Exhaust volute and centrifugal compressor

Abstract

The invention discloses an exhaust volute and a centrifugal compressor, relates to the technical field of centrifugal compressors, and mainly aims to reduce the boundary dimension of the centrifugal compressor under the condition of ensuring that the pneumatic performance of the centrifugal compressor is at a stable level. According to the main technical scheme, the exhaust volute comprises a machine shell and a plurality of partition plates, the multiple partition plates are arranged in the machine shell and fixedly connected with the machine shell through seam allowance structures, a volute chamber is formed between every two adjacent partition plates, the molded line of each volute chamber is a curve, and when the section of each volute chamber is round, the volute chamber is provided with a plurality of spiral grooves. Said curve complying with formula: # imgabs0 #

Description

Technical Field

[0001] The present application belongs to the technical field of centrifugal compressors, and in particular relates to an exhaust volute and a centrifugal compressor. Background Art

[0002] Centrifugal compressors are widely used in various process flows, such as petrochemical, environmental protection, electric power, energy storage and other fields, mainly used to increase the pressure of various process gases. As an important stator component in centrifugal compressors, the exhaust volute mainly collects the gas that has been pressurized and accelerated by the compressor impeller, slows it down, and guides it out of the compressor body.

[0003] At present, with the large-scale production capacity in various fields, centrifugal compressor equipment has increased accordingly, and the weight of the equipment and the difficulty of processing and manufacturing have increased sharply. The exhaust volute of the traditional centrifugal compressor is mainly divided into two types: outer volute and inner volute. The exhaust volute of the outer volute type has good aerodynamic performance, but the external dimensions are large; the exhaust volute of the inner volute type has small external dimensions, but poor aerodynamic performance. In order to reduce the external dimensions of the unit, reduce weight and reduce the difficulty of processing and manufacturing, while ensuring the aerodynamic performance of the centrifugal compressor unit, the exhaust volute of the centrifugal compressor needs to be redesigned. Summary of the invention

[0004] In view of this, the present application provides an exhaust volute and a centrifugal compressor, the main purpose of which is to reduce the external dimensions of the centrifugal compressor while ensuring that the aerodynamic performance of the centrifugal compressor is at a stable level.

[0005] In order to achieve the above objectives, this application mainly provides the following technical solutions:

[0006] In one aspect of the present application, an exhaust volute is provided, the exhaust volute comprising a casing and a plurality of baffles, the plurality of baffles being arranged in the casing and connected and fixed to the casing through a stop structure, a volute chamber being formed between two adjacent baffles, the profile of the volute chamber being a curve, and when the cross section of the volute chamber is circular, the curve conforms to the formula:

[0007]

[0008] In the formula, r is the inlet radius of the volute at any angle around the casing; s is the inner cavity radius of the casing; r is the cross-sectional radius of the volute;

[0009] Wherein, the cross-sectional radius r of the volute chamber conforms to the formula:

[0010]

[0011] In the formula, is any angle of the casing circumference; M is a transition parameter;

[0012] Wherein, the transition parameter M conforms to the formula:

[0013]

[0014] In the formula, c ′ 4u is the inlet tangential airflow velocity of the housing; r ′ 4 is the inlet radius of the casing; Q ′ 4 is the volume flow at the inlet of the casing.

[0015] Optionally, the exhaust volute further includes an impeller. When a bladeless diffuser is provided on the downstream side of the impeller in the flow direction, the exhaust volute satisfies the formula:

[0016]

[0017] In the formula, is the inlet radius of the casing at 360 degrees in the circumferential direction of the casing; r2 is the outlet radius of the impeller.

[0018] Optionally, the widths of the vaneless diffusers in the flow direction are the same, and the airflow direction angles of the gas flowing in the vaneless diffusers are the same.

[0019] Optionally, the exhaust volute further includes an impeller. When a blade diffuser is provided on the downstream side of the impeller in the flow direction, the exhaust volute satisfies the formula:

[0020]

[0021] In the formula, is the inlet radius of the casing at 360 degrees in the circumferential direction of the casing; r2 is the outlet radius of the blade diffuser.

[0022] Optionally, a cross section of the volute chamber is tangent to the casing.

[0023] Another aspect of the present application also provides an exhaust volute, the exhaust volute comprising a casing and a plurality of partitions, the plurality of partitions being arranged in the casing and connected and fixed to the casing through a stop structure, a volute chamber being formed between two adjacent partitions, the profile of the volute chamber being a curve, and when the cross section of the volute chamber is a square, the curve conforms to the formula:

[0024]

[0025] In the formula, r is the inlet radius of the volute at any angle around the casing; sis the inner cavity radius of the casing; x is the cross-sectional width of the volute;

[0026] The inner radius of the housing is r s Conforms to the formula:

[0027]

[0028] Wherein, x is the cross-sectional width of the volute chamber; is any angle of the casing circumference; M is a transition parameter;

[0029] Wherein, the transition parameter M conforms to the formula:

[0030]

[0031] In the formula, c ′ 4u is the inlet tangential airflow velocity of the housing; r ′ 4 is the inlet radius of the casing; Q ′ 4 is the volume flow at the inlet of the casing.

[0032] Optionally, a cross section of the volute chamber is perpendicular to the casing.

[0033] In another aspect of the present application, an exhaust volute is provided, the exhaust volute comprising a casing and a plurality of partitions, the plurality of partitions being arranged in the casing and connected and fixed to the casing through a stop structure, a volute chamber being formed between two adjacent partitions, the profile of the volute chamber being a curve, and when the cross section of the volute chamber is a rectangle, the curve conforms to the formula:

[0034]

[0035] In the formula, r is the inlet radius of the volute at any angle around the casing; s is the inner cavity radius of the casing; is any angle of the casing circumference; M is a transition parameter; L is the cross-sectional width of the volute chamber;

[0036] Wherein, the transition parameter M conforms to the formula:

[0037]

[0038] In the formula, c ′ 4u is the inlet tangential airflow velocity of the housing; r ′ 4 is the inlet radius of the casing; Q ′ 4 is the volume flow at the inlet of the casing.

[0039] Optionally, a cross section of the volute chamber is perpendicular to the casing.

[0040] In another aspect of the present application, a centrifugal compressor is provided, comprising the exhaust volute described in any one of the above.

[0041] By means of the above technical solution, the present application has at least the following beneficial effects:

[0042] The embodiments of the present application provide an exhaust volute and a centrifugal compressor, wherein the profile of the volute chamber in the exhaust volute adopts a curved design. Compared with the traditional design of the volute chamber with a simple geometric shape, the curved profile can well fit the internal spatial structure of the centrifugal compressor, thereby closely fitting the internal contour of the centrifugal compressor, avoiding the space waste that may be caused by the traditional simple geometric shape volute chamber, and effectively reducing the external dimensions of the centrifugal compressor. At the same time, when the gas after being pressurized and accelerated by the impeller of the centrifugal compressor enters the volute chamber, the curved profile conforms to the natural law of gas flow, which can make the gas flow smoother, thereby reducing the turbulence phenomenon in the airflow, reducing the energy loss caused by the turbulent airflow, and ensuring that the centrifugal compressor has good aerodynamic performance. BRIEF DESCRIPTION OF THE DRAWINGS

[0043] Figure 1 This is a schematic structural diagram of an exhaust volute of an optional embodiment of the present application;

[0044] Figure 2 This is a schematic diagram of the structure of the volute chamber at different circumferential angles of the casing of an optional embodiment of the present application;

[0045] Figure 3 for Figure 2 Cross-sectional view at AA in the middle.

[0046] The reference numerals are:

[0047] 1. Casing; 2. Partition; 3. Volute chamber. DETAILED DESCRIPTION

[0048] The preferred embodiments of the present application are described below in conjunction with the accompanying drawings. It should be understood that the preferred embodiments described herein are only used to illustrate and explain the present application and are not used to limit the present application.

[0049] See also Figures 1 to 3 As shown, an embodiment of the present application provides an exhaust volute, which includes a casing 1 and a plurality of partitions 2. The plurality of partitions 2 are arranged in the casing 1 and are connected and fixed to the casing 1 through a stop structure. A volute chamber 3 is formed between two adjacent partitions 2. The profile of the volute chamber 3 is a curve. When the cross section of the volute chamber 3 is circular, the curve conforms to the formula:

[0050]

[0051] In the formula, r is the inlet radius of the volute chamber 3 at any angle around the casing 1; s is the inner cavity radius of the casing 1; r is the cross-sectional radius of the volute chamber 3;

[0052] Among them, the cross-sectional radius r of the volute chamber 3 conforms to the formula:

[0053]

[0054] In the formula, is any angle around the housing 1; M is a transition parameter;

[0055] Among them, the transition parameter M conforms to the formula:

[0056]

[0057] In the formula, c ′ 4u is the inlet tangential airflow velocity of the housing 1; r ′ 4 is the inlet radius of the casing 1; Q ′ 4 is the volume flow at the inlet of the casing 1.

[0058] It should be noted that the inlet diameter of each cross section of the exhaust volute depends on the minimum inner diameter of the volute chamber 3 , and the shape of each cross section is determined by the volute chamber 3 .

[0059] In this embodiment, when the cross section of the volute chamber 3 is circular, by setting the profile of the volute chamber 3 to a curve that conforms to Formula 1, it can be well matched to the internal spatial structure of the centrifugal compressor, thereby closely fitting the internal contour of the centrifugal compressor, avoiding the space waste that may be caused by the volute chamber 3 of a traditional simple geometric shape, so that the external dimensions of the centrifugal compressor can be effectively reduced. At the same time, when the gas after being pressurized and accelerated by the impeller of the centrifugal compressor enters the volute chamber 3, the curved profile conforms to the natural law of gas flow, which can make the gas flow smoother, thereby reducing the turbulence phenomenon in the airflow, reducing the energy loss caused by the turbulent airflow, and ensuring that the centrifugal compressor has good aerodynamic performance.

[0060] Wherein, formula 1 is used to determine the inlet radius of the volute chamber 3 at different circumferential angles of the housing 1. It can be understood that determining the inlet radius of the volute chamber 3 at different circumferential angles of the housing 1 is very important for designing the shape and size of the volute chamber 3, because the inlet radius of the volute chamber 3 at different circumferential angles of the housing 1 affects the flow state of gas entering the volute chamber 3. Here, when the inlet radius of the volute chamber 3 at different circumferential angles of the housing 1 meets formula 1, it has good aerodynamic performance.

[0061] Wherein, Formula 2 is used to express the relationship between the cross-sectional radius of the volute chamber 3 and the circumferential angle and transition parameter of the housing 1. Here, Formula 2 can be used to calculate the cross-sectional radius of the volute chamber 3 at different positions according to different angles and transition parameters, thereby determining the specific shape of the volute chamber 3.

[0062] The transition parameter M in formula 3 is determined by the inlet tangential airflow velocity, inlet radius and volume flow rate at the inlet of the casing 1. Here, the transition parameter M plays a bridge role in the entire volute design, which is used to link the inlet characteristics of the airflow with the shape parameters of the volute chamber 3 to ensure that the design of the volute can adapt to specific airflow conditions.

[0063] In the above embodiment, the cross section of the volute chamber 3 is tangent to the casing 1 .

[0064] It should be noted that when the cross-section of the volute chamber 3 is tangent to the casing 1, the airflow can be smoother when entering the casing 1 from the volute chamber 3 or flowing between the two, reducing the energy loss caused by turbulence and vortices when the airflow encounters non-tangent discontinuous structures, thereby improving the aerodynamic efficiency of the centrifugal compressor exhaust system.

[0065] In the above embodiment, the exhaust volute further includes an impeller. When a vaneless diffuser is provided on the downstream side of the impeller in the flow direction, the exhaust volute satisfies the formula:

[0066]

[0067] In the formula, is the inlet radius of the casing 1 at 360 degrees in the circumferential direction of the casing 1; r2 is the outlet radius of the impeller.

[0068] It should be noted that Formula 4 is a limiting condition when the exhaust volute uses a vaneless diffuser after the impeller. Specifically, if the inlet radius of the casing 1 at 360 degrees does not satisfy Formula 4, the exhaust volute design scheme currently described will not be applicable.

[0069] In addition, when a bladeless diffuser is configured behind the impeller, the above-mentioned exhaust volute design is based on the following assumptions: the width of the bladeless diffuser remains consistent in the direction of gas flow; the gas flowing in the bladeless diffuser has the same airflow direction angle; there is no friction loss in the gas flowing in the casing 1, and the gas density is a constant value.

[0070] Furthermore, when the impeller is provided with a blade diffuser on the downstream side of the flow direction, the exhaust volute meets the formula:

[0071]

[0072] In the formula, is the inlet radius of the casing 1 at 360 degrees in the circumferential direction of the casing 1; r2 is the outlet radius of the blade diffuser.

[0073] It should be noted that when a vane diffuser structure is located behind the impeller, if the inlet radius of the casing 1 is greater than the outlet radius of the vane diffuser at 360 degrees, the above exhaust volute design is still applicable.

[0074] Here, taking a centrifugal compressor unit used in a methanol to olefins process as an example, the above exhaust volute design scheme is further explained in combination with specific numerical values.

[0075] According to the centrifugal compressor design specifications, the impeller diameter is known to be 510 mm, that is, r2 = 0.255 m; the inner cavity radius r of the casing 1 s =0.605m. According to the design parameter requirements, the numerical simulation method is used to calculate the aerodynamic parameters of the vaneless diffuser outlet, and r is selected. ′ 4=0.425m is used as the position for calculating the transition parameter M, and c ′ 4u =84.8m / s, Q ′ 4 = 2.268 m 3 / s, then according to formula 3, the transition parameter M=36023.15 can be calculated, and then the transition parameter M and are substituted into formula 2 to calculate the cross-sectional radius r of the volute 3 at different circumferential angles. Finally, according to formula 1, the inlet radius of the volute 3 at any circumferential angle of the housing 1 is calculated. The inlet radius values ​​of the volute 3 at any circumferential angle of the housing 1 are shown in Table 1:

[0076] Table 1

[0077]

[0078] At this time, according to formula 4, we can get Meet the exhaust volute design requirements.

[0079] Further, in order to fully illustrate the above exhaust volute design scheme, another exhaust volute is provided, the exhaust volute includes a casing 1 and a plurality of partitions 2, the plurality of partitions 2 are arranged in the casing 1, and are connected and fixed to the casing 1 through a stop structure, a volute chamber 3 is formed between two adjacent partitions 2, and the profile of the volute chamber 3 is a curve. When the cross section of the volute chamber 3 is a square, the curve meets the formula:

[0080]

[0081] In the formula, r is the inlet radius of the volute chamber 3 at any angle around the casing 1; s is the inner cavity radius of the casing 1; x is the cross-sectional width of the volute chamber 3;

[0082] Among them, the inner radius r of the housing 1 is s Conforms to the formula:

[0083]

[0084] Wherein, x is the cross-sectional width of the volute chamber 3; is any angle around the housing 1; M is a transition parameter;

[0085] Among them, the transition parameter M conforms to the formula:

[0086]

[0087] In the formula, c ′ 4u is the inlet tangential airflow velocity of the housing 1; r ′ 4 is the inlet radius of the casing 1; Q ′ 4 is the volume flow at the inlet of the casing 1.

[0088] In this embodiment, when the cross section of the volute chamber 3 is square, by setting the profile of the volute chamber 3 to a curve that conforms to Formula 6, it can also fit well with the internal spatial structure of the centrifugal compressor, thereby closely fitting the internal contour of the centrifugal compressor, avoiding the space waste that may be caused by the volute chamber 3 of a traditional simple geometric shape, so that the external dimensions of the centrifugal compressor can be effectively reduced. At the same time, when the gas after being pressurized and accelerated by the impeller of the centrifugal compressor enters the volute chamber 3, the curved profile conforms to the natural law of gas flow, which can make the gas flow smoother, thereby reducing the turbulence phenomenon in the airflow, reducing the energy loss caused by the turbulent airflow, and ensuring that the centrifugal compressor has good aerodynamic performance.

[0089] Among them, Formula 6 describes the relationship between the inlet radius of the volute chamber 3, the inner cavity radius of the housing 1, and the cross-sectional width of the volute chamber 3 when the cross section of the volute chamber 3 is square. It can be understood that it is very important to determine the inlet radius of the volute chamber 3 at different circumferential angles of the housing 1, and the inlet radius of the volute chamber 3 at different circumferential angles of the housing 1 affects the flow state of gas entering the volute chamber 3. Here, when the inlet radius of the volute chamber 3 at different circumferential angles of the housing 1 meets Formula 6, it has good aerodynamic performance.

[0090] Among them, Formula 7 is used to indicate that the inner cavity radius of the casing 1 is related to the cross-sectional width, transition parameters and related flow parameters of the volute chamber 3. Here, Formula 7 reflects how to determine the inner cavity radius of the casing 1 based on the consideration of the gas flow characteristics and the structure of the volute chamber 3 to ensure the smooth flow of gas in the volute.

[0091] The transition parameter M in formula 8 is determined by the inlet tangential airflow velocity, inlet radius and volume flow rate at the inlet of the casing 1. Here, the transition parameter M plays a bridging role in the design of the entire exhaust volute, which links the inlet characteristics of the airflow with the shape parameters of the volute chamber 3 to ensure that the design of the exhaust volute can adapt to specific airflow conditions.

[0092] In the above embodiment, the cross section of the volute chamber 3 is perpendicular to the casing 1 .

[0093] It should be noted that when the cross-section of the volute chamber 3 is perpendicular to the casing 1, it can ensure the consistency of the direction of the airflow when it transitions between the volute chamber 3 and the casing 1, reduce unnecessary directional changes of the airflow when passing through this area, and make the airflow enter the casing 1 more smoothly from the volute chamber 3, thereby reducing the energy loss of the airflow and improving the aerodynamic efficiency of the centrifugal compressor.

[0094] Further, in order to fully illustrate the above exhaust volute design scheme, another exhaust volute is provided, the exhaust volute includes a casing 1 and a plurality of partitions 2, the plurality of partitions 2 are arranged in the casing 1, and are connected and fixed to the casing 1 through a stop structure, a volute chamber 3 is formed between two adjacent partitions 2, and the profile of the volute chamber 3 is a curve. When the cross section of the volute chamber 3 is a rectangle, the curve meets the formula:

[0095]

[0096] In the formula, r is the inlet radius of the volute chamber 3 at any angle around the casing 1; s is the inner radius of the housing 1; is any angle of the casing 1 in the circumferential direction; M is the transition parameter; L is the cross-sectional width of the volute chamber 3;

[0097] Among them, the transition parameter M conforms to the formula:

[0098]

[0099] In the formula, c ′ 4u is the inlet tangential airflow velocity of the housing 1; r ′ 4 is the inlet radius of the casing 1; Q ′ 4 is the volume flow at the inlet of the casing 1.

[0100] In this embodiment, when the cross section of the volute chamber 3 is rectangular, by setting the profile of the volute chamber 3 to a curve that conforms to Formula 9, it can also fit well with the internal spatial structure of the centrifugal compressor, thereby closely fitting the internal contour of the centrifugal compressor, avoiding the space waste that may be caused by the volute chamber 3 of a traditional simple geometric shape, so that the external dimensions of the centrifugal compressor can be effectively reduced. At the same time, when the gas after being pressurized and accelerated by the impeller of the centrifugal compressor enters the volute chamber 3, the curved profile conforms to the natural law of gas flow, which can make the gas flow smoother, thereby reducing the turbulence phenomenon in the airflow, reducing the energy loss caused by the turbulent airflow, and ensuring that the centrifugal compressor has good aerodynamic performance.

[0101] Wherein, Formula 9 describes the relationship between the change of the inlet radius of the volute chamber 3 and the circumferential angle of the random shell 1 when the cross section of the volute chamber 3 is rectangular.

[0102] Specifically, the inner radius r of the housing 1 is s It is a basic structural dimension parameter, which determines the size of the internal space of the housing 1. The transition parameter M comprehensively reflects the inlet tangential airflow velocity c ′ 4u , inlet radius r ′ 4 and volume flow rate Q at the inlet ′ 4. These airflow parameters affect the size of the inlet radius of the volute chamber 3 through the transition parameter M. The cross-sectional width L of the volute chamber 3 also plays an important role in formula 9, which is related to the circumferential angle of the housing 1. Together they determine the specific values ​​of the inlet radius of the volute chamber 3 at different angles.

[0103] The transition parameter M in formula 10 is the inlet tangential airflow velocity c of the housing 1. ′ 4u , inlet radius r ′ 4 and volume flow rate Q at the inlet ′ 4 decided.

[0104] Specifically, the inlet tangential airflow velocity c ′ 4u It reflects the velocity characteristics of the airflow when it enters the housing 1, which is related to the inlet radius r ′ 4 together affect the state of the airflow entering the casing 1.

[0105] In the above embodiment, the cross section of the volute chamber 3 is also perpendicular to the casing 1 .

[0106] It should be noted that when the cross-section of the volute chamber 3 is perpendicular to the casing 1, it can ensure the consistency of the direction of the airflow when it transitions between the volute chamber 3 and the casing 1, reduce unnecessary directional changes of the airflow when passing through this area, and make the airflow enter the casing 1 more smoothly from the volute chamber 3, thereby reducing the energy loss of the airflow and improving the aerodynamic efficiency of the centrifugal compressor.

[0107] Furthermore, based on the fact that the cross-sections of the volute chamber 3 are respectively circular, square and rectangular, three types of exhaust volutes are obtained. Accordingly, the embodiment of the present application also provides a centrifugal compressor.

[0108] It is easy for those skilled in the art to understand that, under the premise of no conflict, the above-mentioned advantageous methods can be freely combined and superimposed.

[0109] The above are only preferred embodiments of the present application and are not intended to limit the present application. Any modifications, equivalent replacements and improvements made within the spirit and principles of the present application shall be included in the protection scope of the present application. The above are only preferred implementations of the present application. It should be pointed out that for ordinary technicians in this technical field, several improvements and variations can be made without departing from the technical principles of the present application, and these improvements and variations should also be regarded as the protection scope of the present application.

Claims

1. An exhaust volute, characterized in that: The exhaust volute comprises a casing (1) and a plurality of partitions (2), wherein the plurality of partitions (2) are arranged in the casing (1) and are connected and fixed to the casing (1) via a stop structure, and a volute chamber (3) is formed between two adjacent partitions (2), wherein the profile of the volute chamber (3) is a curve, and when the cross section of the volute chamber (3) is circular, the curve conforms to the formula: In the formula, is the inlet radius of the volute chamber (3) at any angle in the circumferential direction of the housing (1); r s is the inner cavity radius of the casing (1); r is the cross-sectional radius of the volute chamber (3); The cross-sectional radius r of the volute chamber (3) conforms to the formula: In the formula, is any angle in the circumferential direction of the housing (1); M is a transition parameter; Wherein, the transition parameter M conforms to the formula: In the formula, c ′ 4u is the inlet tangential airflow velocity of the housing (1); r ′ 4 is the inlet radius of the housing (1); Q ′ 4 is the volume flow at the inlet of the casing (1).

2. The exhaust volute according to claim 1, characterized in that: The exhaust volute further comprises an impeller. When a vaneless diffuser is provided on the downstream side of the impeller in the flow direction, the exhaust volute satisfies the formula: In the formula, is the inlet radius of the casing (1) at 360 degrees in the circumferential direction of the casing (1); and r2 is the outlet radius of the impeller.

3. The exhaust volute according to claim 2, characterized in that: The widths of the vaneless diffusers in the flow direction are the same, and the airflow direction angles of the gas flowing in the vaneless diffusers are the same.

4. The exhaust volute according to claim 1, characterized in that: The exhaust volute further comprises an impeller. When a blade diffuser is provided on the downstream side of the impeller in the flow direction, the exhaust volute satisfies the formula: In the formula, is the inlet radius of the casing (1) at 360 degrees in the circumferential direction of the casing (1); and r2 is the outlet radius of the blade diffuser.

5. The exhaust volute according to claim 1, characterized in that: The cross section of the volute chamber (3) is tangent to the casing (1).

6. An exhaust volute, characterized in that: The exhaust volute comprises a casing (1) and a plurality of partitions (2), wherein the plurality of partitions (2) are arranged in the casing (1) and are connected and fixed to the casing (1) via a stop structure, and a volute chamber (3) is formed between two adjacent partitions (2), wherein the profile of the volute chamber (3) is a curve, and when the cross section of the volute chamber (3) is a square, the curve conforms to the formula: In the formula, is the inlet radius of the volute chamber (3) at any angle in the circumferential direction of the housing (1); r s is the inner cavity radius of the casing (1); x is the cross-sectional width of the volute chamber (3); The inner radius r of the housing (1) is s Conforms to the formula: Wherein, x is the cross-sectional width of the volute chamber (3); is any angle in the circumferential direction of the housing (1); M is a transition parameter; Wherein, the transition parameter M conforms to the formula: In the formula, c ′ 4u is the inlet tangential airflow velocity of the housing (1); r ′ 4 is the inlet radius of the housing (1); Q ′ 4 is the volume flow at the inlet of the casing (1).

7. The exhaust volute according to claim 6, characterized in that: The cross section of the volute chamber (3) is perpendicular to the casing (1).

8. An exhaust volute, characterized in that: The exhaust volute comprises a casing (1) and a plurality of partitions (2), wherein the plurality of partitions (2) are arranged in the casing (1) and are connected and fixed to the casing (1) via a stop structure, and a volute chamber (3) is formed between two adjacent partitions (2), wherein the profile of the volute chamber (3) is a curve, and when the cross section of the volute chamber (3) is a rectangle, the curve conforms to the formula: In the formula, is the inlet radius of the volute chamber (3) at any angle in the circumferential direction of the housing (1); r s is the inner cavity radius of the casing (1); is any angle in the circumferential direction of the housing (1); M is a transition parameter; L is the cross-sectional width of the volute chamber (3); Wherein, the transition parameter M conforms to the formula: In the formula, c ′ 4u is the inlet tangential airflow velocity of the housing (1); r ′ 4 is the inlet radius of the housing (1); Q ′ 4 is the volume flow at the inlet of the casing (1).

9. The exhaust volute according to claim 8, characterized in that: The cross section of the volute chamber (3) is perpendicular to the casing (1).

10. A centrifugal compressor, characterized in that: Comprising the exhaust volute as described in any one of claims 1-9.

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