Combined bearing

Abstract

The utility model provides a combined bearing, including the outer ring and the inner race, the outer ring and the inner race between forming the first raceway and two second raceways of axial interval, the first raceway setting in the middle part, two second raceways are arranged respectively at the both sides of first raceway axial, the first raceway is full of a plurality of cylindrical rollers, the second raceway is provided with a plurality of ball rollers. In view of prior art's insufficient, the utility model provides a combined bearing can bear larger radial load, and can bear certain axial load.

Description

Technical Field

[0001] This utility model relates to the field of bearings, and in particular to a combined bearing. Background Technology

[0002] Bearings are crucial components used for rotating support in mechanical bodies. Their performance directly determines the operating accuracy, stability, and service life of equipment. Among them, cylindrical roller bearings, due to their line contact structure between the rollers and raceways, possess excellent radial load-bearing capacity, low friction coefficient, and low temperature rise during high-speed operation. They are widely used in transmission systems where radial loads are dominant. However, due to structural design limitations, the rollers and raceways of cylindrical roller bearings can only transmit radial force, which is not efficient. Therefore, in some scenarios where radial bearings are required to withstand axial loads, angular contact ball bearings are often used. Through the angular contact structure between the rollers and raceways, they can simultaneously withstand radial and axial loads. However, because the rollers and raceways of ball bearings are in point contact, their radial load-bearing capacity is much lower than that of cylindrical roller bearings, and they are prone to excessive contact stress under heavy-load conditions. Utility Model Content

[0003] In view of the shortcomings of the existing technology, this utility model provides a combined bearing that can withstand large radial loads and a certain axial load.

[0004] To achieve the above objectives, this utility model provides a combined bearing, including an outer ring and an inner ring, with a first raceway and two second raceways forming an axial gap between the outer ring and the inner ring. The first raceway is located in the middle, and the two second raceways are respectively located on both sides of the first raceway along the axial direction. The first raceway is fully filled with a plurality of cylindrical rollers, and the second raceways are filled with a plurality of ball rollers.

[0005] The advantages of the above technical solution are as follows: By axially spacing the first raceway in the middle and the second raceways on both sides, and then installing cylindrical rollers and ball rollers respectively, on the one hand, the cylindrical rollers fully loaded in the first raceway can give full play to their line contact bearing advantage, greatly improving the overall radial load bearing capacity of the bearing and meeting the radial support requirements under heavy load scenarios. On the other hand, the ball rollers on both sides can bear the axial load, realizing the synchronous and stable bearing of the composite load. On the other hand, by integrating the radial bearing structure and the axial bearing structure between the same outer ring and inner ring, there is no need to add multiple sets of bearings. This not only significantly simplifies the bearing assembly process of the equipment, but also greatly reduces the axial installation space, while avoiding the coaxiality deviation problem when multiple bearings are combined, thus improving the overall accuracy.

[0006] The present invention can be further configured such that: an annular groove is provided at the position of the outer ring corresponding to the first raceway, the inner walls on both sides of the annular groove abut against the two ends of the cylindrical roller respectively, and an oil groove is provided at the corner of the annular groove.

[0007] By further configuring the annular groove at the first raceway of the outer ring and the oil groove at the corner of the inner wall, on the one hand, the inner wall of the annular groove on both sides of the axial direction abuts against the end of the cylindrical roller, which can play an axial limiting role for the cylindrical roller. On the other hand, the oil groove at the corner of the inner wall of the annular groove can effectively store lubricating oil, ensuring the lubrication of the cylindrical roller and ensuring the reliability of the bearing operation.

[0008] The present invention can be further configured such that: the inner ring is provided with retaining edges on both sides corresponding to the axial direction of the first raceway, and the retaining edges are spaced apart from the cylindrical rollers.

[0009] By further configuring the flange, on the one hand, the flange can axially limit the cylindrical roller from the inner ring side, preventing the cylindrical roller from axially moving or leaving the raceway when it is running at high speed or under impact load. On the other hand, the spacing between the flange and the cylindrical roller can avoid direct contact between the two and generate additional friction, which also reduces friction loss and temperature rise, ensuring the overall service life of the bearing.

[0010] The present invention can be further configured such that: a retainer for spacing and guiding the ball rollers is provided at the second raceway, the retainer including an annular frame, a number of protrusions and a number of pockets, the number of protrusions being arranged at intervals along the frame and extending axially, and the pockets being formed by the protrusions at intervals.

[0011] By further refining the design, a retainer is installed at the second raceway, and the retainer is configured to have a frame, several protrusions, and several pockets. The protrusions are spaced apart to form pockets, which can ensure the guiding and spacing effects while occupying less space and avoiding interference.

[0012] The present invention can be further configured such that: the retainer includes an abutting portion located near the inner ring of the pocket, the abutting portion is semi-circular and extends from the end of one side of the protrusion to the end of the other side of the protrusion, and the cross-section of the abutting portion is tapered towards the end.

[0013] By further designing the contact section and making it tapered, the contact area between the contact section and the ball is reduced, thus lowering the frictional resistance between them. This prevents excessive heat generated by friction during high-speed operation, which could lead to abnormal temperature rise. Furthermore, the conical surface guides the lubricating oil to converge in the contact area between the ball and the raceway, enhancing the lubrication effect and solving the problem of insufficient lubrication in certain areas under high-speed conditions. Attached Figure Description

[0014] Figure 1 This is a perspective view of an embodiment of the present utility model; Figure 2This is a cross-sectional structural diagram of an embodiment of the present utility model; Figure 3 This is a schematic diagram of the inner ring structure in an embodiment of this utility model; Figure 4 This is a schematic diagram of the cage structure in an embodiment of the present invention; Wherein: outer ring 1; annular groove 11; oil groove 12; inner ring 2; flange 21; first raceway 3; second raceway 4; cylindrical roller 5; ball roller 6; cage 7; frame 71; protrusion 72; pocket 73; abutment 74. Detailed Implementation

[0015] An embodiment of this utility model of a combined bearing is shown below. Figure 1-4 As shown: It includes an outer ring 1 and an inner ring 2. The outer ring 1 and the inner ring 2 form an axially spaced first raceway 3 and two second raceways 4. The first raceway 3 is located in the middle, and the two second raceways 4 are respectively located on both sides of the first raceway 3 along the axial direction. The first raceway 3 is fully filled with a number of cylindrical rollers 5, and the second raceways 4 are provided with a number of ball rollers 6.

[0016] The outer ring 1 is provided with an annular groove 11 at the position corresponding to the first raceway 3. The inner walls of the annular groove 11 on both sides of the axis respectively abut against the two ends of the cylindrical roller 5, and an oil groove 12 is provided at the corner of the inner wall of the annular groove 11.

[0017] The inner ring 2 is provided with flanges 21 on both sides of the first raceway 3 along the axial direction, and the flanges 21 are spaced apart from the cylindrical rollers 5.

[0018] The second raceway 4 is provided with a retainer 7 for spacing and guiding the ball rollers 6. The retainer 7 includes an annular frame 71, a plurality of protrusions 72 and a plurality of pockets 73. The plurality of protrusions 72 are arranged at intervals along the frame 71 and extend axially, and the pockets 73 are formed at intervals by the protrusions 72.

[0019] The retainer 7 includes an abutment portion 74 located near the inner ring 2 in the pocket 73. The abutment portion 74 is semi-circular and extends from the end of one side protrusion 72 to the end of the other side protrusion 72. The cross-section of the abutment portion 74 is tapered towards the end.

[0020] The above examples are merely one preferred embodiment of this utility model. Ordinary variations and substitutions made by those skilled in the art within the scope of this utility model's technical solution are all included within the protection scope of this utility model.

Claims

1. A combined bearing, comprising an outer ring and an inner ring, characterized in that: The outer ring and the inner ring form an axially spaced first raceway and two second raceways. The first raceway is located in the middle, and the two second raceways are respectively located on both sides of the first raceway along the axial direction. The first raceway is fully filled with a number of cylindrical rollers, and the second raceways are filled with a number of ball rollers.

2. The combined bearing according to claim 1, characterized in that: The outer ring is provided with an annular groove at the position corresponding to the first raceway. The inner walls on both sides of the annular groove abut against the two ends of the cylindrical roller, and an oil groove is provided at the corner of the inner wall of the annular groove.

3. The combined bearing according to claim 2, characterized in that: The inner ring is provided with flanges on both sides corresponding to the axial direction of the first raceway, and the flanges are spaced apart from the cylindrical rollers.

4. The combined bearing according to claim 1, 2, or 3, characterized in that: The second raceway is provided with a retainer for spacing and guiding the ball rollers. The retainer includes an annular frame, several protrusions and several pockets. The protrusions are arranged at intervals along the frame and extend axially, and the pockets are formed by the protrusions at intervals.

5. The combined bearing according to claim 4, characterized in that: The retainer includes an abutment located near the inner ring of the pocket. The abutment is semi-circular and extends from the end of one protrusion to the end of the other protrusion. The cross-section of the abutment is tapered towards the end.

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