Diffuser and compressor with adjustable vanes

Abstract

The present invention relates to a diffuser with adjustable vanes and a compressor, the diffuser comprising: a first diffuser part engaging a pressure shell; a second diffuser part engaging a back plate; and a vane, the vane comprising a first and a second vane part, the first vane part being fixed to the first and / or second diffuser part, while the second vane part is freely extending radially outward from the first vane part, such that the vane is elastically deformable between a first state and a second state, wherein in the first state the vane remains in an undeformed initial state, while in the second state the second vane part is at least partially deflected away from or towards the impeller, and wherein the vane elastically deforms from the first state to the second state with an increase of the air flow pressure acting on the vane. Such a diffuser enables a significant increase of the compressor surge margin and an increase of the efficiency in the choked flow regime section, reduces the product cost and increases the product reliability.

Description

Technical Field

[0001] This invention relates to a diffuser with adjustable blades. Additionally, this invention also relates to a compressor. Background Technology

[0002] Currently, in existing compressor technologies, such as centrifugal compressors, vaned diffusers (VDs), such as straight-blade and curved-blade diffusers, can be incorporated to assist in converting kinetic energy into pressure energy. Such compressors with vaned diffusers may encounter several problems during operation. For example, the surge margin of such compressors is significantly reduced. Additionally, there is a significant efficiency loss during the choke point phase of such compressors.

[0003] While the use of adjustable blade diffusers (VD) can significantly alleviate the above problems, it requires extremely complex logic control devices and actuation mechanisms, which will significantly increase product costs and is not conducive to improving market competitiveness.

[0004] Therefore, there is a need to improve existing diffusers and compressors in order to provide an improved diffuser and compressor that overcomes one or more of the disadvantages present in the prior art. Summary of the Invention

[0005] The inventors discovered that the reduced surge margin and efficiency loss during choke conditions in compressors are related to the diffuser blade structure. For example, existing blade diffusers have a fixed angle and a narrow operating range. When the compressor flow rate is lower than the design value, the fixed-angle blades restrict fluid discharge, causing fluid stagnation, backflow, or flow separation within the blade channels. Blade diffusers have poor adaptability to changes in operating conditions; once they deviate from the design point, the energy conversion efficiency of the fluid between the impeller and diffuser decreases, the stable operating range is rapidly compressed, and the surge margin is significantly reduced.

[0006] Furthermore, when the compressor flow rate is too high, fluid blockage can lead to throttling and friction losses. Also, because the fluid directly impacts the blade surface, kinetic energy is wasted instead of being converted into the pressure energy required by the compressor, resulting in energy waste. This significantly reduces the efficiency of kinetic energy conversion to pressure energy, leading to a substantial loss in the overall efficiency of the compressor.

[0007] Therefore, the present invention provides a diffuser with adjustable blades. According to a first aspect of the invention, a diffuser with adjustable blades is provided, which can be disposed radially outside the impeller of a compressor, and may include: a first diffuser portion engaging a compressor housing; a second diffuser portion disposed opposite to the first diffuser portion and engaging a compressor backplate; and blades comprising a first blade portion and a second blade portion, wherein the first blade portion is fixed to the first diffuser portion and / or the second diffuser portion, and the second blade portion extends freely radially outward from the first blade portion, such that the blade is elastically deformable between a first state and a second state, wherein in the first state the blade remains in an undeformed initial state, and in the second state the second blade portion deflects at least partially away from or towards the impeller, and wherein the blade elastically deforms from the first state to the second state as the airflow pressure acting on the blade increases.

[0008] This diffuser significantly improves compressor surge margin and increases efficiency in choke conditions. Furthermore, it adaptively adjusts based on airflow pressure—a passive adjustment based on compressed airflow—eliminating the need for complex control logic and separate actuation mechanisms, thus reducing product cost and improving reliability.

[0009] According to the above aspects of the present invention, preferably, the blade can be made of spring steel, and the elastic modulus of the spring steel can be between 180 GPa and 215 GPa.

[0010] The blade achieves high toughness through the use of spring steel, and also enables it to maintain high fatigue resistance even under extreme high temperatures, such as around 250 degrees Celsius, at the compressor end of a turbocharger.

[0011] According to the above aspects of the present invention, preferably, the ratio between the first length of the first blade portion and the second length of the second blade portion can be between 0.15 and 0.30.

[0012] This blade configuration allows for greater variability and range of the diffuser, thus adapting to a wider range of pressures.

[0013] According to the above aspects of the present invention, preferably, the first axial height of the first blade portion can be greater than the second axial height of the second blade portion.

[0014] In this way, there is a predetermined gap on both sides of the second blade section in the axial direction, so that when the second blade section undergoes elastic deformation, it can pivot freely between the pressure shell and the back plate without collision or friction, which further improves the reliability of the product.

[0015] According to the above aspects of the present invention, preferably, the thickness of the blade can decrease from the first blade portion toward the second blade portion.

[0016] In this way, while ensuring the attachment strength of the blades, the blades are allowed to have a sufficient range of deformation, so as to better adapt to changes in the output pressure of the compressor.

[0017] According to the above aspects of the invention, preferably, the ratio of the first maximum thickness of the first blade portion to the second minimum thickness of the second blade portion is between 2.5 and 3.2. The inventors have found that this thickness setting enables better elastic deformation and achieves a balance between improving compressor surge margin and increasing efficiency in the choke point operating section.

[0018] Preferably, the second blade portion may also include a free end, and the thickness of the free end tapers toward the end, for example, the free end may taper to a thickness close to zero.

[0019] According to the above aspects of the present invention, preferably, the first diffuser portion and the second diffuser portion may each have an annular body, wherein the first blade portion is fixed to the annular body and is equidistantly spaced along the circumferential direction.

[0020] This setup allows the diffuser to be manufactured and installed into the compressor more easily, reducing costs while enhancing product reliability.

[0021] According to the above aspects of the present invention, preferably, an arc-shaped transition portion may be provided at the attachment portion between the first blade portion and the annular body.

[0022] This arrangement can reduce the stress level experienced by the blades during frequent deformation, thereby improving the product's service life.

[0023] According to a second aspect of the present invention, a compressor is provided, which may include: a diffuser as described in the first aspect; an impeller disposed radially inside the diffuser; a pressure shell having a first mounting groove; and a back plate opposite to the pressure shell and having a second mounting groove, wherein a first diffuser portion and a second diffuser portion of the diffuser are respectively mounted in the first mounting groove and the second mounting groove.

[0024] This configuration allows for a significant increase in compressor surge margin and efficiency during choke conditions. Additionally, the mounting slot allows for more reliable radial and axial mounting of the diffuser.

[0025] According to the above aspects of the present invention, preferably, the compressor may further include: a first locking portion, which may be disposed at at least one of a first mounting groove and a second mounting groove; and a second locking portion, which may be disposed at at least one of a first diffuser portion and a second diffuser portion, wherein the first locking portion may cooperate with the second locking portion to prevent circumferential movement of the diffuser.

[0026] This design reliably holds the diffuser in place, allowing the blades to deform accordingly under different pressures to accommodate airflow impacts at varying angles. Furthermore, this structure facilitates manufacturing and installation, further improving production efficiency while ensuring product reliability.

[0027] Therefore, the diffuser with adjustable blades of the present invention can meet the usage requirements, overcome the shortcomings of the prior art, and achieve the intended purpose. Attached Figure Description

[0028] To further illustrate the present invention, the diffuser with adjustable blades according to the present invention will be described in detail below with reference to the accompanying drawings and specific embodiments, in which:

[0029] Figure 1 This is a schematic cross-sectional perspective view of a compressor according to a non-limiting embodiment of the present invention;

[0030] Figure 2 yes Figure 1 A schematic cross-sectional view of a portion of the compressor shown;

[0031] Figure 3 This is a schematic perspective view of a diffuser according to a non-limiting embodiment of the present invention;

[0032] Figure 4 This is a schematic top view of a diffuser according to a non-limiting embodiment of the present invention;

[0033] Figure 5 This is a schematic enlarged view of a portion of a diffuser according to a non-limiting embodiment of the present invention;

[0034] Figure 6 This is a top view of a portion of a diffuser according to a non-limiting embodiment of the present invention;

[0035] Figure 7 This is another schematic enlarged view of a portion of a diffuser according to a non-limiting embodiment of the present invention;

[0036] Figure 8 This is yet another schematic enlarged view of a portion of a diffuser according to a non-limiting embodiment of the present invention;

[0037] Figure 8A This is yet another schematic enlarged view of a portion of a diffuser according to a non-limiting embodiment of the present invention;

[0038] Figure 9 This is a schematic diagram of the compressor housing according to a non-limiting embodiment of the present invention;

[0039] Figure 10 This is a schematic cross-sectional perspective view of a portion of the compressor housing according to a non-limiting embodiment of the present invention;

[0040] Figure 11 This is a schematic diagram of the back panel of a compressor according to a non-limiting embodiment of the present invention;

[0041] Figure 12 This is a schematic cross-sectional perspective view of a portion of the back panel of a compressor according to a non-limiting embodiment of the present invention;

[0042] Figure 13 The stress level of the diffuser blades under surge conditions is shown according to a non-limiting embodiment of the invention;

[0043] Figure 14 The stress level of the diffuser blades under choked conditions is shown according to a non-limiting embodiment of the invention;

[0044] Figure 15 A schematic diagram of the deformation of a diffuser blade under surge conditions is shown according to a non-limiting embodiment of the present invention;

[0045] Figure 16 A schematic diagram of the deformation of diffuser blades under choke conditions is shown according to a non-limiting embodiment of the present invention;

[0046] Figure 17 A schematic operating state of a diffuser according to a non-limiting embodiment of the present invention under surge conditions is shown;

[0047] Figure 18 A schematic operating state of a diffuser according to a non-limiting embodiment of the present invention under a blocked condition is shown;

[0048] Figure 19 A schematic aerodynamic performance comparison is shown between a diffuser according to a non-limiting embodiment of the present invention and prior art fixed-blade diffusers and bladeless diffusers.

[0049] The above figures are for illustrative purposes only and are not drawn to scale.

[0050] The reference numerals in the figures are listed in the figures and embodiments:

[0051] 1000 - Compressor, including:

[0052] 100 - Diffuser, including:

[0053] 10 – First diffuser section;

[0054] 20 – Second diffuser section;

[0055] 30 - Blades, including:

[0056] 31 – First blade section;

[0057] 31A – First end;

[0058] 32 – Second blade section;

[0059] 32A – Second terminal;

[0060] 33 – Transition section;

[0061] 40 - First locking part;

[0062] 50 - Second locking part;

[0063] α – First angle;

[0064] L1 – First length;

[0065] L2 – Second length;

[0066] H1 – First axial height;

[0067] H2 – Second axial height;

[0068] T1 – First maximum thickness;

[0069] T2 – Second minimum thickness;

[0070] 200 - Impeller;

[0071] 300 - Pressure shell, including:

[0072] 310 – First mounting slot;

[0073] 400 - Back panel, including:

[0074] 410 - Second mounting slot. Detailed Implementation

[0075] It should be understood that, unless explicitly stated otherwise, the invention may take various alternative orientations and sequences of steps. It should also be understood that the specific apparatus shown in the drawings and described in the specification are merely exemplary embodiments of the inventive concept disclosed and defined herein. Therefore, unless expressly stated otherwise, the specific orientations, directions, or other features involved in the various disclosed embodiments should not be considered limiting.

[0076] Figure 1 This is a schematic cross-sectional perspective view of a compressor 1000 according to a non-limiting embodiment of the present invention; and Figure 2 yes Figure 1 A schematic cross-sectional view of a portion of the compressor 1000 shown.

[0077] As shown in the figure and as a non-limiting example, the compressor 1000 can be a turbocharged compressor or a centrifugal compressor. In this embodiment of the invention, the compressor 1000 may mainly include: a diffuser 100, an impeller 200, a pressure casing 300, and a back plate 400, etc. The structure and arrangement of the remaining components of the compressor 1000 can be similar to the structure and arrangement of a centrifugal compressor in the prior art, and for the sake of simplicity, the invention will not describe them in detail.

[0078] In the embodiments shown in conjunction with the accompanying drawings, the diffuser 100 may be a bladed diffuser and may be disposed radially outward of the impeller 200 of the compressor 1000. Correspondingly, the impeller 200 may be disposed radially inward of the diffuser 100.

[0079] As described in more detail below with reference to the accompanying drawings, the diffuser 100 may mainly include a first diffuser section 10, a second diffuser section 20, and blades 30.

[0080] Figure 3 This is a schematic perspective view of a diffuser 100 according to a non-limiting embodiment of the present invention; Figure 4 This is a schematic top view of a diffuser 100 according to a non-limiting embodiment of the present invention; and Figure 5 This is a schematic enlarged view of a portion of a diffuser 100 according to a non-limiting embodiment of the present invention.

[0081] As shown in the figure, the first diffuser portion 10 and the second diffuser portion 20 may each have an annular body. The second diffuser portion 20 and the first diffuser portion 10 may be arranged opposite each other, for example, spaced apart along the axial direction.

[0082] The first diffuser section 10 and the second diffuser section 20 may be made of metallic materials, such as spring steel.

[0083] A plurality of blades 30 may be arranged between the first diffuser portion 10 and the second diffuser portion 20. According to an embodiment of the present invention, the blades 30 may include a first blade portion 31 and a second blade portion 32, and the first blade portion 31 may be fixed to the first diffuser portion 10 and the second diffuser portion 20, such as... Figure 3 and Figure 5 This is shown more clearly in the text.

[0084] Preferably, the first blade portion 31 is fixed to the annular body and spaced equidistantly along the circumferential direction. Additionally, preferably, an arc-shaped transition portion 33 may be provided at the attachment point between the first blade portion 31 and the annular body.

[0085] In a preferred embodiment, the blade 30 can be made of spring steel, and the elastic modulus of the spring steel is between 180 GPa and 215 GPa. In this case, the first blade portion 31 and the second blade portion 32 can be integrally formed.

[0086] The blade 30 can be welded to the first diffuser portion 10 and the second diffuser portion 20, or the blade 30 can be integrally formed with the first diffuser portion 10 and the second diffuser portion 20, for example, by first molding and then performing corresponding machining.

[0087] In another embodiment, the blade 30 may be made of a copper-beryllium alloy or a high-temperature resistant composite material, and may be able to withstand temperatures above 250 degrees Celsius. For example, an example of a high-temperature resistant composite material may be carbon fiber material coated with a heat-resistant material or a heat-resistant coating.

[0088] In an alternative embodiment not shown, the first blade portion 31 may be fixed only to the first diffuser portion 10, or it may be fixed only to the second diffuser portion 20.

[0089] Figure 6 This is a top view of a portion of a diffuser 100 according to a non-limiting embodiment of the present invention.

[0090] like Figure 6 As schematically shown, the blade 30 may extend between a first end 31A and a second end 32A. The first blade portion 31 may have a first length L1 measured from the first end 31A, and the second blade portion 32 may have a second length L2 measured from the second end 32A. The first length L1 may be the length of the portion fixed to the first diffuser portion 10 and the second diffuser portion 20, while the second length L2 may be the length of the unfixed blade 30, for example, a length that can be freely bent or deformed.

[0091] As an example, the first length L1 and the second length L2 can be actual lengths measured along the profile of the blade 30, for example, along the approximate curvature of the blade 30. Preferably, the ratio between the first length L1 and the second length L2 can be between 0.15 and 0.30.

[0092] In addition, as in the same way Figure 6As shown, the thickness of the blade 30 can vary along its length. For example, the thickness of the blade 30 can decrease from the first blade portion 31 toward the second blade portion 32. Preferably, the thickness of the blade 30 can decrease smoothly from the first blade portion 31 toward the second blade portion 32.

[0093] Preferably, the ratio of the first maximum thickness T1 of the first blade portion 31 to the second minimum thickness T2 of the second blade portion 32 is between 2.5 and 3.2. It should be understood that the second minimum thickness T2 of the second blade portion 32 is the thickness of the blade not measured at the free end or the second end 32A, and therefore, the second minimum thickness T2 is a positive value that is not zero.

[0094] Figure 7 This is another schematic enlarged view of a portion of a diffuser 100 according to a non-limiting embodiment of the present invention; and Figure 8 and Figure 8A This is a further schematic enlarged view of a portion of the diffuser 100 according to a non-limiting embodiment of the present invention.

[0095] As shown in the figure and in a preferred embodiment, the first blade portion 31 may have a first axial height H1, while the second blade portion 32 may have a second axial height H2, and the first axial height H1 may be greater than the second axial height H2. In other words, a step may exist at the transition between the first blade portion 31 and the second blade portion 32, particularly with steps on both sides along the axial direction. Preferably, the step may smoothly transition between the first blade portion 31 and the second blade portion 32 to reduce stress concentration generated during elastic deformation of the blade 30, thereby improving the product's service life and reliability.

[0096] In addition, such as Figure 8 As shown in more detail, the first end 31A of the first blade portion 31 may have a smooth profile to better guide the airflow.

[0097] Figure 9 This is a schematic diagram of the pressure casing 300 of a compressor 1000 according to a non-limiting embodiment of the present invention; and Figure 10 This is a schematic cross-sectional perspective view of a portion of the housing 300 of a compressor 1000 according to a non-limiting embodiment of the present invention.

[0098] As shown in the figure, the pressure shell 300 may be provided with a first mounting groove 310, which may extend circumferentially, for example, provided at the shoulder of the pressure shell 300 and may be formed as a circular groove.

[0099] Figure 11 This is a schematic diagram of the back plate 400 of a compressor 1000 according to a non-limiting embodiment of the present invention; and Figure 12 This is a schematic cross-sectional perspective view of a portion of the back panel 400 of a compressor 1000 according to a non-limiting embodiment of the present invention.

[0100] As shown in the figure, the back plate 400 may be provided with a second mounting groove 410, which may extend circumferentially to form a circular recess. When installed on the compressor 1000, the back plate 400 may be opposite to the compressor housing 300, and the first mounting groove 310 and the second mounting groove 410 may be axially aligned. At this time, the first diffuser portion 10 and the second diffuser portion 20 of the diffuser 100 may be respectively installed in the first mounting groove 310 and the second mounting groove 410.

[0101] In a preferred embodiment, the first mounting groove 310 and the second mounting groove 410 may be provided with draft angles to facilitate molding and assembly operations. For example, draft angles of 5° or 10° may be provided on the radial inner surface and radial outer surface of the groove wall of the first mounting groove 310 and the second mounting groove 410, respectively, to balance processing feasibility and assembly accuracy.

[0102] In addition, such as Figure 12 As can be seen more clearly, the second mounting groove 410 may be provided with a first locking portion 40. This first locking portion 40 may be formed as a recess and may communicate with the second mounting groove 410. Accordingly, and referring to... Figure 3 and Figure 4 The second diffuser portion 20 may be provided with a second locking portion 50. The second locking portion 50 may be in the form of a protrusion, and the first locking portion 40 may cooperate with the second locking portion 50 to prevent the diffuser 100 from moving circumferentially.

[0103] Alternatively, the first locking part 40 may be provided on the first mounting groove 310, and the second locking part 50 may be provided on the first diffuser part 10.

[0104] Furthermore, although the first locking portion 40 and the second locking portion 50 are depicted in the form of recesses and protrusions in the accompanying drawings to facilitate manufacturing and assembly, those skilled in the art can also conceive of other types of locking structures, as long as the two can cooperate with each other to achieve the desired circumferential blocking function.

[0105] In this way, the first diffuser portion 10 can engage with the compressor housing 300, while the second diffuser portion 20 can engage with the compressor back plate 400, and the second blade portion 32 extends freely radially outward from the first blade portion 31.

[0106] As the impeller 200 rotates, the airflow pressure experienced by the blades 30 gradually increases with the increase in rotational speed, causing the second blade portion 32 to deflect at least partially away from or towards the impeller 200. In this way, the blades 30 can elastically deform between the first and second states.

[0107] It is understandable that the specific deflection direction of the second blade section 32 (away from or close to the impeller 200) depends on the magnitude and distribution characteristics of the airflow pressure it bears, which in turn determines whether the second blade section 32 functions as a lifting surface or a suction surface.

[0108] According to an embodiment of the present invention, the first state may refer to the initial state in which the blade 30 remains undeformed, for example, when the impeller 200 is not rotating or the rotation speed is too low to overcome the elastic force of the second blade portion 32.

[0109] As an example, in the first state, the tangent of the first blade portion 31 of the blade 30 and the radial direction can form a first angle α. The setting of the first angle α can depend on the arrangement of the impeller 200 and related structures. Preferably, in embodiments of the present invention, the first angle α can be, for example, between 70 and 80 degrees, and more preferably 74 degrees.

[0110] Accordingly, the second state can refer to the state in which the second blade portion 32 is at least partially deflected and deformed. Therefore, the blade 30 according to the invention can elastically deform from the first state to the second state as the airflow pressure acting on the blade 30 increases.

[0111] According to an embodiment of the invention, this deflection deformation of the second blade portion 32 in the second state can be a deflection deformation in two different directions. For example, under the surge condition of the compressor 1000, the second blade portion 32 can deflect towards the impeller 200, particularly its second end 32A and the portion theren. Conversely, under the blockage condition of the compressor 1000, the second blade portion 32 can deflect away from the impeller 200, particularly its second end 32A and the portion theren.

[0112] Figure 13 The stress level of the blade 30 of the diffuser 100 according to a non-limiting embodiment of the present invention under surge conditions is shown; Figure 14 The stress level of the blade 30 of the diffuser 100 according to a non-limiting embodiment of the present invention under choke conditions is shown. Figure 15 A schematic diagram of the deformation of the blade 30 of the diffuser 100 according to a non-limiting embodiment of the present invention under surge conditions is shown; while Figure 16 A schematic diagram of the deformation of the blade 30 of the diffuser 100 according to a non-limiting embodiment of the present invention under a blocked condition is shown.

[0113] exist Figures 13 to 16 In the diagram, the blade position shown by the line drawing is the position in the first state, at which point the blade 30 is not deformed and is in its initial position. The blade position shown in the rendering is the position in the second state, at which point the blade 30 is at least partially deformed, and the direction of deformation varies depending on the operating state of the compressor 1000.

[0114] exist Figure 13 and Figure 14 The diagram shows the equivalent stress level of blade 30 when it deforms, and the unit is megapascal (MPa). Figure 15 and Figure 16 The equivalent total deformation level of blade 30 when deformation occurs is shown in millimeters (mm).

[0115] like Figure 13 and 15 As shown, compressor 1000 is in surge condition, and the curvature of blade 30 has increased compared to its initial state, that is, in Figure 13 and 15 In the middle, the second end 32A of the second blade portion 32 of the blade 30 deflects downward, that is, deflects closer to the impeller 200.

[0116] At this time, from Figure 13 It can be seen that the stress level is highest at the transition between the first blade portion 31 and the second blade portion 32, reaching approximately 130 MPa. Furthermore, from... Figure 15 As can be seen, the second blade portion 32 of the blade 30 has undergone slight deformation from the position close to the first blade portion 31, and the deformation is the greatest at its free end or second end 32A, and can reach a deformation amount of about 0.8 mm. For example, the deformation amount at the second end 32A can be between 0.69 and 0.78 mm.

[0117] like Figure 14 and 16 As shown, compressor 1000 is in a blocked condition, and the curvature of blade 30 is reduced compared to its initial state, that is, in Figure 13 and 15 In the middle, the free end of the second blade portion 32 of the blade 30 is deflected upward, that is, deflected away from the impeller 200, so that the blade 30 as a whole looks straighter, or even bent in the opposite direction.

[0118] At this time, from Figure 14 It can be seen that, similarly, the stress level is highest at the transition between the first blade portion 31 and the second blade portion 32, and can be approximately 30 MPa. Furthermore, from... Figure 16As can be seen, the second blade portion 32 of the blade 30 has undergone slight deformation from the position near the first blade portion 31, and the deformation is greatest at its free end or second end 32A, and can reach a deformation amount of about 0.17 mm. For example, the deformation amount at the second end 32A can be between 0.15 and 0.17 mm.

[0119] Figure 17 The diagram illustrates a schematic operating state of the diffuser 100 under surge conditions according to a non-limiting embodiment of the present invention; while Figure 18 The diagram illustrates the schematic operating state of the diffuser 100 under blocked conditions according to a non-limiting embodiment of the present invention.

[0120] exist Figure 17 and 18 In the embodiment, the degree of deformation of the blade 30 is related to Figure 15 and 16 Compared to further increases. For example, such as Figure 17 As shown, the second blade portion 32 of the blade 30 has undergone slight deformation from its position near the first blade portion 31, with the greatest deformation occurring at its free end or second end 32A, reaching a deformation of approximately 2.5 mm. For example, the deformation at the second end 32A can be between 2.2 and 2.6 mm. Similarly, from Figure 18 As can be seen, the second blade portion 32 of the blade 30 has undergone slight deformation from the position near the first blade portion 31, and the deformation is the greatest at its free end or second end 32A, and can reach a deformation amount of about 3.2 mm. For example, the deformation amount at the second end 32A can be between 2.8 and 3.3 mm.

[0121] Figure 19 A schematic aerodynamic performance comparison is shown between a diffuser 100 according to a non-limiting embodiment of the present invention and prior art fixed-blade diffusers and bladeless diffusers. Figure 19 In the diagram, the horizontal axis represents mass flow rate, while the vertical axis represents compressor efficiency.

[0122] As shown in the figure, compared with a compressor with a fixed-blade diffuser, the compressor equipped with a diffuser 100 according to an embodiment of the present invention has a leftward shift in its efficiency peak, thereby increasing the surge margin. Furthermore, compared with a compressor without a blade diffuser, the compressor equipped with a diffuser 100 according to an embodiment of the present invention has a smoother and rightward shift in its efficiency curve to the right of the peak value, thereby increasing the efficiency at the choke point.

[0123] The terms “left side” and “right side” used herein to indicate orientation or direction, and the terms “first” and “second” used to indicate sequence, are merely to enable those skilled in the art to better understand the concept of the invention as illustrated in the preferred embodiments, and are not intended to limit the invention. Unless otherwise stated, all sequences, orientations, or directions are used only to distinguish one element / component / structure from another, and unless otherwise stated, do not indicate any particular order, sequence of operations, direction, or orientation. For example, in an alternative embodiment, “right side” could be “left side”, etc.

[0124] As used herein, unless otherwise specified, the terms “approximately” and “about” are interpreted as indicating a value or range of values ​​plus or minus five percent, or a deviation of the shape and / or position from the value by plus or minus five percent.

[0125] In summary, the diffuser 100 with adjustable blades according to embodiments of the present invention overcomes the shortcomings of the prior art and achieves the intended purpose of the invention.

[0126] While the diffuser with adjustable blades of the present invention has been described above with reference to preferred embodiments, those skilled in the art should recognize that the above examples are merely illustrative and should not be construed as limiting the invention. Therefore, various modifications and variations can be made to the invention within the spirit and scope of the claims, and all such modifications and variations will fall within the scope claimed by the claims.

Claims

1. A diffuser (100) with adjustable blades, characterized in that, The diffuser (100) is disposed radially outside the impeller (200) of the compressor and includes: The first diffuser section (10) engages with the compressor housing (300). The second diffuser section (20) is disposed opposite to the first diffuser section (10) and engages with the back plate (400) of the compressor; and The blade (30) includes a first blade portion (31) and a second blade portion (32), wherein the first blade portion (31) is fixed to the first diffuser portion (10) and / or the second diffuser portion (20), and the second blade portion (32) extends freely radially outward from the first blade portion (31), such that the blade (30) can elastically deform between a first state and a second state. In the first state, the blade (30) remains in its undeformed initial state, while in the second state, the second blade portion (32) is at least partially deflected away from or towards the impeller (200), and As the airflow pressure acting on the blade (30) increases, the blade (30) elastically deforms from the first state to the second state.

2. The diffuser (100) according to claim 1, characterized in that, The blade (30) is made of spring steel, and the elastic modulus of the spring steel is between 180 GPa and 215 GPa.

3. The diffuser (100) according to claim 1, characterized in that, The ratio between the first length (L1) of the first blade portion (31) and the second length (L2) of the second blade portion (32) is between 0.15 and 0.

30.

4. The diffuser (100) according to claim 1, characterized in that, The first axial height (H1) of the first blade portion (31) is greater than the second axial height (H2) of the second blade portion (32).

5. The diffuser (100) according to claim 1, characterized in that, The thickness of the blade (30) decreases from the first blade portion (31) toward the second blade portion (32).

6. The diffuser (100) according to claim 5, characterized in that, The ratio of the first maximum thickness (T1) of the first blade portion (31) to the second minimum thickness (T2) of the second blade portion (32) is between 2.5 and 3.

2.

7. The diffuser (100) according to any one of claims 1-6, characterized in that, The first diffuser portion (10) and the second diffuser portion (20) each have an annular body, wherein the first blade portion (31) is fixed to the annular body and is equidistantly spaced along the circumferential direction.

8. The diffuser (100) according to claim 7, characterized in that, An arc-shaped transition portion (33) is provided at the attachment portion between the first blade portion (31) and the annular body.

9. A compressor (1000), characterized in that, The compressor includes: The diffuser (100) according to any one of claims 1-8; Impeller (200) disposed on the radially inner side of the diffuser (100); Pressure shell (300), the pressure shell being provided with a first mounting groove (310); and A back plate (400) is opposite to the pressure shell (300) and is provided with a second mounting groove (410). The first diffuser portion (10) and the second diffuser portion (20) of the diffuser (100) are respectively installed in the first mounting slot (310) and the second mounting slot (410).

10. The compressor (1000) according to claim 9, characterized in that, Also includes: A first locking portion (40) is provided at at least one of the first mounting groove (310) and the second mounting groove (410); as well as A second locking portion (50) is provided at at least one of the first diffuser portion (10) and the second diffuser portion (20). The first locking part (40) cooperates with the second locking part (50) to prevent the diffuser (100) from moving circumferentially.

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