Shell assembly of gas compressor, gas compressor and engine

Abstract

The invention provides a shell assembly of a gas compressor, the gas compressor and an engine. The shell assembly of the gas compressor comprises a gas compressor shell and a shell cover, the backflow ring and the noise suppressor are sequentially installed in the air inlet cavity in the direction away from the impeller cavity. The first inner cavity, the second inner cavity and the impeller cavity are communicated; the backflow ring comprises an inner ring structure, a ring cavity and an outer ring structure; a first gap is defined by one end of the inner ring structure and the cavity wall of the impeller cavity; an annular groove is formed in the periphery of one end of the noise suppressor; one end of the inner ring structure is inserted into the annular groove to define a second gap; the noise suppressor, the outer ring structure and the cavity wall of the air inlet cavity are sequentially connected in an abutting mode in the axial direction of the air inlet cavity. The inner diameter of the outer ring structure is smaller than or equal to that of the outer wall of the annular groove; the first gap, the annular cavity, the annular groove and the second gap are sequentially communicated to form a backflow cavity. The noise suppressor and the backflow ring are installed at the air inlet end of the air compressor, and the effects of reducing noise propagation and reducing surge are achieved through the reliable axial positioning and radial size relation.

Description

Technical Field

[0001] The present application relates to the technical field of compressors, and in particular to a compressor casing assembly, a compressor, and an engine. Background Art

[0002] Surge is a vibration that occurs in a compressor under abnormal operating conditions when the air flow rate decreases to a certain level. Surge is very harmful to the compressor, causing severe mechanical vibration of compressor components, local overheating, performance degradation, and system instability, often resulting in severe damage to components in a very short period of time.

[0003] A common and relatively economical method to reduce the risk of surge is to add a recirculation cavity at the inlet end of the compressor, and the recirculation cavity is a cavity design. Some studies have shown that adding guide vanes in the recirculation cavity can further optimize the surge margin and balance the efficiency of the surge zone, but adding guide vanes is difficult to implement industrially. For example, an integrated design will bring manufacturing difficulties, while a split design has higher requirements for the relative position of parts. It is necessary to ensure the integrity of the entire recirculation channel, including the smoothness of the recirculation cavity, the dimensional accuracy of the inlet and outlet channels, and the accuracy of the radial fitting dimensions and axial positioning dimensions, as well as the reliability of the assembly. Once the assembly becomes loose during application, it will increase the risk of surge and noise. In severe cases, it will cause the parts to collide with the compressor impeller, resulting in rotor failure. Summary of the Invention

[0004] In response to the shortcomings of existing methods, this application proposes a compressor casing assembly, a compressor and an engine to solve the problems of low compressor surge margin, surge and noise risks, and difficulties in industrial implementation in related technologies.

[0005] In a first aspect, an embodiment of the present application provides a compressor casing assembly, comprising: a compressor housing having an air inlet chamber and an impeller chamber; The reflux ring and the noise suppressor are sequentially installed in the air inlet chamber in a direction away from the impeller chamber; the first inner cavity of the noise suppressor, the second inner cavity of the reflux ring and the impeller chamber are sequentially connected; The reflux ring includes an inner ring structure, an annular cavity and an outer ring structure which are sequentially arranged from the inside to the outside along the radial direction of the second inner cavity; One end of the inner ring structure facing the impeller chamber is enclosed with the wall of the impeller chamber to form a first gap; An annular groove is provided on the periphery of one end of the cavity wall of the noise suppressor facing the reflux ring; the inner ring structure is partially inserted into the annular groove at one end facing the noise suppressor, and forms a second gap with the inner wall of the annular groove; Along the axial direction of the air intake chamber, the noise suppressor, the outer ring structure and the cavity wall of the air intake chamber abut in sequence; the inner diameter of the outer ring structure is less than or equal to the inner diameter of the outer wall of the annular groove; The first gap, the annular cavity, the annular groove and the second gap are connected in sequence to form a reflux cavity.

[0006] Optionally, the recirculation ring further comprises a plurality of guide vanes arranged in the annular cavity around the axis of the second inner cavity; The plurality of guide vanes are respectively connected to the inner ring structure and the outer ring structure.

[0007] Optionally, the inner ring structure, the plurality of guide vanes and the outer ring structure are integrally formed.

[0008] Optionally, along the axial direction of the intake chamber, one end of the noise suppressor away from the outer ring structure is flush with the surface of the intake end of the intake chamber or is retracted inwardly relative to the intake end of the intake chamber.

[0009] Optionally, along the direction from the noise suppressor to the backflow ring, the diameter of at least a portion of the first inner cavity gradually decreases.

[0010] Optionally, the inner wall of the first inner cavity has an S-shaped cross-section on the axial cross-section of the first inner cavity; or The cross-sectional shape of the first inner cavity on its axial cross-section is conical.

[0011] Optionally, along the direction of the noise suppressor pointing to the recirculation ring, the inner wall diameter of the air inlet end of the inner ring structure gradually decreases; and / or, The minimum diameter of the inner wall of the inner ring structure is smaller than the minimum diameter of the first inner cavity.

[0012] Optionally, the return ring is transitionally matched with the compressor casing; and / or, The noise suppressor is interference fit with the compressor casing.

[0013] Optionally, the material of the reflow ring includes aluminum alloy or plastic; and / or, The noise suppressor is made of the same material as the compressor housing.

[0014] In a second aspect, an embodiment of the present application provides a compressor, comprising: a casing assembly of the compressor as described above.

[0015] In a third aspect, an embodiment of the present application provides an engine, comprising: a compressor as described above.

[0016] The beneficial technical effects brought about by the technical solutions provided in the embodiments of the present application include: In an embodiment of the present application, a noise suppressor and a recirculation ring are installed at the air inlet end of the compressor, which can improve the surge margin and stability of the compressor and reduce the probability and risk of surge. The noise suppressor and the recirculation ring are two independent components. The noise suppressor and the recirculation ring can be manufactured, installed, disassembled, maintained or replaced separately. They are easy to manufacture and easy to operate, with high flexibility and adaptability, and the two components will not cause interference.

[0017] Additional aspects and advantages of the present application will be given in part in the following description, which will become apparent from the following description, or will be learned through practice of the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] The above and / or additional aspects and advantages of the present application will become apparent and easily understood from the following description of the embodiments in conjunction with the accompanying drawings, in which: Figure 1 A schematic cross-sectional view of a casing assembly of a compressor provided in an embodiment of the present application; Figure 2 for Figure 1 Schematic diagram of the local enlarged structure at A in the middle; Figure 3 A schematic diagram of an exploded structure of a compressor casing assembly provided in an embodiment of the present application; Figure 4 for Figure 3 A schematic cross-sectional view of the casing assembly of the intermediate compressor; Figure 5 A schematic cross-sectional structural diagram of a compressor casing of a compressor casing assembly provided in an embodiment of the present application; Figure 6 A schematic structural diagram of a return ring of a compressor casing assembly provided in an embodiment of the present application; Figure 7 for Figure 6 A schematic diagram of the structure of the central recirculation ring from one perspective; Figure 8 A schematic diagram of a cross-sectional perspective structure of a return ring of a compressor casing assembly provided in an embodiment of the present application (for example, Figure 7 Middle BB section view); Figure 9 A schematic cross-sectional structure diagram of a return ring of a compressor casing assembly provided in an embodiment of the present application (for example, Figure 7 BB-direction cross-sectional view); Figure 10 A schematic structural diagram of a noise suppressor of a compressor casing assembly provided in an embodiment of the present application from one perspective; Figure 11A schematic structural diagram of a noise suppressor of a compressor casing assembly provided in an embodiment of the present application from another perspective; Figure 12 A schematic cross-sectional structural diagram of a noise suppressor of a compressor casing assembly provided in an embodiment of the present application; Figure 13 is the compressor performance diagram of the baseline solution; Figure 14 A compressor performance diagram of a compressor casing assembly provided in an embodiment of the present application; Figure 15 A performance comparison chart of a compressor casing assembly provided in an embodiment of the present application and a compressor of a baseline solution; Figure 16 A schematic cross-sectional view of a compressor casing assembly provided in an embodiment of the present application applied to a turbocharger.

[0019] Reference numerals: 100- compressor casing assembly; 10- compressor housing; 11- air inlet chamber; 12- impeller chamber; 13- fifth wall; 14- volute; 20-recirculation ring; 21-second inner cavity; 22-first wall; 23-annular cavity; 24-guide vane; 25-fourth wall; 26-inner ring structure; 27-outer ring structure; 28-second wall; 29-third wall; 30-noise suppressor; 31-first inner cavity; 32-inner wall of the annular groove; 33-annular groove; 41-second gap; 42-first gap; 50-reflux cavity; 1000-turbocharger; 200- compressor end; 210- compressor impeller; 300-turbine end; 310-volute assembly; 320-turbine; 400-middle shell assembly; 410-pressure end back plate; 500-diffusion channel; 600-Turbine shaft. DETAILED DESCRIPTION

[0020] The following describes the embodiments of the present application in conjunction with the accompanying drawings. It should be understood that the embodiments described below in conjunction with the accompanying drawings are exemplary descriptions for explaining the technical solutions of the embodiments of the present application and do not constitute a limitation on the technical solutions of the embodiments of the present application.

[0021] Those skilled in the art will understand that, unless otherwise stated, the terms "said" and "the" used herein may also include plural forms. It should be further understood that the term "including" used in the specification of this application refers to the presence of the features, integers and / or components, but does not exclude the implementation of other features, information, data, steps, operations, elements, components and / or their combinations supported by the technical field. The term "and / or" used herein refers to at least one of the items defined by the term, for example, "A and / or B" can be implemented as "A", or as "B", or as "A and B".

[0022] In order to make the objectives, technical solutions and advantages of this application clearer, the implementation methods of this application will be further described in detail below with reference to the accompanying drawings.

[0023] In some related technologies, the noise suppressor and return ring are integrated into a single insert. However, due to manufacturability issues, this integrated insert cannot accommodate blades. Recent research has shown that adding blades to the noise suppressor can help improve compressor efficiency. However, the blades designed for the noise suppressor are very thin, making it difficult to ensure sufficient strength during manufacturing, making them unsustainable, unreliable, and cost-effective.

[0024] The compressor casing assembly, compressor and engine provided in this application are intended to solve the above technical problems in related technologies.

[0025] The following is a detailed description of the technical solution of the present application and how the technical solution of the present application solves the above-mentioned technical problems with specific embodiments. It should be noted that the following embodiments can refer to, draw on, or combine with each other, and the same terms, similar features, and similar implementation steps in different embodiments will not be repeated.

[0026] The embodiment of the present application provides a compressor housing assembly 100. The structural schematic diagram of the compressor housing assembly 100 is shown in FIG. Figure 1 、 Figure 3 and Figure 4 Shown, including: The compressor housing 10 has an air intake chamber 11 and an impeller chamber 12, such as Figure 5 shown.

[0027] A ported shroud 20 and a noise suppressor 30 are sequentially installed in the intake chamber 11 in a direction away from the impeller chamber 12 ; a first inner cavity 31 of the noise suppressor 30 , a second inner cavity 21 of the ported shroud 20 , and the impeller chamber 12 are sequentially connected.

[0028] In the embodiment of the present application, the recirculation ring 20 and the noise suppressor 30 are both installed in the air inlet chamber 11 of the compressor casing 10, and the recirculation ring 20 is close to the impeller chamber 12, and the noise suppressor 30 is located on the side of the recirculation ring 20 away from the impeller chamber 12. The compressor casing 10 is used to carry the recirculation ring 20 and the noise suppressor 30. The first inner cavity 31 of the noise suppressor 30, the second inner cavity 21 of the recirculation ring 20 and the impeller chamber 12 are connected in sequence, serving as the main channel of the compressor. The gas can enter the impeller chamber 12 after passing through the first inner cavity 31 of the noise suppressor 30 and the second inner cavity 21 of the recirculation ring 20 in sequence. The compressor impeller and other components are installed in the impeller chamber 12. The high-speed rotating compressor impeller in the impeller chamber 12 can do work on the gas entering the impeller chamber 12, thereby increasing the gas pressure and increasing the gas kinetic energy.

[0029] The recirculation ring 20 optimizes the airflow path and reduces turbulence, significantly improving the compressor's stability and surge margin, thereby achieving greater operational stability and safety margins, and enhancing system stability. The noise suppressor 30's primary function is to stabilize the intake air flow and reduce vortex disturbances.

[0030] Installing a noise suppressor 30 and a return ring 20 at the air inlet end of the compressor can reduce the probability and risk of surge.

[0031] Moreover, in the embodiment of the present application, the noise suppressor 30 and the reflow ring 20 are two independent components, and the noise suppressor 30 and the reflow ring 20 can be manufactured, installed, disassembled, maintained or replaced separately. They are easy to manufacture and operate, and have high flexibility and adaptability, and the two components will not cause interference.

[0032] It should be noted that in the embodiments of this application, Figures 1 to 12 The thin arrow in the middle indicates: the corresponding figure mark represents space.

[0033] Alternatively, as Figure 4 、 Figures 6 to 9 As shown, in the embodiment of the present application, the recirculation ring 20 includes an inner ring structure 26 , an annular cavity 23 and an outer ring structure 27 which are sequentially arranged from the inside to the outside along the radial direction of the second inner cavity 21 .

[0034] The inner ring structure 26, at one end facing the impeller chamber 12 (i.e., the outlet end), encloses the wall of the impeller chamber 12 to form a first gap 42. An annular groove 33 is provided on the periphery of the end of the wall of the noise suppressor 30 facing the return ring 20 (i.e., the outlet end). The inner ring structure 26, at one end facing the noise suppressor 30 (i.e., the main channel inlet end of the inner ring structure 26), is partially inserted into the annular groove 33 and encloses the inner wall 32 of the annular groove 33 to form a second gap 41. Along the axial direction of the intake chamber 11, the noise suppressor 30, the outer ring structure 27, and the wall of the intake chamber 11 are in contact with each other in sequence. The inner diameter of the outer ring structure 27 is less than or equal to the inner diameter of the outer wall of the annular groove 33. The first gap 42, the annular cavity 23, the annular groove 33, and the second gap 41 are connected in sequence to form the return chamber 50.

[0035] In the embodiment of the present application, the inner ring structure 26 encloses the second inner cavity 21. The air inlet end of the second inner cavity 21 (i.e., the end facing the noise suppressor 30) is connected to the first inner cavity 31, and the air outlet end (i.e., the end facing the impeller chamber 12) is connected to the impeller chamber 12. The outer ring structure 27 is sleeved around the outer periphery of the inner ring structure 26, and the outer ring structure 27 and the inner ring structure 26 enclose an annular cavity 23.

[0036] The air outlet end of the inner ring structure 26 (ie, the fourth wall 25 ) and the cavity wall of the impeller chamber 12 (ie, the fifth wall 13 ) enclose a first gap 42 , so that the annular cavity 23 can communicate with the impeller chamber 12 through the first gap 42 .

[0037] The annular groove 33 of the noise suppressor 30 surrounds the first inner cavity 31 and is located at the air outlet end of the first inner cavity 31. The inner ring structure 26 is partially inserted into the annular groove 33 at one end facing the noise suppressor 30. A portion of the inner wall of the inner ring structure 26 (i.e., a portion of the first wall 22) and the inner wall 32 of the annular groove 33 form a second gap 41, allowing the second inner cavity 21 to communicate with the annular groove 33 through the second gap 41, and the annular groove 33 to communicate with the annular cavity 23.

[0038] The first gap 42 , the annular cavity 23 , the annular groove 33 and the second gap 41 are connected in sequence to form a reflux cavity 50 . The air inlet end of the reflux cavity 50 is connected to the impeller chamber 12 , and the air outlet end is connected to the second inner cavity 21 .

[0039] The gas enters the impeller chamber 12 through the main channel, that is, through the first inner cavity 31 and the second inner cavity 21 in sequence. A portion of the gas in the impeller chamber 12 is compressed, pressurized and energized, and then passes through the diffuser channel 500 composed of the compressor housing 10 and the pressure end back plate 410 of the intermediate housing assembly 400 for further pressurization, and then enters the volute 14 of the compressor housing 10 and is guided to the engine intake to enhance the performance of the engine. The other portion of the gas flows back to the second inner cavity 21 (such as through the return cavity 50, that is, through the first gap 42, the annular cavity 23, the annular groove 33 and the second gap 41 in sequence) through the return cavity 50. Figure 2 As shown, the thick arrow indicates the flow direction of the gas in the reflux chamber 50), which can achieve secondary flow, stabilize the airflow, and reduce noise.

[0040] Furthermore, by providing a reflow cavity 50 at the impeller chamber 12, the reflow cavity 50 itself needs to ensure smoothness, and the opening accuracy of the first gap 42 at the front end and the second gap 41 at the rear end need to be ensured, which can prevent the compressor from entering a surge condition and achieve anti-surge protection. The curvature of the annular groove 33 of the noise suppressor 30 is an important component of the reflow cavity 50. The reflow ring 20 has an outer ring structure 27. The inner diameter of the outer ring structure 27 is less than or equal to the inner diameter of the outer wall of the annular groove 33 of the noise suppressor 30, so that the inner diameter of the outer ring structure 27 matches the size of the annular groove 33, ensuring the formation of a smooth reflow cavity 50. The reflow cavity 50 is formed as a cavity, which can absorb fixed-frequency and broadband aerodynamic noise and reduce the propagation of noise. At the same time, the reflow cavity 50 combined with the bladed reflow ring helps to increase the surge margin and reduce the occurrence of surge.

[0041] The end of the outer ring structure 27 facing the impeller chamber 12 abuts the wall of the intake chamber 11, while the end of the outer circumferential wall of the noise suppressor 30 facing the return ring 20 abuts the end of the outer ring structure 27 facing away from the impeller chamber 12. The noise suppressor 30 precisely stops the return ring 20 in the correct axial position, ensuring its axial position and achieving reliable axial positioning. Both the return ring 20 and the noise suppressor 30 are installed within the intake chamber 11 of the compressor casing 10. Assembly reliability is ensured through radially matching dimensions (e.g., a transition fit between the outer ring structure 27 of the return ring 20 and the wall of the intake chamber 11 of the compressor casing 10, and an interference fit between the noise suppressor 30 and the wall of the intake chamber 11). Precise axial dimensioning ensures the first gap 42, the second gap 41, and the relative positions of the intake chamber 11 of the compressor casing 10, the return ring 20, and the noise suppressor 30.

[0042] The embodiment of the present application achieves the effect of reducing noise transmission and lowering surge through reliable axial positioning and radial dimension relationship.

[0043] It should be noted that, in the embodiment of the present application, the cavity wall of the noise suppressor 30 refers to the outer peripheral wall of the noise suppressor 30 that encloses the first inner cavity 31. The opening of the annular groove 33 of the noise suppressor 30 faces the recirculation ring 20.

[0044] Alternatively, as Figure 1 As shown, in the embodiment of the present application, the noise suppressor 30, the inner ring structure 26 and the cavity wall of the impeller chamber 12 are coaxially arranged along the axis L, that is, the first inner cavity 31, the second inner cavity 21 and the impeller chamber 12 are coaxial.

[0045] Alternatively, as Figure 1 and Figure 2 As shown, in the embodiment of the present application, the first gap 42 is an annular gap extending around the axis L. The second gap 41 is an annular gap extending around the axis L.

[0046] Alternatively, as Figure 4 、 Figures 6 to 9 As shown, in the embodiment of the present application, the recirculation ring 20 further includes a plurality of guide vanes 24 arranged in the annular cavity 23 around the axis of the second inner cavity 21 ; the plurality of guide vanes 24 are respectively connected to the inner ring structure 26 and the outer ring structure 27 .

[0047] In the embodiment of the present application, the outer ring structure 27 is connected to the inner ring structure 26 through a plurality of guide vanes 24. The plurality of guide vanes 24 are arranged in the annular cavity 23 and distributed around the axis of the second inner cavity 21 (i.e., the axis L). The plurality of guide vanes 24 divide the annular cavity 23 into a plurality of cavities. There is a cavity between any two adjacent guide vanes 24. The air inlet ends of the plurality of cavities are connected to the first gap 42, and the air outlet ends are connected to the annular groove 33.

[0048] In the embodiment of the present application, guide vanes 24 are provided in the annular cavity 23 of the return ring 20 , which helps to increase the surge margin of the compressor, which is very useful for applications with a wide operating range.

[0049] The return ring 20 is formed as a vaned ported shroud. The vaned return ring 20 and the noise suppressor 30 are each independent components, enabling low-cost mass production. The compressor casing assembly 100 provided in the present embodiment enables the assembly of a low-cost, mass-producible vaned return ring within the compressor casing 10.

[0050] Optionally, in an embodiment of the present application, the inner ring structure 26 , the plurality of guide vanes 24 and the outer ring structure 27 are integrally formed.

[0051] Optionally, in the embodiment of the present application, depending on the material, the return ring 20 with guide vanes can be made by a die casting process or by injection molding, which is easy to manufacture.

[0052] In the embodiment of the present application, the recirculation ring 20 with guide vanes is provided with openings on both sides (i.e., the air inlet side and the air outlet side), so that both sides remain open to facilitate installation and processing operations during the die-casting process.

[0053] Of course, in other optional embodiments of the present application, the inner ring structure 26, the multiple guide vanes 24 and the outer ring structure 27 can also be designed as separate types according to actual needs, and the inner ring structure 26, the multiple guide vanes 24 and the outer ring structure 27 can be assembled and fixed together when necessary.

[0054] Alternatively, as Figure 5 As shown, in the embodiment of the present application, the air inlet chamber 11 is a cylindrical cavity. The outer ring structure 27 is a cylindrical pipe. The outer peripheral wall of the noise suppressor 30 is cylindrical, that is, has a cylindrical outer contour.

[0055] Alternatively, as Figure 1 、 Figure 2 、 Figures 4 to 6 ,as well as Figures 9 to 12 As shown, in this embodiment of the present application, along the axial direction of the intake chamber 11, the end of the noise suppressor 30 away from the outer ring structure 27 is flush with the surface of the intake end of the intake chamber 11. That is, along the axial direction, the sum of the outer circumferential wall length of the noise suppressor 30 and the length of the outer ring structure 27 is equal to the length of the intake chamber 11. This ensures a smooth surface at the compressor intake end, protects the noise suppressor 30, reduces damage, and provides a neat and aesthetically pleasing appearance.

[0056] Of course, in other optional embodiments of the present application, according to actual needs, the end of the noise suppressor 30 away from the outer ring structure 27 along the axial direction of the air intake chamber 11 can be slightly retracted inward relative to the air intake end of the air intake chamber 11. That is, along the axial direction, the sum of the length of the outer peripheral wall of the noise suppressor 30 and the length of the outer ring structure 27 is slightly less than the length of the air intake chamber 11.

[0057] Alternatively, as Figure 1 、 Figure 4 and Figure 12 As shown, in the embodiment of the present application, along the direction from the noise suppressor 30 to the recirculation ring 20 , the diameter of at least a portion of the first inner cavity 31 gradually decreases.

[0058] In the embodiment of the present application, gas flows into the first inner cavity 31 from the inlet end of the first inner cavity 31 (i.e., the end away from the second inner cavity 21), and then flows into the second inner cavity 21 through the outlet end of the first inner cavity 31. Along the direction from the noise suppressor 30 toward the recirculation ring 20 (i.e., the direction from the first inner cavity 31 toward the second inner cavity 21), the diameter of at least a portion of the first inner cavity 31 gradually decreases, that is, the inner circumferential wall of at least a portion of the first inner cavity 31 contracts. This design helps guide the airflow into the compressor casing 10, reduces intake shock and throttling losses, improves compressor efficiency, and reduces intake noise.

[0059] It should be noted that, in the embodiment of the present application, “at least part” includes part and all, for example, at least part of the first inner cavity 31 includes part of the first inner cavity 31 (i.e., a part of the first inner cavity 31) and the entire first inner cavity 31.

[0060] Alternatively, as Figure 1 、 Figure 4 and Figure 12As shown, in the embodiment of the present application, the inner wall of the first inner cavity 31 has an S-shaped cross-section on the axial section of the first inner cavity 31.

[0061] It should be noted that the axial cross section refers to the cross section through the axis. For example, the axial cross section of the first inner cavity 31 is the cross section through the axis of the first inner cavity 31 (ie, Figure 1 and Figure 5 Axis L) shown in cross section.

[0062] In the embodiment of the present application, on the axial cross-section, the cross-sectional shape of the inner wall of the first inner cavity 31 is S-shaped, and the inner peripheral wall of the first inner cavity 31 is formed as a whole into a shape similar to a bell mouth, which is used to guide the gas into the compressor casing 10 and improve the compressor performance.

[0063] Of course, in other optional embodiments of the present application, the cross-sectional shape of the first inner cavity 31 on its axial cross-section may be tapered, depending on actual needs. Alternatively, the cross-sectional shape of the first inner cavity 31 on its axial cross-section may be conical. Alternatively, in the embodiment of the present application, the cross-sectional shape of the inner wall of the first inner cavity 31 is not limited to an S-shape or a cone, and may be designed into other regular or irregular shapes, depending on actual needs, as long as the diameter of at least a portion of the first inner cavity 31 gradually decreases.

[0064] Optionally, in the embodiment of the present application, the noise suppressor 30 is interference fit with the compressor casing 10. The purpose of using interference fit is to ensure a sufficiently large positive pressure to prevent the insert from separating from the body at high temperatures, that is, to prevent the noise suppressor 30 from separating from the compressor casing 10 at high temperatures.

[0065] Optionally, in the embodiment of the present application, the noise suppressor 30 is installed in the air intake chamber 11 of the compressor casing 10 by press fitting, or is installed by an industrial refrigerator to prevent damage caused by uneven contact surfaces during assembly.

[0066] In the embodiment of the present application, the noise suppressor 30 adopts a press-in design, is embedded in the air intake chamber 11 of the compressor casing 10, and contacts the return ring 20 to ensure the axial position of the return ring 20.

[0067] Alternatively, as Figures 10 to 12As shown, in the embodiment of the present application, the noise suppressor 30 has an inner circumferential wall, an outer circumferential wall, a first side surface facing the recirculation ring 20, and a second side surface facing the compressor intake end. The inner circumferential wall of the noise suppressor 30 encloses a first inner cavity 31; the outer circumferential wall of the noise suppressor 30 is interference-fitted with the inner circumferential wall of the intake chamber 11 of the compressor casing 10 and contacts the outer ring structure 27 to ensure the axial position of the recirculation ring 20; a portion of the first side surface of the noise suppressor 30 is recessed inward (away from the recirculation ring 20) to form an annular groove 33, and the second side surface is flush with the surface of the intake end of the compressor casing 10 or slightly indented into the intake chamber 11 relative to the surface of the intake end of the compressor casing 10.

[0068] Optionally, in the embodiment of the present application, the return ring 20 is transitionally matched with the compressor casing 10 .

[0069] Optionally, in the embodiment of the present application, the outer peripheral wall of the outer ring structure 27 of the recirculation ring 20 is transitionally matched with the inner peripheral wall of the intake chamber 11 of the compressor casing 10 .

[0070] In this embodiment, the return ring 20 and the compressor casing 10 are connected using a transitional design to minimize radial deviation. The noise suppressor 30 is connected to the compressor casing 10 using a press-fit design to secure the return ring 20 and prevent it from falling off.

[0071] The return ring 20 axially contacts the step of the compressor casing 10 ; along the axial direction, the cumulative length of the return ring and the length of the noise suppressor (ie, the sum) is flush with the length of the intake chamber 11 of the compressor casing 10 or slightly retracted.

[0072] Alternatively, as Figure 1 、 Figure 2 、 Figure 4 and Figure 9 As shown, in the embodiment of the present application, the inner wall diameter of the air inlet end of the inner ring structure 26 gradually decreases along the direction of the noise suppressor 30 pointing to the return ring 20. This design can guide the airflow into the compressor casing 10, helping to improve the efficiency of the compressor.

[0073] Alternatively, as Figure 1 and Figure 2 As shown, in the embodiment of the present application, the minimum diameter of the inner wall of the inner ring structure 26 is smaller than the minimum diameter of the first inner cavity 31, which helps to increase the kinetic energy of the gas.

[0074] Alternatively, as Figures 6 to 9As shown, in the embodiment of the present application, the inner circumferential wall of the inner ring structure 26 encloses the second inner cavity 21, and the inner circumferential wall includes a first wall surface 22 and a second wall surface 28 connected to each other. The first wall surface 22 is close to the noise suppressor 30, and the second wall surface 28 is close to the impeller chamber 12. In the axial cross-section of the inner ring structure 26, the cross-sectional shape of the first wall surface 22 is conical, so that the diameter of the inlet end of the second inner cavity 21 gradually decreases. The cross-sectional shape of the second wall surface 28 is cylindrical, and the diameter of the second wall surface 28 is equal to the minimum diameter of the first wall surface 22.

[0075] Alternatively, as Figure 8 and Figure 9 As shown, in the embodiment of the present application, in the axial cross section, the cross-sectional shape of the first wall surface 22 is conical, and the cross-sectional shape of the second wall surface 28 is cylindrical.

[0076] Of course, in other optional embodiments of the present application, the diameter of the second wall 28 can be designed to gradually decrease in the direction from the noise suppressor 30 to the recirculation ring 20 according to actual needs.

[0077] Of course, in other optional embodiments of the present application, the inner wall shape of the inner ring structure 26 can also be designed into other shapes according to actual needs, as long as the diameter of at least part of the inner wall of the inner ring structure 26 gradually decreases along the direction of the recirculation ring 20 pointed by the noise suppressor 30.

[0078] Alternatively, as Figure 8 and Figure 9 As shown, in the embodiment of the present application, the outer peripheral wall of the inner ring structure 26 includes a third wall surface 29 and a fourth wall surface 25 connected to each other. The third wall surface 29 is close to the noise suppressor 30, and the fourth wall surface 25 is close to the impeller chamber 12. The guide vane 24 is connected to the third wall surface 29 of the inner ring structure 26.

[0079] In this embodiment, the end of the first wall 22 away from the second wall 28 is connected to the end of the third wall 29 away from the fourth wall 25. The end of the second wall 28 away from the first wall 22 is connected to the end of the fourth wall 25 away from the third wall 29.

[0080] Alternatively, as Figure 1 、 Figure 2 、 Figure 8 、 Figure 9 and Figure 12 As shown, in this embodiment of the present application, the first wall surface 22 is inclined relative to the axis of the second inner cavity 21 (i.e., axis L), and the distance between the first wall surface 22 and the axis of the second inner cavity 21 gradually decreases along the direction from the first inner cavity 31 to the second inner cavity 21. The inner ring structure 26 is inserted into the annular groove 33 toward the end of the noise suppressor 30. The first wall surface 22 cooperates with the inner wall 32 of the annular groove 33 to enclose a second gap 41.

[0081] Alternatively, as Figure 1 、 Figure 2 、 Figure 5 、 Figure 8 and Figure 9 As shown, in the embodiment of the present application, the cavity wall of the impeller chamber 12 has a fifth wall surface 13, and the fifth wall surface 13 is close to the recirculation ring 20. The fifth wall surface 13 cooperates with the fourth wall surface 25 to enclose a first gap 42.

[0082] Alternatively, as Figure 5 and Figure 9 As shown, in the embodiment of the present application, the fourth wall 25 is inclined relative to the axis of the second inner cavity 21 (i.e., the axis L), and the fifth wall 13 is inclined relative to the axis of the impeller chamber 12 (i.e., the axis L), and along the direction of the second inner cavity 21 pointing to the impeller chamber 12, the distance between the fourth wall 25 and the axis of the second inner cavity 21 gradually decreases, and the distance between the fifth wall 13 and the axis of the impeller chamber 12 gradually decreases.

[0083] Alternatively, as Figures 6 to 9 As shown, in the embodiment of the present application, the overall shape of the return ring 20 with guide vanes is similar to a cylindrical pipe.

[0084] Optionally, in the embodiment of the present application, the axial dimensions of the compressor casing 10 , the recirculation ring 20 , and the noise suppressor 30 should be carefully calculated, for example, by stack-up calculation, to ensure that the designs of the second gap 41 and the first gap 42 meet the requirements.

[0085] Optionally, in the embodiment of the present application, the material of the reflow ring 20 includes aluminum alloy or plastic.

[0086] Optionally, in the embodiment of the present application, the reflow ring 20 may be made of aluminum (including single-element aluminum and aluminum alloy), or may be made of plastic, such as special plastic.

[0087] Optionally, in the embodiment of the present application, the material of the noise suppressor 30 is the same as that of the compressor housing 10. This prevents the noise suppressor 30 from falling off even during operation. Reliability is ensured by the material selection, particularly by using the same material for the noise suppressor 30 and the compressor housing 10.

[0088] An embodiment of the present application provides a compressor casing assembly, comprising a compressor casing 10 and an insert installed at the air inlet end of the compressor casing 10, wherein the insert comprises a two-part structure, namely a return ring 20 with guide vanes and a noise suppressor 30. The return ring 20 with guide vanes and the noise suppressor 30 are sequentially installed from the air inlet end of the compressor casing 10 to the inside of the air inlet chamber 11. In an embodiment of the present application, the first inner cavity 31 of the noise suppressor 30, the second inner cavity 21 of the return ring 20 with guide vanes and the impeller chamber 12 of the compressor casing 10 are sequentially connected to form a main channel. The gas can pass through the main channel, sequentially through the first inner cavity 31 and the second inner cavity 21 into the impeller chamber 12, and the high-speed rotating compressor impeller is used to perform work in the impeller chamber 12 to achieve supercharging.

[0089] In the embodiment of the present application, the first wall 22 of the return ring 20 with guide vanes and the inner wall 32 of the annular groove 33 of the noise suppressor 30 enclose a second gap 41. The two ends of the second gap 41 are respectively connected to the second inner cavity 21 and the annular groove 33, and the annular groove 33 is connected to the annular cavity 23 of the return ring 20 with guide vanes. A plurality of guide vanes 24 are provided in the annular cavity 23 of the return ring 20 with guide vanes, and the plurality of guide vanes 24 are sequentially spaced around the axis of the second inner cavity 21. The fourth wall 25 of the return ring 20 with guide vanes and the fifth wall 13 of the impeller chamber 12 enclose a first gap 42. The two ends of the first gap 42 are respectively connected to the annular cavity 23 and the impeller chamber 12.

[0090] The first gap 42, the annular cavity 23, the annular groove 33 and the second gap 41 are sequentially connected to form a reflux cavity 50. Both ends of the reflux cavity 50 are connected to the impeller chamber 12 and the second inner cavity 21 respectively.

[0091] Optionally, in an embodiment of the present application, a compressor casing assembly 100 including a return ring 20 with guide vanes and a noise suppressor 30 having an S-shaped inner wall cross-section and a baseline solution are tested and compared.

[0092] Figure 13 is the compressor performance diagram of the baseline solution, Figure 14 is a compressor performance diagram of the compressor casing assembly 100 provided in an embodiment of the present application, Figure 15 This is a performance comparison chart of the compressor casing assembly 100 provided in the embodiment of the present application and the compressor of the benchmark solution (wherein R represents the compressor casing assembly 100 provided in the embodiment of the present application, and B represents the benchmark solution). Figures 13 to 15In the graph, the horizontal axis represents the Corrected Air Flow (in kilograms per second, or kg / s), the vertical axis represents the Pressure Ratio, the solid circular line represents efficiency, the dashed line on the left represents the surge line, and the solid line on the right represents the choke line. The area between the two represents the range within which the compressor can operate normally, known as the flow envelope. The larger the compressor's flow envelope, the higher its efficiency and performance.

[0093] from Figure 13 and Figure 14 It can be seen that compared with the baseline solution, the peak efficiency of the compressor shell assembly 100 provided by the embodiment of the present application is improved by 1pt (1%), and the efficiency island area is significantly increased. At a pressure ratio of 3.5, the width of the 80% efficiency island increases by about 13%. Figure 15 It can be seen that the compressor casing assembly 100 provided in the embodiment of the present application has a significantly increased surge margin compared to the baseline solution, and the width of the relationship curve between the corrected flow rate and the pressure ratio increases by about 10% at a pressure ratio of 3.5.

[0094] Therefore, the compressor casing assembly 100 provided in the embodiment of the present application can effectively improve the surge margin under the same pressure ratio compared with the traditional solution (such as the baseline solution).

[0095] In addition, compared with traditional equipment, the compressor casing assembly 100 provided in the embodiment of the present application is easier to assemble, is reliable, meets strength standards, and has controllable costs.

[0096] Optionally, the compressor casing assembly provided in the embodiment of the present application can be applied to the compressor field, and further, can be applied to a turbocharger.

[0097] Based on the same inventive concept, an embodiment of the present application provides a compressor, which includes: a compressor casing assembly 100 as described above.

[0098] Optionally, in the embodiment of the present application, the compressor may be a centrifugal compressor or an axial flow compressor.

[0099] Optionally, in the embodiment of the present application, the compressor includes but is not limited to a turbocharger 1000 .

[0100] Alternatively, as Figure 16As shown, in the embodiment of the present application, the turbocharger 1000 includes a compressor end 200, a turbine end 300, and an intermediate housing assembly 400. The compressor end 200 includes a compressor housing assembly 100 and a compressor impeller 210. The turbine end 300 includes a volute assembly 310 and a turbine 320. The intermediate housing assembly 400 is disposed between the compressor housing assembly 100 and the volute assembly 310, and the intermediate housing assembly 400 includes bearings. The turbine shaft 600 is mounted in the intermediate housing assembly 400. The compressor impeller 210 is fixedly mounted on one end of the turbine shaft 600 and is located within the impeller chamber 12 of the compressor housing assembly 100. The turbine 320 is fixedly mounted on the other end of the turbine shaft 600 and is located within the chamber defined by the volute assembly 310. The rotor consisting of the compressor impeller 210, the turbine 320, and the turbine shaft 600 is freely rotatable via bearings.

[0101] Gas (e.g., exhaust gas from the engine) enters the chamber housing the turbine 320 through the air inlet of the volute assembly 310, driving the turbine 320 to rotate. The turbine 320, via the turbine shaft 600, drives the compressor impeller 210 to rotate, causing gas (e.g., ambient air) to enter the first inner chamber 31 of the noise suppressor 30 through the air inlet of the compressor casing assembly 100 and flow through the second inner chamber 21 of the return ring 20 to the impeller chamber 12.

[0102] A portion of the gas in the impeller chamber 12 flows back into the second inner chamber 21 through the reflux cavity 50 (i.e., sequentially through the first gap 42, the annular cavity 23, the annular groove 33, and the second gap 41). The majority of the gas in the impeller chamber 12 is accelerated and pre-pressurized by the high-speed rotating compressor impeller 210, increasing the gas pressure and kinetic energy. This accelerated and pre-pressurized gas is further pressurized through the diffuser 500 formed by the compressor casing 10 and the compression end backplate 410 of the center casing assembly 400. The gas is then directed through the volute 14 of the compressor casing 10 to the engine intake, enhancing engine performance.

[0103] It should be noted that since the compressor provided in the embodiment of the present application includes the shell assembly of the compressor provided in the embodiment of the present application, the compressor provided in the embodiment of the present application also has the above-mentioned beneficial effects of the shell assembly of the compressor provided in the embodiment of the present application, which will not be repeated here.

[0104] Based on the same inventive concept, an embodiment of the present application provides an engine, which includes: a compressor as described above.

[0105] Optionally, in the embodiment of the present application, the engine includes but is not limited to an automobile engine and an aircraft engine. The engine provided in the embodiment of the present application can be applied to fields such as vehicles and aircraft.

[0106] It should be noted that, since the engine provided in the embodiment of the present application includes the compressor provided in the embodiment of the present application, the engine provided in the embodiment of the present application also has the above-mentioned beneficial effects of the compressor provided in the embodiment of the present application, which will not be repeated here.

[0107] By applying the embodiments of the present application, at least the following beneficial effects can be achieved: In the embodiment of the present application, the recirculation ring and the noise suppressor are both installed in the air inlet chamber of the compressor housing, and the recirculation ring is close to the impeller chamber, and the noise suppressor is located on the side of the recirculation ring away from the impeller chamber. The first inner cavity of the noise suppressor, the second inner cavity of the recirculation ring and the impeller chamber are connected in sequence, serving as the main channel of the compressor. The gas can enter the impeller chamber after passing through the first inner cavity of the noise suppressor and the second inner cavity of the recirculation ring in sequence. The impeller and other components of the compressor are installed in the impeller chamber. The high-speed rotating impeller in the impeller chamber can do work on the gas entering the impeller chamber, thereby increasing the gas pressure and increasing the gas kinetic energy.

[0108] The recirculation ring optimizes the airflow path and reduces turbulence, significantly improving compressor stability and surge margin, thereby achieving greater operational stability and safety margins, and enhancing system stability. The main function of the noise suppressor is to stabilize the intake air flow and reduce vortex disturbances.

[0109] Installing a noise suppressor and a return ring at the intake end of the compressor can reduce the probability and risk of surge.

[0110] Moreover, in the embodiment of the present application, the noise suppressor and the return ring are two independent components, which can be manufactured, installed, disassembled, maintained or replaced separately. They are easy to manufacture and operate, and have high flexibility and adaptability, and the two components will not cause interference.

[0111] In the description of the present application, the directions or positional relationships indicated by words such as "center", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", and "outside" are based on the exemplary directions or positional relationships shown in the accompanying drawings. They are for the convenience of describing or simplifying the description of the embodiments of the present application, and do not indicate or imply that the device or component referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be understood as limitations on the present application.

[0112] The terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of the technical features being referred to. Thus, a feature specified as "first" or "second" may explicitly or implicitly include one or more of such features. Throughout this application, unless otherwise specified, "plurality" means two or more.

[0113] In the description of this specification, specific features, structures, materials or characteristics may be combined in an appropriate manner in any one or more embodiments or examples.

[0114] The above is only part of the implementation methods of the present application. It should be pointed out that for ordinary technicians in this technical field, without departing from the technical concept of the solution of the present application, other similar implementation methods based on the technical ideas of the present application also fall within the protection scope of the embodiments of the present application.

Claims

1. A compressor casing assembly, characterized in that: include: a compressor housing having an air inlet chamber and an impeller chamber; A recirculation ring and a noise suppressor are sequentially installed in the air inlet chamber in a direction away from the impeller chamber; the first inner cavity of the noise suppressor, the second inner cavity of the recirculation ring and the impeller chamber are sequentially connected; The recirculation ring includes an inner ring structure, an annular cavity and an outer ring structure arranged in sequence from the inside to the outside along the radial direction of the second inner cavity; One end of the inner ring structure facing the impeller chamber is enclosed with the cavity wall of the impeller chamber to form a first gap; An annular groove is provided on the periphery of one end of the cavity wall of the noise suppressor facing the reflux ring; the inner ring structure is partially inserted into the annular groove toward the end of the noise suppressor, and forms a second gap with the inner wall of the annular groove; Along the axial direction of the air intake chamber, the noise suppressor, the outer ring structure and the cavity wall of the air intake chamber abut in sequence; the inner diameter of the outer ring structure is less than or equal to the inner diameter of the outer wall of the annular groove; The first gap, the annular cavity, the annular groove and the second gap are connected in sequence to form a reflux cavity.

2. The compressor casing assembly according to claim 1, characterized in that: The recirculation ring further comprises a plurality of guide vanes arranged in the annular cavity around the axis of the second inner cavity; The plurality of guide vanes are respectively connected to the inner ring structure and the outer ring structure.

3. The compressor casing assembly according to claim 2, characterized in that: The inner ring structure, the plurality of guide vanes and the outer ring structure are integrally formed.

4. The compressor casing assembly according to claim 1, wherein: Along the axial direction of the air intake chamber, one end of the noise suppressor away from the outer ring structure is flush with the surface of the air intake end of the air intake chamber or is retracted inwardly relative to the air intake end of the air intake chamber.

5. The compressor casing assembly according to claim 1, wherein: Along the direction from the noise suppressor to the backflow ring, the diameter of at least a portion of the first inner cavity gradually decreases.

6. The compressor casing assembly according to claim 5, characterized in that: The inner wall of the first inner cavity has an S-shaped cross-section on the axial cross-section of the first inner cavity; or The cross-section of the first inner cavity on its axial section is tapered.

7. The compressor casing assembly according to claim 1, wherein: Along the direction from the noise suppressor to the recirculation ring, the inner wall diameter of the air inlet end of the inner ring structure gradually decreases; and / or, The minimum diameter of the inner wall of the inner ring structure is smaller than the minimum diameter of the first inner cavity.

8. The compressor casing assembly according to claim 1, wherein: The return ring and the compressor casing are in transitional fit; and / or, The noise suppressor is interference fit with the compressor casing.

9. The compressor casing assembly according to claim 1, wherein: The material of the reflow ring includes aluminum alloy or plastic; and / or, The material of the noise suppressor is the same as that of the compressor casing.

10. A compressor, characterized in that: include: A compressor casing assembly according to any one of claims 1 to 9.

11. An engine, characterized in that: include: The compressor according to claim 10.

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