Bearing for a vertical shaft

Abstract

The application discloses a bearing for a vertical shaft, comprising an outer ring and an inner ring, two rows of retainers are arranged between the outer ring and the inner ring, rolling bodies are assembled in the retainers, the retainers comprise an upper edge part, a pocket part and a lower edge part, the upper edge part is arranged along the axial direction of the outer ring, the lower edge part is arranged along the radial direction of the outer ring, the pocket part is arranged obliquely, a plurality of pockets are arranged on the pocket part, pocket beams are formed between adjacent pockets on the pocket part, a plurality of outer convex ribs are arranged obliquely on the outer circumferential wall of the retainer, a plurality of inner convex ribs are arranged obliquely on the inner circumferential wall of the retainer, and the inner convex ribs and the outer convex ribs are arranged at positions corresponding to the pocket beams. The bearing has the advantages of simple structure, effective solution to the problems of uneven distribution of lubricating grease, double-row bearing lubricating grease flow and poor sealing reliability in the prior art, and effective improvement of the operation stability and service life of the bearing.

Description

Technical Field

[0001] This invention relates to a bearing for a vertical shaft. Background Technology

[0002] In the field of industrial transmission equipment, rolling bearings, as core support components, are widely used in various installation conditions, including horizontal and vertical installations. Among them, tapered roller bearings, due to their ability to carry both radial and axial loads, have become a key selection for equipment such as vertical motors and vertical pumps. The lubrication reliability of rolling bearings directly determines the service life of the equipment. The internal grease is usually stored in the bearing cavity formed by the inner ring, outer ring, and rolling elements. For vertically installed tapered roller bearings, whose axis is arranged along the direction of gravity, the influence of gravity is more significant, leading to uneven grease settling and distribution. Grease easily detaches from the meshing area between the rolling elements and the raceway, settling and accumulating in the lower space of the bearing. This results in the upper rolling elements being in a state of insufficient lubrication for a long time, causing faults such as excessive temperature rise and raceway spalling. In double-row tapered roller bearings, the two rows of rollers share the same lubrication space, lacking an effective oil separator. Grease from one row can easily flow to the other row, further exacerbating the problem of uneven lubrication distribution. Traditional cages have a single function; existing cages only have the basic function of limiting the rolling elements and cannot guide the return of settled grease. Currently, the industry often alleviates the above problems by increasing the amount of grease filling and shortening the maintenance cycle. However, such methods are only temporary solutions. They not only increase the operation and maintenance costs, but also cannot fundamentally solve the technical pain points of grease settlement, crossflow and seal failure in vertical shaft bearings. Summary of the Invention

[0003] To address the shortcomings of existing technologies, this invention provides a bearing for vertical shafts. It has a simple structure and effectively solves problems such as uneven grease distribution, grease cross-flow in double-row bearings, and poor sealing reliability in existing technologies, thereby effectively improving the operating stability and service life of the bearing.

[0004] To achieve the above objectives, the present invention provides a bearing for a vertical shaft, comprising an outer ring and an inner ring, wherein two raceways are provided between the outer ring and the inner ring, and a cage is provided in each raceway. Rolling elements are assembled in the cage, and the cage has a frustoconical profile. The cage includes an upper edge, a pocket portion, and a lower edge portion. The upper edge portion is located closer to the edge of the outer ring than the lower edge portion. The upper edge portion is arranged along the axial direction of the outer ring, and the lower edge portion is arranged along the radial direction of the outer ring. The pocket portion is obliquely connected between the upper edge portion and the lower edge portion. The pocket portion has a plurality of pockets, and a pocket beam is formed between adjacent pockets. A plurality of outwardly protruding ribs are obliquely provided on the outer peripheral wall of the cage, and a plurality of inwardly protruding ribs are obliquely provided on the inner peripheral wall of the cage. The inwardly and outwardly protruding ribs are arranged corresponding to the pocket beam positions.

[0005] The beneficial effect of this design is that the upper edge is arranged axially, the lower edge is arranged radially, and the pocket is connected at an incline. This structure is adapted to the gravity direction under vertical working conditions, so that the cage rotates to form an upward grease guiding tendency. The outer and inner ribs extend from the upper edge to the lower edge and are arranged at an angle. During bearing operation, the surface of the outer rib forms a preset angle with respect to the outer diameter generatrix of the cage, i.e., the straight line tangent to the outer diameter profile of the cage. The surface of the inner rib also forms a preset angle with respect to the inner diameter generatrix of the cage. The range of these two angles is 2° to 20°. When the bearing operates in a vertical position, the grease that settles and accumulates below the rolling elements due to gravity will come into contact with the rotating cage. At this time, the inclined inner and outer ribs will act like pumping blades, and under the combined action of their inclined surfaces, they will generate an upward component force on the grease along the inclined surface. The direction of this component force is opposite to the direction of gravity, thereby actively pumping the grease from the bottom of the bearing back to the meshing area between the rolling elements and the inner and outer raceways, ensuring that the upper rolling elements can also be adequately lubricated, and avoiding failures such as temperature rise, peeling, and accelerated wear of the upper rolling elements due to insufficient lubrication. The frustum-shaped profile provides a high degree of matching with the tapered roller raceway, resulting in smoother rolling element operation and significantly improved radial and axial positioning accuracy, while reducing frictional losses between the cage and rolling elements, as well as between the inner and outer rings. The pocket beam and raised ribs work together to enhance the cage's structural strength, reducing the risk of deformation under high-speed operation and extending the cage's service life. This design eliminates the need for increased grease filling and maintenance frequency, achieving active grease return through pure structural optimization, significantly improving the operational stability and durability of vertical bearings and reducing equipment maintenance costs.

[0006] As a further feature of the present invention, the outer rib extends from the upper edge to the lower edge, and the inner rib extends from the upper edge to the lower edge.

[0007] The benefits of this design are: it can better guide the movement of oil, improve the performance of the structure, and at the same time, the structure is simple and the operation is stable. Pure structural optimization realizes the active return of grease, which greatly improves the operational stability and durability of vertical bearings and reduces equipment maintenance costs.

[0008] As a further feature of the present invention, the contact surface between the outer ring and the rolling element is inclined, the contact surface between the inner ring and the rolling element is inclined, and an oil guide groove is provided on the contact surface between the inner ring and the rolling element corresponding to the edge of the rolling element.

[0009] The beneficial effects of this design are as follows: By setting the contact surfaces of the inner and outer rings with the rolling elements to an inclined structure, and adding oil guide grooves to the inner ring contact surface, the lubrication and load-bearing performance of the vertical shaft bearing is further enhanced. The inclined contact surface fully conforms to the conical surface of the tapered rollers, increasing the contact area and allowing the bearing to simultaneously withstand greater radial and axial loads. This makes it suitable for heavy-duty vertical equipment such as vertical motors and vertical pumps, improving the overall load-bearing capacity and operational safety of the bearing. The oil guide grooves on the inner ring are arranged along the edges of the rolling elements, forming directional lubrication channels during bearing rotation. This allows for the rapid collection of grease guided back by the cage and precise delivery to the critical meshing positions between the rolling elements and the inner ring raceway, eliminating lubrication dead zones and ensuring uniform lubrication along the entire circumference of the rolling elements. The oil guide grooves also reduce the frictional resistance between the rolling elements and the inner ring, reducing frictional heat generation, effectively controlling bearing temperature rise, and preventing problems such as grease failure and raceway softening due to high temperatures. The inclined contact surface combined with the oil guide grooves ensures smoother grease flow, reducing grease retention and clumping, and improving grease utilization. This structure is simple and easy to manufacture, does not change the overall installation dimensions of the bearing, and can directly replace traditional double-row tapered roller bearings. It has strong versatility and significantly improves the lubrication effect and load-bearing reliability of vertical bearings without increasing costs.

[0010] As a further feature of the present invention, an oil baffle ring is provided between the inner ring and the outer ring. The oil baffle ring is disposed between two raceways. The oil baffle ring is provided with a first baffle wall and a second baffle wall. The first baffle wall abuts against the inner peripheral wall of the outer ring, and the second baffle wall abuts against the outer peripheral wall of the inner ring. An abutting groove is provided on the outer peripheral wall of the inner ring corresponding to the position of the second baffle wall, and the second baffle wall is fitted into the abutting groove.

[0011] The beneficial effects of this design are as follows: The oil retainer ring divides the internal space of the bearing into two independent lubrication chambers, with each row of rolling elements corresponding to a dedicated lubrication area. This prevents grease from flowing from one row of bearings to the other due to gravity or pressure differences, ensuring a stable and sufficient lubrication supply to both raceways and preventing malfunctions caused by insufficient lubrication on one side. The first retainer wall tightly abuts against the inner circumferential wall of the outer ring, while the second retainer wall, in conjunction with the inner ring's contact groove, forms a double seal, blocking the axial flow path of the grease and preventing external impurities from entering the bearing. The fitting structure of the second retainer wall and the contact groove improves the installation and positioning accuracy of the oil retainer ring, preventing radial movement during operation and ensuring long-term stable operation. This oil retainer ring structure does not directly contact the rotating inner ring, resulting in no additional frictional loss, no increase in bearing operating resistance, and no impact on bearing speed or efficiency. The contact groove design also enhances the local structural strength of the inner ring, improving the overall rigidity of the bearing. By physically isolating the lubrication space of the double rows, the crossflow problem is solved at its source. Combined with the cage oil guide structure, synchronous and stable lubrication of the double row bearings is achieved, which greatly extends the service life of the bearings and improves the continuous operation capability of vertical equipment.

[0012] As a further feature of the present invention, a shallow groove is provided on the outer peripheral wall of the outer ring corresponding to the position of the oil baffle ring.

[0013] The advantages of this design are as follows: The circumferential groove structure formed by the shallow groove serves as a gripping force point, providing operators with a stable gripping area during bearing handling, pressing, and assembly. This effectively prevents outer ring slippage, improves the safety and controllability of assembly operations, and is particularly suitable for automated production lines and manual assembly scenarios, significantly reducing the risk of assembly damage. Simultaneously, without weakening the outer ring structural strength and raceway precision, the shallow groove removes excess material, achieving a lightweight outer ring structure, reducing the overall weight of the bearing, decreasing equipment operating load and energy consumption, and making it more suitable for equipment scenarios requiring lightweighting, such as vertical motors and vertical pumps. The shallow groove processing technology is simple and low-cost, and does not affect the bearing's core performance characteristics of sealing, lubrication, and load-bearing capacity.

[0014] As a further feature of the present invention, a sealing ring is provided between the inner ring edge and the outer ring edge. The sealing ring includes a skeleton and a sealing lip. One end of the skeleton is connected to the inner peripheral wall of the outer ring, and the other end of the skeleton is connected to the sealing lip. The sealing lip abuts against the outer peripheral wall of the inner ring.

[0015] The beneficial effects of this design are as follows: The sealing ring employs a composite structure of a skeleton and a sealing lip. One end of the skeleton is fixed to the inner circumference of the outer ring, providing stable support and preventing the sealing ring from detaching or shifting under high pressure, vibration, and high-speed operation, thus ensuring the long-term stability of the sealing structure. The sealing lip elastically contacts the outer circumference of the inner ring, forming a dynamic sealing pair that adaptively conforms to the rotation of the inner ring. This effectively prevents internal grease leakage, avoiding lubrication failure due to grease loss, and also blocks external contaminants such as dust, moisture, and debris from entering the bearing, preventing impurities from causing wear and jamming of the raceways and rolling elements. The skeleton enhances the overall rigidity of the sealing ring, while the sealing lip ensures sealing elasticity and wear resistance, making it suitable for the long-term continuous operation of vertical bearings. It exhibits excellent oil resistance, temperature resistance, and aging resistance. This sealing ring is installed on the edge of the bearing, without occupying internal lubrication space or affecting grease flow or the cage's oil guiding effect. Together with the oil retainer ring, oil guide groove, and rib structure, it forms a comprehensive sealing and lubrication system. The contact seal between the sealing lip and the inner ring results in low frictional resistance, does not increase bearing operating power consumption, and improves transmission efficiency. Reliable sealing extends the service life of grease and the maintenance cycle of bearings, reduces equipment downtime maintenance costs, and ensures the safe, stable, and long-term operation of vertical equipment.

[0016] As a further feature of the present invention, both the inner and outer convex ribs are provided in segments.

[0017] The beneficial effects of this design are as follows: By arranging the inner and outer ribs in a segmented structure, the oil churning resistance generated by the cage during high-speed rotation can be effectively reduced, thereby reducing bearing operating power consumption and temperature rise. The segmented structure can improve the stress distribution at the root of the ribs, reduce stress concentration, improve the cage's fatigue and deformation resistance, and extend its service life. At the same time, the segmented ribs can form multi-stage grease guidance, preventing grease from forming a continuous thick film on the rib surface and remaining there, making the grease distribution more uniform and the return flow smoother, further improving the lubrication stability and operational reliability of the vertical bearing. Attached Figure Description

[0018] Figure 1 This is a partial cross-sectional structural diagram of the first embodiment of the present invention; Figure 2 This is a schematic diagram of the cage structure in the first embodiment of the present invention; Figure 3 This is a perspective view of the first embodiment of the present invention; Figure 4 This is a schematic cross-sectional view of the oil baffle ring in the first embodiment of the present invention; Figure 5 This is a schematic diagram of the cage structure in the second embodiment of the present invention. Detailed Implementation

[0019] A first embodiment of the present invention for a bearing for a vertical shaft, for example Figures 1 to 4As shown: The ring includes an outer ring 1 and an inner ring 2. Two raceways are provided between the outer ring 1 and the inner ring 2. A cage 3 is provided in each raceway, and rolling elements 4 are assembled in the cage 3. The cage 3 has a frustum-shaped profile and includes an upper edge 31, a pocket 32, and a lower edge 33. The upper edge 31 is closer to the edge of the outer ring 1 than the lower edge 33. The upper edge 31 is arranged along the axial direction of the outer ring 1, and the lower edge 33 is arranged along the radial direction of the outer ring 1. The pocket portion 32 is obliquely connected between the upper edge portion 31 and the lower edge portion 33. The pocket portion 32 has several pockets, and a pocket beam is formed between adjacent pockets. Several outwardly protruding ribs 34 are obliquely arranged on the outer peripheral wall of the retainer 3, extending from the edge of the upper edge portion 31 to the edge of the lower edge portion 33. Several inwardly protruding ribs 35 are obliquely arranged on the inner peripheral wall of the retainer 3, extending from the edge of the upper edge portion 31 to the edge of the lower edge portion 33. The beneficial effect of this arrangement is that, with the upper edge portion 31 arranged axially and the lower edge portion 33 arranged radially, and the pocket portion 32 obliquely connected, the structure is highly compatible with the direction of gravity under vertical working conditions, causing the retainer 3 to form an upward grease-guiding tendency when rotating. The outer rib 34 and the inner rib 35 extend from the upper edge 31 to the lower edge 33 and are arranged at an angle. During bearing operation, the surface of the outer rib 34 forms a preset angle with respect to the outer diameter generatrix of the cage 3, i.e., the straight line tangent to the outer diameter profile of the cage 3. The surface of the inner rib 35 also forms a preset angle with respect to the inner diameter generatrix of the cage 3. The range of these two angles is 2° to 20°. When the bearing operates in a vertical position, the ribs that settle and accumulate below the rolling elements 4 due to gravity... The grease comes into contact with the rotating cage 3. At this time, the inclined inner ribs 35 and outer ribs 34 act like pumping blades, generating an upward component force on the grease under the combined action of their inclined surfaces. This component force is opposite to the direction of gravity, thus actively pumping the grease from the bottom of the bearing back to the meshing area of ​​the rolling elements 4 and the inner and outer rings 1 raceways. This ensures that the upper rolling elements 4 also receive sufficient lubrication, preventing failures such as overheating, peeling, and accelerated wear due to insufficient lubrication. The frustum-shaped profile has a high matching degree with the tapered roller raceways, resulting in smoother operation of the rolling elements 4 and significantly improved radial and axial positioning accuracy, reducing frictional losses between the cage 3 and the rolling elements 4, as well as the inner and outer rings 1. The pocket beam and ribs work together to enhance the structural strength of the cage 3, reducing the risk of deformation under high-speed operation and extending the service life of the cage 3. This design does not require increasing the amount of grease filling or maintenance frequency. It achieves active grease return through pure structural optimization, significantly improving the operational stability and durability of the vertical bearing and reducing equipment operation and maintenance costs.

[0020] As a further feature of this embodiment, the contact surface between the outer ring 1 and the rolling element 4 is inclined, and the contact surface between the inner ring 2 and the rolling element 4 is also inclined. An oil guide groove 21 is provided on the contact surface between the inner ring 2 and the rolling element 4 corresponding to the edge of the rolling element 4. The beneficial effects of this configuration are: by setting the contact surfaces between the inner and outer rings 1 and the rolling element 4 to an inclined structure, and adding an oil guide groove 21 to the contact surface of the inner ring 2, the lubrication and load-bearing performance of the vertical shaft bearing is further enhanced. The inclined contact surface fully conforms to the conical surface of the tapered roller, increasing the contact area and allowing the bearing to simultaneously withstand larger radial and axial loads. This makes it suitable for heavy-duty vertical equipment such as vertical motors and vertical pumps, improving the overall load-bearing capacity and operational safety of the bearing. The oil guide groove 21 on the inner ring 2 is arranged corresponding to the edge of the rolling element 4, forming a directional lubrication channel when the bearing rotates. This allows for rapid collection of the grease guided back by the cage 3 and precise delivery to the key meshing positions between the rolling element 4 and the raceway of the inner ring 2, eliminating lubrication dead zones and ensuring uniform lubrication along the entire circumference of the rolling element 4. The oil guide groove 21 also reduces the frictional resistance between the rolling element 4 and the inner ring 2, reduces frictional heat generation, effectively controls the bearing temperature rise, and avoids problems such as grease failure and raceway softening caused by high temperature annealing. The inclined contact surface combined with the oil guide groove 21 makes the grease flow more smoothly, reduces grease retention and clumping, and improves grease utilization. This structure is simple and easy to process, does not change the overall bearing installation dimensions, and can directly replace traditional double-row tapered roller bearings. It has strong versatility and significantly improves the lubrication effect and load-bearing reliability of vertical bearings without increasing costs.

[0021] As a further provision of this embodiment, an oil baffle ring 5 is also provided between the inner ring 2 and the outer ring 1. The oil baffle ring 5 is disposed between the two raceways, and the oil baffle ring 5 is provided with a first baffle wall 51 and a second baffle wall 52. The first baffle wall 51 abuts against the inner circumferential wall of the outer ring, and the second baffle wall 52 abuts against the outer circumferential wall of the inner ring 2. A contact groove is provided on the outer circumferential wall of the inner ring 2 corresponding to the position of the second baffle wall 52, and the second baffle wall 52 is fitted into the contact groove. The beneficial effect of this configuration is that the oil baffle ring 5 divides the internal space of the bearing into two independent lubrication chambers, with each row of rolling elements 4 corresponding to a dedicated lubrication area. This prevents the grease in one row of bearings from flowing to the other row due to gravity or pressure difference, ensuring that both rows of raceways can obtain a stable and sufficient lubrication supply, and preventing failure caused by insufficient lubrication on one side. The first baffle wall 51 tightly abuts against the inner circumferential wall of the outer ring 1, and the second baffle wall 52 cooperates with the contact groove of the inner ring 2 to form a double sealing barrier, blocking the axial flow path of the grease, and at the same time preventing external impurities from entering the bearing. The fitting structure of the second baffle 52 and the contact groove improves the installation and positioning accuracy of the oil baffle ring 5, prevents radial movement during operation, and ensures long-term stable operation of the oil baffle ring 5. This oil baffle ring 5 structure does not directly contact the rotating inner ring 2, resulting in no additional frictional loss, no increase in bearing operating resistance, and no impact on bearing speed or efficiency. The contact groove design also enhances the local structural strength of the inner ring 2, improving the overall rigidity of the bearing. By physically isolating the double-row lubrication space, the crossflow problem is solved at its source. Combined with the oil guiding structure of the cage 3, synchronous and stable lubrication of the double-row bearings is achieved, significantly extending bearing service life and improving the continuous operation capability of vertical equipment.

[0022] As a further feature of this embodiment, a shallow groove 11 is provided on the outer peripheral wall of the outer ring 1 corresponding to the position of the oil baffle ring 5. The advantages of this design are: the circumferential groove structure formed by the shallow groove 11 can serve as a gripping force point, providing a stable gripping area for operators during bearing handling, pressing, and assembly, effectively preventing slippage of the outer ring 1, improving the safety and controllability of assembly operations, and is particularly suitable for automated production lines and manual assembly scenarios, significantly reducing the risk of assembly damage. Simultaneously, the shallow groove 11 removes excess material without weakening the structural strength and raceway precision of the outer ring 1, achieving a lightweight structure for the outer ring 1, reducing the overall weight of the bearing, decreasing equipment operating load and energy consumption, and making it more suitable for equipment scenarios requiring lightweighting, such as vertical motors and vertical pumps. The shallow groove 11 has a simple processing technology and low cost, and does not affect the bearing's core performance of sealing, lubrication, and load-bearing capacity.

[0023] As a further provision of this embodiment, a sealing ring 6 is provided between the edge of the inner ring 2 and the edge of the outer ring 1. The sealing ring 6 includes a skeleton 61 and a sealing lip 62. One end of the skeleton 61 is connected to the inner peripheral wall of the outer ring 1, and the other end of the skeleton 61 is connected to the sealing lip 62. The sealing lip 62 abuts against the outer peripheral wall of the inner ring 2. The beneficial effects of this configuration are: with this configuration, the sealing ring adopts a composite structure of skeleton 61 and sealing lip 62. One end of the skeleton 61 is fixed to the inner peripheral wall of the outer ring 1, providing stable support and preventing the sealing ring 6 from falling off or shifting under high pressure, vibration, and high-speed operation, thus ensuring the long-term stability of the sealing structure. The sealing lip 62 elastically abuts against the outer peripheral wall of the inner ring 2, forming a dynamic sealing pair. It adaptively fits with the rotation of the inner ring 2, which can effectively prevent the leakage of internal grease and prevent grease loss leading to lubrication failure. It can also prevent external dust, water vapor, debris, and other contaminants from entering the bearing, avoiding impurities from causing wear and jamming of the raceway and rolling elements 4. The skeleton 61 enhances the overall rigidity of the sealing ring 6, while the sealing lip 62 ensures sealing elasticity and wear resistance, making it suitable for the long-term continuous operation of vertical bearings. It exhibits excellent oil resistance, temperature resistance, and aging resistance. The sealing ring 6 is installed on the bearing edge, without occupying internal lubrication space or affecting grease flow or the oil guiding effect of the cage 3. Together with the oil retainer ring 5, oil guide groove 21, and rib structure, it forms a comprehensive sealing and lubrication system. The contact seal between the sealing lip 62 and the inner ring 2 results in low frictional resistance, does not increase bearing operating power consumption, and improves transmission efficiency. Through reliable sealing, it extends the service life of the grease and the bearing maintenance cycle, reduces equipment downtime maintenance costs, and ensures the safe, stable, and long-term operation of vertical equipment.

[0024] The cage structure of the second embodiment of the bearing for vertical shafts of the present invention is as follows: Figure 5 As shown: The retainer 3 includes an upper edge 31, a pocket portion 32, and a lower edge 33. The upper edge 31 is positioned closer to the edge of the outer ring 1 than the lower edge 33. The upper edge 31 is arranged along the axial direction of the outer ring 1, and the lower edge 33 is arranged along the radial direction of the outer ring 1. The pocket portion 32 is obliquely connected between the upper edge 31 and the lower edge 33. The pocket portion 32 has several pockets, and a pocket beam is formed between adjacent pockets. Several outwardly protruding ribs 34 are obliquely arranged on the outer peripheral wall of the retainer 3, and several inwardly protruding ribs 35 are obliquely arranged on the inner peripheral wall of the retainer 3. The inwardly protruding ribs 35 and the outwardly protruding ribs 34 are arranged corresponding to the pocket beam positions. The inwardly protruding ribs 35 and the outwardly protruding ribs 34 are both segmented.

[0025] The above examples are merely one preferred embodiment of the present invention. Ordinary variations and substitutions made by those skilled in the art within the scope of the technical solution of the present invention are all included within the protection scope of the present invention.

Claims

1. A bearing for a vertical shaft, comprising an outer ring and an inner ring, wherein two rows of raceways are provided between the outer ring and the inner ring, and a cage is respectively provided in each raceway, wherein rolling elements are assembled in the cage, characterized in that: The retainer has a frustum-shaped profile and includes an upper edge, a pocket portion, and a lower edge. The upper edge is closer to the outer edge of the outer ring than the lower edge. The upper edge is arranged along the axial direction of the outer ring, and the lower edge is arranged along the radial direction of the outer ring. The pocket portion is obliquely connected between the upper edge and the lower edge. The pocket portion has a plurality of pockets and a pocket beam is formed between adjacent pockets. The outer peripheral wall of the retainer has a plurality of outwardly protruding ribs, and the inner peripheral wall of the retainer has a plurality of inwardly protruding ribs. The inwardly and outwardly protruding ribs are arranged corresponding to the pocket beam positions.

2. The bearing for a vertical shaft according to claim 1, characterized in that: The outer rib extends from the upper edge to the lower edge, and the inner rib extends from the upper edge to the lower edge.

3. The bearing for a vertical shaft according to claim 2, characterized in that: The contact surface between the outer ring and the rolling element is inclined, and the contact surface between the inner ring and the rolling element is also inclined. An oil guide groove is provided on the contact surface between the inner ring and the rolling element corresponding to the edge of the rolling element.

4. The bearing for a vertical shaft according to claim 3, characterized in that: An oil baffle ring is also provided between the inner ring and the outer ring. The oil baffle ring is located between two raceways. The oil baffle ring is provided with a first baffle wall and a second baffle wall. The first baffle wall abuts against the inner circumferential wall of the outer ring, and the second baffle wall abuts against the outer circumferential wall of the inner ring. A contact groove is provided on the outer circumferential wall of the inner ring corresponding to the position of the second baffle wall, and the second baffle wall is fitted into the contact groove.

5. The bearing for a vertical shaft according to claim 4, characterized in that: A shallow groove is provided on the outer peripheral wall of the outer ring corresponding to the position of the oil baffle ring.

6. The bearing for a vertical shaft according to claim 1, characterized in that: A sealing ring is also provided between the inner ring edge and the outer ring edge. The sealing ring includes a skeleton and a sealing lip. One end of the skeleton is connected to the inner peripheral wall of the outer ring, and the other end of the skeleton is connected to the sealing lip. The sealing lip abuts against the outer peripheral wall of the inner ring.

7. The bearing for a vertical shaft according to claim 1, characterized in that: Both the inner and outer ribs are provided in segments.

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