Electrically-assisted turbocharger cooling system

Abstract

The invention discloses an electric auxiliary turbocharger cooling system, and relates to the technical field of electric auxiliary turbocharger temperature field control, the electric auxiliary turbocharger cooling system comprises a motor rotor, an oil cooling cavity is formed between the motor rotor and a rotating shaft, the rotating shaft is provided with a rotating shaft center forward oil throwing port located in the oil cooling cavity, and the motor rotor is provided with a rotor 3D forward oil throwing port; the volute heat insulation water cooling loop is used for blocking heat transfer between the motor stator and the turbine, and the motor stator is covered with the middle shell three-dimensional water cooling loop in the axial direction of the motor stator. The vortex end oil pool is wound on the rotating shaft and located between the vortex end oil floating bearing and the motor rotor, and the rotating shaft is provided with a vortex end rotating shaft 3D reverse oil suction port located in the vortex end oil pool; and the pressure end oil pool is wound on the rotating shaft and located between the pressure end oil floating bearing and the motor rotor, and the rotating shaft is provided with a pressure end rotating shaft 3D reverse oil suction port located in the pressure end oil pool. According to the application, the stator and the rotor in the permanent magnet synchronous motor can be comprehensively cooled, so that the reliability and the stability of the operation of the electric auxiliary turbocharger are improved.

Description

Technical Field

[0001] The present invention relates to the technical field of temperature field control of an electrically assisted turbocharger, and more particularly to a cooling system for an electrically assisted turbocharger. Background Art

[0002] The electrically assisted turbocharger is a traditional turbocharger with a permanent magnet synchronous motor connected in series to provide auxiliary power in addition to exhaust energy, thereby solving the problems of insufficient power and turbo lag of the traditional turbocharger at low speeds.

[0003] However, when the permanent magnet synchronous motor is connected in series with the supercharger, one side of the motor rotor is connected to the turbine on the same rotating shaft. High heat from the turbine is transferred along the rotating shaft to the motor rotor, causing high-temperature demagnetization of the motor rotor. The other side of the permanent magnet motor rotor is also connected to the compressor impeller on the same rotating shaft. High heat from the compressor is also transferred along the rotating shaft to the motor rotor, causing high-temperature demagnetization of the motor rotor. Furthermore, the motor stator is connected to the supercharger volute by metal, and high exhaust gas temperatures are transferred along the turbine casing to the motor stator. Furthermore, the motor stator is also connected to the supercharger compressor casing by metal, and heat energy generated by the compressor is also transferred to the motor stator, causing insulation and enameled wire failure, and even posing serious safety hazards.

[0004] Therefore, how to fully cool the stator and rotor in the permanent magnet synchronous motor to improve the reliability and stability of the operation of the electrically assisted turbocharger is an urgent problem to be solved by those skilled in the art. Summary of the Invention

[0005] In view of this, an object of the present invention is to provide an electrically assisted turbocharger cooling system, which can comprehensively cool the stator and rotor in a permanent magnet synchronous motor to improve the reliability and stability of the electrically assisted turbocharger operation.

[0006] In order to achieve the above object, the present invention provides the following technical solutions:

[0007] An electrically assisted turbocharger cooling system includes a housing, a rotating shaft rotatably disposed in the housing, and a compressor impeller and a turbine respectively disposed at two ends of the rotating shaft, and further includes:

[0008] The motor rotor is sleeved on the rotating shaft and spaced apart from the rotating shaft to form an oil cooling cavity, and the rotating shaft is provided with a shaft center forward oil throwing port located in the oil cooling cavity, and the motor rotor is provided with a rotor 3D forward oil throwing port;

[0009] The motor stator is arranged on the outer periphery of the motor rotor, and a volute insulated water cooling loop is provided between the motor stator and the turbine to block heat transfer between the two. The motor stator is covered with a mid-shell three-dimensional water cooling loop along its axial direction;

[0010] A turbine end oil pool is wound around the rotating shaft and located between the turbine end oil floating bearing and the motor rotor. The rotating shaft is provided with a turbine end rotating shaft 3D reverse oil suction port located in the turbine end oil pool;

[0011] A compression end oil pool is wound around the rotating shaft and is located between the compression end oil floating bearing and the motor rotor. The rotating shaft is provided with a compression end rotating shaft 3D reverse oil suction port located in the compression end oil pool;

[0012] Among them, the reverse oil suction port of the turbine end shaft 3D and the reverse oil suction port of the pressure end shaft 3D are both connected with the forward oil throwing port of the shaft center through the central hole cavity of the shaft, and the forward oil throwing port of the shaft center is then connected with the oil cooling cavity, the forward oil throwing port of the rotor 3D, and the gap between the motor rotor and the motor stator in sequence.

[0013] On the other hand, the reverse oil suction port of the vortex end shaft 3D includes multiple vortex end shaft oil suction channels. When viewed from the axial direction of the shaft, the multiple vortex end shaft oil suction channels radiate outward in a straight line or spiral shape with the axis of the shaft as the center, and the radiation direction is opposite to the rotation direction of the shaft.

[0014] On the other hand, the reverse oil suction port of the vortex end shaft 3D includes multiple vortex end shaft oil suction channels. When observed from the radial direction of the shaft, the vortex end shaft oil suction channels are inclined along the direction from the outside of the shaft to its axis toward the forward oil rejection port at the center of the shaft.

[0015] On the other hand, the reverse oil suction port of the compression end shaft 3D includes multiple compression end shaft oil suction channels. When observed from the axial direction of the shaft, the multiple compression end shaft oil suction channels radiate outward in a linear or spiral manner with the axis of the shaft as the center, and the radiation direction is opposite to the rotation direction of the shaft.

[0016] On the other hand, the reverse oil suction port of the compression end shaft 3D includes multiple compression end shaft oil suction channels. When observed from the radial direction of the shaft, the compression end shaft oil suction channels are inclined along the direction from the outside of the shaft to its axis toward the forward oil dumping port at the center of the shaft.

[0017] On the other hand, the forward oil-swing port at the center of the rotating shaft includes a plurality of rotating shaft oil-swing channels. When viewed from the axial direction of the rotating shaft, the plurality of rotating shaft oil-swing channels radiate outward in a linear or spiral manner with the axis of the rotating shaft as the center, and the radiation direction is the same as the rotation direction of the rotating shaft.

[0018] On the other hand, the reverse oil suction port of the vortex end shaft 3D includes a plurality of vortex end shaft oil suction channels. When viewed from the axial direction of the shaft, the plurality of vortex end shaft oil suction channels radiate outward in a straight line or spiral shape with the axis of the shaft as the center, and the radiation direction is opposite to the rotation direction of the shaft.

[0019] The reverse oil suction port of the compression end shaft 3D includes a plurality of compression end shaft oil suction passages. When viewed from the axial direction of the shaft, the plurality of compression end shaft oil suction passages radiate outward in a straight line or spiral shape with the axis of the shaft as the center, and the radiation direction is opposite to the rotation direction of the shaft.

[0020] The reverse oil suction port of the vortex end shaft 3D and the reverse oil suction port of the pressure end shaft 3D are symmetrically arranged with the forward oil rejection port in the center of the shaft as the center. When observed from the axial direction of the shaft, the oil suction channels of the vortex end shaft and the oil suction channels of the pressure end shaft are the same in number and in the same radiation direction.

[0021] On the other hand, the reverse oil suction port of the vortex end shaft 3D includes a plurality of vortex end shaft oil suction channels. When viewed from the radial direction of the shaft, the vortex end shaft oil suction channels are inclined along the direction from the outer side of the shaft to the axis thereof toward the forward oil ejection port at the center of the shaft.

[0022] The reverse oil suction port of the pressure end shaft 3D includes a plurality of pressure end shaft oil suction channels. When viewed from the radial direction of the shaft, the pressure end shaft oil suction channels are inclined from the outer side of the shaft to the axis thereof toward the forward oil discharge port at the center of the shaft.

[0023] The reverse oil suction port of the vortex end shaft 3D and the reverse oil suction port of the compression end shaft 3D are symmetrically arranged with the forward oil rejection port in the center of the shaft as the center. When observed from the radial direction of the shaft, the number of the vortex end shaft oil suction channels and the compression end shaft oil suction channels are the same, and the inclination angles of the vortex end shaft oil suction channels and the compression end shaft oil suction channels along the direction from the outside of the shaft to its axis are the same and the inclination directions are opposite.

[0024] On the other hand, the forward oil-swing port of the rotor 3D includes a plurality of rotor oil-swing channels. When viewed from the axial direction of the motor rotor, the plurality of rotor oil-swing channels radiate outward in a linear or vortex shape with the axis of the motor rotor as the center, and the radiation direction is the same as the rotation direction of the motor rotor.

[0025] On the other hand, the rotor 3D is provided with two forward oil-slinging ports, namely the turbine end rotor 3D forward oil-slinging port and the compressor end rotor 3D forward oil-slinging port, and are respectively arranged adjacent to the two ends of the permanent magnets on the motor rotor.

[0026] On the other hand, the forward oil-slinging port of the rotor 3D includes a plurality of rotor oil-slinging channels. When viewed from the axial direction of the motor rotor, the plurality of rotor oil-slinging channels radiate outward in a straight line or in a vortex shape with the axis of the motor rotor as the center, and the radiation direction is the same as the rotation direction of the motor rotor.

[0027] Observed from the radial direction of the motor rotor, the rotor oil-swing channel in the forward oil-swing port of the turbine end rotor 3D is inclined toward the compressor impeller along the direction from the axis of the motor rotor to the outside thereof.

[0028] On the other hand, the forward oil-slinging port of the rotor 3D includes a plurality of rotor oil-slinging channels. When viewed from the axial direction of the motor rotor, the plurality of rotor oil-slinging channels radiate outward in a straight line or in a vortex shape with the axis of the motor rotor as the center, and the radiation direction is the same as the rotation direction of the motor rotor.

[0029] Observed from the radial direction of the motor rotor, the rotor oil-slinging channel in the forward oil-slinging port of the compression-end rotor 3D is inclined toward the turbine along the direction from the axis of the motor rotor to the outside thereof.

[0030] On the other hand, the forward oil-slinging port of the rotor 3D includes a plurality of rotor oil-slinging channels. When viewed from the axial direction of the motor rotor, the plurality of rotor oil-slinging channels radiate outward in a straight line or in a vortex shape with the axis of the motor rotor as the center, and the radiation direction is the same as the rotation direction of the motor rotor.

[0031] The rotor 3D is provided with two forward oil-slinging ports, namely the turbine end rotor 3D forward oil-slinging port and the compressor end rotor 3D forward oil-slinging port, and are respectively arranged adjacent to the two ends of the permanent magnets on the motor rotor;

[0032] Observed from the radial direction of the motor rotor, the rotor oil-slinging channel in the forward oil-slinging port of the turbine end rotor 3D is inclined toward the compressor impeller from the axis of the motor rotor to the outer side thereof;

[0033] Observed from the radial direction of the motor rotor, the rotor oil-slinging channel in the forward oil-slinging port of the compression end rotor 3D is inclined toward the turbine from the axis of the motor rotor to the outside thereof;

[0034] The shaft center forward oil-slinging port is arranged at the center of the permanent magnet on the motor rotor, and the turbine end rotor 3D forward oil-slinging port and the compressor end rotor 3D forward oil-slinging port are symmetrically arranged with the shaft center forward oil-slinging port as the center;

[0035] Observed from the radial direction of the motor rotor, the rotor oil-splitting passages in the forward oil-splitting port of the turbine end rotor 3D and the forward oil-splitting port of the compression end rotor 3D have the same inclination angle from the axis of the motor rotor to its outside and are inclined in opposite directions.

[0036] On the other hand, the forward oil-slinging port of the rotor 3D includes a plurality of rotor oil-slinging channels. When viewed from the axial direction of the motor rotor, the plurality of rotor oil-slinging channels radiate outward in a straight line or in a vortex shape with the axis of the motor rotor as the center, and the radiation direction is the same as the rotation direction of the motor rotor.

[0037] The rotor 3D is provided with two forward oil-slinging ports, namely the turbine end rotor 3D forward oil-slinging port and the compressor end rotor 3D forward oil-slinging port, and are respectively arranged adjacent to the two ends of the permanent magnets on the motor rotor;

[0038] The shaft center forward oil-slinging port is arranged at the center of the permanent magnet on the motor rotor, and the turbine end rotor 3D forward oil-slinging port and the compressor end rotor 3D forward oil-slinging port are symmetrically arranged with the shaft center forward oil-slinging port as the center;

[0039] Observed from the axial direction of the motor rotor, the number of the rotor oil-swing passages in the forward oil-swing port of the turbine-end rotor 3D and the forward oil-swing port of the compressor-end rotor 3D are the same and their radiation directions are the same.

[0040] On the other hand, when viewed from the axial direction of the casing, the volute insulating water cooling circuit is arranged in the casing along the circumference of the vortex end oil pool.

[0041] On the other hand, the three-dimensional water-cooling loop in the middle shell is spirally extended along the axis direction of the motor stator, and the three-dimensional water-cooling loop in the middle shell fluctuates in a wave-like manner along the radial direction.

[0042] The electric-assisted turbocharger cooling system provided by the present invention, on the one hand, uses oil cooling technology to cool the motor stator and rotor. The specific process is as follows: the reverse oil suction port of the turbine end shaft 3D sucks the lubricating oil in the turbine end oil pool into the central hole cavity of the shaft, the reverse oil suction port of the pressure end shaft 3D sucks the lubricating oil in the pressure end oil pool into the central hole cavity of the shaft, and the forward oil throwing port in the center of the shaft throws the lubricating oil in the shaft into the oil cooling cavity, thereby achieving full-area cooling of the internal motor rotor. Then, the forward oil throwing port of the rotor 3D throws the lubricating oil in the oil cooling cavity and splashes it onto the inner winding of the motor stator. The splashed lubricating oil is partially reflected to the outer surface of the motor rotor after being blocked by the winding, thereby achieving external cooling of the inner winding of the motor stator and the motor rotor. Therefore, the present invention uses oil cooling technology to achieve full-area cooling and temperature control of the motor rotor, and also achieves cooling and temperature control of the inner winding of the stator adjacent to the motor rotor.

[0043] On the other hand, water cooling technology is used to cool the motor stator. The specific process is as follows: the insulated water cooling loop in the volute blocks heat transfer from the turbine side to the motor stator, achieving thermal insulation protection for the motor stator. In addition, the three-dimensional water cooling loop in the middle casing cools the outer windings of the motor stator and the entire stator core. Therefore, the present invention uses water cooling technology to block heat transfer from the volute to the motor stator and simultaneously cool the outer windings of the motor stator and the entire stator core. In combination with the above-mentioned oil cooling technology, it achieves full-area cooling and temperature control of the motor stator.

[0044] In summary, the electrically assisted turbocharger cooling system provided by the present invention combines oil cooling and water cooling technologies, and can comprehensively cool the stator and rotor in the permanent magnet synchronous motor to achieve full-range temperature control of the stator and rotor of the permanent magnet synchronous motor, thereby improving the reliability and stability of the operation of the electrically assisted turbocharger. BRIEF DESCRIPTION OF THE DRAWINGS

[0045] In order to more clearly illustrate the embodiments of the present invention 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 invention. For ordinary technicians in this field, other drawings can be obtained based on the provided drawings without paying any creative work.

[0046] Figure 1 This is a schematic structural diagram of an electrically assisted turbocharger cooling system provided by the present invention;

[0047] Figure 2 This is a schematic diagram of the 3D reverse oil suction port of the turbine end shaft provided by the present invention along the axis of the shaft;

[0048] Figure 3 This is a schematic diagram of the oil-slinging port in the center of the rotating shaft provided by the present invention along the axis of the rotating shaft;

[0049] Figure 4 A cross-sectional view of the rotating shaft provided by the present invention along the axis direction;

[0050] Figure 5 This is a schematic diagram of the 3D forward oil-slinging port of the turbine end rotor provided by the present invention along the axis of the motor rotor;

[0051] Figure 6 A cross-sectional view of the motor rotor provided by the present invention along the axis direction;

[0052] Figure 7 This is a cooling oil circuit diagram for the stator and rotor of the permanent magnet synchronous motor provided by the present invention;

[0053] Figure 8This is a schematic diagram of the structure of the volute insulation water cooling loop provided by the present invention;

[0054] Figure 9 This is a schematic structural diagram of the three-dimensional water cooling loop in the middle shell provided by the present invention.

[0055] Reference numerals:

[0056] 1-Casing; 2-Compressor impeller; 3-Turbine; 4-Shaft; 5-Motor rotor; 6-Motor stator; 7-Turbine end oil floating bearing; 8-Turbine end oil sump; 9-Turbine end oil seal; 10-Compression end oil floating bearing; 11-Compression end oil sump; 12-Compression end oil seal; 13-Turbine end shaft 3D reverse oil suction port; 14-Compression end shaft 3D reverse oil suction port; 15-Shaft center forward oil dump port; 16-Oil cooling chamber; 17a-Turbine end rotor 3D forward oil dump port ;17b-3D forward oil-swing port of the compression end rotor;18-oil-cooling channel;19-volute insulation water-cooling loop;20-middle shell three-dimensional water-cooling loop;21-return oil outlet;22-oil inlet channel;51-permanent magnet;131-vortex end shaft oil suction channel;141-compression end shaft oil suction channel;151-shaft oil-swing channel;171a-vortex end rotor oil-swing channel;171b-compression end rotor oil-swing channel;A-rotation direction of shaft;B-rotation direction of motor rotor. DETAILED DESCRIPTION

[0057] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0058] The core of the present invention is to provide an electrically assisted turbocharger cooling system, which can comprehensively cool the motor rotor in the permanent magnet synchronous motor to improve the reliability and stability of the operation of the electrically assisted turbocharger cooling system.

[0059] It should be noted that in this embodiment, the directions or positional relationships indicated by "up", "down", "front", "back", etc. are based on the directions or positional relationships shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific direction, be constructed and operated in a specific direction, and therefore cannot be understood as a limitation on this application.

[0060] Please refer to Figure 1The present invention provides a specific embodiment of an electrically assisted turbocharger cooling system, comprising a housing 1, a rotating shaft 4 rotatably disposed in the housing 1, and a compressor impeller 2 and a turbine 3 respectively disposed at both ends of the rotating shaft 4, and further comprising a motor rotor 5, a motor stator 6, a turbine end oil pool 8, and a compressor end oil pool 11.

[0061] The motor rotor 5 is sleeved on the rotating shaft 4 and is spaced apart from the rotating shaft 4 to form an oil cooling chamber 16 , and the rotating shaft 4 is provided with a shaft center forward oil throwing port 15 located in the oil cooling chamber 16 , and the motor rotor 5 is provided with a rotor 3D forward oil throwing port.

[0062] The motor stator 6 is arranged on the outer periphery of the motor rotor 5, and a volute insulating water cooling loop 19 is provided between the motor stator 6 and the turbine 3 to block heat transfer between the two. The motor stator 6 is covered with a middle shell three-dimensional water cooling loop 20 along its axial direction.

[0063] The turbine end oil pool 8 is wound around the rotating shaft 4 and is located between the turbine end oil floating bearing 7 and the motor rotor 5. The rotating shaft 4 is provided with a turbine end rotating shaft 3D reverse oil suction port 13 located in the turbine end oil pool 8.

[0064] The compression end oil pool 11 is wound around the rotating shaft 4 and is located between the compression end oil floating bearing 10 and the motor rotor 5 . The rotating shaft 4 is provided with a compression end rotating shaft 3D reverse oil suction port 14 located in the compression end oil pool 11 .

[0065] Among them, the reverse oil suction port 13 of the turbine end shaft 3D and the reverse oil suction port 14 of the compression end shaft 3D are both connected to the forward oil throwing port 15 in the center of the shaft through the central hole cavity of the shaft 4. The forward oil throwing port 15 in the center of the shaft is then connected to the oil cooling cavity 16, the forward oil throwing port of the rotor 3D, and the gap between the motor rotor 5 and the motor stator 6 in sequence.

[0066] In this embodiment, the casing 1 includes a middle casing, a volute and a compression casing. The rotating shaft 4 is arranged in the middle casing. One end of the rotating shaft 4 can be rotatably arranged in the volute and is sleeved with the turbine 3 on the volute. The other end of the rotating shaft 4 can be rotatably arranged in the compression casing and is sleeved with the compressor impeller on the compression casing.

[0067] It should be noted that the motor rotor 5 in a permanent magnet synchronous motor is primarily composed of permanent magnets 51 and a rotor core. The permanent magnets 51 are disposed on the outer circumference of the rotor core. The permanent magnets 51 are used to provide the required magnetic field, and the rotor core supports the permanent magnets 51 and provides a magnetic circuit. Furthermore, the motor stator 6 in a permanent magnet synchronous motor is primarily composed of stator windings and a stator core. The stator windings are wound around the stator core and connected to a power source. The current in the stator windings interacts with the magnetic field generated by the permanent magnets 51 to generate torque, thereby driving the motor rotor 5 to rotate. Therefore, the stator windings and permanent magnets 51 are key components for achieving energy conversion, and both generate heat when the motor is running.

[0068] In this embodiment, the motor stator 6 is arranged on the middle shell around the outer circumference of the motor rotor 5, and a preset distance is left between the inner side of the motor stator 6 and the outer side of the motor rotor 5. The motor rotor 5 is sleeved on the rotating shaft 4. The electromagnetic field coupling is realized through the preset distance between the stator and the rotor, and the electromagnetic torque is generated to realize the rotation of the motor shaft 4.

[0069] A preset distance is left between the inner side of the motor rotor 5 and the outer side of the rotating shaft 4, forming an oil cooling chamber 16 therebetween. The oil cooling chamber 16 covers the entire inner area of ​​the permanent magnet 51. Furthermore, a preset distance is left between the inner winding of the motor stator 6 and the permanent magnet 51, which not only allows electromagnetic induction between the stator winding and the permanent magnet 51 but also forms an oil cooling channel 18 for the flow of lubricating oil.

[0070] In this embodiment, a turbine oil bearing 7 is mounted on the rotating shaft 4 near the turbine 3 to support the rotation of the turbine end of the rotating shaft 4. A turbine oil pool 8 is mounted around the rotating shaft 4 and located between the turbine oil bearing 7 and the motor rotor 5. This allows the rotating shaft 4 to be immersed in the turbine oil pool 8, which contains lubricating oil. It should be noted that a turbine oil seal 9 is mounted on the rotating shaft 4 between the turbine oil pool 8 and the motor rotor 5 to prevent leakage of the lubricating oil in the turbine oil pool 8.

[0071] In this embodiment, a compression-end oil-floating bearing 10 is mounted on the rotating shaft 4 near the compressor impeller to support the compression-end rotation of the rotating shaft 4. A compression-end oil reservoir 11 is disposed around the rotating shaft 4 and located between the compression-end oil-floating bearing 10 and the motor rotor 5. This allows the rotating shaft 4 to be immersed in the compression-end oil reservoir 11, which contains lubricating oil. It should be noted that a compression-end oil seal 12 is mounted on the rotating shaft 4 between the compression-end oil reservoir 11 and the motor rotor 5 to prevent leakage of the lubricating oil in the compression-end oil reservoir 11.

[0072] In this embodiment, the rotating shaft 4 is a hollow rotating shaft 4 and is provided with a reverse oil suction port 13 for the vortex end rotating shaft 3D, which is immersed in the vortex end oil pool 8. The reverse oil suction port 13 for the vortex end rotating shaft 3D is used to draw the lubricating oil in the vortex end oil pool 8 into the central cavity of the rotating shaft 4. The rotating shaft 4 is also provided with a reverse oil suction port 14 for the pressure end rotating shaft 3D, which is immersed in the pressure end oil pool 11. The reverse oil suction port 14 for the pressure end rotating shaft 3D is used to draw the lubricating oil in the pressure end oil pool 11 into the central cavity of the rotating shaft 4.

[0073] In this embodiment, a shaft center forward oil-swinging port 15 communicating with the oil-cooling chamber 16 is provided on the outer wall of the shaft 4 . The shaft center forward oil-swinging port 15 is used to swing the lubricating oil in the central cavity of the shaft 4 into the oil-cooling chamber 16 .

[0074] In this embodiment, a rotor 3D forward oil ejection port is provided near the permanent magnet 51 on the motor rotor 5. The rotor 3D forward oil ejection port is used to eject the lubricating oil in the oil cooling cavity 16 into the oil cooling channel 18 to simultaneously cool the inner winding of the motor stator 6 and the outer surface of the permanent magnet 51.

[0075] In this embodiment, the volute insulation water cooling loop 19 is set in the volute and is located between the volute stop and the vortex end oil pool 8. Figure 1 and Figure 8 The volute insulation water cooling loop 19 contains a coolant, such as water, to prevent the heat on the turbine 3 side from being transferred to the motor stator 6, thereby providing thermal insulation protection for the motor stator 6.

[0076] In this embodiment, the three-dimensional water cooling loop 20 of the middle shell is arranged around the outer circumference of the motor stator 6 in an area of ​​the middle shell adjacent to the motor stator 6. The three-dimensional water cooling loop 20 of the middle shell contains coolant, such as water, to cool the outer winding of the motor stator 6.

[0077] To sum up, in the above embodiment, when the electric-assisted turbine 3 supercharger cooling system is cooling and controlling the temperature of the electric-assisted turbine 3 supercharger, the permanent magnet synchronous motor drives the rotating shaft 4 to rotate, and the reverse oil suction port 13 of the turbine end rotating shaft 3D and the reverse oil suction port 14 of the pressure end rotating shaft 3D on both sides of the rotating shaft 4 both suck in lubricating oil, and the lubricating oil is then thrown out from the forward oil throwing port 15 in the center of the rotating shaft into the oil cooling chamber 16, so as to realize the full-area cooling of the internal area of ​​the motor rotor 5, and then the lubricating oil is thrown out through the forward oil throwing port of the rotor 3D and splashed onto the inner winding of the motor stator 6. The splashed lubricating oil is blocked by the winding and partially reflected to the outer surface of the motor rotor 5, so as to realize the cooling of the inner winding of the motor stator 6 and the external of the motor rotor 5 (that is, the outer surface cooling of the permanent magnet 51). At the same time, the volute insulated water cooling loop 19 blocks the heat on the turbine 3 side from being transferred to the motor stator 6, thereby achieving thermal insulation protection for the motor stator 6, and the middle shell three-dimensional water cooling loop 20 cools the outer winding of the motor stator 6 and the entire area of ​​the stator core.

[0078] Therefore, the above-mentioned electrically assisted turbine 3 supercharger cooling system combines oil cooling and water cooling technology to fully cool the stator and rotor in the permanent magnet synchronous motor to achieve full-range temperature control of the stator and rotor of the permanent magnet synchronous motor, thereby improving the reliability and stability of the operation of the electrically assisted turbine 3 supercharger.

[0079] It should be noted that both the turbine oil-floating bearing 7 and the pressure-end oil-floating bearing 10 contain lubricating oil to reduce frictional losses during the rotation of the shaft 4 and ensure stable rotation of the shaft 4. The housing 1 is typically provided with an oil inlet passage 22, which connects the turbine oil-floating bearing 7 and the pressure-end oil-floating bearing 10. The specific structure of the oil inlet passage 22 can be referenced in the prior art and is not the focus of the present invention, so it will not be described in detail herein.

[0080] Based on the above examples, please refer to Figure 1 The vortex end oil floating bearing 7 is connected to the vortex end oil pool 8, and the pressure end oil floating bearing 10 is connected to the pressure end oil pool 11.

[0081] Thus, lubricating oil of a temperature that meets the requirements is injected into the compression-end oil-floating bearing 10 and the turbine-end oil-floating bearing 7, so that the lubricating oil performs both lubrication and cooling functions. On the one hand, by using the oil inlet of the oil-floating bearing itself to replenish the oil pool, not only is sufficient coolant in the turbine-end oil pool 8 and the compression-end oil pool 11 ensured, but also the need to add an additional oil inlet for replenishing the oil pool, thereby simplifying the structure and saving manufacturing costs. On the other hand, the lubricating oil in both the turbine-end oil-floating bearing 7 and the compression-end oil-floating bearing 10 has a cooling capacity, which allows the turbine-end oil-floating bearing 7 and the turbine-end oil pool 8 to jointly block heat transfer from the turbine 3 to the motor rotor 5, and the compression-end oil-floating bearing 10 and the compression-end oil pool 11 to jointly block heat transfer from the compressor impeller 2 to the motor rotor 5, thereby enhancing the cooling effect of the motor rotor 5, further ensuring the reliable and stable operation of the motor rotor 5, and further improving the reliability and stability of the operation of the electrically assisted turbine 3 supercharger.

[0082] Considering the specific structure of the reverse oil suction port 13 of the vortex end shaft 3D in the axial direction of the shaft 4, based on the above embodiment, please refer to Figure 2 The reverse oil suction port 13 of the vortex end shaft 3D includes multiple vortex end shaft oil suction channels 131. When viewed from the axial direction of the shaft 4, the multiple vortex end shaft oil suction channels 131 radiate outward in a straight line or spiral shape with the axis of the shaft 4 as the center, and the radiation direction is opposite to the rotation direction of the shaft 4.

[0083] This is equivalent to observing from the axial direction of the shaft 4 that all the vortex shaft oil suction channels 131 are inclined in a direction opposite to the shaft rotation direction A and are spaced apart around the axis of the shaft 4, wherein the vortex shaft oil suction channels 131 can be linear or curved vortex-shaped. In this way, when the shaft 4 rotates, the lubricating oil will tend to maintain its original position due to inertia, and will produce a rotational motion in the opposite direction to the shaft 4. Moreover, the inclination direction of all the vortex shaft oil suction channels 131 in the reverse oil suction port 13 of the vortex shaft 3D is opposite to the rotation direction of the shaft 4. The lubricating oil in the vortex oil suction pool will flow into the central cavity of the shaft 4 through the vortex shaft oil suction channels 131 due to inertia, thereby realizing the oil suction function of the reverse oil suction port 13 of the vortex shaft 3D.

[0084] Further considering the specific structure of the reverse oil suction port 13 of the vortex end shaft 3D in the radial direction of the shaft 4, based on the above embodiment, please refer to Figure 4Observed from the radial direction of the rotating shaft 4, the vortex end rotating shaft oil suction channel 131 is inclined from the outer side of the rotating shaft 4 to the axis thereof toward the shaft center forward oil-swinging port 15. In this way, the lubricating oil sucked in by the reverse oil suction port 13 of the vortex end rotating shaft 3D will flow toward the shaft center forward oil-swinging port 15, so that the lubricating oil sucked in by the reverse oil suction port 13 of the vortex end rotating shaft 3D will all flow toward the shaft center forward oil-swinging port 15, thereby ensuring that the lubricating oil flowing into the rotating shaft 4 is all spun out into the oil cooling chamber 16 through the shaft center forward oil-swinging port 15, thereby ensuring the smooth and reliable delivery of lubricating oil to the rotating shaft 4 and avoiding lubricating oil retention in the rotating shaft 4 and waste of lubricating oil.

[0085] Considering the specific structure of the reverse oil suction port 14 of the pressure end shaft 3D in the axial direction of the shaft 4, based on the above embodiment, please refer to Figure 3 The reverse oil suction port 14 of the pressure end shaft 3D includes multiple pressure end shaft oil suction channels 141. When viewed from the axial direction of the shaft 4, the multiple pressure end shaft oil suction channels 141 radiate outward in a straight line or spiral shape with the axis of the shaft 4 as the center, and the radiation direction is opposite to the rotation direction of the shaft 4.

[0086] This is equivalent to observing from the axial direction of the rotating shaft 4 that all the pressure-end rotating shaft oil suction channels 141 are inclined in a direction opposite to the rotating shaft rotation direction A and are spaced apart around the axis of the rotating shaft 4, wherein the pressure-end rotating shaft oil suction channels 141 can be linear or curved spiral-shaped. In this way, when the rotating shaft 4 rotates, the lubricating oil will tend to maintain its original position due to inertia and will produce a rotational motion in the opposite direction to the rotating shaft 4. The inclination direction of all the pressure-end rotating shaft oil suction channels 141 in the pressure-end rotating shaft 3D reverse oil suction port 14 is opposite to the rotation direction of the rotating shaft 4. The lubricating oil in the pressure-end oil suction pool will flow into the central hole of the rotating shaft 4 through the pressure-end rotating shaft oil suction channels 141 due to inertia, thereby realizing the oil suction function of the pressure-end rotating shaft 3D reverse oil suction port 14.

[0087] Further considering the specific structure of the reverse oil suction port 14 of the pressure end shaft 3D in the radial direction of the shaft 4, based on the above embodiment, please refer to Figure 4 Observed from the radial direction of the rotating shaft 4, the oil suction passage 141 of the pressure-end rotating shaft is inclined from the outer side of the rotating shaft 4 to the axis thereof toward the center of the rotating shaft, toward the forward oil-swinging port 15 at the center of the rotating shaft. This causes the lubricating oil sucked in by the reverse oil suction port 14 of the pressure-end rotating shaft 3D to flow toward the forward oil-swinging port 15 at the center of the rotating shaft, so that all the lubricating oil sucked in by the reverse oil suction port 14 of the pressure-end rotating shaft 3D flows toward the forward oil-swinging port 15 at the center of the rotating shaft. This ensures that all the lubricating oil flowing into the rotating shaft 4 is spun out into the oil-cooling chamber 16 through the forward oil-swinging port 15 at the center of the rotating shaft, thereby ensuring smooth and reliable lubricating oil transportation from the rotating shaft 4 and preventing lubricating oil from being retained in the rotating shaft 4 and causing waste of lubricating oil.

[0088] Taking into account the specific structure of the central forward oil-swing port 15 of the rotating shaft in the axial direction of the rotating shaft 4, on the basis of the above embodiment, the central forward oil-swing port 15 of the rotating shaft includes a plurality of rotating shaft oil-swing channels 151. When observed from the axial direction of the rotating shaft 4, the plurality of rotating shaft oil-swing channels 151 radiate outward in a linear or spiral shape with the axis of the rotating shaft 4 as the center, and the radiation direction is the same as the rotation direction of the rotating shaft 4.

[0089] Equivalently, when viewed from the axial direction of the shaft 4, all of the shaft oil-swing passages 151 are inclined in the same direction as the shaft's rotational direction A and are spaced apart around the axis of the shaft 4. The shaft oil-swing passages 151 can be linear or vortex-shaped. Thus, as the shaft 4 rotates, the lubricating oil tends to maintain its original position due to inertia, generating a rotational motion opposite to the shaft 4. The inclination of all of the shaft oil-swing passages 151 in the shaft's central forward oil-swing port 15 is aligned with the direction of shaft 4's rotation. Due to inertia, the lubricating oil in the shaft 4 is ejected through the shaft oil-swing passages 151, thereby achieving the oil-swing function of the shaft's central forward oil-swing port 15.

[0090] In order to achieve radial balance of the rotating shaft 4, based on the above embodiment, please refer to Figure 2 、 Figure 3 and Figure 7 The reverse oil suction port 13 of the turbine end shaft 3D and the reverse oil suction port 14 of the pressure end shaft 3D are symmetrically arranged with the forward oil rejection port 15 in the center of the shaft as the center. When observed from the axial direction of the shaft 4, the number of the turbine end shaft oil suction channels 131 and the pressure end shaft oil suction channels 141 are the same and the radiation direction is the same.

[0091] It can be understood that the number of the vortex end shaft oil suction channels 131 and the compression end shaft oil suction channels 141 is the same, which can keep the oil suction volume of the vortex end oil suction port and the compression end oil suction port consistent. Furthermore, from the axial observation of the shaft 4, all the vortex end shaft oil suction channels 131 and all the compression end shaft oil suction channels 141 are symmetrically arranged with the oil rejection port 15 in the center of the shaft as the center and have the same radiation direction, which is beneficial to keep the radial oil suction force of the vortex end and the pressure end of the shaft 4 consistent, so that the shaft 4 remains balanced in the radial direction.

[0092] In order to achieve the balance of the rotating shaft 4 in the axial direction, based on the above embodiment, please refer to Figure 1 and Figure 7 The reverse oil suction port 13 of the turbine end shaft 3D and the reverse oil suction port 14 of the pressure end shaft 3D are symmetrically arranged with the forward oil rejection port 15 in the center of the shaft as the center. When observed from the radial direction of the shaft 4, the number of the turbine end shaft oil suction channels 131 and the compression end shaft oil suction channels 141 are the same, and the inclination angles of the turbine end shaft oil suction channels 131 and the compression end shaft oil suction channels 141 along the direction from the outside of the shaft 4 to its axis are the same and the inclination directions are opposite.

[0093] It can be understood that the number of the vortex end shaft oil suction channels 131 and the compression end shaft oil suction channels 141 is the same, which can keep the oil suction volume of the vortex end oil suction port and the compression end oil suction port consistent. Furthermore, from the radial observation of the shaft 4, all the vortex end shaft oil suction channels 131 and all the compression end shaft oil suction channels 141 are symmetrically arranged with the oil discharge port 15 in the center of the shaft as the center, and the inclination angles along the direction from the outside of the shaft 4 to its axis are the same and the inclination directions are opposite, which is conducive to ensuring that the axial oil suction force of the vortex end and the compression end of the shaft 4 remain consistent, so that the shaft 4 remains balanced in the axial direction.

[0094] Considering the specific structure of the rotor 3D forward oil-slinging port in the axial direction, based on the above embodiment, please refer to Figure 5 The forward oil-slinging port of the rotor 3D includes a plurality of rotor oil-slinging channels. When viewed from the axial direction of the motor rotor 5, the plurality of rotor oil-slinging channels radiate outward in a linear or vortex shape with the axis of the motor rotor 5 as the center, and the radiation direction is the same as the rotation direction of the motor rotor 5.

[0095] This means that, when viewed axially from the motor rotor 5, all rotor oil-swing passages are inclined in the same direction as the motor rotor's rotational direction B and are spaced apart around the axis of the motor rotor 5. The rotor oil-swing passages can be linear or vortex-shaped. Thus, as the shaft 4 rotates, the lubricating oil tends to maintain its original position due to inertia, generating a rotational motion opposite to that of the motor rotor 5. The inclination of all rotor oil-swing passages in the forward oil-swing port of the rotor 3D is aligned with the rotational direction of the motor rotor 5. Due to inertia, the lubricating oil in the oil-cooling chamber 16 is swept out of the motor rotor 5 through the rotor oil-swing passages, thereby achieving the oil-swing function of the forward oil-swing port of the rotor 3D.

[0096] In order to enhance the cooling effect of the outer surface of the permanent magnet 51, based on the above embodiment, please refer to Figure 1 The rotor 3D is provided with two forward oil-slinging ports, namely the turbine-end rotor 3D forward oil-slinging port 17a and the compressor-end rotor 3D forward oil-slinging port 17b, and are respectively arranged adjacent to the two ends of the permanent magnet 51 on the motor rotor 5.

[0097] It should be noted that the temperature at the ends of the outer surface of the permanent magnet 51 is higher than the temperature at its center. Therefore, the forward oil-slinging port 17a of the turbine rotor 3D faces the first end of the permanent magnet 51, while the forward oil-slinging port 17b of the compressor rotor 3D faces the second end of the permanent magnet 51. This increases the amount of lubricating oil splashed onto the outer surfaces of the ends of the permanent magnet 51, thereby enhancing the cooling effect on the outer surface of the permanent magnet 51.

[0098] Taking into account the specific radial structure of the forward oil-splitting port 17a of the turbine end rotor 3D, on the basis of the above embodiment, observed from the radial direction of the motor rotor 5, the rotor oil-splitting channel in the forward oil-splitting port 17a of the turbine end rotor 3D is inclined toward the compressor impeller 2 along the direction from the axis of the motor rotor 5 to its outside.

[0099] like Figure 6 As shown, since the forward oil-slinging port 17a of the vortex end rotor 3D is located at the vortex end of the motor rotor 5, if all the vortex end rotor oil-slinging channels 171a in the forward oil-slinging port 17a of the vortex end rotor 3D are inclined toward the compressor impeller 2, the lubricating oil thrown out by the forward oil-slinging port 17a of the vortex end rotor 3D will be better splashed onto the outer surface of the first end of the permanent magnet 51, and flow toward the outer surface of the second end of the permanent magnet 51 in the oil-cooling channel 18, so as to better cool the middle area of ​​the outer surface of the permanent magnet 51 and the inner winding of the motor stator 6 opposite thereto, thereby reducing the cooling dead zone of the outer surface of the permanent magnet 51 and the inner winding of the motor stator 6.

[0100] Taking into account the specific radial structure of the forward oil-swing port 17b of the compression end rotor 3D, on the basis of the above embodiment, observed from the radial direction of the motor rotor 5, the rotor oil-swing channel in the forward oil-swing port 17b of the compression end rotor 3D is inclined toward the turbine 3 along the direction from the axis of the motor rotor 5 to its outside.

[0101] Similarly, if Figure 6 As shown, since the forward oil-slinging port 17b of the pressure-end rotor 3D is located at the pressure end of the motor rotor 5, if all the pressure-end rotor oil-slinging channels 171b in the forward oil-slinging port 17b of the pressure-end rotor 3D are inclined toward the turbine 3, the lubricating oil thrown out by the forward oil-slinging port 17b of the pressure-end rotor 3D will be better splashed onto the outer surface of the second end of the permanent magnet 51, and flow toward the outer surface of the first end of the permanent magnet 51 in the oil-cooling channel 18, so as to further reduce the cooling dead zone of the outer surface of the permanent magnet 51 and the inner winding of the motor stator 6 facing it, thereby further better cooling the outer surface of the permanent magnet 51 and the inner winding of the motor stator 6.

[0102] Therefore, the forward oil-fling port 17a of the turbine end rotor 3D and the forward oil-fling port 17b of the pressure end rotor 3D are arranged in the radial direction according to the above two embodiments. The forward oil-fling port 17a of the turbine end rotor 3D and the forward oil-fling port 17b of the pressure end rotor 3D not only fully cool the outer surface areas of the two ends of the permanent magnet 51, but also fully cool the middle outer surface area of ​​the permanent magnet 51 and the inner winding of the motor stator 6, thereby realizing full-area cooling of the permanent magnet 51 and the inner winding of the motor stator 6.

[0103] In order to achieve axial balance of the motor rotor 5, on the basis of the above embodiment, the forward oil-fling port 15 at the center of the shaft is arranged at the center position of the permanent magnet 51 on the motor rotor 5, and the forward oil-fling port 17a of the turbine end rotor 3D and the forward oil-fling port 17b of the pressure end rotor 3D are symmetrically arranged with the forward oil-fling port 15 at the center of the shaft as the center; when observed from the radial direction of the motor rotor 5, the rotor oil-fling channels in the forward oil-fling port 17a of the turbine end rotor 3D and the forward oil-fling port 17b of the pressure end rotor 3D have the same inclination angle from the axis of the motor rotor 5 to its outside and are in opposite inclination directions.

[0104] Specifically, such as Figure 6 and Figure 7 As shown, the turbine rotor oil-slinging passages 171a and the pressure rotor oil-slinging passages 171b are the same number, and the center position of the permanent magnet 51 is directly opposite the position of the forward oil-slinging port 15 at the center of the rotating shaft. The turbine rotor 3D forward oil-slinging port 17a and the pressure rotor 3D forward oil-slinging port 17b are symmetrically arranged around the forward oil-slinging port 15 at the center of the rotating shaft (i.e., the center position of the permanent magnet 51), so that the oil-slinging amount at both ends of the motor rotor 5 remains consistent. Furthermore, when viewed from the radial direction of the motor rotor 5, the turbine rotor oil-slinging passages 171a and the pressure rotor oil-slinging passages 171b have the same inclination angle from the axis of the motor rotor 5 to its outer side, and the inclination directions are opposite. This helps to ensure that the axial oil-slinging force at both ends of the motor rotor 5 remains consistent, thereby maintaining the balance of the motor rotor 5 in the axial direction.

[0105] In order to achieve radial balance of the motor rotor 5, on the basis of the above embodiment, the forward oil-fling port 15 at the center of the shaft is arranged at the center position of the permanent magnet 51 on the motor rotor 5, and the forward oil-fling port 17a of the turbine end rotor 3D and the forward oil-fling port 17b of the pressure end rotor 3D are symmetrically arranged with the forward oil-fling port 15 at the center of the shaft as the center; when observed from the axial direction of the motor rotor 5, the number of rotor oil-fling channels in the forward oil-fling port 17a of the turbine end rotor 3D and the forward oil-fling port 17b of the pressure end rotor 3D are the same and the radiation direction is the same.

[0106] Specifically, such as Figure 6 and Figure 7 As shown, the turbine rotor oil-slinging passages 171a and the pressure rotor oil-slinging passages 171b are identical in number, and the center position of the permanent magnet 51 is directly opposite the position of the forward oil-slinging port 15 at the center of the shaft. The turbine rotor 3D forward oil-slinging port 17a and the pressure rotor 3D forward oil-slinging port 17b are symmetrically arranged around the forward oil-slinging port 15 at the center of the shaft (i.e., the center position of the permanent magnet 51), ensuring that the oil-slinging amount at both ends of the motor rotor 5 remains consistent. Furthermore, when viewed from the axial direction of the motor rotor 5, the turbine rotor oil-slinging passages 171a and the pressure rotor oil-slinging passages 171b radiate in the same direction, which helps ensure that the radial oil-slinging force at both ends of the motor rotor 5 remains consistent, thereby maintaining radial balance of the motor rotor 5.

[0107] Based on any of the above examples, please refer to Figure 9 The middle shell three-dimensional water cooling loop 20 is arranged to extend spirally along the axial direction of the motor stator 6, so that the middle shell three-dimensional water cooling loop 20 completely covers the outer winding of the motor stator 6, avoiding the generation of a cooling dead zone and the phenomenon of insufficient cooling of the outer winding of the motor stator 6. The middle shell three-dimensional water cooling loop 20 fluctuates in a wave-like manner along the radial direction, which can increase the cooling area of ​​the middle shell three-dimensional water cooling loop 20, thereby improving the cooling effect of the outer winding of the motor stator 6.

[0108] Based on any of the above examples, please refer to Figure 1 The upper part of the shell 1 is provided with an oil inlet channel 22, which extends along the axis of the motor stator 6 and is arranged in the shell 1 adjacent to the outer periphery of the motor stator 6, and the oil inlet channel 22 is connected to the turbine end oil float bearing 7 and the pressure end oil float bearing 10. Therefore, the oil inlet channel 22 is arranged adjacent to the outer periphery of the motor stator 6, and the lubricating oil in the oil inlet channel 22 can cool the outer winding of the motor stator 6. Therefore, while supplying oil to the turbine end oil pool 8 and the pressure end oil, the outer winding of the motor stator 6 is cooled, which further improves the cooling effect of the motor stator 6. It should be noted that the shell 1, that is, the middle shell, is provided with an oil return outlet 21, and the lubricating oil in the oil cooling channel 18 can be discharged outside the shell 1 through the oil return outlet 21.

[0109] 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.

[0110] The various embodiments in this specification are described in a progressive manner, and each embodiment focuses on the differences from other embodiments. The same or similar parts between the various embodiments can be referenced to each other.

[0111] The above describes in detail the electrically assisted turbocharger cooling system provided by the present invention. Specific examples are used herein to illustrate the principles and implementation methods of the present invention. The description of the above embodiments is intended only to facilitate understanding of the method and core concepts of the present invention. It should be noted that those skilled in the art may make various improvements and modifications to the present invention without departing from the principles of the present invention, and such improvements and modifications fall within the scope of protection of the claims of the present invention.

Claims

1. An electrically assisted turbocharger cooling system, comprising a housing (1), a rotating shaft (4) rotatably disposed in the housing (1), and a compressor impeller (2) and a turbine (3) respectively disposed at two ends of the rotating shaft (4), characterized in that: Also includes: The motor rotor (5) is sleeved on the rotating shaft (4) and is spaced apart from the rotating shaft (4) to form an oil cooling chamber (16), and the rotating shaft (4) is provided with a rotating shaft center forward oil throwing port (15) located in the oil cooling chamber (16), and the motor rotor (5) is provided with a rotor 3D forward oil throwing port; A motor stator (6) is arranged on the outer periphery of the motor rotor (5), and a volute insulating water cooling loop (19) for blocking heat transfer between the motor stator (6) and the turbine (3) is provided between the motor stator (6) and the turbine (3), and the motor stator (6) is covered with a middle shell three-dimensional water cooling loop (20) along its axial direction; A turbine end oil pool (8) is arranged around the rotating shaft (4) and is located between the turbine end oil floating bearing (7) and the motor rotor (5); the rotating shaft (4) is provided with a turbine end rotating shaft 3D reverse oil suction port (13) located in the turbine end oil pool (8); A pressure end oil pool (11) is wound around the rotating shaft (4) and is located between the pressure end oil floating bearing (10) and the motor rotor (5); the rotating shaft (4) is provided with a pressure end rotating shaft 3D reverse oil suction port (14) located in the pressure end oil pool (11); The reverse oil suction port (13) of the turbine end rotating shaft 3D and the reverse oil suction port (14) of the pressure end rotating shaft 3D are both connected to the central forward oil throwing port (15) of the rotating shaft through the central hole cavity of the rotating shaft (4), and the central forward oil throwing port (15) of the rotating shaft is then connected to the oil cooling cavity (16), the forward oil throwing port of the rotor 3D, and the gap between the motor rotor (5) and the motor stator (6) in sequence.

2. The electrically assisted turbocharger cooling system according to claim 1, characterized in that: The vortex end shaft 3D reverse oil suction port (13) comprises a plurality of vortex end shaft oil suction passages (131). When viewed from the axial direction of the shaft (4), the plurality of vortex end shaft oil suction passages (131) radiate outward in a linear or spiral manner with the axis of the shaft (4) as the center, and the radiation direction is opposite to the rotation direction of the shaft (4).

3. The electrically assisted turbocharger cooling system according to claim 1, characterized in that: The vortex end shaft 3D reverse oil suction port (13) comprises a plurality of vortex end shaft oil suction passages (131). When viewed from the radial direction of the shaft (4), the vortex end shaft oil suction passages (131) are inclined along a direction from the outer side of the shaft (4) to the axis thereof toward the shaft center forward oil ejection port (15).

4. The electrically assisted turbocharger cooling system according to claim 1, characterized in that: The pressure end shaft 3D reverse oil suction port (14) comprises a plurality of pressure end shaft oil suction passages (141). When viewed from the axial direction of the shaft (4), the plurality of pressure end shaft oil suction passages (141) radiate outward in a linear or spiral manner with the axis of the shaft (4) as the center, and the radiation direction is opposite to the rotation direction of the shaft (4).

5. The electrically assisted turbocharger cooling system according to claim 1, characterized in that: The pressure end shaft 3D reverse oil suction port (14) comprises a plurality of pressure end shaft oil suction passages (141). When viewed from the radial direction of the shaft (4), the pressure end shaft oil suction passages (141) are inclined from the outer side of the shaft (4) to the axis thereof toward the shaft center forward oil ejection port (15).

6. The electrically assisted turbocharger cooling system according to claim 1, characterized in that: The shaft center forward oil-swing port (15) comprises a plurality of shaft oil-swing passages (151). When viewed from the axial direction of the shaft (4), the plurality of shaft oil-swing passages (151) radiate outward in a linear or spiral manner with the axis of the shaft (4) as the center, and the radiation direction is the same as the rotation direction of the shaft (4).

7. The electrically assisted turbocharger cooling system according to claim 1, characterized in that: The vortex end shaft 3D reverse oil suction port (13) comprises a plurality of vortex end shaft oil suction passages (131), and when viewed from the axial direction of the shaft (4), the plurality of vortex end shaft oil suction passages (131) radiate outward in a straight line or in a spiral shape with the axis of the shaft (4) as the center, and the radiation direction is opposite to the rotation direction of the shaft (4); The pressure end shaft 3D reverse oil suction port (14) comprises a plurality of pressure end shaft oil suction passages (141), and when viewed from the axial direction of the shaft (4), the plurality of pressure end shaft oil suction passages (141) radiate outward in a linear or spiral manner with the axis of the shaft (4) as the center, and the radiation direction is opposite to the rotation direction of the shaft (4); The reverse oil suction port (13) of the turbine end rotating shaft 3D and the reverse oil suction port (14) of the pressure end rotating shaft 3D are symmetrically arranged with the forward oil dumping port (15) at the center of the rotating shaft as the center. When observed from the axial direction of the rotating shaft (4), the number of the turbine end rotating shaft oil suction channels (131) and the pressure end rotating shaft oil suction channels (141) are the same and the radiation direction is the same.

8. The electrically assisted turbocharger cooling system according to claim 1, characterized in that: The vortex end shaft 3D reverse oil suction port (13) comprises a plurality of vortex end shaft oil suction passages (131), and when viewed from the radial direction of the shaft (4), the vortex end shaft oil suction passages (131) are inclined along the direction from the outer side of the shaft (4) to the axis thereof toward the shaft center forward oil ejection port (15); The pressure end shaft 3D reverse oil suction port (14) comprises a plurality of pressure end shaft oil suction passages (141), and when viewed from the radial direction of the shaft (4), the pressure end shaft oil suction passages (141) are inclined from the outer side of the shaft (4) to the axis thereof toward the shaft center forward oil ejection port (15); The reverse oil suction port (13) of the vortex end rotating shaft 3D and the reverse oil suction port (14) of the pressure end rotating shaft 3D are symmetrically arranged with the forward oil dumping port (15) at the center of the rotating shaft as the center. When observed from the radial direction of the rotating shaft (4), the number of the vortex end rotating shaft oil suction channels (131) and the number of the pressure end rotating shaft oil suction channels (141) are the same. The inclination angles of the vortex end rotating shaft oil suction channels (131) and the pressure end rotating shaft oil suction channels (141) along the direction from the outer side of the rotating shaft (4) to the axis thereof are the same and the inclination directions are opposite.

9. The electrically assisted turbocharger cooling system according to claim 1, characterized in that: The rotor 3D forward oil-slinging port comprises a plurality of rotor oil-slinging passages. When viewed from the axial direction of the motor rotor (5), the plurality of rotor oil-slinging passages radiate outward in a linear or vortex shape with the axis of the motor rotor (5) as the center, and the radiation direction is the same as the rotation direction of the motor rotor (5).

10. The electrically assisted turbocharger cooling system according to claim 1, characterized in that: The rotor 3D is provided with two forward oil-slinging ports, namely a turbine-end rotor 3D forward oil-slinging port (17a) and a compressor-end rotor 3D forward oil-slinging port (17b), and are respectively arranged adjacent to two ends of the permanent magnet (51) on the motor rotor (5).

11. The electrically assisted turbocharger cooling system according to claim 10, characterized in that: The forward oil-slinging port of the rotor 3D comprises a plurality of rotor oil-slinging passages. When viewed from the axial direction of the motor rotor (5), the plurality of rotor oil-slinging passages radiate outwards in a linear or vortex shape with the axis of the motor rotor (5) as the center, and the radiation direction is the same as the rotation direction of the motor rotor (5); Observed from the radial direction of the motor rotor (5), the rotor oil-slinging passage in the oil-slinging port (17a) of the turbine end rotor 3D is inclined toward the compressor impeller (2) along the direction from the axis of the motor rotor (5) to the outside thereof.

12. The electrically assisted turbocharger cooling system according to claim 10, characterized in that: The forward oil-slinging port of the rotor 3D comprises a plurality of rotor oil-slinging passages. When viewed from the axial direction of the motor rotor (5), the plurality of rotor oil-slinging passages radiate outwards in a linear or vortex shape with the axis of the motor rotor (5) as the center, and the radiation direction is the same as the rotation direction of the motor rotor (5); Observed from the radial direction of the motor rotor (5), the rotor oil-slinging passage in the oil-slinging port (17b) of the compression-end rotor 3D is inclined toward the turbine (3) along the direction from the axis of the motor rotor (5) to the outside thereof.

13. The electrically assisted turbocharger cooling system according to claim 1, characterized in that: The forward oil-slinging port of the rotor 3D comprises a plurality of rotor oil-slinging passages. When viewed from the axial direction of the motor rotor (5), the plurality of rotor oil-slinging passages radiate outwards in a linear or vortex shape with the axis of the motor rotor (5) as the center, and the radiation direction is the same as the rotation direction of the motor rotor (5); The rotor 3D is provided with two forward oil-slinging ports, which are divided into a turbine-end rotor 3D forward oil-slinging port (17a) and a compressor-end rotor 3D forward oil-slinging port (17b), and are respectively arranged adjacent to two ends of the permanent magnet (51) on the motor rotor (5); When observed from the radial direction of the motor rotor (5), the rotor oil-slinging passage in the oil-slinging port (17a) of the turbine end rotor 3D is inclined toward the compressor impeller (2) along the direction from the axis of the motor rotor (5) to the outside thereof; Observing from the radial direction of the motor rotor (5), the rotor oil-slinging passage in the downstream oil-slinging port (17b) of the compression end rotor 3D is inclined toward the turbine (3) along the direction from the axis of the motor rotor (5) to the outside thereof; The shaft center forward oil-slinging port (15) is arranged at the center position of the permanent magnet (51) on the motor rotor (5), and the turbine end rotor 3D forward oil-slinging port (17a) and the compressor end rotor 3D forward oil-slinging port (17b) are symmetrically arranged with the shaft center forward oil-slinging port (15) as the center; Observed from the radial direction of the motor rotor (5), the rotor oil-slinging passages in the forward oil-slinging port (17a) of the turbine end rotor 3D and the forward oil-slinging port (17b) of the pressure end rotor 3D have the same inclination angle and opposite inclination directions in the direction from the axis of the motor rotor (5) to the outside thereof.

14. The electrically assisted turbocharger cooling system according to claim 1, characterized in that: The forward oil-slinging port of the rotor 3D comprises a plurality of rotor oil-slinging passages. When viewed from the axial direction of the motor rotor (5), the plurality of rotor oil-slinging passages radiate outwards in a linear or vortex shape with the axis of the motor rotor (5) as the center, and the radiation direction is the same as the rotation direction of the motor rotor (5); The rotor 3D is provided with two forward oil-slinging ports, which are divided into a turbine-end rotor 3D forward oil-slinging port (17a) and a compressor-end rotor 3D forward oil-slinging port (17b), and are respectively arranged adjacent to two ends of the permanent magnet (51) on the motor rotor (5); The shaft center forward oil-slinging port (15) is arranged at the center position of the permanent magnet (51) on the motor rotor (5), and the turbine end rotor 3D forward oil-slinging port (17a) and the compressor end rotor 3D forward oil-slinging port (17b) are symmetrically arranged with the shaft center forward oil-slinging port (15) as the center; Observed from the axial direction of the motor rotor (5), the number of rotor oil-slinging passages in the forward oil-slinging opening (17a) of the turbine-end rotor 3D and the forward oil-slinging opening (17b) of the compressor-end rotor 3D are the same and their radiation directions are the same.

15. The electrically assisted turbocharger cooling system according to claim 1, characterized in that: When viewed from the axial direction of the casing (1), the volute insulating water cooling loop (19) is arranged in the casing (1) along the circumference of the vortex end oil pool (8).

16. The electrically assisted turbocharger cooling system according to claim 1, characterized in that: The middle shell three-dimensional water cooling loop (20) is arranged to extend spirally along the axis direction of the motor stator (6), and the middle shell three-dimensional water cooling loop (20) fluctuates in a wave-like manner along the radial direction.

Images