Multi-cavity oil storage bearing

Abstract

The utility model relates to the technical field of range extenders, in particular to a multi-cavity oil storage bearing. Comprising a bearing body, an annular main oil storage groove is formed in the middle of the outer wall of the bearing body and communicates with the inner wall of the bearing body through a plurality of flow guide holes evenly formed in the radial direction, and a first auxiliary oil storage groove and a second auxiliary oil storage groove communicating with the flow guide holes are formed in the two sides of the flow guide holes correspondingly; the first auxiliary oil storage tank and the second auxiliary oil storage tank are arranged in the bearing body and axially extend along the bearing body, and a plurality of first end surface oil storage tanks and a plurality of second end surface oil storage tanks are circumferentially distributed at two ends of the bearing body; the first end face oil storage groove and the second end face oil storage groove communicate with the flow guide hole through the first auxiliary oil storage groove and the second auxiliary oil storage groove correspondingly. Lubricating oil is driven to dynamically circulate among the cavities through centrifugal force, an adhesive oil film is formed during shutdown, the lubricating oil is released instantly during starting, lubrication is maintained for more than 30 seconds in an oil shortage state, and the lubrication duration is prolonged by more than 5 times compared with that of a traditional bearing.

Description

Technical Field

[0001] This utility model relates to the field of range extender technology, specifically to a multi-chamber oil reservoir bearing. Background Technology

[0002] Turbochargers are required in range-extended electric vehicles (REEVs). As the core boosting component of the generator, the turbocharger's bearings operate in harsh environments, with temperatures exceeding 930°C and speeds reaching over 200,000 rpm. These extreme conditions place high demands on bearing lubrication. Especially since REEVs typically use charging for power and only activate the generator when the battery is low, the turbocharger needs to operate. However, the interval between two consecutive turbocharger operations is usually more than 30 days. During such a long interval, the lubricating oil in the lubrication system may have flowed back due to gravity, leading to lubrication system failure. This lubrication failure causes dry friction in the bearings due to direct metal-to-metal contact, a significant technical challenge affecting turbocharger reliability. Therefore, this paper proposes a bearing specifically designed for REEVs that can solve the dry friction problem caused by prolonged periods of inactivity in turbochargers. Utility Model Content

[0003] The problem to be solved is to provide bearings that can resolve the dry friction problem caused by prolonged disuse of turbochargers.

[0004] To achieve the above objectives, this utility model provides the following technical solution: a multi-chamber oil reservoir bearing, comprising a bearing body, an annular main oil reservoir in the middle of the outer wall of the bearing body, the annular main oil reservoir being connected to the inner wall of the bearing body through a plurality of radially uniformly arranged guide holes, a first auxiliary oil reservoir and a second auxiliary oil reservoir being respectively provided on both sides of the guide holes and connected to the guide holes, the first auxiliary oil reservoir and the second auxiliary oil reservoir being disposed in the bearing body and extending along the axial direction of the bearing body, a plurality of first end face oil reservoirs and a plurality of second end face oil reservoirs being circumferentially distributed at both ends of the bearing body; the first end face oil reservoirs and the second end face oil reservoirs being connected to the guide holes through the first auxiliary oil reservoirs and the second auxiliary oil reservoirs respectively.

[0005] Preferably, the diameter of the guide hole is 0.5 to 1.5 mm.

[0006] Preferably, the first and second end face oil storage tanks are fan-shaped grooves, with 4 to 6 evenly distributed around the circumference, and each groove has a volume of 0.1 to 0.5 cm³. 3 .

[0007] Preferably, the inner diameter of the first auxiliary oil storage tank and the second auxiliary oil storage tank is 0.2 to 0.5 mm.

[0008] Preferably, the first auxiliary oil storage tank and the second auxiliary oil storage tank are arranged along the same axis, and the axis radially penetrates the guide hole.

[0009] Compared with existing technologies, this utility model provides a multi-chamber oil reservoir bearing with the following advantages: Lubricating oil is driven by centrifugal force to circulate between the annular main oil reservoir, guide hole, auxiliary oil reservoir, and end face oil reservoir, rapidly forming an oil film upon startup after shutdown. The structure of the auxiliary oil reservoir and end face oil reservoir allows for 1.5 times the oil storage capacity of traditional designs during shutdown, with a measured oil film thickness ≥2μm, maintaining lubrication even in the absence of oil for more than 30 seconds, thus extending the bearing's service life. Attached Figure Description

[0010] Figure 1 This is a schematic diagram of a bearing structure in the prior art;

[0011] Figure 2 This is a schematic diagram of the left end face structure of the bearing of this utility model;

[0012] Figure 3 This is a schematic diagram of the right end face structure of the bearing of this utility model;

[0013] Figure 4 for Figure 2 A schematic diagram of the cross-sectional structure in the middle;

[0014] Figure 5 This is a schematic diagram of the bearing lubrication process of this utility model;

[0015] Explanation of reference numerals in the attached drawings: 1. Bearing body; 2. Annular main oil reservoir; 3. Guide hole; 4. First auxiliary oil reservoir; 5. Second auxiliary oil reservoir; 6. First end face oil reservoir; 7. Second end face oil reservoir. Detailed Implementation

[0016] The technical solutions of the present utility model will now be described with reference to the accompanying drawings in the embodiments of the present utility model:

[0017] like Figure 1The image shows a bearing used in a turbocharger of a range-extended electric vehicle (REEV). It includes an annular main oil reservoir 2 and guide holes 3. The annular main oil reservoir 2 distributes lubricating oil to the inner and outer surfaces of the bearing body 1 through the guide holes 3, forming an oil film. As described in the background section, when the turbocharger is restarted after a long interval, the lubricating oil in the lubrication system flows back due to gravity, causing lubrication system failure and dry friction. To solve the above problem, this invention provides a multi-chamber oil reservoir bearing, including a bearing body 1. An annular main oil reservoir 2 is provided in the middle of the outer wall of the bearing body 1. The annular main oil reservoir 2 is connected to the inner wall of the bearing body 1 through a plurality of radially uniformly arranged guide holes 3. The diameter of the guide holes 3 is preferably 0.5–1.5 mm. A first auxiliary oil reservoir 4 and a second auxiliary oil reservoir 5 are respectively provided on both sides of the guide holes 3, communicating with the guide holes 3. The first auxiliary oil reservoir 4 and the second auxiliary oil reservoir 5 are arranged coaxially, with the axis radially penetrating the guide holes 3. The inner diameter of the first auxiliary oil reservoir 4 and the second auxiliary oil reservoir 5 is 0.2–0.5 mm. The first auxiliary oil reservoir 4 and the second auxiliary oil reservoir 5 are disposed inside the bearing body 1 and extend along the axial direction of the bearing body 1. Multiple first end-face oil reservoirs 6 and multiple second end-face oil reservoirs 7 are circumferentially distributed at both ends of the bearing body 1. The first end-face oil reservoirs 6 and the second end-face oil reservoirs 7 are respectively connected to the guide hole 3 through the first auxiliary oil reservoir 4 and the second auxiliary oil reservoir 5. The first end-face oil reservoirs 6 and the second end-face oil reservoirs 7 are preferably fan-shaped grooves, with 4 to 6 evenly distributed circumferentially, and a single groove volume of 0.1 to 0.5 cm³. 3 .

[0018] like Figure 2-4 In the embodiment shown, an annular main oil reservoir 2 is provided on the outer wall of the bearing body 1. The depth of the annular main oil reservoir 2 is 0.2-0.6 mm, generally 0.4 mm. Six guide holes 3 are radially distributed in the middle of the bearing body 1, and the six guide holes 3 are connected to the annular main oil reservoir 2. A first auxiliary oil reservoir 4 and a second auxiliary oil reservoir 5 are provided through each guide hole 3 on both sides. The first auxiliary oil reservoir 4 and the second auxiliary oil reservoir 5 are coaxial and are both connected to the annular main oil reservoir 2 through the guide holes 3. The first auxiliary oil reservoir 4 and the second auxiliary oil reservoir 5 respectively penetrate through both ends of the bearing body 1 and are respectively connected to the first end face oil reservoir 6 and the second end face oil reservoir 7 on both end faces of the bearing body 1. The first end face oil reservoir 6 and the second end face oil reservoir 7 can realize the function of re-storing oil.

[0019] Six first end-face oil reservoirs 6 and second end-face oil reservoirs 7 are evenly distributed circumferentially at both ends of the bearing body 1. The first end-face oil reservoirs 6 and second end-face oil reservoirs 7 are preferably fan-shaped grooves. The first end-face oil reservoirs 6 and second end-face oil reservoirs 7 are naturally connected to the first auxiliary oil reservoir 4 and second auxiliary oil reservoir 5 at both ends of the bearing. Utilizing the centrifugal force of the rotating bearing body 1, the lubricating oil in the annular main oil reservoir 2 is thrown into the first auxiliary oil reservoir 4, second auxiliary oil reservoir 5, first end-face oil reservoir 6, and second end-face oil reservoir 7, forming a dynamic oil replenishment mechanism. When the machine is stopped, these auxiliary oil reservoirs and end-face oil reservoirs can store a certain amount of oil. Simultaneously, according to the characteristics of lubricating oil, a certain amount will adhere to their respective walls. When the turbocharger starts rotating, this lubricating oil will be thrown out by centrifugal force to initiate lubrication, preventing the turbocharger from operating without oil for a short period, avoiding dry friction, and extending the turbocharger's lifespan.

[0020] This invention enables the bearing body 1 to maintain lubrication for more than 30 seconds even when the oil supply is interrupted, which is more than 5 times longer than the traditional design. The oil storage volume of the bearing body 1 is increased to 1.5 times that of the traditional design.

[0021] like Figure 5 The diagram illustrates the lubrication process of this invention. After the engine is turned off and in a stopped state, the oil pump stops supplying oil, and the lubricating oil accumulates at a lower position on the bearing body 1 under gravity. The annular main oil reservoir 2 accumulates approximately 0.85 cm³ of oil. 3 This forms the core oil storage pool. The inner walls of the six first auxiliary oil storage tanks 4 and six second auxiliary oil storage tanks 5 form an adhesive oil film through capillary effect. The six first end-face oil storage tanks 6 and six second end-face oil storage tanks 7 store oil at a depth of 0.28 cm³ using a fan-shaped groove structure. 3 Upon restarting after a shutdown, the rotor's centrifugal force accelerates and activates, causing oil to be ejected from the guide hole 3, forming a bearing oil film. The oil reservoirs 6 and 7 on the first and second ends release stored oil for dynamic replenishment, ensuring the bearing body 1 is fully lubricated and providing operational assurance before the arrival of oil from the oil pump. Figure 1 A comparative test of the storage weight of lubricating oil in traditional bearings and bearings of this invention was conducted. (Test subjects)

[0022] (1) Traditional bearings: Lacking auxiliary oil reservoirs and end-face oil reservoirs, they only contain an annular main oil reservoir (approximately 1.25 cm³). 3 );

[0023] (2) Improved bearing (this utility model): includes an annular main oil reservoir + first / second auxiliary oil reservoir + first / second end face oil reservoir (total oil storage volume approximately 1.78 cm³). 3 (This is approximately 1.4 times that of traditional bearings).

[0024] 2. Experimental Procedure

[0025] 1) Oil immersion treatment: Immerse both types of bearings in Mobil 1 fully synthetic machine oil (SAE 5W-40) for 24 hours until saturated;

[0026] 2) Weighing after standing: After removing and draining for 1 minute, weigh using an analytical balance (0.1 mg precision) at 5, 10 and 30 days of standing, and record the residual weight of lubricating oil;

[0027] 3) Environmental control: The test environment temperature is 25±2℃ and the humidity is 50±5%. Avoid light and vibration interference.

[0028] 3. Experimental Data

[0029]

[0030] 4. Results Analysis

[0031] a. Auxiliary oil storage tank (inner diameter 0.2-0.5mm): Utilizes capillary effect to form an oil film adhesion, retaining approximately 41% of the initial oil volume after standing for 30 days;

[0032] b. End face oil reservoir (fan-shaped groove, single groove volume 0.1~0.5cm³) 3 The circumferential distribution design increases the oil film contact area and reduces oil backflow caused by gravity.

[0033] c. Traditional bearings rely solely on the annular main oil reservoir. After 30 days of standing, more than 80% of the oil is lost, mainly due to the lubricating oil flowing back along the inner wall of the bearing under the influence of gravity.

[0034] 5. Experimental Conclusions

[0035] The bearing of this utility model has a multi-chamber structure (annular main oil reservoir + auxiliary oil reservoir + end face oil reservoir), which significantly improves the lubricating oil storage capacity. After standing for 30 days, the residual oil amount is 3.4 times that of the traditional design. The improved bearing effectively inhibits the loss of lubricating oil after long-term shutdown through capillary effect and multi-chamber oil storage design, providing sufficient lubrication reserves for restarting.

[0036] II. Life Testing of Traditional and Improved Bearings

[0037] 1. Test subjects:

[0038] (1) One supercharger equipped with conventional bearings;

[0039] (2) One supercharger equipped with the bearing of this utility model;

[0040] 2. Experimental Procedure

[0041] 2.1 Oil Immersion Treatment: Immerse both turbochargers in Mobil 1 fully synthetic motor oil (SAE 5W-40) and soak for 24 hours until saturated.

[0042] 2.2 Settling: With the oil inlet of the turbocharger facing upwards and the oil return facing downwards, let it stand for 30 days;

[0043] 2.3 Experiment

[0044] After a 30-day settling period, first install the turbocharger with the conventional bearing onto the turbocharger test bench. Do not connect lubricating oil to the turbocharger's oil inlet. Then, directly blow high-pressure gas from the turbine inlet to the turbine speed of 60,000 r / min within 10 seconds. Then stop the gas supply and allow the turbocharger to stop naturally. Use the same method to install the turbocharger with the bearing of this invention onto the test bench. Disassemble and inspect both turbochargers to check the wear of the two types of floating bearings.

[0045]

[0046] In summary, the bearing of this utility model has a multi-chamber structure, which includes an annular main oil reservoir, an auxiliary oil reservoir, and an end-face oil reservoir. The annular main oil reservoir, the auxiliary oil reservoir, and the end-face oil reservoir are interconnected, which significantly improves the bearing's lubricating oil storage capacity and solves the dry friction problem caused by the long-term non-use of turbochargers in range-extended new energy vehicles.

[0047] The above embodiments are merely some, not all, of the embodiments of this utility model. All other embodiments obtained by those skilled in the art based on the embodiments of this utility model without inventive effort are within the scope of protection of this utility model.

Claims

1. A multi-chamber oil reservoir bearing, comprising a bearing body (1), wherein an annular main oil reservoir (2) is provided in the middle of the outer wall of the bearing body (1), and the annular main oil reservoir (2) is connected to the inner wall of the bearing body (1) through a plurality of radially uniformly arranged guide holes (3), characterized in that: The guide hole (3) is provided with a first auxiliary oil storage tank (4) and a second auxiliary oil storage tank (5) on both sides, which are connected to the guide hole (3). The first auxiliary oil storage tank (4) and the second auxiliary oil storage tank (5) are located inside the bearing body (1) and extend along the axial direction of the bearing body (1). Multiple first end face oil storage tanks (6) and multiple second end face oil storage tanks (7) are distributed circumferentially at both ends of the bearing body (1). The first end face oil storage tank (6) and the second end face oil storage tank (7) are connected to the guide hole (3) through the first auxiliary oil storage tank (4) and the second auxiliary oil storage tank (5), respectively.

2. The multi-chamber oil reservoir bearing of claim 1, wherein: The diameter of the guide hole (3) is 0.5 to 1.5 mm.

3. The multi-chamber oil reservoir bearing of claim 1 or 2, wherein: The first end face oil storage tank (6) and the second end face oil storage tank (7) are fan-shaped grooves, with 4 to 6 evenly distributed around the circumference, and the volume of a single groove is 0.1 to 0.5 cm³. 3 .

4. The multi-chamber oil reservoir bearing of claim 1 or 2, wherein: The inner diameter of the first auxiliary oil storage tank (4) and the second auxiliary oil storage tank (5) is 0.2 to 0.5 mm.

5. The multi-chamber oil reservoir bearing of claim 1, wherein: The first auxiliary oil storage tank (4) and the second auxiliary oil storage tank (5) are arranged on the same axis, and the axis radially passes through the guide hole (3).

Images