CN204552954U - The two-stage adjustable pressurization system of internal-combustion engine - Google Patents
The two-stage adjustable pressurization system of internal-combustion engine Download PDFInfo
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- CN204552954U CN204552954U CN201420859973.6U CN201420859973U CN204552954U CN 204552954 U CN204552954 U CN 204552954U CN 201420859973 U CN201420859973 U CN 201420859973U CN 204552954 U CN204552954 U CN 204552954U
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Abstract
The utility model provides a kind of two-stage adjustable pressurization system of internal-combustion engine, and it includes two groups of cylinder of internal-combustion engine groups; Cylinder of internal-combustion engine group is provided with high pressure stage turbine and lower pressure stage turbine in discharge directions; Cylinder of internal-combustion engine group is provided with low pressure stage gas compressor, intercooler and high pressure stage gas compressor on airintake direction; High pressure stage turbine is total to transmission shaft with the high pressure stage gas compressor organized, lower pressure stage turbine and the same low pressure stage gas compressor organized transmission shaft altogether; The side of one intake and exhaust bypass valve is communicated with the outlet of high pressure stage gas compressor, and opposite side is communicated with the suction port of high pressure stage turbine.The outlet of two groups of high pressure stage gas compressors and the suction port of high pressure stage turbine is communicated with by arranging an only intake and exhaust bypass valve, suction port and air outlet that a high pressure stage turbine bypass valve is communicated with two groups of high pressure stage turbines are set further, make only to use less bypass valve just can regulate to be applicable to various different operating mode to whole system.
Description
Technical field
The utility model relates to the pressurization system of internal-combustion engine, particularly a kind of two-stage adjustable pressurization system of internal-combustion engine.
Background technique
Along with the enforcement of following boats and ships Abgasgesetz with to the internal-combustion engine high power densities such as diesel engine, high efficiency pursuit, the two-step supercharging technology with more high pressure ratio is the trend of the internal combustion engine developments such as marine diesel engine.But the internal-combustion engine overwhelming majority such as current marine diesel engine are single stage superchargings.Mostly existing two-step supercharging technology is the pattern of employing high pressure stage pressurized machine and a low pressure stage pressurized machine series connection, the disclosed a kind of internal-combustion engine of such as Chinese patent (publication number CN 1834421A), its at least two-stage exhaust-gas turbocharger that there is motor and be made up of high pressure supercharging device and low-pressure supercharging device, the charger-air cooler that its mesohigh supercharging device has high-pressure turbine stage, high pressure compressor and is connected between high pressure compressor and motor.But its boost pressure is unadjustable, and pressurization system can not be made in the full working scope that diesel engine runs to keep high efficiency.
The two-step supercharging system with boost pressure regulating power is also employed, but these systems all exist certain problem.Such as international monopoly (WO 2010/097979 A1) adopts 4 bypath valves such as 5 bypass such as low pressure stage gas compressor bypass valve, the venting of high pressure stage turbo valve or venting valve regulated boost pressure, Chinese patent CN 103615309A employing high pressure stage turbine bypass valve, lower pressure stage turbine bypass valve to regulate boost pressures.But for Marine V Type diesel engine, because it has the special construction of two row cylinders, two row suction tude and two row outlet pipes, the supercharging pressure control valve door of these systems is many, system architecture can be caused complicated and be difficult to problems such as arranging, overall dimension is huge, pipeline linear loss is large, controlling method is complicated, manufacture cost is high.
Model utility content
The technical problem to be solved in the present invention is to overcome the low defect of operational efficiency under prior art pressurization system of internal combustion engine Part load, and providing under a kind of full working scope condition all can the two-stage adjustable pressurization system of internal-combustion engine of Effec-tive Function.
The present invention solves above-mentioned technical problem by following technical proposals:
A two-stage adjustable pressurization system for internal-combustion engine, its feature is, it includes the cylinder of internal-combustion engine group that two groups have several cylinder of internal-combustion engine respectively;
Described cylinder of internal-combustion engine group in discharge directions be successively communicated be provided with a high pressure stage turbine and a lower pressure stage turbine;
Described cylinder of internal-combustion engine group on airintake direction be successively communicated be provided with a low pressure stage gas compressor, an intercooler and a high pressure stage gas compressor;
Described high pressure stage turbine is total to transmission shaft with the described high pressure stage gas compressor organized, described lower pressure stage turbine and the same described low pressure stage gas compressor organized transmission shaft altogether;
The side of one intake and exhaust bypass valve is communicated with the outlet of high pressure stage gas compressor described in two groups, and opposite side is communicated with the suction port of high pressure stage turbine described in two groups.
That is, in discharge directions, waste gas is discharged after high pressure stage turbine, lower pressure stage turbine, and energizes high-pressure level turbine and lower pressure stage turbine rotate, and then kinetic energy is passed to high pressure stage gas compressor and low pressure stage gas compressor with the charge-air pressure both increasing by common transmission shaft.
In addition, the air inlet of two groups of cylinder of internal-combustion engine groups, exhaust lay out share an intake and exhaust bypass valve.By this structure, can by regulating the aperture of intake and exhaust bypass valve, (pressure of air inlet circuit is greater than the pressure of exhausting waste gas circuit to utilize the pressure reduction between high pressure stage blower outlet and high pressure stage turbine inlet, therefore after opening intake and exhaust bypass valve, air can enter exhaust lay out from inlet line), make partial air not enter intercooler and enter high pressure stage turbine, improving turbine output rate, reaching the object improving boost pressure.
Preferably, a high pressure stage turbine bypass valve side is communicated with the suction port of high pressure stage turbine described in two groups, and the other end is communicated with the air outlet of high pressure stage turbine described in two groups.
That is, the air inlet of two groups of cylinder of internal-combustion engine groups, exhaust lay out share a high pressure stage turbine bypass valve.By this structure, can by regulating the aperture of high pressure stage turbine bypass valve, utilize the pressure difference between high pressure stage turbine inlet and lower pressure stage turbine import, part I. C. engine exhaust is made directly to enter lower pressure stage turbine without high pressure stage turbine, reduce two-stage turbine total output, reach the object reducing boost pressure.
Preferably, described in two groups, intercooler shares the cooling waterpump of a regulating flow quantity.
Preferably, the suction port of cylinder of internal-combustion engine group described in two groups shares a cylinder of internal-combustion engine inlet gas cooling device.By this structure, two row pressurized airs can be made to share an intercooler, effectively utilize arrangement space, decrease internal combustion engine part quantity and size, Structure of Internal-Combustion Engine can be made compacter.
Preferably, the suction port of described intercooler and air outlet are respectively arranged with an air-inlet cavity and an outlet chamber, at least one guide plate is respectively arranged with in described air-inlet cavity and described outlet chamber, one end of described guide plate and the air inlet of described intercooler or the airflow direction of giving vent to anger parallel, the other end is bent to suction port perpendicular to described intercooler or air outlet.
Herein, the effect arranging guide plate is that the air draught distribution making to enter intercooler is more even, can reduce the cooling effect of flow-disturbing loss and then raising intercooler like this.
Preferably, the joint of described intercooler, described high pressure stage gas compressor, described low pressure stage gas compressor, described high pressure stage turbine and described lower pressure stage turbine and pipeline is provided with described guide plate.
Positive progressive effect of the present invention is: be communicated with the outlet of two groups of high pressure stage gas compressors and the suction port of high pressure stage turbine by arranging an only intake and exhaust bypass valve, suction port and air outlet that a high pressure stage turbine bypass valve is communicated with two groups of high pressure stage turbines are set further, make only to use less bypass valve just can regulate to be applicable to the various different operating conditions of internal-combustion engine to whole system.
Accompanying drawing explanation
Fig. 1 is the structural representation of the two-stage adjustable pressurization system of the internal-combustion engine of present pre-ferred embodiments.
Fig. 2 is the stereogram of the low pressure stage gas compressor of present pre-ferred embodiments and the linkage structure of intercooler.
Fig. 3 is the plan view of the air-inlet cavity of present pre-ferred embodiments.
Fig. 4 is the structural representation of the section of the air-inlet cavity of present pre-ferred embodiments.
Embodiment
Lift preferred embodiment below, and come by reference to the accompanying drawings clearlyer intactly the utility model to be described.
Fig. 1 is the structural representation of the two-stage adjustable pressurization system of the internal-combustion engine of the present embodiment, as shown in Figure 1, the two-stage adjustable pressurization system of the internal-combustion engine of the present embodiment is used for Marine V Type diesel engine, and it includes cylinder of diesel engine group and two-step supercharging module 2 that two groups have several cylinder of internal-combustion engine respectively.
The outlet pipe 1 of cylinder of diesel engine group is communicated with successively with outlet pipe 13 and is provided with high pressure stage turbine 4 and lower pressure stage turbine 8 in discharge directions.The suction tude 15 of two groups of cylinder of diesel engine groups is communicated with successively and is provided with low pressure stage gas compressor 6, intercooler 5 and high pressure stage gas compressor 3 on airintake direction.
High pressure stage turbine 4 is total to transmission shaft with the high pressure stage gas compressor 3 organized, lower pressure stage turbine 8 and the same low pressure stage gas compressor 6 organized transmission shaft altogether.
The side of intake and exhaust bypass valve 12 is communicated with the outlet of two groups of high pressure stage gas compressors 3, and opposite side is communicated with the suction port of two groups of high pressure stage turbines 4.High pressure stage turbine bypass valve 10 side is communicated with the suction port (being namely communicated with the suction port of high pressure stage turbine 4 by the bypass line 11 shown in Fig. 1) of two groups of high pressure stage turbines 4, and the other end is communicated with the air outlet (between the turbine namely between connected graph 1 mesohigh level turbine 4 and lower pressure stage turbine 8 outlet pipe 7) of two groups of high pressure stage turbines 4.
Two groups of intercoolers 5 share the cooling waterpump 9 of regulating flow quantity.
The suction port of two groups of cylinder of diesel engine groups shares a cylinder of internal-combustion engine inlet gas cooling device 4.
Fig. 2 is the stereogram of the low pressure stage gas compressor of the present embodiment and the linkage structure of intercooler, Fig. 3 is the plan view of the air-inlet cavity of the present embodiment, Fig. 4 is the structural representation of the section of the air-inlet cavity of the present embodiment, as shown in figs. 2 to 4, the suction port of intercooler 5 and air outlet are respectively arranged with air-inlet cavity 21 and outlet chamber 22.The air-inlet cavity 21 of intercooler 5 is by the outlet of intake elbow 24 with low pressure stage gas compressor 6.Be respectively arranged with guide plate 23 in air-inlet cavity 21 and outlet chamber 22, one end of guide plate 23 and the air inlet of intercooler 5 or the airflow direction of giving vent to anger parallel, the other end is bent to suction port perpendicular to intercooler 5 or air outlet.It is two deciles that corresponding interface is split at the two ends of guide plate 23 respectively.In addition, high pressure stage gas compressor 3, low pressure stage gas compressor 6, high pressure stage turbine 4 and lower pressure stage turbine 8 is provided with guide plate with the joint of pipeline.
The cooling water inflow of intercooler 5 and cylinder of internal-combustion engine inlet gas cooling device 4 is adjustable, different cooling water flows is provided by the cooling waterpump 9 of adjustable flow, the running state that can control the gas temperature after interstage cooler and system matches, after preferred interstage cooler, gas temperature is 40-50 DEG C, gas temperature after different interstage cooler can be provided under the different operating mode of diesel engine, optimization system overall performance, improves system total efficiency.
On the one hand, by regulating the aperture of high pressure stage turbine bypass valve, utilize the pressure difference between the import of high pressure stage turbine and the import of lower pressure stage turbine, part diesel exhaust gas is made directly to enter lower pressure stage turbine without high-pressure turbine, reduce two-stage turbine total output, reach the object reducing boost pressure.On the other hand, two tubulation roads share an intake and exhaust bypass valve, can by regulating the aperture of intake and exhaust bypass valve, utilize the pressure reduction between high pressure stage blower outlet and high pressure stage turbine inlet, make partial air not enter intercooler and enter high pressure stage turbine, improve turbine power, reach the object improving boost pressure.
For the structural type of Marine V Type diesel engine, a low pressure stage pressurized machine and a high pressure stage pressurized machine is equipped respectively for often organizing cylinder, respectively interstage cooler is configured with, in order to reduce the air temperature entering high pressure stage gas compressor between two low pressure stage gas compressors and high pressure stage gas compressor.Interstage cooler is placed in below low pressure stage pressurized machine, by this structure, can save installing space, controls diesel engine size.Two row high pressure stage blower outlet pipelines pass through particular design, two row pressurized airs are made to enter cylinder of internal-combustion engine inlet gas cooling device 4 (it can use same cooling unit with intercooler 5) by an intake manifold, this intake manifold is positioned in the v-angle of diesel engine, and cylinder of internal-combustion engine inlet gas cooling device is positioned at one end of diesel engine.By this structure, two row pressurized airs can be made to share a cylinder of internal-combustion engine inlet gas cooling device, effectively utilize arrangement space, decrease diesel engine part quantity and size, engine block can be made compacter.
Although the foregoing describe the specific embodiment of the present invention, it will be understood by those of skill in the art that this only illustrates, protection scope of the present invention is defined by the appended claims.Those skilled in the art, under the prerequisite not deviating from principle of the present invention and essence, can make various changes or modifications to these mode of executions, and these change and amendment all falls into protection scope of the present invention.
Claims (6)
1. a two-stage adjustable pressurization system for internal-combustion engine, is characterized in that, it includes the cylinder of internal-combustion engine group that two groups have several cylinder of internal-combustion engine respectively;
Described cylinder of internal-combustion engine group in discharge directions be successively communicated be provided with a high pressure stage turbine and a lower pressure stage turbine;
Described cylinder of internal-combustion engine group on airintake direction be successively communicated be provided with a low pressure stage gas compressor, an intercooler and a high pressure stage gas compressor;
Described high pressure stage turbine is total to transmission shaft with the described high pressure stage gas compressor organized, described lower pressure stage turbine and the same described low pressure stage gas compressor organized transmission shaft altogether;
The side of one intake and exhaust bypass valve is communicated with the outlet of high pressure stage gas compressor described in two groups, and opposite side is communicated with the suction port of high pressure stage turbine described in two groups.
2. the two-stage adjustable pressurization system of internal-combustion engine as claimed in claim 1, it is characterized in that, a high pressure stage turbine bypass valve side is communicated with the suction port of high pressure stage turbine described in two groups, and the other end is communicated with the air outlet of high pressure stage turbine described in two groups.
3. the two-stage adjustable pressurization system of internal-combustion engine as claimed in claim 1, it is characterized in that, described in two groups, intercooler shares the cooling waterpump of a regulating flow quantity.
4. the two-stage adjustable pressurization system of internal-combustion engine as claimed in claim 1, is characterized in that, the suction port of cylinder of internal-combustion engine group described in two groups shares a cylinder of internal-combustion engine inlet gas cooling device.
5. the two-stage adjustable pressurization system of internal-combustion engine as claimed in claim 1, it is characterized in that, the suction port of described intercooler and air outlet are respectively arranged with an air-inlet cavity and an outlet chamber, at least one guide plate is respectively arranged with in described air-inlet cavity and described outlet chamber, one end of described guide plate and the air inlet of described intercooler or the airflow direction of giving vent to anger parallel, the other end is bent to suction port perpendicular to described intercooler or air outlet.
6. the two-stage adjustable pressurization system of internal-combustion engine as claimed in claim 5, it is characterized in that, the joint of described intercooler, described high pressure stage gas compressor, described low pressure stage gas compressor, described high pressure stage turbine and described lower pressure stage turbine and pipeline is provided with described guide plate.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420859973.6U CN204552954U (en) | 2014-12-29 | 2014-12-29 | The two-stage adjustable pressurization system of internal-combustion engine |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201420859973.6U CN204552954U (en) | 2014-12-29 | 2014-12-29 | The two-stage adjustable pressurization system of internal-combustion engine |
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| CN201420859973.6U Expired - Fee Related CN204552954U (en) | 2014-12-29 | 2014-12-29 | The two-stage adjustable pressurization system of internal-combustion engine |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104533599A (en) * | 2014-12-29 | 2015-04-22 | 中国船舶重工集团公司第七一一研究所 | Two-stage adjustable pressurization system of internal combustion engine |
| CN107939509A (en) * | 2017-11-20 | 2018-04-20 | 潍柴动力股份有限公司 | The two-step supercharging cascade EDFA control system and control method of a kind of engine |
-
2014
- 2014-12-29 CN CN201420859973.6U patent/CN204552954U/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104533599A (en) * | 2014-12-29 | 2015-04-22 | 中国船舶重工集团公司第七一一研究所 | Two-stage adjustable pressurization system of internal combustion engine |
| CN104533599B (en) * | 2014-12-29 | 2017-06-20 | 中国船舶重工集团公司第七一一研究所 | The two-stage adjustable pressurization system of internal combustion engine |
| CN107939509A (en) * | 2017-11-20 | 2018-04-20 | 潍柴动力股份有限公司 | The two-step supercharging cascade EDFA control system and control method of a kind of engine |
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| 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: 20150812 Termination date: 20201229 |
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| CF01 | Termination of patent right due to non-payment of annual fee |