A centrifugal compressor, turbocharger and vehicle

Abstract

The embodiment of the present application provides a centrifugal compressor, a turbocharger and a vehicle, wherein the centrifugal compressor comprises an impeller, a shell and a guide vane assembly, the impeller comprises a disc and a plurality of blades, the blades are arranged on a side of the disc along a radial direction and extend along the radial direction; the shell is provided with an airflow channel, the impeller is rotatably arranged in the airflow channel, the shell is provided with an air inlet along a circumferential direction of the impeller, the shell is provided with an air outlet along a radial direction of the impeller, the air outlet is located on a side of the impeller provided with the blades, and the airflow channel is connected with the air inlet and the air outlet; the guide vane assembly is arranged on the shell, the guide vane assembly comprises a guide vane, the airflow channel is provided with a mounting cavity on an inner wall upstream of the impeller along an airflow direction, and the guide vane is telescopically arranged in the mounting cavity; in an extended state of the guide vane, at least part of the guide vane is located in the airflow channel; and in a retracted state of the guide vane, the guide vane is completely located in the mounting cavity. The centrifugal compressor in the embodiment of the present application improves the working efficiency through the telescopic guide vane.

Description

Technical Field

[0001] This invention relates to the field of gas compression technology, specifically to a centrifugal compressor, a turbocharger, and a vehicle. Background Technology

[0002] In recent years, turbocharging technology has been widely used in vehicle engineering.

[0003] A turbocharger consists of components such as a centrifugal compressor and a turbine. The centrifugal compressor compresses outside gas and then feeds it into the engine's combustion chamber to improve the engine's low-speed torque and maximum power.

[0004] Centrifugal compressors contain impellers. The negative pressure generated by the rotation of the impeller draws outside air into the compressor. While the impeller blades are rotating, the direction of airflow and the direction of blade rotation constantly change. As the airflow rate decreases, the absolute velocity of the airflow also decreases, causing the angle between the relative velocity direction of the airflow and the blades to gradually increase. When this relative angle increases to a certain extent, airflow separation occurs, making the centrifugal compressor unable to operate stably. Summary of the Invention

[0005] In view of this, embodiments of this application aim to provide a centrifugal compressor, turbocharger, and vehicle capable of suppressing flow separation in the airflow.

[0006] To achieve the above objectives, the technical solution of this application embodiment is implemented as follows:

[0007] This invention provides a centrifugal compressor, which includes:

[0008] An impeller includes a disk and a plurality of blades, the blades being disposed on one radial side of the disk and extending radially;

[0009] The housing has an airflow channel, the impeller is rotatably disposed in the airflow channel, the housing has an air inlet along the circumference of the impeller, the housing has an air outlet along the radial direction of the impeller, and the air outlet is located on the side of the impeller where the blades are disposed, and the airflow channel connects the air inlet and the air outlet;

[0010] A guide vane assembly is disposed on the housing. The guide vane assembly includes a guide vane. The airflow channel is provided with an installation cavity on the inner wall of the impeller upstream along the airflow direction. The installation cavity is open to communicate with the airflow channel. The guide vane is retractably disposed in the installation cavity.

[0011] In the extended state of the guide vane, at least a portion of the guide vane is located in the airflow channel; in the retracted state of the guide vane, the guide vane is completely located in the mounting cavity.

[0012] In some embodiments, the guide vane is rotatable, and its rotation direction is perpendicular to its extension direction.

[0013] In some embodiments, the projection of the mounting cavity along the extension and retraction direction of the guide vane is circular.

[0014] In some embodiments, the airflow channel includes an air inlet section and an impeller section connected sequentially along the airflow direction, the impeller is disposed in the impeller section, the outlet of the air inlet section is connected to the inlet of the impeller section, and the mounting cavity is disposed at the outlet position of the air inlet section.

[0015] In some embodiments, in the extended state of the guide vane, the maximum radial dimension of the projection of the portion of the guide vane extending out of the mounting cavity along the axial direction is h, and the maximum radial dimension of the projection of the tip of the blade along the airflow direction is H, where h ≤ 1 / 4H.

[0016] In some embodiments, in the extended state of the guide vane, the minimum distance between the end of the guide vane along the airflow direction and the beginning of the blade along the airflow direction within its projection range along the airflow direction is L1, and the dimension of the guide vane along the airflow direction is L2, where L1≤L2.

[0017] In some embodiments, the mounting cavity is located on the side of the airflow channel that is radially away from the wheel.

[0018] In some embodiments, in the extended state of the guide vane, the projection of the edge of the windward end of the vane away from the disc in the projection along the airflow direction is located within the projection range of the portion of the guide vane extending out of the mounting cavity.

[0019] In some embodiments, the guide vane assembly includes a spring and an electromagnet, the guide vane is made of iron-based material, the spring is connected between the housing and the guide vane, the electromagnet is disposed on the housing, and the electromagnet can be selectively energized to generate magnetic force on the guide vane. Under the force applied by the electromagnet and the spring, the guide vane switches between an extended state and a retracted state.

[0020] In some embodiments, the guide vane assembly includes a telescopic rod, the inner wall of the mounting cavity is provided with a mounting hole, the telescopic rod passes through the mounting hole, one end of the spring is connected to the guide vane, and the other end of the spring is connected to the inner wall of the mounting cavity.

[0021] In some embodiments, the electromagnet is located on the outer surface of the housing and on the side opposite to the mounting cavity.

[0022] This invention also provides a turbocharger, which includes any of the centrifugal compressors described in the foregoing embodiments.

[0023] This invention also provides a vehicle, which includes an engine and the turbocharger described in the foregoing embodiments, wherein the turbocharger's boost outlet is connected to the engine's airflow inlet.

[0024] The centrifugal compressor in this embodiment of the invention uses guide vanes to adjust the airflow direction of the blades, reducing the probability of airflow separation at the windward end of the blades and improving the operating stability of the centrifugal compressor. By switching the extended and retracted states of the guide vanes under different operating conditions, on the one hand, under low airflow conditions, the guide vanes can reduce the probability of airflow separation at the windward end of the blades; on the other hand, under high airflow conditions, the obstruction effect of the guide vanes on the airflow is reduced, thus reducing the kinetic energy loss of the airflow. This allows the centrifugal compressor in this embodiment of the invention to have a wider stable operating speed range and improves the working efficiency of the centrifugal compressor. Attached Figure Description

[0025] Figure 1 This is a schematic diagram of a centrifugal compressor in the retracted state of the guide vanes in one embodiment of the present invention, wherein the dashed arrows represent the airflow direction;

[0026] Figure 2 for Figure 1 The embodiment is a schematic diagram of a centrifugal compressor with the guide vanes extended. In this diagram, the dashed arrows represent the airflow direction, H is the maximum radial dimension of the blade tip along the airflow direction, and h is the maximum radial dimension of the projection of the portion of the guide vane extending out of the mounting cavity.

[0027] Figure 3 This is a schematic diagram of a centrifugal compressor in the extended state of the guide vane in another embodiment of the present invention. The dashed arrow represents the airflow direction, L1 is the minimum distance between the end of the guide vane along the airflow direction and the beginning of the blades along the airflow direction within the projection range along the airflow direction, and L2 is the dimension of the guide vane along the airflow direction.

[0028] Explanation of reference numerals in the attached figures

[0029] 10 housing; 10a airflow channel; 10b mounting cavity; 10c air inlet section; 10d impeller section; 10e air inlet; 10f air outlet; 10g mounting hole; 20 impeller; 21 disc; 22 blade; 30 guide vane assembly; 31 guide vane; 32 spring; 33 electromagnet; 34 telescopic rod Detailed Implementation

[0030] It should be noted that, unless otherwise specified, the embodiments and technical features in the embodiments of this application can be combined with each other, and the detailed descriptions in the specific implementation should be understood as explanations of the purpose of this application and should not be regarded as undue limitations on this application.

[0031] In the description of this application, "axial," "radial," or positional orientation or relationship is based on the appendix. Figure 1 The orientations or positional relationships shown are intended only for the convenience of describing this application and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0032] This invention provides a centrifugal compressor, see reference. Figure 1 and 2 The centrifugal compressor includes an impeller 20, a housing 10, and a guide vane assembly 30.

[0033] The impeller 20 includes a disk 21 and a plurality of blades 22, the blades 22 being disposed on one radial side of the disk 21 and extending radially. The plurality of blades 22 are arranged at intervals along the circumference of the disk 21.

[0034] The housing 10 is provided with an airflow channel 10a, and the impeller 20 is rotatably disposed in the airflow channel 10a. That is, when the centrifugal compressor is in operation, the impeller 21 rotates, thereby driving the blades 22 to rotate. During the rotation, the blades 22 push the gas, thereby generating an airflow in the airflow channel 10a.

[0035] The casing 10 has an air inlet 10e along the circumference of the impeller 20, and an air outlet 10f along the radial direction of the impeller 20, with the air outlet 10f located on the side of the impeller 20 where the blades 22 are located. The airflow passage 10a connects the air inlet 10e and the air outlet 10f. The airflow generated by the rotation of the impeller 20 is discharged from the centrifugal compressor through the air outlet 10f. At the same time, a negative pressure is generated in the airflow passage 10a, causing outside air to be drawn into the airflow passage 10a through the air inlet 10e, thereby continuously outputting airflow through the air outlet 10f.

[0036] The guide vane assembly 30 is disposed on the housing 10. The guide vane assembly 30 includes a guide vane 31. An installation cavity 10b is provided on the inner wall of the airflow channel 10a located upstream of the impeller 20 along the airflow direction. The installation cavity 10b is open to communicate with the airflow channel 10a. The guide vane 31 is retractably disposed in the installation cavity 10b.

[0037] The guide vane 31 includes an extended state and a retracted state.

[0038] Understandably, the guide vane 31 can switch between the extended and retracted states according to the actual working conditions.

[0039] With the guide vane 31 extended, at least a portion of the guide vane 31 is located in the airflow passage 10a. At least a portion of the guide vane 31 extends into the airflow passage 10a through the open position of the mounting cavity 10b. The portion of the guide vane 31 located in the airflow passage 10a causes a change in the airflow direction after passing through the guide vane 31, thereby adjusting the relative angle between the airflow direction and the upstream windward end of the blade 22 along the airflow direction. This suppresses the tendency for airflow separation near the windward end, thus improving the operational stability of the centrifugal compressor.

[0040] Understandably, during the rotation of the impeller 20, the linear velocity of the end of the blade 22 that is radially away from the axis of rotation of the impeller 21 is the greatest, making it more prone to airflow separation. Therefore, the mounting cavity 10b is located upstream of the airflow direction at the end of the blade 22 that is radially away from the axis of rotation of the impeller 21, so that the guide vane 31 can more easily adjust the airflow direction passing through the end of the blade 22 that is radially away from the axis of rotation of the impeller 21, thereby suppressing the occurrence of airflow separation.

[0041] It is understood that the housing 10 has an air inlet 10e along the circumference of the impeller 20. Therefore, the end of the blade 22 that is radially away from the axis of rotation of the impeller 21 is located at the end of the airflow channel 10a near the air inlet 10e. The windward end is the end of the blade 22 that is radially away from the axis of rotation of the impeller 21.

[0042] With the guide vane 31 retracted, it is completely contained within the mounting cavity 10b. This reduces airflow energy loss due to obstruction by the guide vane 31 under conditions of high airflow, thereby improving the operating efficiency of the centrifugal compressor.

[0043] In this embodiment of the invention, the centrifugal compressor uses guide vanes 31 to adjust the airflow direction of the blades 22, thereby reducing the probability of airflow separation at the windward end of the blades 22 and improving the operational stability of the centrifugal compressor. By switching the extended and retracted states of the guide vanes 31 under different operating conditions, on the one hand, under low airflow conditions, the guide vanes 31 can reduce the probability of airflow separation at the windward end of the blades 22; on the other hand, under high airflow conditions, the obstruction effect of the guide vanes 31 on the airflow is reduced, thus reducing the kinetic energy loss of the airflow. This results in a wider stable operating speed range for the centrifugal compressor in this embodiment of the invention, improving its operational efficiency.

[0044] It is understandable that the guide vane assembly 30 includes several guide vanes 31, and the specific number of guide vanes 31 is not limited.

[0045] For example, the number of guide vanes 31 is the same as the number of blades 22. This ensures a one-to-one correspondence between each guide vane 31 and each blade 22, so that each blade 22 has a corresponding guide vane 31 to guide the airflow at its windward end, thereby further improving the working stability and efficiency of the centrifugal compressor.

[0046] It is understandable that several guide vanes 31 are spaced apart circumferentially.

[0047] It is understandable that the guide vane 31 is a thin-plate structure, with its thickness direction roughly perpendicular to the airflow direction. On the one hand, the side of the guide vane 31 obstructs the airflow, thus deflecting its direction; on the other hand, it reduces the kinetic energy loss caused by the guide vane 31 cutting through the airflow.

[0048] In some embodiments, both the windward end of the blade 22 and the guide vane 31 extend radially.

[0049] Understandably, as the impeller 20 rotates, the orientation of the windward end of each blade 22 changes periodically. Therefore, the position of the guide vane 31 needs to be selectively adjusted to adapt to the changes in the windward orientation.

[0050] For example, the guide vane 31 is rotatable, and its rotation direction is perpendicular to its extension direction. By rotating the guide vane 31, the relative angle between the guide vane 31 and the windward end of the blade 22 is kept within a certain range, thereby more effectively suppressing the tendency of airflow separation at the windward end of the blade 22.

[0051] Understandably, the rotation angle of each guide vane 31 can be controlled independently. During the operation of the impeller 20, the current angle of each guide vane 31 is determined based on the required airflow rate and the rotational speed of the impeller 20.

[0052] It is understandable that the specific shape of the mounting cavity 10b is not limited.

[0053] For example, the projection of the mounting cavity 10b along the extension and retraction direction of the guide vane 31 has the same shape as the projection of the guide vane 31, so that the guide vane 31 can only rotate after it has fully extended out of the mounting cavity 10b. This reduces the distance between the inner wall of the mounting cavity 10b and the guide vane 31, thereby reducing the volume of the mounting cavity 10b, lowering the probability of airflow entering the mounting cavity 10b and generating turbulence, and reducing noise.

[0054] For example, the projection of the mounting cavity 10b along the extension and retraction direction of the guide vane 31 is circular. This allows the guide vane 31 to rotate even when partially located within the mounting cavity 10b, thereby enabling the adjustment of the size of the portion of the guide vane 31 extending out of the mounting cavity 10b according to the airflow velocity. Simultaneously, the rotation of the guide vane 31 adjusts the airflow direction to adapt to the orientation of the windward end, improving the adjustment capability of the guide vane 31 and further expanding the stable operating speed range of the centrifugal compressor.

[0055] Understandably, the cross-sectional area of ​​the airflow channel 10a perpendicular to the airflow direction gradually decreases at least partially along the airflow direction in order to pressurize the gas.

[0056] In some embodiments, see Figure 1 The airflow channel 10a includes an inlet section 10c and an impeller section 10d connected sequentially along the airflow direction. An impeller 20 is disposed within the impeller section 10d. The outlet of the inlet section 10c is connected to the inlet of the impeller section 10d. The cross-sectional area of ​​the impeller section 10d perpendicular to the airflow direction gradually decreases along the airflow direction. The impeller 20 rotates within the impeller section 10d, causing the airflow from the inlet section 10c to form a high-speed airflow within the impeller section 10d. Simultaneously, due to the gradually decreasing cross-sectional area of ​​the impeller section 10d, the distance between gas molecules in the high-speed airflow decreases, thereby achieving pressurization.

[0057] In some embodiments, see Figure 1 The mounting cavity 10b is located at the outlet position of the air inlet section 10c. This reduces the distance between the guide vane 31 and the windward end, allowing the airflow, after being directionally adjusted by the guide vane 31, to quickly contact the windward end, further reducing the probability of airflow separation at the windward end of the blade 22.

[0058] Understandably, the size of the guide vane 31 determines the magnitude of the total frictional force between the airflow and the guide vane 31, which has a significant impact on the energy loss of the airflow.

[0059] In some embodiments, when the guide vane 31 is extended, the end of the guide vane 31 away from the mounting cavity 10b is spaced apart from the inner wall of the airflow channel 10a. On the one hand, this avoids friction between the guide vane 31 and the inner wall of the airflow channel 10a, which could damage the guide vane 31; on the other hand, it reduces the airflow in contact with the guide vane 31, thereby reducing the kinetic energy loss of the airflow.

[0060] In some embodiments, see Figure 2With the guide vane 31 extended, the maximum radial dimension of the portion of the guide vane 31 extending out of the mounting cavity 10b in the axial projection is h, and the maximum radial dimension of the projection of the tip of the blade along the airflow direction is H, where h ≤ 1 / 4H. This further reduces the airflow in contact with the guide vane 31, thereby reducing frictional energy loss between the airflow and the guide vane 31 and lowering the kinetic energy loss of the airflow.

[0061] In some embodiments, see Figure 3 With the guide vane 31 extended, the minimum distance between the end of the guide vane 31 along the airflow direction and the beginning of the blade 22 along the airflow direction within its projection range is L1, and the dimension of the guide vane 31 along the airflow direction is L2, where L1 ≤ L2. This allows the guide vane 31 to be as close as possible to the blade 22, enabling the airflow guided by the guide vane 31 to quickly contact the blade 22 and improve the guiding effect.

[0062] It is understandable that the radial end of the blade 22 is in contact with the disk 21, while the other end is suspended. Since the linear velocity of the suspended end of the blade 22 is greater, the airflow near the suspended end is more likely to separate than the airflow near the end in contact with the disk 21.

[0063] In some embodiments, see Figure 2 and Figure 3 The mounting cavity 10b is located on the side of the airflow channel 10a that is radially away from the wheel 21. This is so that when the guide vane 31 is extended, the guide vane 31 is closer to the end of the windward side that is radially away from the wheel 21, thereby better reducing the probability of airflow separation near the end of the windward side that is radially away from the wheel 21.

[0064] Understandably, the dimensions of the portion of the guide vane 31 extending out of the mounting cavity 10b can be adjusted according to the actual operating conditions to enable the centrifugal compressor to have a wider range of stable operating speeds.

[0065] It is understandable that the blade 22 is spaced apart from the inner wall of the airflow channel 10a.

[0066] Understandably, the size of the portion of the guide vane 31 extending out of the mounting cavity 10b should be adapted to the position of the edge of the windward end.

[0067] Specifically, see Figure 2 and Figure 3With the guide vane 31 extended, in the projection along the airflow direction, the projection of the edge of the windward end of the blade 22 away from the wheel 21 is located within the projection range of the portion of the guide vane 31 extending out of the mounting cavity 10b. This ensures that, with the guide vane 31 extended, the airflow, after being directionally adjusted by the guide vane 31, can continue flowing and contact the edge of the windward end away from the wheel 21. This allows the guide vane 31 to adjust the airflow direction near the edge of the windward end away from the wheel 21, improving the airflow regulation efficiency of the guide vane 31 and reducing the probability of airflow separation at the edge of the windward end away from the wheel 21.

[0068] The specific method for switching the guide vane 31 between the extended and retracted states is not limited.

[0069] In some embodiments, see Figure 1 The guide vane assembly 30 includes a spring 32 and an electromagnet 33. The spring 32 is connected between the housing 10 and the guide vane 31. The electromagnet 33 is disposed on the housing 10. The electromagnet 33 can be selectively energized to generate a magnetic force on the guide vane 31. Under the force applied by the electromagnet 33 and the spring 32, the guide vane 31 switches between an extended state and a retracted state. Thus, by selecting the timing and current intensity of energizing the electromagnet 33, the switching between the extended and retracted states of the guide vane 31 and the size of the portion of the guide vane 31 extending out of the mounting cavity 10b can be controlled.

[0070] It is understandable that the type of magnetic force generated between the energized electromagnet 33 and the guide vane 31 is not limited.

[0071] For example, the guide vane 31 is made of a magnetic material. The energized electromagnet 33 generates a magnetic attraction between itself and the guide vane 31. The electromagnet 33 is located on the side of the guide vane 31 away from the mounting cavity 10b. When the guide vane 31 is in the extended state, the electromagnet 33 is energized and the spring 32 applies a pulling force to the guide vane 31 in the direction of the mounting cavity 10b.

[0072] For example, the guide vane 31 is made of a magnetic material. The energized electromagnet 33 generates a magnetic repulsion force between itself and the guide vane 31. The electromagnet 33 is located on the side of the guide vane 31 closer to the mounting cavity 10b. When the guide vane 31 is in the extended state, the electromagnet 33 is energized and the spring 32 applies a pulling force to the guide vane 31 in the direction of the mounting cavity 10b.

[0073] For example, the guide vane 31 is made of iron-based material. The energized electromagnet 33 generates a magnetic attraction between itself and the guide vane 31. The electromagnet 33 is located on the side of the guide vane 31 away from the mounting cavity 10b. When the guide vane 31 is in the extended state, the electromagnet 33 is energized and the spring 32 applies a pulling force to the guide vane 31 in the direction of the mounting cavity 10b.

[0074] It is understandable that the specific location of spring 32 is not limited.

[0075] In some embodiments, see Figure 1 The spring 32 is disposed in the mounting cavity 10b. This avoids the spring 32 occupying the space in the airflow channel 10a, and also avoids the spring 32 directly blocking the flow of air and causing loss of kinetic energy of the airflow, thereby reducing the probability of turbulence and noise caused by the spring 32.

[0076] Understandably, it is necessary to constrain the extension and retraction direction of the guide vane 31 in order to reduce the probability of jamming during the switching process between the extended and retracted states.

[0077] In some embodiments, see Figure 1 The guide vane assembly 30 includes a telescopic rod 34. A mounting hole 10g is provided on the inner wall of the mounting cavity 10b, through which the telescopic rod 34 passes. One end of a spring 32 is connected to the guide vane 31, and the other end of the spring 32 is connected to the inner wall of the mounting cavity 10b. The constraint of the telescopic rod 34 by the inner wall of the mounting hole 10g guides the movement direction of the guide vane 31, avoiding direct guidance of the telescopic movement of the guide vane 31 through the inner wall of the mounting cavity 10b, and reducing the probability of friction between the guide vane 31 and the inner wall of the mounting cavity 10b during telescopic movement.

[0078] It is understandable that the extension direction of the mounting hole 10g and the telescopic rod 34 is the same as the extension direction of the guide vane 31.

[0079] In some embodiments, see Figure 3 The mounting hole 10g penetrates the inner wall of the airflow channel 10a, allowing a portion of the telescopic rod 34 to extend to the outside of the housing 10. This enables the telescopic rod 34 to have a larger extension stroke, thereby facilitating the guide vane 31 to better adjust the airflow direction under different operating conditions and further expanding the stable operating speed range of the centrifugal compressor.

[0080] In some embodiments, see Figure 1 The telescopic rod 34 passes through the inner coil of the spring 32. The telescopic rod 34 limits the movement of the spring 32, reducing the probability of the spring 32 twisting and deforming during stretching and compression.

[0081] It is understandable that the magnetic force generated by electromagnet 33 can penetrate a medium of a certain thickness. Therefore, the specific installation position of electromagnet 33 can be optimized according to the actual assembly and maintenance needs.

[0082] In some embodiments, see Figure 3The electromagnet 33 is located on the outer surface of the housing 10. On the one hand, the magnetic force generated by the electromagnet 33 can penetrate the housing 10 and exert an effect on the guide vane 31; on the other hand, during subsequent maintenance, the operator can maintain or replace the electromagnet 33 without disassembling the housing 10, thus improving work efficiency.

[0083] In some embodiments, see Figure 1 and Figure 3 The electromagnet 33 is located on the side opposite to the mounting cavity 10b. This reduces the distance between the electromagnet 33 and the guide vane 31, making it easier for the magnetic force generated by the electromagnet 33 to effectively act on the guide vane 31.

[0084] It is understandable that the materials used in the housing 10 and impeller 20 do not interact with the magnetic force generated by the electromagnet 33. For example, both the housing 10 and impeller 20 are made of aluminum alloy.

[0085] This invention also provides a turbocharger, which includes the centrifugal compressor described in any of the foregoing embodiments.

[0086] This invention also provides a vehicle, which includes an engine and the turbocharger described in the foregoing embodiments. The turbocharger's boost outlet 10f is connected to the engine's airflow inlet. Gas pressurized by the centrifugal compressor is discharged through the boost outlet 10f and enters the combustion chamber through the engine's airflow inlet. The gas mixes with fuel and is ignited, thus enabling the engine to perform work. The boosted gas output by the turbocharger effectively increases the engine's maximum output power, improves torque output at low speeds, and reduces fuel consumption.

[0087] The various embodiments / implementations provided in this application can be combined with each other without creating contradictions.

[0088] The above description is merely a preferred embodiment of this application and is not intended to limit the application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the scope of protection of this application.

Claims

1. A centrifugal compressor, characterized in that, include: An impeller includes a disk and a plurality of blades, the blades being disposed on one radial side of the disk and extending radially; The housing has an airflow channel, the impeller is rotatably disposed in the airflow channel, the housing has an air inlet along the circumference of the impeller, the housing has an air outlet along the radial direction of the impeller, and the air outlet is located on the side of the impeller where the blades are disposed, and the airflow channel connects the air inlet and the air outlet; A guide vane assembly is disposed on the housing. The guide vane assembly includes a guide vane. The airflow channel is provided with an installation cavity on the inner wall of the impeller upstream along the airflow direction. The installation cavity is open to communicate with the airflow channel. The guide vane is retractably disposed in the installation cavity. In the extended state of the guide vane, at least a portion of the guide vane is located in the airflow channel. The guide vane is rotatable, and its rotation direction is perpendicular to its extension direction. The rotation angle of the guide vane can be controlled independently. In the retracted state of the guide vane, the guide vane is completely located in the mounting cavity. The projection of the mounting cavity along the extension and retraction direction of the guide vane has the same shape as the projection of the guide vane, so that the guide vane can only rotate after it is fully extended out of the mounting cavity; or, the projection of the mounting cavity along the extension and retraction direction of the guide vane is circular, so that the guide vane can still rotate even when part of it is located inside the mounting cavity.

2. The centrifugal compressor according to claim 1, characterized in that, The airflow channel includes an air inlet section and an impeller section connected sequentially along the airflow direction. The impeller is located in the impeller section. The outlet of the air inlet section is connected to the inlet of the impeller section. The mounting cavity is located at the outlet of the air inlet section.

3. The centrifugal compressor according to claim 2, characterized in that, In the extended state of the guide vane, the maximum radial dimension of the projection of the portion of the guide vane extending out of the mounting cavity along the axial direction is h, and the maximum radial dimension of the projection of the tip of the blade along the airflow direction is H, where h ≤ 1 / 4H.

4. The centrifugal compressor according to claim 1, characterized in that, In the extended state of the guide vane, the minimum distance between the end of the guide vane along the airflow direction and the beginning of the blade along the airflow direction within its projection range along the airflow direction is L1, and the dimension of the guide vane along the airflow direction is L2, where L1≤L2.

5. The centrifugal compressor according to claim 1, characterized in that, The mounting cavity is located on the side of the airflow channel that is radially away from the wheel.

6. The centrifugal compressor according to claim 5, characterized in that, In the extended state of the guide vane, in the axial projection, the projection of the edge of the windward end of the vane on the side away from the wheel disk is located within the projection range of the portion of the guide vane extending out of the mounting cavity.

7. The centrifugal compressor according to claim 1, characterized in that, The guide vane assembly includes a spring and an electromagnet. The spring is connected between the housing and the guide vane, and the electromagnet is disposed on the housing. The electromagnet can be selectively energized to generate a magnetic force on the guide vane. Under the force applied by the electromagnet and the spring, the guide vane switches between an extended state and a retracted state.

8. The centrifugal compressor according to claim 7, characterized in that, The guide vane assembly includes a telescopic rod, and the inner wall of the mounting cavity is provided with a mounting hole. The telescopic rod passes through the mounting hole. One end of the spring is connected to the guide vane, and the other end of the spring is connected to the inner wall of the mounting cavity.

9. The centrifugal compressor according to claim 7, characterized in that, The electromagnet is located on the outer surface of the housing and on the side opposite to the mounting cavity.

10. A turbocharger, characterized in that, The turbocharger includes the centrifugal compressor of any one of claims 1-9.

11. A vehicle, characterized in that, The vehicle includes an engine and a turbocharger as described in claim 10, wherein the turbocharger's boost outlet is connected to the engine's airflow inlet.

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