CN111075768A - Centrifugal compressor volute with auxiliary noise reduction structure - Google Patents
Centrifugal compressor volute with auxiliary noise reduction structure Download PDFInfo
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- CN111075768A CN111075768A CN201911335477.4A CN201911335477A CN111075768A CN 111075768 A CN111075768 A CN 111075768A CN 201911335477 A CN201911335477 A CN 201911335477A CN 111075768 A CN111075768 A CN 111075768A
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- China
- Prior art keywords
- air inlet
- inlet pipe
- compressor volute
- compressor
- volute
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Classifications
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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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- 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
- F04D29/08—Sealings
- F04D29/083—Sealings 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
- F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps 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
- F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
- F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
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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
-
- 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
- F04D29/663—Sound attenuation
-
- 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
- F04D29/663—Sound attenuation
- F04D29/665—Sound attenuation by means of resonance chambers or interference
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/40—Application in turbochargers
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention provides a centrifugal compressor volute with an auxiliary silencing structure, which comprises an auxiliary silencing air inlet pipe, an air inlet pipe sealing ring, a compressor volute processed by a belt box and a bolt, wherein the air inlet pipe sealing ring is arranged in a sealing ring groove of the air inlet pipe, and the auxiliary silencing air inlet pipe is arranged at an inlet of the compressor volute. The structure of the outlet of the auxiliary silencing air inlet pipe is equivalent to that of a silencing ring of a casing treatment supercharger; an annular resonant cavity is formed between the outer wall surface of the outlet pipeline of the auxiliary silencing air inlet pipe and the outer wall surface of a casing channel of the compressor volute. The centrifugal compressor volute with the auxiliary silencing air inlet pipe has double silencing effects, firstly, the inner diameter of an outlet pipeline of the air inlet pipe is matched with the inner diameter of a main air inlet channel of the compressor volute, so that the pneumatic noise generated by high-speed convection collision of return air flow in a casing channel and air flow at the outlet of the air inlet pipe when the compressor is operated near a surge working condition is weakened; and secondly, the pneumatic noise of the compressor with a certain frequency can be eliminated.
Description
Technical Field
The invention belongs to the technical field of exhaust gas turbocharging, and particularly relates to a centrifugal compressor volute with an auxiliary silencing structure.
Background
The special requirement of the vehicle engine for continuously improving the power per liter, continuously reducing the displacement and recovering the plateau environment power leads the pressure ratio and the rotating speed of the gas compressor of the turbocharger to be continuously improved. With the increase of the pressure ratio and the rotating speed of the compressor, the pneumatic noise generated by the compressor of the supercharger is increasingly serious.
For the research of the pneumatic noise reduction method of the air compressor, the existing research method mainly includes noise reduction from two aspects of noise source and transmission path, the main means of noise reduction from the aspect of the noise source is to adjust the structure parameters of the air compressor, a diffuser and a volute, and the main means of noise reduction from the aspect of the transmission path is to additionally arrange a silencer at the inlet of the air compressor, additionally arrange a coating layer on the surface of the volute, additionally arrange an anti-vortex ring at an air inlet and the like.
In the prior art, the structural parameters of parts such as a gas compressor and the like are changed inevitably from the aspect of noise source, and the performance of the supercharger is influenced as a result; noise reduction in the propagation path adds structural components that increase the overall weight of the supercharger and may interfere with airflow, thereby affecting supercharger performance. Therefore, there is a need for a structure that reduces noise without affecting the performance and weight of the supercharger.
Disclosure of Invention
In view of this, the present invention is directed to a centrifugal compressor volute with an auxiliary noise reduction structure, which effectively reduces the aerodynamic noise generated by the compressor while playing a role of guiding air flow and intaking.
In order to achieve the purpose, the technical scheme of the invention is realized as follows:
a centrifugal compressor volute with an auxiliary silencing structure comprises an auxiliary silencing air inlet pipe, a bolt, an air inlet pipe sealing ring and a compressor volute processed by a belt box, wherein the auxiliary silencing air inlet pipe is arranged at an inlet of the compressor volute and is connected through the bolt; the inner diameter d1 of the pipeline at the outlet of the auxiliary silencing air inlet pipe, the inner diameter d2 of the main channel of the inlet of the compressor volute and the inner diameter d3 of the channel of the casing of the compressor volute meet the requirements: d2 < d1 < d 3; an annular resonant cavity is formed between the outer wall surface of the outlet pipeline of the auxiliary silencing air inlet pipe and the outer wall surface of a casing channel of the compressor volute.
Furthermore, the clearance fit position of the outlet end of the auxiliary silencing air inlet pipe and the inlet end of the compressor volute is sealed by an air inlet pipe sealing ring, and the air inlet pipe sealing ring is arranged in a sealing ring groove of the auxiliary silencing air inlet pipe.
Further, the outer diameter D1 of the pipeline at the outlet of the auxiliary silencing air inlet pipe, the outer diameter D3 of the compressor volute casing channel and the inner diameter D3 of the compressor volute casing channel meet the following requirements: d3 is not less than D1 not less than (2 XD 3+ D3)/3.
Further, the axial clearance a between the end surface of the pipeline at the outlet of the auxiliary silencing air inlet pipe and the end surface of the outer wall of the compressor volute casing channel meets the requirement: a is more than 0 and less than or equal to 3 mm; the axial clearance S between the end surface of the pipeline at the outlet of the auxiliary silencing air inlet pipe and the end surface of the inner wall of the compressor volute casing channel and the inner diameter d2 of the compressor volute inlet main channel meet the requirements: d2/20 is not less than S not more than d 2/10.
Compared with the prior art, the invention has the following advantages:
(1) the structure characteristics formed by matching the outlet of the air inlet pipe and the inlet of the volute of the air compressor have double silencing effects on pneumatic noise of the air compressor, and firstly, the inner diameter of the pipeline at the outlet of the air inlet pipe is matched with the inner diameter of the main air inlet channel of the volute of the air compressor, so that the pneumatic noise generated by high-speed convection collision of return air flow in a casing channel and air flow at the outlet of the air inlet pipe when the air compressor is operated near a surge working condition is weakened; and after the air inlet pipe is connected with the compressor volute, the outer wall surface of the outlet pipeline of the air inlet pipe and the outer wall surface of the casing channel of the compressor volute form an annular resonant cavity, so that the pneumatic noise of the compressor with a certain frequency can be eliminated.
(2) The auxiliary silencing air inlet pipe can be designed into a bent pipe or a straight pipe under the condition of ensuring the structural characteristics of an outlet, the air inlet direction of the supercharger can be flexibly designed according to actual requirements, the total weight of the supercharger is not obviously increased while the silencing effect is realized through the structural design, and the auxiliary silencing air inlet pipe is simple in structure, convenient to assemble and disassemble, good in sealing performance and strong in adaptability.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate an embodiment of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:
FIG. 1 is a perspective view of a centrifugal compressor volute with a secondary silencing structure according to an embodiment of the present invention;
FIG. 2 is a schematic cross-sectional view of a centrifugal compressor volute with a secondary silencing structure according to an embodiment of the invention;
FIG. 3 is a schematic diagram of a critical dimension of a centrifugal compressor volute with a secondary silencing structure according to an embodiment of the present invention;
fig. 4 is a perspective view of an auxiliary silencing inlet pipe according to an embodiment of the present invention.
Description of reference numerals:
1-auxiliary silencing air inlet pipe; 2-bolt; 3-air inlet pipe sealing ring; 4-compressor volute.
Detailed Description
It should be noted that the embodiments and features of the embodiments may be combined with each other without conflict.
In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like, indicate orientations or positional relationships based on those shown in the drawings, and are used only for convenience in describing the present invention and for simplicity in description, and do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be construed as limiting the present invention. Furthermore, the terms "first", "second", etc. are used 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," "second," etc. may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.
In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art through specific situations.
The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings.
A centrifugal compressor volute with an auxiliary silencing structure is shown in figures 1 to 4 and comprises an auxiliary silencing air inlet pipe 1, an air inlet pipe sealing ring 3 and a compressor volute 4 with a casing, wherein the auxiliary silencing air inlet pipe 1 is arranged at an inlet of the compressor volute 4 and is connected with the compressor volute through a bolt 2; the outer annular surface of one side of the outlet end of the auxiliary silencing air inlet pipe 1 is in clearance fit with the inner annular surface of the corresponding position of the inlet end of the compressor volute 4, and is sealed by an air inlet pipe sealing ring 3, and the air inlet pipe sealing ring 3 is arranged in a sealing ring groove of the auxiliary silencing air inlet pipe 1;
the inner diameter d1 of the pipeline at the outlet of the auxiliary silencing air inlet pipe 1, the inner diameter d2 of the inlet main channel of the compressor volute 4 and the inner diameter d3 of the casing channel of the compressor volute 4 meet the requirements: d2 < d1 < d 3; an annular resonant cavity is formed between the outer wall surface of the outlet pipeline of the auxiliary silencing air inlet pipe 1 and the outer wall surface of the casing channel of the compressor volute 4.
The outer diameter D1 of the pipeline at the outlet of the auxiliary silencing air inlet pipe 1, the outer diameter D3 of the casing channel of the compressor volute 4 and the inner diameter D3 of the casing channel of the compressor volute 4 meet the requirements: d3 is not less than D1 not less than (2 XD 3+ D3)/3.
The axial clearance a between the end surface of the pipeline at the outlet of the auxiliary silencing air inlet pipe 1 and the end surface of the outer wall of the casing channel of the compressor volute 4 meets the requirement: a is more than 0 and less than or equal to 3 mm; the axial clearance S between the end surface of the pipeline at the outlet of the auxiliary silencing air inlet pipe 1 and the end surface of the inner wall of the casing channel of the compressor volute 4 and the inner diameter d2 of the main inlet channel of the compressor volute 4 meet the requirements: d2/20 is not less than S not more than d 2/10.
In the embodiment, the auxiliary silencing air inlet pipe 1 is in a bent pipe form, is positioned at the inlet of the compressor volute 4 and provides a direction-changing flow-guiding air inlet effect for the inlet of the compressor volute 4. When the compressor operates near a surge working condition, airflow enters a casing channel of the compressor from a main air inlet channel of the volute 4 of the compressor through the oblique seam channel under the action of pressure difference, is mixed with the airflow at the inlet of the main air inlet channel and then flows into the main air inlet channel again.
If the auxiliary silencing air inlet pipe 1 is not arranged, the two air flows are subjected to high-speed convection collision to generate larger aerodynamic noise; after the auxiliary silencing air inlet pipe 1 is arranged, airflow of a casing channel is guided by the outer wall surface of an outlet pipeline of the auxiliary silencing air inlet pipe 1 and then mixed with the airflow at the outlet of the auxiliary silencing air inlet pipe 1 to enter a main air inlet channel of a compressor volute 4, the axial speed directions of the two airflows are the same, and aerodynamic noise generated by high-speed convection collision is weakened.
After the auxiliary silencing air inlet pipe 1 is connected with the compressor volute 4, an annular resonant cavity is formed by the outer wall surface of an outlet pipeline of the auxiliary silencing air inlet pipe 1 and the outer wall surface of a casing channel of the compressor volute 4, and the existence of the resonant cavity can eliminate the pneumatic noise of the compressor with certain frequency.
The auxiliary silencing air inlet pipe 1 plays a role in diversion, diversion and air inlet, and can effectively reduce the pneumatic noise of the air compressor on the basis of not additionally increasing the total weight of the supercharger.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.
Claims (4)
1. The utility model provides a centrifugal compressor spiral case with supplementary amortization structure which characterized in that: the auxiliary silencing air inlet pipe (1) is arranged at an inlet of the compressor volute (4) and connected through the bolt (2), and an outer annular surface on one side of an outlet end of the auxiliary silencing air inlet pipe (1) is in clearance fit with an inner annular surface at a position corresponding to an inlet end of the compressor volute (4);
the inner diameter d1 of the pipeline at the outlet of the auxiliary silencing air inlet pipe (1), the inner diameter d2 of the main inlet channel of the compressor volute (4) and the inner diameter d3 of the casing channel of the compressor volute (4) meet the requirements: d2 < d1 < d 3;
an annular resonant cavity is formed between the outer wall surface of the outlet pipeline of the auxiliary silencing air inlet pipe (1) and the outer wall surface of a casing channel of the compressor volute (4).
2. The centrifugal compressor volute with secondary silencing structure of claim 1, wherein: the clearance fit position of supplementary amortization intake pipe (1) exit end and compressor spiral case (4) entrance point relies on intake pipe sealing washer (3) to seal, intake pipe sealing washer (3) are arranged in the sealed annular of supplementary amortization intake pipe (1).
3. The centrifugal compressor volute with secondary silencing structure of claim 1, wherein: the outer diameter D1 of the pipeline at the outlet of the auxiliary silencing air inlet pipe (1), the outer diameter D3 of the casing channel of the compressor volute (4) and the inner diameter D3 of the casing channel of the compressor volute (4) meet the requirements: d3 is not less than D1 not less than (2 XD 3+ D3)/3.
4. The centrifugal compressor volute with secondary silencing structure of claim 1, wherein: the axial clearance a between the end surface of the pipeline at the outlet of the auxiliary silencing air inlet pipe (1) and the end surface of the outer wall of the casing channel of the compressor volute (4) meets the requirement: a is more than 0 and less than or equal to 3 mm; the axial clearance S between the end surface of the pipeline at the outlet of the auxiliary silencing air inlet pipe (1) and the end surface of the inner wall of the casing channel of the compressor volute (4) and the inner diameter d2 of the main inlet channel of the compressor volute (4) meet the requirements: d2/20 is not less than S not more than d 2/10.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911335477.4A CN111075768A (en) | 2019-12-20 | 2019-12-20 | Centrifugal compressor volute with auxiliary noise reduction structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911335477.4A CN111075768A (en) | 2019-12-20 | 2019-12-20 | Centrifugal compressor volute with auxiliary noise reduction structure |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN111075768A true CN111075768A (en) | 2020-04-28 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201911335477.4A Pending CN111075768A (en) | 2019-12-20 | 2019-12-20 | Centrifugal compressor volute with auxiliary noise reduction structure |
Country Status (1)
| Country | Link |
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| CN (1) | CN111075768A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112282988A (en) * | 2020-10-26 | 2021-01-29 | 大连中车泽通机械有限公司 | Air filter of turbocharger of diesel engine |
| CN115076137A (en) * | 2022-07-19 | 2022-09-20 | 威海克莱特菲尔风机股份有限公司 | High-efficiency low-noise centrifugal fan for offshore wind power cooling system |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
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| JP2007127108A (en) * | 2005-11-07 | 2007-05-24 | Mitsubishi Heavy Ind Ltd | Compressor of exhaust turbosupercharger |
| CN101501303A (en) * | 2006-08-04 | 2009-08-05 | Abb涡轮系统有限公司 | Granular material damper |
| CN102518605A (en) * | 2005-02-23 | 2012-06-27 | 康明斯涡轮增压技术有限公司 | Compressor |
| US20170350420A1 (en) * | 2016-06-01 | 2017-12-07 | Borgwarner Inc. | Ported Shroud Geometry to Reduce Blade-Pass Noise |
| US20190032676A1 (en) * | 2017-07-31 | 2019-01-31 | Trane International Inc. | Combined secondary inlet bell and flow grid for a centrifugal fan or centrifugal compressor |
| CN109667794A (en) * | 2017-10-17 | 2019-04-23 | 博格华纳公司 | Multi-piece type compressor housing for turbocharger |
| CN110017303A (en) * | 2017-12-01 | 2019-07-16 | 曼恩能源方案有限公司 | Radial compressor |
-
2019
- 2019-12-20 CN CN201911335477.4A patent/CN111075768A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102518605A (en) * | 2005-02-23 | 2012-06-27 | 康明斯涡轮增压技术有限公司 | Compressor |
| JP2007127108A (en) * | 2005-11-07 | 2007-05-24 | Mitsubishi Heavy Ind Ltd | Compressor of exhaust turbosupercharger |
| CN101501303A (en) * | 2006-08-04 | 2009-08-05 | Abb涡轮系统有限公司 | Granular material damper |
| US20170350420A1 (en) * | 2016-06-01 | 2017-12-07 | Borgwarner Inc. | Ported Shroud Geometry to Reduce Blade-Pass Noise |
| US20190032676A1 (en) * | 2017-07-31 | 2019-01-31 | Trane International Inc. | Combined secondary inlet bell and flow grid for a centrifugal fan or centrifugal compressor |
| CN109667794A (en) * | 2017-10-17 | 2019-04-23 | 博格华纳公司 | Multi-piece type compressor housing for turbocharger |
| CN110017303A (en) * | 2017-12-01 | 2019-07-16 | 曼恩能源方案有限公司 | Radial compressor |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112282988A (en) * | 2020-10-26 | 2021-01-29 | 大连中车泽通机械有限公司 | Air filter of turbocharger of diesel engine |
| CN115076137A (en) * | 2022-07-19 | 2022-09-20 | 威海克莱特菲尔风机股份有限公司 | High-efficiency low-noise centrifugal fan for offshore wind power cooling system |
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Application publication date: 20200428 |
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| RJ01 | Rejection of invention patent application after publication |