A supercharger

Abstract

The application discloses a supercharger, and relates to the technical field of superchargers, which comprises a rotating shaft, an intermediate shell, a thrust bearing, an opening and closing mechanism and the like.

Description

Technical Field

[0001] This application relates to the field of turbocharger technology, and particularly to a turbocharger. Background Technology

[0002] Turbochargers are key components for improving engine performance, increasing power output, and reducing fuel consumption and emissions. As turbochargers evolve towards higher pressure ratios, higher flow rates, and higher speeds, oil leakage at the turbocharger's pressure end has become increasingly prominent. Oil leakage leads to decreased turbocharger performance, increased oil consumption, and in severe cases, turbocharger damage.

[0003] Traditional turbocharger sealing ring technology mainly utilizes oil baffles and shaft seal structures to create a labyrinth seal, extending the leakage path of engine oil to the compressor end, thereby achieving a seal. However, when the engine is idling or unloaded for extended periods, the thrust bearing bearing near the turbine end typically bears the axial force of the turbocharger, while the thrust bearing near the pressure end does not. At this time, there is still a certain amount of pressurized engine oil flowing through the axial gap between the thrust bearing bearing bearing near the pressure end and the shaft seal (engine oil pressure around 80-200 kPa). If the rotor shaft drives the shaft seal to rotate at this time, the labyrinth seal still cannot completely eliminate the dynamic-static gap, causing engine oil to be thrown out radially at a certain speed, which can easily lead to compressor oil leakage problems.

[0004] Meanwhile, when the engine is running at high operating conditions, the exhaust temperature in front of the turbine (the engine exhaust temperature, which is basically the same as the turbine inlet temperature) is high. The heat will be transferred to the floating bearing near the turbine through the shaft. Excessive temperature will reduce the viscosity of the oil and affect the oil film bearing capacity, or cause carbon deposits. These problems will lead to wear of the floating bearing and seriously affect the reliability of the turbocharger.

[0005] Therefore, how to prevent oil leakage between the thrust bearing near the pressure end bearing surface and the shaft seal, and how to prevent the floating bearing from overheating are technical problems that need to be solved by those skilled in the art. Summary of the Invention

[0006] The purpose of this application is to provide a turbocharger that can shut off the oil passage supplying oil to the axial contact surface of the thrust bearing and shaft seal, thereby preventing oil from appearing on the contact surface between the thrust bearing and shaft seal and completely solving the oil leakage problem; at the same time, it can also control the amount of cooling oil in the floating bearing according to the engine operating conditions, so that the floating bearing is at a safe operating temperature and improve the reliability of the turbocharger.

[0007] To achieve the above objectives, this application provides a booster, comprising:

[0008] Shaft;

[0009] An intermediate shell is provided inside, which has an oil inlet channel and a bearing mounting position. The intermediate shell includes a support part located on the outer periphery of the rotating shaft. A floating bearing is filled between the support part and the rotating shaft in a circumferential interval. The support part has a main oil passage and a secondary oil passage that connect the oil inlet channel and the floating bearing. The main oil passage and the secondary oil passage are circumferentially distributed.

[0010] A thrust bearing is fixedly installed at the bearing mounting position. The thrust bearing has a first oil passage and a slot. The slot communicates with the first oil passage and divides the first oil passage into a first oil delivery channel and a second oil delivery channel. The bottom of the slot has a first inclined surface at an angle of less than 90° to the oil delivery direction of the first oil passage. The oil inlet end of the first oil delivery channel communicates with the oil inlet channel. The oil outlet end of the first oil delivery channel is located on the first inclined surface. The oil inlet end of the second oil delivery channel is located on one of the slot walls. The oil outlet end of the second oil delivery channel delivers oil to the axial contact surface of the thrust bearing and the shaft seal.

[0011] The opening and closing mechanism includes a slider and an elastic element disposed in the intermediate shell. The slider is provided with a second inclined surface that cooperates with the first inclined surface. The elastic element is used to provide an elastic force for sealing and pressing the second inclined surface against the first inclined surface. The liquid in the first oil delivery channel is used to provide pressure to the second inclined surface away from the first inclined surface.

[0012] The slider has a connecting rod on the side opposite to the first inclined surface. The connecting rod passes through the support and slides into the auxiliary oil passage. The sliding connecting rod is used to connect or disconnect the oil inlet channel and the auxiliary oil passage.

[0013] In some embodiments, the angle between the first inclined surface and the oil conveying direction of the first oil passage is greater than 0° and less than or equal to 45°.

[0014] In some embodiments, the liquid pressure in the first oil delivery channel changes dynamically with the operating conditions of the booster, and the dynamically changing liquid pressure exists in at least two states. In one state, the component of the liquid pressure acting on the second inclined surface in the sliding direction of the slider is greater than the elastic force of the elastic element; in the other state, the component of the liquid pressure acting on the second inclined surface in the sliding direction of the slider is less than the elastic force of the elastic element.

[0015] In some embodiments, the slot has an opening on the bearing surface of the thrust bearing opposite to the shaft seal, the slider enters and exits the slot through the opening, and the elastic force provided by the elastic element to the slider is opposite in direction to the axial pressure of the shaft seal on the thrust bearing.

[0016] In some embodiments, the outer periphery of the slider slides and seals against the groove wall of the slot, and the slot between the first inclined surface and the second inclined surface forms a sealed cavity communicating with the first oil delivery channel and the second oil delivery channel.

[0017] In some embodiments, the connecting rod is provided with an inner channel, one end of which has an oil inlet located on the outer circumferential surface of the connecting rod, and the other end has an oil outlet communicating with the auxiliary oil passage;

[0018] When the first inclined surface and the second inclined surface are sealed and pressed together, the oil inlet is misaligned with the oil inlet channel to shut off the oil inlet channel and the auxiliary oil passage;

[0019] When the first inclined surface separates from the second inclined surface, the oil inlet is connected to the oil inlet channel to connect the oil inlet channel and the auxiliary oil passage.

[0020] In some embodiments, the system further includes a turbine unit and a compressor unit. The turbine unit includes a turbine housing and a turbine rotor. The compressor unit includes a compressor housing and a compressor impeller. The turbine housing and the compressor housing are fixedly connected at both ends of the intermediate housing. The turbine rotor and the compressor impeller are coaxially connected via a rotating shaft. The thrust bearing is sleeved on the outer circumference of the rotating shaft.

[0021] In some embodiments, the support portion abuts axially against the bearing surface of the thrust bearing facing the turbine unit, the support portion is provided with a receiving groove, the slider is slidably disposed in the receiving groove, the elastic element is a spring, the spring is sleeved on the outer periphery of the connecting rod, and the two ends of the spring are respectively connected to the bottom of the slider and the receiving groove.

[0022] In some embodiments, the shaft seal is sleeved on the outer periphery of the rotating shaft and abuts against the bearing surface of the thrust bearing facing the compressor unit.

[0023] In some embodiments, a thrust sleeve is fitted on the rotating shaft, and a thrust bearing is fitted on the outer periphery of the thrust sleeve. The inner ring of the thrust bearing has a first annular cavity that communicates with the oil outlet end of the second oil delivery channel. The axial contact surface of the thrust bearing and the shaft seal corresponds to the first annular cavity.

[0024] In some embodiments, the thrust bearing is further provided with a second oil passage, the oil inlet end of the second oil passage is connected to the oil inlet channel, the inner ring of the thrust bearing is provided with a second annular cavity connected to the oil outlet end of the second oil delivery channel, the first annular cavity and the second annular cavity are independently provided, and the axial contact surface of the thrust bearing and the thrust sleeve corresponds to the second annular cavity.

[0025] The beneficial effects of this application are as follows: When the engine is idling for a long time under no-load conditions, the oil pressure in the oil inlet channel is low, resulting in low pressure in the first oil passage. The elastic force of the elastic element can overcome the liquid pressure in the first oil passage, causing the slider to move into the slot until the second inclined surface on the slider seals tightly against the first inclined surface of the slot. The first and second oil passages are then shut off. At this time, the second oil passage cannot continue to supply oil to the axial contact surface of the thrust bearing and shaft seal, preventing oil from appearing on the contact surface of the thrust bearing and shaft seal, thus completely solving the oil leakage problem. When the engine is running at high operating conditions, the turbocharger speed is high, and the oil pressure in the oil inlet channel also increases accordingly. This causes the pressure in the first oil passage to overcome the elastic force of the elastic element, causing the second inclined surface of the slider to separate from the first inclined surface of the slot. The first oil passage remains connected to the second oil passage through the slot, thereby supplying oil to the axial contact surface of the thrust bearing and shaft seal.

[0026] A connecting rod is provided on the side of the slider away from the first inclined surface. The connecting rod can move synchronously with the slider. When the engine is idling for a long time or under no-load conditions, the connecting rod can be in the position of shutting off the oil inlet channel and the auxiliary oil passage. At this time, the oil supply needs of the floating bearing can be met only through the main oil passage. When the engine is under high operating conditions, the connecting rod moves with the slider to the position of opening the oil inlet channel and the auxiliary oil passage, thereby increasing the oil supply of the floating bearing through the auxiliary oil passage. This leads to the high-pressure oil being diverted to the shoulder of the floating bearing near the turbine unit. The high-pressure oil is then sprayed onto the shoulder, reducing the oil film temperature at the floating bearing, improving the oil film bearing capacity, reducing carbon deposits, and improving the reliability of the shaft system. Attached Figure Description

[0027] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only embodiments of this application. For those skilled in the art, other drawings can be obtained based on the provided drawings without creative effort.

[0028] Figure 1 This is a schematic diagram of the turbocharger structure provided in an embodiment of this application;

[0029] Figure 2 for Figure 1 Enlarged structural diagram at point A in the middle;

[0030] Figure 3 This is a schematic diagram showing the first oil passage in a conductive state as provided in the embodiments of this application;

[0031] Figure 4 for Figure 1 Enlarged structural diagram at point B;

[0032] Figure 5This is a schematic diagram showing the state of the internal channel connecting the oil inlet channel and the auxiliary oil passage provided in an embodiment of this application;

[0033] Figure 6 This application provides a schematic diagram of the three-dimensional structure of the thrust bearing in an embodiment.

[0034] Figure 7 This is a cross-sectional view of a thrust bearing provided in an embodiment of this application;

[0035] Figure 8 This is a schematic diagram of the opening and closing mechanism provided in an embodiment of this application;

[0036] Figure 9 This is a cross-sectional view of the thrust bearing provided in an embodiment of this application.

[0037] Figure 10 This is a schematic diagram of the first oil delivery channel structure provided in an embodiment of this application;

[0038] Figure 11 This is a schematic diagram of the second oil delivery channel structure provided in an embodiment of this application.

[0039] In the diagram: 1-Intermediate shell; 2-Thrust bearing; 3-Turbine shell; 4-Turbine rotor; 5-Compressor shell; 6-Compressor impeller; 7-Shaft; 8-Slider; 9-Elastic element;

[0040] 11-Oil inlet channel; 12-Support section; 13-Receiving groove; 121-Secondary oil passage;

[0041] 21-First oil passage; 22-First annular cavity; 23-Second annular cavity; 24-Slot; 25-Second oil passage; 211-First oil delivery channel; 212-Second oil delivery channel; 241-First inclined surface;

[0042] 71-Shaft seal; 72-Thrust sleeve; 73-Floating bearing;

[0043] 81-Second inclined surface; 82-Connecting rod; 821-Inner channel. Detailed Implementation

[0044] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0045] It should be noted that in this embodiment, the orientation or positional relationship indicated by terms such as "upper," "lower," "front," and "rear" is based on the orientation or positional relationship shown in the accompanying drawings. It is used only for the convenience of describing this application and for simplifying the description, and does 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, it should not be construed as a limitation of this application. Furthermore, "first," "second," "third," and "fourth" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0046] To enable those skilled in the art to better understand the present application, the present application will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0047] like Figures 1 to 11 As shown, in this embodiment, a turbocharger is provided, including an intermediate housing 1, a thrust bearing 2 and an opening and closing mechanism. An oil inlet channel 11 is provided inside the intermediate housing 1. External engine oil is delivered to the intermediate housing 1 through the oil inlet channel 11 and is supplied to at least the two bearing surfaces of the thrust bearing 2, thereby ensuring that the two bearing surfaces of the thrust bearing 2 have sufficient engine oil.

[0048] The intermediate shell 1 also has a bearing mounting position, and the thrust bearing 2 can be fixedly installed at the bearing mounting position to ensure that the thrust bearing 2 can be fixed relative to the intermediate shell 1. The specific structural features of the bearing mounting position will not be described in detail here, but can be referred to the existing technology.

[0049] The thrust bearing 2 has two bearing surfaces: one facing the compressor unit and the other facing the turbine unit. The bearing surface facing the compressor unit abuts against the shaft seal 71, and the bearing surface facing the turbine unit abuts against the thrust sleeve 72. When the engine is idling or under no-load conditions for a long time, the compressor unit has a small intake flow rate, low intake temperature, and low power. At this time, the turbine unit has the same flow rate as the compressor unit, but the turbine inlet temperature is high, resulting in a lower expansion ratio of the turbine than that of the compressor unit. In addition, the turbine rotor 4 is smaller than the compressor impeller 6. This causes the axial force of the turbocharger to point from the turbine unit to the compressor unit, making the shaft 7 and the shaft seal 71 and thrust sleeve 72 on the shaft 7 tend to move towards the compressor unit. At this time, in order to resist the axial movement of the shaft 7, the thrust bearing 2 will bear the axial force of the thrust sleeve 72 on the bearing surface facing the turbine unit, while the bearing surface facing the compressor unit does not need to bear the axial force of the shaft seal 71.

[0050] The pressure ratio is the ratio of the compressor unit's outlet pressure to its inlet pressure; the expansion ratio is the ratio of the turbine unit's inlet pressure to its outlet pressure.

[0051] When the bearing surface of the thrust bearing 2 facing the compressor unit does not bear the axial force of the shaft seal 71, a certain axial clearance will exist between the bearing surface of the thrust bearing 2 and the shaft seal 71, which can easily lead to oil leakage from this axial clearance. This application, however, completely closes the oil circuit during long-term idling and no-load operation of the engine, preventing the oil from reaching the aforementioned axial clearance and thus eliminating the oil leakage problem.

[0052] Specifically, the thrust bearing 2 is provided with a first oil passage 21 and an oil groove. The slot 24 is connected to the first oil passage 21 and divides the complete first oil passage 21 into a first oil delivery channel 211 and a second oil delivery channel 212. The bottom of the slot 24 has a first inclined surface 241 with an angle of less than 90° to the oil delivery direction of the first oil passage 21. The oil inlet end of the first oil delivery channel 211 is connected to the oil inlet channel 11, so that the engine oil can enter the first oil passage 21. The oil outlet end of the first oil delivery channel 211 is located on the first inclined surface 241.

[0053] The oil inlet of the second oil supply channel 212 is located on one side wall of the slot 24, and the oil outlet of the second oil supply channel 212 can supply oil to the thrust bearing 2 and the axial contact surface of the bearing.

[0054] The opening and closing mechanism includes a slider 8 and an elastic element 9 disposed in the intermediate shell 1. The slider 8 can be movably disposed in the groove. The slider 8 is provided with a second inclined surface 81 that cooperates with the first inclined surface 241. When the engine is idling for a long time under no-load conditions, the oil pressure in the oil inlet channel 11 is small, and the corresponding oil pressure in the first oil delivery channel 211 is also small. The elastic element 9 can overcome the oil pressure in the first oil delivery channel 211, so that the slider 8 moves into the groove until the second inclined surface 81 abuts against the first inclined surface 241. Under the elastic force of the elastic element 9, the second inclined surface 81 and the first inclined surface 241 are sealed and abutted, thereby shutting off the oil outlet of the first oil delivery channel 211 on the first inclined surface 241, realizing the physical cut-off of the oil supply of the second oil delivery channel 212, so that there is no oil leakage between the bearing surface of the thrust bearing 2 and the contact surface of the shaft seal 71.

[0055] When the engine is operating at high operating conditions, the intake flow of the compressor unit of the turbocharger is large in most cases. At this time, the flow of the turbine unit is the same as that of the compressor, and the turbine inlet temperature is still high, resulting in a lower turbine expansion ratio than the compressor pressure ratio. The axial force of the turbocharger is still directed from the turbine unit to the compressor unit. However, when the intake flow of the compressor unit increases to a certain extent, the pressure ratio drops significantly, and the pressure ratio may be less than the expansion ratio. At this time, the axial force of the turbocharger will be directed from the compressor unit to the turbine unit. That is, the bearing surface of the thrust bearing 2 facing the compressor unit bears the axial force of the shaft seal 71, and the bearing surface of the thrust bearing 2 facing the turbine unit does not need to bear the axial force of the thrust sleeve 72.

[0056] When the engine is running at high operating conditions, the turbocharger speed is relatively high, and the oil pressure in the oil inlet passage 11 increases significantly. This leads to an increase in the oil pressure in the first oil delivery passage 211. After increasing to a certain level, the oil pressure will generate a thrust on the second inclined surface 81 that is sufficient to overcome the elastic force of the elastic element 9, thereby pushing the second inclined surface 81 away from the first inclined surface 241. At this time, the oil outlet end of the first oil delivery passage 211 is opened, and the first oil delivery passage 211 and the second oil delivery passage 212 remain connected. The first oil passage 21 can continue to provide sufficient oil to the contact surface between the thrust bearing 2 and the shaft seal 71. Since the thrust bearing 2 faces the bearing surface of the compressor unit and bears the axial force of the shaft seal 71, there is no axial clearance between the thrust bearing 2 and the shaft seal 71, or the axial clearance is compressed to the point that it does not meet the requirements for oil leakage. Therefore, the oil cannot leak from the contact surface between the thrust bearing 2 and the shaft seal 71. Moreover, at this time, the turbocharger speed is relatively high, the pressure ratio is relatively high, and the back pressure of the compressor impeller 6 is also high. Under this condition, the compressor unit is not prone to oil leakage.

[0057] It should be noted that, based on the fact that the first inclined surface 241 and the first oil passage 21 form an angle of less than 90° with the oil delivery direction, the second inclined surface 81 also forms an angle of less than 90° with the oil delivery direction of the first oil passage 21. Therefore, when the oil pressure in the first oil passage 211 acts on the second inclined surface 81, it will generate a component force that pushes the second inclined surface 81 away from the first inclined surface 241. As the oil pressure increases, this component force will also increase. Thus, after increasing to a certain extent, it can overcome the elastic force of the elastic element 9 and cause the second inclined surface 81 of the slider 8 to disengage from the first inclined surface 241.

[0058] As can be seen, this application, through the movable slider 8, elastic element 9, and hydraulic drive, enables the elastic force of the elastic element 9 to overcome the oil pressure in the first oil supply channel 211 when the engine is idling for a long time under no-load conditions. This allows the second inclined surface 81 on the slider 8 to seal tightly against the first inclined surface 241 of the slot 24, shutting off the first oil passage 21 and completely solving the oil leakage problem. When the engine is running under high operating conditions, the pressure in the first oil passage 21 can overcome the elastic force of the elastic element 9, causing the second inclined surface 81 of the slider 8 to separate from the first inclined surface 241, opening the first oil passage 21, and thus supplying oil to the axial contact surface of the thrust bearing 2 and the shaft seal 71.

[0059] Furthermore, Figure 3In this context, α represents the angle between the first inclined surface 241 and the oil delivery direction. To make it easier for the oil in the first oil delivery channel 211 to exert pressure on the second inclined surface 81, pushing the slider 8 away from the first inclined surface 241, the angle α can be minimized, for example, 0° < α ≤ 45°. This ensures that the component of the oil pressure acting on the second inclined surface 81 in the direction of slider 8 movement is greater than or equal to the component in the oil delivery direction. This increases the thrust generated by the oil on the slider 8 in the direction of slider 8 movement and reduces the friction between the slider 8 and the side wall of the slot 24. Furthermore, if the angle α is too small, with a fixed slider 8 height, the length of the second inclined surface 81 in the sliding direction of the slider 8 will be short. This will result in the oil thrust only pushing the slider 8 a short distance. Although this can still achieve the connection between the first oil delivery channel 211 and the second oil delivery channel 212, there is a possibility that the slider 8 cannot fully open the oil inlet of the second oil delivery channel 212 due to insufficient movement distance, affecting the oil delivery volume of the first oil passage 21. Therefore, 15° < α ≤ 30° is preferable.

[0060] Furthermore, the liquid pressure in the oil inlet passage 11 changes dynamically with the operating conditions of the turbocharger. That is, when the engine is idling for a long time under no-load conditions, the liquid (oil) pressure in the oil inlet passage 11 is relatively low; when the engine is running under high operating conditions, the liquid pressure in the oil inlet passage 11 is relatively high. This application binds the lubrication requirements of the bearing surface of the thrust bearing 2 to the dynamic operating conditions of the turbocharger, and uses the inherent parameter of the turbocharger - oil pressure - as a control signal. Without additional sensors or electronic control, it can achieve low-condition oil cut-off and leak prevention, and high-condition oil supply and lubrication.

[0061] It should be noted that the liquid pressure in the first oil delivery channel 211 is consistent with the liquid pressure in the oil inlet channel 11, and therefore will also change dynamically. The dynamically changing liquid pressure in the first oil delivery channel 211 exists in at least two states. In one state, the component of the liquid pressure acting on the second inclined surface 81 in the sliding direction of the slider 8 is greater than the elastic force of the elastic element 9, i.e., the high working condition state, which causes the second inclined surface 81 to separate from the first inclined surface 241 and open the first oil passage 21. In the other state, the component of the liquid pressure acting on the second inclined surface 81 in the sliding direction of the slider 8 is less than the elastic force of the elastic element 9, i.e., the low working condition state, which causes the second inclined surface 81 to seal against the first inclined surface 241 and close the first oil passage 21.

[0062] The slot 24 has an opening on the bearing surface of the thrust bearing 2 away from the shaft seal 71, through which the slider 8 can enter the slot 24. The elastic force provided by the elastic element 9 to the slider 8 is opposite to the axial pressure of the shaft seal 71 on the thrust bearing 2. That is, when the second inclined surface 81 seals against the second inclined surface 81, the elastic force generated by the elastic element 9 will indirectly act on the thrust bearing 2 through the slider 8. The axial pressure of the shaft seal 71 on the thrust bearing 2 is opposite to this elastic force, so that the elastic force can bear part of the axial pressure of the shaft seal 71 on the thrust bearing 2, thereby reducing the pressure of the thrust bearing 2 on the bearing mounting position. In other words, due to the elastic force provided by the elastic element 9, the bearing capacity of the thrust bearing 2 bearing the shaft seal 71 comes from the bearing mounting position on one hand and from the elastic force of the elastic element 9 on the other hand, thereby sharing the pressure on the bearing mounting position, improving the stability of the bearing mounting position and increasing the service life of the turbocharger.

[0063] In addition, to prevent oil leakage from the slot 24 and affecting the amount of oil in the first oil passage 21, the outer periphery of the slider 8 can be slidably sealed to the groove wall of the slot 24, so that the slot 24 between the first inclined surface 241 and the second inclined surface 81 forms a sealed cavity that communicates with the first oil delivery channel 211 and the second oil delivery channel 212; when the first inclined surface 241 and the second inclined surface 81 are separated, the sealed cavity can automatically connect the first oil delivery channel 211 and the second oil delivery channel 212, thereby opening the first oil passage 21.

[0064] In some embodiments, the slot 24 can be a slot structure with a regular cross section, such as a rectangular slot or a cylindrical slot. The structure of the outer periphery of the slider 8 is adapted to the structure of the slot 24. No further restrictions are imposed here, and all fall within the protection scope of this application.

[0065] In addition, the turbocharger also includes a rotating shaft 7, and the intermediate housing 1 includes a support portion 12 located on the outer periphery of the rotating shaft 7. A floating bearing 73 is filled between the support portion 12 and the rotating shaft 7 in a circumferential interval. The support portion 12 is provided with a main oil passage and a secondary oil passage 121 that connect the oil inlet channel 11 and the floating bearing 73. The main oil passage and the secondary oil passage 121 are circumferentially distributed. The main oil passage always maintains the connection between the floating bearing 73 and the oil inlet channel 11, so that the floating bearing 73 has a certain lubrication effect.

[0066] However, when the engine is running under high operating conditions, the oil demand of the floating bearing 73 will increase in order to ensure the lubrication effect of the floating bearing 73. Therefore, this application adds an auxiliary oil passage 121 and controls the connection between the auxiliary oil passage 121 and the oil inlet passage 11 through the connecting rod 82 structure, thereby changing the amount of oil delivered to the floating bearing 73 and ensuring the operational reliability of the floating bearing 73.

[0067] Specifically, a connecting rod 82 is provided on the side of the slider 8 away from the first inclined surface 241. The connecting rod 82 can pass through the support part 12 and slide into the auxiliary oil passage 121. The connecting rod 82 can move synchronously with the slider 8, thereby connecting or disconnecting the oil inlet channel and the auxiliary oil passage 121 through the sliding connecting rod 82.

[0068] Furthermore, an inner channel 821 is provided on the connecting rod 82. One end of the inner channel 821 has an oil inlet located on the outer circumference of the connecting rod 82, and the other end has an oil outlet connected to the auxiliary oil passage 121. When the engine is running under high operating conditions, the oil pressure in the oil inlet channel 11 increases significantly, the second inclined surface 81 separates from the first inclined surface 241, and the slider 8 drives the connecting rod 82 to move in the auxiliary oil passage 121. Under high operating conditions, the oil demand of the floating bearing 73 increases. Therefore, when the first inclined surface 241 separates from the second inclined surface 81, the oil inlet connects with the oil inlet channel 11 to connect the oil inlet channel 11 and the auxiliary oil passage 121. This allows the oil in the auxiliary oil passage 121 to flow to the shoulder of the floating bearing 73 and be sprayed onto the shoulder by high-pressure oil. This reduces the heat transfer from the rotating shaft 7 to the floating bearing, lowers the oil film temperature at the floating bearing 73, improves the oil film bearing capacity, reduces carbon deposits, and improves the reliability of the shaft system.

[0069] Furthermore, under high engine operating conditions, the turbine unit has high pressure, preventing oil leakage caused by the auxiliary oil passage 121 supplying oil to the floating bearing 73.

[0070] When the engine is idling for a long time under no-load conditions, the first inclined surface 241 and the second inclined surface 81 are sealed and pressed together. The oil demand of the floating bearing 73 can be met by the main oil passage. Therefore, under the action of the slider 8, the connecting rod 82 causes the oil inlet and the oil inlet channel 11 to be misaligned, thereby shutting off the oil inlet channel 11 and the auxiliary oil passage 121.

[0071] The turbocharger of this application also includes a turbine unit and a compressor unit. The turbine unit includes a turbine housing 3 and a turbine rotor 4. The compressor unit includes a compressor housing 5 and a compressor impeller 6. The turbine housing 3 and the compressor housing 5 are fixedly connected at both ends of the intermediate housing 1. The turbine rotor 4 and the compressor impeller 6 are coaxially connected through a rotating shaft 7. The thrust bearing 2 is sleeved on the outer periphery of the rotating shaft 7.

[0072] The intermediate shell 1 includes a support portion 12 located on the outer periphery of the rotating shaft 7. The support portion 12 abuts against the bearing surface of the thrust bearing 2 facing the turbine unit in the axial direction, providing a certain support for the thrust bearing 2. A receiving groove 13 is provided on the support portion 12, and the slider 8 is slidably disposed in the receiving groove 13. The receiving groove 13 corresponds to the opening of the slot 24, so that the slider 8 can smoothly enter the slot 24 from the receiving groove 13. The elastic element 9 can be a spring with a preload, and the two ends of the spring are respectively connected to the bottom of the slider 8 and the receiving groove 13, thereby providing the slider 8 with an elastic force to move towards the slot 24.

[0073] Furthermore, the shaft seal 71 is fitted around the outer circumference of the rotating shaft 7 and rotates synchronously with the rotating shaft 7. The shaft seal 71 abuts against the bearing surface of the thrust bearing 2 facing the compressor unit. The thrust sleeve 72 is fitted around the rotating shaft 7 and also rotates synchronously with the rotating shaft 7. The thrust bearing 2 is fitted around the outer circumference of the thrust sleeve 72, and the thrust sleeve 72 has an annular portion that abuts against the bearing surface of the thrust bearing 2. The inner ring of the thrust bearing 2 is provided with a first annular cavity 22 that communicates with the oil outlet end of the second oil supply channel 212. The axial contact surfaces of the thrust bearing 2 and the shaft seal 71 correspond to the first annular cavity 22, so that the oil in the first annular cavity 22 can penetrate to the axial contact surfaces of the thrust bearing 2 and the shaft seal 71, thereby achieving lubrication of the bearing surface on one side of the thrust bearing 2.

[0074] The thrust bearing 2 is also provided with a second oil passage 25. The oil inlet end of the second oil passage 25 is connected to the oil inlet channel 11. The inner ring of the thrust bearing 2 is provided with a second annular cavity 23 connected to the oil outlet end of the second oil delivery channel 212. The first annular cavity 22 and the second annular cavity 23 are independently set. The axial contact surface of the thrust bearing 2 and the thrust sleeve 72 corresponds to the second annular cavity 23, so that the oil in the second annular cavity 23 can penetrate to the axial contact surface of the thrust bearing 2 and the thrust sleeve 72, thereby achieving lubrication of the bearing surface on the other side of the thrust bearing 2.

[0075] It should be noted that in this specification, relational terms such as first and second are used only to distinguish one entity from several other entities, and do not necessarily require or imply any such actual relationship or order between these entities.

[0076] This document uses specific examples to illustrate the principles and implementation methods of this application. The descriptions of the embodiments above are only for the purpose of helping to understand the method and core ideas of this application. It should be noted that those skilled in the art can make several improvements and modifications to this application without departing from the principles of this application, and these improvements and modifications also fall within the protection scope of the claims of this application.

Claims

1. A booster, characterized in that, include: Rotating shaft (7); An intermediate shell (1) is provided with an oil inlet channel (11) and a bearing mounting position inside. The intermediate shell (1) includes a support part (12) located on the outer periphery of the rotating shaft (7). A floating bearing (73) is filled between the support part (12) and the rotating shaft (7) in a circumferential interval. The support part (12) is provided with a main oil passage and a secondary oil passage (121) connecting the oil inlet channel (11) and the floating bearing (73). The main oil passage and the secondary oil passage (121) are distributed circumferentially. A thrust bearing (2) is fixedly installed at the bearing mounting position. The thrust bearing (2) is provided with a first oil passage (21) and a slot (24). The slot (24) is connected to the first oil passage (21) and divides the first oil passage (21) into a first oil delivery channel (211) and a second oil delivery channel (212). The bottom of the slot (24) has a first inclined surface (241) at an angle of less than 90° to the oil delivery direction of the first oil passage (21). The oil inlet end of the first oil delivery channel (211) is connected to the oil inlet channel (11). The oil outlet end of the first oil delivery channel (211) is located on the first inclined surface (241). The oil inlet end of the second oil delivery channel (212) is located on one of the groove walls of the slot (24). The oil outlet end of the second oil delivery channel (212) delivers oil to the axial contact surface of the thrust bearing (2) and the shaft seal (71). The opening and closing mechanism includes a slider (8) and an elastic element (9) disposed on the intermediate shell (1). The slider (8) is provided with a second inclined surface (81) that cooperates with the first inclined surface (241). The elastic element (9) is used to provide an elastic force for the second inclined surface (81) to seal against the first inclined surface (241). The liquid in the first oil channel (211) is used to provide pressure for the second inclined surface (81) away from the first inclined surface (241). The slider (8) is provided with a connecting rod (82) on the side away from the first inclined surface (241). The connecting rod (82) passes through the support part (12) and slides into the auxiliary oil passage (121). The sliding connecting rod (82) is used to connect or disconnect the oil inlet channel (11) and the auxiliary oil passage (121).

2. The booster according to claim 1, characterized in that, The angle between the first inclined surface (241) and the oil conveying direction of the first oil passage (21) is greater than 0° and less than or equal to 45°.

3. The booster according to claim 1, characterized in that, The liquid pressure in the first oil delivery channel (211) changes dynamically with the working conditions of the booster, and the dynamically changing liquid pressure exists in at least two states. In one state, the component of the liquid pressure acting on the second inclined surface (81) in the sliding direction of the slider (8) is greater than the elastic force of the elastic element (9); in the other state, the component of the liquid pressure acting on the second inclined surface (81) in the sliding direction of the slider (8) is less than the elastic force of the elastic element (9).

4. The booster according to claim 1, characterized in that, The slot (24) has an opening on the bearing surface of the thrust bearing (2) away from the shaft seal (71). The slider (8) enters and exits the slot (24) through the opening, and the elastic force provided by the elastic element (9) to the slider (8) is opposite to the axial pressure of the shaft seal (71) on the thrust bearing (2).

5. The booster according to claim 1, characterized in that, The outer periphery of the slider (8) slides and seals with the groove wall of the slot (24), and the slot (24) between the first inclined surface (241) and the second inclined surface (81) forms a sealed cavity communicating with the first oil delivery channel (211) and the second oil delivery channel (212).

6. The booster according to claim 1, characterized in that, The connecting rod (82) is provided with an inner channel (821). One end of the inner channel (821) has an oil inlet located on the outer circumference of the connecting rod (82), and the other end has an oil outlet communicating with the auxiliary oil passage (121). When the first inclined surface (241) and the second inclined surface (81) are sealed together, the oil inlet is misaligned with the oil inlet channel (11) to shut off the oil inlet channel (11) and the auxiliary oil passage (121). When the first inclined surface (241) separates from the second inclined surface (81), the oil inlet is connected to the oil inlet channel (11) to connect the oil inlet channel (11) and the auxiliary oil passage (121).

7. The booster according to claim 1, characterized in that, It also includes a turbine unit and a compressor unit. The turbine unit includes a turbine housing (3) and a turbine rotor (4). The compressor unit includes a compressor housing (5) and a compressor impeller (6). The turbine housing (3) and the compressor housing (5) are fixedly connected at both ends of the intermediate housing (1). The turbine rotor (4) and the compressor impeller (6) are coaxially connected through the rotating shaft (7). The thrust bearing (2) is sleeved on the outer circumference of the rotating shaft (7).

8. The booster according to claim 7, characterized in that, The support part (12) abuts against the bearing surface of the thrust bearing (2) facing the turbine unit in the axial direction. The support part (12) is provided with a receiving groove (13). The slider (8) is slidably disposed in the receiving groove (13). The elastic element (9) is a spring. The spring is sleeved on the outer periphery of the connecting rod, and the two ends of the spring are respectively connected to the bottom of the slider (8) and the receiving groove (13).

9. The booster according to claim 7, characterized in that, The shaft seal (71) is fitted around the outer circumference of the rotating shaft (7) and abuts against the bearing surface of the thrust bearing (2) facing the compressor unit.

10. The booster according to claim 7, characterized in that, A thrust sleeve (72) is fitted on the rotating shaft (7), and the thrust bearing (2) is fitted on the outer periphery of the thrust sleeve (72). The inner ring of the thrust bearing (2) is provided with a first annular cavity (22) that communicates with the oil outlet end of the second oil supply channel (212). The axial contact surfaces of the thrust bearing (2) and the shaft seal (71) correspond to the first annular cavity (22).

11. The booster according to claim 10, characterized in that, The thrust bearing (2) is also provided with a second oil passage (25), the oil inlet end of the second oil passage (25) is connected to the oil inlet channel (11), the inner ring of the thrust bearing (2) is provided with a second annular cavity (23) connected to the oil outlet end of the second oil delivery channel (212), the first annular cavity (22) and the second annular cavity (23) are independently set, and the axial contact surface of the thrust bearing (2) and the thrust sleeve (72) corresponds to the second annular cavity (23).

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