WO2015128936A1 - 多段電動遠心圧縮機及び内燃機関の過給システム - Google Patents
多段電動遠心圧縮機及び内燃機関の過給システム Download PDFInfo
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- WO2015128936A1 WO2015128936A1 PCT/JP2014/054506 JP2014054506W WO2015128936A1 WO 2015128936 A1 WO2015128936 A1 WO 2015128936A1 JP 2014054506 W JP2014054506 W JP 2014054506W WO 2015128936 A1 WO2015128936 A1 WO 2015128936A1
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- compressor
- pressure
- pressure stage
- centrifugal compressor
- impeller
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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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the 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
- F02B33/00—Engines characterised by provision of pumps for charging or scavenging
- F02B33/32—Engines with pumps other than of reciprocating-piston type
- F02B33/34—Engines with pumps other than of reciprocating-piston type with rotary pumps
- F02B33/40—Engines with pumps other than of reciprocating-piston type with rotary pumps of non-positive-displacement type
-
- 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
- F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
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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
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/02—Drives of pumps; Varying pump drive gear ratio
- F02B39/08—Non-mechanical drives, e.g. fluid drives having variable gear ratio
- F02B39/10—Non-mechanical drives, e.g. fluid drives having variable gear ratio electric
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/0002—Controlling intake air
- F02D41/0007—Controlling intake air for control of turbo-charged or super-charged engines
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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
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/08—Centrifugal pumps
- F04D17/10—Centrifugal pumps for compressing or evacuating
- F04D17/12—Multi-stage 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
- F04D25/00—Pumping installations or systems
- F04D25/02—Units comprising pumps and their driving means
- F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
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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
- F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
- F04D27/004—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids by varying driving speed
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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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
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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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B2037/122—Control of rotational speed of the pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2200/00—Input parameters for engine control
- F02D2200/02—Input parameters for engine control the parameters being related to the engine
- F02D2200/04—Engine intake system parameters
- F02D2200/0406—Intake manifold pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2200/00—Input parameters for engine control
- F02D2200/60—Input parameters for engine control said parameters being related to the driver demands or status
- F02D2200/602—Pedal position
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/18—Circuit arrangements for generating control signals by measuring intake air flow
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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
- F05D2220/00—Application
- F05D2220/40—Application in turbochargers
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- 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
- the present disclosure relates to a multistage electric centrifugal compressor and a supercharging system for an internal combustion engine including the multistage electric centrifugal compressor.
- An engine which is an example of an internal combustion engine, has been downsized, and demands for low-speed torque up and improved response have been increasing. As a means for realizing these requirements, a motor-driven compressor has attracted attention.
- a system provided with a multistage electric centrifugal compressor using this electric compressor includes, for example, a low pressure stage turbo in an intake passage and an exhaust passage of an engine, and an electric compression is performed in an intake passage downstream of a low pressure stage compressor of the low pressure stage turbo.
- There is one configured to be equipped with a machine see Patent Document 1).
- the electric two-stage system is configured to perform two-stage supercharging such as supercharging by a low-pressure stage turbo at a first stage and supercharging by an electric compressor at a second stage.
- the low pressure stage turbo includes a low pressure stage turbine disposed in the exhaust passage and driven by the exhaust, and a low pressure stage compressor disposed in the intake passage and driven by the rotational torque of the low pressure stage turbine.
- the electric compressor is configured to include a high pressure stage compressor which is disposed in the intake passage downstream of the low pressure stage compressor and driven by the rotational torque of the electric motor.
- JP-A-2013-24059 (see FIG. 6) JP 2004-11440 A
- At least some embodiments of the present invention may facilitate control of the drive means of the rotating shaft and control of the pressure ratio when using a single-shaft, two-stage centrifugal compressor. It is an object of the present invention to provide a multistage electric centrifugal compressor and a supercharging system for an internal combustion engine.
- the multi-stage electric centrifugal compressor according to some embodiments of the present invention
- An impeller of a low pressure stage compressor is connected to one end side of a rotating shaft extending from both sides of an electric motor, an impeller of a high pressure stage compressor is connected to the other end side of the rotating shaft, and compressed by the low pressure stage compressor
- a multistage electric centrifugal compressor which recompresses the intake air by the high pressure stage compressor
- the low pressure compressor and the high pressure compressor have a pressure ratio of intake air compressed by rotation of an impeller of the low pressure compressor and pressure of intake air compressed by rotation of an impeller of the high pressure compressor. The ratio and the ratio are formed to be different from each other.
- the low pressure compressor and the high pressure compressor are operated by the pressure ratio of the intake air compressed by the rotation of the impeller of the low pressure compressor and the rotation of the impeller of the high pressure compressor. Since the pressure ratio of the compressed intake air is formed to be different from each other, when the impeller of the low-pressure compressor and the impeller of the high-pressure compressor rotate, the pressure ratio is set by the braking action. The difference between the inertia force of the larger compressor and the inertia force of the compressor having the smaller pressure ratio is considered to be the inertia force acting on the rotation axis, and the inertia force is reduced. Therefore, a multistage electric centrifugal compressor capable of easily performing rotation control of the electric motor can be realized.
- the low pressure compressor and the high pressure compressor are the pressure ratio of the intake air compressed by the rotation of the impeller of the low pressure compressor, the pressure ratio of the high pressure compressor Since the pressure ratio of the intake air compressed by the rotation is formed to be different from each other, utilizing the fact that the supercharging efficiency of the low pressure compressor and the high pressure compressor at different rotational speeds are different.
- the expansion ratio of the pressure ratio of each of the low pressure compressor and the high pressure compressor when changing the rotation speed from the above rotation speed can be made different, and the pressure ratio of the multistage electric centrifugal compressor changes gently It can be done. Therefore, it is possible to realize a multistage electric centrifugal compressor capable of easily performing arbitrary pressure ratio control.
- the diameter of the impeller of the low pressure stage compressor and the diameter of the impeller of the high pressure stage compressor are configured to have different sizes.
- the diameter of the impeller of the low-pressure stage compressor and the diameter of the impeller of the high-pressure stage compressor have different sizes, they are compressed by the low-pressure stage compressor.
- the pressure ratio of the intake air to the pressure ratio of the intake air compressed by the high-pressure stage compressor can be easily made different. For this reason, when the impeller of the low pressure stage compressor and the impeller of the high pressure stage compressor rotate, the inertial force acting on the rotation shaft can be further reduced. Therefore, a multistage electric centrifugal compressor capable of easily performing rotation control of the electric motor can be realized.
- the diameter of the impeller of the low pressure compressor and the diameter of the impeller of the high pressure compressor have different sizes, they are compressed by the low pressure compressor.
- the pressure ratio of the intake air to the pressure ratio of the intake air compressed by the high-pressure stage compressor can be easily made different. For this reason, it is possible to smooth the pressure ratio fluctuation of the multistage electric centrifugal compressor due to the increase and decrease of the rotational speed of the impeller of the low pressure stage compressor and the impeller of the high pressure stage compressor. Therefore, it is possible to realize a multistage electric centrifugal compressor capable of easily performing arbitrary pressure ratio control.
- the shape of the impeller of the low pressure stage compressor and the shape of the impeller of the high pressure stage compressor are configured to have different shapes.
- the shape of the impeller of the low-pressure stage compressor and the shape of the impeller of the high-pressure stage compressor have different shapes from each other, it is possible to adjust the range of the intake flow path flowing in the compressor is there. Therefore, the pressure ratio of the intake air compressed by the low-pressure stage compressor and the pressure ratio of the intake air compressed by the high-pressure stage compressor can be easily made different from each other. For this reason, when the impeller of the low pressure stage compressor and the impeller of the high pressure stage compressor rotate, the inertial force acting on the rotation shaft can be further reduced. Therefore, a multistage electric centrifugal compressor capable of easily performing rotation control of the electric motor can be realized.
- the diameter of the impeller of the low pressure compressor and the diameter of the impeller of the high pressure compressor have different sizes, they are compressed by the low pressure compressor.
- the pressure ratio of the intake air to the pressure ratio of the intake air compressed by the high-pressure stage compressor can be easily made different. For this reason, it is possible to smooth the pressure ratio fluctuation of the multistage electric centrifugal compressor due to the increase and decrease of the rotational speed of the impeller of the low pressure stage compressor and the impeller of the high pressure stage compressor. Therefore, it is possible to realize a multistage electric centrifugal compressor capable of easily performing arbitrary pressure ratio control.
- a map showing the relationship between the rotational speed of the electric motor and the discharge pressure or discharge flow rate of the multistage electric centrifugal compressor An upper controller for controlling the operation of the internal combustion engine compares the intake pressure or the intake flow rate required for the multistage centrifugal compressor with the map to derive the required number of revolutions of the electric motor, and is derived by the verification means And a controller configured to control the number of rotations of the electric motor so as to achieve the required number of rotations.
- the control means controls the rotational speed of the electric motor so as to obtain the required rotational speed derived by the collating means. Therefore, the intake pressure or intake flow rate required by the host controller or the intake pressure or intake flow rate of the multistage centrifugal compressor It can be the same as the intake flow rate. For this reason, in addition to the improvement of the response at low speed of the internal combustion engine and the assist function of the other turbochargers, the assist of the other turbochargers is required also during steady operation, the electric motor The rotation speed can be easily controlled.
- the supercharging system for an internal combustion engine according to some embodiments of the present invention
- the discharge side of the multistage electric centrifugal compressor according to claim 1 is connected to the intake side of another turbocharger.
- the discharge air of the multistage electric centrifugal compressor is introduced into the suction side of the centrifugal compressor of the turbocharger.
- the multistage electric centrifugal compressor can easily control the rotation of the electric motor, in addition to the improvement of the response at the low speed of the internal combustion engine and the assist function of other turbochargers,
- the electric motor can easily control the number of rotations of the rotating shaft when assist of another turbocharger is required even during steady operation. For this reason, it is possible to supply the internal combustion engine with supercharging of intake air according to the demand via another supercharger.
- the multistage electric centrifugal compressor supplies the intake air compressed by the low-pressure stage compressor to the high-pressure stage compressor and further compresses it, the turbocharger is provided with the compressor only at one end of the rotating shaft In comparison, an intake with a higher pressure ratio can be obtained. Therefore, it is possible to realize a supercharging system of an internal combustion engine capable of supercharging desired intake air even when the maximum rotation speed of the multistage electric centrifugal compressor is lowered.
- the other turbocharger is configured to be a turbocharger including an exhaust turbine that is rotated by exhaust gas of an internal combustion engine, and a centrifugal compressor that is rotated by the rotation of the exhaust turbine.
- the other turbocharger is a turbocharger provided with an exhaust turbine rotated by the exhaust gas of the internal combustion engine and a centrifugal compressor rotated by the rotation of the exhaust turbine. Since the intake air is compressed by the three-stage compressor, the intake air having a higher pressure can be supplied to the internal combustion engine as compared with the case where the intake air is compressed by the two-stage compressor. Therefore, even if the rotational speed of the multistage electric centrifugal compressor is lowered, the pressure of the intake air supercharged to the internal combustion engine can be made the desired pressure. Thus, it is possible to prevent the life of the multistage electric centrifugal compressor from being reduced.
- FIGS. 1 and 2 according to the attached drawings.
- the multistage electric centrifugal compressor will be described.
- the material of the component described in this embodiment, the shape, the relative arrangement, etc. are not the meaning which limits the scope of the present invention to this, but are only a mere illustration example.
- the multistage electric centrifugal compressor 1 is a low pressure stage provided with a rotary shaft 3 rotatably supported and a low pressure stage impeller 11 mounted on one end side of the rotary shaft 3
- the compressor 10 a high-pressure stage compressor 20 having a high-pressure stage impeller 21 attached to the other end side of the rotary shaft 3, and an electric motor rotor 30 mounted at a longitudinal intermediate portion of the rotary shaft 3 And be configured.
- an electric motor stator (not shown) disposed so as to surround the electric motor rotor 30 is provided around the electric motor rotor 30, and has an electric motor rotor 30 and an electric motor stator to provide an electric motor (not shown). Configured.
- the low pressure stage compressor 10 includes a low pressure stage impeller 11 attached to one end side of the rotary shaft 3 and a low pressure stage housing 16 surrounding the low pressure stage impeller 11.
- the low pressure stage housing 16 has a space 17 for rotatably accommodating the low pressure stage impeller 11 therein.
- a suction port 17a for taking in the intake air is opened at one end side of the central portion of the space portion 17, and a flow path 17c which is in communication with the suction port 17a in the radial direction of the space portion 17 and curves in the circumferential direction of the low pressure stage compressor 10. Is formed.
- a discharge port 17b communicating with the flow path 17c is opened at one end in the width direction of the low-pressure stage housing 16, that is, the front end of the paper surface of FIG. 1, a discharge port 17b communicating with the flow path 17c is opened.
- the intake air flowing in from the suction port 17a is heated by being compressed by the low-pressure stage impeller 11, flows through the flow path 17c, and is discharged from the discharge
- a circular insertion port 18 is opened in a side view where the low pressure stage impeller 11 can be inserted.
- the insertion opening 18 is opened larger than the low-pressure stage impeller 11 to expose a part of the flow path 17c.
- the side surface 16a on the insertion port 18 side of the low-pressure stage housing 16 is formed in a planar shape, and is formed in an annular shape in a side view.
- a back plate 35 attached to the side surface 16a of the low pressure stage housing 16 is provided so as to close the exposed flow path 17c.
- a motor housing 45 for holding the electric motor rotor 30 and the bearing 40R is attached to the back plate 35 on the high pressure stage compressor 20 side. The details of the motor housing 45 will be described later.
- the low-pressure stage impeller 11 includes a disc-shaped back plate 12 and a truncated cone-shaped boss 13 integrally provided on the back plate 12 so as to project perpendicularly from the surface on one side of the back plate 12; A plurality of wings 14 are provided so as to radially project from the outer peripheral surface of the boss portion 13 to the back plate 12.
- a through hole 13 a is provided at the central portion of the boss portion 13, and the rotary shaft 3 is inserted into the through hole 13 a, and the low-pressure stage impeller 11 is attached to the rotary shaft 3 via a nut 15.
- the diameter of the low pressure stage impeller 11 is smaller than the diameter of the high pressure stage impeller 21 of the high pressure stage compressor 20 described later.
- the pressure ratio of the low pressure stage compressor 10 is smaller than the pressure ratio of the high pressure stage compressor 20.
- the diameter of the high-pressure stage impeller 21 may be smaller than the diameter of the low-pressure stage impeller 11. In this case, the pressure ratio of the high pressure compressor 20 is smaller than the pressure ratio of the low pressure compressor 10.
- the high-pressure stage compressor 20 is configured in the same manner as the low-pressure stage compressor 10, and includes a high-pressure stage impeller 21 attached to the other end of the rotating shaft 3 and a high-pressure stage housing 26 surrounding the high-pressure stage impeller 21. It has.
- the high pressure stage housing 26 has a space portion 27 that rotatably accommodates the high pressure stage impeller 21 therein. At the other end of the space portion 27, a suction port 27a for sucking the intake air is opened, and in the radial direction of the space portion 27, a flow path 27c which communicates with the suction port 27a and curves in the circumferential direction of the high pressure stage compressor 20 is formed. It is done.
- the intake air flowing in from the suction port 27a is compressed by the high-pressure stage impeller 21, and is heated, flows through the flow path 27c, and is discharged from the discharge port 27b.
- the suction port 27 a of the high pressure stage housing 26 is in communication with the discharge port 17 b of the low pressure stage housing 16 via the intake communication passage 29.
- a circular insertion port 28 is opened in a side view in which the high-pressure stage impeller 21 can be inserted.
- the insertion opening 28 opens larger than the high-pressure stage impeller 21 to expose a part of the flow path 27 c.
- the side surface 26a on the insertion port 28 side of the high pressure stage housing 26 is formed in a planar shape, and is formed in an annular shape in a side view.
- the high-pressure stage impeller 21 is configured in the same manner as the low-pressure stage impeller 11, and is integrally provided on the back plate 22 so as to project orthogonally from the disk-like back plate 22 and one surface of the back plate 22. And a plurality of wings 24 radially projected from the outer peripheral surface of the boss portion 23 to the back plate 22.
- a through hole 23a is provided at the central portion of the boss portion 23, and the other end of the rotary shaft 3 is inserted through the through hole 23a, and the high-pressure stage impeller 21 is attached to the other end of the rotary shaft 3 via a nut 15. It is done.
- the low-pressure stage impeller 11 is attached to one end side of the rotating shaft 3
- the high-pressure stage impeller 21 is attached to the other end side of the rotating shaft 3
- the low-pressure stage impeller 11 and the high-pressure stage impeller 21 rotate. It rotates integrally with the shaft 3.
- the diameter of the high-pressure stage impeller 21 is larger than the diameter of the low-pressure stage impeller 11 described above. For this reason, the pressure ratio of the high pressure stage compressor 20 is larger than the pressure ratio of the low pressure stage compressor 10. As described above, when the diameter of the low-pressure stage impeller 11 is larger than the diameter of the high-pressure stage impeller 21, the pressure ratio of the high-pressure stage impeller 21 is the pressure ratio of the low-pressure stage impeller 11 It becomes smaller than.
- a pair of bearings 40 ⁇ / b> R and 40 ⁇ / b> L arranged at intervals in the axial direction is provided at the longitudinal middle portion of the rotating shaft 3.
- These bearings 40R and 40L are grease type rolling bearings.
- the bearing 40L on the high pressure stage compressor 20 side is provided in the bearing housing 50.
- the bearing housing 50 is formed in an annular shape, and an insertion hole 50a through which the rotary shaft 3 can be inserted is provided at the center thereof, and the diameter of the insertion hole 50a on the low pressure stage compressor 10 side is larger than that of the insertion hole 50a.
- the bearing mounting hole 50b is provided.
- a bearing 40L is mounted in the bearing mounting hole 50b, the rotary shaft 3 is inserted into the bearing 40L, and the rotary shaft 3 is rotatably supported via the bearing 40L.
- An annular projecting step 51 is provided at an end of the bearing housing 50 on the high pressure stage compressor 20 side in a side view fitted to the insertion port 28 of the high pressure stage housing 26, and the radial direction of the projecting step 51
- an annular surface 52 is provided opposite to and in contact with the side surface 26 a of the high pressure stage housing 26.
- the bearing housing 50 is integrally fixed to the high pressure stage housing 26 via a bolt 53 inserted into the high pressure stage housing 26.
- the side surface 54 on the low pressure stage compressor 10 side of the bearing housing 50 is provided with a circular engagement recess 54 a in a side view.
- the end of the motor housing 45 on the high pressure stage compressor 20 side is inserted into the engagement recess 54 a.
- a rotor space 45b rotatably surrounding the electric motor rotor 30 is provided on the bearing housing 50 side of the motor housing 45, and a bearing 40R is mounted on the low pressure stage compressor 10 side of the rotor space 45b.
- a hole 45c is provided.
- the electric motor rotor 30 is a rotor of the electric motor, is configured to rotate the rotating shaft 3 by receiving a driving force by a motor coil (not shown), and can rotate at high speed.
- the electric motor rotor 30 and the motor coil are controlled by a motor control device 74 described later.
- the intake air discharged from the exhaust port 17 b flows through the intake communication passage 29 and flows into the high pressure stage compressor 20 from the suction port 27 a of the high pressure stage compressor 20.
- the intake air flowing into the high pressure stage compressor 20 is further compressed through the flow path 27c in the high pressure stage compressor 20, and is discharged from the discharge port 27b with a predetermined pressure ratio.
- the pressure ratio of the intake compressed by the low-pressure stage compressor 10 and the pressure ratio of the intake compressed by the high-pressure stage compressor 20 are different from each other in size.
- the expansion ratio of each compression ratio of the machine 20 can be made different, and the compression ratio of the multistage electric centrifugal compressor 1 can be changed smoothly. Therefore, the multistage electric centrifugal compressor 1 which can perform arbitrary compression ratio control easily is realizable.
- the pressure ratio of the intake compressed by the low pressure compressor 10 and the pressure ratio of the intake compressed by the high pressure compressor 20 are different from each other in size, so When the low-pressure stage impeller 11 of the compressor 10 and the high-pressure stage impeller 21 of the high-pressure stage compressor 20 rotate, the inertial force and pressure ratio of the high-pressure stage compressor 20 having a larger pressure ratio are small due to the braking action.
- the difference with the inertial force of the lower pressure stage compressor 10 is considered to be the inertial force acting on the rotating shaft 3, and the inertial force can be reduced. Therefore, the multistage electric centrifugal compressor 1 capable of easily performing the rotation control of the electric motor rotor 30 can be realized.
- FIGS. 1 and 2 a supercharging system for an internal combustion engine provided with the above-described multistage electric centrifugal compressor 1 will be described with reference to FIGS. 1 and 2.
- an engine will be described as an example of an internal combustion engine.
- the discharge side of the high-pressure stage compressor 20 of the multistage electric centrifugal compressor 1 is connected to the intake side of the turbocharger 62.
- the turbocharger 62 includes an exhaust turbine 63 rotated by the exhaust gas of the engine 60 and a centrifugal compressor 65 rotated by the rotation of the exhaust turbine 63.
- the discharge pressure of the high-pressure stage compressor 20 of the multistage electric centrifugal compressor 1 is supplied via the intake passage 64b so as to be introduced to the intake side of the centrifugal compressor 65 of the turbocharger 62.
- the intake passage 64 b on the upstream side of the turbocharger 62 communicates with the discharge port 27 c of the high-pressure stage compressor 20 of the multistage electric centrifugal compressor 1.
- the centrifugal compressor 65 of the turbocharger 62 communicates with the intake side of the engine 60 through the intake passage 64c, and the exhaust turbine 63 of the turbocharger 62 communicates with the exhaust side of the engine 60 through the exhaust passage 61. ing.
- the multistage electric centrifugal compressor 1 was mentioned above, the description is abbreviate
- An intake pressure sensor 70 is provided in the intake passage 64c for detecting the pressure of intake air flowing through the intake passage 64c. Instead of the intake pressure sensor 70, an intake flow sensor that detects the flow rate of intake air may be used.
- the intake pressure sensor 70 is electrically connected to an engine control device 71 that controls the operation (ignition timing and fuel supply amount) of the engine 60.
- the engine control device 71 receives a target intake amount and fuel injection amount of intake air supplied to the engine 60 in response to a signal of an accelerator opening sensor 72 (a sensor that outputs a signal proportional to a depression amount of an accelerator pedal (not shown)). The amount is set, and the operation of the multistage electric centrifugal compressor 1 and the fuel injection device (not shown) is controlled so as to achieve the set target intake amount and fuel injection amount.
- the engine control device 71 sends a signal corresponding to the target intake air amount to the collation unit 73.
- the collating means 73 stores in advance the relationship between the required number of revolutions of the electric motor rotor 30 and the discharge flow rate of the multistage electric centrifugal compressor 1 and is provided with a map 73a, and the electric motor rotor 30 corresponding to the target intake amount sent from Derive the required number of revolutions of A signal corresponding to the derived required number of revolutions of the electric motor rotor 30 is sent to a motor control device 74 that controls the rotation of the electric motor rotor 30.
- the motor control device 74 controls the rotation of the electric motor rotor 30 so that the required number of rotations of the electric motor rotor 30 sent from the collating means 73 can be obtained.
- the exhaust gas discharged from the engine 60 causes the exhaust turbine 63 to rotate through the exhaust passage 61, and the centrifugal compressor receives the rotation of the exhaust turbine 63.
- the intake air is compressed at 65 to charge the engine 60 with intake air.
- the intake air taken in from the intake passage 64a connected to the low pressure stage compressor 10 of the multistage electric centrifugal compressor 1 flows in from the suction port 27a of the low pressure stage compressor 10, it is compressed by the low pressure stage compressor 10
- the pressure is discharged from the discharge port 17b, flows through the intake communication passage 29, is supplied to the high pressure stage compressor 20, is further compressed by the high pressure stage compressor 20, and becomes a further high pressure.
- the high-pressure intake air flows through the intake passage 64b connecting the high-pressure stage compressor 20 and the centrifugal compressor 65 and is supplied to the centrifugal compressor 65, and the intake air having a higher pressure is the centrifugal compressor 65 And the engine 60 are supplied to the engine 60 through an intake passage 64 c.
- the required number of revolutions of the electric motor rotor 30 of the multistage electric centrifugal compressor 1 is an electric motor corresponding to the target intake air amount from the map so that the matching means becomes the target intake air amount required by the engine control device.
- the necessary number of revolutions of the motor rotor 30 is selected and derived. For this reason, since the electric motor rotor 30 rotates at this derived
- the supercharging system of the engine 60 of the present application compresses the intake air with the three-stage compressors 10, 20, 65, the pressure is higher than that when the intake air is compressed with the two-stage compressor.
- the intake air can be supplied to the engine 60. Therefore, even if the rotational speed of the multistage electric centrifugal compressor 1 is lowered, the pressure of the intake air supercharged to the engine 60 can be made the desired pressure. Therefore, the deterioration of the life of the multistage electric centrifugal compressor 1 can be prevented.
- the multistage electric centrifugal compressor 1 can easily control the rotation of the electric motor rotor 30 regardless of the operating condition of the engine 60, the response of the engine 60 at low speed can be improved, and the turbocharger In addition to the assist function 62, when the assist of the turbocharger 62 is required even during steady operation, the rotational speed of the rotating shaft 3 can be easily controlled by the electric motor rotor 30. For this reason, intake of pressure according to demand can be supplied to the engine 60 via the turbocharger 62.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Supercharger (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Control Of Positive-Displacement Air Blowers (AREA)
Abstract
Description
電動モータの両側から延びる回転軸の一端側に低圧段圧縮機の羽根車を接続し、前記回転軸の他端側に高圧段圧縮機の羽根車を接続し、前記低圧段圧縮機によって圧縮された吸気を前記高圧段圧縮機により再度圧縮する多段電動遠心圧縮機であって、
前記低圧段圧縮機及び前記高圧段圧縮機は、前記低圧段圧縮機の羽根車の回転によって圧縮された吸気の圧力比と、前記高圧段圧縮機の羽根車の回転によって圧縮された吸気の圧力比とが互いに異なる大きさになるように形成されている。
前記低圧段圧縮機の羽根車の径と、前記高圧段圧縮機の羽根車の径は、互いに異なる大きさを有しているように構成される。
前記低圧段圧縮機の羽根車の形状と、前記高圧段圧縮機の羽根車の形状は、互いに異なる形状を有しているように構成される。
前記電動モータの回転数と前記多段電動遠心圧縮機の吐出圧力又は吐出流量との関係を示すマップと、
内燃機関の作動を制御する上位コントローラが前記多段遠心圧縮機に要求する吸気圧力又は吸気流量と前記マップとを照合して前記電動モータの必要回転数を導出する照合手段と
前記照合手段により導出された前記必要回転数になるように前記電動モータの回転数を制御する制御装置とを備えるように構成される。
前記請求項1に記載の多段電動遠心圧縮機の吐出側が他の過給機の吸気側に接続され、
前記多段電動遠心圧縮機の吐出空気を前記ターボ過給機の遠心圧縮機の吸気側に導入するように構成される。
前記他の過給機は、内燃機関の排気ガスにより回転する排気タービンと、前記排気タービンの回転を受けて回転する遠心圧縮機とを備えるターボチャージャとするように構成される。
吸気を3段の圧縮機で圧縮するので、2段の圧縮機で吸気を圧縮する場合と比較して、より高圧の圧力となった吸気を内燃機関に供給することができる。このため、多段電動遠心圧縮機の回転数を下げても、内燃機関に過給される吸気の圧力を所望の圧力とすることができる。よって、多段電動遠心圧縮機の寿命の低下を防止することができる。
3、66 回転軸
10 低圧段圧縮機
11 低圧段羽根車(羽根車)
12、22 背面板
13、23 ボス部
13a、23a 貫通孔
14、24 翼
15 ナット
16 低圧段ハウジング
16a、26a、54 側面
17、27 空間部
17a、27a 吸入口
17b、27b 流路
17c、27c 排出口
18、28 挿入口
20 高圧段圧縮機
21 高圧段羽根車(羽根車)
26 高圧段ハウジング
29 吸気連通路
30 電動モータ
35 背板
40R、40L 軸受
45 モータハウジング
45a、50a 挿通孔
45b モータ装着孔
45c、50b 軸受装着孔
46 フィン
50 軸受ハウジング
51 突出段部
52 面部
53 ボルト
54a 係合凹部
60 エンジン(内燃機関)
61 排気通路
62 ターボ過給機
63 排気タービン
64 吸気通路
65 遠心圧縮機
70 吸気圧力センサ
71 エンジン制御装置(上位コントローラ)
72 アクセル開度スイッチ
73 照合手段
74 モータ制御装置(制御装置)
Claims (6)
- 電動モータの両側に一対の遠心圧縮機を連結し、前記一対の遠心圧縮機は一方が低圧段圧縮機であり、他方が高圧段圧縮機になるように直列接続された多段電動遠心圧縮機であって、
前記低圧段圧縮機及び前記高圧段圧縮機は、前記低圧段圧縮機の圧力比と、前記高圧段圧縮機の圧力比とが互いに異なる大きさになるように形成されている
ことを特徴とする多段電動遠心圧縮機。 - 前記低圧段圧縮機の羽根車の径と、前記高圧段圧縮機の羽根車の径は、互いに異なる大きさを有している
ことを特徴とする請求項1に記載の多段電動遠心圧縮機。 - 前記低圧段圧縮機の羽根車の形状と、前記高圧段圧縮機の羽根車の形状は、互いに異なる形状を有している
ことを特徴とする請求項1又は2に記載の多段電動遠心圧縮機。 - 前記電動モータの回転数と前記多段電動遠心圧縮機の吐出圧力又は吐出流量との関係を示すマップと、
内燃機関の作動を制御する上位コントローラが前記多段遠心圧縮機に要求する吸気圧力又は吸気流量と前記マップとを照合して前記電動モータの必要回転数を導出する照合手段と、
前記照合手段により導出された前記必要回転数になるように前記電動モータの回転数を制御する制御装置とを備えた
ことを特徴とする請求項1に記載の多段電動遠心圧縮機。 - 前記請求項1に記載の多段電動遠心圧縮機の吐出側が他の過給機の吸気側に接続され、
前記多段電動遠心圧縮機の吐出空気を前記ターボ過給機の遠心圧縮機の吸気側に導入するようにした
ことを特徴とする内燃機関の過給システム。 - 前記他の過給機は、内燃機関の排気ガスにより回転する排気タービンと、前記排気タービンの回転を受けて回転する遠心圧縮機とを備えるターボチャージャとした
ことを特徴とする請求項5に記載の内燃機関の過給システム。
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US15/113,137 US10174670B2 (en) | 2014-02-25 | 2014-02-25 | Multi-stage electric centrifugal compressor and supercharging system for internal combustion engine |
JP2016504885A JP6466910B2 (ja) | 2014-02-25 | 2014-02-25 | 多段電動遠心圧縮機及び内燃機関の過給システム |
CN201480069105.0A CN105829728B (zh) | 2014-02-25 | 2014-02-25 | 多级电动离心压缩机及内燃机的增压*** |
EP14884028.3A EP3112686A4 (en) | 2014-02-25 | 2014-02-25 | Multistage electric centrifugal compressor and supercharging system of internal combustion engine |
PCT/JP2014/054506 WO2015128936A1 (ja) | 2014-02-25 | 2014-02-25 | 多段電動遠心圧縮機及び内燃機関の過給システム |
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EP (1) | EP3112686A4 (ja) |
JP (1) | JP6466910B2 (ja) |
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Also Published As
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EP3112686A1 (en) | 2017-01-04 |
CN105829728B (zh) | 2019-05-28 |
CN105829728A (zh) | 2016-08-03 |
JPWO2015128936A1 (ja) | 2017-03-30 |
EP3112686A4 (en) | 2017-01-04 |
US10174670B2 (en) | 2019-01-08 |
US20170002727A1 (en) | 2017-01-05 |
JP6466910B2 (ja) | 2019-02-06 |
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