A floating bearing structure and turbocharger core component

Abstract

The utility model provides a kind of floating bearing structure and turbocharger core component, wherein the asymmetric lubricant distribution design formed by bearing middle section, turbine end flange, impeller end flange and oil inlet of floating bearing structure, solve the problem of mismatching of lubricating effect caused by difference of working environment at both ends of rotor shaft;Since turbine end usually bears higher load and temperature, obtaining more lubricant helps to improve the lubrication and cooling conditions of the end, thereby reducing the radial runout of shaft orbit, improving operation stability, compared with the floating bearing of two-end symmetrical design, the present scheme can more effectively adapt to the actual working condition requirement of both ends of rotor shaft;Turbocharger core component can realize effective supply and distribution of lubricant by setting floating bearing structure in bearing mounting groove of shell and making lubricant flow channel communicate with oil inlet of floating bearing structure.

Description

Technical Field

[0001] This utility model relates to the field of turbocharging technology, specifically to a floating bearing structure and a core component of a turbocharger. Background Technology

[0002] As a crucial component of the entire turbocharger, the core component of the turbocharger serves to connect the turbine end and the compressor end.

[0003] In existing technologies, the main structure of a turbocharger's core component generally includes a housing and a floating bearing housed within the housing. The rotor shaft passes through the floating bearing to connect the turbine and compressor impellers at both ends. Lubricating oil in the lubrication channels within the housing enters the floating bearing to lubricate the rotor shaft. Due to the differences in structure and operating environment between the turbine end and compressor end of the rotor shaft, the loads they bear during operation and the lubrication effects also differ. Existing technologies often design the structures at both ends of the floating bearing to be identical, resulting in a lack of matching lubrication effects at both ends of the rotor shaft. This leads to a large radial runout of the rotor shaft's axis trajectory and poor stability of the axis trajectory. Utility Model Content

[0004] The problem to be solved by this utility model is to provide a floating bearing structure that can improve the stability of the shaft trajectory based on the difference in working environment at both ends of the rotor shaft, and a core component of a turbocharger with such a floating bearing structure.

[0005] The technical solution adopted by this utility model to solve the above problems is: a floating bearing structure, comprising:

[0006] The middle section of a bearing;

[0007] A turbine end flange, wherein the turbine end flange is disposed at one end of the bearing middle section;

[0008] An impeller end flange, wherein the turbine end flange is disposed at the other end of the bearing section; and

[0009] An oil inlet is provided, wherein the oil inlet is located in the middle section of the bearing; when lubricant flows from the oil inlet to the turbine end flange and the impeller end flange respectively, the turbine end flange receives more lubricant than the impeller end flange.

[0010] Compared with existing technologies, this invention solves the problem of mismatched lubrication effects caused by differences in working environment at both ends of the rotor shaft by using an asymmetrical lubricant distribution design formed by the bearing middle section, turbine end flange, impeller end flange, and oil inlet. Since the turbine end usually bears higher loads and temperatures, obtaining more lubricant helps improve the lubrication and cooling conditions at this end, thereby reducing the radial runout of the shaft trajectory and improving operational stability. Compared with floating bearings with symmetrical designs at both ends, this solution can more effectively adapt to the actual working conditions at both ends of the rotor shaft.

[0011] The present invention discloses a floating bearing structure, wherein the oil inlet is disposed at one end of the bearing section near the impeller end flange; when the lubricant flows from the oil inlet to the turbine end flange and the impeller end flange respectively, the distance the lubricant travels to the turbine end flange is greater than the distance it travels to the impeller end flange.

[0012] The present invention discloses a floating bearing structure in which the radial dimension of the turbine end flange is set to be larger than the radial dimension of the impeller end flange.

[0013] The present invention discloses a floating bearing structure, which further includes an oil guide groove, wherein the oil guide groove is respectively disposed on the inner wall of the turbine end flange and the impeller end flange; when the lubricant flows through the turbine end flange and the impeller end flange, it is retained in the oil guide groove.

[0014] The present invention discloses a floating bearing structure, wherein the oil guide groove is constructed in a spiral shape and is disposed on the inner wall of the turbine end flange and / or the impeller end flange.

[0015] The present invention provides a floating bearing structure, wherein the oil guide groove is constructed as a straight groove.

[0016] The oil guide grooves are configured as multiple channels and are arranged to be distributed circumferentially along the inner wall of the turbine end flange and / or the impeller end flange.

[0017] The present invention provides a floating bearing structure, which further includes a plurality of end face grooves; the turbine end flange has a first thrust surface disposed at one end away from the middle section of the bearing, and the impeller end flange has a second thrust surface disposed at one end away from the middle section of the bearing; the end face grooves are disposed on the first thrust surface and the second thrust surface;

[0018] The end face groove disposed on the first thrust surface is respectively connected to a plurality of oil guide grooves disposed on the inner wall of the turbine end flange; the end face groove disposed on the second thrust surface is respectively connected to a plurality of oil guide grooves disposed on the inner wall of the impeller end flange.

[0019] The technical solution adopted by this utility model to solve the above problems is: a core component of a turbocharger, comprising:

[0020] A housing, wherein the housing has a bearing mounting groove and a lubricant flow channel; and

[0021] The floating bearing structure includes:

[0022] The middle section of a bearing;

[0023] A turbine end flange, wherein the turbine end flange is disposed at one end of the bearing middle section;

[0024] An impeller end flange, wherein the turbine end flange is disposed at the other end of the bearing section; and

[0025] An oil inlet is provided, wherein the oil inlet is located in the middle section of the bearing; when lubricant flows from the oil inlet to the turbine end flange and the impeller end flange respectively, the turbine end flange receives more lubricant than the impeller end flange.

[0026] The floating bearing structure is disposed in the bearing mounting groove; the lubricant flow channel is configured to communicate with the oil inlet.

[0027] Compared with existing technologies, this invention, by placing the floating bearing structure within the bearing mounting groove of the housing and connecting the lubricant flow channel to the oil inlet of the floating bearing structure, enables effective supply and distribution of lubricant. The design of the lubricant flow channel allows for uniform distribution and thorough lubrication of all parts of the floating bearing structure, improving the continuity and stability of lubrication. This addresses the problem of mismatched lubrication and cooling effects at both ends of the floating bearing and improves the stability of the rotor shaft's trajectory.

[0028] This utility model discloses a core component of a turbocharger, wherein the lubricant flow channel includes an inlet flow channel, a collecting flow channel, and an outlet flow channel; the lubricant enters from the inlet flow channel, flows through the floating bearing structure, and then flows into the collecting flow channel from both ends of the bearing mounting groove and both ends of the floating bearing structure, and then flows out from the outlet flow channel through the collecting flow channel.

[0029] The lubricant flow channel further includes a bypass flow channel disposed in the inlet flow channel.

[0030] This utility model discloses a core component of a turbocharger, wherein the bearing mounting groove includes an impeller end groove section, a turbine end groove section, and an intermediate groove section disposed between the impeller end groove section and the turbine end groove section;

[0031] The axial dimension of the impeller end slot section is set to be larger than that of the turbine end slot section;

[0032] The bearing mounting groove further includes a liquid storage cavity disposed between the intermediate groove section and the bearing middle section. Attached Figure Description

[0033] Figure 1 This is a perspective view of a floating bearing structure according to a preferred embodiment of the present invention;

[0034] Figure 2 This is a cross-sectional schematic diagram of a floating bearing structure according to a preferred embodiment of the present invention;

[0035] Figure 3 This is a cross-sectional schematic diagram of a floating bearing structure according to another preferred embodiment of the present invention;

[0036] Figure 4 This is a cross-sectional schematic diagram of a floating bearing structure according to another preferred embodiment of the present invention;

[0037] Figure 5 This is a perspective view of the core components of a turbocharger according to a preferred embodiment of the present invention;

[0038] Figure 6 This is a cross-sectional schematic diagram of the core component of a turbocharger according to a preferred embodiment of the present invention;

[0039] Figure 7 This is a schematic diagram of the floating bearing structure according to a preferred embodiment of the present invention in the core component of a turbocharger.

[0040] Figure 8 This is a schematic diagram showing the flow direction of the lubricant inside the floating bearing structure according to a preferred embodiment of the present invention;

[0041] In the picture:

[0042] Bearing middle section 1;

[0043] Turbine end flange 2; First thrust surface 21;

[0044] Impeller end flange 3; Second thrust surface 31;

[0045] Oil inlet 4;

[0046] Oil guide groove 5;

[0047] 6. Housing; bearing mounting groove 61, lubricant flow channel 62; impeller end groove section 611, turbine end groove section 612, intermediate groove section 613, liquid storage chamber 614; liquid inlet flow channel 621, liquid collection flow channel 622, liquid outlet flow channel 623, bypass flow channel 624;

[0048] End face groove 7. Detailed Implementation

[0049] Before describing any embodiment of this invention in detail, it should be understood that the invention is not limited in its application to the details of the construction and arrangement of the components set forth in the following description or illustrated in the following figures. The invention is capable of other embodiments and can be practiced or carried out in various ways. Furthermore, it should be understood that the wording and terminology used herein are for descriptive purposes and should not be considered limiting. The use of “comprising” or “having” and variations thereof herein is intended to cover the items set forth below and their equivalents, as well as any additional items. Unless otherwise specified or limited, the terms “installation,” “connection,” “support,” and “linkage,” and variations thereof are used broadly and cover both direct and indirect installation, connection, support, and linking. Moreover, “connection” and “linkage” are not limited to physical or mechanical connections or links.

[0050] Furthermore, firstly, in the disclosure of this utility model, the terms "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, the above terms should not be construed as a limitation on this utility model. Secondly, the term "a" should be understood as "at least one" or "one or more," that is, in one embodiment, the number of an element can be one, while in another embodiment, the number of the element can be multiple. The term "a" should not be construed as a limitation on the quantity.

[0051] Those skilled in the art should understand that the embodiments of the present invention described above and shown in the accompanying drawings are merely examples and do not limit the present invention. The purpose of the present invention has been fully and effectively achieved. The function and structural principle of the present invention have been shown and explained in the embodiments. Without departing from the described principle, the implementation of the present invention may have any variations or modifications.

[0052] The embodiments of this utility model will be further described below with reference to the accompanying drawings.

[0053] Please see Figure 1-4 The floating bearing structure shown includes a bearing section 1, a turbine end flange 2, an impeller end flange 3, and an oil inlet 4; the turbine end flange 2 is disposed at one end of the bearing section 1; the turbine end flange 2 is disposed at the other end of the bearing section 1; the oil inlet 4 is disposed in the bearing section 1; when lubricant flows from the oil inlet 4 to the turbine end flange 2 and the impeller end flange 3 respectively, the turbine end flange 2 receives more lubricant than the impeller end flange 3.

[0054] In some embodiments, the turbine end flange 2 and the impeller end flange 3 are fixed to both ends of the bearing middle section 1 by welding or integral molding. The oil inlet 4 can be located on the side of the bearing middle section 1, and its orifice size can be adjusted according to the lubricant flow requirements. The uneven distribution of lubricant can be achieved by, but is not limited to: the oil inlet 4 being located biased towards the turbine end flange 2, the oil passage cross-sectional area being larger on the turbine end flange 2 side, or the oil passage resistance being smaller on the turbine end flange 2 side.

[0055] In practical use, this invention solves the problem of mismatched lubrication effect caused by the difference in working environment at both ends of the rotor shaft through an asymmetrical lubricant distribution design. Since the turbine end usually bears higher load and temperature, obtaining more lubricant helps to improve the lubrication and cooling conditions at this end, thereby reducing the radial runout of the shaft trajectory and improving the running stability. Compared with floating bearings with symmetrical design at both ends, this solution can more effectively adapt to the actual working conditions at both ends of the rotor shaft.

[0056] Please continue reading. Figure 1-4 The oil inlet 4 is located at one end of the bearing middle section 1 near the impeller end flange 3; when the lubricant flows from the oil inlet 4 to the turbine end flange 2 and the impeller end flange 3 respectively, the distance the lubricant travels to the turbine end flange 2 is greater than the distance it travels to the impeller end flange 3.

[0057] In some embodiments, the location of the oil inlet 4 directly affects the distribution effect of the lubricant. When the oil inlet 4 is arranged close to the impeller end flange 3, the lubricant needs to travel a longer flow path to reach the turbine end flange 2, while the path to reach the impeller end flange 3 is shorter. This arrangement can be achieved in the following ways: the oil inlet 4 can be located at 1 / 4 of the axial length of the bearing middle section 1, close to the impeller end flange 3; or the distance between the centerline of the oil inlet 4 and the end face of the impeller end flange 3 is less than its distance from the end face of the turbine end flange 2; or an inclined oil passage is machined in the bearing middle section 1, so that the oil inlet 4 is biased towards the impeller end flange 3 in radial projection.

[0058] In use, this invention achieves differentiated lubricant distribution by optimizing the position of the oil inlet 4. Since the lubricant needs to travel a longer distance to reach the turbine end flange 2, the oil supply at that end is objectively reduced, thus balancing the actual lubrication and cooling effects at both flanges. This arrangement can adapt to the different working load requirements at both ends of the rotor shaft, avoiding instability in the shaft trajectory caused by uneven lubrication and cooling. Compared with symmetrically arranged oil inlets 4, this scheme better suits the actual working conditions of the turbine end and impeller end, improving the operational stability of the bearing system.

[0059] Please continue reading. Figure 2The radial dimension of the turbine end flange 2 is set to be greater than the radial dimension of the impeller end flange 3.

[0060] In some embodiments, the turbine end flange 2 and the impeller end flange 3 have different dimensional configurations in the radial direction, such as... Figure 2 As shown, the radial dimension of turbine end flange 2 is denoted as L1, and the radial dimension of impeller end flange 3 is denoted as L2, with L1 being greater than L2. This increase in the radial dimension of turbine end flange 2 facilitates the formation of a lubricating oil film in this area. Since the turbine end operates at a higher temperature and bears a larger radial load, a larger radial dimension increases the thickness of the lubricating oil film and improves lubrication and cooling effects. Simultaneously, maintaining a larger radial dimension for turbine end flange 2 ensures structural strength, thus balancing the different lubrication requirements at both ends. Consequently, the radial runout of the rotor shaft's axis during operation is reduced, and stability is improved.

[0061] Please continue reading. Figure 1-4 It further includes an oil guide groove 5, wherein the oil guide groove 5 is respectively disposed on the inner wall of the turbine end flange 2 and the impeller end flange 3; when the lubricant flows through the turbine end flange 2 and the impeller end flange 3, it is retained in the oil guide groove 5.

[0062] In use, this invention, by incorporating oil guide grooves 5, allows the lubricant to be more effectively distributed on the inner wall surface of the flange. Since the turbine end flange 2 and the impeller end flange 3 each have independent oil guide grooves 5, they can be specifically designed according to the different lubrication requirements at both ends. The presence of the oil guide grooves 5 ensures that the lubricant is more stably maintained in the contact area, preventing rapid lubricant loss and improving the uniformity of lubricant distribution, thereby enhancing the stability of bearing operation. The improved lubricant retention helps reduce frictional loss and extend bearing life.

[0063] Please continue reading. Figure 3 The oil guide groove 5 is constructed in a spiral shape and is disposed on the inner wall of the turbine end flange 2 and / or the impeller end flange 3.

[0064] In other embodiments, the spiral oil guide groove 5 refers to a spiral groove structure machined on the inner wall surface. As a further preferred embodiment, a single-headed right-handed spiral groove can be provided on the inner wall of the turbine end flange 2, and a double-headed left-handed spiral groove can be provided on the inner wall of the impeller end flange 3. Furthermore, the starting end of the spiral oil guide groove 5 can correspond to the position of the oil inlet 4, and the ending end can extend to the flange end. Thus, when the lubricant flows through the inner wall of the flange, it is guided by the spiral oil guide groove 5 to form a rotating flow.

[0065] To address this, the spiral oil guide groove 5 causes the lubricant to rotate as it flows through the inner wall of the flange, thereby extending the residence time of the lubricant on the flange's inner wall. This allows for more effective and even distribution of the lubricant on the flange's inner wall surface, preventing lubricant accumulation or loss in localized areas. Especially when the radial dimension of the turbine end flange 2 is small, the spiral oil guide groove 5 ensures that the limited lubricant is fully utilized. Therefore, this technical solution can improve the lubrication effect difference at both ends of the floating bearing, resulting in a more stable rotor shaft trajectory.

[0066] Please continue reading. Figure 2 The oil guide groove 5 is constructed as a straight groove; the oil guide groove 5 is configured as multiple grooves and is configured to be distributed circumferentially along the inner wall of the turbine end flange 2 and / or the impeller end flange 3.

[0067] In some embodiments, the straight-groove oil guide groove 5 refers to a straight groove structure extending along the axial direction, and its cross-sectional shape can be rectangular, trapezoidal, or other geometric shapes suitable for flow guidance. The arrangement of multiple oil guide grooves 5 includes, but is not limited to: 4-12 oil guide grooves 5 evenly distributed on the inner wall of the flange; the circumferential spacing between adjacent oil guide grooves 5 remains equal. The oil guide groove 5 can be machined by broaching, milling, or electrical discharge machining processes.

[0068] In use, this invention, by setting multiple circumferentially distributed straight grooves 5 for oil guiding, can significantly improve the axial distribution of lubricant. When the lubricant enters from the oil inlet 4, the multiple straight grooves can simultaneously guide the lubricant to diffuse evenly along the axial direction, avoiding localized insufficient lubrication. This structure not only ensures rapid delivery of lubricant to the inner wall of the flange, but also enhances the oil film carrying capacity through the multi-groove structure, effectively reducing the radial runout amplitude of the rotor shaft during operation.

[0069] Please continue reading. Figure 1 , Figure 2 The turbine end flange 2 further includes a plurality of end face grooves 7; the turbine end flange 2 has a first thrust surface 21 disposed at one end away from the bearing middle section 1, and the impeller end flange 3 has a second thrust surface 31 disposed at one end away from the bearing middle section 1; the end face grooves 7 are disposed on the first thrust surface 21 and the second thrust surface 31; the end face grooves 7 disposed on the first thrust surface 21 are respectively connected to a plurality of oil guide grooves 5 disposed on the inner wall of the turbine end flange 2; the end face grooves 7 disposed on the second thrust surface 31 are respectively connected to a plurality of oil guide grooves 5 disposed on the inner wall of the impeller end flange 3.

[0070] In some embodiments, the end face groove 7 can be configured as an annular groove, a radial groove, or a straight groove. As a further preferred embodiment, the end face groove 7 is constructed as a radial straight groove communicating with the oil guide groove 5. Specifically, the number of end face grooves 7 corresponds to the number of oil guide grooves 5, with each oil guide groove 5 connected to one end face groove 7. A transition arc can be provided at the connection between the end face groove 7 and the oil guide groove 5 to reduce flow resistance.

[0071] In use, this invention provides an end face groove 7 connected to the oil guide groove 5 on the thrust surface, allowing lubricant to flow smoothly from the oil guide groove 5 into the thrust surface area. This results in a more uniform distribution of lubricant on the thrust surface, improving the lubricant circulation effect, further enhancing the lubrication and cooling effects of the lubricant, reducing radial runout of the rotor shaft during operation, and improving the stability of the shaft trajectory.

[0072] Understandably, please continue reading. Figure 4 The straight-groove oil guide groove 5 can be set at one of the turbine end flange 2 and the impeller end flange 3, and the spiral-shaped oil guide groove 5 can be set at the other of the turbine end flange 2 and the impeller end flange 3, so as to adapt to different turbocharger core components.

[0073] Please continue reading. Figure 4-8 The diagram shows a core component of a turbocharger, comprising: a housing 6 and a floating bearing structure; the housing 6 has a bearing mounting groove 61 and a lubricant flow channel 62; the floating bearing structure includes a bearing section 1, a turbine end flange 2, an impeller end flange 3, and an oil inlet 4; the turbine end flange 2 is disposed at one end of the bearing section 1; the turbine end flange 2 is disposed at the other end of the bearing section 1; the oil inlet 4 is disposed in the bearing section 1; when lubricant flows from the oil inlet 4 to the turbine end flange 2 and the impeller end flange 3 respectively, the turbine end flange 2 receives more lubricant than the impeller end flange 3; the floating bearing structure is disposed in the bearing mounting groove 61; the lubricant flow channel 62 is configured to communicate with the oil inlet 4.

[0074] In practical use, by placing the floating bearing structure within the bearing mounting groove 61 of the housing 6 and connecting the lubricant flow channel 62 to the oil inlet 4 of the floating bearing structure, effective lubricant supply and distribution can be achieved. The design of the lubricant flow channel 62 ensures that the lubricant is evenly distributed and fully lubricates all parts of the floating bearing structure. The bypass flow channel 624 can regulate the flow rate and pressure of the lubricant to ensure lubrication effect, and can also distribute the lubricant to other components of the turbocharger core component. The axial dimension of the impeller end groove section 611 is smaller than that of the turbine end groove section 612, which can adapt to the lubrication requirements of different ends. The liquid reservoir 614 helps to temporarily store lubricant, improve the continuity and stability of lubrication, thereby solving the problem of mismatch between lubrication and cooling effects at both ends of the floating bearing and improving the stability of the rotor shaft centerline trajectory.

[0075] Please continue reading. Figure 6 , Figure 7 The lubricant flow channel 62 includes an inlet flow channel 621, a collecting flow channel 622, and an outlet flow channel 623. The lubricant enters from the inlet flow channel 621, flows through the floating bearing structure, and then flows into the collecting flow channel 622 from both ends of the bearing mounting groove 61 and both ends of the floating bearing structure, and then flows out from the outlet flow channel 623 through the collecting flow channel 622. The lubricant flow channel 62 further includes a bypass flow channel 624 disposed in the inlet flow channel 621.

[0076] In some embodiments, the inlet channel 621 can adopt a straight-through pipe structure, and the collecting channel 622 is constructed as an annular cavity structure; the bypass channel 624 is configured as a branch pipe connected in parallel with the inlet channel 621. Thus, by optimizing the structure of the lubricant channel 62, this invention achieves multi-path distribution and pressure regulation of the lubricant. The inlet channel 621 ensures a basic oil supply, while the bypass channel 624 can regulate system pressure or distribute lubricant to other components of the turbocharger core component, avoiding seal failure due to excessive pressure. The annular design of the collecting channel 622 facilitates uniform lubricant distribution, while the arrangement of the outlet channel 623 allows for lubricant circulation, effectively controlling the lubricant flow distribution and providing differentiated lubrication effects at both ends of the floating bearing, thereby improving the stability of the rotor shaft operation.

[0077] Please continue reading. Figure 6 , Figure 7 The bearing mounting groove 61 includes an impeller end groove section 611, a turbine end groove section 612, and an intermediate groove section 613 disposed between the impeller end groove section 611 and the turbine end groove section 612; the axial dimension of the impeller end groove section 611 is set to be larger than that of the turbine end groove section 612; the bearing mounting groove 61 further includes a liquid storage cavity 614 disposed between the intermediate groove section 613 and the bearing middle section 1.

[0078] In some embodiments, the impeller end groove 611 and the turbine end groove 612 are used to accommodate the impeller end flange 3 and the turbine end flange 2 of the floating bearing structure, respectively. An intermediate groove 613 connects the impeller end groove 611 and the turbine end groove 612, forming a complete bearing mounting space. The liquid reservoir 614 is constructed as an annular groove surrounding the inner wall of the intermediate groove 613, for temporarily storing lubricant flowing in from the oil inlet 4. As a further preferred embodiment, the axial dimension of the impeller end groove 611 is smaller than that of the turbine end groove 612 to accommodate the larger radial dimension of the impeller end flange 3.

[0079] In use, this invention, by setting impeller end grooves 611 and turbine end grooves 612 of different sizes, can better match the different structural requirements at both ends of the floating bearing. The matching design of the intermediate groove 613 and the liquid storage chamber 614 allows the lubricant to be temporarily stored in the liquid storage chamber 614 before being evenly distributed to both ends of the bearing. This structure effectively solves the problem of uneven lubrication caused by identical structures at both ends in the prior art, and improves the stability of the rotor shaft operation. The setting of the liquid storage chamber 614 also improves the fault tolerance of the lubrication system, and can still maintain a short-term lubrication effect when the instantaneous oil supply is insufficient.

[0080] It is worth mentioning that the liquid storage cavity 614 can be formed by hollowing out the inner wall of the intermediate groove section 613 or by hollowing out the outer wall of the bearing middle section 1. In this embodiment, the liquid storage cavity 614 is formed by hollowing out the inner wall of the intermediate groove section 613, so that the outer wall structure of the floating bearing structure remains consistent, which is beneficial to the processing of the floating bearing structure and also better ensures the structural strength of the bearing middle section 1.

[0081] The above description only illustrates the preferred embodiment of this utility model and should not be construed as limiting the scope of the claims. This utility model is not limited to the above embodiments, and variations in its specific structure are permitted. All changes made within the scope of the independent claims of this utility model are also within the scope of protection of this utility model.

Claims

1. A floating bearing structure, characterized in that, include: One bearing middle section (1); A turbine end flange (2), wherein the turbine end flange (2) is disposed at one end of the bearing middle section (1); An impeller end flange (3), wherein the turbine end flange (2) is disposed at the other end of the bearing middle section (1); and An oil inlet (4) is provided in the middle section (1) of the bearing; when the lubricant flows from the oil inlet (4) to the turbine end flange (2) and the impeller end flange (3) respectively, the turbine end flange (2) receives more lubricant than the impeller end flange (3).

2. The floating bearing structure according to claim 1, characterized in that: The oil inlet (4) is located at one end of the bearing middle section (1) near the impeller end flange (3); when the lubricant flows from the oil inlet (4) to the turbine end flange (2) and the impeller end flange (3) respectively, the distance the lubricant flows to the turbine end flange (2) is greater than the distance it flows to the impeller end flange (3).

3. The floating bearing structure according to claim 1 or 2, characterized in that: The radial dimension of the turbine end flange (2) is set to be greater than the radial dimension of the impeller end flange (3).

4. The floating bearing structure according to claim 3, characterized in that: It further includes an oil guide groove (5), wherein the oil guide groove (5) is respectively disposed on the inner wall of the turbine end flange (2) and the impeller end flange (3); when the lubricant flows through the turbine end flange (2) and the impeller end flange (3), it is retained in the oil guide groove (5).

5. The floating bearing structure according to claim 4, characterized in that: The oil guide groove (5) is constructed in a spiral shape and is disposed on the inner wall of the turbine end flange (2) and / or the impeller end flange (3).

6. The floating bearing structure according to claim 4, characterized in that: The oil guide groove (5) is constructed as a straight groove; The oil guide groove (5) is configured as multiple channels and is configured to be distributed circumferentially along the inner wall of the turbine end flange (2) and / or the impeller end flange (3).

7. The floating bearing structure according to claim 6, characterized in that: It further includes multiple end face grooves (7); the turbine end flange (2) has a first thrust surface (21) disposed at one end away from the bearing middle section (1), and the impeller end flange (3) has a second thrust surface (31) disposed at one end away from the bearing middle section (1); the end face grooves (7) are disposed on the first thrust surface (21) and the second thrust surface (31); The end face groove (7) provided on the first thrust surface (21) is connected to a plurality of oil guide grooves (5) provided on the inner wall of the turbine end flange (2); the end face groove (7) provided on the second thrust surface (31) is connected to a plurality of oil guide grooves (5) provided on the inner wall of the impeller end flange (3).

8. A core component of a turbocharger, characterized in that, include: A housing (6), wherein the housing (6) has a bearing mounting groove (61) and a lubricant flow channel (62); and The floating bearing structure according to any one of claims 1-7; The floating bearing structure is disposed in the bearing mounting groove (61); the lubricant flow channel (62) is configured to communicate with the oil inlet (4).

9. The core component of the turbocharger according to claim 8, characterized in that: The lubricant flow channel (62) includes an inlet flow channel (621), a collecting flow channel (622), and an outlet flow channel (623). The lubricant enters from the inlet flow channel (621), flows through the floating bearing structure, and then flows into the collecting flow channel (622) from both ends of the bearing mounting groove (61) and the two ends of the floating bearing structure, and then flows out from the outlet flow channel (623) through the collecting flow channel (622). The lubricant channel (62) further includes a bypass channel (624) disposed in the inlet channel (621).

10. The core component of the turbocharger according to claim 9, characterized in that: The bearing mounting groove (61) includes an impeller end groove section (611), a turbine end groove section (612), and an intermediate groove section (613) disposed between the impeller end groove section (611) and the turbine end groove section (612). The axial dimension of the impeller end slot section (611) is set to be larger than that of the turbine end slot section (612). The bearing mounting groove (61) further includes a liquid storage cavity (614) disposed between the intermediate groove section (613) and the bearing middle section (1).

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