Supercharger

Abstract

The invention discloses a supercharger, and relates to the technical field of superchargers. An oil inlet channel and a bearing mounting position are arranged in the middle shell, the middle shell comprises a supporting part, and the gap between the supporting part and the circumferential direction of the rotating shaft is filled with a floating bearing, a supporting part main oil duct and a supporting part auxiliary oil duct; the thrust bearing is provided with a first oil duct and an inserting groove, the groove bottom of the inserting groove is provided with a first inclined face, the included angle between the first inclined face and the oil conveying direction of the first oil duct is smaller than 90 degrees, the oil inlet end of the first oil conveying channel is communicated with the oil inlet channel, and the oil outlet end of the first oil conveying channel is located on the first inclined face; the opening and closing mechanism comprises a sliding block and an elastic piece which are arranged on the middle shell, the sliding block is provided with a second inclined plane matched with the first inclined plane, and the elastic piece provides elastic force for the second inclined plane to tightly abut against the first inclined plane in a sealing mode; a connecting rod is arranged on the side, away from the first inclined face, of the sliding block, penetrates through the supporting part and slidably extends into the auxiliary oil channel, and the sliding connecting rod is used for communicating or disconnecting the oil inlet channel and the auxiliary oil channel.

Description

Technical Field

[0001] The present application relates to the technical field of superchargers, and in particular to a supercharger. Background Art

[0002] Turbochargers are key components for improving engine performance, boosting power output while reducing fuel consumption and emissions. As turbochargers evolve toward higher pressure ratios, higher flow rates, and higher speeds, oil leakage on the compression side of the turbocharger has become increasingly prominent. Leakage can lead to decreased turbocharger performance, increased oil consumption, and, in severe cases, even turbocharger damage.

[0003] Traditional supercharger sealing ring technology mainly uses oil baffles and shaft seal structures to produce a labyrinth seal, extending the oil leakage path to the compressor end, thereby achieving sealing; however, when the supercharger is idling and operating at no load for a long time, the thrust bearing bearing surface close to the vortex end usually bears the supercharger axial force, and the thrust bearing close to the compression end does not bear the supercharger axial force. At this time, the axial gap between the thrust bearing bearing surface close to the compression end and the shaft seal still has oil at a certain pressure flowing through it (oil pressure is about 80-200kpa). At this time, if the rotor shaft drives the shaft seal to rotate, the labyrinth seal still cannot completely avoid the existence of the dynamic and static gaps, resulting in the oil being thrown out radially at a certain speed, which is prone to compressor oil leakage problems.

[0004] At the same time, when the engine is running at high operating conditions, the exhaust temperature before the turbine (engine exhaust temperature, basically the same as the turbine unit inlet temperature) is high, and the heat will be transferred to the floating bearing close to the turbine unit through the rotating shaft. Excessive temperature will reduce the oil viscosity and affect the oil film carrying capacity, or cause carbon deposits. These problems will cause wear of the floating bearing and seriously affect the reliability of the supercharger.

[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 supercharger that can shut off the oil channel that supplies oil to the axial contact surface of the thrust bearing and the shaft seal, thereby preventing oil from appearing on the contact surface between the thrust bearing and the shaft seal, and completely solving the oil leakage problem; at the same time, it also controls the cooling oil amount of the floating bearing according to the engine operating conditions, so that the floating bearing is at a safe operating temperature, thereby improving the reliability of the supercharger.

[0007] To achieve the above objectives, the present application provides a supercharger, comprising:

[0008] shaft;

[0009] An intermediate housing, wherein an oil inlet passage and a bearing mounting position are provided therein, the intermediate housing including a support portion located on the outer periphery of the rotating shaft, a floating bearing being filled in the circumferential interval between the support portion and the rotating shaft, and a main oil passage and a secondary oil passage connecting the oil inlet passage and the floating bearing, the main oil passage and the secondary oil passage being circumferentially distributed;

[0010] a thrust bearing fixedly disposed at the bearing mounting position, the thrust bearing being provided with a first oil passage and a slot, the slot being in communication with the first oil passage and dividing the first oil passage into a first oil delivery passage and a second oil delivery passage, the slot having a bottom having a first inclined surface forming an angle less than 90° with the oil delivery direction of the first oil passage, an oil inlet end of the first oil delivery passage being in communication with the oil inlet passage, an oil outlet end of the first oil delivery passage being located on the first inclined surface, an oil inlet end of the second oil delivery passage being located on a slot wall of the slot, and an oil outlet end of the second oil delivery passage delivering oil to an axial contact surface between the thrust bearing and the shaft seal;

[0011] an opening and closing mechanism comprising a slider and an elastic member provided on the intermediate housing, wherein the slider is provided with a second inclined surface cooperating with the first inclined surface, the elastic member is used to provide elastic force for the second inclined surface to seal against the first inclined surface, and the liquid in the first oil transfer channel is used to provide pressure for the second inclined surface to move away from the first inclined surface;

[0012] A connecting rod is provided on the side of the slider away from the first inclined surface. The connecting rod passes through the support portion and slides into the auxiliary oil channel. The sliding connecting rod is used to connect or disconnect the oil inlet channel and the auxiliary oil channel.

[0013] In some embodiments, an angle formed between the first inclined surface and the oil delivery direction of the first oil channel 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 working condition of the supercharger, 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 member; in another 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 member.

[0015] In some embodiments, the slot is provided with an opening on the bearing surface of the thrust bearing on the side facing away from the shaft seal, the slider enters and exits the slot through the opening, and the elastic force provided by the elastic member to the slider is opposite to the direction of the axial pressure of the shaft seal on the thrust bearing.

[0016] In some embodiments, the outer periphery of the slider is slidably sealed with the slot wall of the slot, and the slot between the first inclined surface and the second inclined surface forms a sealed cavity connected to 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 the inner channel has an oil inlet located on the outer peripheral surface of the connecting rod, and the other end has an oil outlet connected to the auxiliary oil channel;

[0018] When the first inclined surface and the second inclined surface are sealed and pressed against each other, the oil inlet and the oil inlet passage are misaligned to shut off the oil inlet passage and the auxiliary oil passage;

[0019] When the first inclined surface is separated from the second inclined surface, the oil inlet is communicated with the oil inlet passage to communicate with the oil inlet passage and the auxiliary oil passage.

[0020] In some embodiments, a turbine unit and a compressor unit are further included, wherein the turbine unit includes a turbine casing and a turbine rotor, and the compressor unit includes a compressor casing and a compressor impeller. Both ends of the intermediate casing are fixedly connected to the turbine casing and the compressor casing, the turbine rotor and the compressor impeller are coaxially connected through a rotating shaft, and the thrust bearing is sleeved on the outer periphery of the rotating shaft.

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

[0022] In some embodiments, the shaft seal sleeve is disposed 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 provided on the rotating shaft, the thrust bearing is provided on the outer periphery of the thrust sleeve, the inner ring of the thrust bearing is provided with a first annular cavity connected to the oil outlet end of the second oil transfer channel, and 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 channel, the oil inlet end of the second oil channel 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 arranged, and the axial contact surface of the thrust bearing and the thrust sleeve corresponds to the second annular cavity.

[0025] The beneficial effect of the present application is that when the engine is idling for a long time or operating under no-load conditions, the oil pressure in the oil inlet channel is low, resulting in a low pressure in the first oil channel. The elastic force of the elastic member can overcome the liquid pressure in the first oil channel, thereby causing the slider to move into the slot until the second inclined surface on the slider seals against the first inclined surface of the slot, and the first and second oil channels are shut off. At this time, the second oil channel cannot continue to supply oil to the axial contact surface between the thrust bearing and the shaft seal, preventing oil from appearing on the contact surface between the thrust bearing and the shaft seal, and completely solving the oil leakage problem. When the engine is operating at high operating conditions, the speed of the supercharger is high, and the oil pressure in the oil inlet channel also increases accordingly, causing the pressure in the first oil channel to overcome the elastic force of the elastic member, causing the second inclined surface of the slider to separate from the first inclined surface of the slot, and the first oil channel to maintain communication with the second oil channel through the slot, thereby supplying oil to the axial contact surface between the thrust bearing and the shaft seal.

[0026] A connecting rod is provided on the side of the slider away from the first inclined surface, and the connecting rod can move synchronously with the slider. When the engine is idling or no-load for a long time, the connecting rod can be in a position to close the oil inlet channel and the auxiliary oil channel. At this time, the oil supply demand of the floating bearing can be met only through the main oil channel; when the engine is in high working condition, the connecting rod moves with the slider to a position to open the oil inlet channel and the auxiliary oil channel, thereby increasing the oil supply to the floating bearing through the auxiliary oil channel, and then diverting the high-pressure engine oil to the shoulder position of the floating bearing close to the side of the turbine unit. The high-pressure engine oil is sprayed onto the shoulder to reduce the oil film temperature at the floating bearing, improve the oil film bearing capacity, reduce carbon deposits, and improve the reliability of the shaft system. BRIEF DESCRIPTION OF THE DRAWINGS

[0027] In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are merely embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on the provided drawings without any creative work.

[0028] Figure 1 A schematic diagram of the structure of a supercharger provided in an embodiment of the present application;

[0029] Figure 2 for Figure 1 A in the middle is an enlarged structural diagram;

[0030] Figure 3 A schematic diagram of a first oil passage in a conducting state provided in an embodiment of the present application;

[0031] Figure 4 for Figure 1 The enlarged structural diagram at B in the middle;

[0032] Figure 5This is a schematic diagram of the state where the inner channel provided in the embodiment of the present application is connected to the oil inlet channel and the auxiliary oil channel;

[0033] Figure 6 A schematic diagram of the three-dimensional structure of a thrust bearing provided in an embodiment of the present application;

[0034] Figure 7 A cross-sectional view of a thrust bearing provided in an embodiment of the present application;

[0035] Figure 8 A schematic diagram of the opening and closing mechanism structure provided in an embodiment of the present application;

[0036] Figure 9 A cross-sectional view from another perspective of the thrust bearing provided in an embodiment of the present application;

[0037] Figure 10 A schematic diagram of the structure of the first oil delivery channel provided in an embodiment of the present application;

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

[0039] In the figure: 1-intermediate housing; 2-thrust bearing; 3-turbine housing; 4-turbine rotor; 5-compressor housing; 6-compressor impeller; 7-rotating shaft; 8-slider; 9-elastic member;

[0040] 11- oil inlet channel; 12- support portion; 13- receiving groove; 121- auxiliary oil channel;

[0041] 21 - first oil channel; 22 - first annular cavity; 23 - second annular cavity; 24 - slot; 25 - second oil channel; 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 DESCRIPTION

[0044] The following will be combined with the drawings in the embodiments of this application to clearly and completely describe the technical solutions in the embodiments of this application. Obviously, the embodiments described are only part of the embodiments of this application, not all of the embodiments. Based on the embodiments in this application, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of this application.

[0045] It should be noted that in this embodiment, the directions or positional relationships indicated by "upper," "lower," "front," and "back" are based on the directions or positional relationships shown in the accompanying drawings and are intended solely to facilitate the description of this application and simplify the description. They do not indicate or imply that the devices or components referred to must have a specific direction, be constructed, or operate in a specific direction. Therefore, they should not be construed as limitations on 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] In order to enable those skilled in the art to better understand the present application, the present application is further described in detail below with reference to the accompanying drawings and specific implementation methods.

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

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

[0049] Among them, the two bearing surfaces of the thrust bearing 2 are respectively a bearing surface facing the compressor group and a bearing surface facing the turbine group. The bearing surface facing the compressor group abuts against the shaft seal 71, and the bearing surface facing the turbine group abuts against the thrust sleeve 72; when the engine is idling for a long time and in no-load conditions, the intake flow rate of the compressor group is small, the intake temperature is low, and the power is low. At this time, the flow rate of the turbine group is the same as that of the compressor group, but the temperature in front of the turbine is high, resulting in a lower pressure ratio of the turbine expansion ratio than that of the compressor group, and the size of the turbine rotor 4 is smaller than that of the compressor impeller 6, which causes the axial force of the supercharger to be directed from the turbine group to the compressor group, so that the rotating shaft 7 and the shaft seal 71 and thrust sleeve 72 on the rotating shaft 7 have a tendency to move toward the compressor group. At this time, in order to hinder the axial movement of the rotating shaft 7, the thrust bearing 2 will make the bearing surface of the thrust bearing 2 facing the turbine group bear the axial force of the thrust sleeve 72, and the bearing surface of the thrust bearing 2 facing the compressor group does not need to bear the axial force of the shaft seal 71.

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

[0051] When the bearing surface of thrust bearing 2 facing the compressor unit is not bearing the axial force of shaft seal 71, a certain axial gap will exist between the bearing surface of thrust bearing 2 and shaft seal 71, which can easily lead to oil leakage from this axial gap. This application completely closes the oil circuit during prolonged engine idling and no-load conditions, preventing oil from reaching this axial gap and eliminating the oil leakage problem.

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

[0053] The oil inlet end of the second oil delivery channel 212 is located on a side wall of the slot 24 , and the oil outlet end of the second oil delivery channel 212 can deliver 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 member 9 provided on the intermediate housing 1. The slider 8 can be movably arranged in the slide groove, and a second inclined surface 81 is provided on the slider 8 to cooperate with the first inclined surface 241; when the engine is idling or in no-load condition for a long time, the oil pressure in the oil inlet channel 11 is relatively small, and the corresponding oil pressure in the first oil delivery channel 211 is also relatively small. The elastic member 9 can overcome the oil pressure in the first oil delivery channel 211, so that the slider 8 moves toward the inside of the slide groove until the second inclined surface 81 abuts against the first inclined surface 241, and under the elastic force of the elastic member 9, the second inclined surface 81 is sealed against the first inclined surface 241, thereby shutting off the oil outlet end of the first oil delivery channel 211 on the first inclined surface 241, and physically cutting off the oil supply to 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 running at high operating conditions, in most cases, the intake flow rate of the compressor group of the supercharger is large. At this time, the flow rate of the turbine group is the same as that of the compressor, and the temperature in front of the turbine is still high, resulting in the expansion ratio of the turbine being lower than the pressure ratio of the compressor, and the axial force of the supercharger is still directed from the turbine group to the compressor group; however, when the intake flow rate of the compressor group increases to a certain level, the pressure ratio drops significantly, and the pressure ratio will be less than the expansion ratio. At this time, the axial force of the supercharger will be directed from the compressor group to the turbine group, that is, the bearing surface of the thrust bearing 2 facing the compressor group bears the axial force of the shaft seal 71, and the bearing surface of the thrust bearing 2 facing the turbine group does not need to bear the axial force of the thrust sleeve 72.

[0056] When the engine is running at high operating conditions, the speed of the supercharger is relatively high, and the oil pressure in the oil inlet channel 11 is significantly increased, which will cause the oil pressure in the first oil delivery channel 211 to increase. 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 member 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 channel 211 is opened, and the first oil delivery channel 211 and the second oil delivery channel 212 remain connected. The first oil channel 21 can continue to provide sufficient oil to the contact surface between the thrust bearing 2 and the shaft seal 71, and because the bearing surface of the thrust bearing 2 facing the compressor unit bears the axial force of the shaft seal 71, there is no axial gap between the thrust bearing 2 and the shaft seal 71, or the axial gap is compressed to a level that does not meet the oil leakage requirement, and the oil cannot leak from the contact surface between the thrust bearing 2 and the shaft seal 71. Moreover, at this time, the speed of the supercharger is high, the pressure is relatively high, and the wheel back pressure of the compressor impeller 6 is also high. The compressor unit is not prone to oil leakage in this state.

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

[0058] It can be seen that the present application uses a movable slider 8, an elastic member 9 and an oil pressure drive, so that when the engine is idling for a long time or in a no-load condition, the elastic force of the elastic member 9 can overcome the oil pressure in the first oil supply channel 211, thereby sealing the second inclined surface 81 on the slider 8 with the first inclined surface 241 of the slot 24, and the first oil channel 21 is closed, completely solving the oil leakage problem; when the engine is running at a high operating condition, the pressure in the first oil channel 21 can overcome the elastic force of the elastic member 9, so that the second inclined surface 81 of the slider 8 is separated from the first inclined surface 241, and the first oil channel 21 is opened, thereby supplying oil to the axial contact surface of the thrust bearing 2 and the shaft seal 71.

[0059] Further, Figure 3Where α is the angle between the first inclined surface 241 and the oil delivery direction. To make it easier for the pressure of the oil in the first oil delivery channel 211 acting on the second inclined surface 81 to push 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 pressure of the oil acting on the second inclined surface 81 in the direction of slider 8's movement is greater than or equal to the component in the oil delivery direction. This not only increases the thrust exerted by the oil on the slider 8 in the direction of its movement, but also reduces the friction between the slider 8 and the sidewalls of the slot 24. Furthermore, if the angle α is too small, the length of the second inclined surface 81 in the sliding direction of the slider 8 is short, given a constant slider 8 height. This will result in the thrust exerted by the oil only moving a short distance. While communication between the first oil delivery channel 211 and the second oil delivery channel 212 can be achieved, insufficient movement of the slider 8 may prevent the slider 8 from fully opening the oil inlet end of the second oil delivery channel 212, affecting the oil delivery capacity of the first oil channel 21. Therefore, a more preferred angle is 15° < α ≤ 30°.

[0060] In addition, the liquid pressure in the oil inlet channel 11 will change dynamically with the working condition of the supercharger, that is, when the engine is idling or no-load for a long time, the liquid (oil) pressure in the oil inlet channel 11 is relatively low; when the engine is running at high working conditions, the liquid pressure in the oil inlet channel 11 is relatively high; the present application dynamically binds the lubrication requirements of the bearing surface of the thrust bearing 2 with the working condition of the supercharger, and uses the inherent parameter of the supercharger - oil pressure as a control signal, without the need for additional sensors or electronic controls, to achieve oil cut-off and leakage prevention under low working conditions and oil supply and lubrication under high working conditions.

[0061] It should be pointed out 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, and the dynamically changing liquid pressure in the first oil delivery channel 211 has at least two states. In one state, the liquid pressure acting on the second inclined surface 81, the component force in the sliding direction of the slider 8 is greater than the elastic force of the elastic member 9, that is, the high working condition state, so that the second inclined surface 81 is separated from the first inclined surface 241, and the first oil channel 21 is opened; in another state, the liquid pressure acting on the second inclined surface 81, the component force in the sliding direction of the slider 8 is less than the elastic force of the elastic member 9, that is, the low working condition state, so that the second inclined surface 81 is sealed and abutted with the first inclined surface 241, closing the first oil channel 21.

[0062] The slot 24 is provided with an opening on the bearing surface of the thrust bearing 2 on the side away from the shaft seal 71, and the slider 8 can enter the slot 24 through the opening; and the elastic force provided by the elastic member 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 is sealed and abutted against the second inclined surface 81, the elastic force generated by the elastic member 9 will indirectly act on the thrust bearing 2 through the slider 8, and the axial pressure of the shaft seal 71 on the thrust bearing 2 is opposite to the 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 on the thrust bearing 2 on the bearing mounting position; in other words, due to the elastic force provided by the elastic member 9, the bearing capacity of the thrust bearing 2 to bear the shaft seal 71 comes from the bearing mounting position on the one hand, and from the elastic force of the elastic member 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 supercharger.

[0063] In addition, in order to prevent the engine oil from leaking in the slot 24 and affecting the oil amount in the first oil channel 21, the outer periphery of the slider 8 can be slid and sealed with the slot 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 connected to 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 realizing the opening of the first oil channel 21.

[0064] In some embodiments, the slot 24 can be a slot structure with regular cross-sections such as a rectangular slot or a cylindrical slot, and the structure of the periphery of the slider 8 is compatible with the structure of the slot 24. No excessive restrictions are made here, and all fall within the scope of protection of this application.

[0065] The supercharger also includes a rotating shaft 7. The intermediate housing 1 includes a support portion 12 located on the outer periphery of the rotating shaft 7. A floating bearing 73 is placed circumferentially between the support portion 12 and the rotating shaft 7. The support portion 12 is provided with a main oil passage and auxiliary oil passages 121 that connect the oil inlet passage 11 and the floating bearing 73. The main and auxiliary oil passages 121 are distributed circumferentially. The main oil passage maintains a constant connection between the floating bearing 73 and the oil inlet passage 11, providing a certain degree of lubrication for the floating bearing 73.

[0066] However, when the engine is running at high operating conditions, in order to ensure the lubrication effect of the floating bearing 73, the oil demand of the floating bearing 73 will increase. Therefore, this application adds a secondary oil channel 121 and controls the connection between the secondary oil channel 121 and the oil inlet channel 11 through the connecting rod 82 structure, thereby changing the amount of oil delivered to the floating bearing 73 and ensuring the operating 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 be passed through the support part 12 and slid into the auxiliary oil channel 121. The connecting rod 82 can move synchronously with the slider 8, thereby connecting or shutting off the oil inlet channel and the auxiliary oil channel 121 through the sliding connecting rod 82.

[0068] Furthermore, an inner channel 821 is provided on the connecting rod 82, and one end of the inner channel 821 has an oil inlet located on the outer peripheral surface of the connecting rod 82, and the other end has an oil outlet connected to the auxiliary oil channel 121; when the engine is running at high operating conditions, the oil pressure in the oil inlet channel 11 is significantly increased, the second inclined surface 81 is separated from the first inclined surface 241, and the slider 8 will drive the connecting rod 82 to move in the auxiliary oil channel 121, and the oil demand of the floating bearing 73 increases under high operating conditions. Therefore, when the first inclined surface 241 is separated 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 channel 121, so that the oil in the auxiliary oil channel 121 is drained to the shoulder position of the floating bearing 73, and is sprayed to the shoulder by high-pressure oil, thereby reducing the heat transfer of the rotating shaft 7 to the floating bearing, reducing the oil film temperature at the floating bearing 73, improving the oil film bearing capacity, reducing carbon deposits, and improving the reliability of the shaft system.

[0069] Furthermore, when the engine is in high operating condition, the turbine unit has a relatively high pressure, and there will be no oil leakage problem caused by the auxiliary oil passage 121 supplying oil to the floating bearing 73 .

[0070] When the engine is idling for a long time or in no-load condition, the first inclined surface 241 and the second inclined surface 81 are sealed tightly together, and the oil demand of the floating bearing 73 can be met by the main oil channel. Therefore, at this time, the connecting rod 82, driven by the slider 8, 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 channel 121.

[0071] The supercharger of the present 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 two ends of the intermediate housing 1 are fixedly connected to the turbine housing 3 and the compressor housing 5. 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 housing 1 includes a support portion 12 located on the outer periphery of the rotating shaft 7. This support portion 12 axially abuts the bearing surface of the thrust bearing 2 facing the turbine unit, providing a certain degree of support for the thrust bearing 2. A receiving groove 13 is defined in the support portion 12, within which the slider 8 slides. The receiving groove 13 corresponds to the opening of the slot 24, allowing the slider 8 to smoothly enter the slot 24 from the receiving groove 13. The elastic member 9 can be a spring with a preloaded force. The spring's ends are respectively connected to the slider 8 and the bottom of the receiving groove 13, providing the elastic force for the slider 8 to move toward the slot 24.

[0073] Furthermore, a shaft seal 71 is sleeved around the outer circumference of the rotating shaft 7 and rotates synchronously with the rotating shaft 7. The shaft seal 71 abuts the bearing surface of the thrust bearing 2 facing the compressor unit. A thrust sleeve 72 is sleeved around the rotating shaft 7 and also rotates synchronously with the rotating shaft 7. The thrust bearing 2 is sleeved around the outer circumference of the thrust sleeve 72, and the thrust sleeve 72 has an annular portion that abuts the bearing surface of the thrust bearing 2. A first annular cavity 22 is provided on the inner ring of the thrust bearing 2, which is connected to the oil outlet end of the second oil delivery channel 212. The axial contact surface between the thrust bearing 2 and the shaft seal 71 corresponds to the first annular cavity 22, so that the oil in the first annular cavity 22 can penetrate the axial contact surface between the thrust bearing 2 and the shaft seal 71, thereby lubricating the bearing surface on one side of the thrust bearing 2.

[0074] The thrust bearing 2 is also provided with a second oil channel 25, the oil inlet end of the second oil channel 25 is connected to the oil inlet channel 11, and 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 arranged, and the axial contact surface of the thrust bearing 2 and the thrust sleeve 72 corresponds to the second annular cavity 23, so that the engine oil in the second annular cavity 23 can penetrate into the axial contact surface of the thrust bearing 2 and the thrust sleeve 72, thereby realizing 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 merely used to distinguish one entity from other entities, but do not necessarily require or imply any actual relationship or order between these entities.

[0076] This document uses specific examples to illustrate the principles and implementation methods of this application. The description of the above examples is only intended to help understand the method and core ideas of this application. It should be noted that for those skilled in the art, without departing from the principles of this application, various improvements and modifications can be made to this application, and such improvements and modifications also fall within the scope of protection of the claims of this application.

Claims

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

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

3. The supercharger according to claim 1, characterized in that The liquid pressure in the first oil delivery channel (211) changes dynamically with the working condition of the supercharger, and the dynamically changed liquid pressure has at least two states. In one state, the component force 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 member (9); in the other state, the component force 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 member (9).

4. The supercharger according to claim 1, characterized in that The slot (24) is provided with an opening on the bearing surface of the thrust bearing (2) on the side facing 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 member (9) to the slider (8) is opposite in direction to the axial pressure of the shaft seal (71) on the thrust bearing (2).

5. The supercharger according to claim 1, characterized in that The outer periphery of the slider (8) is slidably sealed 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 that is connected to the first oil delivery channel (211) and the second oil delivery channel (212).

6. The supercharger 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 peripheral surface of the connecting rod (82), and the other end has an oil outlet connected to the auxiliary oil channel (121); When the first inclined surface (241) and the second inclined surface (81) are sealed and pressed against each other, the oil inlet and the oil inlet channel (11) are misaligned to shut off the oil inlet channel (11) and the auxiliary oil channel (121); When the first inclined surface (241) is separated 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 channel (121).

7. The supercharger according to claim 1, characterized in that The invention also includes a turbine unit and a compressor unit, wherein the turbine unit includes a turbine housing (3) and a turbine rotor (4), and the compressor unit includes a compressor housing (5) and a compressor impeller (6). Both ends of the intermediate housing (1) are fixedly connected to the turbine housing (3) and the compressor housing (5), the turbine rotor (4) and the compressor impeller (6) are coaxially connected via the rotating shaft (7), and the thrust bearing (2) is sleeved on the outer periphery of the rotating shaft (7).

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

9. The supercharger according to claim 7, characterized in that The shaft seal (71) is sleeved on the outer periphery of the rotating shaft (7) and abuts against the bearing surface of the thrust bearing (2) facing the compressor unit.

10. The supercharger according to claim 7, characterized in that A thrust sleeve (72) is sleeved on the rotating shaft (7), the thrust bearing (2) is sleeved 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) connected to the oil outlet end of the second oil delivery channel (212), and the axial contact surface between the thrust bearing (2) and the shaft seal (71) corresponds to the first annular cavity (22).

11. The supercharger according to claim 10, characterized in that The thrust bearing (2) is further provided with a second oil passage (25), the oil inlet end of the second oil passage (25) being in communication with the oil inlet passage (11), the inner ring of the thrust bearing (2) being provided with a second annular cavity (23) in communication with the oil outlet end of the second oil delivery passage (212), the first annular cavity (22) and the second annular cavity (23) being independently provided, and the axial contact surface of the thrust bearing (2) and the thrust sleeve (72) corresponding to the second annular cavity (23).

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