CN1363764A - Boosting system for steaming turbine of IC engine - Google Patents
Boosting system for steaming turbine of IC engine Download PDFInfo
- Publication number
- CN1363764A CN1363764A CN01101560A CN01101560A CN1363764A CN 1363764 A CN1363764 A CN 1363764A CN 01101560 A CN01101560 A CN 01101560A CN 01101560 A CN01101560 A CN 01101560A CN 1363764 A CN1363764 A CN 1363764A
- Authority
- CN
- China
- Prior art keywords
- turbine
- steam
- steaming
- gas
- vapour
- 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
Links
Images
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Landscapes
- Supercharger (AREA)
Abstract
A turbine boosted IC (diesel) system features that on the basis of turbine booster, a return heat circulating unit using the afterheat of the exhausted air of turbine booster is used to generate steam, which is mixed with the exhausted air of IC engine and then introduced to turbine to greatly increase its power, resulting in low oil consumption and higher overall performance.
Description
The present invention relates to a kind of turbocharged internal engine system, especially turbocharged diesel system.
Because the progress of turbocharging technology, make internal-combustion engine especially every performance index such as power, Economy, weight and volume of diesel engine all obtained tangible improvement.Modern high-power diesel engine has almost all adopted turbo charging installation, and wherein most widely used be the exhaust gas turbocharge device.Turbocharging internal-combustion engines is the compound engine that internal-combustion engine and turbosupercharger are formed, under various operating modes, turbo charging installation should provide enough air quantities to internal-combustion engine, if the air demand deficiency of turbosupercharger will cause the deterioration of working procedure.Yet, when engine conditions changes, exhaust gas flow and parameter also all change, the result of shuttle internal-combustion engine and helicoid turbosupercharger characteristic coupling normally turbo-charged diesel the boost pressure deficiency can occur when low operating mode is moved, little and the more high inherent characteristic of waste gas row's temperature of burning excess air coefficient, it directly shows is exactly that turbosupercharger can not provide operating conditions desired pressure ratio, satisfies the requirement to air quantity.
The roadability (roadability of a specific turbosupercharger) of the turbosupercharger of figure one expression turbo-charged diesel under different operating conditionss is promptly in following pressure ratio that can provide of different turbine inlet corrected flows.As seen from the figure, at declared working condition, i.e. design point, pressure ratio that pressurized machine provides and conforming to that diesel oil requires.When hanging down operating mode, the roadability difference provides different with the pressure ratio difference that requires.By automobile-used characteristic, Ne=cn
2, Ne=cn
3The pressure ratio that pressurized machine can provide during the operation of (Ne-power, n-rotating speed) characteristic all can not meet the demands.
In order to improve the low-load performance of turbo-charged diesel, currently on turbo charge system, adopted how sharp measure, as put the waste gas pressurization system, put (or back) throttling pressurization system before the pressurization system, turbine of pressurized air, bypass pressurization system and backheat bypass pressurization system etc.Various improvement projects all have its pluses and minuses separately.
The purpose of this invention is to provide a kind of novel turbocharger system, it can increase substantially the pressure ratio of turbosupercharger, the pressure ratio under the especially low operating mode, thus improve the performance of hanging down operating mode, improve the power of turbocharging internal-combustion engines, reduce the oil consumption rate of turbocharging internal-combustion engines.
The present invention is on the basis of turbosupercharger, utilizes the exhaust heat of turbosupercharger, and a Rankine backheat circulation is set, and constitutes a kind of boosting system for steaming turbine of novelty.The steam that the mat waste heat is produced injects turbine will improve turbine power significantly, make pressure ratio and flow increase by the gas compressor of its driving, thereby reach the power that improves turbocharging internal-combustion engines, reduce its oil consumption rate, obviously improve the purpose of low-load performance.
Systematic schematic diagram of the present invention is seen Fig. 2.Its main flow process is:
The working medium air enters cylinder of internal-combustion engine 2 through gas compressor 1 supercharging, and compression and combustion work done final vacuum enters turbine 3.Water enters exhaust heat boiler 4 as second kind of working medium, absorbs heat and become superheated vapor in exhaust heat boiler 4 from the turbine exhaust waste heat, be injected into turbine by special steam injection system before.The mixed working fluid expansion working drive pressure mechanism of qi of being made up of two kinds of working medium (combustion gas, steam) in turbine 3 is after exhaust heat boiler 4 enters atmosphere.The steam flow of re-injection can satisfy the needs of turbocharging internal-combustion engines by modulating valve 5 controls.Excess steam can be drawn by bypath system 6 and uses it for anything else or discharge.
Fig. 3 is an another kind of systematic schematic diagram of the present invention.Its main flow process is:
The working medium air enters cylinder of internal-combustion engine 2 through gas compressor 1 supercharging, and compression and combustion work done final vacuum enters turbine 3.On-the-spot existing steam is through decompression or reducing-and-cooling plant 10 and modulating valve 5 injection turbines 3.By mixed working fluid expansion working in turbine 3 of combustion gas, vapour composition, the drive pressure mechanism of qi enters atmosphere at last.
Obviously, system shown in Figure 3 adopts under a kind of specific occasion, promptly on-the-spot existing existing suitable steam source.At this moment, though there is not the used heat utilization, it is very simple that whole system becomes, and still can effectively realize target of the present invention.
Be described below for capital equipment among the present invention and system:
1. steaming turbine pressurized machine
Two inependent modes are arranged: the fuel gas temperature and the pressure of turbine inlet (engine exhaust gas outlet) in the turbosupercharger.But in the steaming turbine pressurized machine, also has an inependent mode: the ratio of steam mass flow and combustion gas quality flow, i.e. vapour/gas ratio.The size of vapour/gas ratio is bigger to the pressure ratio of turbosupercharger, change in rotational speed influence, because depress steam specific heat at least than air waiting---and the specific heat of fuel combustion product doubles, so the acting ability of steam is bigger.Steam injecting temperature is then less relatively to the influence of pressure ratio, rotating speed.Fig. 4 illustrates the variation that a specific pressurized machine is annotated characteristic behind the vapour, along with vapour/gas than increasing, the pressure ratio of turbosupercharger increases.
When select vapour/gas than the time should take all factors into consideration following factor and make optimal selection:
(1) internal-combustion engine is to the requirement of pressurized machine pressure ratio, flow;
(2) surge margin of gas compressor;
(3) rev limit of turbosupercharger;
(4) through-current capability of turbine;
(5) compactedness of exhaust heat boiler (size, weight);
(6) take into account full re-injection and zero re-injection.
Usually, annotate the vapour position and should move to the upstream of turbine as far as possible so that steam and gas blending is even as far as possible, therefore, annotate on the outlet pipe that the vapour position is located at internal-combustion engine and be advisable, only under extreme case, be located on the suction tude of turbine.
When select big vapour/gas than the time, the nozzle ring area is made corresponding adjustment possibly in view of the above, to guarantee that maximum vapour/gas is than the through-current capability under the condition.
The back pressure of steaming turbine pressurized machine raises because exhaust heat boiler is housed turbine outlet, raises and the loss that brings much larger than back pressure but annotate the power gain that obtains behind the vapour.
2. exhaust heat boiler
Exhaust heat boiler absorbs the turbosupercharger heat of exhaust and produces steam.When turbosupercharger was moved in non-re-injection mode, the composition of exhaust was combustion gas; When moving in the re-injection mode, the composition of exhaust is that combustion gas adds steam.
Turbocharged internal engine system require exhaust heat boiler structure height compactness, in light weight, thermal inertia is little.Its design philosophy is not to maximally utilise exhaust heat fecund steam, but according to the requirement of turbosupercharger, and is compromise in steam production and exhaust heat boiler size, weight intercropping.The exhaust heat boiler structure should be selected direct current cooker or pump circulation pattern, adopts enhanced heat transfer component, or the unique construction of highly compact.Exhaust heat boiler should be designed to allow " dry combustion method ", and when some parts of exhaust heat boiler broke down or require work " zero " notes automotive capable, exhaust heat boiler can be made dry-running.
3. steam injection system
For superheated vapor is imported turbosupercharger from exhaust heat boiler, re-injection system need be set.
To Fig. 2 system, mainly should comprise and annotate steam flow adjustable valve, notes vapour nozzle, purge system, steam by-pass system.Purge system 7 (Fig. 2,3) is to tie up to preheating before the work for annotating steam pipe, has prevented that water enters charging turbine with fixed attention.Bypath system is for discharging possible excess steam and shut down at diesel engine, and exhaust heat boiler is bigger because of thermal inertia, continues to produce the usefulness of the discharging of steam.
To Fig. 3 system, also should comprise a temperature-decreased pressure reducer.
4. turbine exhaust bypath system
Exhaust gas bypass system 8 (Fig. 2,3) is the system that may need setting under some specified conditions.
Internal-combustion engine has increased the resistance that its waste gas is discharged after the installing turbosupercharger, also have the additional flue gas resistance of exhaust heat boiler when adopting the steaming turbine pressurized machine, to this responsive internal-combustion engine, can adopt exhaust gas bypass system for improving its starting performance to some.
In addition, the adjusting by the exhaust gas bypass system is effective steam regulation output also, can adopt this method under some specified conditions.
Now, turbo charge system has developed various ways, and the steam injection system can be applied to various types of turbo charge systems fully.
As an example, Fig. 5 has provided the notes vapour pressurization system schematic representation of drive turbine.
In order to further specify the superiority of boosting system for steaming turbine of the present invention, introduce an example.
Certain use for diesel engine turbosupercharger, its calibrating parameters sees Table one.
Fig. 1 has illustrated the turbosupercharger matching property of turbo-charged diesel under different operating conditionss.And pointed out, in, during low operating mode, the pressure ratio that pressurized machine can provide can not satisfy by automobile-used characteristic, Ne=cn
2, Ne=cn
3The characteristic operation is to the requirement of pressure ratio.Now adopt steaming turbine supercharged diesel system as the improvement measure.
After Fig. 6 represents to adopt boosting system for steaming turbine, this pressurized machine at different vapour/gas than following obtainable pressure ratio value added.
Fig. 7 represents to adopt the roadability of turbosupercharger behind the boosting system for steaming turbine.This characteristic is 0.06 time acquisition at steam-to-gas ratio.As seen from Figure 7, the turbosupercharger after the steam injection can satisfy Ne=cn
2, Ne=cn
3To the requirement of pressure ratio, even during by the operation of automobile-used characteristic, its performance also is greatly improved.And, when declared working condition and high operating mode, in turbosupercharger rotating speed allowable, also can make pressure ratio that bigger rising is arranged.
It is about 16% that second table has reflected finally that the effect of Steam-injected Turbo-charged Diesel system, the power averaging of diesel engine increase, and oil consumption rate on average descends about 1.8%.
To sum up, the steaming turbine boosting internal combustion engine system of the present invention's proposition has following characteristics:
(1) significantly improves power of IC engine
Because second working medium is water, is waiting the steam specific heat of depressing at least than air---the specific heat of fuel combustion product doubles.In other words, steam can be done bigger mechanical work than I. C. engine exhaust (air---fuel combustion product) as main working medium.Along with the increase of vapour/gas ratio, the power of charging turbine increases thereupon, thereby the flow of gas compressor, pressure ratio are increased, and the power of internal-combustion engine is increased considerably.
(2) improve the efficiency of internal combustion engine
For former pressurization system, new system of the present invention has increased exhaust heat boiler to produce steam, and this has increased the power consumption of pump water.In fact, the power consumption of pump water pressurization is little, then need a large amount of energy but water is become steam, and this is to utilize exhaust heat in native system, and this has just improved the efficient of boosting system for steaming turbine, thereby has improved the efficient of internal-combustion engine.If (cold water between the cylinder cooling water of internal-combustion engine, air inlet linked to each other with the exhaust heat boiler feedwater then can further improve can utilization ratio).
(3) Du Te parameter matching and regulative mode
Two inependent modes are arranged: turbine inlet temperature (TIT) and pressure ratio in the common turbocharger design.Three inependent modes are arranged: turbine inlet temperature (TIT), pressure and vapour/gas ratio in the boosting system for steaming turbine design of the present invention.For one for the equipped turbosupercharger of internal-combustion engine, the intake condition of turbine has been determined by the exhaust parameter of diesel engine, and for one for the equipped steaming turbine pressurized machine of internal-combustion engine, its turbine inlet parameter still can be regulated by the variation of vapour/gas ratio.After adopting the steaming turbine pressurized machine, the air pressure of supercharger outlet, flow all are improved largely under each operating mode, the vapour regulating system of notes and turbine exhaust bypass regulating system are arranged in addition, integrated use can obtain a characteristic of approaching mutually with the desired turbosupercharger characteristic of moving law.
(4) part load performance is good
Common turbosupercharger fails to reach the expected value of internal-combustion engine under this operating mode because of the turbine drives underpower makes the pressure ratio of pressurized machine and flow when sub load.In the boosting system for steaming turbine of the present invention, the mass flow rate of turbine can increase the output of turbine with the straightforward procedure that changes steam flow, improves the air mass flow and the pressure ratio of pressurized machine, thereby makes part load performance good.
(5) real feasibility
Boosting system for steaming turbine of the present invention can be reequiped enforcement on original turbosupercharger, mainly be to have added some equipment, system, and less to the change of former turbosupercharger, the power of IC engine that is obtained and the improvement of oil consumption rate are schemes that reality is feasible again clearly.
In fact, the operating temperature of the mixed working fluid of charging turbine import is starkly lower than the operating temperature of not annotating vapour originally behind the notes vapour, so this also makes the operating life of charging turbine prolong.
(6) step response
Steaming turbine boosting internal combustion engine of the present invention system than former turbocharged internal engine system many exhaust heat boiler parts that thermal inertia is relatively large, this will make system of the present invention produce transient response with respect to original system and lag behind.In order to improve step response, exhaust heat boiler adopts little inertia design, and preferable method is to adopt the vapour/gas ratio of appropriateness when sub load, and like this, speed of response only depends on the speed of annotating steam control valve.
Should see also that in addition one of turbo-charged diesel transient response lagging reasons is that pressurized machine is poor at the pressurized effect of low velocity zone, has limited the transient response of motor.System of the present invention can obviously improve the pressurized effect of low velocity zone, has improved the transient response of supercharged diesel engine in this.
To annotate characteristic variations figure Fig. 5 behind the vapour be the roadability of the steaming turbine pressurized machine of Steam-injected Turbo-charged Diesel under different operating conditionss for pressurized machine for pressure ratio gain diagram Fig. 7 that notes vapour pressurization system schematic representation Fig. 6 of drive turbine is obtained after for pressurized machine notes vapour to description of drawings: Fig. 1 in order to simplify boosting system for steaming turbine schematic diagram Fig. 4 for boosting system for steaming turbine schematic diagram Fig. 3 at the roadability Fig. 2 of the turbosupercharger under the different operating conditionss for turbo-charged diesel
Table one
Certain turbocharger calibrating parameters
Table two
| Title | Unit | Parameter |
| Turbine inlet temperature (TIT) | ℃ | 580 |
| Air mass flow | Kg/s | 5.5 |
| Pressure ratio | 2.88 | |
| Efficiency of turbocharger | 0.72 |
Benefit behind the employing boosting system for steaming turbine
| Steam-to-gas ratio=0.06 | |||||
| Former pressure ratio | 1.502 | 1.877 | 2.275 | 2.499 | 2.88 |
| Increased power (%) | 16.21 | 16.11 | 16.46 | 16.43 | 14.74 |
| Rate of fuel consumption decline (%) | 2.3 | 1.95 | 1.73 | 1.61 | 1.32 |
Claims (6)
1. the turbocharged internal engine system of a steam injection is characterized in that utilizing the exhaust heat of turbosupercharger on the basis of conventional turbocharger, and a Rankine backheat circulation is set, and constitutes a kind of boosting system for steaming turbine of novelty.The water vapor that the mat waste heat is produced, after I. C. engine exhaust mixes, enter work done in the turbine of turbosupercharger, thereby pressure ratio and flow by the gas compressor of its driving are increased, reach the power that improves turbocharging internal-combustion engines, reduce oil consumption rate and obviously improve the purpose of its low-load performance.This steaming turbine boosting internal combustion engine system is made up of steaming turbine pressurized machine, exhaust heat boiler, steam injection system, turbine exhaust bypath system, regulator control system and corresponding supplementary equipment, subsystem.Its main flow process is:
The working medium air enters cylinder of internal-combustion engine 2 through gas compressor 1 supercharging, and compression and combustion work done final vacuum enters turbine 3.Water enters exhaust heat boiler 4 as second kind of working medium, absorbs heat and become superheated vapor in exhaust heat boiler 4 from the turbine exhaust waste heat, be injected into turbine by special steam injection system before.The mixed working fluid expansion working drive pressure mechanism of qi of being made up of two kinds of working medium (combustion gas, steam) in turbine 3 is after exhaust heat boiler 4 enters atmosphere.The steam flow of re-injection can satisfy the needs of turbocharging internal-combustion engines by throttle valve 5 controls.Superfluous water steam can be drawn by bypath system 6 and uses it for anything else or discharge.
2. steaming turbine boosting internal combustion engine according to claim 1 system is characterized in that can adopting the simplified system of system as mentioned above under this specific occasions when on-the-spot existing existing suitable steam source.Its main flow process is:
The working medium air enters cylinder of internal-combustion engine 2 through gas compressor 1 supercharging, and compression and combustion work done final vacuum enters turbine 3.On-the-spot existing steam is through decompression or reducing-and-cooling plant 10 and modulating valve 5 injection turbines 3.By mixed working fluid expansion working in turbine 3 of combustion gas, vapour composition, the drive pressure mechanism of qi enters atmosphere at last.
3. steaming turbine boosting internal combustion engine according to claim 1 system is characterized in that must adopting in the system turbosupercharger of steam injection.In steaming turbine supercharging circulation, increased a new inependent mode: the ratio of steam mass flow and combustion gas quality flow, i.e. vapour/gas ratio.The variation of vapour/gas ratio is bigger to the properties influence of turbosupercharger, should take all factors into consideration following factor and make optimal selection:
(1) internal-combustion engine is to the requirement of pressurized machine pressure ratio, flow;
(2) surge margin of gas compressor;
(3) rev limit of turbosupercharger;
(4) through-current capability of turbine;
(5) compactedness of exhaust heat boiler (size, weight);
(6) take into account full re-injection and zero re-injection.
The nozzle ring area should be made corresponding adjustment according to vapour/gas ratio of determining, guarantee maximum vapour/gas than under through-current capability, the turbine air inlet and exhaust piper should consider that also the influence of vapour/gas ratio examines the school.
4. steaming turbine boosting internal combustion engine according to claim 1 system is characterized in that being provided with in the system exhaust heat boiler and re-injection system, the also optional in case of necessity turbine exhaust bypath system of establishing.
The working medium of exhaust heat boiler is combustion and steam mixture/water or combustion gas/water.Exhaust heat boiler structure height compactness, little inertia, permission " dry combustion method " can be made dry-running.
Re-injection system is formed by annotating steam flow adjustable valve (or throttle valve), quick-closing valve, notes vapour nozzle, purge system and steam by-pass system etc.
5. steaming turbine boosting internal combustion engine according to claim 1 system is characterized in that the regulative mode that it is unique.Vapour regulating system and turbine exhaust bypass regulating system are annotated in integrated use, can obtain a characteristic of approaching mutually with the desired turbosupercharger characteristic of moving law.
6. steaming turbine boosting internal combustion engine according to claim 1 system is characterized in that this boosting system for steaming turbine can be applied in existing various types of turbo charge system.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB011015608A CN1258642C (en) | 2001-01-02 | 2001-01-02 | Boosting system for steaming turbine of IC engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB011015608A CN1258642C (en) | 2001-01-02 | 2001-01-02 | Boosting system for steaming turbine of IC engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1363764A true CN1363764A (en) | 2002-08-14 |
| CN1258642C CN1258642C (en) | 2006-06-07 |
Family
ID=4652133
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB011015608A Expired - Fee Related CN1258642C (en) | 2001-01-02 | 2001-01-02 | Boosting system for steaming turbine of IC engine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1258642C (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102183003A (en) * | 2011-03-16 | 2011-09-14 | 哈尔滨工程大学 | Bypass afterburning composite regenerative turbo supercharging system of boiler |
| CN101595288B (en) * | 2006-12-07 | 2011-12-14 | Abb研究有限公司 | Method and system for monitoring process states of an internal combustion engine |
| CN102472157A (en) * | 2009-08-12 | 2012-05-23 | 罗伯特·博世有限公司 | Device for assisting a supercharging device |
| CN102483014A (en) * | 2009-07-21 | 2012-05-30 | 雷诺卡车公司 | Engine arrangement with an improved exhaust heat recovery arrangement |
| CN102900511A (en) * | 2012-09-19 | 2013-01-30 | 上海交通大学 | Exhaust energy recovery system capable of self-adapting to working conditions |
| CN103104369A (en) * | 2012-01-27 | 2013-05-15 | 摩尔动力(北京)技术股份有限公司 | Turbine distribution thermomotor |
| CN103397953A (en) * | 2012-07-03 | 2013-11-20 | 摩尔动力(北京)技术股份有限公司 | Atmospheric distribution entropy cycle engine |
| CN105190175A (en) * | 2013-03-26 | 2015-12-23 | 月岛机械株式会社 | Pressurized fluidized furnace equipment |
| CN106014681A (en) * | 2016-07-08 | 2016-10-12 | 蓝龙飞 | Afterheat gradient utilization system of power generation internal combustion engine |
| CN111425316A (en) * | 2020-03-31 | 2020-07-17 | 中国科学院工程热物理研究所 | Distributed combined cooling heating and power system based on internal combustion engine and regulation and control method thereof |
-
2001
- 2001-01-02 CN CNB011015608A patent/CN1258642C/en not_active Expired - Fee Related
Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101595288B (en) * | 2006-12-07 | 2011-12-14 | Abb研究有限公司 | Method and system for monitoring process states of an internal combustion engine |
| US8689554B2 (en) | 2009-07-21 | 2014-04-08 | Renault Trucks | Engine arrangement with an improved exhaust heat recovery arrangement |
| CN102483014A (en) * | 2009-07-21 | 2012-05-30 | 雷诺卡车公司 | Engine arrangement with an improved exhaust heat recovery arrangement |
| CN102472157A (en) * | 2009-08-12 | 2012-05-23 | 罗伯特·博世有限公司 | Device for assisting a supercharging device |
| CN102183003A (en) * | 2011-03-16 | 2011-09-14 | 哈尔滨工程大学 | Bypass afterburning composite regenerative turbo supercharging system of boiler |
| CN103104369B (en) * | 2012-01-27 | 2015-07-29 | 摩尔动力(北京)技术股份有限公司 | A kind of turbine distribution thermomotor |
| CN103104369A (en) * | 2012-01-27 | 2013-05-15 | 摩尔动力(北京)技术股份有限公司 | Turbine distribution thermomotor |
| CN103397953A (en) * | 2012-07-03 | 2013-11-20 | 摩尔动力(北京)技术股份有限公司 | Atmospheric distribution entropy cycle engine |
| CN102900511A (en) * | 2012-09-19 | 2013-01-30 | 上海交通大学 | Exhaust energy recovery system capable of self-adapting to working conditions |
| CN105190175A (en) * | 2013-03-26 | 2015-12-23 | 月岛机械株式会社 | Pressurized fluidized furnace equipment |
| CN105190175B (en) * | 2013-03-26 | 2017-03-22 | 月岛机械株式会社 | Pressurized fluidized furnace equipment |
| US9933156B2 (en) | 2013-03-26 | 2018-04-03 | Tsukishima Kikai Co., Ltd. | Pressurized fluidized furnace equipment |
| CN106014681A (en) * | 2016-07-08 | 2016-10-12 | 蓝龙飞 | Afterheat gradient utilization system of power generation internal combustion engine |
| CN111425316A (en) * | 2020-03-31 | 2020-07-17 | 中国科学院工程热物理研究所 | Distributed combined cooling heating and power system based on internal combustion engine and regulation and control method thereof |
| CN111425316B (en) * | 2020-03-31 | 2021-03-05 | 中国科学院工程热物理研究所 | Distributed combined cooling heating and power system based on internal combustion engine and regulation and control method thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1258642C (en) | 2006-06-07 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN100376774C (en) | Turbo charge diesel-type piston engine and method for controlling such an engine | |
| EP2347108B1 (en) | An exhaust arrangement for an internal combustion engine | |
| US6543230B1 (en) | Method for adjusting a boosted internal combustion engine with exhaust gas recirculation | |
| US20070180824A1 (en) | Control of supercharged engine with variable geometry turbocharger and electric supercharger | |
| US20060101819A1 (en) | Method and system for influencing the quantity of exhaust gas recirculated in a pressure charged internal combustion engine | |
| WO2006052993A2 (en) | Secondary engine providing exhaust-gas to egr system | |
| CA2445184C (en) | Methods and apparatus for controlling peak firing pressure for turbo-charged diesel engines | |
| CN102278193A (en) | Auxiliary pressurization system of internal combustion engine | |
| CN1258642C (en) | Boosting system for steaming turbine of IC engine | |
| Heim | Existing and future demands on the turbocharging of modern large two-stroke diesel engines | |
| CN111188704B (en) | Gasoline homogeneous charge compression ignition engine system and method capable of achieving high heat efficiency and low emission | |
| CN1820136A (en) | Internal combustion engine | |
| JPS5857069A (en) | Fuel injection device | |
| EP1625295A1 (en) | Turbo charge diesel-type piston engine and method for controlling such an engine | |
| EP1788225B1 (en) | System and method for controlling the charging air flow of an internal combustion engine | |
| US8408189B2 (en) | Petrol engine having a low-pressure EGR circuit | |
| CN2149482Y (en) | Turbine pressure-increase diesel engine | |
| US3487634A (en) | Constant horsepower internal combustion engines | |
| CN215170349U (en) | Shunting exhaust system of supercharged five-stroke engine | |
| Fort et al. | Evaluation of positive-displacement supercharging and waste heat recovery for an LHR diesel | |
| JPH0579334A (en) | Supercharge engine | |
| Bradbury et al. | Turbocharging a crank-case scavenged and direct-injected two-stroke engine for snowmobile applications | |
| Wang et al. | Effect of High and Low Pressure EGR on Diesel Engine Matched with Mechanical Turbo-compound | |
| CN118052073A (en) | Design method of high-pressure-ratio low-heat-dissipation air-cooled engine with post-injection strategy | |
| CN114704364A (en) | Emission control system and method |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20060607 Termination date: 20170102 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |