CN112160939A - Compressor channel and compressor - Google Patents
Compressor channel and compressor Download PDFInfo
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- CN112160939A CN112160939A CN202011238374.9A CN202011238374A CN112160939A CN 112160939 A CN112160939 A CN 112160939A CN 202011238374 A CN202011238374 A CN 202011238374A CN 112160939 A CN112160939 A CN 112160939A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
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Abstract
本发明涉及一种压缩机流道及压缩机。该压缩机流道包括扩压器、弯道和回流器，弯道连通扩压器和回流器；扩压器具有相对的第一内侧壁和第一外侧壁，弯道具有相对的第二内侧壁和第二外侧壁，回流器具有相对的第三内侧壁和第三外侧壁；第二内侧壁包括依次连接的第一内侧弧壁段、内侧直壁段和第二内侧弧壁段，第二外侧壁包括依次连接的第一外侧弧壁段、外侧直壁段和第二外侧弧壁段，内侧直壁段和外侧直壁段在压缩机流道的流道截面上的投影呈直线；第一内侧弧壁段和第一外侧弧壁段分别与第一内侧壁和第一外侧壁连接，第二内侧弧壁段和第二外侧弧壁段分别与第三内侧壁和第三外侧壁连接。本发明能有效改善叶轮进口气流条件和做功能力，降低能量消耗。
The invention relates to a compressor flow channel and a compressor. The compressor flow channel includes a diffuser, a bend and a returner, and the bend communicates with the diffuser and the returner; the diffuser has opposite first inner side walls and first outer side walls, and the bend has a second opposite inner side wall and second outer side wall, the reflux device has a third inner side wall and a third outer side wall opposite; the second inner side wall comprises a first inner side arc wall segment, an inner straight wall segment and a second inner side arc wall segment connected in sequence, the first The two outer side walls include a first outer arc wall section, an outer straight wall section and a second outer arc wall section which are connected in sequence, and the projections of the inner straight wall section and the outer straight wall section on the flow channel section of the compressor flow channel are straight lines; The first inner arc wall segment and the first outer arc wall segment are respectively connected with the first inner side wall and the first outer side wall, and the second inner arc wall segment and the second outer arc wall segment are respectively connected with the third inner side wall and the third outer side wall. connect. The invention can effectively improve the air flow condition and working capacity of the impeller inlet, and reduce energy consumption.
Description
Technical Field
The invention relates to the technical field of compressors, in particular to a compressor flow channel and a compressor.
Background
In the multistage centrifugal compressor, airflow enters a bend after being diffused in a diffuser, enters a reflux device after turning 180 degrees in the bend, and the airflow flowing out of the diffuser is introduced into the next stage as uniformly as possible by the reflux device. In the prior art, the inner side wall of the curve and the outer side wall of the curve usually adopt a concentric circle structure to form an airflow channel, and at this time, the mode has larger energy loss when the airflow passes through the curve.
Inner container of the invention
The invention provides a compressor flow channel and a compressor aiming at the problem of large energy loss of airflow passing through a bend, and the compressor flow channel and the compressor have the technical effects of small energy loss, high working efficiency and good working stability.
A compressor flow channel comprises a diffuser, a bend and a reflux device, wherein the diffuser and the reflux device are oppositely arranged, an inlet of the bend is communicated with an outlet of the diffuser, and an outlet of the bend is communicated with an inlet of the reflux device;
the diffuser has first and second opposite inner and outer side walls, the bend has second and second opposite outer side walls, and the return has third and third opposite inner and outer side walls;
the second inner side wall comprises a first inner side arc wall section, an inner side straight wall section and a second inner side arc wall section which are connected in sequence, the second outer side wall comprises a first outer side arc wall section, an outer side straight wall section and a second outer side arc wall section which are connected in sequence, and projections of the inner side straight wall section and the outer side straight wall section on a flow passage section of the compressor flow passage are straight lines;
the first inner arc wall section and the first outer arc wall section are respectively connected with the first inner side wall and the first outer side wall, and the second inner arc wall section and the second outer arc wall section are respectively connected with the third inner side wall and the third outer side wall.
In one embodiment, a projection of the inner straight wall section on the flow passage section is a first transverse straight line, a projection of the outer straight wall section on the flow passage section is a second transverse straight line, the second transverse straight line is parallel to a central axis of the compressor, and an included angle between an extension line of the first transverse straight line and the central axis is-20 degrees to-20 degrees.
In one embodiment, a projection of the third inner side wall on the flow passage section is a first vertical line, a projection of the third outer side wall on the flow passage section is a second vertical line, and an included angle between an extension line of the first vertical line and the central axis and an included angle between an extension line of the second vertical line and the central axis are both between 70 ° and 90 °.
In one embodiment, an included angle between an extension line of the first vertical line and an extension line of the second vertical line is between 0 ° and 20 °.
In one embodiment, an extension line of the first vertical line and an extension line of the second vertical line are both perpendicular to a central axis of the compressor.
In one embodiment, an extension of the first vertical line is at an acute angle to the central axis, and an extension of the second vertical line is perpendicular to the central axis.
In one embodiment, the first inner side wall and the first inner side arc wall section, the first inner side arc wall section and the inner side straight wall section, the inner side straight wall section and the second inner side arc wall section, and the second inner side arc wall section and the third inner side wall are all tangent-connected or smoothly transitionally-connected;
the first outer side wall and the first outer side wall section, the first outer side wall section and the outer side straight wall section, the outer side straight wall section and the second outer side wall section, and the second outer side wall section and the third outer side wall are all in tangent connection or smooth transition connection.
In addition, the embodiment of the invention also provides a compressor, which is provided with the compressor flow channel in any embodiment.
In one embodiment, the compressor has multiple stages of the compressor flow passages, the multiple stages of the compressor flow passages are sequentially communicated, and an inlet of the diffuser of the subsequent stage of the compressor flow passage is communicated with an outlet of the reflux device of the previous stage of the compressor flow passage.
In one embodiment, the compressor is a single cantilever compressor.
The compressor runner, the bend, includes a first turning runner formed by a first inner side arc wall section and a first outer side arc wall section, a direct runner formed by an inner side straight wall section and an outer side straight wall section, and a second turning runner formed by a second inner side arc wall section and a second outer side arc wall section. When the airflow enters the curved channel through the diffuser outlet after being diffused by the diffuser, the airflow sequentially passes through the first turning flow channel, the straight flow channel and the second turning flow channel and finally enters the flow channel of the reflux device. When the airflow passes through the first turning flow channel, the airflow direction deflects 90 degrees along the clockwise (or anticlockwise) direction, when the airflow passes through the straight flow channel, the airflow direction basically keeps unchanged, and when the airflow passes through the second turning flow channel, the airflow direction deflects 90 degrees along the clockwise (or anticlockwise) direction, so that the airflow can turn 180 degrees on the inner side of the curve.
Compared with the prior art, the method can reduce the channel diffusion degree of the front half part of the curve and the local diffusion degree near the inner side wall of the outlet of the curve, reduce the pressure loss of the air flow at the inner side of the curve, avoid the air flow from generating larger separation loss at the inner side wall of the outlet of the curve, further effectively improve the inlet air flow condition and the working capacity of the next-stage impeller, reduce the energy consumption of the compressor, and improve the working efficiency and the stability of the compressor. In addition, the structure of the curve can be flexibly adjusted by increasing or decreasing the length of the straight flow passage so as to adapt to the actual running condition of the compressor.
Drawings
FIG. 1 is a schematic view of a compressor flow channel according to an embodiment of the present invention;
fig. 2 is a schematic structural diagram of a compressor flow channel according to another embodiment of the present invention.
Description of reference numerals:
a diffuser 1; a first inner side wall 11; a first outer side wall 12; a bend 2; a second inner side wall 21; a first inner side arc wall section 211; an inner straight wall section 212; a second inner arc wall section 213; a second exterior side wall 22; a first outer arc wall section 221; an outer straight wall section 222; a second outer sidewall segment 223; a reflux vessel 3; a third inner side wall 31; a third outer side wall 32; a central axis 4.
Detailed Description
In order to make the aforementioned objects, features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in detail below. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention. This invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein.
In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicate orientations and positional relationships based on those shown in the drawings, and are used merely for convenience of description and for simplicity of description, and do not indicate or imply that the device or element so referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be considered as limiting the present invention.
The terms "first" and "second" are used herein for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise.
In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; they may be directly connected or indirectly connected through intervening media, or they may be. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
In the present invention, unless otherwise expressly stated or limited, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through an intermediate. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.
It will be understood that when an element is referred to as being "secured to" or "disposed on" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and the like as used herein are for illustrative purposes only and do not denote a unique embodiment.
Referring to fig. 1, an embodiment of the present invention provides a compressor flow channel, including a diffuser, a curved conduit 2 and a backflow device 3, where the diffuser and the backflow device 3 are arranged oppositely, an inlet of the curved conduit 2 is communicated with an outlet of the diffuser, and an outlet of the curved conduit 2 is communicated with an inlet of the backflow device 3; the diffuser is provided with a first inner side wall 11 and a first outer side wall 12 which are opposite, the bend 2 is provided with a second inner side wall 21 and a second outer side wall 22 which are opposite, and the return device 3 is provided with a third inner side wall 31 and a third outer side wall 32 which are opposite; the second inner side wall 21 comprises a first inner side arc wall section 211, an inner side straight wall section 212 and a second inner side arc wall section 213 which are connected in sequence, the second outer side wall 22 comprises a first outer side arc wall section 221, an outer side straight wall section 222 and a second outer side arc wall section 223 which are connected in sequence, and the projections of the inner side straight wall section 212 and the outer side straight wall section 222 on the section of the flow passage of the compressor are straight lines; the first inner and outer arc wall sections 211 and 221 are connected to the first inner and outer sidewalls 11 and 12, respectively, and the second inner and outer arc wall sections 213 and 223 are connected to the third inner and outer sidewalls 31 and 32, respectively.
It is understood that the first inner sidewall 11 and the first outer sidewall 12 form a diffuser flow passage; the second inner side wall 21 and the second outer side wall 22 form a curved flow passage; the third inner side wall 31 and the third outer side wall 32 form a reflux device flow channel; the compressor flow passage is formed when the first inner and outer arc wall sections 211 and 221 are connected to the first inner and outer side walls 11 and 12, respectively, and the second inner and outer arc wall sections 213 and 223 are connected to the third inner and outer side walls 31 and 32, respectively.
The diffuser, the curve 2, and the reflux unit 3 are flow passages through which air flows, the inner wall is a flow passage wall surface close to the central axis 4 of the compressor, the outer wall is a flow passage wall surface far from the central axis 4 of the compressor, the central axis 4 of the compressor is the central axis 4 of the main shaft of the compressor, and the impeller, the diffuser, the curve 2, and the reflux unit 3 of the compressor all have the central axis 4 of the compressor as installation axes. The flow passage cross section of the compressor flow passage is a cross section through the central axis 4 of the compressor.
The curve 2 includes a first curve flow path formed by the first inner side arc wall section 211 and the first outer side arc wall section 221, a direct flow path formed by the inner side straight wall section 212 and the outer side straight wall section 222, and a second curve flow path formed by the second inner side arc wall section 213 and the second outer side arc wall section 223. When the airflow enters the bend 2 through the diffuser outlet after being diffused by the diffuser, the airflow sequentially passes through the first turning flow channel, the straight flow channel and the second turning flow channel and finally enters the flow channel of the reflux device. When the airflow passes through the first turning flow channel, the airflow direction deflects 90 degrees along the clockwise (or anticlockwise) direction, when the airflow passes through the straight flow channel, the airflow direction basically keeps unchanged, and when the airflow passes through the second turning flow channel, the airflow direction deflects 90 degrees along the clockwise (or anticlockwise) direction, so that the airflow can complete 180-degree turning at the inner side of the bend 2.
Due to the design of the straight flow channel, compared with the prior art, the turning radian at the inlet of the bend 2 and the turning radian at the outlet of the bend 2 can be reduced, thereby avoiding the situation that the air flow turns too fast at the inner side of the bend 2, reducing the channel diffusion degree of the front half part of the bend 2 and the local diffusion degree near the inner side wall of the outlet of the bend 2, reducing the pressure loss of the air flow at the inner side of the bend 2, avoiding the air flow from generating larger separation loss at the inner side wall of the outlet of the bend 2, further effectively improving the inlet air flow condition and the work-doing capacity of the next-stage impeller, reducing the energy consumption of the compressor, and improving the working efficiency and the. In addition, the structure of the curve 2 can be flexibly adjusted by increasing or decreasing the length of the straight flow passage so as to adapt to the actual operation condition of the compressor.
It is understood that the projections of the four wall surfaces of the first inner side wall segment 211, the first outer side wall segment 221, the second inner side wall segment 213 and the second outer side wall segment 223 of the curve 2 on the flow passage section are all arcs.
Alternatively, referring to fig. 1 and 2, the first inner side arc wall section 211, the second inner side arc wall section, the first outer side arc wall section 221, and the second outer side arc wall section 223 are arc sections, and the radius of curvature of the first inner side arc wall section 211, the second inner side arc wall section, the first outer side arc wall section 221, and the second outer side arc wall section 223 is larger than the radius of curvature of the prior art when the curve 2 adopts a concentric structure, that is, the turning radian at the inlet of the curve 2 and the turning radian at the outlet.
Further, the compressor flow passage is a revolving structure in which the central axis 4 of the compressor is a rotating shaft, that is, the diffuser, the curve 2 and the return passage are formed to rotate with the central axis 4 of the compressor as a center line.
In an alternative embodiment, the projection of the inner straight-wall section 212 on the flow passage cross section is a first horizontal straight line, the projection of the outer straight-wall section 222 on the flow passage cross section is a second horizontal straight line, the second horizontal straight line is parallel to the central axis 4 of the compressor, and the extension line of the first horizontal straight line forms an included angle of-20 degrees to 20 degrees with the central axis 4 of the compressor. In this case, the compressor can be adapted to different compressor models according to the change in the diameter of the straight passage formed by the first horizontal straight line and the second horizontal straight line.
Alternatively, referring to fig. 2, the first horizontal line and the second horizontal line are parallel, i.e. both parallel to the central axis 4 of the compressor, and the velocity of the gas in the straight flow channel is not changed, so that the compressor is suitable for models with moderate flow rate.
Optionally, the included angle between the extension line of the first transverse straight line and the central axis 4 of the compressor is-20 degrees to 0 degrees (excluding 0 degrees), and the straight flow channel gradually shrinks along the flowing direction of the airflow; when the air compressor is used, the air flow rate can be increased, the air compressor is suitable for models with small flow rate, and the work efficiency of the compressor is improved.
In actual use, the extension line of the first transverse straight line may form an angle of-15 °, -10 °, -5 °, or-1 °, etc., with the central axis 4 of the compressor.
Alternatively, referring to fig. 1, an included angle between an extension line of the first transverse straight line and the central axis 4 of the compressor is 0 ° to 20 ° (excluding 0 °), and at this time, the straight flow passage is gradually expanded along the flow direction of the gas flow, so that the gas flow velocity can be reduced, and the compressor is suitable for a machine type with a large flow velocity, and is helpful for pressurization.
In actual use, the angle between the extension line of the first horizontal line and the central axis 4 of the compressor may be 15 °, 10 °, 5 °, 1 °, or the like.
In an alternative embodiment, referring to fig. 1 and fig. 2, the projection of the third inner sidewall 31 on the flow channel cross section is a first vertical line, the projection of the third outer sidewall 32 on the flow channel cross section is a second vertical line, and both the included angle between the extension line of the first vertical line and the central axis 4 of the compressor and the included angle between the extension line of the second vertical line and the central axis 4 of the compressor are 70-90 °. And the different compressor models can be adapted according to the drift diameter change of the return channel formed by the first vertical line and the second vertical line. When the included angle between the extension line of the first vertical line and the central axis 4 of the compressor and the included angle between the extension line of the second vertical line and the central axis 4 of the compressor are both 70-90 degrees, the airflow flowing into the reflux device 3 through the bend 2 can uniformly flow to the impeller of the next stage.
Optionally, an included angle between an extension line of the first vertical line and an extension line of the second vertical line is between 0 ° and 20 °, and the first vertical line and the second vertical line include two arrangement relationships, one arrangement relationship is that the first vertical line and the second vertical line are parallel, and the other arrangement relationship is that an acute angle is formed between the extension line of the first vertical line and the extension line of the second vertical line.
Referring to fig. 1, when the included angle between the first vertical line and the second vertical line is 0 °, that is, the first vertical line is parallel to the second vertical line, the drift diameter of the flow channel formed by the first vertical line and the second vertical line is not changed, and the speed of the air flow is kept unchanged when the air flow passes through the reflux unit 3. Preferably, the first vertical line and the second vertical line are both perpendicular to the central axis 4 when being parallel, which is helpful to reduce the turning radian and energy loss when the air flows through the return device 3 to the bottom impeller.
Referring to fig. 2, when an acute angle is formed between the extension line of the first vertical line and the extension line of the second vertical line, the first vertical line and the second vertical line form a flow passage with a gradually increasing drift diameter, that is, the reflux device 3 gradually expands, so that the flow rate of the airflow is reduced, the pressure is increased, and at this time, the reflux device 3 has a certain diffusion function, so as to adapt to the condition that the reflux device 3 needs to diffuse, for example, when the flow rate of the compressor is high, the energy utilization rate of the compressor is improved.
In actual use, an extension line of the second vertical line may be made perpendicular to the central axis 4 of the compressor, and an extension line of the first vertical line may be made at an acute angle, for example, 75 °, 77 °, 80 °, 85 °, 88 °, or the like, with respect to the central axis 4 of the compressor. At the moment, the optimization and improvement of the structure part of the existing diffuser are not needed, and the design period is shortened; meanwhile, the weight of the compressor is reduced, and the lightweight design of the compressor is realized.
Further, a blade (not shown) is disposed on the reflux unit 3, the blade is disposed at an outlet of the reflux unit 3, one end of the blade is connected to an outer side wall of the reflux unit 3, and the other end of the blade extends toward an inner side wall of the reflux unit 3 with a gap therebetween. The vanes of the reflux unit 3 may be those of the prior art, and the vane structure of the reflux unit 3 is not limited thereto.
The blades are arranged at the outlet of the reflux device 3, so that the airflow at the outlet of the reflux device 3 is as uniform as possible, and the problem of gas prewhirl when the gas enters the inlet of the next-stage impeller is avoided.
Preferably, the first inner side wall 11 and the first inner side arc-shaped wall section 211, the first inner side arc-shaped wall section 211 and the inner side straight-wall section 212, the inner side straight-wall section 212 and the second inner side arc-shaped wall section 213, and the second inner side arc-shaped wall section 213 and the third inner side wall are all connected tangentially or in a smooth transition manner, so as to avoid the unevenness of the connection part from affecting the pneumatic performance of the compressor.
Further, the first outer side wall 12 and the first outer side arc wall section 221, the first outer side arc wall section 221 and the outer side straight wall section 222, the outer side straight wall section 222 and the second outer side arc wall section 223, and the second outer side arc wall section 223 and the third outer side wall 32 are all connected tangentially or in a smooth transition manner, so as to avoid unevenness at the connection from affecting the aerodynamic performance of the compressor.
According to the compressor flow channel provided by the embodiment of the invention, by optimizing the structure of the curve 2, the second inner side wall 21 of the curve 2 comprises a first inner side arc wall section 211, an inner side straight wall section 212 and a second inner side arc wall section 213 which are connected in sequence, the second outer side wall 22 of the curve 2 comprises a first outer side arc wall section 221, an outer side straight wall section 222 and a second outer side arc wall section 223 which are connected in sequence, and the projections of the inner side straight wall section 212 and the outer side straight wall section 222 on the flow channel section of the compressor are straight lines. Compared with the prior art, the compressor flow channel in the embodiment of the invention can reduce the turning radian at the inlet of the curve 2 and the turning radian at the outlet of the curve 2, thereby avoiding the condition that airflow turns too fast at the inner side of the curve 2, reducing the channel diffusion degree of the front half part of the curve 2 and the local diffusion degree near the inner side wall of the outlet of the curve 2, reducing the pressure loss of the airflow at the inner side of the curve 2, avoiding the airflow from generating larger separation loss at the inner side wall of the outlet of the curve 2, further effectively improving the inlet airflow condition and the work-doing capacity of a next-stage impeller, reducing the energy consumption of the compressor, and improving the working efficiency and the stability of the compressor. In addition, the structure of the curve 2 can be flexibly adjusted by increasing or decreasing the length of the straight flow passage so as to adapt to the actual operation condition of the compressor.
In addition, an embodiment of the present invention further provides a compressor (not shown), which has a compressor flow channel as described in any of the above embodiments. Since the compressor has the compressor flow passage, the compressor has all the advantages of the compressor flow passage, which are not described herein.
In an alternative embodiment, the compressor is a multi-stage compressor having a plurality of compressor flow passages, the plurality of compressor flow passages are sequentially communicated, and an inlet of a diffuser of a subsequent compressor flow passage is communicated with an outlet of the reflux unit 3 of a previous compressor flow passage.
Optionally, in an airflow path structure of the compressor, an impeller is arranged at a communication position of adjacent two-stage compressor runners, an inlet end of the impeller is communicated with an outlet of the previous-stage reflux device 3, and an outlet end of the impeller is communicated with an inlet of the next-stage diffuser; an impeller is arranged at the inlet of the first-stage compressor flow passage, and the outlet of the impeller is communicated with the inlet of a diffuser of the first compressor flow passage; the outlet of the last stage compressor flow passage is connected with a volute, and the outlet of the reflux device 3 of the last stage compressor flow passage is communicated with the volute; in this way, multi-stage compression can be achieved.
Of course, other layout manners may also be adopted for the airflow multi-stage compression, which is not described herein.
Preferably, the compressor is a two-stage compressor or a three-stage compressor, and at the moment, the compressor flow channel can meet the compression requirement of the compressor, so that the problem of compressor surge caused by large energy loss due to too many compression stages is solved.
Preferably, the compressor is a single cantilever compressor.
The technical features of the embodiments described above may be arbitrarily combined, and for the sake of brevity, all possible combinations of the technical features in the embodiments described above are not described, but should be considered as being within the scope of the present specification as long as there is no contradiction between the combinations of the technical features.
The above-mentioned embodiments only express several embodiments of the present invention, and the description thereof is more specific and detailed, but not construed as limiting the scope of the invention. It should be noted that, for a person skilled in the art, several variations and modifications can be made without departing from the inventive concept, which falls within the scope of the present invention. Therefore, the protection scope of the present patent shall be subject to the appended claims.
Claims (10)
1. A compressor flow channel is characterized by comprising a diffuser, a bend and a reflux device, wherein the diffuser and the reflux device are oppositely arranged, the inlet of the bend is communicated with the outlet of the diffuser, and the outlet of the bend is communicated with the inlet of the reflux device;
the diffuser has first and second opposite inner and outer side walls, the bend has second and second opposite outer side walls, and the return has third and third opposite inner and outer side walls;
the second inner side wall comprises a first inner side arc wall section, an inner side straight wall section and a second inner side arc wall section which are connected in sequence, the second outer side wall comprises a first outer side arc wall section, an outer side straight wall section and a second outer side arc wall section which are connected in sequence, and projections of the inner side straight wall section and the outer side straight wall section on a flow passage section of the compressor flow passage are straight lines;
the first inner arc wall section and the first outer arc wall section are respectively connected with the first inner side wall and the first outer side wall, and the second inner arc wall section and the second outer arc wall section are respectively connected with the third inner side wall and the third outer side wall.
2. The compressor runner of claim 1 wherein a projection of the inner straight wall section onto the runner section is a first transverse straight line, a projection of the outer straight wall section onto the runner section is a second transverse straight line, the second transverse straight line is parallel to a central axis of the compressor, and an extension line of the first transverse straight line forms an included angle of-20 ° to the central axis.
3. The compressor flow channel of claim 2, wherein a projection of the third inner side wall on the flow channel cross section is a first vertical line, a projection of the third outer side wall on the flow channel cross section is a second vertical line, and both an included angle between an extension line of the first vertical line and the central axis and an included angle between an extension line of the second vertical line and the central axis are between 70 ° and 90 °.
4. The compressor flowpath according to claim 3, wherein an angle between an extension of the first vertical line and an extension of the second vertical line is between 0 ° and 20 °.
5. The compressor flow passage of claim 4 wherein an extension of the first vertical line and an extension of the second vertical line are both perpendicular to a central axis of the compressor.
6. The compressor flowpath of claim 4 wherein an extension of the first vertical line is at an acute angle to the central axis and an extension of the second vertical line is perpendicular to the central axis.
7. The compressor flowpath of claim 1 wherein the first inner sidewall and the first inner sidewall section, the first inner sidewall section and the inner straight wall section, the inner straight wall section and the second inner sidewall section, the second inner sidewall section and the third inner sidewall are all tangent or smoothly transitionally connected;
the first outer side wall and the first outer side wall section, the first outer side wall section and the outer side straight wall section, the outer side straight wall section and the second outer side wall section, and the second outer side wall section and the third outer side wall are all in tangent connection or smooth transition connection.
8. A compressor having a compressor flow passage according to any one of claims 1 to 7.
9. The compressor of claim 8, wherein the compressor has a plurality of stages of the compressor flow passages, the plurality of stages of the compressor flow passages being in series communication, an inlet of the diffuser of a subsequent stage of the compressor flow passage being in communication with an outlet of the flow reverser of a preceding stage of the compressor flow passage.
10. The compressor of claim 8, wherein the compressor is a single cantilever compressor.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011238374.9A CN112160939A (en) | 2020-11-09 | 2020-11-09 | Compressor channel and compressor |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202011238374.9A CN112160939A (en) | 2020-11-09 | 2020-11-09 | Compressor channel and compressor |
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|---|---|---|---|---|
| DE902299C (en) * | 1943-08-08 | 1954-01-21 | Hellmut Weinrich | Centrifugal compressor |
| JPH08193600A (en) * | 1995-01-17 | 1996-07-30 | Hitachi Ltd | Centrifugal compressor |
| US6203275B1 (en) * | 1996-03-06 | 2001-03-20 | Hitachi, Ltd | Centrifugal compressor and diffuser for centrifugal compressor |
| CN106662120A (en) * | 2014-09-18 | 2017-05-10 | 三菱重工业株式会社 | Centrifugal compressor |
| CN110439826A (en) * | 2019-08-05 | 2019-11-12 | 浙江盾安机电科技有限公司 | Centrifugal compressor |
| WO2020170487A1 (en) * | 2019-02-20 | 2020-08-27 | 株式会社日立インダストリアルプロダクツ | Multi-stage centrifugal fluid machine |
| CN214036258U (en) * | 2020-11-09 | 2021-08-24 | 珠海格力电器股份有限公司 | Compressor runner and compressor |
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2020
- 2020-11-09 CN CN202011238374.9A patent/CN112160939A/en not_active Withdrawn
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE902299C (en) * | 1943-08-08 | 1954-01-21 | Hellmut Weinrich | Centrifugal compressor |
| JPH08193600A (en) * | 1995-01-17 | 1996-07-30 | Hitachi Ltd | Centrifugal compressor |
| US6203275B1 (en) * | 1996-03-06 | 2001-03-20 | Hitachi, Ltd | Centrifugal compressor and diffuser for centrifugal compressor |
| CN106662120A (en) * | 2014-09-18 | 2017-05-10 | 三菱重工业株式会社 | Centrifugal compressor |
| WO2020170487A1 (en) * | 2019-02-20 | 2020-08-27 | 株式会社日立インダストリアルプロダクツ | Multi-stage centrifugal fluid machine |
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| CN214036258U (en) * | 2020-11-09 | 2021-08-24 | 珠海格力电器股份有限公司 | Compressor runner and compressor |
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