CN101363330B - Turbine boosting expansion machine - Google Patents
Turbine boosting expansion machine Download PDFInfo
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- CN101363330B CN101363330B CN2008101570986A CN200810157098A CN101363330B CN 101363330 B CN101363330 B CN 101363330B CN 2008101570986 A CN2008101570986 A CN 2008101570986A CN 200810157098 A CN200810157098 A CN 200810157098A CN 101363330 B CN101363330 B CN 101363330B
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Abstract
The present invention provides a gas bearing boosting turboexpander which comprises a middle casing. The left end of the middle casing is equipped with a turbine volute, and the right end thereof is equipped with a booster volute. A rotor is arranged in the middle casing in a rotatable way. Two ends of the rotor are respectively provided with an expansion wheel and a boosting wheel. The rotor is sleeved with two gas bearings which are used for supporting the expansion wheel and the boosting wheel. The gas bearing boosting turboexpander has the advantages of simple structure, less axial waste, low cost, good safety performance, and great capability of reducing the discharge of oil steam in an oil bearing expander, thus reducing the pollution to the environment. Based on the advantages of the expander, a milestone base for the development of the boosting turboexpander is settled.
Description
Technical field
The present invention relates to a kind of booster expansion turbine, especially a kind of booster expansion turbine of using gases bearing.
Background technique
Booster expansion turbine is that air separation equipment and rock gas petroleum gas liquefaction separation equipment and low temperature breaking equipment etc. obtain the necessary crucial portion of cold machine, is the heart that guarantees complete equipment stable operation.Its cardinal principle is to utilize the gas that certain pressure is arranged to carry out adiabatic expansion externally acting and the interior energy of spent gas itself in turbo-expander, thereby gas self is cooled off consumingly and reaches the purpose of refrigeration.The energy of turbo-expander output is reclaimed or braking blower consumption by coaxial compressor.
Booster expansion turbine comprises a middle casing, the left end of middle casing is installed the turbine spiral case, right-hand member is equipped with volute of booster, be provided with rotor in the middle casing, in turbine spiral case and volute of booster, be provided with expansion wheel and impeller of booster respectively at the two ends of rotor.Present booster expansion turbine is used to support the general employing oil bearing of expansion wheel and impeller of booster, and this structure can be brought a lot of inconvenience.Because the working medium of oil bearing is a lubricant oil, and lubricant oil might leak from the outlet port of inflating end in the working procedure of decompressor, this moment, lubricant oil just contacted with air, and the danger of burning just might be arranged; In addition, owing to need provide lubricant oil to oil bearing, so generally also need to increase a cover oil supply system in the work system of decompressor, this will increase the cost of a whole set of expander system and the complexity of structure.
The expansion wheel and the impeller of booster of booster expansion turbine use at present generally are to be formed by aluminum casting, and expansion wheel that obtains like this and impeller of booster are all comparatively coarse, influence the performance of whole decompressor.In addition, because the present expansion wheel and the shape cause of impeller of booster blade, cause its working efficiency neither be very high.
Summary of the invention
The objective of the invention is to solve above-mentioned technical problem, provide that a kind of Safety performance is good, cost is low, simple in structure, energy consumption is less and booster expansion turbine that efficient is higher.
Purpose of the present invention is achieved through the following technical solutions:
A kind of booster expansion turbine, comprise a middle casing, the left end of described middle casing is installed the turbine spiral case, right-hand member is equipped with volute of booster, be provided with rotor in the described middle casing rotationally, two ends at described rotor are provided with expansion wheel and impeller of booster respectively in turbine spiral case and volute of booster, on described rotor, be arranged with left gas bearing and right gas bearing, described left gas bearing is used for supporting expansion wheel, be provided with stuffing box gland between described left gas bearing and the expansion wheel, described right gas bearing is used for supporting impeller of booster, be provided with spacing sealing plate between described right gas bearing and the impeller of booster, be connected with 4 adapter assemblies on the described middle casing, be respectively a left side, right gas bearing provides bearing gas, and provides blanket gas for stuffing box gland and spacing sealing plate.
Further, be provided with the bearing stop collar between described left gas bearing and the right gas bearing, described bearing stop collar is set in outside the rotor and with middle casing and cooperates.
Described expansion wheel comprises wheel disc and the wheel cap that interfixes, and is evenly equipped with blade on the described wheel disc, and described blade is the parabolic setting of cylinder.Connect fixing for soldering between the wheel disc of described expansion wheel and the wheel cap.The surface of the wheel cap of described expansion wheel is provided with 5 ring teeth.
Described impeller of booster comprises wheel disc and the wheel cap that interfixes, and described wheel disc is provided with blade, the line setting in the shape of a spiral of described blade, and the cross section of two relative faces of blade is a concentric circle.Connect fixing for soldering between the wheel disc of described impeller of booster and the wheel cap.The surface of the wheel cap of described impeller of booster is provided with 5 ring teeth.
Again further, the ratio of the width of blade of the blade of the wheel disc of described impeller of booster and blade height is between 20～25.The airflow inlet angle of described impeller of booster is between 30～35 degree, and the flow outlet angle is between 35～40 degree.
Further, be provided with fluid director between described turbine spiral case and the expansion wheel, after gas is entered by the turbine volute inlet, the expansion wheel of after the fluid director mean allocation, flowing through again.
Again further, described middle casing is provided with adapter assembly, and also is provided with adapter assembly on the end cover body that volute of booster links to each other, is connected with equilibrium valve between described two adapter assemblies.
Beneficial effect of the present invention is mainly reflected in: simple in structure, the axle loss is little, and the energy utilization is thorough, and price has only about the 1/6-1/8 of same parameter oil bearing decompressor; Safety performance is good, does not have the danger of burning; And can reduce the discharging of oily vapour in the oil bearing decompressor, reduced pollution to environment.In addition, use numerical control milling machine processing simple expansion wheel and impeller of booster, and on both wheel discs, all be welded with wheel cap, the working efficiency of whole booster expansion turbine is further enhanced.
Description of drawings
Below in conjunction with accompanying drawing technical solution of the present invention is described further:
Fig. 1: the plan view of booster expansion turbine of the present invention.
Fig. 2: among Fig. 1 along the sectional view of H-H direction.
Fig. 3: the cut-away view of the expansion wheel of booster expansion turbine of the present invention.
Fig. 4: the plan view of the expansion wheel of booster expansion turbine of the present invention.
Fig. 5: the enlarged view of A part among Fig. 3.
Fig. 6: the cut-away view of the impeller of booster of booster expansion turbine of the present invention.
Fig. 7: the plan view of the impeller of booster of booster expansion turbine of the present invention.
Fig. 8: the enlarged view of B part among Fig. 6.
Fig. 9: the enlarged view of C part among Fig. 6.
Figure 10: the plan view of the fluid director of booster expansion turbine of the present invention.
Wherein:
1 turbine spiral case, 2 middle casings, 3 volute of booster
4 expansion wheel, 5 stuffing box glands, 6 left gas bearing
7 bearing stop collars, 8 rotors, 9 right gas bearing
10 collets, 11 spacing sealing plate 12 impeller of boosters
Diffuser 15 fluid directors in 13 Diffusers 14
16 thermal shields, 17 connecting sleeves, 19 end cover bodies
20 equilibrium valves, 41 wheel discs, 42 wheel caps
43 blades, 44 ring teeth, 121 wheel discs
122 wheel caps, 123 blades, 124 ring teeth
D width of blade H blade height α airflow inlet angle
The outlet of β flow outlet angle a expansion gas inlet b expansion gas
The outlet of c supercharging gas inlet d supercharging gas
18a, 18b, 18c, 18d, 18e, 18f, 18g adapter assembly
Embodiment
As depicted in figs. 1 and 2, the present invention has disclosed a kind of gas bearing booster expansion turbine, the same with prior art, comprise a middle casing 2, the left end of described middle casing 2 is installed turbine spiral case 1, right-hand member is equipped with volute of booster 3, be provided with rotor 8 rotationally in the described middle casing 2, in turbine spiral case 1 and volute of booster 3, be provided with expansion wheel 4 and impeller of booster 12 respectively at the two ends of described rotor 8.Be that with the prior art difference be arranged with left gas bearing 6 and right gas bearing 9 on described rotor 8, described left gas bearing 6 is used for supporting expansion wheel 4, described right gas bearing 9 is used for supporting impeller of booster 12.
Because the oiling agent of gas bearing is an air, so do not worry the problem that whether can burn.In addition, gas bearing also has following characteristics.1. frictional resistance is extremely low: because gas viscosity is more much lower than liquid, at room temperature air viscosity only is five a thousandths of No. 10 machinery oil, and the frictional resistance of bearing is directly proportional with viscosity, so the frictional ratio fluid lubricated bearing of gas bearing is low.2. it is big to be suitable for velocity range: the frictional resistance of gas bearing is low, and temperature rise is low.3. the Applicable temperature scope is wide: gas can keep gaseous state in the temperature range greatly, and its viscosity temperature influence is very little.Therefore behind the using gases bearing, it is more thorough that energy can utilize.
When booster expansion turbine moves, the high pressure-temperature gas that is easy to take place the impeller of booster back of the body flows to the bearing place along main shaft, thereby make the bearing expanded by heating, the end clearance of itself and main shaft is diminished, seize or stuck phenomenon take place, the present invention is provided with bearing stop collar 7 between left gas bearing 6 and right gas bearing 9, it is outer and fixing with middle casing 2 that described bearing stop collar 7 is set in rotor 8.Such design has improved the bearing capacity of bearing, and it can force the expansion that suppresses bearing face, to guarantee the fit up gap.
The left end of turbine spiral case 1 of the present invention is connected with Diffuser 13, and linking with Diffuser 13 is connected with an interior Diffuser 14, and described interior Diffuser 14 is arranged on the inside of turbine spiral case 1.The right-hand member of turbine spiral case 1 is connected with thermal shield 16 and connecting sleeve 17, is socketed on the middle casing 2.Be provided with fluid director 15 between described turbine spiral case 1 and the expansion wheel 4, as shown in figure 10, the surface of fluid director 15 is evenly equipped with a projection that encloses the gas channeling effect.After gas is entered by turbine spiral case 1 inlet, the expansion wheel 4 of after fluid director 15 mean allocation, flowing through again.
Be provided with stuffing box gland 5 between described left gas bearing 6 and the expansion wheel 4, be provided with collet 10 and spacing sealing plate 11 between described right gas bearing 9 and the impeller of booster 12.Like this, make the outer leakage quantity of gas be controlled in the minimum scope, in stuffing box gland 5 and spacing sealing plate 11, also can charge into normal temperature blanket gas (dry air or nitrogen) and leak with the flow through cryogenic gas of decompressor of prevention.
As shown in Figure 2, on middle casing 2, be provided with 4 adapter assemblies, provide bearing gas and blanket gas thereby connect source of the gas respectively.Wherein, adapter assembly 18a provides bearing gas for left gas bearing 6, and adapter assembly 18b provides bearing gas for right gas bearing 9, and adapter assembly 18c provides blanket gas for spacing sealing plate 11, and adapter assembly 18d provides blanket gas for stuffing box gland 5.So just not needing needs to provide an oil supply system to decompressor as prior art, thus of the present invention simple in structure, with low cost, and improved the stability of decompressor operation.
In addition, also be provided with the adapter assembly 18e of a connection tachometer on the middle casing 2, the point of contact of adapter assembly 18e inside abuts on the rotor 8, is used for measuring in expansion wheel work the rotating speed of rotor.
In conjunction with illustrated in figures 1 and 2, middle casing 2 is provided with adapter assembly 18f, and also is provided with adapter assembly 18g on the end cover body 19 that volute of booster 3 links to each other, is connected with equilibrium valve 20 between described two adapter assemblies.She Ji reason is for the pressure that makes the impeller of booster back of the body refluxes like this, only need turn equilibrium valve 20 and get final product, and is simple and safe, and balance the axial force of rotor.
Shown in Fig. 3,4,5, expansion wheel of the present invention comprises wheel disc 41 and the wheel cap 42 that interfixes, and connects fixingly for soldering between wheel disc 41 and the wheel cap 42 in this preferred embodiment, and certainly the present invention does not get rid of other fixedly connected mode.Be evenly equipped with blade 43 on the described wheel disc 41, described blade 43 is the setting of cylinder parabola, and the cylindrical cross-section of two relative faces of blade 43 is parabolic, promptly dissects two surfaces of blade with the concentric circle cylinder, and the cross surface of cutting of formation is a parabola.Such setting, make gas along turbine spiral case 1 after the fluid director mean allocation, speed can reach more than 200 meter per seconds, air-flow becomes certain included angle with the blade of expansion wheel, impact expansion wheel and make its high speed rotating, air-flow enters into expansion wheel along the radial direction of blade then, in expansion wheel, change its direction after, flow out along the axial direction of expansion wheel, promptly this moment, gas was axial flow directly entad.
Most important characteristic of the present invention is that expansion wheel adopts reaction wheel.So-called reactionary style refers to that the air-flow in the decompressor only carries out demi-inflation in nozzle, just enters expansion wheel with certain speed, promotes the expansion wheel rotation.Air-flow also further expands after entering expansion wheel, and the recoil force that further expansion produced of air-flow further promotes externally acting of expansion wheel rotation.This recoil force erect image advances the same from the high velocity air promotion rocket of rocket motor afterbody ejection.Concerning the reactionary style decompressor, pressure is divided into twice landing in fluid director and expansion wheel.It also is so that the enthalpy of gas changes, and promptly changes part energy in fluid director, changes part energy again in expansion wheel.Usually the degree of reaction that turbo-expander is called turbo-expander at what (being the reduction numerical value of enthalpy) of expansion wheel self-energy conversion and the ratio of quantity (total enthalpy drop) by fluid director and the conversion of the whole level of impeller self-energy.Obviously, concerning traditional impulse expansion turbine, degree of reaction is zero, and it is hungry that reaction turbine is expanded, and degree of reaction is generally about 0.5.Because the pressure drop of air-flow in nozzle is very big in impulse expansion turbine, generally reduce to about 0.135MPa (absolute pressure) from about 0.55MPa (absolute pressure), the speed of jet expansion air-flow is very high, and flow losses are big, thereby efficient is lower, and efficient generally has only 68% one 72%.For the reaction turbine decompressor, it generally is to reduce to about 0.27MPa from 0.55MPa that the pressure in nozzle falls, and gas flow velocity at nozzle outlet is relatively low, and flow losses are also less.Efficiency of expander generally can reach 80% one 90%.Therefore, the impulse expansion turbine that the reactionary style decompressor is traditional relatively, working efficiency has improved a lot.
Further, the surface of described wheel cap 42 is provided with 5 ring teeth 44, and the surface engagement formation labyrinth sealing with interior Diffuser 14 makes the sealing effect of whole decompressor better, has reduced leakage current amount in the gas.In addition, wheel disc 41 and wheel cap 42 are the wrought aluminium machining and form.This preferred embodiment is that numerical control milling machine processes, and the input coordinate value just can process expansion wheel of the present invention, and is simple and convenient.
Shown in Fig. 6～9, impeller of booster 12 of the present invention comprises wheel disc 121 and the wheel cap 122 that interfixes, and connects fixingly for soldering between wheel disc 121 and the wheel cap 122 in this preferred embodiment, and certainly the present invention does not get rid of other fixedly connected mode.Described wheel disc 121 is provided with blade 123, the line setting in the shape of a spiral of described blade 123, and the cross section of two relative faces of blade 123 is a concentric circle.
In this preferred embodiment, the width of blade D of blade 123 and the ratio of blade height H are between 20～25, and the airflow inlet angle [alpha] is between 30～35 degree, and the flow outlet angle beta is between 35～120 degree.Such structure is promoted the efficient of whole impeller of booster further.
Further, the surface of described wheel disc 121 is provided with 5 ring teeth 124, with the surface engagement formation labyrinth sealing of end cover body 19; The surface of described wheel cap 122 is provided with 5 ring teeth 124 equally, and the surface engagement formation labyrinth sealing with spacing sealing plate 11 makes the sealing effect of whole decompressor better like this, guarantees that gas internal leakage flow reduces.In addition, wheel disc 121 and wheel cap 122 are the wrought aluminium machining and form.This preferred embodiment is that numerical control milling machine processes, and the input coordinate value just can process impeller of booster of the present invention, and is simple and convenient.
Introduce the gas flow direction of decompressor of the present invention below with reference to Fig. 1.At inflating end, gas enters along the inlet of a direction from turbine spiral case 1, the expansion wheel 4 of after fluid director 15 mean allocation, flowing through again, and 13 ends flow out along the b direction from Diffuser then.At pressurized end, 19 inlet enters gas along the c direction from end cover body, the impeller of booster 12 of flowing through, and 3 outlet is flowed out along the d direction from volute of booster then.Expansion ratio of the present invention reaches 5.67, and pressure ratio is 1.25.In addition, for decompressor, the method for most economical best adjusting function is to change the nozzle vane height, when decompressor is in different operating mode, the cold that needs may be different, at this moment just can take to regulate expansion tolerance with the nozzle of different blade heights.
The present invention still has multiple concrete mode of execution, and all employings are equal to replacement or equivalent transformation and all technological schemes of forming, all drop within the scope of protection of present invention.
Claims (9)
1. booster expansion turbine, comprise a middle casing (2), the left end of described middle casing (2) is installed turbine spiral case (1), right-hand member is equipped with volute of booster (3), be provided with rotor (8) in the described middle casing (2) rotationally, two ends at described rotor (8) are provided with expansion wheel (4) and impeller of booster (12) respectively in turbine spiral case (1) and volute of booster (3), it is characterized in that: on described rotor (8), be arranged with left gas bearing (6) and right gas bearing (9), described left gas bearing (6) is used for supporting expansion wheel (4), be provided with stuffing box gland (5) between described left gas bearing (6) and the expansion wheel (4), described right gas bearing (9) is used for supporting impeller of booster (12), be provided with spacing sealing plate (11) between described right gas bearing (9) and the impeller of booster (12), be connected with 4 adapter assemblies on the described middle casing (2), be respectively a left side, right gas bearing (6,9) provide bearing gas, and provide blanket gas for stuffing box gland (5) and spacing sealing plate (11), described expansion wheel (4) comprises wheel disc (41) and the wheel cap (42) that interfixes, be evenly equipped with blade (43) on the described wheel disc (41), described blade (43) is the parabolic setting of cylinder, described impeller of booster (12) comprises wheel disc (121) and the wheel cap (122) that interfixes, described wheel disc (121) is provided with blade (123), described blade (123) line setting in the shape of a spiral, and the cross section of two relative faces of blade (123) is a concentric circle, be provided with bearing stop collar (7) between described left gas bearing (6) and the right gas bearing (9), described bearing stop collar (7) is set in outside the rotor (8), and cooperate with middle casing (2).
2. booster expansion turbine according to claim 1 is characterized in that: connect fixing for soldering between the wheel disc (41) of described expansion wheel (4) and the wheel cap (42).
3. booster expansion turbine according to claim 2 is characterized in that: the surface of the wheel cap (42) of described expansion wheel (4) is provided with 5 ring teeth (44).
4. booster expansion turbine according to claim 1 is characterized in that: connect fixing for soldering between the wheel disc (121) of described impeller of booster (12) and the wheel cap (122).
5. booster expansion turbine according to claim 4 is characterized in that: the surface of the wheel cap (122) of described impeller of booster (12) is provided with 5 ring teeth (124).
6. booster expansion turbine according to claim 1 is characterized in that: the width of blade (D) of the blade (123) of the wheel disc (121) of described impeller of booster (12) and the ratio of blade height (H) are between 20～25.
7. booster expansion turbine according to claim 1 is characterized in that: the airflow inlet angle (α) of described impeller of booster (12) is between 30～35 degree, and flow outlet angle (β) is between 35～40 degree.
8. booster expansion turbine according to claim 1, it is characterized in that: be provided with fluid director (15) between described turbine spiral case (1) and the expansion wheel (4), after gas is entered by turbine spiral case (1) inlet, the expansion wheel (4) of after fluid director (15) mean allocation, flowing through again.
9. booster expansion turbine according to claim 1, it is characterized in that: described middle casing (2) is provided with adapter assembly (18f), with also be provided with adapter assembly (18g) on the end cover body (19) that volute of booster (3) links to each other, be connected with equilibrium valve (20) between described two adapter assemblies.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2008101570986A CN101363330B (en) | 2008-09-18 | 2008-09-18 | Turbine boosting expansion machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2008101570986A CN101363330B (en) | 2008-09-18 | 2008-09-18 | Turbine boosting expansion machine |
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| Publication Number | Publication Date |
|---|---|
| CN101363330A CN101363330A (en) | 2009-02-11 |
| CN101363330B true CN101363330B (en) | 2011-07-06 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2008101570986A Active CN101363330B (en) | 2008-09-18 | 2008-09-18 | Turbine boosting expansion machine |
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| CN (1) | CN101363330B (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102003221A (en) * | 2010-11-16 | 2011-04-06 | 苏州制氧机有限责任公司 | After-boosted turbo expander for gas bearing |
| CN102661174A (en) * | 2012-02-24 | 2012-09-12 | 苏州制氧机有限责任公司 | Supercharged turbo expander |
| CN102865111A (en) * | 2012-09-21 | 2013-01-09 | 联优机械(常熟)有限公司 | H-shaped cylinder structure for external work output connection of turbo expander |
| CN106761972B (en) * | 2016-12-22 | 2018-08-31 | 东方电气集团东方汽轮机有限公司 | A kind of axial admission radial direction exhaust casting volute structure |
| CN107489466B (en) * | 2017-09-30 | 2023-09-19 | 苏州制氧机股份有限公司 | High-efficiency rear-supercharging adjustable nozzle gas bearing turbine expander |
| CN113048076A (en) * | 2021-03-16 | 2021-06-29 | 西安交通大学 | Air compression and expansion integrated device |
| CN113250763B (en) * | 2021-05-26 | 2024-03-22 | 中国科学院合肥物质科学研究院 | Eddy current braking turbine expander |
| CN114483213B (en) * | 2022-01-26 | 2023-05-30 | 杭州新亚低温科技有限公司 | High-flow deep cooling gas bearing turbine expander |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN86103011A (en) * | 1986-04-29 | 1987-11-18 | 西安交通大学 | All-dynamic pressured gas bearing hypothermia boost pressure-decompressor |
| CN86207338U (en) * | 1986-09-27 | 1988-02-10 | 杭州光明节能空调设备厂 | Axial-flow ventilator |
| CN2388351Y (en) * | 1999-08-06 | 2000-07-19 | 汤润泉 | Miniature turbine expansion engine |
| CN2527712Y (en) * | 2001-12-07 | 2002-12-25 | 关明 | Air sealing ring for bearing box oil catch of steam turbine |
-
2008
- 2008-09-18 CN CN2008101570986A patent/CN101363330B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN86103011A (en) * | 1986-04-29 | 1987-11-18 | 西安交通大学 | All-dynamic pressured gas bearing hypothermia boost pressure-decompressor |
| CN86207338U (en) * | 1986-09-27 | 1988-02-10 | 杭州光明节能空调设备厂 | Axial-flow ventilator |
| CN2388351Y (en) * | 1999-08-06 | 2000-07-19 | 汤润泉 | Miniature turbine expansion engine |
| CN2527712Y (en) * | 2001-12-07 | 2002-12-25 | 关明 | Air sealing ring for bearing box oil catch of steam turbine |
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| CN101363330A (en) | 2009-02-11 |
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Address after: Wuzhong District Mudu town Suzhou city Jiangsu province 215101 Spring Road No. 31 Patentee after: SUZHOU OXYGEN PLANT CO., LTD. Address before: Wuzhong District Mudu town Suzhou city Jiangsu province 215101 Spring Road No. 31 Patentee before: Suzhou Oxygen Plant Co., Ltd. |