CN1277317A - Supercharger set for large diesel engine - Google Patents
Supercharger set for large diesel engine Download PDFInfo
- Publication number
- CN1277317A CN1277317A CN00118185A CN00118185A CN1277317A CN 1277317 A CN1277317 A CN 1277317A CN 00118185 A CN00118185 A CN 00118185A CN 00118185 A CN00118185 A CN 00118185A CN 1277317 A CN1277317 A CN 1277317A
- Authority
- CN
- China
- Prior art keywords
- diffuser
- air
- gas compressor
- pressure booster
- outlet
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
- F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/44—Fluid-guiding means, e.g. diffusers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B3/00—Engines characterised by air compression and subsequent fuel addition
- F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F7/00—Casings, e.g. crankcases or frames
- F02F2007/0097—Casings, e.g. crankcases or frames for large diesel engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2250/00—Geometry
- F05D2250/50—Inlet or outlet
- F05D2250/52—Outlet
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
Abstract
A group of supercharger for a large diesel engine is proposed, including a compressor (2) for compressing gas, which is supplied air to the cylinders (11) of the large diesel engine (10). The compressor (2) comprises an outlet(23) for compressed air and a rotor (21) disposed on an axis (A) for compressing air. The supercharger also includes a turbine (3) driven by exhaust gas from the cylinder (11) for driving a rotor (21) of the compressor(2), and a diffuser (4) connected to the outlet (23) of the compressor (2) for reducing flow rate of the compressed air. The outlet (23) of the compressor (2) is disposed at a height equivalent to the axis (A) of the compressor (2) or higher at a predetermined height based on an ordinary moving direction.
Description
The present invention relates to the large-scale diesel engine pressure booster set of independent claims leading portion part.
Pressure booster set is used for being compressed in the air of scavenging and combustion process supply cylinder in for example as the large-scale diesel engine at boats and ships main driving machine group or stationary power generation station, and this air is known as scavenging or pressurized air.
Pressure booster set generally includes a gas compressor, and wherein, fresh air is sucked by rotor, by compression, and is discharged by outlet volute; A turbine, the rotor of its drive pressure mechanism of qi; A charger-air cooler.This turbine is driven by the hot waste gas that produces in cylinder during burning.This turbine and gas compressor also are known as turbocharger.The charger-air cooler that pressurized air is cooled therein is placed in after this turbocharger.These air are after passing through charger-air cooler, and most of container through being called inlet collector arrives each cylinder.The pattern that depends on large-scale diesel engine, air input cylinder occurs in different positions.For example, in the uniflow scavenging two stroke engine, the scavenging port of air through being arranged on the cylinder inferior segment is introduced in the cylinder.For example in four stroke engine, pressurized air is transfused in the cylinder through one or more suction valves that are arranged on the cylinder head.
For improving supercharging efficient, a diffuser roughly is arranged between blower outlet and the charger-air cooler, and in diffuser, the flow velocity of the air of discharging from gas compressor reduces, and through this diffuser, pressure can recover.This diffuser for example is known as expanding duct, and the flow cross of air is expansion continuously therein.
Yet the advantage with known pressure booster set of gas compressor, diffuser and charger-air cooler is the specific range that must keep between gas compressor and the charger-air cooler, so that an effective diffuser is set there.This makes the size of pressure booster set become big, and this follows large-scale diesel engine is designed to as far as possible conserve space and utilizes the hope of the useful space to run in the opposite direction ideally.
Therefore, the objective of the invention is for large-scale diesel engine provides a kind of compact especially and space-saving pressure booster set, and need not sacrifice the efficient of diffuser.This pressure booster set should be guaranteed the measured to the greatest extent useful space of utilizing.
Satisfy this purpose pressure booster set and be characteristics with independent claims and be feature.
Therefore, according to the present invention, a kind of large-scale diesel engine and pressure booster set have been proposed, it comprises a gas compressor, be used to compress the air of supplying with the large-scale diesel engine cylinder as scavenging air, described gas compressor has a compressed air outlet and one to be arranged on the axle to be used for compressed-air actuated rotor; Turbine in order to the driving compressor rotor, this turbine can be by the exhaust gas driven of cylinder; A diffuser is connected in the outlet of gas compressor, to reduce velocity of compressed air.The outlet of gas compressor is arranged on a certain height, is in or is higher than the height of compressorshaft with respect to the normal operation direction.
By this measure, but the diffuser side direction is placed on the gas compressor, like this, and gas compressor and can obviously shorten with the distance between rear such as the charger-air cooler, and the length of diffuser need not shorten streamwise and see the time, this length is necessary for its validity.This allows the structure of pressure booster set compact especially, and its free space is perfectly utilized.
The unit that comprises gas compressor and turbine is known as turbocharger.This gas compressor and turbine are accommodated in the public housing usually.Therefore, hereinafter, " gas compressor base plane " and " turbocharger base plane " is understood as has same meaning.
Diffuser preferably is designed to tubular, and it is expanded along air-flow direction, the corresponding basically base plane that extends to gas compressor or turbocharger.This gas compressor or turbocharger are corresponding to be installed on the platform, therefore its bottom plane is on this platform, because this diffuser does not protrude from respectively under gas compressor or the turbocharger bottom plane, therefore, flowing into therebetween charger-air cooler from the air of diffuser can directly be placed under this platform.Like this, the general construction height of pressure booster set has reduced, this for the large-scale diesel engine structure as far as possible compactness be particular importance.
Proved when diffuser effectively especially during at least along the roughly tapered expansion of a part of its height already, half of its angle of flare be less than 12 °, particularly 4 ° to 8 °.
In addition, be favourable if be designed to diffuser with respect to air-flow direction to small part bending.Thereby diffuser can side direction be settled, and as far as possible in abutting connection with gas compressor, like this, can utilize the useful space fully by the utmost point.This diffuser for example can design like this in its end that is connected with blower outlet, makes it form a continuous outlet volute.
If diffuser is in its end that links to each other with blower outlet, its air inlet area is to 1/3 of the discharge area that reaches this diffuser the other end, then the usefulness for diffuser is favourable, by this measure, the air high flow rate that for example can reach 100M/S in the outlet of gas compressor can drop to enough low numerical value in diffuser, for example reach 30-40m/s in the outlet port of gas compressor.Like this, just can return to quite high pressure, from the viewpoint of thermokinetics, this is particularly advantageous for supercharging efficient.
In a preferential especially embodiment, this diffuser is made into a single-piece.
In another preferential embodiment, this diffuser comprises at least two parts, and they are arranged in order with respect to air-flow direction, and a compensator section is arranged between these two parts.By means of this compensator, the thermal expansion that can compensate diffuser and spiral case changes.
In addition, be favourable when diffuser has one during in order to fixing diffuser with in order to the securing means of the power of peptizaiton on diffuser, this securing means be arranged on basically with compressor rotor axle sustained height on.Because this Diffuser does not also reach its maximum flow cross section on this height, therefore, the power that is produced by air pressure is so not big yet.
Pressure booster set of the present invention is specially adapted to wish the compact especially and space-saving large-scale diesel engine of its structure.
To draw other favourable measure of the present invention and preferential embodiment in the dependent claims.
Below with reference to exemplary embodiment and description of drawings the present invention.Each does not draw these signals in proportion, wherein:
Fig. 1 represents to have the large-scale diesel engine as the pressure booster set of exemplary embodiment of the present;
Fig. 2 is with gas compressor and diffuser perpendicular to section presentation graphs 1 exemplary embodiment of rotor shaft;
Fig. 3 as shown in Figure 2, but expression is pressure booster set as the present invention's second exemplary embodiment.
In the following description, the regulation of relevant position, such as " on, down, thereon, at it down ... " relevant with the normal operation direction shown in Fig. 1-3.In addition, between scavenging and pressurized air, there is not notional difference.
Fig. 1 represents the major component of large-scale diesel engine exemplary with the local height schematic representation, and it is designed to a direct current scavenging two-stoke cycle engine, and it is represented with label 10 on the whole.In common many cylinders of large-scale diesel engine 10 one represents with label 11.
Device one piston 14 in cylinder 11, it can upper and lowerly move.This piston is connected on the unshowned crosshead through a unshowned piston rod 15, and crosshead is connected on the bent axle of large-scale diesel engine 10 through a push rod at the other end.Be provided with some scavenging ports 16 in the inferior segment of cylinder 11, these scavenging air mouths are covered by piston 14 or expose, and depend on position of piston.The fresh air that is called scavenging or pressurized air is in scavenging port 16 can flow into cylinder 11, shown in arrow S.
Be provided with one or more nozzles 12 in the district on cylinder 11, be used for fuel is sprayed in the fuel chambers of cylinder 11, also be provided with the outlet valve 13 of a center arrangement, the combustion gas that produces in combustion process is flowed out as waste gas through this valve.Waste gas is in the waste gas connection pipe fitting inflow exhaust gas trap 6 of outlet valve 13 vicinities.Exhaust gas collector 6 also is connected in other cylinder in a similar fashion.
Exemplary with the pressure booster set of the present invention of label 1 expression has scavenging air on the whole, to cylinder 11 inflations.This pressure depressor group 1 comprises one in order to compressed-air actuated gas compressor 2, turbine 3 in order to drive pressure mechanism of qi 2, one is configured in gas compressor 2 back in order to reducing the diffusers 4 of pressurized air flow velocity, and the charger-air cooler 5 that cooled off within it of pressurized air.Gas compressor 2 and turbine 3 are arranged in the public housing, constitute a turbocharger.
Air flows to an inlet collector 18 from the outlet of charger-air cooler 5 through a pressure piping 17, and scavenging air arrives the scavenging port 16 of cylinder 11 from this inlet collector.When piston 14 exposed scavenging port 16, scavenging air can flow in the cylinder 11, shown in arrow S among Fig. 1.
Gas compressor 2 (see figure 2)s comprise a rotor 21, and it is set on the A, and are provided with some blades or wheel leaf 11, and it stretches out from axle A in all cases.The sense of rotation of rotor 21 is indicated by the arrow D among Fig. 2.Around rotor 21, be provided with an outlet volute 22.Some second static stators 25 are arranged between rotor 21 and the outlet volute 22 by radial direction in original known mode.Outlet volute 22 surrounds the radial outer end of second stator 25, and delimits the spirality chamber 22a of radial expansion when the sense of rotation D along rotor 21 sees, therefore, when when sense of rotation D sees, the distance increase between second stator, 25 radial outer ends and the outlet volute 22.The import of gas compressor 2 is arranged like this, and the fresh air that makes suction flow to rotor 21 along the direction of axle A, shown in arrow F among Fig. 2.Rotor 21 pushes fresh air in the helical cavity 22a, and pressurized air arrives the outlet 23 of gas compressor 2 from helical cavity.
In the case, because the end that outlet 23 is meant outlet volute 22, this means the cross-section area of outlet volute 22, and it just is in helical cavity 22a and just in time finishes it around first of axle A turn-take 360 ° (complete volutions).In the sectional elevation of Fig. 2, helical cavity 22a begins in the position with the B mark, and radially expands one when when sense of rotation D sees.Like this, in the figure, the outer wall of outlet volute 22 has provided a helix.The place that this helix is finished 360 ° of its first coils is the outlet 23 of gas compressor 2.According to the expression of Fig. 2, the cross section of outlet 23 is that a prolongation that radially extends of A to B point line is arranged.According to the present invention, the outlet 23 of gas compressor 2 is arranged in the height of the axle A that is higher than gas compressor 2 under the direction of normal operation shown in Fig. 2.
The housing of gas compressor 2 or turbocharger 2,3 also has a base 24, and it is installed on the platform 19 that is fixed in motor body.The base plane 24a that 24 following interface is called gas compressor 2 is recognized at the end, and base 24 this time of usefulness interfaces contact with platform 19.
The rotor of gas compressor drives (see figure 1) by turbine 3 by original known mode.For this reason, turbine 3 preferably is installed in and installs on the same axle A of rotor 21.Waste gas flows out from exhaust gas collector 6, flow to turbine 3 through a flue gas leading 7, and drives the envoy.Behind the turbine 3 of flowing through, waste gas flows out through another flue gas leading that does not show, shown in arrow G among Fig. 1.
Rotation turbine 3 is through the rotor 21 of axle A drive pressure mechanism of qi 2.The latter sucks fresh air through suction port, and this suction port is in the back on diagram plane among Fig. 1, therefore cannot see.Fresh air flow to rotor 21 from the direction of axle A, and pushes helical cavity 22a by its wheel blade 211.After this, pressurized air flows out gas compressor 2 through exporting 23.
The outlet 23 of gas compressor 2 is connected in diffuser 4.Diffuser 4 is designed to tubular, and expands along air-flow direction.Diffuser 4 has a compressed air outlet district 42 at the one end.
In the exemplary embodiment shown in Fig. 2, diffuser 4 is made into single-piece.As shown in Figure 2, diffuser 4 is designed to arc, the outlet volute 22 of gas compressor 2 is connected.Calm the anger 2 outlet 23 of diffuser next-door neighbour, its cross section streamwise increases.An end that is connected in outlet 23 of diffuser 4 constitutes the entrance region 41 of diffuser 4, and it is identical with the cross section of the outlet 23 of diffuser 4.
Diffuser 4 can be designed to a construction package with outlet volute 22, making it is a whole constituent element of gas compressor 2.Yet, also diffuser 4 can be made single parts, then, for example it is connected with outlet volute 22 by flange connection or welding.
In exemplary embodiment shown in Figure 1, directly be placed in platform 19 following charger-air coolers 5 and comprise a gas transmission road 51, it is connected in the lower end of expanding section 4, and the air of diffuser 4 outlet areas 42 of flowing through can be flowed in the charger-air cooler 5 through this gas transmission road 51.
In exemplary embodiment shown in Figure 2, in the lower end of diffuser 4, promptly roughly on the height of platform 19, be provided with a compensator section 43, with the thermal expansion of the spiral shaped housing of compensation diffuser 4 and outlet volute 22.Compensator section 43 is for example made bellows, and be connected in diffuser 4 through flange connector 43a.Then, the intake duct 51 of charger-air cooler 5 is in abutting connection with compensator section 53.
In addition, unshowned tight device together is set preferably on diffuser 4, so that disperse power and torque to the housing of motor.
Preferably whole diffuser 4 is designed like this, make its discharge area 42 be at least two times of its inlet-duct area 41, preferably be at least three times, because these physical dimensions, height to the pressurized air flow velocity of 100m/s of diffuser 4 inlet-duct areas 41 of for example flowing through generally can be reduced to 40-30m/s, like this, air pressure is increased to suitable degree.
The view that Fig. 3 is similar to Fig. 2 is represented the gas compressor and the diffuser 4 of another exemplary embodiment of pressure booster set of the present invention.Below main its difference of discussing, in addition, the mode of explanation embodiment illustrated in fig. 2 also is applicable to mode embodiment illustrated in fig. 3.Especially has same meaning among the label among Fig. 3 and Fig. 2.
In Fig. 3 embodiment, diffuser 4 comprises two-part 4a, and 4b is designed to pipe cross-section with it in all cases, and the streamwise end-to-end.Top 4a is designed to arc, and just in time in abutting connection with the outlet 23 of gas compressor 2, its cross section is preferably made streamwise to be increased.With the inlet-duct area 41 of the end formation diffuser 4 that exports the 23 top 4a that link to each other, it is identical with the cross-section area of the outlet 23 of gas compressor 2.Top 4a along with the equidirectional bending of outlet volute 22, roughly extend to 21 residing height of rotor, therefore, the discharge area of top 4a is roughly parallel with platform 19.Top 4a and outlet volute 22 can be designed to a structural entity, like this, top 4a is a whole constituent element of gas compressor 2.Yet also top 4a can be made independent parts, then, for example it is connected to outlet volute 22 by flange connection or welding.
In this embodiment, gas compressor 43 is arranged between top 4a and the bottom 4b.Gas compressor 43 for example is connected in upper and lower part 4a, the 4b of diffuser through flange connector 43a., be preferably in securing means is set on the diffuser, because the result of diffuser 4 internal pressures acts on power or the moment on the base 24 of spiral case or turbocharger 2,3 respectively for reducing with the power and the moment of peptizaiton on this motor body.Because diffuser 4 does not also reach its maximum cross section on the height of axle A, the power that is produced therein by static pressure is also less big especially.Therefore, this securing means roughly is arranged on rotor 21 the axle A height with regard to its mechanical stress, be favourable.
The bottom 4b self compensation section 43 of diffuser extends to the platform 19 that turbocharger 2,3 is mounted thereon.Platform 19 preferably is fixed in by securing means 44 in the lower end of bottom 4b.Like this, discharge area 42 corresponding positions of diffuser 4 with the same high height of the base plane 24a of gas compressor 2 or turbocharger 2,3 on.This bottom 4b is designed to funnel shaped, this means that its self compensation section 43 is to the roughly tapered expansion of discharge area 42.Wherein, the cross section of bottom 4b can be designed to have some angles, as square, or circular.Making half angle of flare α less than 12 °, is favourable with regard to particularly 4 °-8 ° efficient with regard to diffuser 4 are tried one's best well.
Diffuser 4 expands to the base plane 24a of gas compressor 2 from the outlet 23 of gas compressor 2, and diffuser 4 stops on this plane.Wherein, diffuser 4 is such expansions, the size of its inlet-duct area 41 still reach diffuser 4 discharge area 42 to mostly, preferably at the most 1/3.
Because the outlet 23 of (Fig. 2 and 3) gas compressor is in or is higher than the height of the axle A of rotor 21 in two embodiments of the present invention, therefore the diffuser 4 that has enough spaces will have about the above-mentioned geometrical shape of angle of flare α and inlet/outlet area (41,42) ratio between the outlet 23 of gas compressor 2 and base plane 24a or platform 19 is placed in the there.Like this, diffuser 4 terminates on the height of base plane 24a of gas compressor 2 or turbocharger 2,3, and need not reduce the diffuser effective length.Because the outstanding downwards base plane 24a that surpasses gas compressor 2 or platform 19 of diffuser 4, thus charger-air cooler 5 can be directly installed on platform 19 under, need not in other words at interval, so the height overall of pressure booster set 1 has reduced.
Obviously, pressure booster set 1 of the present invention also is applicable to other large-scale diesel engine except that uniflow scavenging two stroke engine as herein described.For example, pressure booster set 1 of the present invention also can be a constituent element of 4 stroke large diesel machines by similar mode, and in this diesel engine, pressurized air is imported in the cylinder through one or more suction valves that are arranged on the cylinder head.
Claims (9)
1. the pressure booster set of large-scale diesel engine, it comprises a gas compressor (2) in order to the air in the cylinder (11) that compresses the large-scale diesel engine (10) that is transfused to as scavenging air, described gas compressor (2) has a compressed air outlet (23) and one and is arranged on axle (A) and goes up voltage supply rotor (21) that air uses that contracts; The turbine (3) that also comprises a rotor (21) in order to drive pressure mechanism of qi (2), this turbine (3) can be by the exhaust gas driven of discharging in cylinder (11); Also comprise a diffuser (4), it is connected in the outlet (23) of gas compressor (2), to reduce velocity of compressed air, it is characterized in that the outlet (23) of gas compressor (2) is arranged on the height that is in or is higher than the axle (A) of gas compressor (2) with respect to the normal operation direction.
2. by the described pressure booster set of claim 1, it is characterized in that diffuser (4) is designed to tubular, it is expanded along air-flow direction, and the extend to gas compressor basically base plane of (2).
3. by the described pressure booster set of claim 2, it is characterized in that comprising a charger-air cooler (5), air from diffuser (4) flows in it, this gas compressor is placed on the platform (19) with its base plane (24a), and charger-air cooler (5) directly be placed in platform (19) below.
4. by the described pressure booster set of one of aforesaid right requirement, it is characterized in that diffuser (4) is at least along the tapered basically expansion of one partial-length, the angle of flare＜α〉half be less than 12 °, especially 4 °-8 °.
5. by the described pressure booster set of claim 1, it is characterized in that diffuser (4) is designed to respect to air-flow direction to the small part bending.
6. by the described pressure booster set of claim 1, it is characterized in that diffuser (4) is connected an end at it with the outlet (23) of gas compressor (2), its inlet-duct area (41) reach discharge area (42) at its other end extremely mostly, especially at the most 1/3.
7. by the described pressure booster set of claim 1, it is characterized in that diffuser (4) comprise two parts (4a, 4b), they join end to end with respect to air-flow direction, a compensator (43) is arranged between these two-part.
8. by the described pressure booster set of claim 1, it is characterized in that diffuser (4) has securing means, with the power of peptizaiton on diffuser (4), this robust means is arranged on basically axle (A) sustained height with the rotor (21) of gas compressor (2).
9. comprise large-scale diesel engine by the described pressure booster set of above-mentioned arbitrary claim (1).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP99810521 | 1999-06-14 | ||
| EP99810521.7 | 1999-06-14 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1277317A true CN1277317A (en) | 2000-12-20 |
| CN1175189C CN1175189C (en) | 2004-11-10 |
Family
ID=8242876
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB001181858A Expired - Fee Related CN1175189C (en) | 1999-06-14 | 2000-06-13 | Supercharger set for large diesel engine |
Country Status (7)
| Country | Link |
|---|---|
| EP (1) | EP1061265B1 (en) |
| JP (1) | JP2001020747A (en) |
| KR (1) | KR100659677B1 (en) |
| CN (1) | CN1175189C (en) |
| DE (1) | DE50011843D1 (en) |
| DK (1) | DK1061265T3 (en) |
| PL (1) | PL340532A1 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102444463A (en) * | 2010-10-05 | 2012-05-09 | 福特环球技术公司 | Internal combustion engine with liquid-cooled turbine and method for cooling the turbine |
| CN102606530A (en) * | 2011-01-18 | 2012-07-25 | 德昌电机(深圳)有限公司 | Centrifugal device and cleaning device |
| CN103206411A (en) * | 2012-01-17 | 2013-07-17 | 哈米尔顿森德斯特兰德公司 | Fuel System Centrifugal Boost Pump Volute |
| CN104169544A (en) * | 2012-03-15 | 2014-11-26 | 西门子公司 | Compressor inlet manifold for a gas turbine engine |
| CN105683582A (en) * | 2013-08-19 | 2016-06-15 | 动力推进系统有限公司 | Diffuser for a forward-swept tangential flow compressor |
| CN106050700A (en) * | 2016-07-19 | 2016-10-26 | 东莞市宏铭通风设备有限公司 | Noiseless fan structure |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4011368B2 (en) * | 2002-02-27 | 2007-11-21 | 京セラ株式会社 | Wireless communication system and wireless communication method |
| JP4590167B2 (en) * | 2003-06-05 | 2010-12-01 | セイコー化工機株式会社 | Centrifugal blower |
| DK1881173T3 (en) * | 2006-07-19 | 2009-07-20 | Waertsilae Nsd Schweiz Ag | Multi-diffuser for a piston-combustion engine and piston-combustion engine |
| NL1040722B1 (en) * | 2014-03-12 | 2015-11-19 | Mitsubishi Turbocharger And Engine Europe B V | Compressor housing. |
| DE102018215888A1 (en) * | 2018-09-19 | 2020-03-19 | Robert Bosch Gmbh | compressor |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB567156A (en) * | 1943-06-22 | 1945-01-31 | Oswald Wans | Improvements in or relating to turbo-blowers |
| CH286975A (en) * | 1951-05-01 | 1952-11-15 | Karrer Josef | Centrifugal fan, in particular fan with spiral housing. |
| DE19710408B4 (en) * | 1997-03-13 | 2010-08-05 | Man B & W Diesel A/S | Reciprocating internal combustion engine |
-
2000
- 2000-05-15 DE DE50011843T patent/DE50011843D1/en not_active Revoked
- 2000-05-15 EP EP00810411A patent/EP1061265B1/en not_active Revoked
- 2000-05-15 DK DK00810411T patent/DK1061265T3/en active
- 2000-05-18 JP JP2000146166A patent/JP2001020747A/en active Pending
- 2000-06-01 KR KR1020000029865A patent/KR100659677B1/en not_active IP Right Cessation
- 2000-06-05 PL PL00340532A patent/PL340532A1/en not_active Application Discontinuation
- 2000-06-13 CN CNB001181858A patent/CN1175189C/en not_active Expired - Fee Related
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102444463A (en) * | 2010-10-05 | 2012-05-09 | 福特环球技术公司 | Internal combustion engine with liquid-cooled turbine and method for cooling the turbine |
| CN102444463B (en) * | 2010-10-05 | 2016-05-11 | 福特环球技术公司 | There is the internal combustion engine of liquid-cooling type turbine and the method for cooling turbomachine |
| CN102606530A (en) * | 2011-01-18 | 2012-07-25 | 德昌电机(深圳)有限公司 | Centrifugal device and cleaning device |
| CN103206411A (en) * | 2012-01-17 | 2013-07-17 | 哈米尔顿森德斯特兰德公司 | Fuel System Centrifugal Boost Pump Volute |
| CN103206411B (en) * | 2012-01-17 | 2015-12-02 | 哈米尔顿森德斯特兰德公司 | Fuel System Centrifugal Boost Pump Volute |
| CN104169544A (en) * | 2012-03-15 | 2014-11-26 | 西门子公司 | Compressor inlet manifold for a gas turbine engine |
| CN104169544B (en) * | 2012-03-15 | 2017-03-08 | 西门子公司 | Suction port of compressor manifold for gas turbine engine |
| CN105683582A (en) * | 2013-08-19 | 2016-06-15 | 动力推进系统有限公司 | Diffuser for a forward-swept tangential flow compressor |
| CN106050700A (en) * | 2016-07-19 | 2016-10-26 | 东莞市宏铭通风设备有限公司 | Noiseless fan structure |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1175189C (en) | 2004-11-10 |
| KR20010007159A (en) | 2001-01-26 |
| KR100659677B1 (en) | 2006-12-21 |
| DE50011843D1 (en) | 2006-01-19 |
| PL340532A1 (en) | 2000-12-18 |
| DK1061265T3 (en) | 2006-02-06 |
| EP1061265B1 (en) | 2005-12-14 |
| EP1061265A1 (en) | 2000-12-20 |
| JP2001020747A (en) | 2001-01-23 |
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