CN110940526B - Blending device of single-stranded high-temperature hot gas and cold air for engine test bed - Google Patents
Blending device of single-stranded high-temperature hot gas and cold air for engine test bed Download PDFInfo
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Abstract
本发明公开了一种发动机试车台用单股高温热气与冷空气的掺混装置，其包括同轴线配置的冷空气腔体、掺混段内腔体和稳流段，掺混段内腔体由扩张段、等直段和收缩段依次相连而成，其位于扩张段的端部设置有高温热气进气口，另一端与稳流段相连；冷空气腔体通过外壳体密封包裹住掺混段内腔体而构成，在外壳体上设置有多个冷空气进气口；在扩张段上设置有多个冷空气稳流孔、在等直段上设置有多个冷空气掺混孔、在收缩段上设置有多个使冷空气逆气流吹入的冷空气吹离孔；在稳流段靠近出口的侧壁上设置有多个调压排气孔，与调压排气孔连接的调压管道上设置有调压阀。本发明能够满足3～10kg/s新型发动机试车台的低温度损失和气流均匀试验需求。
The invention discloses a single-strand high-temperature hot air and cold air mixing device for an engine test bench, which comprises a coaxially arranged cold air cavity, an inner cavity of a mixing section, a steady flow section, and an inner cavity of the mixing section. The body consists of an expansion section, an equal straight section and a contraction section which are connected in sequence. The end of the expansion section is provided with a high-temperature hot air inlet, and the other end is connected to the steady flow section; the cold air cavity is sealed and wrapped by the outer shell. The outer casing is provided with a plurality of cold air inlets; the expansion section is provided with a plurality of cold air stabilizing holes, and the equal straight section is provided with a plurality of cold air mixing holes . A plurality of cold air blow-off holes are arranged on the shrinking section to blow the cold air in against the airflow; a plurality of pressure regulating and exhaust holes are arranged on the side wall of the steady flow section near the outlet, which are connected with the pressure regulating and exhaust holes There is a pressure regulating valve on the pressure regulating pipeline. The invention can meet the low temperature loss and air flow uniformity test requirements of a 3-10kg/s new engine test bed.
Description
Technical Field
The invention relates to a single-strand high-temperature hot gas and cold air mixing device for an engine test bed.
Background
With the development of hypersonic aircraft technology, a scramjet engine is the key technology to be solved firstly, and a new engine test technology needs a test bed with the capability of being closer to a pure air test medium so as to eliminate the influence of combustion products on engine test data or avoid the occurrence of wrong engine test results. This kind of test bed generally adopts the two-stage heating mode, and the pure air heater is adopted to the first grade, and the combustion heater oxygenating gas mode is generally adopted to the second grade to obtain the test medium that is closer to pure and clean air, the test air current that lower combustion product quality accounts for the ratio promptly, and through mixing device, accurate control air current temperature makes the air current even, satisfies different flow requirement engine test requirements.
Compared with the conventional engine test bed, the new engine test bed requires that the mass ratio of combustion products in the test medium is low enough, so that the temperature loss of the heated high-temperature test medium passing through the mixing device is small enough. Under the condition that the air heating capacity of the first-stage pure and clean air heater is limited, the temperature is generally lower than 700 ℃, if the temperature loss of the blending device behind the heater is increased, the increased temperature loss of the airflow behind the blending device can be overcome only by improving the heating capacity of the second-stage combustion heater and increasing the temperature of the airflow at the outlet of the heater, and the test airflow meeting the test requirement of the engine is obtained; meanwhile, the heating capacity of the second-stage combustion heater is improved, more fuel is required to be combusted, more heat energy is released, and the mass ratio of combustion products in the test airflow is improved. Therefore, new engine runs require a low temperature loss air flow blending device.
In order to control the proportion of combustion products to be lower, the temperature of test airflow heated by the two-stage heater is lower than 1150 ℃, and the temperature of test airflow passing through the blending device is not lower than 1000 ℃, so that the novel blending device needs to meet the requirements of low-temperature loss and airflow uniformity.
Among the new engine test beds, a small engine test bed is an essential device for performing a local test piece test of an engine. The flow and the total energy of the test airflow are small, single-stranded high-temperature test airflow is obtained through a single set of two-stage heaters, the temperature of the test airflow is accurately controlled by mixing a small amount of cold air, the airflow is uniform, and the design requirement of a 3-10 kg/s novel engine test bed is met.
The defects of the prior art are as follows:
a. in the literature, "a high-temperature gas mixing device" the mixing device is a conventional engine test bed device, and in the test bed, high-temperature gas is obtained by obtaining the high-temperature gas through a primary combustion heater and supplementing oxygen, and then cold air is mixed through a mixer to obtain a test medium meeting requirements. The temperature of the combustion airflow of the incoming flow of the mixing device is up to 1000-1600 ℃, the temperature of the required test airflow is only 600 ℃, the mass ratio of the mixable cold air is very high, the cooling and heat insulation mode of the mixing device is not specially designed, and the temperature loss of the airflow is large after the mixing device is used. If being applied to novel engine test bed, along with the cold air flow accounts for the ratio and reduces, cold air mixing section heat protection structure must not satisfy the operation requirement.
b. The blending device in the literature 'high-reliability multi-blade cold and hot air flow blending turbulence device' is a conventional engine test bed device, can realize the blending of 1800K-magnitude high-temperature fuel gas with the flow of 5-20 kg/s and cold air with the flow of 3-50 kg/s, has high cold air mass ratio and large overall temperature loss, and cannot meet the use requirements of a novel test bed. The wall surface heat-proof mode is mainly that the heat-proof structure is directly realized by cold air. If being applied to novel engine test bed, along with the cold air flow rate ratio reduction, the cold air blending section must not satisfy the operation requirement.
c. In the conventional gas flow engine test bed mixing device, the mixing section usually adopts high-cold air to form air film cooling heat protection or adopts water cooling heat protection, the air flow uniform section adopts a water cooling structure to prevent heat, the temperature loss of high-temperature air flow of the structure is high, and the low-temperature loss test requirement of a 3-10 kg/s novel engine test bed cannot be met.
Disclosure of Invention
According to the blending device of the single-stranded high-temperature hot gas and cold air for the engine test bed, the temperature loss of the test airflow in the blending device is reduced through a specific blending configuration design, the low-temperature loss requirement and the airflow uniformity requirement of a 3-10 kg/novel engine test bed are met, and the test requirements of local test pieces of engines with different flow rates are met.
The single-stranded high-temperature hot gas and cold air mixing device for the engine test bed comprises a cold air cavity, a mixing section inner cavity and a steady flow section which are coaxially arranged, wherein the mixing section inner cavity is formed by sequentially connecting an expansion section, an equal straight section and a contraction section, a high-temperature hot gas inlet is formed in the end part of the expansion section, and the other end of the mixing section is connected with the steady flow section; the cold air cavity is formed by sealing and wrapping the inner cavity of the mixing section through an outer shell, and a plurality of cold air inlets are formed in the outer shell; the expansion section is provided with a plurality of cold air flow stabilizing holes, the equal straight section is provided with a plurality of cold air mixing holes, and the contraction section is provided with a plurality of cold air blow-off holes for blowing in cold air against airflow; the steady flow section is a short equal straight section, a plurality of pressure regulating exhaust holes are formed in the side wall close to the outlet of the steady flow section, and a pressure regulating valve is arranged on a pressure regulating pipeline connected with the pressure regulating exhaust holes.
Preferably said hot gas inlet is located on said axis.
Preferably, the number of the cold air inlets is 8 or 4, and the cold air inlets are uniformly arranged along the circumferential direction in a mode of surrounding the high-temperature hot air inlet, and the central axis of the cold air inlet is parallel to the axis.
Preferably cold air steady flow hole has evenly arranged 16 along circumference, and all porose axis extension lines pass through the axis, and with the contained angle of axis is 45, makes the cold air following current blow in the cavity in the blending section, cold air steady flow hole has independent pipe wall, runs through the outer shell in the expansion section of cavity in the blending section.
Preferably the cold air mixing hole sets up more than 2 rows along the axial, every row evenly is provided with 16 holes along circumference, and all porose axis extension lines pass through the axis, and with the axis is perpendicular, the cold air mixing hole has independent pipe wall, runs through the interior outer shell of the equal straight section of cavity in the mixing section.
Preferably, 16 holes are uniformly arranged in the cold air blow-off holes along the circumferential direction, the extension lines of the axes of all the holes pass through the axes and form an included angle of 60 degrees with the axes, so that the cold air is blown into the cavity in the blending section against the airflow, and the cold air blow-off holes are provided with independent pipe walls and penetrate through the inner shell and the outer shell of the contraction section in the blending section.
Preferably, the flow velocity of the steady flow section corresponding to the inner diameter of the steady flow section is equal to 30m/s, and the length of the steady flow section is 3 times of the inner diameter.
Preferably, the number of the pressure-regulating exhaust holes is 4 or 6, the extension line of the hole axis is intersected and vertical to the axis, the maximum flow is designed to be 4.5kg/s, and the air flow velocity in the hole corresponding to the hole diameter is 60-100 m/s.
Preferably, cavity and stationary flow section in the blending section all adopt double-deck casing to carry out thermal-insulated heat preservation, wherein, the expansion section the contraction section with the outer casing of stationary flow section adopts the water-cooling casing, the outer casing of the equal straight section of cavity in the blending section is through the cold air heat transfer cooling of cold air cavity.
Preferably the cold air cavity flow design is 0.7 ~ 1.5kg/s, and inside circumference evenly sets up 8 or 4 baffles, will the cold air cavity is divided into a plurality of independent cavitys, and every independent cavity corresponds the same quantity's cold air inlet, cold air steady flow hole, cold air mixing hole and cold air blow-off hole, and the maximum velocity of flow that cold air passageway size corresponds is less than 8 m/s.
Compared with the existing mixing device, the mixing device reduces the overall temperature loss of the mixing device through expanding and contracting modes such as the internal pneumatic configuration of the mixing section, the specific cold air injection mode, the short steady flow section and the overall heat insulation and preservation scheme of the double-layer shell, and the whole device has the functions of accurate temperature control, stable pressure, uniform flow, different flow tests of engine test pieces and the like, and meets the requirements of low temperature loss and uniform airflow tests of a 3-10 kg/s novel engine test bed.
Drawings
FIG. 1 is a schematic view of a blending apparatus according to the present invention.
Description of the symbols:
1 high-temperature hot gas inlet; 2 a cold air inlet; 3, a cold air cavity; 4, a cold air steady flow hole; 5 cold air mixing holes; 6 blowing cold air away from the holes; 7 mixing section expanding section outer shell-water cooling shell; 8 mixing section equal straight section outer shell; 9 mixing section contraction section outer shell-water cooling shell; 10 outer shell of steady flow section-water cooling shell; 11 a porous inner insulating shell; 12 a choke ring; 13 pressure regulating exhaust holes; 14 a specific engine test piece throttling throat; 15 pressure regulating pipelines; 16 an exhaust cooling section; 17 pressure regulating valve.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and specific embodiments.
The single-strand high-temperature hot gas and cold air mixing device for the engine test bed is shown in figure 1. Single-stranded high-temperature hot gas with a certain flow enters the inner cavity of the mixing section from the high-temperature hot gas inlet 1; cold air with micro-adjustable flow enters a cold air cavity 3 through a plurality of cold air inlets 2 which are uniformly distributed in the circumferential direction, and then enters an inner cavity of the mixing section through cold air stabilizing holes 4, cold air mixing holes 5 and cold air blow-off holes 6 which penetrate through outer shells and porous inner heat insulation shells of the mixing section; in the inner cavity of the blending section, the entering high-temperature hot gas and cold air are blended; after mixing, the gas enters the whole cavity in the steady flow section to obtain a uniform test medium; the uniform test medium is supplied to an engine test piece through the throttling throat, and redundant test medium is discharged into the atmosphere through the pressure regulating exhaust hole 13, the pressure regulating pipeline 15, the exhaust cooling section 16, the steady flow section pressure regulating valve 17 and the like in sequence. The scheme of the invention is explained in detail as follows:
(1) the design flow of high-temperature hot air of the mixing device is 6-9 kg/s, the design flow of cold air is 0.7-1.5 kg/s, the ratio of the cold air to the cold air is lower than 15%, the maximum exhaust flow is not higher than 4.5kg/s, and the flow of a local test piece of the engine is 3-10 kg/s, which is a design index of the mixing device.
(2) The flow of the high-temperature hot gas inlet 1 is designed to be 6-9 kg/s, the flow speed corresponding to the preferred inner diameter is not lower than 110m/s, and the wall surface of the high-temperature hot gas inlet is water-cooled for heat protection. High-temperature hot gas is blown into the inner cavity of the blending section at a high speed, so that the high-temperature hot gas has better anti-interference performance;
(3) an inner cavity structure of a blending section which is expanded and contracted is adopted, the preferred diameter of the inner cavity of the blending section is 1.3 times of the diameter of the steady flow section, and the preferred length of the blending section is 2 times of the diameter of the inner cavity;
(4) the flow of the cold air inlet 2 is designed to be 0.7-1.5 kg/s, the cold air inlet is circumferentially and uniformly arranged, the number of the air inlets is preferably 8 or 4, and the flow speed corresponding to the inner diameter of the air inlet is preferably 20-25 m/s. The upper stream of the cold air inlet 2 is provided with a throttling throat and a pressure regulating valve, the pressure in front of the throttling throat is accurately and micro-regulated, the micro-regulation of the cold air flow is realized, and the cold air flow is directly mixed with high-temperature hot air, so that the stable control of the temperature of the high-temperature air flow in the mixing device is realized.
(5) The cold air cavity flow design is 0.7-1.5 kg/s, and the whole is rotatory passageway, and inside circumference evenly sets up the baffle, divides the cold air cavity into a plurality of independent cavitys, and every independent cavity corresponds the same quantity cold air inlet 2, cold air steady flow hole 4, cold air mixing hole 5, cold air blow-off hole 6, and preferred baffle quantity is 8 or 4, and the preferred maximum velocity of flow of cold air passageway size is less than 8 m/s. This design makes the cold air cavity internal flow even, ensures that the steady discharge orifice of cold air, cold air mixing hole, the flow in cold air blow-off hole distribute according to the design on the low reaches mixing section casing, ensures the heat protection effect and the thermal-insulated effect of mixing section under less cold air flow, ensures the low disturbance of cold air to high temperature steam simultaneously.
(6) The overall heat-proof heat-preservation layout scheme of the porous inner-layer heat-insulation shell and each section of outer-layer shell is adopted. The porous inner layer heat insulation shell is made of high-temperature alloy materials, the thickness is preferably 3-5 mm, micropores are uniformly distributed on the porous inner layer heat insulation shell, the diameter of each micropore is preferably 2-3 mm, and the distance between every two adjacent micropores is preferably 20 mm; a gap layer is arranged between the porous inner-layer heat-insulating shell and each outer-layer shell, and a choke ring 12 is axially arranged on the gap layer to prevent airflow of the gap layer from flowing along the axial direction and reduce convection heat exchange of the airflow in the gap layer, the thickness of the gap layer is preferably 30mm or more, the inner surface of the choke ring 12 is connected with the porous inner-layer heat-insulating shell in a welding way, the outer surface of the choke ring 12 is in clearance fit with each section of outer-layer shell, and the distance between the choke rings along the wall surface is preferably 600 mm; the outer shells of the mixing section expansion section, the mixing section contraction section and the flow stabilization section are water-cooled shells, the outer shells of the mixing section equal-straight sections are cooled through cold air heat exchange of a cold air cavity, and the wall thickness of each outer shell is determined according to the pressure bearing requirement. Through the static air bed of being close in the interstitial layer, make between porous inlayer thermal-insulated casing and each outer casing can only pass through the heat conduction of air and the radiation mode heat transfer between the surface, the heat transfer capacity of these two kinds of heat transfer modes is less than the heat transfer capacity of convection heat transfer greatly under 1000 ℃ of the magnitude of a class in service behavior, double shell design makes thermal-insulated ability improve greatly, under the effect of high temperature test medium, porous inlayer casing bears the high temperature and does not bear the high pressure, each section outer casing bears the high pressure and does not bear the high temperature, can change the design and satisfy the high temperature high pressure resistant demand. Meanwhile, the porous inner shell is a high-temperature shell, so that the temperature difference between the shell and the internal airflow is greatly reduced, the heat transfer energy loss of the high-temperature airflow is reduced, and the temperature loss of the high-temperature airflow in the mixing device is reduced.
(7) The design flow rate of cold air in the cold air stabilizing hole 4 in the blending section is preferably 2% -3%, the cold air is uniformly distributed in the circumferential direction, the number of the preferred holes is 16, the axis extension lines of all the holes pass through the axis of the blending device, the holes and the axis of the blending device form an included angle, so that the cold air is blown into the inner cavity of the blending section along with the air flow, the preferred included angle is 45 degrees, the flow rate of the cold air in the holes corresponding to the preferred aperture is not lower than 40m/s, and the cold air stabilizing hole is provided with an independent pipe wall and penetrates through the inner shell and the outer shell of the expanding section of the blending section. On one hand, a small amount of cold air is blown into the inner cavity of the mixing section through the dispersed cold air stabilizing holes, so that the disturbance intensity of the cold air can be reduced; on the other hand, by adopting the blowing mode, the high-temperature air in the inner cavity expansion section of the blending section is stably blown away from the inner shell of the expansion section of the blending section, so that the heat exchange effect of high-temperature hot gas and the wall surface is reduced, and the temperature loss of high-temperature air flow in the blending device can be reduced; and thirdly, the cold air flow stabilizing hole penetrates through the gap layer between the inner shell and the outer shell in a design, so that the speed of the air flow speed in the gap layer is not increased, the convective heat transfer effect of the gap layer between the inner shell and the outer shell in the expansion section of the mixing section is ensured to be at a low level, and the low temperature loss of the internal high-temperature air flow is ensured.
(8) The design flow rate of cold air of the cold air mixing holes 5 in the mixing section is preferably 6-7%, the row number of the axial holes is preferably not less than 2, the single row of holes are circumferentially and uniformly arranged, the number of the single row of holes is preferably 16, the extension lines of the axes of all the holes pass through the axis of the mixing device and are perpendicular to the axis, the flow rate of cold air in the holes corresponding to the preferred aperture is not less than 40m/s, and the cold air mixing holes are provided with independent pipe walls and penetrate through the inner shell and the outer shell of the straight section of the mixing section. On one hand, cold air is blown into the inner cavity of the blending section through the dispersed cold air blending holes, so that the disturbance intensity of the cold air can be reduced; on the other hand, a small amount of cold air is blown into the inner cavity of the equal straight section of the blending section through the cold air blending hole, so that high-temperature air flow can be far away from the wall surface of the equal straight section, the heat exchange effect of high-temperature hot air and the wall surface is reduced, and the temperature loss of the high-temperature air flow in the blending device can be reduced; and thirdly, the cold air mixing holes are designed in a penetrating way, so that cold air does not enter a gap layer between the inner shell and the outer shell of the equal straight section of the mixing section, the speed of the air flow velocity in the gap layer is not increased, the convection heat exchange effect of the gap layer between the inner shell and the outer shell of the equal straight section of the mixing section is ensured to be at a low level, and the low-temperature loss of high-temperature air flow of the equal straight section of the mixing section is ensured.
(9) The design flow rate of cold air of the cold air blow-off holes 6 in the blending section is preferably 4% -5%, the cold air blow-off holes are circumferentially and uniformly arranged, the number of the preferred holes is 16, the axis extension lines of all the holes pass through the axis of the blending device, the holes and the axis of the blending device form an included angle to enable the cold air to be blown into the cavity in the blending section in a reverse airflow manner, the preferred included angle is 60 degrees, the flow rate of cold air in the holes corresponding to the preferred aperture is not lower than 40m/s, and the cold air blow-off holes are provided with independent pipe walls and penetrate through the inner shell and the outer shell of the contraction section of the blending section. On one hand, the dispersed cold air blow-off holes 6 blow cold air into the inner cavity of the blending section, so that the disturbance intensity of the cold air can be reduced; on the other hand, a small amount of cold air is blown into the inner cavity of the contraction section of the blending section through the cold air blow-off holes, so that high-temperature air flow can be far away from the wall surface of the contraction section of the blending section, the heat exchange effect of high-temperature hot air and the wall surface is reduced, and the temperature loss of the high-temperature air flow in the blending device can be reduced; the cold air blow-off hole penetrates through the design, so that the cold air does not enter a gap layer between the inner shell and the outer shell of the equal straight section of the mixing section, the speed of the air flow velocity in the gap layer is not increased, the convection heat exchange effect of the gap layer between the inner shell and the outer shell of the equal straight section of the mixing section is ensured to be at a low level, and the low temperature loss of the high-temperature air flow of the equal straight section of the mixing section is ensured.
(10) And a short steady flow section pneumatic layout is adopted, the flow velocity of the steady flow section corresponding to the inner diameter of the steady flow section is preferably not higher than 30m/s, and the length of the steady flow section is preferably 3 times of the inner diameter. On one hand, the specific cold air injection mode is adopted, so that the disturbance intensity of the cold air is low, and the requirement on uniformity of airflow can be met by adopting the short steady flow section pneumatic layout; on the other hand, the short steady flow section layout is adopted, the energy loss distance of the high-temperature airflow is reduced, and finally the temperature loss of the high-temperature airflow is reduced.
(11) The maximum flow design requirement of the pressure-regulating exhaust holes 13 is 4.5kg/s, the pressure-regulating exhaust holes are arranged near the outlet of the steady flow section and are uniformly distributed in the circumferential direction, the number of the optimized holes is 4 or 6, the extension lines of the axes of the holes are intersected and vertical to the axis of the rectifying device, the air flow speed in the holes corresponding to the optimized hole diameter is 60-100 m/s, and the shell of the pressure-regulating exhaust holes is a water-cooling pressure-bearing shell.
(12) The downstream of the pressure regulating vent hole 13 is provided with a pressure regulating pipeline 15, an exhaust cooling section 16 and a pressure regulating valve 17 in sequence, the shell of the pressure regulating pipeline is a water-cooled shell, the exhaust cooling section preferably adopts a water spray cooler or a shell-and-tube heat exchanger, and the pressure regulating valve adopts a conventional pressure regulating valve. And redundant high-temperature air flow in the mixing device is discharged by adjusting the pressure regulating valve, so that the pressure stability control of the high-temperature air flow is realized.
(13) And the downstream of the outlet of the steady flow section is provided with throttling throats 14 of specific engine test pieces with different sizes, and the system is combined to realize the test requirement of the engine local test piece with the flow of 3-10 kg/s and meet the low-temperature loss and air flow uniformity requirements of a novel test bed with the flow of 3-10 kg/s.
Those skilled in the art will appreciate that those matters not described in detail in the present specification are well known in the art.
Claims (10)
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Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3899923A (en) * | 1971-05-13 | 1975-08-19 | Teller Environmental Systems | Test process and apparatus for treatment of jet engine exhaust |
| CN2077952U (en) * | 1989-12-23 | 1991-05-29 | 北京航空航天大学 | A new kiln heating device |
| CN2095344U (en) * | 1991-04-20 | 1992-02-05 | 包头钢铁稀土公司设计院 | Multi-flow wind mixer |
| CN101581450A (en) * | 2008-05-13 | 2009-11-18 | 通用电气公司 | Method and apparatus for cooling and dilution tuning gas turbine combustor linear and transition piece interface |
| CN102182586A (en) * | 2011-04-29 | 2011-09-14 | 奇瑞汽车股份有限公司 | ERG (exhaust gas recirculation) mixer |
| CN102817600A (en) * | 2012-08-30 | 2012-12-12 | 中国海洋石油总公司 | Jet flow pressure regulating device of water injection well |
| CN203490076U (en) * | 2013-09-12 | 2014-03-19 | 沈阳黎明航空发动机(集团)有限责任公司 | Aeroengine ground indoor stand air intake heating device |
| CN203837917U (en) * | 2014-04-08 | 2014-09-17 | 中国燃气涡轮研究院 | Cone wall hole type non-isothermal air inlet mixing device |
| CN109718679A (en) * | 2018-12-25 | 2019-05-07 | 中国航天空气动力技术研究院 | A kind of mixed stable voltage chamber device |
| CN110080918A (en) * | 2019-05-13 | 2019-08-02 | 中国人民解放军陆军装甲兵学院 | A kind of preheating device and pre-heating mean based on diesel engine radiators heat |
-
2019
- 2019-12-26 CN CN201911371130.5A patent/CN110940526B/en not_active Expired - Fee Related
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3899923A (en) * | 1971-05-13 | 1975-08-19 | Teller Environmental Systems | Test process and apparatus for treatment of jet engine exhaust |
| CN2077952U (en) * | 1989-12-23 | 1991-05-29 | 北京航空航天大学 | A new kiln heating device |
| CN2095344U (en) * | 1991-04-20 | 1992-02-05 | 包头钢铁稀土公司设计院 | Multi-flow wind mixer |
| CN101581450A (en) * | 2008-05-13 | 2009-11-18 | 通用电气公司 | Method and apparatus for cooling and dilution tuning gas turbine combustor linear and transition piece interface |
| CN102182586A (en) * | 2011-04-29 | 2011-09-14 | 奇瑞汽车股份有限公司 | ERG (exhaust gas recirculation) mixer |
| CN102817600A (en) * | 2012-08-30 | 2012-12-12 | 中国海洋石油总公司 | Jet flow pressure regulating device of water injection well |
| CN203490076U (en) * | 2013-09-12 | 2014-03-19 | 沈阳黎明航空发动机(集团)有限责任公司 | Aeroengine ground indoor stand air intake heating device |
| CN203837917U (en) * | 2014-04-08 | 2014-09-17 | 中国燃气涡轮研究院 | Cone wall hole type non-isothermal air inlet mixing device |
| CN109718679A (en) * | 2018-12-25 | 2019-05-07 | 中国航天空气动力技术研究院 | A kind of mixed stable voltage chamber device |
| CN110080918A (en) * | 2019-05-13 | 2019-08-02 | 中国人民解放军陆军装甲兵学院 | A kind of preheating device and pre-heating mean based on diesel engine radiators heat |
Non-Patent Citations (2)
| Title |
|---|
| "基于CFD的航空发动机试车台进气加温装置气动性能分析";曹海峰 等;《燃气涡轮试验与研究》;20190228;第32卷(第1期);47-51 * |
| "导流锥角度对室内发动机试车台影响的研究";张珺 等;《机械管理开发》;20191015;第34卷(第10期);64-67 * |
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| CN110940526A (en) | 2020-03-31 |
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