CN111963461A - Novel disrotatory fan - Google Patents
Novel disrotatory fan Download PDFInfo
- Publication number
- CN111963461A CN111963461A CN202010808687.7A CN202010808687A CN111963461A CN 111963461 A CN111963461 A CN 111963461A CN 202010808687 A CN202010808687 A CN 202010808687A CN 111963461 A CN111963461 A CN 111963461A
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- Prior art keywords
- impeller
- counter
- rotating fan
- primary
- flow
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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
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
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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
- F04D19/00—Axial-flow pumps
- F04D19/007—Axial-flow pumps multistage fans
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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
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
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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
- F04D29/52—Casings; Connections of working fluid for axial pumps
- F04D29/522—Casings; Connections of working fluid for axial pumps especially adapted for elastic fluid pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention provides a novel counter-rotating fan which comprises a casing, wherein a primary impeller and a secondary impeller are arranged in the casing along the axis of the counter-rotating fan, fluid enters the primary impeller in an oblique flow mode at an angle inclined to the axis of the counter-rotating fan, and finally flows out of the secondary impeller in an angle parallel to or inclined to the axis of the counter-rotating fan. The first-stage impeller adopts a meridian acceleration blade profile, is different from the traditional axial flow design and adopts a diagonal flow design, and the flow channel design can be better matched with the blades to provide an optimal pneumatic flow field. The counter-rotating fan creatively adopts the primary diagonal flow impeller and the secondary axial flow impeller, and the total result can achieve the performance target of the fan in higher pressure and wider stable operation area.
Description
Technical Field
The invention relates to an axial flow fan, in particular to an axial flow convection cyclone machine.
Background
The entire system through which the ventilator delivers air is called a ductwork. The pressure loss and the resistance of the pipe network formed during the gas transportation process are caused by friction, vortex, impact during sudden diffusion, and the like. In order to obtain and maintain a certain air flow in the network, it is necessary to have the ventilator generate a pressure equal to the resistance of the network, given the flow and velocity.
The marine ventilator is generally classified into a centrifugal ventilator and an axial-flow ventilator in terms of structural form. Axial fans are becoming more and more the main fan type of marine ventilation systems due to their characteristics of large flow, convenient arrangement of pipes, etc. Due to the special limitations of small size and light weight of the marine fan, when the design of a single-stage axial flow fan cannot meet the technical requirements, or factors such as processing period, cost and the like are considered, the counter-rotating fan becomes the first choice for the high-performance marine fan.
Counter-rotating fans are a special form of axial flow fans. Two impellers of the device are guide vanes, and two stages of impellers are respectively arranged at the shaft extension ends of respective motors. The two motors have opposite rotation directions, so that a contra-rotation structure is formed. The adoption of the disrotatory structure reduces guide vanes between the conventional two stages of impellers, thereby improving the static pressure efficiency of the fan. According to the change of the ventilation resistance, the optimal matching relation of the two stages of impellers is selected, so that the fan efficiency is higher, and the efficient operation range is wider.
However, when a higher pressure output is required for a certain air quantity, the conventional counter-rotating fan composed of two axial-flow impellers cannot meet the requirement of pneumatic performance.
Disclosure of Invention
Aiming at the defects of the prior art, the invention aims to provide a counter-rotating fan, which further improves the pneumatic performance of the fan through the structural design of two stages of impellers.
In order to achieve the purpose, the invention adopts the following technical means:
a contra-rotating fan comprises a shell, a primary impeller and a secondary impeller are arranged in the shell along the axial line of the contra-rotating fan, fluid enters the primary impeller in an oblique flow at an angle oblique to the axial line of the contra-rotating fan, and finally flows out of the secondary impeller in an angle parallel to or oblique to the axial line of the contra-rotating fan.
Preferably, the first-stage impeller adopts a meridional acceleration blade type, the relative diameter of a hub at the inlet side of the first-stage impeller is 0.50-0.56, and the relative diameter of a hub at the outlet side of the first-stage impeller is 0.65-0.7.
More preferably, the casing of the first-stage impeller section is designed to be a conical cylinder, and the blade top gap between the first-stage impeller and the casing is 0.8-1.5% of the length of the blade.
In particular, the axial clearance between the first-stage impeller and the second-stage impeller is adjustable within the range of 40mm-150 mm.
Furthermore, the external dimension of the counter-rotating fan shell is less than phi 930mm x1300mm, the weight is less than 700 kg, and when the flow is 23000m3/h, the wind pressure is not less than 2000 pa.
Preferably, the first-stage impeller and the second-stage impeller are both directly suspended at the shaft extension end of the counter-rotating fan motor and are driven by two motors with the same rotating speed and power.
Compared with the prior art, the invention has the following beneficial technical effects:
the counter-rotating fan creatively adopts the primary diagonal flow impeller and the secondary axial flow impeller, and the total result can achieve the performance target of the fan in higher pressure and wider stable operation area.
The counter-rotating fan of the invention has the advantages that under the conditions of limited overall dimension and weight (the overall dimension is ensured to be less than phi 930mmx1300mm, the weight is less than 700 kilograms, and the flow requirement of the counter-rotating fan is 23000m3And/h), the actual measurement of the air pressure reaches 2080pa, and the traditional counter-rotating fan cannot achieve the purpose of the invention.
Meanwhile, the two-stage impeller of the counter-rotating fan is directly hung at the shaft extension end of the motor, two identical motors with the same rotating speed and power are preferentially selected for driving, the counter-rotating fan is more suitable for ships, has interchangeability and universality, and facilitates management in the whole life cycle range of organization production, replacement of spare parts in the later period and the like.
Drawings
FIG. 1 is a schematic view of a counter-rotating fan according to the present invention.
Fig. 2 is a schematic view of a counter-rotating fan (inorganic shell part) according to the present invention.
FIG. 3 is a schematic view of a primary impeller.
FIG. 4 is a schematic view of a counter-rotating fan according to the present invention.
Fig. 5 is a schematic view of the present invention in which the housing is partially a tapered cylinder.
Fig. 6 and 7 show equivalent alternatives to the cyclone of the present invention.
FIG. 8 is a domain solution result graph.
FIG. 9 is a face grid result graph.
FIG. 10 is a graph of boundary layer mesh results.
FIG. 11 is a core hexahedral mesh result diagram.
Fig. 12 is a graph of the overall grid results.
FIG. 13 is a result graph of the global streamline distribution of the design condition.
FIG. 14 is a graph of the design condition half-section velocity vector distribution results.
Wherein: 1 casing, 2 first-stage impellers, 3 second-stage impellers, 4 inlet side hubs and 5 outlet side hubs.
The embodiments of the present invention will be further described with reference to the drawings and examples.
Detailed Description
Generally, the impeller is composed of a hub and a plurality of blades arranged on the outer wall of the hub, all the blades are annularly arrayed on the hub by taking the central axis of the hub as a center, and the meridional acceleration blade profile of the invention is a traditional meridional acceleration blade profile, namely, the blade profile is twisted by an angle in the radius direction to form the blades. The outer edge of the blade and the central axis of the hub form an angle of 20-30 degrees. Typically, the blade includes a shank, and the blade is mounted to the hub by passing through the hub with a nut and spring washer. The position relationship such as the mounting distance between the blades in the first-stage impeller or the blades in the second-stage impeller in the invention is related to the hub diameter and the number of the blades, and generally, the number of the blades is between 5 and 14. Because the invention focuses on the hub design, the traditional meridional acceleration blade profile can be used in the scheme of the invention without making excessive requirements on the blade profile and the like of the blade.
In addition, the blade top gap is the distance between the outer side of the first-stage impeller and the casing, and the straightening is generally 0.8-1.5% of the length of the blade, and preferably is 0.8%.
The axial clearance between the primary impeller and the secondary impeller is the axial distance along the shaft of the contra-rotating fan.
The technical key point of the invention is that in the design of the counter-rotating fan, the design method of the diagonal flow impeller is adopted at the first stage, and the traditional counter-rotating fan can not realize the aim of the invention under the conditions of limited overall dimension and weight.
As shown in fig. 8-14, in order to obtain the excellent matching relationship of the two-stage flow field, the most popular analog calculation method in the industry is used to perform adjustment and repeated calculation for many times, and finally, an ideal matching effect is obtained. The process is described as follows: firstly, a calculation domain is constructed through an assembly drawing of the cyclone fan, and an accurate performance result is obtained through modeling solving and grid division of a single flow channel. The calculation model established is shown in fig. 8 below. Adopting a plurality of grid combination modes to carry out gridding division: the main channel uses a high-precision surface grid; adding boundary layer grids around the airflow channel in consideration of boundary layer flow; the calculation is more accurate by adopting the core hexahedral mesh except for the boundary layer (see fig. 9 and 12). And after the grid division is completed, performing simulation calculation on the flow field. Corresponding numerical calculation is respectively carried out on different working conditions, the streamline and the velocity vector distribution of the numerical simulation result of the design point are shown in a figure 13 and a figure 14, and the flow can reach the expected requirement under the set pressure level as can be seen from a streamline graph. The flow is very smooth and no separation of the gas streams occurs. The unit can stably operate under the working condition. After the optimal matching calculation of the two-stage impeller flow field is obtained, a detailed structural design is carried out. After the production of a prototype object is completed, on the basis of a large number of tests, a wider non-stall operation area is obtained by adjusting different axial gaps between two stages of impellers (shortening or lengthening the distance between the two stages of impellers), which has very important significance for the reliability and safety of a fan.
Example 1:
the embodiment provides a contra-rotating fan, which comprises a casing 1, wherein a primary impeller 2 and a secondary impeller 3 are arranged in the casing along the axial line of the contra-rotating fan, fluid enters the primary impeller 1 in an oblique flow at an angle oblique to the axial line of the contra-rotating fan, and finally flows out of the secondary impeller 3 in an angle parallel to or oblique to the axial line of the contra-rotating fan.
The key point of the technology of the invention is that in the design of the counter-rotating fan, the design method of the diagonal flow impeller is adopted at the first stage. The second stage of the counter-rotating fan can adopt the design method of an axial flow type impeller or a diagonal flow type impeller; meanwhile, in order to have wider application range, on the basis that the primary impeller is in a diagonal flow mode, the casing can also be designed into a tapered cylinder in a matching mode, so that the design target of higher performance is achieved. When the primary stage is in a diagonal flow mode, the blade top gap between the primary stage impeller and the casing can be 0.8-1.5% of the length of the blade according to the conventional design. Smaller tip clearances are recommended without increasing costs.
Different from the traditional axial flow design, the first-stage impeller or the first-stage impeller adopts a diagonal flow design, and the flow channel design can be better matched with the blades to provide an optimal pneumatic flow field. The inclined flow impeller adopts a traditional meridional acceleration blade profile, and the blade profile is twisted by an angle in the radius direction to form a blade. The type of blade has strong work-doing capability, and the diameter of the fan impeller is the smallest under the same pressure. Meanwhile, under the matching of the oblique flow channel, the size of the fan is further reduced, and conditions are created for the integral weight reduction of the fan. The design of the diagonal flow channel is shown in table 1 below:
TABLE 1
| Relative diameter of hub at inlet side of first-stage impeller | Relative diameter of hub at outlet side of first-stage impeller |
| 0.50～0.56 | 0.65～0.70 |
The second stage impeller is designed in axial flow or diagonal flow mode. Through the design of the better performance matching relation of the two stages of impellers, a range with higher efficiency and wider stable operation range can be obtained.
In particular, the axial clearance between the first-stage impeller 2 and the second-stage impeller 3 is adjustable within the range of 40mm-150mm, and on the basis of a large number of tests, by adjusting different axial clearances between the two-stage impellers (shortening or lengthening the distance between the two-stage impellers), a wider non-stall operating region is obtained, which has very important significance for the reliability and safety of the fan. The comparative data are listed in table 2 below:
TABLE 2
Effect verification:
the counter-rotating fan of the invention is utilized to complete the sample machine physical test, the performance reaches the design target, and the invention is proved to be feasible and explained as follows:
by applying the design of the invention, the prototype conditions applied are as follows: the flow of the counter-rotating fan is required to be 23000m under the limiting conditions that the overall dimension of the counter-rotating fan is ensured to be less than phi 930mmx1300mm and the weight is less than 700 kg3At the time of/h, the wind pressure reaches 2000 pa. The test result of a real object prototype proves that when the flow of the counter-rotating fan reaches the required value of 23000m3/h, the actual measurement of the wind pressure reaches 2080pa, the actual measurement of the pneumatic performance meets the design requirement, and the test result fully proves that the design structure is effective.
It should be noted that the present invention is not limited to the only embodiment, and the object of the present invention can be achieved by appropriately optimizing the blade profile by the embodiment given below. In the process of developing a specific engineering project, due to the consideration of comprehensive factors such as process level, supply period, production cost and the like, the following embodiments can be used as alternatives, as shown in fig. 4-7, the machine shell, the blade profile and the like are respectively optimized properly, but the invention is within the protection scope.
Claims (7)
1. The utility model provides a to cyclone, includes casing (1), sets up one-level impeller (2) and second grade impeller (3) along to cyclone axis in casing (1), its characterized in that, one-level impeller inlet side wheel hub (4) relative diameter is greater than one-level impeller outlet side wheel hub (5) relative diameter, and fluid gets into one-level impeller (2) with the angle skew flow that inclines with the cyclone axis, flows out second grade impeller (3) with the angle that is parallel with the cyclone axis or inclines at last.
2. The counter-rotating fan according to claim 1, wherein the primary impeller (2) is of a meridional acceleration blade type, the relative diameter of the hub (4) on the inlet side of the primary impeller (2) is 0.50-0.56, and the relative diameter of the hub (5) on the outlet side of the primary impeller (2) is 0.65-0.7.
3. The counter-rotating fan according to claim 1, characterized in that the casing of the primary impeller (2) section is designed as a conical cylinder, and the blade tip clearance between the primary impeller (2) and the casing (1) is 0.8-1.5% of the blade length.
4. Counter-rotating fan according to claim 1, characterized in that the axial gap between the primary (2) and secondary (3) impellers is adjustable between 40mm and 150 mm.
5. Counter-rotating fan according to claim 1, characterized in that the counter-rotating fan casing (1) has dimensions of less than Φ 930mm 1300mm, a weight of less than 700 kg and a flow rate of 23000m3And at the time of/h, the wind pressure is not less than 2000 pa.
6. The counter-rotating fan according to claim 1, wherein the primary impeller (2) and the secondary impeller (3) are both directly suspended at the shaft extension end of the counter-rotating fan motor and are driven by two motors with the same rotating speed and power.
7. The counter-rotating fan according to claim 1, wherein an inlet guide housing and an outlet guide housing are respectively provided on the outer sides of the primary impeller (2) and the secondary impeller (3).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010808687.7A CN111963461A (en) | 2020-08-12 | 2020-08-12 | Novel disrotatory fan |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010808687.7A CN111963461A (en) | 2020-08-12 | 2020-08-12 | Novel disrotatory fan |
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| Publication Number | Publication Date |
|---|---|
| CN111963461A true CN111963461A (en) | 2020-11-20 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010808687.7A Pending CN111963461A (en) | 2020-08-12 | 2020-08-12 | Novel disrotatory fan |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113441295A (en) * | 2021-06-04 | 2021-09-28 | 江西中烟工业有限责任公司 | High-efficiency cyclone separator with built-in impeller structure |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201461470U (en) * | 2009-07-22 | 2010-05-12 | 哈尔滨航飞工业机械有限公司 | Explosion-proof type pressing type disrotatory axial flow local ventilator for mine |
| CN102094837A (en) * | 2009-12-14 | 2011-06-15 | 国立大学法人东京大学 | Double counter-rotating axial flow fan |
| CN103912509A (en) * | 2013-01-05 | 2014-07-09 | 上海涌华通风设备有限公司 | Meridionally-accelerated mixed-flow fan |
| JP5937490B2 (en) * | 2012-11-14 | 2016-06-22 | ミネベア株式会社 | Blower |
| CN206299588U (en) * | 2016-11-30 | 2017-07-04 | 威海克莱特菲尔风机股份有限公司 | Axial flow blower with zero clearance formula fan air drum |
| CN108644126A (en) * | 2018-04-16 | 2018-10-12 | 江苏大学镇江流体工程装备技术研究院 | A kind of shaft-driven guide-vane of list is to revolving mixed-flow pump |
| CN209053821U (en) * | 2018-10-15 | 2019-07-02 | 广东美的白色家电技术创新中心有限公司 | To counter-rotating fan |
| CN111043063A (en) * | 2018-10-15 | 2020-04-21 | 广东美的白色家电技术创新中心有限公司 | Counter-rotating fan |
-
2020
- 2020-08-12 CN CN202010808687.7A patent/CN111963461A/en active Pending
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201461470U (en) * | 2009-07-22 | 2010-05-12 | 哈尔滨航飞工业机械有限公司 | Explosion-proof type pressing type disrotatory axial flow local ventilator for mine |
| CN102094837A (en) * | 2009-12-14 | 2011-06-15 | 国立大学法人东京大学 | Double counter-rotating axial flow fan |
| JP5937490B2 (en) * | 2012-11-14 | 2016-06-22 | ミネベア株式会社 | Blower |
| CN103912509A (en) * | 2013-01-05 | 2014-07-09 | 上海涌华通风设备有限公司 | Meridionally-accelerated mixed-flow fan |
| CN206299588U (en) * | 2016-11-30 | 2017-07-04 | 威海克莱特菲尔风机股份有限公司 | Axial flow blower with zero clearance formula fan air drum |
| CN108644126A (en) * | 2018-04-16 | 2018-10-12 | 江苏大学镇江流体工程装备技术研究院 | A kind of shaft-driven guide-vane of list is to revolving mixed-flow pump |
| CN209053821U (en) * | 2018-10-15 | 2019-07-02 | 广东美的白色家电技术创新中心有限公司 | To counter-rotating fan |
| CN111043063A (en) * | 2018-10-15 | 2020-04-21 | 广东美的白色家电技术创新中心有限公司 | Counter-rotating fan |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113441295A (en) * | 2021-06-04 | 2021-09-28 | 江西中烟工业有限责任公司 | High-efficiency cyclone separator with built-in impeller structure |
| CN113441295B (en) * | 2021-06-04 | 2022-07-15 | 江西中烟工业有限责任公司 | High-efficiency cyclone separator with built-in impeller structure |
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Application publication date: 20201120 |