and 1.5 mm. This design makes it easier to split the bearing outer ring in half, and the cross-section is relatively regular. The separation groove 270 provides operating space for machining the outer V-groove 250 and reduces the groove depth of the outer V-groove, facilitating the distance between the bottoms of the outer V-groove 250 and the inner V-groove 260 to be controlled between 1 and 1.5 mm.

[0051] Furthermore, the radial angle between the outer ring rib 240 and the outer ring is 15'-20', the end face of the roller 300 is set as a spherical base surface 310, and a roller pocket 320 is designed at the center of the cylindrical roller end face. The outer ring rib 240 is in contact with the roller spherical base surface 310 for limiting position.

[0052] Based on the above technical solution, Figure 4 As shown, the bearing rib 240 forms an angle γ with the radial direction, which can be 15' or 20', etc. Figure 5As shown in the figure, the cylindrical roller end face is designed with a spherical base surface, and the center of the cylindrical roller end face is designed with a roller pocket. The spherical base surface 310 radius R is designed differently according to the bearing size and contact position. This reduces the contact area between the bearing rib and the cylindrical roller, which can reduce wear and increase the maximum speed of the bearing.

[0053] Furthermore, the two end faces of the outer edge of the disc retainer 400 correspond to the sidewalls of the retainer limiting groove 230, forming an axial gap 600 between the disc retainer 400 and the outer ring 200. The outer diameter surface of the disc retainer 400 corresponds to the bottom of the retainer limiting groove 230, forming a radial gap 700 between the disc retainer 400 and the outer ring 200. This radial gap 700 is larger than the axial gap 600 to prevent retainer wear during operation.

[0054] Specifically, the radial clearance is 0.7~1.0mm, and the axial clearance is 0.2~0.4mm. The clearance may vary slightly depending on the bearing size.

[0055] Based on the above technical solution, the distance between the two side walls of the retaining frame limit groove 230 is the limit width P of the outer ring, and the limit groove width P is slightly larger than the width Q of the disc retaining frame to prevent it from affecting the rotation; it should be noted that the limit groove width P cannot be too large relative to the width Q of the disc retaining frame, and the size difference cannot exceed the value range of the axial clearance to prevent the retaining frame from being skewed during the operation of the bearing.

[0056] Furthermore, the disc-type retainer includes an annular body, which is an integrally formed sheet-type disc, and the outer edge of the annular body of the disc-type retainer is assembled in the retainer limiting groove 230 of the outer ring; a number of retainer beams 410 extending toward the center direction of the disc-type retainer are formed along the circumferential inner diameter of the annular body, and the number of retainer beams 410 are evenly arranged in the annular body; a pocket 420 of the disc-type retainer is formed between each two adjacent retainer beams 410, and the pocket 420 is semi-open, and each of the pockets 420 is formed by the side walls of two adjacent retainer beams 410 to form a contact surface that cooperates with the outer surface of the roller 300, that is, the inner wall surface of the pocket 420; during assembly, the roller 300 is installed into the pocket 420 from one side of the disc-type retainer, so that the entire pocket inner wall surface 421 contacts the outer diameter surface of the roller.

[0057] Based on the above technical solution, since the pocket 420 adopts a semi-open form, the end of the cage beam 410 extending toward the center of the cage is the free end 411 of the cage beam.

[0058] A locking notch 430 for the pocket 420 is formed between the free ends 411 of each pair of adjacent retainer beams. This prevents the roller 300 from falling out of the pocket 420 and serves to lock the roller. The distance of the locking notch 430 is determined through reasonable calculation. Specifically, the retainer locking notch dimension L2 is generally approximately 1 mm smaller than the rolling element diameter. This locking amount is not fixed and is designed differently based on the substrate.

[0059] Through the above-mentioned lock 430 design, the roller 300 is installed in the pocket 420, so that the bearing outer ring 200, the roller 300 and the disc retainer 400 form an assembly, preventing the roller 300 from falling from the inner diameter direction during installation.

[0060] Furthermore, the center diameter of the circle in which the pocket 420 is located matches the roller diameter.

[0061] Furthermore, the disc retainer 400 holds the roller 300 in the radial direction of the roller 300 and the disc retainer 400 is located in the middle of the entire axial length of the roller 300 .

[0062] The width of the cage beam depends on the center diameter of the circle where the pocket is located and the diameter of the roller. Under the condition of the same number of rollers, the larger the roller diameter, the larger the center diameter of the circle where the pocket is located, and the smaller the cage beam width. This solution can increase the number of rollers and improve the bearing capacity of the bearing by reducing the cage beam width.

[0063] Furthermore, the outer edge of the disc retainer 400 is evenly provided with a plurality of oil holes along the circumferential direction, and the plurality of oil holes include the same number of radial lubricating oil holes 440 and axial lubricating oil holes 450 that correspond one to one; the plurality of axial lubricating oil holes 450 are all provided on the outer edge of the disc retainer corresponding to the position of the retainer beam 410 and pass through the end faces of both sides of the disc retainer 400, and the plurality of radial lubricating oil holes 440 are all provided perpendicular to the axial lubricating oil holes 450 from the outer diameter surface of the disc retainer 400 and are connected with the axial lubricating oil holes 450.

[0064] Based on the above technical solution, the radial lubricating oil hole 440 is set in the middle of the outer diameter surface of the disc retainer 400, and several radial lubricating oil holes 440 are evenly distributed on the outer diameter surface of the disc retainer 400 along the ring, and several radial lubricating oil holes 440 correspond to the split surface between the two split half outer rings.

[0065] The assembly method of the above-mentioned disc-type retainer cylindrical roller bearing is as follows: the outer ring 200 is integrally machined and formed, and corresponding outer V-grooves 250 and inner V-grooves 260 are machined on the inner and outer diameter surfaces of the integral outer ring 400. The integral outer ring is split along the outer V-grooves 250 and inner V-grooves 260 to form two annular split outer ring halves 210 and 220. When assembling the bearing, the roller 300 is first installed into the disc-type retainer 400. The roller 300 is installed into the pocket 420 from one side of the disc-type retainer 400 so that the entire inner wall surface of the pocket 420 contacts the outer diameter surface of the roller 300; the disc-type retainer 400 with the roller 300 is then installed in the retainer limit groove 230 between the two split outer ring halves. The two split outer ring halves 210 and 220 are then locked by multiple clamping rings. After the outer components are assembled, the inner ring is finally installed into the bearing from one side.

[0066] It should be noted that the parts not described in detail in the present invention are prior art.

[0067] 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 to 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 device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation to the present invention.

[0068] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of the technical features being referred to. Thus, a feature specified as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of this utility model, "plurality" means at least two, such as two, three, etc., unless otherwise specifically defined.

[0069] In this utility model, unless otherwise specified or limited, the terms "installed," "connected," "connect," "fixed," etc. should be understood in a broad sense. For example, they can refer to fixed connection, detachable connection, or integration; mechanical connection, electrical connection; direct connection, or indirect connection through an intermediate medium; internal communication between two components, or interaction between two components, unless otherwise specified. Those skilled in the art will understand the specific meanings of the above terms in this utility model based on specific circumstances.

[0070] In the present invention, unless otherwise expressly specified or limited, when a first feature is "above" or "below" a second feature, it may mean that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediary. Furthermore, when a first feature is "above," "above," or "above" a second feature, it may mean that the first feature is directly above or diagonally above the second feature, or simply means that the first feature is at a higher level than the second feature. When a first feature is "below," "below," or "below" a second feature, it may mean that the first feature is directly below or diagonally below the second feature, or simply means that the first feature is at a lower level than the second feature.

[0071] 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 an intermediate 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 an intermediate element. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used herein are for illustrative purposes only and do not represent the only implementation methods.

[0072] The above examples are merely preferred embodiments of the present invention. Obviously, the present invention is not limited to the above examples and is subject to numerous variations. Any variations that can be directly derived or conceived by a person skilled in the art from the disclosure of the present invention should be considered within the scope of protection of the present invention.

Claims

1. A cylindrical roller bearing with a disc cage, characterized in that: It includes an inner ring, an outer ring, a roller and a disc retainer, the inner ring and the outer ring are coaxially arranged, and the disc retainer and a plurality of rollers are arranged between the inner ring and the outer ring; the outer ring is formed by combining two annular split half outer rings, and a retainer limiting groove for positioning the disc retainer is provided in the middle of the inner diameter surface of the outer ring, the retainer limiting groove is formed between the two split half outer rings, the outer edge of the disc retainer is assembled in the retainer limiting groove, and outer ring ribs are provided on both sides of the inner diameter surface of the outer ring, and the rollers are axially limited by the outer ring ribs.

2. A disc-type retainer cylindrical roller bearing according to claim 1, characterized in that: An outer V-shaped groove is provided in the middle of the outer diameter surface of the outer ring, and the outer V-shaped groove is arranged in a circle along the ring; an inner V-shaped groove is provided on the outer diameter surface of the retaining frame limiting groove, and the inner V-shaped groove is arranged in a circle along the ring; the outer V-shaped groove is symmetrically arranged along the axial center line of the outer ring, and the bottom of the outer V-shaped groove is located on the axial center line of the outer ring; the inner V-shaped groove is symmetrically arranged along the axial center line of the outer ring, and the bottom of the inner V-shaped groove is located on the axial center line of the outer ring.

3. The disc-type retainer cylindrical roller bearing according to claim 2, characterized in that: The two split half outer rings are formed by splitting the integral outer ring along the outer V-shaped groove and the inner V-shaped groove.

4. A disc-type retainer cylindrical roller bearing according to claim 3, characterized in that: A V-shaped separation groove is provided in the middle of the outer diameter surface of the outer ring, and the separation groove is arranged in a circle along the ring. The outer V-shaped groove is provided at the bottom of the separation groove, and the groove mouth of the outer V-shaped groove continues at the bottom of the separation groove; the groove edge inclination angles of the outer V-shaped groove and the inner V-shaped groove are consistent with the machining tool angle, and the groove edge inclination angle of the separation groove is 120°; the distance between the groove bottom of the outer V-shaped groove and the groove bottom of the inner V-shaped groove is 1~1.5mm.

5. The disc-type retainer cylindrical roller bearing according to claim 1, characterized in that: Each split half outer ring is provided with a plurality of semicircular clamping grooves on the outer diameter surface. The plurality of semicircular clamping grooves are evenly arranged around the outer diameter surface of the split half outer ring. The clamping grooves on the two split half outer rings are symmetrically arranged along the split surface of the outer ring, and are paired and combined to form a complete annular clamping groove. An annular clamping ring is embedded in each annular clamping groove, and the two split half outer rings are locked by multiple clamping rings; the inner diameter of the clamping ring is interference fit with the clamping groove.

6. The disc-type retainer cylindrical roller bearing according to claim 1, characterized in that: The radial angle between the outer ring rib and the outer ring is 15'-20'.

7. The disc-type retainer cylindrical roller bearing according to claim 1, characterized in that: The two end faces of the outer edge of the disc retainer correspond to the side walls of the retainer limiting groove, and an axial gap between the disc retainer and the outer ring is formed between the two end faces of the outer edge of the disc retainer and the side walls of the retainer limiting groove; the outer diameter surface of the disc retainer corresponds to the groove bottom of the retainer limiting groove, and a radial gap between the disc retainer and the outer ring is formed between the outer diameter surface of the disc retainer and the groove bottom of the retainer limiting groove; the radial gap is greater than the axial gap.

8. A cylindrical roller bearing with a disc cage according to any one of claims 1 to 7, characterized in that: The disc retainer includes an annular body, which is an integrally formed sheet-type disc. The outer edge of the annular body of the disc retainer is assembled in the retainer limit groove of the outer ring; a number of retainer beams extending toward the center of the disc retainer are formed along the circumferential inner diameter of the annular body, and the number of retainer beams are evenly arranged in the annular body; a pocket of the disc retainer is formed between each two adjacent retainer beams, and the pocket is semi-open, and the center diameter of the circle in which the pocket is located matches the roller diameter.

9. The disc-type retainer cylindrical roller bearing according to claim 8, characterized in that: Each of the pockets is formed by two adjacent retainer beam side walls forming a contact surface that cooperates with the outer surface of the roller, that is, the inner wall surface of the pocket; the disc retainer holds the roller in the radial direction of the roller and the disc retainer is located in the middle position of the entire axial length of the roller; the end of the retainer beam extending toward the center of the disc retainer is the free end of the retainer beam; a locking mouth of the pocket is formed between the free ends of each two adjacent retainer beams.

10. The disc-type retainer cylindrical roller bearing according to claim 8, characterized in that: The outer edge of the disc retainer is evenly provided with a plurality of oil holes along the circumferential direction, and the plurality of oil holes include radial lubricating oil holes and axial lubricating oil holes of the same number and corresponding to each other; the plurality of axial lubricating oil holes are all provided on the outer edge of the disc retainer corresponding to the position of the retainer beam and pass through the end faces of both sides of the disc retainer, and the plurality of radial lubricating oil holes are all provided perpendicular to the axial lubricating oil holes from the outer diameter surface of the disc retainer and are connected to the axial lubricating oil holes.

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