CN104074551A - Turbine wheel split type structure - Google Patents
Turbine wheel split type structure Download PDFInfo
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- CN104074551A CN104074551A CN201410300359.0A CN201410300359A CN104074551A CN 104074551 A CN104074551 A CN 104074551A CN 201410300359 A CN201410300359 A CN 201410300359A CN 104074551 A CN104074551 A CN 104074551A
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- China
- Prior art keywords
- wheel
- blind hole
- wheel disc
- wheel hub
- tapered blind
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Abstract
The invention relates to a turbine wheel split type structure and a processing method. The turbine wheel split type structure is characterized in that a turbine wheel consists of a wheel disc 1 and a hub 2, wherein a conical blind hole is formed in the center of the wheel disc, the hub 2 is provided with a conical structure matched with the conical blind hole of the wheel disc, the wheel disc is formed by processing based on alloy casting and forming and the hub 2 is formed by processing an alloy bar. The height L2 of the conical structure of the hub 2 is greater than the depth L1 of the blind hole, and the wheel disc 1 and the hub 2 are connected by adopting a friction welding way. Therefore, the intensity performance of the core part of the turbine wheel of a supercharger can be improved significantly, the problems that the intensity of the core part is not enough when titanium-aluminum alloy and other materials are applied to the turbine wheel of the supercharger can be solved, the reliability of the turbine wheel of the supercharger can be improved and the operating requirements of the turbine wheel of the supercharger can be met.
Description
Technical field
The invention belongs to turbocharging technology field, be specifically related to a kind of turbine wheel split-type structural and processing method.
Background technique
Turbosupercharger is motor hoisting power density, improve one of adaptive key components and parts of altitude environment, turbine wheel, as the kernel component of turbosupercharger, is being born the function that the exhaust energy of cylinder discharge is converted into the required mechanical work of pressure booster blower impeller work.At present, what booster turbine impeller mainly adopted is cast nickel-base alloy K418 material, but because the density ratio of K418 alloy material is larger, also larger by the rotary inertia of the booster turbine impeller of its casting, cause the transient response of exhaust gas turbocharge motor poor; In addition, the weight of K418 alloy turbine impeller is also larger, is unfavorable for the light-weight design of motor.
For improving turbosupercharged engine transient response, alleviate the weight of turbosupercharger, booster turbine impeller can adopt the Ti-Al alloy material that specific strength is higher to replace K418 alloy material.Because the density of Ti-Al alloy material is 3.87 × 10
3kg/m
3be about 43% of K418 alloy density, and titanium-aluminium alloy has good high-temperature behavior and oxidation resistance, the booster turbine impeller that adopts titanium-aluminium alloy to manufacture, not only can effectively reduce the rotary inertia of turbocharger rotor, improve the transient response of motor, and can reduce the weight of turbine wheel, contribute to realize the lightweight of turbosupercharger and motor.But, because titanium-aluminium alloy belongs to intermetallic compounds, be subject to the impact of material own characteristic and the restriction of booster turbine impeller cast shaping process, by the problem of the booster turbine impeller ubiquity heart portion poor mechanical property of titanium-aluminium alloy casting, the heart portion tensile strength of turbine wheel is only 58% of master alloy tensile strength, cause the hypervelocity nargin deficiency of cast ti al alloy turbine wheel, be difficult to meet the reliability requirement of turbine wheel.
Summary of the invention
The present invention is that solution cast ti al alloy turbine wheel heart portion intensity is lower, the technical problem of turbine wheel poor reliability, proposes a kind of turbine wheel split-type structural and processing method.
Turbine wheel is made up of wheel disc and wheel hub, has tapered blind hole on wheel disc, has the cone structure of welding with wheel disc tapered blind hole on wheel hub, and turbine wheel forms by the friction welding of wheel disc and wheel hub.By analyzing the stress space distribution characteristics of turbine wheel, the dimensional parameters of appropriate design wheel disc tapered blind hole and wheel hub cone structure, wheel disc processes on the basis of Alloys Casting moulding, and wheel hub adopts alloy bar material machining to form.According to the dimensional parameters of the material property parameter of turbine wheel and wheel disc tapered blind hole and wheel hub cone structure, determine the friction-welding technique parameter of wheel disc and wheel hub, adopt the mode of friction welding wheel disc to be formed together with hub welding to complete turbine wheel.
Technological scheme of the present invention:
A kind of turbine wheel split-type structural, is characterized in that: turbine wheel is made up of wheel disc 1 and wheel hub 2, there is tapered blind hole in described wheel disc 1 heart portion, and described wheel hub 2 has the cone structure coordinating with wheel disc 1 tapered blind hole, the height L of described wheel hub 2 cone structures
2be greater than wheel disc 1 tapered blind hole degree of depth L
1, described wheel disc 1 and wheel hub 2 adopt friction welding mode to be connected to form complete turbine wheel.
The split type processing method of a kind of booster turbine impeller, comprises the following steps:
A, determine the stress space distribution characteristics of turbine wheel: adopt finite element simulation computational methods to determine the stress space distribution characteristics of turbine wheel;
B, determine the dimensional parameters of wheel disc tapered blind hole and wheel hub cone structure: according to the structural parameter of turbine wheel and stress space distribution characteristics, determine the dimensional parameters of wheel disc tapered blind hole and wheel hub cone structure, the maximum stress at turbine wheel hub position is arranged in wheel hub cone structure, the tapered blind hole taper angle θ of wheel disc
1for 80-160 °, degree of depth L
1for the 20%-60% of impeller thickness, base diameter Φ D
1for 5-25mm, tapered blind hole bottom B and conical surface A have knuckle R
1; The taper angle θ of wheel hub conical surface C
2with wheel disc tapered blind hole taper theta
1identical, height L
2than tapered blind hole degree of depth L
1large 2-12mm, conical surface end diameter Φ D
2with wheel disc tapered blind hole base diameter Φ D
1identical, between conical surface C and bottom surface D, there is knuckle R
2, R
2size and R
1identical, between the large end of the conical surface and rotating shaft, there is knuckle R
3;
The processing of c, wheel disc: carry out casting and the machining of wheel disc according to wheel disc dimensional parameters definite in step b, wheel disc forms through machining on the basis of Alloys Casting moulding;
The processing of d, wheel hub: adopt alloy bar material, according to hub size parameter definite in step b, alloy bar material is processed into wheel hub;
E, determine the friction-welding technique parameter of wheel disc and wheel hub: according to the dimensional parameters of the material property of turbine wheel and wheel disc tapered blind hole and wheel hub cone structure, determine the friction-welding technique parameter of wheel disc and wheel hub, comprise relative angular velocity of rotation, axial force and the amount of feed between wheel disc and wheel hub;
The friction welding of f, wheel disc and wheel hub: adopt friction welding mode, by fixture, wheel disc and wheel hub are separately fixed to two ends on friction-welding machine, according to the definite process parameter of step e, wheel hub and wheel disc are welded together, form complete turbine wheel.
The invention has the beneficial effects as follows: by analyzing the stress space distribution characteristics of booster turbine impeller, the dimensional parameters of appropriate design wheel disc tapered blind hole and wheel hub cone structure, wheel disc forms through machining on the basis of Alloys Casting moulding, wheel hub forms by alloy bar material machining, determine the friction-welding technique parameter of wheel disc and wheel hub, the turbine wheel that adopts friction welding mode that wheel disc has been formed together with hub welding, carries out machining according to the overall structure dimensional parameters of turbine wheel on this basis.The method and structure can promote the heart portion strength character of booster turbine impeller significantly, the problems such as the heart portion strength deficiency that the materials such as solution titanium-aluminium alloy exist in the time of direct casting booster turbine impeller, the reliability that improves booster turbine impeller, meets the usage requirement of pressurized machine to turbine wheel.
Brief description of the drawings
Fig. 1 is wheeling disk structure schematic diagram.
Fig. 2 is wheel hub structure schematic diagram.
1 wheel hub 2 wheel discs
Fig. 3 is turbine wheel structural representation.
Embodiment
A kind of turbine wheel split-type structural, turbine wheel is made up of wheel disc 1 and wheel hub 2, and there is tapered blind hole in described wheel disc 1 heart portion, taper angle θ
1for 80-160 °, tapered blind hole degree of depth L
1for the 20%-60% of impeller thickness, tapered blind hole base diameter Φ D
1for 5-25mm, there is knuckle R tapered blind hole bottom with the conical surface
1; Described wheel hub 2 has the cone structure coordinating with wheel disc 1 tapered blind hole, the taper angle θ of wheel hub 2 conical surface C
2with wheel disc 1 tapered blind hole taper angle θ
1identical, the height L of wheel hub 2 conical surface C
2than wheel disc 1 tapered blind hole degree of depth L
1large 2-12mm, wheel hub 2 conical surface end diameter Φ D
2with wheel disc 1 tapered blind hole base diameter Φ D
1identical, between the conical surface C of wheel hub 2 and bottom surface D, there is knuckle R
2, R
2size and R
1identical, between the large end of the conical surface of wheel hub 2 and rotating shaft, there is knuckle R
3.In described wheel disc 1, do not comprise the location of maximum stress at turbine wheel hub position, in wheel hub 2, comprise the location of maximum stress at turbine wheel hub position.Described wheel disc 1 is to process on the basis of Alloys Casting moulding; Described wheel hub 2 is processed by alloy bar material; Described wheel disc 1 and wheel hub 2 adopt friction welding mode to form complete turbine wheel.
The height L of wheel hub 2 conical surfaces
2than wheel disc 1 tapered blind hole degree of depth L
1large 2-12mm, is conducive to friction welding firm welding, improves welding quality.
The taper angle θ of wheel disc 1 tapered blind hole
1for 80-160 °, tapered blind hole degree of depth L
1for the 20%-60% of impeller thickness, tapered blind hole base diameter Φ D
1for 5-25mm, there is knuckle R tapered blind hole bottom with the conical surface
1; The taper angle θ of wheel hub 2 conical surface C
2with wheel disc 1 tapered blind hole taper angle θ
1identical, wheel hub 2 conical surface C end diameter Φ D
2with wheel disc 1 tapered blind hole base diameter Φ D
1identical, between the conical surface C of wheel hub 2 and bottom surface D, there is knuckle R
2, R
2size and R
1identical, between the large end of the conical surface of wheel hub 2 and rotating shaft, there is knuckle R
3.Be conducive to improve the reliability of turbine wheel.
Wheel disc 1 processes on the basis of Alloys Casting moulding; Described wheel hub 2 is processed by alloy bar material, is conducive to improve turbine wheel heart portion's intensity and reliability, improves turbine wheel yield rate.
In wheel disc 1, do not comprise the location of maximum stress at turbine wheel hub position, in wheel hub 2, comprise the location of maximum stress at turbine wheel hub position, can further promote the reliability of turbine wheel.
The split type processing method of a kind of turbine wheel, comprises the following steps:
A, determine the stress space distribution characteristics of turbine wheel: adopt finite element simulation computational methods to determine the stress space distribution characteristics of turbine wheel;
B, determine the dimensional parameters of wheel disc tapered blind hole and wheel hub cone structure: according to the structural parameter of turbine wheel and stress space distribution characteristics, determine the dimensional parameters of wheel disc tapered blind hole and wheel hub cone structure, the maximum stress at turbine wheel hub position is arranged in wheel hub cone structure, the tapered blind hole taper angle θ of wheel disc
1for 80-160 °, degree of depth L
1for the 20%-60% of impeller thickness, base diameter Φ D
1for 5-25mm, tapered blind hole bottom B and conical surface A have knuckle R
1; The taper angle θ of wheel hub conical surface C
2with wheel disc tapered blind hole taper theta
1identical, height L
2than tapered blind hole degree of depth L
1large 2-12mm, conical surface end diameter Φ D
2with wheel disc tapered blind hole base diameter Φ D
1identical, between conical surface C and bottom surface D, there is knuckle R
2, R
2size and R
1identical, between the large end of the conical surface and rotating shaft, there is knuckle R
3, as depicted in figs. 1 and 2, for example, be the cast ti al alloy booster turbine impeller that Φ 95mm, thickness are 39.5mm for diameter, the tapered blind hole taper angle θ of wheel disc
1be 85 °, degree of depth L
1for 20mm, base diameter Φ D
1for 10mm, tapered blind hole bottom and conical surface transition fillet R
1for 2mm; The taper angle θ of wheel hub conical surface C
2be 85 °, height L
2for 22mm, conical surface end diameter Φ D
2for 10mm, the knuckle R between conical surface C and bottom surface D
2for 2mm, the knuckle R between the large end of the conical surface and rotating shaft
3for 3mm;
The processing of c, wheel disc: carry out casting and the machining of wheel disc according to wheel disc dimensional parameters definite in step b, wheel disc forms through machining on the basis of Alloys Casting moulding;
The processing of d, wheel hub: adopt alloy bar material, according to hub size parameter definite in step b, alloy bar material is processed into wheel hub;
E, determine the friction-welding technique parameter of wheel disc and wheel hub: according to the dimensional parameters of the material property of turbine wheel and wheel disc tapered blind hole and wheel hub cone structure, determine the friction-welding technique parameter of wheel disc and wheel hub, comprise relative angular velocity of rotation, axial force and the amount of feed between wheel disc and wheel hub;
The friction welding of f, wheel disc and wheel hub: adopt friction welding mode, on friction-welding machine, by fixture, wheel disc and wheel hub are separately fixed to two ends, according to the definite process parameter of step e, wheel hub and wheel disc are welded together, form complete turbine wheel, as shown in Figure 3.
Be the cast ti al alloy booster turbine impeller that Φ 95mm, thickness are 39.5mm for diameter, preferred wheel disc and hub size parameter are: wheel disc tapered blind hole taper angle θ
1be 85 °, degree of depth L
1for 20mm, base diameter Φ D
1for 10mm, tapered blind hole bottom and conical surface transition fillet R
1for 2mm; The taper angle θ of wheel hub conical surface C
2be 85 °, height L
2for 22mm, conical surface end diameter Φ D
2for 10mm, the knuckle R of conical surface C and bottom surface D
2for 2mm, the knuckle R of the large end of the conical surface and rotating shaft
3for 3mm.
Claims (6)
1. a turbine wheel split-type structural, it is characterized in that: turbine wheel is made up of wheel disc (1) and wheel hub (2), there is tapered blind hole in described wheel disc (1) heart portion, described wheel hub (2) has the cone structure coordinating with wheel disc (1) tapered blind hole, the height L of described wheel hub (2) cone structure
2be greater than wheel disc (1) tapered blind hole degree of depth L
1, described wheel disc (1) adopts friction welding mode to be connected with wheel hub (2).
2. turbine wheel split-type structural according to claim 1, is characterized in that: the height L of described wheel hub (2) cone structure
2than wheel disc (1) tapered blind hole degree of depth L
1large 2-12mm.
3. turbine wheel split-type structural according to claim 1, is characterized in that: the taper angle θ of described wheel disc (1) tapered blind hole
1for 80-160 °, tapered blind hole degree of depth L
1for the 20%-60% of impeller thickness, tapered blind hole base diameter Φ D
1for 5-25mm, there is knuckle R tapered blind hole bottom with the conical surface
1; The taper angle θ of wheel hub (2) conical surface C
2with wheel disc (1) tapered blind hole taper angle θ
1identical, wheel hub (2) conical surface C end diameter Φ D
2with wheel disc (1) tapered blind hole base diameter Φ D
1identical, between the conical surface C of wheel hub (2) and bottom surface D, there is knuckle R
2, R
2size and R
1identical, between the large end of the conical surface of wheel hub (2) and rotating shaft, there is knuckle R
3.
4. turbine wheel split-type structural according to claim 1, is characterized in that: described wheel disc (1) processes on the basis of Alloys Casting moulding; Described wheel hub (2) is processed by alloy bar material.
5. turbine wheel split-type structural according to claim 1, it is characterized in that: in described wheel disc (1), do not comprise the location of maximum stress at turbine wheel hub position, the location of maximum stress that comprises turbine wheel hub position in wheel hub (2).
6. the split type processing method of turbine wheel, is characterized in that: comprise the following steps:
A, determine the stress space distribution characteristics of turbine wheel: adopt finite element simulation computational methods to determine the stress space distribution characteristics of turbine wheel;
B, determine the dimensional parameters of wheel disc tapered blind hole and wheel hub cone structure: according to the structural parameter of turbine wheel and stress space distribution characteristics, determine the dimensional parameters of wheel disc tapered blind hole and wheel hub cone structure, the maximum stress at turbine wheel hub position is arranged in wheel hub cone structure, the tapered blind hole taper angle θ of wheel disc
1for 80-160 °, degree of depth L
1for the 20%-60% of impeller thickness, base diameter Φ D
1for 5-25mm, tapered blind hole bottom B and conical surface A have knuckle R
1; The taper angle θ of wheel hub conical surface C
2with wheel disc tapered blind hole taper theta
1identical, height L
2than tapered blind hole degree of depth L
1large 2-12mm, conical surface end diameter Φ D
2with wheel disc tapered blind hole base diameter Φ D
1identical, between conical surface C and bottom surface D, there is knuckle R
2, R
2size and R
1identical, between the large end of the conical surface and rotating shaft, there is knuckle R
3;
The processing of c, wheel disc: carry out casting and the machining of wheel disc according to wheel disc dimensional parameters definite in step b, wheel disc forms through machining on the basis of Alloys Casting moulding;
The processing of d, wheel hub: adopt alloy bar material, according to hub size parameter definite in step b, alloy bar material is processed into wheel hub;
E, determine the friction-welding technique parameter of wheel disc and wheel hub: according to the dimensional parameters of the material property of turbine wheel and wheel disc tapered blind hole and wheel hub cone structure, determine the friction-welding technique parameter of wheel disc and wheel hub, comprise relative angular velocity of rotation, axial force and the amount of feed between wheel disc and wheel hub;
The friction welding of f, wheel disc and wheel hub: adopt friction welding mode, by fixture, wheel disc and wheel hub are separately fixed to two ends on friction-welding machine, according to the definite process parameter of step e, wheel hub and wheel disc are welded together, form complete turbine wheel.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410300359.0A CN104074551B (en) | 2014-06-19 | 2014-06-19 | A kind of turbine wheel split-type structural |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410300359.0A CN104074551B (en) | 2014-06-19 | 2014-06-19 | A kind of turbine wheel split-type structural |
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| Publication Number | Publication Date |
|---|---|
| CN104074551A true CN104074551A (en) | 2014-10-01 |
| CN104074551B CN104074551B (en) | 2015-09-23 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410300359.0A Active CN104074551B (en) | 2014-06-19 | 2014-06-19 | A kind of turbine wheel split-type structural |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108194148A (en) * | 2017-11-22 | 2018-06-22 | 中国北方发动机研究所(天津) | A kind of high reliability radial-flow type booster turbine impeller preparation method |
| CN112360565A (en) * | 2020-10-26 | 2021-02-12 | 北京动力机械研究所 | Twin dissimilar material composite runoff impeller and manufacturing process thereof |
| US11927211B2 (en) | 2017-04-19 | 2024-03-12 | Hilti Aktiengesellschaft | Fastening method and fastening system |
Citations (7)
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| EP0124325A1 (en) * | 1983-04-21 | 1984-11-07 | The Garrett Corporation | Composite compressor wheel for radial compressors |
| JPS62119176A (en) * | 1985-11-19 | 1987-05-30 | トヨタ自動車株式会社 | Manufacture of ceramic turbowheel |
| EP0808989A1 (en) * | 1996-05-23 | 1997-11-26 | Alcatel | Impeller for a radial turbine |
| CN2360609Y (en) * | 1998-12-02 | 2000-01-26 | 亚瑞亚·勃朗勃威力有限公司 | Compressor impeller fixing device for high speed turbine |
| EP1296021A2 (en) * | 2001-09-20 | 2003-03-26 | Nuovo Pignone Holding S.P.A. | Flange connection between compressor shaft and turbine rotor disc |
| CN103862234A (en) * | 2014-02-13 | 2014-06-18 | 中国北方发动机研究所(天津) | Method and structure for improving strength performance of central part of supercharger turbine |
-
2014
- 2014-06-19 CN CN201410300359.0A patent/CN104074551B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2438866A (en) * | 1945-06-01 | 1948-03-30 | United Aircraft Corp | Impeller mounting |
| EP0124325A1 (en) * | 1983-04-21 | 1984-11-07 | The Garrett Corporation | Composite compressor wheel for radial compressors |
| JPS62119176A (en) * | 1985-11-19 | 1987-05-30 | トヨタ自動車株式会社 | Manufacture of ceramic turbowheel |
| EP0808989A1 (en) * | 1996-05-23 | 1997-11-26 | Alcatel | Impeller for a radial turbine |
| CN2360609Y (en) * | 1998-12-02 | 2000-01-26 | 亚瑞亚·勃朗勃威力有限公司 | Compressor impeller fixing device for high speed turbine |
| EP1296021A2 (en) * | 2001-09-20 | 2003-03-26 | Nuovo Pignone Holding S.P.A. | Flange connection between compressor shaft and turbine rotor disc |
| CN103862234A (en) * | 2014-02-13 | 2014-06-18 | 中国北方发动机研究所(天津) | Method and structure for improving strength performance of central part of supercharger turbine |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11927211B2 (en) | 2017-04-19 | 2024-03-12 | Hilti Aktiengesellschaft | Fastening method and fastening system |
| CN108194148A (en) * | 2017-11-22 | 2018-06-22 | 中国北方发动机研究所(天津) | A kind of high reliability radial-flow type booster turbine impeller preparation method |
| CN108194148B (en) * | 2017-11-22 | 2020-04-10 | 中国北方发动机研究所(天津) | Preparation method of high-reliability radial-flow supercharger turbine wheel |
| CN112360565A (en) * | 2020-10-26 | 2021-02-12 | 北京动力机械研究所 | Twin dissimilar material composite runoff impeller and manufacturing process thereof |
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| CN104074551B (en) | 2015-09-23 |
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