Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
  • F04B35/002—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for driven by internal combustion engines
• • 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
  • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
• • 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
  • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
  • F02B37/005—Exhaust driven pumps being combined with an exhaust driven auxiliary apparatus, e.g. a ventilator
• • 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
  • F02B63/00—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices
  • F02B63/06—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices for pumps
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B25/00—Multi-stage pumps
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B41/00—Pumping installations or systems specially adapted for elastic fluids
  • F04B41/06—Combinations of two or more pumps
• • 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
• • 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

Definitions

• Compressor system for the production of compressed air
• the invention relates to a compressor system for generating compressed air consisting of a compressor driven by a Breruikraft ⁇ iaschine, which is connected via a line to compressed air extraction points and to which an exhaust gas turbocharger connected on the drive side to the exhaust gas side of the internal combustion engine supplies pre-compressed air.
• Such a compressor system is intended to improve the efficiency of the system by using the resulting process heat and thus to save energy.
• a compressor system is known in which at least one exhaust gas turbocharger is arranged in the suction and / or pressure line of a compressor on the drive side on the exhaust side of an internal combustion engine and supplies the compressor with compressed air and / or compresses the compressor Compressed air.
• the disadvantage here is that the arrangement of one or more exhaust gas turbochargers in the exhaust line of an internal combustion engine increases its exhaust gas back pressure and thus reduces its mechanical useful output.
• the exhaust gas back pressure rises to approximately 1.5 bar and brings about a reduction in the mechanical useful power due to the higher pushing-out work of the pistons of the internal combustion engine of approximately 20% in conventional internal combustion engines with a low mean effective pressure.
• the exhaust gas back pressure causes the internal combustion engine to be poorly filled with fresh air, which is why the amount of fuel must be reduced in order to achieve complete combustion of the fuel and the performance of the internal combustion engine drops.
• the power loss caused by this is about 10% in conventional naturally aspirated engines.
• a compressor system is known from US Pat. No. 2,849,173, in which a gas turbine is driven by the exhaust gases of a heat engine driving a piston compressor and supplies the piston compressor with pre-compressed air via a compressor driven by the gas turbine.
• a multi-stage axial compressor is disclosed here as an upstream compressor.
• it is disadvantageous that such a compressor system represents an expensive and bulky solution due to the multi-stage axial compressor used and is unsuitable for use as a mobile compressor system.
• there are large power losses of the internal combustion engine due to the high exhaust gas back pressure, which is caused by the gas turbine compressor stage connected downstream.
• An improvement in the efficiency of a compressor system by connecting a pre-compressor stage driven by the exhaust gases is therefore not achieved with this technical teaching.
• the disadvantage here is that the motor and compressor run at the same speed, so that no variation in the pressure and the delivery quantity is possible.
• the motor-compressor unit is therefore not suitable for use as a mobile compressor unit, but is designed for motor operation, since the compressor side is not optimal.
• the aim of the invention is to improve the overall efficiency in a compressor system with an exhaust gas turbocharger connected upstream of the compressor and thus to enable such a compressor system to be used economically.
• An improvement in the overall efficiency is accordingly achieved in that two exhaust gas turbochargers are arranged one behind the other in such a way that the exhaust gas mass flow of a diesel engine first drives the first exhaust gas turbocharger, which supplies compressed air to this diesel engine and then drives the second exhaust gas turbocharger, which supplies the compressor with compressed air.
• the turbine-side impeller geometry of the exhaust gas turbocharger upstream of the displacement compressor for example the diameter of the impeller
• the turbine-side impeller geometry of the exhaust gas turbocharger upstream of the diesel engine for example the outside diameter of the exhaust gas counterpressure, at the impeller pressure and the temperature resulting from the downstream exhaust gas turbocharger of the positive-displacement compressor is adjusted.
• the loss in mechanical useful power is reduced to approximately 15%.
• a loss of performance due to poor filling of the diesel engine with fresh air can be avoided by a higher boost pressure.
• the total power loss of the diesel engine caused by the exhaust gas back pressure is reduced to about 15%.
• the compressor output obtained in the exhaust gas turbocharger upstream of the positive-displacement compressor corresponds to approximately 25% of the mechanical useful output of the engine. This results in a performance gain of 15% for the compressor system according to the invention.
• the compressor system according to the invention with a diesel engine with an exhaust gas turbocharger is advantageous since the usable speed range of the diesel engine is larger here.
• the change in the speed of the diesel engine is of great importance, since the compressed air is extracted from the compressor system fluctuating and the engine speed is increased or decreased depending on the compressed air.
• the usable speed range is, for example, between 2500 revolutions per minute and 1500 revolutions per minute.
• the torque requirement consists of two parts, that of the screw compressor and that of the additional turbocharger.
• the exhaust gas turbocharger output and thus the exhaust gas back pressure also decrease.
• the decreasing exhaust gas counter-current now causes an increase in the mechanically usable engine torque of the diesel engine, so that even in this operating state there is sufficient engine torque to provide the desired final pressure by the compressor. It is thus possible to increase the speed range of the diesel engine towards low speeds, so that a speed range between 2500 revolutions per minute and 1000 revolutions per minute can be used. This corresponds to an increase in the usable speed range by about 50%.
• the usability of lower speeds results in O 01/44635
• Diesel engine has a fuel saving potential of up to 30% compared to conventional compressor systems.
• Another advantage of the compressor system according to the invention is the use of a positive-displacement compressor.
• a positive-displacement compressor In the case of compressor systems driven by internal combustion engines, it is common to regulate the quantity of compressed air supplied also via the engine speed.
• a reduction in engine speed and a resulting loss of admission pressure also results in a reduction in the compressor output of the exhaust gas turbocharger in front of the compressor.
• the resulting lower admission pressure requires the compressor to generate a higher pressure ratio in order to achieve a desired constant final pressure.
• the compressor system according to the invention solves this problem by using a displacement compressor which, even with changing pressure conditions upstream of the compressor, is still able to provide a constant final pressure, since there is practically no damage space.
• a liquid-injected displacement compressor for example a screw or rotary compressor, is to be used.
• Another advantage of using a liquid-injected displacement compressor is that it already provides the required compression in a single-stage design, which means that the entire compressor system is kept structurally small.
• Combustion air is cleaned via an air filter 10 and fed to an exhaust gas turbocharger 20 through an intake line 70.
• a line 72 feeds the now compressed air to an intercooler 90 and a line 74 to the intercooled combustion air to a diesel engine 40.
• a line 41 conducts the exhaust gas of the diesel engine 40 to the exhaust gas turbocharger 20.
• a connection 42 that is as short as possible leads the partially relaxed exhaust gas to a second exhaust gas turbocharger 21. After passing through the exhaust gas turbocharger 21, the relaxed exhaust gas is discharged. The air to be compressed is supplied to the exhaust gas turbocharger 21 via an air filter 11 and an intake line 71.
• a line 75 supplies the now compressed air to an intercooler 91 and a line 75 supplies the pre-compressed air to a liquid-injected displacement compressor 50.
• a pressure line 76 supplies the compressed air with the injection liquid to the pressure vessel 80, where a liquid separator 81 separates the injection liquid from the compressed air.
• the injection liquid is returned to the liquid-injected displacement compressor via a line 77, a filter 60, a line 78, a cooler 61 and a line 79.
• the compressed air is fed from the pressure vessel 80 via the liquid separator 81, a pressure holding check valve 82 and a line 83 to the compressed air extraction points 84.

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Supercharger (AREA)
• Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
• Applications Or Details Of Rotary Compressors (AREA)
• Structures Of Non-Positive Displacement Pumps (AREA)

Applications Claiming Priority (3)

Publications (1)

Family

ID=7932545

Family Applications (1)

Country Status (7)

Families Citing this family (7)

Family Cites Families (18)

• 1999
  • 1999-12-14 DE DE19960152A patent/DE19960152C2/de not_active Expired - Lifetime
• 2000
  • 2000-12-08 CN CNB008037620A patent/CN1175173C/zh not_active Expired - Lifetime
  • 2000-12-08 EP EP00993426A patent/EP1153210A1/de not_active Ceased
  • 2000-12-08 AU AU28296/01A patent/AU2829601A/en not_active Abandoned
  • 2000-12-08 JP JP2001545701A patent/JP2003517133A/ja active Pending
  • 2000-12-08 US US09/890,930 patent/US6726457B2/en not_active Expired - Lifetime
  • 2000-12-08 WO PCT/DE2000/004388 patent/WO2001044635A1/de not_active Application Discontinuation

Non-Patent Citations (1)

Also Published As

Similar Documents

Legal Events