CN112012957B - A compressor for industrial production - Google Patents
A compressor for industrial production Download PDFInfo
- Publication number
- CN112012957B CN112012957B CN202011014045.6A CN202011014045A CN112012957B CN 112012957 B CN112012957 B CN 112012957B CN 202011014045 A CN202011014045 A CN 202011014045A CN 112012957 B CN112012957 B CN 112012957B
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- Prior art keywords
- ring
- volute
- compressor
- impeller
- channel
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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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
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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
- F04D29/66—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
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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
- F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
Abstract
The invention discloses a compressor for industrial production, which comprises a volute (1), an impeller (2), a volute backflow ring (11), a first backflow channel (12) and a diffuser (13), wherein the inner periphery of an inlet section of the volute is provided with the volute backflow ring, the volute backflow ring is connected with the volute and is a static part, the first backflow channel is formed between the volute backflow ring and the volute, the impeller comprises a plurality of blades (21) distributed along the circumferential direction, and the outer periphery of the impeller is provided with the diffuser, and the compressor is characterized in that: the periphery of the blade is connected with an impeller return ring (22), and the impeller return ring and the blade are connected into a whole and are rotating pieces; the impeller return ring comprises an axial part (23) and a radial part (24) which are connected, and the axial part and the radial part form an L-shaped structure. The compressor can further inhibit surge and reduce noise through the design of the impeller backflow ring, thereby improving the overall performance of the compressor.
Description
Technical Field
The invention relates to the technical field of fluid machinery, in particular to a compressor for industrial production.
Background
As shown in fig. 1, the conventional compressor is provided with a backflow structure (including a volute backflow ring 11 and a backflow passage 12) at an inner periphery of a volute 1 and at an inlet of an impeller 2 to suppress surge, thereby improving overall performance of the compressor. However, the conventional volute backflow ring 11 is a static part, so that the effects of inhibiting surging and reducing noise are not good enough, and further improvement/promotion is needed.
Disclosure of Invention
The invention aims to overcome the defects in the prior art, and provides a compressor for industrial production, which can further inhibit surge and reduce noise through the design of an impeller backflow ring compared with a backflow structure in the prior art, thereby improving the overall performance of the compressor and having better technical effects of inhibiting surge and reducing noise.
In order to achieve the purpose, the invention adopts the technical scheme that:
the utility model provides a compressor for industrial production, its includes spiral case (1), impeller (2), spiral case return ring (11), first return flow channel (12), diffuser (13), the inner periphery of the inducer of spiral case is provided with spiral case return flow ring, and spiral case return flow ring is connected with the spiral case, for the stationary part, forms first return flow channel between spiral case return flow ring and the spiral case, and the impeller includes a plurality of blades (21) along circumference distribution, and the periphery of impeller is provided with the diffuser, its characterized in that: the periphery of the blade is connected with an impeller return ring (22), and the impeller return ring and the blade are connected into a whole and are rotating parts; the impeller backflow ring (22) comprises an axial portion (23) and a radial portion (24) which are connected, and the axial portion and the radial portion form an L-shaped structure.
Furthermore, a sealing ring (14) is arranged at the right end of the volute backflow ring, the sealing ring and the axial part are arranged oppositely in the radial direction, and a radial sealing gap is formed between the sealing ring and the axial part; a first channel (31) is formed between the right side of the radial portion and the volute, a second channel (32) is formed between the periphery of the volute backflow ring and the volute, a third channel (33) is formed between the left side of the volute backflow ring and the volute, and the first channel, the second channel and the third channel are communicated and form a first backflow channel.
Further, the outer diameter of the radial portion is greater than the outer diameter of the volute recirculation ring.
Furthermore, a plurality of through holes (25) are formed in the axial portion and distributed along the circumferential direction of the axial portion, one end of each through hole is communicated with a flow channel between each blade, and the other end of each through hole is communicated with the sealing gap.
Furthermore, the right end of the sealing ring is provided with an inclined part (26), and the distance between the inclined part and the radial part gradually increases from the radial outer side to the radial inner side in the radial direction to form a sealing part.
Further, the through hole forms a fourth channel (34), the sealing gap forms a fifth channel (35), a sixth channel (36) is formed between the left side of the axial portion and the volute return ring, and the fourth channel, the fifth channel and the sixth channel are communicated and form a second return channel.
Further, in the axial direction, the through hole is located between the leading edge of the blade and the inclined portion.
Further, the compressor is a centrifugal compressor.
Compared with the backflow structure in the prior art, the fluid machine/compressor for industrial production can further inhibit surge and reduce noise through the design of the impeller backflow ring, thereby improving the overall performance of the compressor and having better technical effects of inhibiting surge and reducing noise.
Drawings
FIG. 1 is a schematic view of a compressor for industrial production according to the prior art;
FIG. 2 is a schematic view of a compressor for industrial production according to the present invention;
fig. 3 is a schematic structural view of another embodiment of the compressor for industrial production according to the present invention.
In the figure: volute 1, impeller 2, volute return ring 11, (first) return channel 12, (vane) diffuser 13, sealing ring 14, vane 21, impeller return ring 22, axial portion 23, radial portion 24, through hole/through groove 25, inclined portion 26, first channel 31, second channel 32, third channel 33, fourth channel 34, fifth channel 35, sixth channel 36.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all, embodiments of the present invention. All other embodiments, which can be obtained by a person skilled in the art without inventive step based on the embodiments of the present invention, are within the scope of protection of the present invention.
The present invention will be described in further detail with reference to the accompanying drawings.
As shown in fig. 2 to 3, a compressor for industrial production includes a volute 1, an impeller 2, a volute backflow ring 11, a first backflow channel 12, and a diffuser 13, the volute backflow ring 11 is disposed on an inner periphery of an inlet section of the volute 1, the volute backflow ring 11 is connected to the volute 1, and is a stationary component, the first backflow channel 12 is formed between the volute backflow ring 11 and the volute 1, the impeller 2 includes a plurality of vanes 21 distributed along a circumferential direction, and the diffuser 13 is disposed on an outer periphery of the impeller 2, and is characterized in that: the periphery of the blade 21 is connected with an impeller return ring 22, the impeller return ring 22 and the blade 21 are connected into a whole and are rotating parts, the impeller return ring 22 comprises an axial part 23 and a radial part 24 which are connected, and the axial part 23 and the radial part 24 form an L-shaped structure.
The volute return ring 11 is provided at its right end with a sealing ring 14, which sealing ring 14 is arranged diametrically opposite the axial portion 23, forming a radial sealing gap/micro gap therebetween. A first channel 31 is formed between the right side of the radial portion 24 and the volute 1, a second channel 32 is formed between the periphery of the volute return ring 11 and the volute 1, a third channel 33 is formed between the left side of the volute return ring 11 and the volute 1, and the first channel 31, the second channel 32 and the third channel 33 are communicated and form a first return channel 12.
The present invention can suppress surge and reduce noise by designing the impeller return ring 22, thereby improving the overall performance of the compressor.
Further, the outer diameter of the radial portion 24 is larger than the outer diameter of the volute return ring 11.
In another preferred embodiment, as shown in fig. 3, a plurality of through holes/through slots 25 are provided on the axial portion 23, the plurality of through holes 25 are distributed along the circumferential direction of the axial portion 23, one end of each through hole 25 is communicated with the flow passage between the blades 21 and the blade 21, and the other end is communicated with the sealing gap; the right end of the seal ring 14 is provided with an inclined portion 26, and the distance between the inclined portion 26 and the radial portion 24 gradually increases from the radially outer side to the radially inner side in the radial direction, forming a seal portion.
The through hole 25 forms a fourth passage 34, the seal gap forms a fifth passage 35, a sixth passage 36 is formed between the left side of the axial portion 23 and the volute return ring 11, and the fourth passage 34, the fifth passage 35 and the sixth passage 36 are communicated to form a second return passage.
Further, in the axial direction, the through hole 25 is located between the leading edge of the blade 21 and the inclined portion 26.
The present invention can further suppress surge and reduce noise by the design of the impeller return ring 22 and the plurality of through holes/through grooves 25, thereby improving the overall performance of the compressor.
Compared with the backflow structure in the prior art, the fluid machine/compressor for industrial production can further inhibit surge and reduce noise through the design of the impeller backflow ring, thereby improving the overall performance of the compressor and having better technical effects of inhibiting surge and reducing noise.
The above-described embodiments are illustrative of the present invention and not restrictive, it being understood that various changes, modifications, substitutions and alterations can be made herein without departing from the principles and spirit of the invention, the scope of which is defined by the appended claims and their equivalents.
Claims (7)
1. A compressor for industrial production, it includes spiral case (1), impeller (2), spiral case return ring (11), first return passage (12), diffuser (13), the inner periphery of the inducer of spiral case is provided with spiral case return ring, and spiral case return ring is connected with the spiral case, for the stationary part, forms first return passage between spiral case return ring and the spiral case, and the impeller includes a plurality of blades (21) along circumference distribution, and the periphery of impeller is provided with the diffuser, its characterized in that: the periphery of the blade is connected with an impeller return ring (22), and the impeller return ring and the blade are connected into a whole and are rotating parts; the impeller backflow ring (22) comprises an axial part (23) and a radial part (24) which are connected, and the axial part and the radial part form an L-shaped structure;
the right end of the volute backflow ring is provided with a sealing ring (14), the sealing ring and the axial part are arranged oppositely in the radial direction, and a radial sealing gap is formed between the sealing ring and the axial part; a first channel (31) is formed between the right side of the radial portion and the volute, a second channel (32) is formed between the periphery of the volute backflow ring and the volute, a third channel (33) is formed between the left side of the volute backflow ring and the volute, and the first channel, the second channel and the third channel are communicated and form a first backflow channel.
2. A compressor for industrial use as claimed in claim 1 wherein said radial portion has an outer diameter greater than an outer diameter of the volute recirculation ring.
3. A compressor for industrial production according to claim 2, wherein the axial portion is provided with a plurality of through holes (25) distributed along a circumferential direction of the axial portion, one end of the through holes communicating with the flow passage between the vane and the other end communicating with the seal gap.
4. A compressor for industrial production according to claim 3, wherein the right end of the seal ring is provided with an inclined portion (26) whose distance from the radial portion in the radial direction gradually increases from the radially outer side to the radially inner side to form the seal portion.
5. A compressor for industrial use according to claim 4 wherein said through hole constitutes a fourth passage (34), the seal clearance constitutes a fifth passage (35), a sixth passage (36) is formed between the left side of the axial portion and the volute return ring, and the fourth, fifth and sixth passages communicate and constitute a second return passage.
6. A compressor for industrial use according to claim 5 wherein the through hole is located between the leading edge of the blade and the inclined portion in the axial direction.
7. A compressor for industrial production according to claim 1 or 2, wherein the compressor is a centrifugal compressor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011014045.6A CN112012957B (en) | 2020-09-24 | 2020-09-24 | A compressor for industrial production |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011014045.6A CN112012957B (en) | 2020-09-24 | 2020-09-24 | A compressor for industrial production |
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| Publication Number | Publication Date |
|---|---|
| CN112012957A CN112012957A (en) | 2020-12-01 |
| CN112012957B true CN112012957B (en) | 2022-07-19 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202011014045.6A Active CN112012957B (en) | 2020-09-24 | 2020-09-24 | A compressor for industrial production |
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Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN113775560B (en) * | 2021-09-15 | 2023-12-19 | 浙江理工大学 | Sealing structure of rocket engine turbine pump |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006342682A (en) * | 2005-06-07 | 2006-12-21 | Ishikawajima Harima Heavy Ind Co Ltd | Operation range expanding method and device of centrifugal compressor |
| CN103174678A (en) * | 2013-03-26 | 2013-06-26 | 哈尔滨工程大学 | Centrifugal compressor air guiding recycling structure with multiple channels |
| JP2015175250A (en) * | 2014-03-13 | 2015-10-05 | 株式会社Ihi | centrifugal compressor |
| JP2015190391A (en) * | 2014-03-28 | 2015-11-02 | 株式会社Ihi | centrifugal compressor |
| CN105317746A (en) * | 2014-07-16 | 2016-02-10 | 丰田自动车株式会社 | Centrifugal compressor |
-
2020
- 2020-09-24 CN CN202011014045.6A patent/CN112012957B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006342682A (en) * | 2005-06-07 | 2006-12-21 | Ishikawajima Harima Heavy Ind Co Ltd | Operation range expanding method and device of centrifugal compressor |
| CN103174678A (en) * | 2013-03-26 | 2013-06-26 | 哈尔滨工程大学 | Centrifugal compressor air guiding recycling structure with multiple channels |
| JP2015175250A (en) * | 2014-03-13 | 2015-10-05 | 株式会社Ihi | centrifugal compressor |
| JP2015190391A (en) * | 2014-03-28 | 2015-11-02 | 株式会社Ihi | centrifugal compressor |
| CN105317746A (en) * | 2014-07-16 | 2016-02-10 | 丰田自动车株式会社 | Centrifugal compressor |
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| CN112012957A (en) | 2020-12-01 |
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Effective date of registration: 20220622 Address after: 803, floor 8, No. 101, floor 1-12, building 3, yard 53, Xiaoying North Road, Chaoyang District, Beijing 100101 Applicant after: Beijing prehot Energy Technology Co.,Ltd. Address before: 330000 No. 899 Torch Five Road, Nanchang High-tech Industrial Development Zone, Nanchang City, Jiangxi Province Applicant before: JIANGXI ZIXUAN TECHNOLOGY CO.,LTD. |
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