Centrifugal compressor and electrical equipment

Abstract

The utility model discloses a centrifugal compressor and electrical equipment. The centrifugal compressor comprises a driving structure, a compressor assembly and a compressor assembly, a first-stage compression space is formed in the first-stage volute, a second-stage compression space is formed in the second-stage volute, a first-stage impeller is arranged in the first-stage compression space, a second-stage impeller is arranged in the second-stage compression space, and the first-stage impeller and the second-stage impeller are connected to the two ends of the driving structure respectively; and the inter-stage pipeline assembly forms an inter-stage flow channel, the inter-stage flow channel communicates with the first-stage compression space and the second-stage compression space, and rectification blades are arranged in the inter-stage flow channel. According to the centrifugal compressor disclosed by the utility model, the rectifying blades are arranged in the interstage flow channel to rectify the gas, so that the rotation degree of the gas flow in the interstage flow channel can be reduced, the on-way energy loss of the fluid can be reduced, the flow field effect can be improved, the gas inlet efficiency and the compression efficiency of the secondary impeller can be improved, and the efficiency of the centrifugal compressor can be further improved.

Description

Technical Field

[0001] The utility model relates to the technical field of compressor manufacturing, in particular to a centrifugal compressor and electrical equipment with the centrifugal compressor. Background Art

[0002] In existing centrifugal compressors, in the process of gas flowing from the first-stage impeller to the second-stage impeller, the loss along the way will increase due to the long fluid path and small cross-sectional area, and the airflow rotates forward inside the flow channel, further increasing the loss along the way. At the same time, this rotating forward gas state affects the flow field effect of the second-stage impeller intake, thereby affecting the efficiency of the second-stage impeller, and thus affecting the efficiency of the compressor. Utility Model Content

[0003] The utility model aims to solve at least one of the technical problems existing in the prior art. To this end, the utility model proposes a centrifugal compressor, which can reduce the rotation degree of the airflow in the interstage flow channel, reduce the energy loss of the fluid along the flow, improve the flow field effect, so that the airflow can enter the secondary compression space more evenly and stably for compression, improve the air intake efficiency and compression efficiency of the secondary impeller, and thus improve the efficiency of the centrifugal compressor.

[0004] According to the centrifugal compressor of the embodiment of the utility model, it includes: a driving structure; a primary volute and a secondary volute, a primary compression space is formed in the primary volute, a secondary compression space is formed in the secondary volute, a primary impeller is provided in the primary compression space, a secondary impeller is provided in the secondary compression space, the primary impeller and the secondary impeller are respectively connected to the two ends of the driving structure; an interstage piping assembly, the interstage piping assembly forms an interstage flow channel, the interstage flow channel is respectively connected to the primary compression space and the secondary compression space, and a straightening blade is provided in the interstage flow channel.

[0005] According to the centrifugal compressor of the embodiment of the utility model, an interstage piping assembly is provided, and rectifying blades are provided in the interstage flow channel of the interstage piping assembly to rectify the gas that has passed through the first-stage compression space in the first-stage compression space, thereby reducing the degree of rotation of the airflow in the interstage flow channel, thereby reducing the degree of collision between the airflow and the pipe wall of the interstage piping assembly, reducing the energy loss of the fluid along the way, improving the flow field effect, allowing the airflow to enter the second-stage compression space more evenly and stably for compression, improving the air intake efficiency and compression efficiency of the second-stage impeller, and thereby improving the efficiency of the centrifugal compressor.

[0006] According to some embodiments of the centrifugal compressor of the present invention, the interstage piping assembly includes a first connecting flange, an interstage piping and a second connecting flange, the two ends of the interstage piping are respectively connected to the first connecting flange and the second connecting flange and jointly define the interstage flow channel, the first connecting flange is connected to the first volute, and the second connecting flange is connected to the second volute.

[0007] According to the centrifugal compressor of some embodiments of the present invention, the straightening blade is installed in the first connecting flange.

[0008] According to the centrifugal compressor of some embodiments of the present invention, there are multiple straightening blades, and the multiple straightening blades are distributed in the inter-stage flow passage at intervals around the axis of the inter-stage flow passage.

[0009] According to the centrifugal compressor of some embodiments of the utility model, the outer ends of the plurality of straightening blades are respectively connected to the inner walls of the interstage flow channel, the inner ends of the plurality of straightening blades are spaced apart to form a central flow hole in the interstage flow channel, and the extension lines of the inner ends of the plurality of straightening blades intersect the axis of the interstage flow channel.

[0010] According to the centrifugal compressor of some embodiments of the present invention, the width of the straightening blade in the axial direction of the inter-stage flow channel is arranged to gradually increase from the inner end to the outer end.

[0011] According to the centrifugal compressor of some embodiments of the present invention, the number of the rectifying blades is 3 to 12.

[0012] According to the centrifugal compressor of some embodiments of the present invention, the thickness of the rectifying blade is L, and satisfies: L≤2mm.

[0013] According to the centrifugal compressor of some embodiments of the utility model, the first-stage volute is provided with a first-stage axial air inlet and a first-stage radial air outlet connected to the first-stage compression space, the first-stage radial air outlet is connected to the inlet end of the interstage flow channel, and the second-stage volute is provided with a second-stage axial air inlet and a second-stage radial air outlet connected to the second-stage compression space, the second-stage axial air inlet is connected to the outlet end of the interstage flow channel.

[0014] The utility model also provides an electrical appliance.

[0015] The electrical equipment according to the embodiment of the utility model is provided with any one of the centrifugal compressors described above.

[0016] The advantages of the electrical equipment and the above-mentioned centrifugal compressor over the prior art are the same and will not be described in detail here.

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

[0018] The above and / or additional aspects and advantages of the present invention will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0019] Figure 1 It is a structural schematic diagram of a centrifugal compressor according to an embodiment of the utility model;

[0020] Figure 2 is a structural schematic diagram of an interstage pipeline assembly according to an embodiment of the utility model;

[0021] Figure 3 It is a cross-sectional view of an interstage piping assembly according to an embodiment of the utility model.

[0022] Reference numerals:

[0023] Centrifugal compressor 100,

[0024] Drive structure 1,

[0025] A first-stage volute 2, a first-stage compression space 21, a first-stage impeller 22, a first-stage axial air inlet 23, a first-stage radial air outlet 24,

[0026] Secondary volute 3, secondary compression space 31, secondary impeller 32, secondary axial air inlet 33, secondary radial air outlet 34,

[0027] Interstage pipeline assembly 4 , interstage flow channel 41 , first connecting flange 42 , flange recess 422 , straightening blade 421 , central flow hole 422 , second connecting flange 43 , interstage pipeline 44 . DETAILED DESCRIPTION

[0028] The embodiments of the present invention are described in detail below, and examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0029] In the description of the present utility model, it is necessary to understand that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate positions or positional relationships based on the positions or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present utility model and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present utility model. In addition, features defined as "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present utility model, unless otherwise specified, "multiple" means two or more.

[0030] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installation", "connection" and "connection" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0031] Reference below Figure 1-Figure 3 A centrifugal compressor 100 according to an embodiment of the utility model is described. The centrifugal compressor 100 can reduce the degree of rotation of the airflow in the interstage flow channel 41, reduce the energy loss of the fluid along the flow, improve the flow field effect, and enable the airflow to enter the secondary compression space 31 more evenly and stably for secondary compression, thereby improving the air intake efficiency and compression efficiency of the secondary impeller 32, thereby improving the efficiency of the centrifugal compressor 100.

[0032] like Figure 1-Figure 3 As shown, the centrifugal compressor 100 according to the embodiment of the utility model includes: a driving structure 1, a first-stage volute 2, a second-stage volute 3 and an inter-stage pipeline assembly 4.

[0033] The driving structure 1 is used to provide power to the centrifugal compressor 100, driving the primary impeller 22 and the secondary impeller 32 to operate, so that the centrifugal compressor 100 can operate normally and realize gas compression. In actual design, the driving mechanism can be a component such as a motor, and the rotation of the motor drives the primary impeller 22 and the secondary impeller 32 to rotate at high speed to realize gas compression and achieve the final required gas pressure. For example, the driving structure 1 includes a stator part and a rotor part, and the rotor part can rotate with the primary impeller 22 and the secondary impeller 32 to rotate with the rotor part.

[0034] A primary compression space 21 is formed in the primary volute 2, a secondary compression space 31 is formed in the secondary volute 3, a primary impeller 22 is arranged in the primary compression space 21, a secondary impeller 32 is arranged in the secondary compression space 31, and the primary impeller 22 and the secondary impeller 32 are respectively connected to the two ends of the driving structure 1, so that the driving structure 1 can drive the primary impeller 22 and the secondary impeller 32 to rotate. Among them, the rotor part can extend in the horizontal direction, and the primary impeller 22 and the secondary impeller 32 are respectively connected to the two ends of the rotor part, that is, the primary impeller 22 and the secondary impeller 32 are horizontally oppositely distributed at the two ends of the driving structure 1.

[0035] Specifically, the first-stage volute 2 and the second-stage volute 3 are respectively distributed on both sides of the driving structure 1. When the driving structure 1 starts to drive the first-stage impeller 22 to rotate at high speed, the gas is sucked into the first-stage compression space 21 and is thrown to the edge of the first-stage impeller 22 under the action of centrifugal force, so that the gas obtains kinetic energy, and its pressure and speed increase, thereby realizing the first-stage compression. The gas after the first-stage compression enters the second-stage compression space 31 through the interstage pipeline assembly 4 for the second-stage compression, wherein the second-stage impeller 32, driven by the driving structure 1, sucks the gas after the first-stage compression into the second-stage compression space 31 for compression again, and the gas pressure is further increased, thereby realizing the second-stage compression. Therefore, after the compression of the first-stage impeller 22 and the second-stage impeller 32, the gas pressure is increased.

[0036] Furthermore, the interstage pipeline assembly 4 is formed with an interstage flow channel 41 , which is connected to the first-stage compression space 21 and the second-stage compression space 31 respectively, and a rectifying blade 421 is provided in the interstage flow channel 41 .

[0037] That is to say, the gas after the first-stage compression in the first-stage compression space 21 can enter the interstage flow channel 41, circulate in the interstage flow channel 41, and then enter the second-stage compression space 31. During the gas circulation process, since the gas is a rotating forward airflow when it comes out of the first-stage compression space 21, it will collide with the pipe wall to cause losses along the way, affecting the flow field effect of the second-stage impeller 32 intake, thereby affecting the efficiency of the second-stage impeller 32 and the compression effect of the centrifugal compressor 100. Therefore, a rectifying blade 421 is provided in the interstage flow channel 41. The airflow coming out of the first-stage compression space 21 can be rectified by the rectifying blades 421, and the rotating forward airflow is adjusted to the flow direction of the inter-stage flow channel 41, that is, the flow direction of the gas is closer to laminar flow, thereby reducing the degree of rotation of the airflow, thereby reducing the degree of collision between the airflow and the pipe wall of the inter-stage pipeline assembly 4, reducing the energy loss of the fluid along the way, improving the flow field effect, and allowing the airflow to enter the second-stage impeller 32 more evenly and stably, thereby improving the intake efficiency and compression efficiency of the second-stage impeller 32, thereby improving the efficiency of the centrifugal compressor 100.

[0038] Therefore, by setting the rectifying blades 421, the horizontally opposed first-stage impeller 22 and second-stage impeller 32 can reduce the influence of the centrifugal force of the gas compressed by the first-stage impeller 22 on the intake efficiency and compression efficiency of the second-stage impeller 32 during the gas compression process, thereby improving the efficiency of the centrifugal compressor 100.

[0039] According to the centrifugal compressor 100 of the embodiment of the utility model, an interstage piping assembly 4 is provided, and a rectifying blade 421 is provided in the interstage flow channel 41 of the interstage piping assembly 4 to rectify the gas that has undergone the first-stage compression from the first-stage compression space 21, thereby reducing the degree of rotation of the airflow in the interstage flow channel 41, thereby reducing the degree of collision between the airflow and the pipe wall of the interstage piping assembly 4, reducing the energy loss of the fluid along the way, improving the flow field effect, and allowing the airflow to enter the secondary compression space 31 more evenly and stably for secondary compression, thereby improving the air intake efficiency and compression efficiency of the secondary impeller 32, thereby improving the efficiency of the centrifugal compressor 100.

[0040] In some embodiments, the interstage piping assembly 4 includes a first connecting flange 42, an interstage piping 44 and a second connecting flange 43. The two ends of the interstage piping 44 are respectively connected to the first connecting flange 42 and the second connecting flange 43 and jointly define an interstage flow channel 41. The first connecting flange 42 is connected to the first-stage volute 2, and the second connecting flange 43 is connected to the second-stage volute 3.

[0041] That is to say, the first-stage volute 2 is connected to the interstage pipeline 44 through the first connecting flange 42, and the second-stage volute 3 is connected to the interstage pipeline 44 through the second connecting flange, so that the first-stage volute 2, the interstage pipeline 44 and the second-stage volute 3 form a sealed structure, and the first connecting flange 42 and the second connecting flange 43 are respectively connected to the two ends of the interstage pipeline 44 to jointly define the interstage flow channel 41, so that the gas flowing out of the first-stage compression space 21 can smoothly enter the interstage pipeline 44 through the first connecting flange 42, circulate in the interstage flow channel 41 along the interstage pipeline 44, and finally flow into the secondary compression space 31 through the second connecting flange 43 to perform secondary compression again.

[0042] In actual design, at the connection between the first connecting flange 42 and the interstage pipeline 44, a flange recess 422 is provided on the first connecting flange 42, so that the first connecting flange 42 can be inserted into the flange recess 422 to be tightly connected with the interstage pipeline 44, thereby improving the tightness and reliability of the connection between the two and preventing gas leakage. The connecting end surfaces of the first connecting flange 42 and the flange recess 422 of the interstage pipeline 44 can be connected by welding to improve the connection strength. The provision of the flange recess 422 is conducive to welding between the two, and at the same time can ensure that there are no weld marks and welding slag in the interstage flow channel 41, with a smaller flow resistance, thereby improving the rectification effect of the airflow.

[0043] In some embodiments, the straightening blades 421 are installed in the first connecting flange 42 .

[0044] Specifically, the rectifying blades 421 are arranged in the first connecting flange 42, so that the airflow coming out of the first-stage compression space 21 can be rectified by the rectifying blades 421 in the first connecting flange 42, and the rotating forward airflow or turbulent airflow can be rectified into a stable airflow, thereby reducing the degree of rotation and turbulence of the airflow, making its flow field closer to laminar flow, and improving the flow field effect, thereby reducing the degree of collision with the pipe wall of the inter-stage pipeline 44, reducing airflow loss and energy loss along the way, providing good airflow conditions for the air intake of the secondary impeller 32, improving the air intake efficiency of the secondary impeller 32, and facilitating the secondary impeller 32 to work better and improve efficiency.

[0045] At the same time, since the rectified airflow reduces the impact and collision on the pipe wall of the interstage pipeline 44, the stability, reliability and durability of the interstage pipeline 44 can be improved, so that the interstage pipeline assembly 4 can work stably and its service life can be increased.

[0046] like Figure 2 and Figure 3 As shown, the straightening blade 421 is installed in the first connecting flange 42. In actual design, the first connecting flange 42 and the straightening blade 421 can be designed as a separate body, or processed together, that is, the two can be designed as an integrated whole to ensure the assembly accuracy between the first connecting flange 42 and the straightening blade 421, so that the airflow can flow more smoothly and reduce the loss of airflow. It can also improve the integrity and stability of the interstage pipeline assembly 4, withstand greater airflow impact, and be more conducive to straightening the airflow, thereby improving the straightening effect. At the same time, it can reduce the number of installation steps and improve efficiency.

[0047] In some embodiments, there is a plurality of straightening blades 421 , and the plurality of straightening blades 421 are spaced apart and distributed around the axis of the inter-stage flow passage 41 in the inter-stage flow passage 41 .

[0048] That is, the number of the straightening blades 421 can be set to two, three, four or even more, and multiple straightening blades 421 can be arranged in the interstage flow channel 41 and distributed at intervals around the axis of the interstage flow channel 41, so as to improve the straightening effect, make the airflow enter the interstage flow channel 41 more smoothly, and improve the effect of reducing the energy loss of the airflow.

[0049] In some embodiments, the outer ends of the plurality of straightening blades 421 are respectively connected to the inner walls of the interstage flow channel 41 , the inner ends of the plurality of straightening blades 421 are spaced apart to form a central flow hole 422 in the interstage flow channel 41 , and the extension lines of the inner ends of the plurality of straightening blades 421 intersect the axis of the interstage flow channel 41 .

[0050] Specifically, Figure 3As shown, the middle of the first connecting flange 42 is set to be hollow, which can reduce the flow resistance to the airflow, make the airflow pass through the rectifying blades 421 more smoothly, and increase the airflow flow rate, wherein a plurality of rectifying blades 421 are installed in the first connecting flange 42, and the outer ends thereof are connected to the inner wall of the interstage flow channel 41, and the plurality of rectifying blades 421 are distributed circumferentially along the interstage flow channel 41 so that the inner ends are spaced apart to form a central flow hole 422 in the interstage flow channel 41, so that the airflow can pass through the central flow hole 422 for rectification, and the extension lines of the inner ends of the plurality of rectifying blades 421 intersect the axis of the interstage flow channel 41, that is, the extension lines of the inner ends of the plurality of rectifying blades 421 converge on the same axis, which is coaxial with the axis of the interstage flow channel 41, so that the fluid flowing through the rectifying blades 421 can flow more smoothly, reduce flow resistance and energy loss, thereby improving the rectification efficiency, improving the stability of the airflow flow, and better reducing the degree of rotation of the gas.

[0051] In some embodiments, the axial width of the straightening blade 421 in the interstage flow channel 41 is set to gradually increase from the inner end to the outer end, that is, the closer the straightening blade 421 is to the axis of the interstage flow channel 41, the narrower its blade width is. In other words, the width of the straightening blade 421 along the direction of fluid flow gradually decreases.

[0052] like Figure 3 As shown, the axial width of the straightening blade 421 in the interstage flow channel 41 gradually increases from the inner end to the outer end. By gradually increasing the width of the straightening blade 421, the fluid can be more evenly distributed when passing through the interstage flow channel 41, so as to reduce the unevenness and rotation degree of the fluid, thereby improving the stability and flow efficiency of the fluid. Moreover, since the closer to the outer end of the interstage flow channel 41, the greater the rotation speed of the gas and the greater the impact, the width of the straightening blade 421 at the outer end is set to be larger, which can increase the contact area between the blade and the fluid, thereby further improving the straightening and compression capabilities of the straightening blade 421 for the fluid. At the same time, as the blade width gradually increases, the strength of the blade will also increase, which can better withstand the impact of the airflow with a larger speed at the outer end, which is beneficial to improving the reliability and durability of the straightening blade 421.

[0053] In actual design, the shape of the straightening blade 421 can be designed to be a trapezoid, a triangle, a fan, an ellipse, etc. Multiple straightening blades 421 can all be set to the same shape, for example, all are set to be trapezoidal, or all are set to be triangles, etc., or they can be set to a combination shape, for example, some are set to be trapezoidal, some are set to be triangles, etc., as long as the axial width of the interstage flow channel 41 gradually increases from the inner end to the outer end, and the specific shape can be flexibly selected according to the actual situation.

[0054] In some embodiments, the number of the straightening blades 421 is 3 to 12, that is, the number of the straightening blades 421 can be set to 3, 5, 10, 12 or other numbers.

[0055] Since wider blades will increase the resistance of the fluid, the number of blades can be set to be smaller to improve the straightening effect. Therefore, by setting the number of straightening blades 421 to 3 to 12, the resistance of the straightening blades 421 to the fluid can be reduced, allowing the fluid to flow smoothly through the straightening blades 421, thereby improving the compression efficiency of the centrifugal compressor 100.

[0056] In actual design, chamfers can be set on multiple edges of the rectifying blade 421, and the side of the rectifying blade 421 connected to the inner wall of the interstage flow channel 41 does not need to be set. Setting a chamfer can improve the flow field of the airflow when entering and exiting the rectifying blade 421, further reduce flow resistance, make the airflow flow more smoothly, and improve rectification efficiency.

[0057] In some embodiments, the thickness of the rectifying blade 421 is L, and satisfies: L≤2 mm, that is, the thickness of the rectifying blade 421 can be set to 1 mm, 1.5 mm, 2 mm or other thicknesses.

[0058] Since the thickness of the rectifying blade 421 has a certain influence on the flow efficiency of the airflow, the thicker the rectifying blade 421, the greater the resistance to the airflow and the increased weight; the thinner the rectifying blade 421, the lower its strength and rigidity will be, and it cannot withstand the impact of the airflow well. Therefore, the thickness of the rectifying blade 421 is reasonably set to L≤2mm. Such a setting can not only reduce the flow resistance of the rectifying blade 421 to the airflow and improve the flow efficiency of the airflow, but also enable the rectifying blade 421 to maintain sufficient strength and rigidity, improve its stability, withstand the impact of the fluid, extend its life, and thus better rectify the airflow and improve the rectification effect.

[0059] It can be understood that the larger the value of L is set, the thicker the thickness of the straightening blade 421 is, and the smaller the value of L is set, the thinner the thickness of the straightening blade 421 is. In the actual design, the thickness of the straightening blade 421 can be flexibly adjusted according to actual conditions and is not limited to what is described in this embodiment.

[0060] In some embodiments, the first-stage volute 2 is provided with a first-stage axial air inlet 23 and a first-stage radial air outlet 24 connected to the first-stage compression space 21, and the first-stage radial air outlet 24 is connected to the inlet end of the inter-stage flow channel 41. The second-stage volute 3 is provided with a second-stage axial air inlet 33 and a second-stage radial air outlet 34 connected to the second-stage compression space 31, and the second-stage axial air inlet 33 is connected to the outlet end of the inter-stage flow channel 41.

[0061] That is to say, the gas can enter the primary compression space 21 through the primary axial air inlet 23 for primary compression, and the gas that has undergone primary compression can flow out through the primary radial air outlet 24 and enter the interstage flow channel 41 for rectification. After passing through the interstage flow channel 41, the gas flows out from the outlet end of the interstage flow channel 41, and then enters the secondary compression space 31 through the secondary axial air inlet 33 for secondary compression, thereby completing the compression of the gas from the primary stage to the secondary stage.

[0062] Specifically, Figure 1 As shown, the first-stage volute 2 is provided with a first-stage axial air inlet 23 and a first-stage radial air outlet 24, the second-stage volute 3 is provided with a second-stage axial air inlet 33 and a second-stage radial air outlet 34, and the first-stage compression space 21 and the second-stage compression space 31 are connected through the interstage flow channel 41 of the interstage pipeline assembly 4, so that the gas after the first-stage compression can be rectified and then subjected to the second-stage compression.

[0063] It should be noted that the straightening blades 421 can also be arranged at the first-stage radial air outlet 24 of the first-stage volute 2, and can also realize the rectification of the gas after the first-stage compression. In the actual design, the straightening blades 421 can be cast or processed at the first-stage radial air outlet 24, as long as the function of rectifying the gas after the first-stage compression can be realized.

[0064] The utility model also provides an electrical appliance.

[0065] According to the electrical equipment of the embodiment of the utility model, a centrifugal compressor 100 of any one of the above-mentioned embodiments is provided. In the centrifugal compressor 100, an interstage pipeline assembly 4 is provided, and a rectifying blade 421 is provided in the interstage flow channel 41 of the interstage pipeline assembly 4 to rectify the gas that has undergone the first-stage compression from the first-stage compression space 21, thereby reducing the degree of rotation of the airflow in the interstage flow channel 41, thereby reducing the degree of collision between the airflow and the pipe wall of the interstage pipeline assembly 4, reducing the energy loss of the fluid along the way, improving the flow field effect, and allowing the airflow to enter the secondary compression space 31 more evenly and stably for secondary compression, thereby improving the air intake efficiency and compression efficiency of the secondary impeller 32, thereby improving the efficiency of the centrifugal compressor 100.

[0066] According to the electrical equipment of the embodiment of the utility model, the efficiency of the electrical equipment can be improved and its reliability can be improved by disposing the centrifugal compressor 100 with the rectifying blades 421 in the interstage flow passage 41 .

[0067] In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "illustrative embodiments", "examples", "specific examples", or "some examples" means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the utility model. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.

[0068] Although the embodiments of the present invention have been shown and described, those skilled in the art will appreciate that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and spirit of the present invention, and that the scope of the present invention is defined by the claims and their equivalents.

Claims

1. A centrifugal compressor, characterized in that: include: Drive structure; A primary volute and a secondary volute, wherein a primary compression space is formed in the primary volute, and a secondary compression space is formed in the secondary volute. A primary impeller is arranged in the primary compression space, and a secondary impeller is arranged in the secondary compression space. The primary impeller and the secondary impeller are respectively connected to two ends of the driving structure; An interstage pipeline assembly is formed with an interstage flow passage, the interstage flow passage is respectively connected with the first-stage compression space and the second-stage compression space, and a rectifying blade is arranged in the interstage flow passage.

2. The centrifugal compressor according to claim 1, characterized in that: The interstage pipeline assembly includes a first connecting flange, an interstage pipeline, and a second connecting flange. The two ends of the interstage pipeline are respectively connected to the first connecting flange and the second connecting flange and jointly define the interstage flow channel. The first connecting flange is connected to the first-stage volute, and the second connecting flange is connected to the second-stage volute.

3. The centrifugal compressor according to claim 2, characterized in that: The rectifying blade is installed in the first connecting flange.

4. The centrifugal compressor according to any one of claims 1 to 3, characterized in that: There are a plurality of straightening blades, and the plurality of straightening blades are distributed in the inter-stage flow passage at intervals around the axis of the inter-stage flow passage.

5. The centrifugal compressor according to claim 4, characterized in that: The outer ends of the plurality of straightening blades are respectively connected to the inner walls of the interstage flow passage, the inner ends of the plurality of straightening blades are spaced apart to form a central flow hole in the interstage flow passage, and the extension lines of the inner ends of the plurality of straightening blades intersect the axis of the interstage flow passage.

6. The centrifugal compressor according to claim 5, characterized in that: The width of the straightening blade in the axial direction of the inter-stage flow passage is configured to gradually increase from the inner end to the outer end.

7. The centrifugal compressor according to claim 4, characterized in that: The number of the rectifying blades is 3 to 12.

8. The centrifugal compressor according to any one of claims 1 to 3, characterized in that: The thickness of the rectifying blade is L, and satisfies: L≤2mm.

9. The centrifugal compressor according to any one of claims 1 to 3, characterized in that: The first-stage volute is provided with a first-stage axial air inlet and a first-stage radial air outlet connected to the first-stage compression space, and the first-stage radial air outlet is connected to the inlet end of the inter-stage flow channel. The second-stage volute is provided with a second-stage axial air inlet and a second-stage radial air outlet connected to the second-stage compression space, and the second-stage axial air inlet is connected to the outlet end of the inter-stage flow channel.

10. An electrical device, characterized in that: A centrifugal compressor according to any one of claims 1 to 9 is provided.

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