CN204312394U - With the turbosupercharger of diagonal impeller of compressor - Google Patents
With the turbosupercharger of diagonal impeller of compressor Download PDFInfo
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- CN204312394U CN204312394U CN201420676228.8U CN201420676228U CN204312394U CN 204312394 U CN204312394 U CN 204312394U CN 201420676228 U CN201420676228 U CN 201420676228U CN 204312394 U CN204312394 U CN 204312394U
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Abstract
With a turbosupercharger for diagonal impeller of compressor, comprise turbine box, bearing support, back of the body dish, gas compressor pressure shell, rotor shaft, turbine rotor, diagonal impeller of compressor, thrust plate, thrust bearing, stuffing box gland, oil baffle, thrust housing and thermal shield.Turbine box is connected with bearing support with pressing plate by screw, thermal shield is installed between turbine box and the Transverse plane of bearing support, turbine rotor is fixedly mounted on one end of rotor shaft, rotor shaft is arranged on the sliding bearing inner ring on bearing support, thrust housing, thrust plate, stuffing box gland, and diagonal impeller of compressor is arranged on the other end of rotor shaft successively, and be fixed on rotor shaft by nut, thrust bearing is arranged on thrust housing, oil baffle is arranged on the circular bosses of stuffing box gland, back of the body dish is connected with bearing support by screw, and by back of the body dish, oil baffle is pressed on the end face of thrust bearing, gas compressor pressure shell is connected with back of the body dish with pressing plate by screw.
Description
Technical field
The utility model relates to turbo-charger technical field, particularly a kind of turbosupercharger by adopting diagonal impeller to reduce compressor impeller thrust load.
Background technique
Turbosupercharger utilizes engine exhaust to drive turbo machine, rotating turbine drives coaxial gas compressor work, and gas compressor will enter the compresses fresh air of motor, thus add the air inflow of motor, improve the power of motor, reduce the oil consumption of motor.
Existing turbosupercharger as shown in Figure 1, comprises turbine box 1, bearing support 2, back of the body dish 3, gas compressor pressure shell 4, rotor shaft 5, turbine rotor 6, gas compressor radial-flow impeller 7, thrust plate 8, thrust bearing 9, stuffing box gland 10, oil baffle 11, thrust housing 12 and thermal shield 13.
Turbine box 1 is connected with bearing support 2 with pressing plate by screw, thermal shield 13 is installed between the Transverse plane of turbine box 1 and bearing support 2, turbine rotor 6 is fixedly mounted on one end of rotor shaft 5, rotor shaft 5 is arranged on the sliding bearing inner ring on bearing support 2, thrust housing 12, thrust plate 8, stuffing box gland 10, and compressor impeller 7 is arranged on the other end of rotor shaft 5 successively, and be fixed on rotor shaft 5 by nut, thrust bearing 9 is arranged on thrust housing 12, oil baffle 11 is arranged on the circular bosses of stuffing box gland 10, back of the body dish 3 is connected with bearing support 2 by screw, and by back of the body dish 3, oil baffle 11 is pressed on the end face of thrust bearing 9, gas compressor pressure shell 4 is connected with back of the body dish 3 with pressing plate by screw.
The radial-flow impeller 7 that existing turbosupercharger adopts is as accompanying drawing 3, shown in 4, comprise wheel hub 7-1, plural pieces linear leaf 7-2 and plural pieces short blade 7-3, linear leaf 7-2 is the same with the quantity of short blade 7-3, cross-shaped being evenly distributed on of linear leaf 7-2 and short blade 7-3 is drawn together on wheel hub 7-1, linear leaf 7-2 flow outlet top 7-2-1 is parallel with the axle centre of wheel hub 7-1 with short blade 7-3 flow outlet top 7-3-1, the excircle configuration diameter of linear leaf 7-2 flow outlet top 7-2-1 and the excircle configuration diameter of short blade 7-3 flow outlet top 7-3-1 are all D2, D2 is less than the wheel diameter D1 of wheel hub 1.
Along with turbosupercharger is to high rotating speed, high pressure ratio future development, whole turbocharger bearing system undergos acid test, compressor pressure ratio raises, result in the thrust load increase being pointed to pressure side by turbosupercharger whirlpool end, the thrust load of impeller mainly refers to that compressor inlet is to the pressure P 2 in the pressure P 1 of impeller leading faces and impeller wheel back of the body gap, air compressor wheel carries on the back gap internal pressure P2 when pressurized machine runs well all higher than inlet pressure P1, when the thrust load that impeller wheel back of the body gap internal pressure P2 produces is excessive, oil film between thrust bearing 9 and thrust plate 8 is not enough to bear thrust load and cause the dry friction between part to increase the weight of, under high rotating speed effect, thrust bearing 9 very quick-wearing lost efficacy, impeller blade friction compressor casing is then caused to damage pressurized machine time serious.
At turbosupercharger industry field, mainly start with from two aspects for overcoming thrust load increase, one is by designing new axial bearing surface structure, increase the bearing capacity of oil film, the thrust load numerical value that thrust bearing be can bear increases, this solution can not reduce the thrust load of the compressor impeller wheel back of the body, and when the thrust load of the impeller wheel back of the body is excessive, turbine rotor system and thrust bearing still can produce directly to contact and dry grind; Two is that reach the object indirectly reducing thrust load, but consequent problem is, after increasing turbine box runner, the low-speed performance of motor can be a greater impact, and lays particular emphasis on low-speed performance disagree with present engine by increasing turbine box runner A/R value.
Summary of the invention
The purpose of this utility model be overcome prior art above-mentioned deficiency and a kind of turbosupercharger with diagonal impeller of compressor is provided, reducing by reducing hub disk area the thrust load acting on the hub disk back side, preventing booster thrust bearing produced inefficacy and the pressurized machine fault that causes.
The technical solution of the utility model is: a kind of turbosupercharger with diagonal impeller of compressor, comprises turbine box, bearing support, back of the body dish, gas compressor pressure shell, rotor shaft, turbine rotor, compressor impeller, thrust plate, thrust bearing, stuffing box gland, oil baffle, thrust housing and thermal shield.
Turbine box is connected with bearing support with pressing plate by screw, thermal shield is installed between turbine box and the Transverse plane of bearing support, turbine rotor is fixedly mounted on one end of rotor shaft, rotor shaft is arranged on the sliding bearing inner ring on bearing support, thrust housing, thrust plate, stuffing box gland, and compressor impeller is arranged on the other end of rotor shaft successively, and be fixed on rotor shaft by nut, thrust bearing is arranged on thrust housing, oil baffle is arranged on the circular bosses of stuffing box gland, back of the body dish is connected with bearing support by screw, and by back of the body dish, oil baffle is pressed on the end face of thrust bearing, gas compressor pressure shell is connected with back of the body dish with pressing plate by screw.
Described compressor impeller adopts diagonal impeller, diagonal impeller comprises wheel hub, five ~ seven linear leafs and five ~ seven short blades, linear leaf and cross-shaped being evenly distributed on of short blade are drawn together on wheel hub, linear leaf flow outlet top and short blade flow outlet top are inclined-plane, it is 15 ~ 35 ° with the inclination angle a of axle centre, the blade tip excircle configuration diameter at linear leaf flow outlet top and short blade flow outlet top is all D2, the blade root excircle configuration diameter at linear leaf flow outlet top and short blade flow outlet top is all D3, the blade root at linear leaf flow outlet top and short blade flow outlet top is crossing with the wheel disc circle end face of wheel hub.
When turbosupercharger runs well, act on the thrust load F of impeller primarily of compressor inlet impeller leading faces pressure P 1, pressure P 2 in impeller wheel back of the body gap and the area of contact of gas and impeller determine, F=F2-F1, F1 is the thrust load that P1 acts on impeller front surface, F2 is the thrust load that P2 acts on the impeller wheel back of the body, and compressor impeller wheel carries on the back gap internal pressure P2 when pressurized machine runs well all higher than inlet pressure P1, when after the long-pending reduction in the impeller wheel back side, lifting surface area is also along with reduction, act on impeller wheel back surface load F2 fall and will be greater than the amplitude acting on impeller front surface thrust load F1 and decline, cause taking turns the back of the body by impeller thus and point to the load reduction of impeller leading faces direction, along with the rising of rotating speed, axial load forces F on diagonal impeller reduces more obvious, reduce the loading force that thrust bearing bears, effectively improve the operation conditions of turbosupercharger.
The utility model compared with prior art has following features:
On existing radial flow impeller pressurized machine, change blade wheel structure, reduce impeller wheel back of the body exradius, the surface load F2 of the impeller wheel back of the body is reduced by reducing stress surface, realize the thrust load reducing rotor-support-foundation system, avoid thrust bearing and reduce the life-span because bearing larger axis to load, improve the global reliability of pressurized machine.
Below in conjunction with the drawings and specific embodiments, detailed construction of the present utility model is further described.
Accompanying drawing explanation
Accompanying drawing 1 is existing turbocharger arrangement schematic diagram;
Accompanying drawing 2 is the I portion enlarged view in accompanying drawing 1;
Accompanying drawing 3 is existing radial-flow impeller structural representation;
Accompanying drawing 4 is the A-A sectional view in accompanying drawing 3;
Accompanying drawing 5 is the turbocharger arrangement schematic diagram of band diagonal impeller of compressor;
Accompanying drawing 6 is the structural representation of diagonal impeller;
Accompanying drawing 7 is the B-B sectional view in accompanying drawing 6.
Embodiment
With a turbosupercharger for diagonal impeller of compressor, comprise turbine box 1, bearing support 2, back of the body dish 3, gas compressor pressure shell 4, rotor shaft 5, turbine rotor 6, compressor impeller 14, thrust plate 8, thrust bearing 9, stuffing box gland 10, oil baffle 11, thrust housing 12 and thermal shield 13.
Turbine box 1 is connected with bearing support 2 with pressing plate by screw, thermal shield 13 is installed between the Transverse plane of turbine box 1 and bearing support 2, turbine rotor 6 is fixedly mounted on one end of rotor shaft 5, rotor shaft 5 is arranged on the sliding bearing inner ring on bearing support 2, thrust housing 12, thrust plate 8, stuffing box gland 10, and compressor impeller 14 is arranged on the other end of rotor shaft 5 successively, and be fixed on rotor shaft 5 by nut, thrust bearing 9 is arranged on thrust housing 12, oil baffle 11 is arranged on the circular bosses of stuffing box gland 10, back of the body dish 3 is connected with bearing support 2 by screw, and by back of the body dish 3, oil baffle 11 is pressed on the end face of thrust bearing 9, gas compressor pressure shell 4 is connected with back of the body dish 3 with pressing plate by screw.
Described compressor impeller adopts diagonal impeller, diagonal impeller 14 comprises wheel hub 14-1, seven linear leaf 14-2 and seven short blade 14-3, cross-shaped being evenly distributed on of linear leaf 14-2 and short blade 14-3 is drawn together on wheel hub 14-1, linear leaf 14-2 flow outlet top 14-2-1 and short blade 14-3 flow outlet top 14-3-1 is inclined-plane, it is 15 ~ 35 ° with the inclination angle a of axle centre, the blade tip excircle configuration diameter of linear leaf 14-2 flow outlet top 14-2-1 and short blade 14-3 flow outlet top 14-3-1 is all D2, the blade root excircle configuration diameter of linear leaf 14-2 flow outlet top 14-2-1 and short blade 14-3 flow outlet top 14-3-1 is all D3, the blade root of linear leaf 14-2 flow outlet top 14-2-1 and short blade 14-3 flow outlet top 14-3-1 is crossing with the wheel disc circle end face of wheel hub 14-1.
Claims (1)
1. the turbosupercharger with diagonal impeller of compressor, comprises turbine box, bearing support, back of the body dish, gas compressor pressure shell, rotor shaft, turbine rotor, compressor impeller, thrust plate, thrust bearing, stuffing box gland, oil baffle, thrust housing and thermal shield;
Turbine box is connected with bearing support with pressing plate by screw, thermal shield is installed between turbine box and the Transverse plane of bearing support, turbine rotor is fixedly mounted on one end of rotor shaft, rotor shaft is arranged on the sliding bearing inner ring on bearing support, thrust housing, thrust plate, stuffing box gland, and compressor impeller is arranged on the other end of rotor shaft successively, and be fixed on rotor shaft by nut, thrust bearing is arranged on thrust housing, oil baffle is arranged on the circular bosses of stuffing box gland, back of the body dish is connected with bearing support by screw, and by back of the body dish, oil baffle is pressed on the end face of thrust bearing, gas compressor pressure shell is connected with back of the body dish with pressing plate by screw,
It is characterized in that: described compressor impeller adopts diagonal impeller, diagonal impeller comprises wheel hub, five ~ seven linear leafs and five ~ seven short blades, linear leaf and cross-shaped being evenly distributed on of short blade are drawn together on wheel hub, linear leaf flow outlet top and short blade flow outlet top are inclined-plane, it is 15 ~ 35 ° with the inclination angle a of axle centre, the blade tip excircle configuration diameter at linear leaf flow outlet top and short blade flow outlet top is all D2, the blade root excircle configuration diameter at linear leaf flow outlet top and short blade flow outlet top is all D3, the blade root at linear leaf flow outlet top and short blade flow outlet top is crossing with the wheel disc circle end face of wheel hub.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420676228.8U CN204312394U (en) | 2014-11-13 | 2014-11-13 | With the turbosupercharger of diagonal impeller of compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420676228.8U CN204312394U (en) | 2014-11-13 | 2014-11-13 | With the turbosupercharger of diagonal impeller of compressor |
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| CN204312394U true CN204312394U (en) | 2015-05-06 |
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| CN201420676228.8U Active CN204312394U (en) | 2014-11-13 | 2014-11-13 | With the turbosupercharger of diagonal impeller of compressor |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3196476A1 (en) * | 2016-01-25 | 2017-07-26 | Panasonic Intellectual Property Management Co., Ltd. | Impeller, centrifugal compressor and refrigeration cycle apparatus |
| CN107683374A (en) * | 2015-06-16 | 2018-02-09 | 株式会社Ihi | Sealing structure and booster |
| CN108884837A (en) * | 2016-07-15 | 2018-11-23 | 株式会社Ihi | Sealing structure and booster |
| JPWO2017168642A1 (en) * | 2016-03-30 | 2019-02-14 | 三菱重工エンジン＆ターボチャージャ株式会社 | Impeller, rotating machine, turbocharger |
| WO2022205806A1 (en) * | 2021-04-02 | 2022-10-06 | 湖南天雁机械有限责任公司 | Shafting structure of ball bearing of self-lubricating turbocharge |
-
2014
- 2014-11-13 CN CN201420676228.8U patent/CN204312394U/en active Active
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107683374A (en) * | 2015-06-16 | 2018-02-09 | 株式会社Ihi | Sealing structure and booster |
| US10662965B2 (en) | 2015-06-16 | 2020-05-26 | Ihi Corporation | Sealing structure and turbocharger |
| EP3196476A1 (en) * | 2016-01-25 | 2017-07-26 | Panasonic Intellectual Property Management Co., Ltd. | Impeller, centrifugal compressor and refrigeration cycle apparatus |
| JPWO2017168642A1 (en) * | 2016-03-30 | 2019-02-14 | 三菱重工エンジン＆ターボチャージャ株式会社 | Impeller, rotating machine, turbocharger |
| EP3434908A4 (en) * | 2016-03-30 | 2019-04-03 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Impeller, rotary machine, and turbocharger |
| US10883513B2 (en) | 2016-03-30 | 2021-01-05 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Impeller, rotary machine, and turbocharger |
| CN108884837A (en) * | 2016-07-15 | 2018-11-23 | 株式会社Ihi | Sealing structure and booster |
| CN108884837B (en) * | 2016-07-15 | 2021-07-06 | 株式会社Ihi | Sealing structure and supercharger |
| WO2022205806A1 (en) * | 2021-04-02 | 2022-10-06 | 湖南天雁机械有限责任公司 | Shafting structure of ball bearing of self-lubricating turbocharge |
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