Bearing structure and pump device

Abstract

The utility model provides a bearing structure and pump equipment and relates to the technical field of bearings, the bearing structure comprises a bearing and an oil inlet structure, the bearing comprises a first bearing bush and a second bearing bush which can be buckled with each other, and a shaft hole is formed after the first bearing bush and the second bearing bush are buckled with each other; the oil inlet structure comprises a wear-resisting layer arranged on the inner wall of the shaft hole and a first oil inlet groove formed in the wear-resisting layer, and the depth of the first oil inlet groove is gradually increased from the two ends to the middle in the axial direction of the shaft hole. And the depth of the first oil inlet groove is gradually reduced from top to bottom in the circumferential direction of the shaft hole. The wear-resistant layer on the inner surface of the bearing bush is scraped in a specific shape and depth, so that an optimized oil inlet structure is formed, the supply efficiency of lubricating oil is remarkably improved, the lubricating effect and stability of an oil film are enhanced, the temperature rise of the bearing during working is effectively reduced, and the service life of the bearing is prolonged. And the supporting stability of the rotor and the safety and reliability of equipment operation are ensured.

Description

Technical Field

[0001] This utility model relates to the field of bearing technology, and in particular to a bearing structure and a pump device. Background Technology

[0002] During the operation of horizontal pumps, hydrodynamic radial sliding bearings are prone to excessive temperature rise due to high-speed rotor rotation and large shaft diameter, which directly affects the stability and service life of the pump equipment. Currently, two methods are commonly used in this field to address this issue: one is to perform point-like or point-line scraping on the inner surface of the bearing to increase oil storage and improve lubrication conditions; the other is to add a rectangular oil inlet groove structure to the inner surface of the bearing and change the lubrication method to forced lubrication, such as by setting an oil inlet hole to connect to an external oil station system. However, these existing technologies have certain limitations. While point-like or point-line scraping can improve lubrication to some extent, the limited oil storage area means that its effect on improving temperature rise is not significant for high-speed, large-diameter rotors. Furthermore, it requires a high level of operator skill and makes it difficult to ensure consistent scraping. Adding a rectangular oil inlet groove may reduce the effective support area of ​​the rotor, thus affecting rotor stability and even causing abnormal vibration. Forced lubrication requires an additional oil station system, which not only increases equipment cost and maintenance difficulty but also places higher demands on on-site installation conditions and requires user consent and confirmation of usage conditions. Therefore, how to achieve better lubrication and lower temperature rise by optimizing the surface structure design of the bearing bore without changing the original lubrication method and oil inlet conditions, while ensuring the support stability of the rotor and the safe and reliable operation of the equipment, has become an urgent technical problem to be solved. Utility Model Content

[0003] In order to overcome the above-mentioned defects of the prior art, the technical problem to be solved by the present invention is to provide a bearing structure and pump equipment to achieve better lubrication effect and lower temperature rise, and to ensure the support stability of the rotor and the safe and reliable operation of the equipment.

[0004] The above-mentioned objective of this utility model can be achieved by the following technical solution: this utility model provides a bearing structure, including:

[0005] The bearing includes a first bearing shell and a second bearing shell that can be interlocked, and the first bearing shell and the second bearing shell form a shaft hole after being interlocked;

[0006] The oil inlet structure includes a wear-resistant layer disposed on the inner wall of the shaft hole and a first oil inlet groove disposed on the wear-resistant layer. Along the axial direction of the shaft hole, the depth of the first oil inlet groove gradually increases from both ends to the middle; along the circumferential direction of the shaft hole, the depth of the first oil inlet groove gradually decreases from top to bottom.

[0007] In a preferred embodiment of the present invention, the first bearing bush is disposed above the second bearing bush, and the first oil inlet groove is disposed on the second bearing bush.

[0008] In a preferred embodiment of the present invention, two first oil inlet grooves are provided, and the two first oil inlet grooves are symmetrically arranged on the second bearing.

[0009] In a preferred embodiment of the present invention, along the axial direction of the shaft hole, the first oil inlet groove and the end of the second bearing are spaced apart by a preset distance, the preset distance being 5mm to 8mm.

[0010] In a preferred embodiment of the present invention, along the circumferential direction of the shaft hole, the arc length of the first oil inlet groove is 20% to 30% of the arc length of the second bearing.

[0011] In a preferred embodiment of the present invention, the depth of the first oil inlet groove ranges from 0.1 mm to 0.5 mm.

[0012] In a preferred embodiment of the present invention, the wear-resistant layer is a Babbitt alloy coating, and the first oil inlet groove is formed on the Babbitt alloy coating by scraping.

[0013] In a preferred embodiment of the present invention, the oil inlet structure further includes a second oil inlet groove disposed along the axial direction of the shaft hole on the inner wall of the shaft hole, the second oil inlet groove being disposed corresponding to the first oil inlet groove, and the second oil inlet groove being connected to the corresponding first oil inlet groove.

[0014] In a preferred embodiment of the present invention, the second oil inlet groove includes a first groove segment disposed on the first bearing and a second groove segment disposed on the second bearing. When the first bearing and the second bearing are in a fastening state, the first groove segment and the second groove segment are connected to form the second oil inlet groove.

[0015] In a preferred embodiment of the present invention, the bearing is provided with two mounting notches for the passage of an oil slinger ring.

[0016] This utility model also provides a pump device, including a rotor and the aforementioned bearing structure.

[0017] The technical solution of this utility model has the following significant beneficial effects:

[0018] This invention optimizes the oil inlet structure by scraping the wear-resistant layer on the inner surface of the bearing bush to a specific shape and depth without altering the original bearing structure. This significantly improves the lubricating oil supply efficiency, enhances the lubrication effect and stability of the oil film, and effectively reduces the temperature rise of the bearing during operation. Experiments have shown that using this oil inlet structure can reduce the bearing temperature by up to 15°C, without negatively impacting the rotor's vibration characteristics and stability. This invention achieves superior lubrication and lower temperature rise while ensuring rotor support stability and the safe and reliable operation of the equipment.

[0019] This invention is applicable to hydrodynamic radial sliding bearings used in rotating machinery such as horizontal pumps, and is particularly suitable for applications where high speed and large shaft diameter lead to significant temperature rise issues. Since it requires no changes to the existing lubrication system or the addition of external oil station equipment, it boasts advantages such as low implementation cost, short modification cycle, and ease of promotion. It can provide users with a more stable and reliable bearing operating environment without additional investment, and has promising engineering application prospects.

[0020] Specifically, in this invention, the first and second bearing bushes, when engaged, form a shaft hole for accommodating the rotor. A wear-resistant layer, such as a Babbitt metal coating, is provided on the inner wall of the shaft hole. A first oil inlet groove is formed on this wear-resistant layer through scraping, ensuring the structural integrity of both the first and second bearing bushes while simultaneously providing lubrication through the first oil inlet groove. Furthermore, along the axial direction of the shaft hole, the depth of the first oil inlet groove gradually increases from both ends towards the center; simultaneously, along the circumferential direction of the shaft hole, the depth of the oil inlet groove gradually decreases from top to bottom. This gradual design not only increases the amount of lubricating oil entering and the storage space but also optimizes the flow path of the lubricating oil through a reasonable distribution of oil grooves, thereby effectively improving the lubrication effect and ensuring the support stability of the rotor and the safe and reliable operation of the equipment. Attached Figure Description

[0021] To more clearly illustrate the technical solutions in the embodiments of this utility model, the drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0022] The accompanying drawings described herein are for illustrative purposes only and are not intended to limit the scope of this invention in any way. Furthermore, the shapes and proportions of the components in the drawings are merely illustrative to aid in understanding the invention and do not specifically limit the shapes and proportions of the components. Those skilled in the art, under the guidance of this invention, can select various possible shapes and proportions to implement this invention according to specific circumstances.

[0023] Figure 1 This is a three-dimensional structural diagram of one embodiment of the bearing structure described in this utility model;

[0024] Figure 2 This is a perspective sectional view of one embodiment of the bearing structure and rotor described in this utility model;

[0025] Figure 3 This is a radial cross-sectional view of one embodiment of the bearing structure described in this utility model;

[0026] Figure 4 This is a partially enlarged structural diagram of one embodiment of the first oil inlet groove of this utility model;

[0027] Figure 5 for Figure 3 Schematic diagram of section AA.

[0028] The reference numerals in the above figures are as follows:

[0029] 10. Rotor;

[0030] 20. Oil slinger ring;

[0031] 100. Bearing; 110. First bearing shell; 120. Second bearing shell; 130. Mounting notch;

[0032] 200. Oil inlet structure; 210. Wear-resistant layer; 220. First oil inlet groove; 230. Second oil inlet groove; 231. First groove section; 232. Second groove section. Detailed Implementation

[0033] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0034] Implementation Method 1

[0035] Please refer to the following: Figures 1 to 5As shown, an embodiment of this utility model provides a bearing structure, which includes a bearing 100 and an oil inlet structure 200. The bearing 100 includes a first bearing shell 110 and a second bearing shell 120 that can be interlocked, forming a shaft hole after the first bearing shell 110 and the second bearing shell 120 are interlocked. The oil inlet structure 200 includes a wear-resistant layer 210 disposed on the inner wall of the shaft hole and a first oil inlet groove 220 disposed on the wear-resistant layer 210. Along the axial direction of the shaft hole, the depth of the first oil inlet groove 220 gradually increases from both ends to the middle; along the circumferential direction of the shaft hole, the depth of the first oil inlet groove 220 gradually decreases from top to bottom.

[0036] Overall, such as Figure 1 and Figure 2 In the embodiment shown, the bearing structure, without changing the overall structure of the original bearing 100, performs scraping treatment on the wear-resistant layer 210 on the inner surface of the bearing bush in a specific shape and depth, forming an optimized oil inlet structure 200, which significantly improves the supply efficiency of lubricating oil, enhances the lubrication effect and stability of the oil film, and thus effectively reduces the temperature rise of the bearing 100 during operation.

[0037] Experiments have shown that by adopting this oil inlet structure 200, the temperature of bearing 100 can be reduced by up to 15°C, while the vibration characteristics and stability of rotor 10 are not negatively affected. This invention achieves better lubrication and lower temperature rise while ensuring the support stability of rotor 10 and the safe and reliable operation of the equipment.

[0038] This utility model applies to the hydrodynamic radial sliding bearing 100 used in rotating machinery such as horizontal pumps, and is particularly suitable for applications where high speed and large shaft diameter lead to significant temperature rise issues. Since it requires no changes to the existing lubrication system or the addition of external oil station equipment, it has the advantages of low implementation cost, short modification cycle, and ease of promotion. It can provide users with a more stable and reliable operating environment for the bearing 100 without additional investment, and has promising prospects for engineering applications.

[0039] Specifically, such as Figure 1 and Figure 2In the illustrated embodiment, the first bearing bush 110 and the second bearing bush 120 of this invention, when engaged, form a shaft hole for accommodating the rotor 10. A wear-resistant layer 210 is provided on the inner wall of the shaft hole, and a first oil inlet groove 220 is formed on the wear-resistant layer 210 by scraping. This ensures the structural integrity of the first bearing bush 110 and the second bearing bush 120, while also providing lubrication through the first oil inlet groove 220. Furthermore, along the axial direction of the shaft hole, the depth of the first oil inlet groove 220 gradually increases from both ends to the middle; simultaneously, along the circumferential direction of the shaft hole, the depth of the oil inlet groove gradually decreases from top to bottom. This gradual arrangement not only increases the amount of lubricating oil entering and the storage space, but also optimizes the flow path of the lubricating oil through a reasonable distribution of oil grooves, thereby effectively improving the lubrication effect and ensuring the support stability of the rotor 10 and the safe and reliable operation of the equipment.

[0040] In the embodiments of this utility model, such as Figure 1 , Figure 3 , Figure 4 and Figure 5 In the embodiment shown, along the axial direction of the shaft hole, the area of ​​the first oil inlet groove 220 gradually increases from both ends to the middle; along the circumferential direction of the shaft hole, the area of ​​the first oil inlet groove 220 gradually decreases from top to bottom.

[0041] Designers can adjust the specific shape of the first oil inlet groove 220 according to usage needs, and no specific limitations are imposed here. In one feasible embodiment, the projection of the first oil inlet groove 220 on the horizontal radial direction of the bearing 100 is approximately semi-elliptical. In another feasible embodiment, the projection of the first oil inlet groove 220 on the horizontal radial direction of the bearing 100 is approximately semi-circular.

[0042] In the embodiments of this utility model, such as Figure 1 and Figure 5 In the embodiment shown, the first bearing 110 is disposed above the second bearing 120, and the first oil inlet groove 220 is disposed on the second bearing 120.

[0043] By setting the first bearing shell 110 and the second bearing shell 120 vertically, a horizontal split structure is formed. By scraping a specific area of ​​the wear-resistant layer 210 located on the inner surface of the second bearing shell 120, an optimized first oil inlet groove 220 is formed. The first oil inlet groove 220 significantly improves the efficiency and uniformity of lubricating oil entering the bearing 100.

[0044] Furthermore, such as Figure 1 and Figure 2 In the illustrated embodiment, the bearing 100 is provided with two mounting notches 130 for the passage of the oil slinger ring 20. Specifically, the two mounting notches 130 are symmetrically arranged on the first bearing shell 110, and the oil slinger ring 20 can be installed using the two mounting notches 130.

[0045] During normal operation, the rotor 10 drives the oil slinger ring 20 to rotate. The surface of the oil slinger ring 20 is covered with lubricating oil from the oil sump, and the lubricating oil is continuously delivered to the pump shaft and the surface of the bearing 100. After the lubricating oil enters the first oil inlet groove 220 and the gap between the shaft hole and the rotor 10, it forms an oil film, thereby effectively lubricating the inner surface of the bearing 100 and reducing friction and temperature rise.

[0046] By combining the bearing 100 with the oil slinger ring 20, the oil supply efficiency of the lubrication system is optimized, the stability and reliability of the bearing 100 operation are enhanced, and the use of additional forced lubrication equipment is avoided, reducing system complexity and maintenance costs.

[0047] In the embodiments of this utility model, such as Figure 1 and Figure 3 In the embodiment shown, there are two first oil inlet grooves 220, and the two first oil inlet grooves 220 are symmetrically arranged on the second bearing 120.

[0048] By symmetrically arranging the two first oil inlet grooves 220 on the second bearing shell 120, the two symmetrically distributed first oil inlet grooves 220 synergistically optimize the uniformity and flow of lubricating oil into the bearing 100, further improve lubrication efficiency, effectively increase the supply and storage capacity of lubricating oil, improve the formation quality of oil film, significantly reduce the temperature rise of the bearing 100 during operation, and enhance the stability of the bearing 100.

[0049] In the embodiments of this utility model, such as Figure 1 and Figure 5 In the embodiment shown, along the axial direction of the shaft hole, the ends of the first oil inlet groove 220 and the second bearing 120 are spaced apart by a preset distance L1, which is 5mm to 8mm.

[0050] By spacing the ends of the first oil inlet groove 220 and the second bearing bush 120 by a preset distance L1, the first oil inlet groove 220 can be located inside the second bearing bush 120, preventing the two ends of the first oil inlet groove 220 from penetrating the second bearing bush 120 and causing lubricating oil leakage, so that the lubricating oil can be stably stored in the first oil inlet groove 220.

[0051] Furthermore, by utilizing the gap between the ends of the first oil inlet groove 220 and the second bearing 120, the rotor 10 can be better supported, ensuring the support stability of the rotor 10 and the safe and reliable operation of the equipment.

[0052] Designers can adjust the specific size of the preset distance according to usage needs, and no specific limitations are imposed here. In one feasible embodiment, the preset distance L1 is 5mm. In another feasible embodiment, the preset distance L1 is 6mm. In yet another feasible embodiment, the preset distance L1 is 8mm.

[0053] The distance between the two ends of the first oil inlet groove 220 and the two ends of the second bearing 120 may be equal or unequal, and no specific limitation is made here. Preferably, the distance between the two ends of the first oil inlet groove 220 and the two ends of the second bearing 120 is equal.

[0054] In the embodiments of this utility model, such as Figure 1 and Figure 3 In the embodiment shown, along the circumference of the shaft hole, the arc length L2 of the first oil inlet groove 220 is 20% to 30% of the arc length L3 of the second bearing 120.

[0055] By properly matching the arc length ratio of the first oil inlet groove 220 and the second bearing bush 120, it is helpful to optimize the distribution range and flow characteristics of lubricating oil on the bearing 100. On the basis of improving the uniformity and stability of the oil film, it also avoids weakening the load-bearing capacity of the second bearing bush 120 due to the excessive arc length of the first oil inlet groove 220, thus ensuring the operational stability of the rotor 10.

[0056] Specifically, the longer the arc length of the first oil inlet groove 220 in the circumferential direction, the more lubricating oil will be stored in it, but the area used to support the rotor 10 will be reduced, leading to poor stability and vibration of the rotor 10. Conversely, if the arc length of the first oil inlet groove 220 in the circumferential direction is shorter, although the stability of the rotor 10 is ensured, the amount of lubricating oil stored in the first oil inlet groove 220 will be reduced, thus failing to solve the problem of high bearing temperature. Therefore, after multiple tests, it was found that when the arc length of the first oil inlet groove 220 in the circumferential direction is about 20% to 30% of the arc length of the second bearing bush 120, sufficient lubricating oil can be stored in the first oil inlet groove 220 to solve the problem of high bearing temperature, while also ensuring the stability of the rotor 10.

[0057] Designers can adjust the arc length ratio of the first oil inlet groove 220 according to usage requirements, without specific limitations. In one feasible embodiment, the arc length L2 of the first oil inlet groove 220 is 20% of the arc length L3 of the second bearing 120. In another feasible embodiment, the arc length L2 of the first oil inlet groove 220 is 25% of the arc length L3 of the second bearing 120. In yet another feasible embodiment, the arc length L2 of the first oil inlet groove 220 is 30% of the arc length L3 of the second bearing 120.

[0058] In the embodiments of this utility model, such as Figure 1 and Figure 5 In the illustrated embodiment, the depth of the first oil inlet groove 220 ranges from 0.1 mm to 0.5 mm. In a specific embodiment, the first oil inlet groove 220 is gradually shallower from its deepest point at the axial center outwards, resulting in a gradual change in the depth of the first oil inlet groove 220.

[0059] Among these factors, an appropriate oil film thickness should be selected. The thinner the oil film, the stronger its compressive force, which reduces the oil film's load-bearing capacity and makes it more prone to rupture. Generally, based on the journal size, the mechanical oil film thickness of a conventional pump is approximately 0.06mm to 0.1mm. To address the issue of insufficient oil intake, the shallowest position of the newly scraped first oil inlet groove 220 is preset to 0.1mm, and the initial deepest point of the first oil inlet groove 220 is preset to 0.5mm for mechanical operation testing.

[0060] In this case study, by setting the depth of the first oil inlet groove 220 to 0.1 mm to 0.5 mm, this depth range ensures the flowability of lubricating oil while taking into account the lubrication thickness and support stability required for oil film formation. This effectively improves the uniformity of lubricating oil distribution on the contact surface of the bearing 100, enhances the stability of the oil film, and reduces the coefficient of friction and operating temperature rise.

[0061] Of course, in other feasible embodiments, the designer can adjust the depth range of the first oil inlet groove 220 according to the usage requirements, and no specific limitation is made here. For example, for bearings 100 and rotors 10 with large journals, it is usually necessary to appropriately increase the maximum depth of the first oil inlet groove 220, such as increasing it to 0.8 mm, depending on the temperature of the bearing 100 and the vibration of the rotor 10. However, in any case, the first oil inlet groove 220 should have a uniform transition in both the axial and circumferential directions.

[0062] Furthermore, by setting the depth range of the first oil inlet groove 220 to 0.1mm to 0.5mm, the damage to the bearing structure caused by excessive groove depth is avoided, ensuring the reliable operation of the bearing 100 under high load and high speed conditions.

[0063] Designers can adjust the depth range of the first oil inlet groove 220 according to usage needs, and no specific limitations are imposed here. In one feasible embodiment, the maximum depth of the first oil inlet groove 220 is 0.5 mm, and the shallowest depth of the first oil inlet groove 220 is 0.1 mm. In another feasible embodiment, the maximum depth of the first oil inlet groove 220 is 0.4 mm, and the shallowest depth of the first oil inlet groove 220 is 0.1 mm. In yet another feasible embodiment, the maximum depth of the first oil inlet groove 220 is 0.3 mm, and the shallowest depth of the first oil inlet groove 220 is 0.1 mm.

[0064] In embodiments of this utility model, designers can adjust the specific material and formation method of the wear-resistant layer 210 according to usage requirements, and no specific limitations are imposed here. Preferably, as follows: Figure 3 and Figure 4 In the embodiment shown, the wear-resistant layer 210 is a Babbitt alloy coating, and the first oil inlet groove 220 is formed on the Babbitt alloy coating by scraping.

[0065] The Babbitt alloy coating has excellent wear resistance and embeddability, which helps to form a stable wear-resistant layer 210 on the inner wall of the shaft hole. The wear-resistant layer 210 improves the durability and lubrication performance of the bearing 100.

[0066] Furthermore, the first oil inlet groove 220 formed by scraping the Babbitt alloy coating has good surface compatibility and oil film distribution characteristics, which further enhances the uniform supply of lubricating oil between the contact surfaces and the stable formation of the oil film, and also avoids damage to the structure of the bearing 100, thus ensuring the structural strength of the bearing 100.

[0067] In one feasible embodiment, such as Figure 3 and Figure 5 The embodiment shown describes the steps for forming the first oil inlet groove 220 by scraping the Babbitt alloy coating as follows: Prepare a triangular scraper, cleaning agent, and rag in advance, and wipe the inner surface of the second bearing 120 clean; scrape along the circumference of the second bearing 120 for about 20% to 30% of the arc length to form two first oil inlet grooves 220, and scrape along the axial direction of the second bearing 120; according to the preset scraping depth, for the circumference of the second bearing 120, the depth b at the axial center is uniformly transitioned to the depth a1 on the other side, where b is 0.5mm and a1 is 0.1mm; for the axial direction of the second bearing 120, except for the preset interval on both sides of the bearing 100, the depth a2 on one side is transitioned to the depth b at the axial center, and then to the depth a3 on the other side, where a2 is 0.1mm and a3 is 0.1mm.

[0068] Furthermore, for self-lubricating radial bearings 100 with larger shaft diameters or higher speeds, the value of b can be appropriately increased. For example, taking an 82mm shaft diameter as an example, the value of b is set to 0.5mm, and the value of a is close to 0.1mm. Scraping and testing can be performed using these values ​​first. If the abnormal temperature rise is not resolved after the test, the value of b can be appropriately increased; no specific restrictions are imposed here.

[0069] In the embodiments of this utility model, such as Figure 3 and Figure 5 In the embodiment shown, the oil inlet structure 200 further includes a second oil inlet groove 230 disposed on the inner wall of the shaft hole along the axial direction of the shaft hole. The second oil inlet groove 230 is disposed corresponding to the first oil inlet groove 220, and the second oil inlet groove 230 is connected to the corresponding first oil inlet groove 220.

[0070] By setting a second oil inlet groove 230, when the rotor 10 drives the oil slinger ring 20 to rotate, the surface of the oil slinger ring 20 is covered with lubricating oil from the oil pool, and the lubricating oil is continuously transported to the second oil inlet groove 230 and enters the first oil inlet groove 220 through the second oil inlet groove 230, thereby improving the uniformity of oil intake.

[0071] Specifically, the second oil inlet groove 230 includes a first groove section 231 disposed on the first bearing shell 110 and a second groove section 232 disposed on the second bearing shell 120. When the first bearing shell 110 and the second bearing shell 120 are in a snap-fit ​​state, the first groove section 231 and the second groove section 232 are joined together to form the second oil inlet groove 230.

[0072] By axially arranging the second oil inlet groove 230 along the shaft hole and connecting the second oil inlet groove 230 to the corresponding first oil inlet groove 220, an oil delivery channel is formed by the second oil inlet groove 230, thereby enabling the lubricating oil delivered by the oil slinger ring 20 to be evenly input into the first oil inlet groove 220, which significantly improves the continuity and uniformity of lubricating oil supply.

[0073] Furthermore, by cooperating the first groove segment 231 provided on the first bearing shell 110 and the second groove segment 232 provided on the second bearing shell 120, after the first bearing shell 110 and the second bearing shell 120 are engaged, the first groove segment 231 and the second groove segment 232 can be connected to form a complete second oil inlet groove 230, which is convenient for assembly and processing.

[0074] Designers can adjust the specific shape and structure of the second oil inlet groove 230 according to usage requirements, and no specific limitations are imposed here. Preferably, the cross-section of the second oil inlet groove 230 is arc-shaped. For example, the cross-section of the second oil inlet groove 230 can be semi-circular or semi-elliptical.

[0075] By cooperating with the second oil inlet groove 230 and the oil slinger ring 20, the oil supply stability of the bearing 100 under complex working conditions is effectively enhanced, the lubrication efficiency is improved, the friction loss and temperature rise are reduced, and the service life of the equipment is extended.

[0076] Implementation Method 2

[0077] An embodiment of this utility model provides a pump device, which includes a rotor 10 and a bearing structure as described in Embodiment 1. The structure and effect of the bearing structure are the same as those described in Embodiment 1, and will not be repeated here. Designers can determine the specific model of the pump device according to the usage requirements, and no specific limitations are made here. Preferably, the pump device is a horizontal pump.

[0078] All articles and references disclosed herein, including patent applications and publications, are incorporated herein by reference for various purposes. The term “substantially constitutes…” used to describe a combination should include the identified element, component, part, or step, as well as other elements, components, parts, or steps that do not substantially affect the essential novelty of the combination. The use of the terms “comprising” or “including” to describe combinations of elements, components, parts, or steps herein also contemplates embodiments substantially constituted by such elements, components, parts, or steps. The use of the term “may” herein is intended to indicate that any described attribute “may” include is optional. Multiple elements, components, parts, or steps can be provided by a single integrated element, component, part, or step. Alternatively, a single integrated element, component, part, or step can be divided into multiple separate elements, components, parts, or steps. The disclosure of “a” or “an” used to describe an element, component, part, or step does not imply exclusion of other elements, components, parts, or steps.

[0079] The various embodiments in this specification are described in a progressive manner, with each embodiment focusing on its differences from other embodiments. Similar or identical parts between embodiments can be referred to interchangeably. The above embodiments are only for illustrating the technical concept and features of this utility model, and are intended to enable those skilled in the art to understand the content of this utility model and implement it accordingly. They should not be construed as limiting the scope of protection of this utility model. All equivalent changes or modifications made in accordance with the spirit and essence of this utility model should be included within the scope of protection of this utility model.

Claims

1. A bearing structure, characterized in that, include: The bearing includes a first bearing shell and a second bearing shell that can be interlocked, and the first bearing shell and the second bearing shell form a shaft hole after being interlocked; The oil inlet structure includes a wear-resistant layer disposed on the inner wall of the shaft hole and a first oil inlet groove disposed on the wear-resistant layer. Along the axial direction of the shaft hole, the depth of the first oil inlet groove gradually increases from both ends to the middle; along the circumferential direction of the shaft hole, the depth of the first oil inlet groove gradually decreases from top to bottom.

2. The bearing structure as described in claim 1, characterized in that, The first bearing bush is disposed above the second bearing bush, and the first oil inlet groove is disposed on the second bearing bush.

3. The bearing structure as described in claim 2, characterized in that, There are two first oil inlet grooves, which are symmetrically arranged on the second bearing.

4. The bearing structure as described in claim 2, characterized in that, Along the axial direction of the shaft hole, the first oil inlet groove is spaced at a predetermined distance from the end of the second bearing bush; and / or, along the circumferential direction of the shaft hole, the arc length of the first oil inlet groove is 20% to 30% of the arc length of the second bearing bush.

5. The bearing structure as described in claim 1, characterized in that, The depth of the first oil inlet groove ranges from 0.1 mm to 0.5 mm.

6. The bearing structure as described in claim 1, characterized in that, The wear-resistant layer is a Babbitt alloy coating, and the first oil inlet groove is formed on the Babbitt alloy coating by scraping.

7. The bearing structure as described in claim 1 or 3, characterized in that, The oil inlet structure further includes a second oil inlet groove disposed along the axial direction of the shaft hole on the inner wall of the shaft hole. The second oil inlet groove is disposed corresponding to the first oil inlet groove and is connected to the corresponding first oil inlet groove.

8. The bearing structure as described in claim 7, characterized in that, The second oil inlet groove includes a first groove section disposed on the first bearing and a second groove section disposed on the second bearing. When the first bearing and the second bearing are in a snap-fit ​​state, the first groove section and the second groove section are joined together to form the second oil inlet groove.

9. The bearing structure as described in claim 7, characterized in that, The bearing is provided with two mounting notches for the passage of the oil slinger ring.

10. A pump device, characterized in that, It includes a rotor and a bearing structure as described in any one of claims 1 to 9.

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