US3327693A - Internal combustion engine scavenging blower and load driving arrangement - Google Patents

Internal combustion engine scavenging blower and load driving arrangement Download PDF

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Publication number
US3327693A
US3327693A US488849A US48884965A US3327693A US 3327693 A US3327693 A US 3327693A US 488849 A US488849 A US 488849A US 48884965 A US48884965 A US 48884965A US 3327693 A US3327693 A US 3327693A
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United States
Prior art keywords
impeller
engine
power output
blower
output member
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Expired - Lifetime
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US488849A
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English (en)
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Wilton G Lundquist
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Individual
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Individual
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Priority to US488849A priority Critical patent/US3327693A/en
Priority to GB40059/66A priority patent/GB1161742A/en
Priority to ES0331203A priority patent/ES331203A1/es
Priority to DEL43032U priority patent/DE1993284U/de
Priority to BE687135D priority patent/BE687135A/xx
Priority to NL6613261A priority patent/NL6613261A/xx
Priority to CH1349466A priority patent/CH445198A/de
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Publication of US3327693A publication Critical patent/US3327693A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H33/00—Gearings based on repeated accumulation and delivery of energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2700/00—Supplying, feeding or preparing air, fuel, fuel air mixtures or auxiliary fluids for a combustion engine; Use of exhaust gas; Compressors for piston engines
    • F02M2700/33—Compressors for piston combustion engines
    • F02M2700/331—Charging and scavenging compressors
    • F02M2700/333—Drive thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2706/00—Rotary transmissions with mechanical energy accumulation and recovery without means for automatic selfregulation essentially based on spring action or inertia

Definitions

  • ABSTRACT OF THE DISCLOSURE An internal combustion piston engine having a substantially cyclic torque variation in combination with a kinetic blower having an impeller member interposed between a main power output member of said engine and a load to be driven by said engine, said kinetic blower having a pressure chamber in communication with the intake manifold of said engine for delivering pressure air for scavenging and charging said engine, torsionally effective means connecting said power output member to said impeller member and means drivingly connecting said power output member to said driven load, said connecting means having such relative torsional rigidities respectively that more of the cyclic acceleration and deceleration torque delivered by said power output member is directed to the impeller than to all other flywheel masses in the system.
  • turbine actuating means is provided for imparting prerotation to said impeller member before the same is operably connected to said power output member.
  • This invention relates to an internal combustion engine of the type in which a kinetic compressor is utilized to introduce a compressed gaseous medium to the cylinders of said engine.
  • two cycle engines require some means for supplying air to scavenge and charge the cylinders.
  • Two of the means used for this purpose are (a) centrifugal blowers and (b) axial flow blowers; both of which are kinetic compressors as distinguished from displacement compressors, and as such, have in common high tip-speed impellers, which, although they are light in weight, have large flywheel potential because of their high impeller tip-speeds.
  • FIG. 1 is a top plan view of a multi-cylinder engine showing an embodiment of the present invention
  • FIG. 2 is a longitudinal sectional view taken on line 2-2 of FIG. 1, showing somewhat schematically further features of the invention
  • FIG. 3 is a view similar to FIG. 2 showing a modification of the invention.
  • FIG. 4- is a sectional view taken along the line 4-4 of FIG. 3.
  • the engine is a two cycle engine shown for simplicity purposes as having an in-line cylinder configuration, but as will be understood by those skilled in the art, the cylinders may be disposed in a V configuration, a radial configuration, or a combination of the same.
  • the engine comprises in general a plurality of cylinders such as 1 carried on an engine frame 2 and a centrifugal blower designated in general as 3.
  • each cylinder such as 1 is provided with a piston such as 4 connected in the conventional manner by a wrist pin 5 and a connecting rod 6 to the engine chankshaft 7 which is suitably journaled in the frame 2.
  • the crankshaft 7 has an end 8 on which is rigidly secured a power output gear wheel member 9 in driven mesh with a pinion 10 rigidly fixed to a portion 11 of an output shaft 12 which is suitably journaled for high speed rotation in an anti-friction bearing 13 mounted in the frame 2 and anti-friction means 14 mounted in the blower housing 15.
  • Suitable oil seal means such as 16 is interposed between the blower housing 15 and the power output shaft 12 and the outwardly extending end of the power output shaft 12 carries rigidly secured thereto a centrifugal blower impeller 17.
  • the power output shaft 12 is selectively torsionally rigid for purposes to be more fully described below and is provided with a hollow bore 18 in which is disposed a drive shaft 19 which is substantially less torsionally rigid than the power output shaft 12.
  • the inner end of the drive shaft 19 is drivingly connected to the power shaft 12 by a spline connection 21) and is provided adjacent its opposite end with a large portion 21 slidably engaged within the bore 18 and provided with an O-ring 22 serving as an oil seal.
  • the extreme outer end of the quill shaft 19 is adapted to be connected to the load to be driven as by a clutch symbolically shown as 23.
  • the air supply blower impeller 17 is driven by the power output shaft 12 via an appropriately torsionally rigid drive connection to the engine power output member 9 and is functionally interposed as a flywheel between the engine crankshaft and the driven load connected to the less rigid torsional shaft 19.
  • the torsional rigidity of the connection of the impeller to power output member 9 is of such nature that, during the cyclic accelerations and decelerations of the engine (due to the cyclic torque variations previously mentioned), a greater portion of the acceleration and deceleration torque delivered by the engine power output member 9 is directed to the impeller than to all other separate flywheel masses in the system. Accordingly, the blower impeller 17 can therefore function both as a blower and a flywheel.
  • a further advantage of this arrangement is that the gear ratio between the power output gear wheel 9 and the driven pinion 10, and the tip diameter of the impeller 17 are such as to provide a high impeller tipspeed of from 500 feet per second to up wards of 1500 feet per second as compared to conventional flywheel tip speeds of generally less than 200 feet per second, so that the flywheel potential of the blower impeller 17 can be (lb. for lb.) 6 to more than 50 times as great as that of the conventional flywheel.
  • these tip speeds may be related more specifically to the ratio between the tip speed of the impeller 17 and the mean speed of the pistons such as 4, and to acoomplish the objective of this invention, this ratio must beat least 8:1 to assure practical air supply characteristics. For supercharging, this ratio should be substantially higher than 8:1.
  • An alternate output drive flange for connecting to a driven load may be provided by an axially aligned extension 31 of output drive member 9 without impairing the fiywheel effect of the impeller, provided the previously mentioned cyclic acceleration torque distribution is adhered to in the design.
  • the centrifugal blower housing 3 is provided with an air intake 24 from which air enters a throat 25 of the impeller 17 and is forced outwardly from the tips of the impeller into a pressure chamber 26 in communication with an air inlet manifold 27 which conducts the pressure air (or fuel air mixture) from the centrifugal blower to the engine cylinders such as 1 by way of piston ported intake openings designated in general as 28, the piston ported openings such as 29 serving as exhaust ports which are in communication with air exhaust manifold 29a.
  • Fuel inlet nozzles such as 30 serve in the present embodiment to introduce fuel into the cylinders such as 1. It is to be understood that although the present engine is indicated as a compression ignition engine, it is contemplated that the features of the invention may be equally utilized in a spark ignition engine.
  • FIG. 3 illustrates a variation (mentioned previously) of the invention wherein the blower impeller flywheel is also used as a starter.
  • the configuration is generally similar to that shown in FIG. 2 except that a clutch (designated in general as 40) is interposed between the engine and the impeller flywheel so that the impeller can be independently pre-rotated (by external means) to some selected r.p.m. before it is operably connected to the engine by engaging the clutch.
  • the energy stored in the impeller flywheel can be utilized to crank the engine for starting.
  • the external energizing of the impeller may be continued to continue the cranking of the engine until it begins to operate under its own power.
  • the external source of power to pre-rotate the impeller can be some type of motor, either electric or otherwise.
  • the impeller itself can be used as a turbine wheel and thus pre-rotated by appropriate application of some type of working fluid such as compressed air or some other kind of pressurized gas introduced through appropriately designed nozzle passages.
  • some type of working fluid such as compressed air or some other kind of pressurized gas introduced through appropriately designed nozzle passages.
  • An output shaft pinion is operably connectable to an impeller shaft 12 and an impeller 17' by a clutch designated in general as 40 which is controllably operated by hydraulic fluid introduced in the passage 41.
  • the output drive shaft 1% is connected to a driven load by a conventional clutch such as used in automotive vehicles and symbolically shown as 23'.
  • a conventional clutch such as used in automotive vehicles and symbolically shown as 23'.
  • Engaging clutch 4i will then cause the flywheel effect of the impeller to crank the engine.
  • pressure fluid entering passage 41 passes through suitable connecting passages into a hollow bore 18' in which a hydraulic chamber 42 is provided by means of a sealing plug 43 having an O-sealing ring 44 and held in position by a locking ring 45. From the chamber 42 the activating fluid passes through suitably provided passagesinto the brake chamber 46 which forces the clutch members into activating engagement.
  • a nozzle passage 50 (FIG. 4) is provided in the impeller housing and is in communication with a pipe 51 adapted to supply turbine working fluid (compressed air or other pressurized gas) to the nozzle passage 50 from where the working fluid impinges on the tips of the impeller blades in a substantially tangential (in the direction of impeller rotation) direction and then passes through slots 52 which are cut into the back wall of the impeller 17' at the rim.
  • These slots 52 are oriented at an angle to the impeller wall so that they in effect impart an antirotation direction (relative to the impeller) to the exiting working fluid, thus providing a generally impulse type turbine blade passage in connection with the impeller blade tips.
  • the turbine working fluid can escape either via a blower diffuser passage 53, and thence via the blower chamber 26' and inlet manifold 27' to the engine cylinders such as 1 (as in the previously described embodiment of FIG. 1) or via passages 54 and 55 if the valve 56 is open. Suitable means (not shown) are provided for moving valve 56 to open or closed positions in the direction shown by the arrows. The purpose of this latter escape route is to provide for overboard discharge of the turbine working fluid if either the quantity or the composition of this fluid is such that it would be inadvisable to let it all pass through the engine cylinders.
  • An engine as set forth in claim 1 in which there are a plurality of cylinders provided with reciprocating pistons operatively connected to a crankshaft, said impeller being rotatably connected to said crankshaft for supplying a compressed gaseous medium to the cylinders of said engine, the ratio between the impeller tip speed and the mean piston speed being at least 8: 1.
  • An internal combustion engine as set forth in claim 1 in which a first clutch is interposed between said power output member and said blower impeller, a second clutch interposed between said power output member and said driven load means is provided for imparting pre-rotation to said impeller member before said impeller member is operably connected to said power output member by said first clutch means, said means for imparting prerotation to said impeller member including means for actuating said impeller as a turbine.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Supercharger (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US488849A 1965-09-21 1965-09-21 Internal combustion engine scavenging blower and load driving arrangement Expired - Lifetime US3327693A (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
US488849A US3327693A (en) 1965-09-21 1965-09-21 Internal combustion engine scavenging blower and load driving arrangement
GB40059/66A GB1161742A (en) 1965-09-21 1966-09-07 Internal combustion engine
ES0331203A ES331203A1 (es) 1965-09-21 1966-09-14 Un motor de combustion interna.
DEL43032U DE1993284U (de) 1965-09-21 1966-09-19 Brennkraftmaschine.
BE687135D BE687135A (en)) 1965-09-21 1966-09-20
NL6613261A NL6613261A (en)) 1965-09-21 1966-09-20
CH1349466A CH445198A (de) 1965-09-21 1966-09-20 Brennkraftmaschine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US488849A US3327693A (en) 1965-09-21 1965-09-21 Internal combustion engine scavenging blower and load driving arrangement

Publications (1)

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US3327693A true US3327693A (en) 1967-06-27

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US488849A Expired - Lifetime US3327693A (en) 1965-09-21 1965-09-21 Internal combustion engine scavenging blower and load driving arrangement

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US (1) US3327693A (en))
BE (1) BE687135A (en))
CH (1) CH445198A (en))
DE (1) DE1993284U (en))
ES (1) ES331203A1 (en))
GB (1) GB1161742A (en))
NL (1) NL6613261A (en))

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4907549A (en) * 1988-04-30 1990-03-13 Fuji Jukogyo Kabushiki Kaisha Scavenging system for a two-stroke-cycle engine
US10415518B2 (en) * 2017-12-29 2019-09-17 Chien-Hsiang Huang Supercharger structure for an all terrain vehicle or a utility vehicle

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3504465C1 (de) * 1985-02-09 1986-01-02 M.A.N.-B & W Diesel GmbH, 8900 Augsburg Vorrichtung zum Aufladen eines Verbrennungsmotors
MX167296B (es) * 1989-02-27 1993-03-15 Orbital Eng Pty Motor de combustion interna, sobrealimentado, de cilindro multiples
CN112373675B (zh) 2020-11-13 2022-02-08 重庆宗申航空发动机制造有限公司 一种用于航空动力的螺旋桨传动系统

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1440685A (en) * 1923-01-02 Internal-combustion engine
US2176021A (en) * 1936-09-19 1939-10-10 Fritz P Grutzner Exhaust gas turbine for combustion engines
US2252512A (en) * 1940-09-28 1941-08-12 Keller Vincent Joseph Internal combustion motor
US2255424A (en) * 1937-03-31 1941-09-09 Jandasek Joseph Starting means
US2445965A (en) * 1946-08-07 1948-07-27 Heza H Packwood Power lawn mower with air filtering screen
GB696729A (en) * 1950-09-13 1953-09-09 List Hans Improved arrangements of scavenging air blower driver in two-stroke internal combustion engines
US3253658A (en) * 1965-06-03 1966-05-31 Garrett Corp Torque meter

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1440685A (en) * 1923-01-02 Internal-combustion engine
US2176021A (en) * 1936-09-19 1939-10-10 Fritz P Grutzner Exhaust gas turbine for combustion engines
US2255424A (en) * 1937-03-31 1941-09-09 Jandasek Joseph Starting means
US2252512A (en) * 1940-09-28 1941-08-12 Keller Vincent Joseph Internal combustion motor
US2445965A (en) * 1946-08-07 1948-07-27 Heza H Packwood Power lawn mower with air filtering screen
GB696729A (en) * 1950-09-13 1953-09-09 List Hans Improved arrangements of scavenging air blower driver in two-stroke internal combustion engines
US3253658A (en) * 1965-06-03 1966-05-31 Garrett Corp Torque meter

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4907549A (en) * 1988-04-30 1990-03-13 Fuji Jukogyo Kabushiki Kaisha Scavenging system for a two-stroke-cycle engine
US10415518B2 (en) * 2017-12-29 2019-09-17 Chien-Hsiang Huang Supercharger structure for an all terrain vehicle or a utility vehicle

Also Published As

Publication number Publication date
GB1161742A (en) 1969-08-20
DE1993284U (de) 1968-09-05
NL6613261A (en)) 1967-03-22
BE687135A (en)) 1967-03-20
CH445198A (de) 1967-10-15
ES331203A1 (es) 1967-09-16

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