CN108374792A - A kind of centrifugal compressor using spiral casing flow passage section A/r nonlinear Distributions - Google Patents

A kind of centrifugal compressor using spiral casing flow passage section A/r nonlinear Distributions Download PDF

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Publication number
CN108374792A
CN108374792A CN201810034650.6A CN201810034650A CN108374792A CN 108374792 A CN108374792 A CN 108374792A CN 201810034650 A CN201810034650 A CN 201810034650A CN 108374792 A CN108374792 A CN 108374792A
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volute
flow channel
centrifugal compressor
casing
circumferential
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CN201810034650.6A
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CN108374792B (en
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郑新前
孙振中
邹望之
川久保知己
玉木秀明
王宝潼
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Tsinghua University
IHI Corp
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Tsinghua University
IHI Corp
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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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • 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
    • F04D29/422—Discharge tongues
    • 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
    • F04D29/4226—Fan casings
    • F04D29/4233—Fan casings with volutes extending mainly in axial or radially inward direction
    • 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
    • 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
    • F04D29/444—Bladed diffusers

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

本发明涉及一种采用蜗壳流道截面A/r非线性分布的离心压气机，属于叶轮机械技术领域。本发明的离心压气机包括机壳、离心叶轮、背盘和扩压器。本发明中的蜗壳流道截面的面积半径比(A/r)在周向上是非线性分布的，且在蜗舌附近区域蜗壳流道截面A/r的增长速率低于在其他周向位置的增长速率。本发明能够抑制离心压气机内部的流场畸变，有效降低流场掺混损失，同时有效降低流场的非均匀性，从而大幅度改善离心压气机的气动性能和流动稳定性。

The invention relates to a centrifugal compressor adopting the non-linear distribution of A/r of the volute channel section, belonging to the technical field of impeller machinery. The centrifugal compressor of the present invention includes a casing, a centrifugal impeller, a back plate and a diffuser. The area-to-radius ratio (A/r) of the volute flow passage section in the present invention is distributed non-linearly in the circumferential direction, and the growth rate of the volute flow passage section A/r in the vicinity of the volute tongue is lower than that in other circumferential positions growth rate. The invention can suppress the distortion of the flow field inside the centrifugal compressor, effectively reduce the mixing loss of the flow field, and at the same time effectively reduce the non-uniformity of the flow field, thereby greatly improving the aerodynamic performance and flow stability of the centrifugal compressor.

Description

Centrifugal compressor adopting nonlinear distribution of A/r of volute flow channel section
Technical Field
The invention relates to a centrifugal compressor adopting a volute flow channel section A/r nonlinear distribution, belonging to the technical field of impeller machinery.
Background
The invention relates to a centrifugal compressor adopting the nonlinear distribution of A/r of the cross section of a volute flow channel, which relates to centrifugal compressors of superchargers for various purposes such as vehicle, ship, aviation and the like and centrifugal compressors adopted by blowers and the like.
Compared with the existing reciprocating piston compressor, impeller compressors such as a centrifugal compressor and the like have the advantages of high efficiency, light volume and weight, stable operation and the like. However, the operating condition range of the centrifugal compressor is limited, especially under the non-design conditions of small flow and the like, distortion is formed inside the centrifugal compressor due to the circumferential asymmetry of the volute geometry and the influence of the volute tongue structure, the flow field presents extremely strong circumferential asymmetry, the internal unstable flow of the centrifugal compressor is induced to be too early, stall or even surge is caused, the pressure ratio and the efficiency of the centrifugal compressor are directly reduced, the service life of the centrifugal compressor is shortened, and the centrifugal compressor is damaged even in a short time.
The volute is an important component of the centrifugal compressor, mainly plays a role in collecting compressed gas, and also plays a role in reducing pressure (large flow) or diffusing pressure (small flow) under an off-design working condition because the flow cross-sectional area of the volute is increased in the circumferential direction according to a certain rule. The volute is a channel with a specific radius as an inlet and the area-radius ratio (A/r) of the flow passage section in the circumferential direction is increased continuously. The distribution rule of the area-radius ratio (A/r) of the traditional volute flow channel section is determined by the design working condition points of the centrifugal compressor, the fluid pressure is guaranteed to be kept constant in the circumferential direction theoretically on the premise that the circumferential direction of the fluid entering the volute is uniform, and the effect that the circumferential flow field distortion is not introduced while gas is collected is achieved. Since the flow parameters entering the volute from any circumferential position are assumed to be the same (circumferentially uniform assumption), the conventional volute flow path cross-sectional area to radius ratio (a/r) is linearly distributed in the circumferential direction. In fact, under the influence of the volute tongue structure, the airflow entering the volute casing is different in the circumferential direction, and especially, the airflow parameters (such as static pressure) in the area near the volute tongue can be changed greatly. Under the real flow condition, the volute with the volute flow passage cross section area radius ratio (A/r) in linear distribution often increases the nonuniformity of a flow field, brings a severe flow stability problem, and induces the centrifugal compressor to generate unstable disturbance and even surge too early.
Disclosure of Invention
The invention aims to provide a centrifugal compressor adopting the nonlinear distribution of the section A/r of a volute flow channel, which improves the volute flow channel of the existing centrifugal compressor, inhibits the flow field distortion in the centrifugal compressor, especially the distortion of the flow field near the volute tongue, improves the flow stability in the centrifugal compressor and widens the stable working range of the centrifugal compressor on the premise of ensuring that the structure is not changed greatly.
The invention provides a centrifugal compressor adopting nonlinear distribution of A/r of a volute flow channel section, which comprises a shell, a centrifugal impeller, a back disc and a diffuser; the centrifugal impeller and the diffuser are coaxially installed, the centrifugal impeller is driven by a rotary shaft of the centrifugal compressor, the casing and the back disc are relatively fixed, an annular flow channel is formed between the outer end of the casing and the outer edge of the centrifugal impeller in the radial range, the casing and the back disc form the annular flow channel to form the diffuser, guide vanes can be installed on the diffuser part, or the vanes can not be installed on the diffuser part, the outer end of the annular flow channel is connected with a volute flow channel limited by the volute, the volute is the outer end part of the casing, and the inlet of the volute flow channel is communicated with the outlet of the annular flow channel: the area-radius ratio (A/r) of the cross section of the volute flow channel is nonlinearly changed in the circumferential direction, and the specific embodiment is as follows: in the area near the volute tongue (the area which is circumferentially covered by 90-180 degrees by taking the volute tongue as the center), the increase rate of the volute channel section area radius ratio (A/r) is smaller than that in other circumferential positions.
The invention provides a centrifugal compressor adopting the nonlinear distribution of A/r of the cross section of a volute flow channel, which has the advantages that: according to the centrifugal compressor, the increase rate of the area-radius ratio (A/r) of the cross section of the flow channel of the volute in the area near the volute tongue is smaller than that in other circumferential positions, so that flow field distortion caused by the volute tongue structure can be inhibited, the mixing loss of the flow field and the nonuniformity of the flow field in the centrifugal compressor are effectively reduced, the occurrence of flow instability is delayed, the phenomenon that the flow instability occurs in the circumferential direction at first due to the excessive flow field distortion is relieved, the integral surge of the compressor is induced, and the aerodynamic performance and the flow stability of the centrifugal compressor are greatly improved. Meanwhile, as only local fine adjustment of the volute flow channel is involved, and main structures such as the shell and the like are not changed, no extra cost is generated in the production and processing process.
Drawings
FIG. 1 is a cross-sectional view of a centrifugal compressor employing a non-linear distribution of the volute flow path cross-section A/r in accordance with the present invention.
Figure 2 is a schematic cross-sectional view of a flow path of a volute in the centrifugal compressor shown in figure 1.
Fig. 3 is a schematic view of the centrifugal compressor shown in fig. 1 in a forward view and at a circumferential angle.
FIG. 4 shows the circumferential position of the shape correction factor ε in an embodiment of the present inventionDistribution of (2).
FIG. 5 is a corrected circumferential position of the growth rate k for the volute flowpath cross-section A/r in an embodiment of the present inventionDistribution of (2).
FIG. 6 shows the circumferential position of the volute flow path cross-section A/r in one embodiment of the inventionDistribution of (2).
In fig. 1, 2 and 3, 1 is an inlet of a centrifugal compressor, 2 is a centrifugal impeller, 3 is a diffuser, 4 is a back disc, 5 is a volute flow channel, 6 is a casing, 7 is a volute tongue, 8 is a volute outlet flow channel, 9 is an inlet of the volute flow channel, and 10 is a cross section of the volute flow channel.
Detailed Description
The invention is described in detail below with reference to the accompanying drawings:
the centrifugal compressor adopting the flow channel section A/r nonlinear distribution volute is structurally shown in figure 1 and comprises a casing 6, a centrifugal impeller 2, a back disc 4 and a diffuser 3. The centrifugal impeller 2 and the diffuser 3 are coaxially installed, and the centrifugal impeller 2 is driven to rotate by a shaft. The casing 6 is fixed opposite to the back disc 4, and the outer end of the casing 6 forms a volute flow channel 5. As shown in FIG. 2, the volute flow-path cross-section 10 increases in the circumferential direction along the direction of impeller rotation, essentially the volute flow-path cross-sectional area-to-radius ratio (A/r) increases in the direction of impeller rotation. Wherein the area-to-radius ratio (A/r) of the volute flow passage cross section is defined as:
wherein, R represents the radial position, namely the distance from the center of the rotating shaft, and S is the sectional area of the volute flow channel. According to the centrifugal compressor, the area-to-radius ratio (A/r) of the volute flow passage section is distributed in a non-linear mode in the circumferential direction, and the increase rate of the area-to-radius ratio (A/r) of the volute flow passage section in the area close to the volute tongue 7 is lower than that of other circumferential positions. The circumferential position is defined as shown in fig. 3, the rotation axis is used as the origin of coordinates, the x direction is defined as the direction perpendicular to the volute outlet flow channel 8, and the circumferential position of 0 ° is the position corresponding to the x-axis forward direction, and a circle of rotation along the rotation direction of the impeller corresponds to 360 °. The volute tongue is shown in figure 3 to be located about the 60 position. Compared with other volute flow passage section designs (generally A/r is linearly distributed along the circumferential direction) of the centrifugal compressor, the volute flow passage design of the centrifugal compressor can effectively inhibit flow field distortion caused by the volute tongue 7, reduce flow field mixing loss and flow field unevenness, and effectively improve the pneumatic performance and flow stability of the centrifugal compressor; meanwhile, the invention does not relate to the main structural change of the centrifugal compressor, has simple design and does not increase the additional production and manufacturing cost.
The method for determining the circumferential distribution of the volute flow passage section A/r is described by one embodiment of the invention, and the process is as follows:
1) based on the assumption of circumferential uniformity of a flow field, the increase rate k of the volute channel section area-radius ratio (A/r) in the circumferential direction is obtained through mathematical derivation according to the design parameters of the centrifugal compressorlinear(namely the growth rate corresponding to the traditional volute flow passage section area radius ratio (A/r) linear distribution design), and determining the A/r at the position of the throat of the volute flow passage according to the component matching conditions. Growth rate k in one embodiment of the inventionlinearAnd the value of A/r at the position of the throat of the volute channel is klinear＝0.0314[mm/°]Andwherein the throat opening corresponds to a circumferential position of
2) And determining the values of the shape correction factor epsilon at different circumferential positions. Wherein epsilon ranges from 0< epsilon < 5, and epsilon <1 at a circumferential position near the volute tongue and epsilon >1 at a circumferential position far away from the volute tongue are required. In one embodiment of the invention, the volute tongue position is at a 60 ° position, and the distribution of the shape correction factor epsilon in the circumferential direction is shown in fig. 4.
3) According to the formula k ═ ε · klinearDetermining the corrected growth rate k of the volute channel section area radius ratio (A/r) at each circumferential position by using the + delta k, wherein the delta k is a correction parameter, the values can be different at different circumferential positions, and the value range is-0.5 klinear<δk<0.5·klinear. In one embodiment of the present invention, δ k is taken to be 0 at all circumferential positions, and the distribution of the resulting modified growth rate k in the circumferential direction is shown in fig. 5;
4) according to the formulaDetermining each circumferential positionSo as to obtain the distribution rule of the volute flow passage section A/r in the circumferential direction. The distribution of the volute flow channel section A/r determined in one embodiment of the invention in the circumferential direction is shown in FIG. 6 (note: the volute flow channel 5 and the volute outlet flow channel 8 are intersected to form a volute tongue within the range of 0-60 degrees, and in fact, the volute flow channel is included in the volute outlet flow channel, so the section is shown by a dotted line in the figure). The related parameters in the steps 2) and 3) are defined, so that the obtained volute flow passage cross-section area-radius ratio (A/r) is non-linearly distributed in the circumferential direction, and the area-radius ratio (A/r) in the area near the volute tongue increases at a lower rate than other circumferential positions.

Claims (4)

1.一种离心压气机，包括机壳、离心叶轮、背盘和扩压器；所述的离心叶轮和扩压器同轴安装，离心叶轮由离心压气机旋转轴驱动，所述的机壳与背盘相对固定，在机壳外端和离心叶轮外缘之间的径向范围内，机壳和背盘形成环状流道，构成扩压器，所述环状流道外端连接由蜗壳限定的蜗壳流道，所述蜗壳为机壳的外端部分，蜗壳流道进口和环状流道出口相通，其特征在于：所述蜗壳流道截面的面积半径比(A/r)在周向上非线性变化。1. A centrifugal compressor, comprising a casing, a centrifugal impeller, a back plate and a diffuser; the centrifugal impeller and the diffuser are coaxially installed, and the centrifugal impeller is driven by the rotating shaft of the centrifugal compressor, and the casing Relatively fixed to the back plate, within the radial range between the outer end of the casing and the outer edge of the centrifugal impeller, the casing and the back plate form an annular flow channel to form a diffuser, and the outer end of the annular flow channel is connected by a volute The volute flow channel defined by the casing, the volute is the outer end part of the casing, the inlet of the volute flow channel communicates with the outlet of the annular flow channel, and it is characterized in that the area radius ratio of the volute flow channel section (A /r) changes non-linearly in the circumferential direction. 2.根据权利要求1所述的离心压气机，其特征在于：扩压器部分安装导流叶片。2. The centrifugal compressor according to claim 1, characterized in that guide vanes are installed on the diffuser part. 3.根据权利要求1所述的离心压气机，其特征在于：扩压器部分不安装导流叶片。3. The centrifugal compressor according to claim 1, characterized in that: the diffuser part is not equipped with guide vanes. 4.根据权利要求2或3任意一项所述的离心压气机，其特征在于所述蜗壳流道截面的面积半径比(A/r)在周向非线性变化，具体为：4. The centrifugal compressor according to any one of claims 2 or 3, characterized in that the area-to-radius ratio (A/r) of the volute flow channel cross-section changes non-linearly in the circumferential direction, specifically: 其中，为周向位置，为蜗壳喉口处流道截面的面积半径比，通过部件匹配条件确定，表示蜗壳喉口所在的周向位置，k为所述蜗壳流道截面的面积半径比(A/r)在周向上的修正增长速率，k＝ε·klinear+δk，ε为形状修正因子，在不同周向位置取值可以不同，取值范围为0<ε≤5，且在靠近蜗舌附近的周向位置时ε<1，而在远离蜗舌的周向位置时ε>1，klinear为所述蜗壳流道截面的面积半径比(A/r)在周向上的增长速率，通过计算得到，δk为修正参数，在不同周向位置取值可以不同，取值范围为-0.5·klinear<δk<0.5·klinear。in, is the circumferential position, is the area-to-radius ratio of the flow channel section at the throat of the volute, which is determined by the matching conditions of the components, Indicates the circumferential position of the volute throat, k is the corrected growth rate of the area radius ratio (A/r) of the volute flow channel section in the circumferential direction, k=ε k linear + δk, ε is the shape correction The value of factor can be different at different circumferential positions, and the value range is 0<ε≤5, and ε<1 at the circumferential position near the cochlear tongue, and ε>1 at the circumferential position far away from the cochlear tongue , k linear is the growth rate of the area-to-radius ratio (A/r) of the volute flow channel section in the circumferential direction, which is obtained by calculation, and δk is a correction parameter, which can be different at different circumferential positions, and the value range is -0.5 k linear <δk<0.5 k linear .
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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109989926A (en) * 2019-03-28 2019-07-09 宁波纽新克电机股份有限公司 A high-efficiency flow-preserving centrifugal fan
CN113374734A (en) * 2021-06-24 2021-09-10 珠海格力电器股份有限公司 Expander shell, expander and circulator
CN119026282A (en) * 2024-10-29 2024-11-26 西北工业大学 A design method for a tubular diffuser with a dovetail leading edge

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012184758A (en) * 2011-03-08 2012-09-27 Mitsubishi Heavy Ind Ltd Rotary machine
US20130294903A1 (en) * 2011-03-25 2013-11-07 Mitsubishi Heavy Industries, Ltd. Scroll shape of centrifugal compressor
CN103967842A (en) * 2014-04-02 2014-08-06 华北电力大学（保定） Method for designing volute radius of centrifugal fan based on variable working conditions
CN106802974A (en) * 2016-11-25 2017-06-06 华中科技大学 A kind of centrifugal blower volute Profile Design method

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012184758A (en) * 2011-03-08 2012-09-27 Mitsubishi Heavy Ind Ltd Rotary machine
US20130294903A1 (en) * 2011-03-25 2013-11-07 Mitsubishi Heavy Industries, Ltd. Scroll shape of centrifugal compressor
CN103967842A (en) * 2014-04-02 2014-08-06 华北电力大学（保定） Method for designing volute radius of centrifugal fan based on variable working conditions
CN106802974A (en) * 2016-11-25 2017-06-06 华中科技大学 A kind of centrifugal blower volute Profile Design method

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109989926A (en) * 2019-03-28 2019-07-09 宁波纽新克电机股份有限公司 A high-efficiency flow-preserving centrifugal fan
CN113374734A (en) * 2021-06-24 2021-09-10 珠海格力电器股份有限公司 Expander shell, expander and circulator
CN119026282A (en) * 2024-10-29 2024-11-26 西北工业大学 A design method for a tubular diffuser with a dovetail leading edge
CN119026282B (en) * 2024-10-29 2025-04-18 西北工业大学 A design method for a tubular diffuser with a dovetail leading edge

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