An electric-assisted turbocharger cooling system

Abstract

The present invention discloses an electric-assisted turbocharger cooling system, which relates to the technical field of temperature field control of electric-assisted turbochargers. It includes a motor rotor that forms an oil cooling cavity at an interval from the rotating shaft, and there is a shaft center forward oil slinger in the oil cooling cavity on the rotating shaft, and a rotor 3D forward oil slinger on the motor rotor; a volute heat insulation water cooling loop is used to block the heat transfer between the motor stator and the turbine, and the motor stator is covered with a middle shell three-dimensional water cooling loop along its axial direction; a turbine end oil sump is wound around the rotating shaft and is located between the turbine end oil floating bearing and the motor rotor, and there is a turbine end shaft 3D reverse oil suction port in the turbine end oil sump on the rotating shaft; a compressor end oil sump is wound around the rotating shaft and is located between the compressor end oil floating bearing and the motor rotor, and there is a compressor end shaft 3D reverse oil suction port in the compressor end oil sump on the rotating shaft. This application can comprehensively cool the stator and rotor in the permanent magnet synchronous motor, thereby improving the reliable stability of the operation of the electric-assisted turbocharger.

Description

Technical Field

[0001] The present invention relates to the technical field of temperature field control of an electric-assisted turbocharger, and more specifically, to an electric-assisted turbocharger cooling system. Background Art

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

[0003] However, after the permanent magnet synchronous motor is connected in series with the turbocharger, one side of the motor rotor is connected to the same rotating shaft as the turbine. The high-temperature heat at the turbine end will be transmitted along the rotating shaft to the motor rotor, causing the motor rotor to demagnetize at high temperature. The other side of the permanent magnet motor rotor is also connected to the same rotating shaft as the compressor impeller. The high-temperature heat at the compressor end will also be transmitted along the rotating shaft to the motor rotor, thereby causing the motor rotor to demagnetize at high temperature. In addition, the motor stator is connected to the turbocharger volute through metal, and the high-temperature exhaust gas will be transmitted from the turbine housing to the motor stator. The motor stator is also connected to the turbocharger compressor housing through metal, and the heat energy generated by the compressor will also be transmitted to the motor stator, causing insulation and enameled wire failure, and even posing serious safety hazards.

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

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

[0006] To achieve the above purpose, the present invention provides the following technical solutions:

[0007] An electric-assisted turbocharger cooling system, including a housing, a rotating shaft rotatably arranged in the housing, a compressor impeller and a turbine respectively arranged at both ends of the rotating shaft, and further including:

[0008] A motor rotor, sleeved on the rotating shaft and spaced from the rotating shaft to form an oil cooling cavity, and a shaft center forward oil slinger is arranged on the rotating shaft in the oil cooling cavity, and a rotor 3D forward oil slinger is arranged on the motor rotor;

[0009] A motor stator, arranged on the outer periphery of the motor rotor, and a volute water-cooling loop for blocking the heat transfer between the motor stator and the turbine is arranged between the motor stator and the turbine, and a middle shell three-dimensional water-cooling loop is covered along the axial direction of the motor stator;

[0010] The vortex-end oil sump is wound around the rotating shaft and located between the vortex-end oil floating bearing and the motor rotor. A 3D reverse oil suction port of the vortex-end rotating shaft is provided on the rotating shaft and located in the vortex-end oil sump.

[0011] The pressure-end oil sump is wound around the rotating shaft and located between the pressure-end oil floating bearing and the motor rotor. A 3D reverse oil suction port of the pressure-end rotating shaft is provided on the rotating shaft and located in the pressure-end oil sump.

[0012] Wherein, the 3D reverse oil suction port of the vortex-end rotating shaft and the 3D reverse oil suction port of the pressure-end rotating shaft are both communicated with the forward oil throwing port at the center of the rotating shaft through the central hole cavity of the rotating shaft, and the forward oil throwing port at the center of the rotating shaft is further communicated with the oil cooling cavity, the 3D forward oil throwing port of the rotor, and the gap between the motor rotor and the motor stator in sequence.

[0013] On the other hand, the 3D reverse oil suction port of the vortex-end rotating shaft includes a plurality of oil suction channels of the vortex-end rotating shaft. When observed from the axial direction of the rotating shaft, the plurality of oil suction channels of the vortex-end rotating shaft are linearly radiated or vortex-shaped radiated outward with the axis of the rotating shaft as the center, and the radiation direction is opposite to the rotation direction of the rotating shaft.

[0014] On the other hand, the 3D reverse oil suction port of the vortex-end rotating shaft includes a plurality of oil suction channels of the vortex-end rotating shaft. When observed from the radial direction of the rotating shaft, the oil suction channels of the vortex-end rotating shaft are inclined towards the forward oil throwing port at the center of the rotating shaft along the direction from the outer side of the rotating shaft to its axis.

[0015] On the other hand, the 3D reverse oil suction port of the pressure-end rotating shaft includes a plurality of oil suction channels of the pressure-end rotating shaft. When observed from the axial direction of the rotating shaft, the plurality of oil suction channels of the pressure-end rotating shaft are linearly radiated or vortex-shaped radiated outward with the axis of the rotating shaft as the center, and the radiation direction is opposite to the rotation direction of the rotating shaft.

[0016] On the other hand, the 3D reverse oil suction port of the pressure-end rotating shaft includes a plurality of oil suction channels of the pressure-end rotating shaft. When observed from the radial direction of the rotating shaft, the oil suction channels of the pressure-end rotating shaft are inclined towards the forward oil throwing port at the center of the rotating shaft along the direction from the outer side of the rotating shaft to its axis.

[0017] On the other hand, the forward oil throwing port at the center of the rotating shaft includes a plurality of oil throwing channels of the rotating shaft. When observed from the axial direction of the rotating shaft, the plurality of oil throwing channels of the rotating shaft are linearly radiated or vortex-shaped radiated outward 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 3D reverse oil suction port of the vortex end rotating shaft includes a plurality of oil suction channels of the vortex end rotating shaft. When observed axially from the rotating shaft, the plurality of oil suction channels of the vortex end rotating shaft radiate linearly or spirally outward with the axis of the rotating shaft as the center, and the radiation direction is opposite to the rotation direction of the rotating shaft;

[0019] The 3D reverse oil suction port of the pressure end rotating shaft includes a plurality of oil suction channels of the pressure end rotating shaft. When observed axially from the rotating shaft, the plurality of oil suction channels of the pressure end rotating shaft radiate linearly or spirally outward with the axis of the rotating shaft as the center, and the radiation direction is opposite to the rotation direction of the rotating shaft;

[0020] The 3D reverse oil suction port of the vortex end rotating shaft and the 3D reverse oil suction port of the pressure end rotating shaft are symmetrically arranged with the forward oil throwing port at the center of the rotating shaft as the center. When observed axially from the rotating shaft, the number of the oil suction channels of the vortex end rotating shaft is the same as that of the oil suction channels of the pressure end rotating shaft and the radiation directions are the same.

[0021] On the other hand, the 3D reverse oil suction port of the vortex end rotating shaft includes a plurality of oil suction channels of the vortex end rotating shaft. When observed radially from the rotating shaft, the oil suction channels of the vortex end rotating shaft incline towards the forward oil throwing port at the center of the rotating shaft along the direction from the outside of the rotating shaft to its axis;

[0022] The 3D reverse oil suction port of the pressure end rotating shaft includes a plurality of oil suction channels of the pressure end rotating shaft. When observed radially from the rotating shaft, the oil suction channels of the pressure end rotating shaft incline towards the forward oil throwing port at the center of the rotating shaft along the direction from the outside of the rotating shaft to its axis;

[0023] The 3D reverse oil suction port of the vortex end rotating shaft and the 3D reverse oil suction port of the pressure end rotating shaft are symmetrically arranged with the forward oil throwing port at the center of the rotating shaft as the center. When observed radially from the rotating shaft, the number of the oil suction channels of the vortex end rotating shaft is the same as that of the oil suction channels of the pressure end rotating shaft, and the inclination angles of the oil suction channels of the vortex end rotating shaft and the oil suction channels of the pressure end rotating shaft along the direction from the outside of the rotating shaft to its axis are the same and the inclination directions are opposite.

[0024] On the other hand, the 3D forward oil throwing port of the rotor includes a plurality of oil throwing channels of the rotor. When observed axially from the motor rotor, the plurality of oil throwing channels of the rotor radiate linearly or spirally outward 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 3D forward oil throwing port of the rotor is provided with two, which are divided into the 3D forward oil throwing port of the vortex end rotor and the 3D forward oil throwing port of the pressure end rotor and are respectively arranged adjacent to both ends of the permanent magnet on the motor rotor.

[0026] On the other hand, the rotor 3D forward oil slinger includes a plurality of rotor oil slinger channels. When observed axially from the motor rotor, the plurality of rotor oil slinger channels radiate linearly or in a vortex shape outward 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] When observed radially from the motor rotor, the rotor oil slinger channels in the vortex-end rotor 3D forward oil slinger incline towards the compressor impeller along the direction from the axis of the motor rotor to its outer side.

[0028] On the other hand, the rotor 3D forward oil slinger includes a plurality of rotor oil slinger channels. When observed axially from the motor rotor, the plurality of rotor oil slinger channels radiate linearly or in a vortex shape outward 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] When observed radially from the motor rotor, the rotor oil slinger channels in the pressure-end rotor 3D forward oil slinger incline towards the turbine along the direction from the axis of the motor rotor to its outer side.

[0030] On the other hand, the rotor 3D forward oil slinger includes a plurality of rotor oil slinger channels. When observed axially from the motor rotor, the plurality of rotor oil slinger channels radiate linearly or in a vortex shape outward 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 forward oil slinger is provided with two, which are divided into a vortex-end rotor 3D forward oil slinger and a pressure-end rotor 3D forward oil slinger and are respectively arranged adjacent to both ends of the permanent magnet on the motor rotor;

[0032] When observed radially from the motor rotor, the rotor oil slinger channels in the vortex-end rotor 3D forward oil slinger incline towards the compressor impeller along the direction from the axis of the motor rotor to its outer side;

[0033] When observed radially from the motor rotor, the rotor oil slinger channels in the pressure-end rotor 3D forward oil slinger incline towards the turbine along the direction from the axis of the motor rotor to its outer side;

[0034] The shaft center forward oil slinger is arranged at the center position of the permanent magnet on the motor rotor, and the vortex-end rotor 3D forward oil slinger and the pressure-end rotor 3D forward oil slinger are symmetrically arranged with the shaft center forward oil slinger as the center;

[0035] When observed radially from the motor rotor, the rotor oil slinger channels in the vortex-end rotor 3D forward oil slinger and the pressure-end rotor 3D forward oil slinger have the same inclination angle and opposite inclination directions along the direction from the axis of the motor rotor to its outer side.

[0036] On the other hand, the rotor 3D forward oil slinger includes a plurality of rotor oil slinger channels. When observed axially from the axis of the motor rotor, the plurality of rotor oil slinger channels radiate linearly or spirally outward 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] Two rotor 3D forward oil slingers are provided, which are divided into a vortex-end rotor 3D forward oil slinger and a pressure-end rotor 3D forward oil slinger and are respectively arranged adjacent to both ends of the permanent magnet on the motor rotor.

[0038] The shaft center forward oil slinger is arranged at the center position of the permanent magnet on the motor rotor, and the vortex-end rotor 3D forward oil slinger and the pressure-end rotor 3D forward oil slinger are symmetrically arranged with the shaft center forward oil slinger as the center.

[0039] When observed axially from the axis of the motor rotor, the number of rotor oil slinger channels in the vortex-end rotor 3D forward oil slinger is the same as that in the pressure-end rotor 3D forward oil slinger, and the radiation direction is the same.

[0040] On the other hand, when observed axially from the housing, the volute casing heat-insulated water-cooling loop is arranged circumferentially along the vortex-end oil sump in the housing.

[0041] On the other hand, the middle casing three-dimensional water-cooling loop extends spirally along the axis line direction of the motor stator, and the middle casing three-dimensional water-cooling loop fluctuates in a wavy shape in the radial direction.

[0042] For the electric-assisted turbocharger cooling system provided by the present invention, on the one hand, oil cooling technology is used to cool the motor stator and rotor. The specific process is as follows: the vortex-end shaft 3D reverse oil suction port sucks the lubricating oil in the vortex-end oil sump into the central hole cavity of the shaft, the pressure-end shaft 3D reverse oil suction port sucks the lubricating oil in the pressure-end oil sump into the central hole cavity of the shaft, and then the shaft center forward oil slinger throws the lubricating oil in the shaft out into the oil cooling cavity to achieve full-area cooling of the interior of the motor rotor. Then, the rotor 3D forward oil slinger throws the lubricating oil in the oil cooling cavity out and splashes it onto the inner winding of the motor stator. After being blocked by the winding, part of the splashed lubricating oil is reflected onto the outer surface of the motor rotor, realizing the cooling of the inner winding of the motor stator and the exterior of the motor rotor. Therefore, the present invention uses oil cooling technology to achieve full-area cooling temperature control of the motor rotor, and at the same time, it also realizes the cooling temperature control of the inner winding of the stator adjacent to the motor rotor.

[0043] On the other hand, the water-cooling technology is used to cool the motor stator. The specific process is as follows: The water-cooling loop separated by the volute can block the heat transfer from the turbine side to the motor stator, achieving heat insulation protection for the motor stator. In addition, the three-dimensional water-cooling loop in the middle shell can cool the outer winding of the motor stator and all areas of the stator core. Therefore, the present invention uses the water-cooling technology to block the heat transferred from the volute to the motor stator and simultaneously cool all areas of the outer winding and the stator core of the motor stator. Furthermore, combined with the above oil-cooling technology, the full-area cooling and temperature control of the motor stator are achieved.

[0044] In summary, the electric-assisted turbocharger cooling system provided by the present invention combines oil-cooling and water-cooling technologies, which 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 reliable stability of the operation of the electric-assisted turbocharger. Brief Description of the Drawings

[0045] In order to more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the following will briefly introduce the drawings required for use in the description of the embodiments or the prior art. Obviously, the drawings in the following description are only the embodiments of the present invention. For those of ordinary skill in the art, other drawings can be obtained according to the provided drawings without creative efforts.

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

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

[0048] Figure 3 It is a schematic diagram of the forward oil slinging port of the shaft center along the axis of the shaft of the present invention;

[0049] Figure 4 It is a cross-sectional view of the shaft along the axis of the shaft of the present invention;

[0050] Figure 5 It is a schematic diagram of the 3D forward oil slinging port of the volute end rotor along the axis of the motor rotor of the present invention;

[0051] Figure 6 It is a cross-sectional view of the motor rotor along the axis of the shaft of the present invention;

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

[0053] Figure 8Schematic diagram of the volute heat-insulating water-cooled loop provided by the present invention;

[0054] Figure 9 Schematic diagram of the middle shell three-dimensional water-cooled loop provided by the present invention.

[0055] Reference numerals:

[0056] 1 - housing; 2 - compressor impeller; 3 - turbine; 4 - rotating shaft; 5 - motor rotor; 6 - motor stator; 7 - volute-end oil floating bearing; 8 - volute-end oil sump; 9 - volute-end oil seal; 10 - compressor-end oil floating bearing; 11 - compressor-end oil sump; 12 - compressor-end oil seal; 13 - 3D reverse oil suction port of the volute-end rotating shaft; 14 - 3D reverse oil suction port of the compressor-end rotating shaft; 15 - forward oil throwing port at the center of the rotating shaft; 16 - oil cooling chamber; 17a - 3D forward oil throwing port of the volute-end rotor; 17b - 3D forward oil throwing port of the compressor-end rotor; 18 - oil cooling flow path; 19 - volute heat-insulating water-cooled loop; 20 - middle shell three-dimensional water-cooled loop; 21 - oil return outlet; 22 - oil inlet passage; 51 - permanent magnet; 131 - oil suction passage of the volute-end rotating shaft; 141 - oil suction passage of the compressor-end rotating shaft; 151 - oil throwing passage of the rotating shaft; 171a - oil throwing passage of the volute-end rotor; 171b - oil throwing passage of the compressor-end rotor; A - rotating direction of the rotating shaft; B - rotating direction of the motor rotor. Detailed implementation manners

[0057] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts shall fall within the protection scope of the present invention.

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

[0059] It should be noted that in this embodiment, the orientation or positional relationship indicated by "up", "down", "front", "back", etc. is based on the orientation or positional relationship shown in the accompanying drawings. It is only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation to the present application.

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

[0061] The motor rotor 5 is sleeved on the rotating shaft 4 and forms an oil-cooling cavity 16 at an interval with the rotating shaft 4, and a shaft center forward oil-slinging port 15 located in the oil-cooling cavity 16 is provided on the rotating shaft 4, and a rotor 3D forward oil-slinging port is provided on the motor rotor 5.

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

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

[0064] The compressor-end oil sump 11 is wound around the rotating shaft 4 and is located between the compressor-end oil floating bearing 10 and the motor rotor 5, and a compressor-end shaft 3D reverse oil-sucking port 14 located in the compressor-end oil sump 11 is provided on the rotating shaft 4.

[0065] Wherein, the turbine-end shaft 3D reverse oil-sucking port 13 and the compressor-end shaft 3D reverse oil-sucking port 14 are both communicated with the shaft center forward oil-slinging port 15 through the central hole cavity of the rotating shaft 4, and the shaft center forward oil-slinging port 15 is further communicated with the oil-cooling cavity 16, the rotor 3D forward oil-slinging port, and the gap between the motor rotor 5 and the motor stator 6 in sequence.

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

[0067] It should be noted that the motor rotor 5 in the permanent magnet synchronous motor is mainly composed of a permanent magnet 51 and a rotor core. The permanent magnet 51 is disposed on the outer peripheral surface of the rotor core. The permanent magnet 51 is used to provide the required magnetic field, and the rotor core supports the permanent magnet 51 and provides a magnetic circuit. In addition, the motor stator 6 in the permanent magnet synchronous motor is mainly composed of a stator winding and a stator core. The stator winding is wound around the stator core. The stator winding is connected to a power supply. The current of the stator winding interacts with the magnetic field generated by the permanent magnet 51 to generate a torque, thereby driving the motor rotor 5 to rotate. Therefore, the stator winding and the permanent magnet 51 are key components for realizing energy conversion, and heat will be generated during the operation of the motor.

[0068] In this embodiment, the motor stator 6 is disposed on the middle housing around the outer periphery 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, and the electromagnetic field coupling effect is realized through the preset distance between the stator and the rotor, generating an electromagnetic torque to rotate the motor rotating shaft 4.

[0069] Wherein, a preset distance is left between the inner side of the motor rotor 5 and the outer side of the rotating shaft 4, so that an oil cooling cavity 16 is formed therebetween, and the oil cooling cavity 16 covers the entire inner area of the permanent magnet 51. And a preset distance is left between the inner winding of the motor stator 6 and the permanent magnet 51, which not only enables the electromagnetic induction cooperation between the stator winding and the permanent magnet 51, but also forms an oil cooling flow channel 18 for the lubricating oil to flow between the two.

[0070] In this embodiment, a turbine end oil floating bearing 7 is sleeved on the rotating shaft 4 near the turbine 3 for supporting the turbine end rotation of the rotating shaft 4. The turbine end oil sump 8 is wound around the rotating shaft 4 and located between the turbine end oil floating bearing 7 and the motor rotor 5, so that the rotating shaft 4 is immersed in the turbine end oil sump 8, and the turbine end oil sump 8 is filled with lubricating oil. It should be noted that a turbine end oil seal 9 is sleeved on the rotating shaft 4 between the turbine end oil sump 8 and the motor rotor 5 to prevent the lubricating oil in the turbine end oil sump 8 from leaking.

[0071] In this embodiment, a compression end oil floating bearing 10 is sleeved on the rotating shaft 4 near the compressor impeller for supporting the compression end rotation of the rotating shaft 4. The compression end oil sump 11 is wound around the rotating shaft 4 and located between the compression end oil floating bearing 10 and the motor rotor 5, so that the rotating shaft 4 is immersed in the compression end oil sump 11, and the compression end oil sump 11 is filled with lubricating oil. It should be noted that a compression end oil seal 12 is sleeved on the rotating shaft 4 between the compression end oil sump 11 and the motor rotor 5 to prevent the lubricating oil in the compression end oil sump 11 from leaking.

[0072] In this embodiment, the rotating shaft 4 is a hollow rotating shaft 4, and a turbine end rotating shaft 3D reverse oil suction port 13 immersed in the turbine end oil sump 8 is provided on the rotating shaft 4. The turbine end rotating shaft 3D reverse oil suction port 13 is used to suck the lubricating oil in the turbine end oil sump 8 into the central hole cavity of the rotating shaft 4. A compression end rotating shaft 3D reverse oil suction port 14 immersed in the compression end oil sump 11 is also provided on the rotating shaft 4. The compression end rotating shaft 3D reverse oil suction port 14 is used to suck the lubricating oil in the compression end oil sump 11 into the central hole cavity of the rotating shaft 4.

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

[0074] In this embodiment, a rotor 3D forward oil slinger is provided at a position of the motor rotor 5 adjacent to the permanent magnet 51 thereon. The rotor 3D forward oil slinger is used to sling the lubricating oil in the oil cooling cavity 16 into the oil cooling flow channel 18, so as to cool the inner winding of the motor stator 6 and the outer surface of the permanent magnet 51 simultaneously.

[0075] In this embodiment, the volute heat-insulating water cooling loop 19 is arranged in the volute and located between the volute stop and the volute end oil sump 8, as Figure 1 and Figure 8 shown. The volute heat-insulating 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 playing a role of heat insulation protection for the motor stator 6.

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

[0077] To sum up, when the electric-assisted turbine 3 supercharger cooling system in the above embodiments cools and controls the temperature of the electric-assisted turbine 3 supercharger, the permanent magnet synchronous motor operates to drive the rotating shaft 4 to rotate. The volute end rotating shaft 3D reverse oil suction ports 13 and the compressor end rotating shaft 3D reverse oil suction ports 14 on both sides of the rotating shaft 4 both suck in the lubricating oil, and the lubricating oil is then slung out from the forward oil slinger 15 in the center of the rotating shaft into the oil cooling cavity 16 to realize the full-area cooling inside the motor rotor 5. Then, the lubricating oil is slung out through the rotor 3D forward oil slinger and splashes onto the inner winding of the motor stator 6. After being blocked by the winding, part of the lubricating oil is reflected to the outer surface of the motor rotor 5, realizing the cooling of the inner winding of the motor stator 6 and the outside of the motor rotor 5 (i.e., realizing the cooling of the outer surface of the permanent magnet 51). At the same time, the volute heat-insulating water cooling loop 19 blocks the heat transfer from the turbine 3 side to the motor stator 6, realizing heat 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 all regions of the stator core.

[0078] Therefore, the electric-assisted turbine 3 supercharger cooling system provided above combines oil cooling and water cooling technologies, can comprehensively cool the stator and rotor in the permanent magnet synchronous motor, realize the temperature control of the stator and rotor of the permanent magnet synchronous motor in the full range, and thus improve the reliable stability of the operation of the electric-assisted turbine 3 supercharger.

[0079] It should be noted that both the above-mentioned volute end oil floating bearing 7 and the compressor end oil floating bearing 10 have lubricating oil, which is used to reduce the frictional loss during the rotation of the rotating shaft 4 and ensure the stable rotation of the rotating shaft 4. And an oil inlet passage 22 that is respectively communicated with the volute end oil floating bearing 7 and the compressor end oil floating bearing 10 is usually provided on the housing 1. The specific structural setting of the oil inlet passage 22 can refer to the prior art, which is not the key point protected by the present invention, so it will not be described in detail herein.

[0080] Based on the above embodiments, please refer to Figure 1 , the turbine-end oil floating bearing 7 is communicated with the turbine-end oil sump 8, and the compressor-end oil floating bearing 10 is communicated with the compressor-end oil sump 11.

[0081] Thus, lubricating oil with a temperature meeting the requirements is injected into the compressor-end oil floating bearing 10 and the turbine-end oil floating bearing 7, so that the lubricating oil undertakes the functions of lubrication and cooling. On the one hand, the oil sump is replenished with liquid through the oil inlet channel of the oil floating bearing itself, which not only ensures that there is sufficient cooling liquid in the turbine-end oil sump 8 and the compressor-end oil sump 11, but also avoids adding an additional oil inlet channel for replenishing the oil sump, thereby simplifying the structure and saving the manufacturing cost; on the other hand, the lubricating oil in the turbine-end oil floating bearing 7 and the compressor-end oil floating bearing 10 has cold quantity, so that the turbine-end oil floating bearing 7 and the turbine-end oil sump 8 can jointly play a role in blocking the heat transfer from the turbine 3 to the motor rotor 5, and the compressor-end oil floating bearing 10 and the compressor-end oil sump 11 can jointly play a role in blocking the heat transfer from the compressor impeller 2 to the motor rotor 5, thereby enhancing the effect of cooling and temperature reduction of the motor rotor 5, further ensuring the reliable and stable operation of the motor rotor 5, and further improving the reliable stability of the operation of the electric-assisted turbine 3 supercharger.

[0082] Considering the specific structure of the turbine-end rotating shaft 3D reverse oil suction port 13 in the axial direction of the rotating shaft 4, based on the above embodiments, please refer to Figure 2 , the turbine-end rotating shaft 3D reverse oil suction port 13 includes a plurality of turbine-end rotating shaft oil suction channels 131. When observed from the axial direction of the rotating shaft 4, the plurality of turbine-end rotating shaft oil suction channels 131 are radially radiated outward in a straight line or a vortex shape with the axis of the rotating shaft 4 as the center, and the radiation direction is opposite to the rotation direction of the rotating shaft 4.

[0083] Equivalently, when observed from the axial direction of the rotating shaft 4, all the turbine-end rotating shaft oil suction channels 131 are inclined in a direction opposite to the rotation direction A of the rotating shaft and are arranged at intervals around the axis of the rotating shaft 4, and the turbine-end rotating shaft oil suction channels 131 can be in a straight line or a curved vortex shape. In this way, when the rotating shaft 4 rotates, the lubricating oil tends to maintain its original position due to inertia, and will generate a rotational movement in the opposite direction to the rotating shaft 4. Moreover, the inclination direction of all the turbine-end rotating shaft oil suction channels 131 in the turbine-end rotating shaft 3D reverse oil suction port 13 is opposite to the rotation direction of the rotating shaft 4, and the lubricating oil in the turbine-end oil suction sump will flow into the central cavity of the rotating shaft 4 through the turbine-end rotating shaft oil suction channels 131 due to inertia, thereby realizing the oil suction function of the turbine-end rotating shaft 3D reverse oil suction port 13.

[0084] Further considering the specific structure of the turbine-end rotating shaft 3D reverse oil suction port 13 in the radial direction of the rotating shaft 4, based on the above embodiments, please refer to Figure 4, when observed radially from the rotating shaft 4, the oil suction channel 131 of the vortex end rotating shaft inclines towards the forward oil throwing port 15 at the center of the rotating shaft in the direction from the outside of the rotating shaft 4 to its axis. In this way, the lubricating oil sucked in by the 3D reverse oil suction port 13 of the vortex end rotating shaft will flow towards the forward oil throwing port 15 at the center of the rotating shaft, so as to ensure that the lubricating oil sucked in by the 3D reverse oil suction port 13 of the vortex end rotating shaft all flows to the forward oil throwing port 15 at the center of the rotating shaft, thereby ensuring that the lubricating oil flowing into the rotating shaft 4 is all thrown out into the oil cooling cavity 16 through the forward oil throwing port 15 at the center of the rotating shaft, and further ensuring the smooth and reliable degree of the rotating shaft 4 in transporting the lubricating oil, and avoiding the waste of lubricating oil caused by the retention of lubricating oil in the rotating shaft 4.

[0085] Considering the specific structure of the 3D reverse oil suction port 14 of the pressure end rotating shaft in the axial direction of the rotating shaft 4, on the basis of the above embodiment, please refer to Figure 3 , the 3D reverse oil suction port 14 of the pressure end rotating shaft includes a plurality of oil suction channels 141 of the pressure end rotating shaft. When observed axially from the rotating shaft 4, the plurality of oil suction channels 141 of the pressure end rotating shaft are linearly radiated or vortex-shaped radiated outward with the axis of the rotating shaft 4 as the center, and the radiation direction is opposite to the rotation direction of the rotating shaft 4.

[0086] Equivalently, when observed axially from the rotating shaft 4, all the oil suction channels 141 of the pressure end rotating shaft incline towards the direction opposite to the rotation direction A of the rotating shaft and are arranged at intervals around the axis of the rotating shaft 4, and the oil suction channels 141 of the pressure end rotating shaft can be linear or curved in a vortex shape. In this way, when the rotating shaft 4 rotates, the lubricating oil will tend to maintain its original position due to inertia and will generate a rotational movement in the opposite direction to the rotating shaft 4. The inclination direction of all the oil suction channels 141 of the 3D reverse oil suction port 14 of the pressure end rotating shaft is opposite to the rotation direction of the rotating shaft 4, and the lubricating oil in the pressure end oil suction pool will flow into the central hole cavity of the rotating shaft 4 through the oil suction channels 141 of the pressure end rotating shaft due to inertia, thereby realizing the oil suction function of the 3D reverse oil suction port 14 of the pressure end rotating shaft.

[0087] Further considering the specific structure of the 3D reverse oil suction port 14 of the pressure end rotating shaft in the radial direction of the rotating shaft 4, on the basis of the above embodiment, please refer to Figure 4 , when observed radially from the rotating shaft 4, the oil suction channel 141 of the pressure end rotating shaft inclines towards the forward oil throwing port 15 at the center of the rotating shaft in the direction from the outside of the rotating shaft 4 to its axis. In this way, the lubricating oil sucked in by the 3D reverse oil suction port 14 of the pressure end rotating shaft will flow towards the forward oil throwing port 15 at the center of the rotating shaft, so as to ensure that the lubricating oil sucked in by the 3D reverse oil suction port 14 of the pressure end rotating shaft all flows to the forward oil throwing port 15 at the center of the rotating shaft, thereby ensuring that the lubricating oil flowing into the rotating shaft 4 is all thrown out into the oil cooling cavity 16 through the forward oil throwing port 15 at the center of the rotating shaft, and further ensuring the smooth and reliable degree of the rotating shaft 4 in transporting the lubricating oil, and avoiding the waste of lubricating oil caused by the retention of lubricating oil in the rotating shaft 4.

[0088] Considering the specific structure of the forward oil slinger at the center of the rotating shaft 15 in the axial direction of the rotating shaft 4, on the basis of the above embodiments, the forward oil slinger at the center of the rotating shaft 15 includes a plurality of oil slinger channels 151 of the rotating shaft. When observed from the axial direction of the rotating shaft 4, the plurality of oil slinger channels 151 of the rotating shaft are radially radiated outward in a straight line or a vortex shape centered on the axis of the rotating shaft 4, and the radiation direction is the same as the rotation direction of the rotating shaft 4.

[0089] That is, when observed from the axial direction of the rotating shaft 4, all the oil slinger channels 151 of the rotating shaft are inclined in the same direction as the rotation direction A of the rotating shaft and are arranged at intervals around the axis of the rotating shaft 4, and the oil slinger channels 151 of the rotating shaft can be in a straight line or a curved vortex shape. In this way, when the rotating shaft 4 rotates, the lubricating oil tends to maintain its original position due to inertia and will generate a rotational movement in the opposite direction to the rotating shaft 4. The inclination direction of all the oil slinger channels 151 in the forward oil slinger at the center of the rotating shaft 15 is the same as the rotation direction of the rotating shaft 4. The lubricating oil in the rotating shaft 4 will be thrown out through the oil slinger channels 151 due to inertia, thereby realizing the oil slinging function of the forward oil slinger at the center of the rotating shaft 15.

[0090] To achieve the balance of the rotating shaft 4 in the radial direction, on the basis of the above embodiments, please refer to Figure 2 、 Figure 3 and Figure 7 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 slinger at the center of the rotating shaft 15 as the center. When observed from the axial direction of the rotating shaft 4, the number of the oil suction channels 131 of the vortex end rotating shaft and the number of the oil suction channels 141 of the pressure end rotating shaft are the same and the radiation directions are the same.

[0091] It can be understood that the same number of the oil suction channels 131 of the vortex end rotating shaft and the oil suction channels 141 of the pressure end rotating shaft can make the oil suction amounts of the vortex end oil suction port and the pressure end oil suction port consistent. Further, when observed from the axial direction of the rotating shaft 4, all the oil suction channels 131 of the vortex end rotating shaft and all the oil suction channels 141 of the pressure end rotating shaft are symmetrically arranged with the forward oil slinger at the center of the rotating shaft 15 as the center and the radiation directions are the same, which is beneficial to keeping the radial oil suction forces of the vortex end and the pressure end of the rotating shaft 4 consistent, so that the rotating shaft 4 is balanced in the radial direction.

[0092] To achieve the balance of the rotating shaft 4 in the axial direction, on the basis of the above embodiments, please refer to Figure 1 and Figure 7 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 slinger at the center of the rotating shaft 15 as the center. When observed from the radial direction of the rotating shaft 4, the number of the oil suction channels 131 of the vortex end rotating shaft is the same as the number of the oil suction channels 141 of the pressure end rotating shaft, and the inclination angles of the oil suction channels 131 of the vortex end rotating shaft and the oil suction channels 141 of the pressure end rotating shaft along the direction from the outside of the rotating shaft 4 to its axis are the same and the inclination directions are opposite.

[0093] It can be understood that the number of oil suction channels 131 in the vortex end rotating shaft is the same as that of the oil suction channels 141 in the pressure end rotating shaft, which can keep the oil suction amounts of the oil suction ports in the vortex end and the pressure end consistent. Further, when observing from the radial direction of the rotating shaft 4, all the oil suction channels 131 in the vortex end rotating shaft and all the oil suction channels 141 in the pressure end rotating shaft are symmetrically arranged with the forward oil throwing port 15 at the center of the rotating shaft center, and have the same inclination angle and opposite inclination directions along the direction from the outside to the axis of the rotating shaft 4, which is beneficial to ensuring that the axial oil suction forces at the vortex end and the pressure end of the rotating shaft 4 are consistent, so as to keep the rotating shaft 4 balanced axially.

[0094] Considering the specific structure of the rotor 3D forward oil throwing port axially, on the basis of the above embodiments, please refer to Figure 5 , the rotor 3D forward oil throwing port includes a plurality of rotor oil throwing channels. When observing from the axial direction of the motor rotor 5, the plurality of rotor oil throwing channels radiate linearly or spirally outward 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] Equivalently, when observing from the axial direction of the motor rotor 5, all the rotor oil throwing channels are inclined in the same direction as the rotation direction B of the motor rotor and are arranged at intervals around the axis of the motor rotor 5, and the rotor oil throwing channels can be linear or curved spiral. In this way, when the rotating shaft 4 rotates, the lubricating oil will tend to maintain its original position due to inertia and will generate a rotational movement in the opposite direction to the motor rotor 5. The inclination directions of all the rotor oil throwing channels in the rotor 3D forward oil throwing port are the same as the rotation direction of the motor rotor 5, and the lubricating oil in the oil cooling cavity 16 will be thrown out of the outside of the motor rotor 5 through the rotor oil throwing channels due to inertia, so as to realize the oil throwing function of the rotor 3D forward oil throwing port.

[0096] To enhance the cooling effect on the outer surface of the permanent magnet 51, on the basis of the above embodiments, please refer to Figure 1 , the rotor 3D forward oil throwing port is set to two, which are divided into a vortex end rotor 3D forward oil throwing port 17a and a pressure end rotor 3D forward oil throwing port 17b and are respectively arranged adjacent to both ends of the permanent magnet 51 on the motor rotor 5.

[0097] It should be noted that the temperatures at both ends of the outer surface of the permanent magnet 51 are higher than the temperature in the middle. Therefore. The vortex end rotor 3D forward oil throwing port 17a faces the first end of the permanent magnet 51, and the pressure end rotor 3D forward oil throwing port 17b faces the second end of the permanent magnet 51. In this way, the amount of lubricating oil splashing onto the outer surfaces of both ends of the permanent magnet 51 can be increased, thereby enhancing the cooling effect on the outer surface of the permanent magnet 51.

[0098] Considering the specific mechanism of the 3D forward oil slinger port 17a of the turbine end rotor in the radial direction, on the basis of the above embodiments, when observing from the radial direction of the motor rotor 5, the rotor oil slinger channels in the 3D forward oil slinger port 17a of the turbine end rotor are inclined towards the compressor impeller 2 in the direction from the axis of the motor rotor 5 to its outer side.

[0099] As Figure 6 shown, since the 3D forward oil slinger port 17a of the turbine end rotor is located at the turbine end of the motor rotor 5, if all the turbine end rotor oil slinger channels 171a in the 3D forward oil slinger port 17a of the turbine end rotor are inclined towards the compressor impeller 2, the lubricating oil slung out from the 3D forward oil slinger port 17a of the turbine end rotor can better splash onto the outer surface of the first end of the permanent magnet 51 and flow towards 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 region of the outer surface of the permanent magnet 51 and the inner winding of the motor stator 6 opposite thereto, reducing the cooling dead zones on the outer surface of the permanent magnet 51 and the inner winding of the motor stator 6.

[0100] Considering the specific mechanism of the 3D forward oil slinger port 17b of the pressure end rotor in the radial direction, on the basis of the above embodiments, when observing from the radial direction of the motor rotor 5, the rotor oil slinger channels in the 3D forward oil slinger port 17b of the pressure end rotor are inclined towards the turbine 3 in the direction from the axis of the motor rotor 5 to its outer side.

[0101] Similarly, as Figure 6 shown, since the 3D forward oil slinger port 17b of the pressure end rotor is located at the pressure end of the motor rotor 5, if all the pressure end rotor oil slinger channels 171b in the 3D forward oil slinger port 17b of the pressure end rotor are inclined towards the turbine 3, the lubricating oil slung out from the 3D forward oil slinger port 17b of the pressure end rotor can better splash onto the outer surface of the second end of the permanent magnet 51 and flow towards 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 zones on the outer surface of the permanent magnet 51 and the inner winding of the motor stator 6 opposite thereto, thereby further better cooling the outer surface of the permanent magnet 51 and the inner winding of the motor stator 6.

[0102] Therefore, by arranging the 3D forward oil slinger port 17a of the turbine end rotor and the 3D forward oil slinger port 17b of the pressure end rotor in the radial direction according to the above two embodiments, the 3D forward oil slinger port 17a of the turbine end rotor and the 3D forward oil slinger port 17b of the pressure end rotor can not only fully cool the outer surface regions of both ends of the permanent magnet 51, but also fully cool the middle outer surface region of the permanent magnet 51 and the inner winding of the motor stator 6, thereby realizing the full-region cooling of the permanent magnet 51 and the inner winding of the motor stator 6.

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

[0104] Specifically, as Figure 6 and Figure 7 shown, the number of the vortex end rotor oil slinger channels 171a and the pressure end rotor oil slinger channels 171b is the same, and the center position of the permanent magnet 51 is directly opposite to the position of the shaft center forward oil slinger 15. The vortex end rotor 3D forward oil slinger 17a and the pressure end rotor 3D forward oil slinger 17b are symmetrically arranged with the shaft center forward oil slinger 15 (i.e., the center position of the permanent magnet 51) as the center, so that the oil slinging amounts at both ends of the motor rotor 5 are kept consistent. Further, when observed from the radial direction of the motor rotor 5, the vortex end rotor oil slinger channels 171a and the pressure end rotor oil slinger channels 171b have the same inclination angle and opposite inclination directions along the direction from the axis of the motor rotor 5 to its outside, which is beneficial to ensuring that the oil slinging forces at both ends of the motor rotor 5 in the axial direction are kept consistent, so that the motor rotor 5 is axially balanced.

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

[0106] Specifically, as Figure 6 and Figure 7 shown, the number of the vortex end rotor oil slinger channels 171a and the pressure end rotor oil slinger channels 171b is the same, and the center position of the permanent magnet 51 is directly opposite to the position of the shaft center forward oil slinger 15. The vortex end rotor 3D forward oil slinger 17a and the pressure end rotor 3D forward oil slinger 17b are symmetrically arranged with the shaft center forward oil slinger 15 (i.e., the center position of the permanent magnet 51) as the center, so that the oil slinging amounts at both ends of the motor rotor 5 are kept consistent. Further, when observed from the axial direction of the motor rotor 5, the vortex end rotor oil slinger channels 171a and the pressure end rotor oil slinger channels 171b have the same radiation direction, which is beneficial to ensuring that the oil slinging forces at both ends of the motor rotor 5 in the radial direction are kept consistent, so that the motor rotor 5 is radially balanced.

[0107] Based on any of the above embodiments, please refer to Figure 9 , the middle housing three-dimensional water cooling loop 20 extends spirally along the axis line direction of the motor stator 6, so that the middle housing three-dimensional water cooling loop 20 completely covers the outer winding of the motor stator 6, avoiding the phenomenon of insufficient cooling of the outer winding of the motor stator 6 caused by the generation of cooling dead zones, and the middle housing three-dimensional water cooling loop 20 undulates in a wavy shape in the radial direction, which can increase the cooling area of the middle housing 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 embodiments, please refer to Figure 1 , an oil inlet channel 22 is provided at the upper part of the housing 1. The oil inlet channel 22 extends along the axis line direction of the motor stator 6 and is arranged in the housing 1 adjacent to the outer periphery of the motor stator 6, and the oil inlet channel 22 is communicated with the turbine end oil floating bearing 7 and the compressor end oil floating bearing 10. Thus, 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 play the role of cooling the outer winding of the motor stator 6. Therefore, while realizing the supply of oil to the turbine end oil sump 8 and the compressor end, the outer winding of the motor stator 6 is cooled, further improving the cooling effect of the motor stator 6. It should be noted that the housing 1, that is, the middle housing, is provided with an oil return outlet 21, and the lubricating oil in the oil cooling flow channel 18 can be discharged out of the housing 1 through the oil return outlet 21.

[0109] It should be noted that in this specification, relational terms such as first and second are only used to distinguish one entity from several other entities, and 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. Each embodiment focuses on the differences from other embodiments. The same or similar parts among the various embodiments can be referred to each other.

[0111] The above has introduced in detail an electric-assisted turbocharger cooling system provided by the present invention. Specific examples are used in this article to elaborate on the principle and implementation manner of the present invention. The description of the above embodiments is only used to help understand the method and its core idea of the present invention. It should be pointed out that for those of ordinary skill in the art, without departing from the principle of the present invention, several improvements and modifications can be made to the present invention, and these improvements and modifications also fall within the protection scope 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 cavity (16), wherein the oil cooling cavity (16) covers the entire inner area of ​​the permanent magnet (51) on the motor rotor (5), and the rotating shaft (4) is provided with a rotating shaft center forward oil throwing port (15) located in the oil cooling cavity (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-slinging port (15) of the rotating shaft through the central hole cavity of the rotating shaft (4); the central forward oil-slinging port (15) of the rotating shaft is then connected to the oil cooling cavity (16), the forward oil-slinging port of the rotor 3D, and the gap between the motor rotor (5) and the motor stator (6) in sequence; 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 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); 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; 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.

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 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.

10. The electrically assisted turbocharger cooling system according to claim 1, characterized in that: 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.

11. 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).

12. 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.

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