New energy rolling bearing

Abstract

This utility model discloses a new energy rolling bearing, including an inner ring and an outer ring. The bearing has an open single-row deep groove ball bearing structure. The outer raceway of the inner ring has left-handed and right-handed helical oil guide grooves with opposite rotation directions on both sides. The connection points between the left-handed and right-handed helical oil guide grooves and the outer raceway of the inner ring are each provided with an oil collecting bevel with an inclination angle of 15°. A non-load-bearing zone is provided between the left-handed and right-handed helical oil guide grooves and the oil collecting bevel, and between the right-handed and right-handed helical oil guide grooves and the oil collecting bevel. Chip removal grooves are provided on the non-load-bearing zones of the raceways, and these grooves are connected to the helical oil guide grooves on both sides. The outer ring has planar reference end faces at both ends, and a streamlined arc transition surface is provided at the junction of the two ends of the outer ring and the reference end faces. Several axial straight guide shallow grooves are provided on both sides of the outer ring raceway. This utility model can reduce oil churning loss, has self-cleaning chip removal capability, and effectively improves the bearing's service life and the operating efficiency of the electric drive system.

Description

Technical Field

[0001] This utility model relates to the field of bearing technology, and more specifically, to a new energy rolling bearing. Background Technology

[0002] New energy vehicle electric drive gearboxes generally adopt an open splash oil lubrication structure. Compared with traditional transmission systems, their motor speed is significantly increased, and the operating conditions are characterized by high speed, large alternating torque, and wide temperature range. Existing conventional rolling bearings have several technical defects under such operating conditions: at high speeds, the lubricating oil is easily detached from the raceway friction pair due to strong centrifugal force, leading to local dry friction, causing raceway pitting, galling, or even premature fracture; the outer ring of the bearing is mostly a right-angled cylindrical structure, which generates significant eddy current resistance during high-speed rotation, additionally increasing the power consumption of the electric drive system and reducing the overall vehicle range; metal shavings in the gearbox enter the bearing with the oil and are difficult to remove, accumulating over time to form three-body abrasive wear, accelerating bearing fatigue failure; some existing lubrication enhancement solutions require the addition of additional components such as oil reservoirs, pumping devices, or deflectors, which disrupts the original bearing installation dimension chain and cannot meet the stringent requirements of mass-produced vehicles for assembly cycle time and tolerance consistency. Currently, there is no integrated high-speed rolling bearing in the industry that requires no additional parts, is fully integrated into the bearing body, and has active oil supply, low oil churning loss, and self-chip removal functions. Its adaptability and reliability are difficult to meet the needs of actual applications. Utility Model Content

[0003] To address the shortcomings of existing technologies, the purpose of this utility model is to provide a new energy rolling bearing. By integrating oil guiding, resistance reduction, and chip removal structures into the inner and outer rings of the bearing, it solves the problems of insufficient oil supply, high oil churning loss, abrasive accumulation, and poor assembly compatibility in high-speed open lubrication conditions without changing the installation dimensions.

[0004] To achieve the above objectives, this utility model provides the following technical solution: a new energy rolling bearing, comprising an inner ring, an outer ring, rolling elements, and a cage. The bearing is an open single-row deep groove ball bearing structure. The outer raceway of the inner ring is provided with left-handed and right-handed helical oil guide grooves on both sides, each with opposite rotation directions. The left-handed and right-handed helical oil guide grooves are connected to the outer raceway of the inner ring with an oil collecting bevel at an inclination angle of 15°. A non-load-bearing zone is provided between the left-handed and right-handed helical oil guide grooves and between the right-handed and right-handed helical oil guide grooves. A chip removal groove is provided on the non-load-bearing zone of the raceway, and the chip removal groove is connected to the left-handed and right-handed helical oil guide grooves respectively. The outer ring has planar reference end faces at both ends, and a streamlined arc transition surface is provided at the junction of the two ends of the outer ring and the reference end faces. Several axially oriented shallow guide grooves are provided on both sides of the raceway of the outer ring.

[0005] Furthermore, the left-hand spiral oil guide groove and the right-hand spiral oil guide groove are shallow grooves with an arc bottom, a groove depth of 0.15mm-0.3mm, and a groove width of 0.8mm-1.2mm. They adopt a variable lead design, with a lead of 8mm-10mm on the side closer to the raceway and a lead of 12mm-15mm on the side farther from the raceway.

[0006] Furthermore, the depth of the chip removal groove is 0.05mm-0.1mm.

[0007] Furthermore, the outer ring streamlined arc transition surface has a radius of R1.5mm-R3mm, an axial straight guide shallow groove with a depth of 0.1mm-0.2mm, and 8-12 grooves are evenly distributed along the circumference of the outer ring raceway.

[0008] Furthermore, the outer ring reference end face flatness is ≤0.01mm, and both the inner and outer rings are made of GCr15 bearing steel with a hardness of HRC60-65 and a raceway surface roughness Ra≤0.02μm.

[0009] By adopting the above technical solutions, the following technical effects are achieved: The structural design of the inner ring's bidirectional reverse spiral oil guide groove can create a centrifugal pumping effect under high-speed rotation, actively delivering splashed lubricating oil to the raceway area, ensuring a continuous and sufficient oil film formation on the raceway, and effectively avoiding dry friction failure caused by high-speed insufficient oil; the streamlined arc transition surface of the outer ring can eliminate the eddy current resistance of right-angled edges, significantly reducing oil churning power consumption and improving the energy efficiency of the electric drive system; the inner ring chip removal groove and the outer ring axial guide shallow groove cooperate to form a circulating oil path, which can drive abrasive particles out of the bearing with the oil, reducing abrasive wear and extending bearing service life; at the same time, it retains the standard planar reference end face and installation dimensions, allowing direct replacement of conventional bearings without additional parts, with strong assembly compatibility and suitability for mass production applications. Other improved structures can further enhance oil supply stability and chip removal effect, and improve bearing operating accuracy and structural reliability. Attached Figure Description

[0010] Figure 1 This is a schematic diagram of the overall structure of this utility model; Figure 2 This is a schematic diagram of the outer ring structure; Figure 3 This is a sectional view of the outer ring; Figure 4 Schematic diagram of the inner ring structure Figure 1 ; Figure 5 Schematic diagram of the inner ring structure Figure 2 ; Figure 6 for Figure 5 Enlarged view of point a in the middle.

[0011] 1. Inner ring; 2. Outer ring; 3. Rolling element; 4. Left-hand spiral oil guide groove; 5. Right-hand spiral oil guide groove; 6. Oil collecting bevel; 7. Chip removal groove; 8. Streamlined arc transition surface; 9. Axial straight guide shallow groove; 10. Reference end face. Detailed Implementation

[0012] Reference Figures 1 to 6 The embodiments of this utility model will be further described below.

[0013] The new energy rolling bearing of this embodiment includes an inner ring (1), an outer ring (2), rolling elements (3), and a cage. The bearing is an open single-row deep groove ball bearing. The outer raceway of the inner ring (1) is provided with a left-hand spiral oil guide groove (4) and a right-hand spiral oil guide groove (5) with opposite directions of rotation on both sides. The left-hand spiral oil guide groove (4) and the right-hand spiral oil guide groove (5) are provided with an oil collecting bevel (6) with an inclination angle of 15° at the connection between them and the outer raceway of the inner ring (1). The left-hand spiral oil guide groove (4) and the oil collecting bevel (6) are connected together. The outer ring (2) has a non-load-bearing zone between the right-hand spiral oil guide groove (5) and the oil collection groove (6). A chip removal groove (7) is provided on the non-load-bearing zone of the raceway. The chip removal groove (7) is connected to the left-hand spiral oil guide groove (4) and the right-hand spiral oil guide groove (5) respectively. The outer ring (2) has a planar reference end face (10) at both ends. The junction of the two ends of the outer ring (2) and the reference end face (10) is provided with a streamlined arc transition surface (8). Several axial straight flow shallow grooves (9) are provided on both sides of the raceway of the outer ring (2). During operation, the inner ring rotates synchronously at high speed with the gearbox shaft. The spiral oil guide grooves on both sides, rotating in opposite directions, generate axial pumping thrust as the inner ring rotates, actively transporting the lubricating oil splashed in the gearbox to the raceway area. After being collected by the oil collecting bevel, the oil precisely enters the raceway friction pair, continuously replenishing the raceway with lubricating oil and solving the problem of dry friction caused by the lubricating oil leaving the raceway due to centrifugal force under high-speed conditions. The streamlined arc transition surface of the outer ring's outer diameter optimizes the oil flow field, weakens the eddy current disturbance during rotation, reduces the energy loss caused by oil churning, and achieves the effect of drag reduction and efficiency improvement. The chip removal groove of the inner ring can accommodate metal abrasive particles that enter the bearing with the oil. Together with the axial straight guide shallow groove of the outer ring, it forms a complete oil flow path, driving the abrasive particles to flow out of the bearing with the oil and avoiding abrasive particle accumulation and wear. The reference end faces at both ends ensure the bearing installation positioning accuracy and are fully compatible with existing standard installation structures. They can be directly replaced without changing the assembly process.

[0014] Furthermore, the left-hand spiral oil guide groove (4) and the right-hand spiral oil guide groove (5) are shallow grooves with an arc bottom, a groove depth of 0.15mm-0.3mm, and a groove width of 0.8mm-1.2mm. They adopt a variable lead design, with a lead of 8mm-10mm on the side closer to the raceway and a lead of 12mm-15mm on the side farther from the raceway. The arc bottom shallow groove structure can reduce the oil flow resistance and reduce oil impact loss; the variable lead design makes it easier to capture splashed oil in the large lead section far from the raceway, increasing the oil intake, while the small lead section close to the raceway gradually increases the pumping pressure, accelerating the oil to the raceway, taking into account both the smoothness of oil intake and the pumping intensity, further improving the oil supply stability and oil film thickness, and ensuring the lubrication reliability under high-speed conditions.

[0015] Furthermore, the depth of the chip removal groove (7) is 0.05mm-0.1mm. This depth setting can effectively accommodate and guide metal abrasive particles with the flow of oil without affecting the bearing strength of the raceway, so that the abrasive particles can smoothly flow into the spiral oil guide grooves on both sides and then be discharged from the bearing, avoiding the abrasive particles from entering the bearing area of ​​the raceway and causing three-body wear, thus helping to improve the service life of the bearing.

[0016] Furthermore, the streamlined arc transition surface (8) of the outer ring (2) has a radius of R1.5mm-R3mm, and the axial straight guide shallow groove (9) has a groove depth of 0.1mm-0.2mm, with 8-12 grooves evenly distributed along the circumference of the raceway of the outer ring (2). The arc transition surface of the appropriate size can maximize the reduction of the oil turbulence caused by the right-angle edge, further reducing the oil turbulence power consumption; the guide shallow grooves evenly distributed in the circumference can evenly guide the axial flow of the oil, improve the smoothness of the chip removal passage, and allow the abrasive particles to be quickly discharged from the bearing with the oil, thus enhancing the self-cleaning effect.

[0017] Furthermore, the flatness of the outer ring (2) reference end face (10) is ≤0.01mm, and both the inner ring (1) and the outer ring (2) are made of GCr15 bearing steel with a hardness of HRC60-65 and a raceway surface roughness Ra≤0.02μm. The high-precision reference end face can ensure the axial positioning accuracy after the bearing is press-fitted, and improve the running stability of the shaft system; the bearing steel material and ultra-precision raceway can ensure the structural strength and running accuracy of the bearing, and further improve the service life and running reliability of the bearing.

[0018] In summary, this utility model adopts an integrated bearing body structure design, achieving active pumping oil supply through the inner ring's bidirectional spiral oil guide and oil collection bevel structure, reducing oil churning loss through the outer ring's streamlined transition structure, and achieving self-chip removal function through the oil circuit structure of the inner and outer rings. At the same time, it retains a standard installation interface, effectively solving the problems of bearing failure due to insufficient oil, high energy consumption, rapid abrasive wear, and poor assembly compatibility under high-speed open lubrication conditions in new energy gearboxes. It achieves the technical effects of stable oil supply, low operating consumption, self-cleaning, and immediate use. The overall structure is simple and reliable, and it is suitable for mass production application requirements.

[0019] The above description is merely a preferred embodiment of this utility model. The protection scope of this utility model is not limited to the above embodiments. All technical solutions falling within the scope of this utility model's concept are protected by this utility model. It should be noted that for those skilled in the art, any improvements and modifications made without departing from the principle of this utility model should also be considered within the protection scope of this utility model.

Claims

1. A new energy rolling bearing, comprising an inner ring, an outer ring, rolling elements, and a cage, characterized in that: The bearing is an open single-row deep groove ball bearing. The inner ring outer raceway has left-handed and right-handed spiral oil guide grooves with opposite rotation directions on both sides. The connection points between the left-handed and right-handed spiral oil guide grooves and the inner ring outer raceway are each provided with an oil collecting bevel at an inclination angle of 15°. A non-load-bearing zone is provided between the left-handed spiral oil guide groove and the oil collecting bevel, and between the right-handed spiral oil guide groove and the oil collecting bevel. Chip removal grooves are provided on the non-load-bearing zone of the raceway, and these grooves are connected to the left-handed and right-handed spiral oil guide grooves respectively. The outer ring has planar reference end faces at both ends, and a streamlined arc transition surface is provided at the junction of the two ends of the outer ring and the reference end faces. Several axial straight guide shallow grooves are provided on both sides of the outer ring raceway.

2. The new energy rolling bearing according to claim 1, characterized in that: The left-hand spiral oil guide groove and the right-hand spiral oil guide groove are shallow grooves with an arc bottom, a groove depth of 0.15mm-0.3mm, and a groove width of 0.8mm-1.2mm. They adopt a variable lead design, with a lead of 8mm-10mm on the side closer to the raceway and a lead of 12mm-15mm on the side farther from the raceway.

3. The new energy rolling bearing according to claim 1, characterized in that: The depth of the chip removal groove is 0.05mm-0.1mm.

4. The new energy rolling bearing according to claim 1, characterized in that: The outer ring streamlined arc transition surface has a radius of R1.5mm-R3mm, and the axial straight guide shallow groove has a depth of 0.1mm-0.2mm, with 8-12 grooves evenly distributed along the circumference of the outer ring raceway.

5. The new energy rolling bearing according to claim 1, characterized in that: The outer ring reference end face flatness is ≤0.01mm, and both the inner and outer rings are made of GCr15 bearing steel with a hardness of HRC60-65 and a raceway surface roughness Ra≤0.02μm.

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