US3112658A - Harmonic balancing device for internal combustion engines - Google Patents

Harmonic balancing device for internal combustion engines Download PDF

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Publication number
US3112658A
US3112658A US50368A US5036860A US3112658A US 3112658 A US3112658 A US 3112658A US 50368 A US50368 A US 50368A US 5036860 A US5036860 A US 5036860A US 3112658 A US3112658 A US 3112658A
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United States
Prior art keywords
crankshaft
engine
pendulums
cylinder
connecting rods
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Expired - Lifetime
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US50368A
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English (en)
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Martin J Berlyn
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Individual
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Individual
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Priority to US50368A priority patent/US3112658A/en
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    • 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
    • F16F15/22—Compensation of inertia forces
    • F16F15/26—Compensation of inertia forces of crankshaft systems using solid masses, other than the ordinary pistons, moving with the system, i.e. masses connected through a kinematic mechanism or gear system
    • F16F15/261—Compensation of inertia forces of crankshaft systems using solid masses, other than the ordinary pistons, moving with the system, i.e. masses connected through a kinematic mechanism or gear system where masses move linearly
    • 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
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/20—Multi-cylinder engines with cylinders all in one line
    • 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
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B2075/1804—Number of cylinders
    • F02B2075/1808—Number of cylinders two
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2142—Pitmans and connecting rods
    • Y10T74/2154—Counterbalanced
    • Y10T74/2156—Weight type
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2173—Cranks and wrist pins
    • Y10T74/2183—Counterbalanced

Definitions

  • An object of this invention is to provide, for compensation of primary and secondary unbalance in reciprocating engines, a harmonic balancer of inherently low power consumption.
  • Another object is to provide a harmonic balancer of compact form.
  • Another object is to provide a harmonic balancer of low cost.
  • Another object is to provide a harmonic balancer which will not increase the crankcase depth of vertical engines.
  • Another object is to provide a harmonic balancer which, as applied to parallel twin engines, does not increase the engine length.
  • Another object is to provide a harmonic balancer which will make practicable the commercial high-speed parallel twin engine in sizes considerably greater than heretofore.
  • FIG. 1 shows the transverse median section of a parallel twin engine incorporating the preferred execution of harmonic balancer according to this invention. As shown in FIG. 1, the crankshaft is at top dead centre position.
  • FIG. 2 shows a partial vertical longitudinal section in the plane of the crankshaft axis, corresponding with 22 of FIG. 1.
  • FIG. 3 shows a partial section along 33 of FIG. 1.
  • FIG. 4 shows a section in the same plane as FIG. 1 but with the crankshaft turned through 90 from dead centre.
  • FIG. 5 shows a horizontal section in the plane of the crankshaft axis, corresponding with 55 of FIG. 4.
  • FIG. 6 is a view generally similar to FIG. 4 but shows a modified form of the invention.
  • cranks In the first device, a combination of cranks, connecting rods, and dummy pistons is used.
  • the dummy pistons must be on the opposite side of the crankshaft from the power piston, and the cranks for the dummy pistons must be phased from the power crank.
  • This balancer has proved satisfactory in application to research engines, but it is unattractive for commercial engines and has never been so applied.
  • the two additional cranks (which usually take the form of eccentrics) substantially increase both the length of the crankshaft and the span between crankshaft main bearings.
  • the dummy pistons In vertical engines, the dummy pistons must be below the crankshaft, which increases the depth of the crankcase; furthermore, the power loss due to the friction of the dummy pistons in their guides is unacceptable in commercial engines and is tolerable only in the case of research engines.
  • the parallel twin is dynamically similar to a single-cylinder engine and has only been practicable in small sizes on account of the characteristic vibration at high speeds which is intolerable in engines whose total piston displacement exceeds about 40 cubic inches.
  • the line along which the balancer-generated forces must act is the cylinder am's itself. This is to say that with a harmonic balancer of the dummy-piston type, there must be two identical dum-my pistons symmetrically spaced from the cylinder axis.
  • the line along which the balancer-generated forces must act lies in the median transverse plane of the engine.
  • the balancer cranks mus-t be phased 180 from the power crank; this is to say that a single balancer crankpin in the median transverse plane of a parallel twin would not overlap the power crankpins.
  • the crankshaft structure would have to include two additional crankwebs of greater axial thickness than the webs which connect the power crankpins to the main crankshaft journals. The use of a single dummy piston for the balancing of a parallel twin engine, therefore, does not in fact result in a shorter engine.
  • a harmonic balancer suitable for commercial single-cylinder and parallel twin engines, which does not increase the crankcase depth and in which there are neither crosshead-guided reciprocating counterweights nor geared pairs of shafts carrying rotary counterweights.
  • My harmonic balancer has the further great advantage that its cranks are in phase with the power crank; substantial economy in engine length results from this characteristic when my balancer is applied in singlecrank form to the parallel twin, because the balancer crank-pin overlaps the power crankpins, permitting the use of axially thin webs for connection of the balancer crankpin to the power crankpins.
  • crankpins 5 The forces due to pistons 1 are transmitted to crankpins 5 by way of connecting rods :11.
  • crankpin is provided.
  • crankpin 9 is located in the plane of symmetry between crankpins 5.
  • the eccentricity of crankpin 9 from the axis of crankshaft 14 is preferably about half the eccentricity of crankpins 5.
  • crankshaft 14- and crankpins 5 lie in a common plane.
  • the axis of crankpin 9 also lies in this plane intermediately of crankshaft 14 and crankpins 5.
  • the balancer consists of two connecting rods 3 whose inner ends are journaled side by side on crankpin 9 and whose outer ends comprise relatively massive 'bobweights 7.
  • the two bobweights 7 are on opposite sides of crankpin 9 and are operably connected by wristpins 8 to forked links 13.
  • bobweights 7 are made integral with connecting rods 3 they constitute, in combination with forked links 13, two simple pendulums.
  • connecting rods 11 their upper portions may be assumed to be reciprocating in unison with pistons 1 and their lower portions may be assumed to be rotating in unison with crankpins 5.
  • the outer portions of connecting rods 3, wristpins S, and the lower portions of forked links 13- may be considered as parts of bobweights 7 and constrained to traverse arcuate paths having a radius equal to the distance between the axes of wristpins 8 and fulcrum pins 4.
  • the inner portions of connecting rods 3 may be assumed to be rotating in unison with crankpin 9.
  • crankshaft counterweights can do nothing to compensate secondary unbalance, which has a frequency twice that of crankshaft rotation.
  • bobweights 7 are subjected to cyclical horizontal accelerations, at the the frequency of crankshaft rotation, which exactly oppose and cancel the horizontal components of force created by those portions of counterweights 6 which counterpoise pistons 1, wristpins 1t) and the upper portions of connecting rods 11 (see FIG. 4).
  • bobweights 7 are subjected to cyclical vertical accelerations, at twice the frequency of crankshaft rotation, which exactly oppose and cancel the vertical secondary forces created by accelerations of the reciprocating components of the engine due to cyclical angularity of connecting rods 11 (see FIGS. 1 and 4).
  • my harmonic 'balancer is characterized by low relative velocities of conjugate working parts and by a general arrangement of the components such as to demand no additional depth of crankcase below the crankshaft axis.
  • crankshaft including journals and a crankpin
  • main connecting rod connecting said piston and said crankshaft
  • counterweights fixed to said crankshaft and rotating therewith
  • pendulu-m supporting means carried by said engine frame
  • pendulums pivotally connected to said pendulum supporting means and auxiliary connecting rods connect ing said pendulum-s to said crankshaft and means on said crankshaft operatively connected to said auxiliary connecting rods for driving said pendulurns, the axis of said means for driving said pendulums being intermediate the axis of the crank journals and the axis of said crankpin.
  • an internal combustion en ine having an engine frame, a pair of cylinders in said frame, a piston in each of said cylinders, a crankshaft, a main connecting rod connecting each of said pistons and said crankshaft, counterweights fixed to and rotating with said crankshaft, pendulum supporting means carried by said engine frame, pendulums pivotally connected to said pendulum supportinn means and on opposite sides of said crankshaft and adapted to swing in planes parallel with the planes of rotation of said countenweights and auxiliary connecting rods connecting each of said pendulums with said crankshaft.
  • an internal combustion engine having an engine frame, a pair of cylinders in said frame, a piston in each of said cylinders, a crankshaft, a main connecting rod connecting each of said pistons and said crankshaft, counterweights fixed to and rotating with said crankshaft, pendulum supporting means carried by said engine frame, pendulums pivotally connected to said pendulum supporting means and on opposite sides of said crankshaft and adapted to swing in planes parallel with the planes of rotation of said counterweights and auxiliary connecting rods connecting each of said pendulums with said crankshaft, the pivots for said pendulums being on the same side of the crankshaft axis as the engine cylinders.
  • pendulum supporting means carried by said engine frame, pendulums pivotally connected to said pendulum supporting means and auxiliary connecting rods connecting said pendul-urns to said crankshaft and means on the crank-shaft operatively connected to said auxiliary connecting rods for driving said pendulums, said pendulums each including a pivoted link pivotally connected to said pendulum supporting means and to the auxiliary connecting rods.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
US50368A 1960-08-18 1960-08-18 Harmonic balancing device for internal combustion engines Expired - Lifetime US3112658A (en)

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Application Number Priority Date Filing Date Title
GB909435D GB909435A (enrdf_load_stackoverflow) 1960-08-18
US50368A US3112658A (en) 1960-08-18 1960-08-18 Harmonic balancing device for internal combustion engines

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Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3257109A (en) * 1964-01-06 1966-06-21 Miehle Goss Dexter Inc Regenerative system for alternating motion
US3372624A (en) * 1964-12-10 1968-03-12 Philips Corp Rolling diaphragm device with inertia force compensating means
US3528319A (en) * 1968-01-30 1970-09-15 President Shizuoka Univ Perfectly balanced vibrationless rotation - reciprocation device of crankshaft planetary motion system
US4152956A (en) * 1976-08-24 1979-05-08 Rudolf Hintze Compressor for air-conditioning devices for vehicles
US4351202A (en) * 1969-11-24 1982-09-28 Summers Robert F Engine
US4481918A (en) * 1981-10-15 1984-11-13 Triumph Motorcycles (Meriden) Limited Means for reducing vibration in reciprocating engines
US4819593A (en) * 1988-04-28 1989-04-11 Briggs & Stratton Corporation Pivoting balancer system
US4924727A (en) * 1987-09-09 1990-05-15 Gerber Garment Technologies, Inc. Cutting machine having balanced reciprocating cutter drive mechanism
US5282397A (en) * 1992-03-19 1994-02-01 Briggs & Stratton Corporation Engine balancing system having at least one pivoting counterbalance weight
US5758615A (en) * 1995-10-18 1998-06-02 Meta Motoren-Und-Energie-Technik Gmbh Arrangement for vibration compensation in a reciprocating-piston internal-combustion engine
US6202537B1 (en) 1999-07-13 2001-03-20 Caterpillar Inc. Connecting rod for horizontally opposed compressor
US6295962B1 (en) * 1996-04-02 2001-10-02 Naxsym Engine Technology Ltd. Crankshaft and piston arrangement
US20040211384A1 (en) * 2003-04-28 2004-10-28 Karl Glinsner Mass balancing for internal combustion engine
WO2006113971A1 (en) * 2005-04-27 2006-11-02 Righteous Design Pty Ltd A balanced crank assembly
US20110083631A1 (en) * 2007-05-31 2011-04-14 Meta Motoren- Und Energie-Technik Gmbh Method and device for reducing rotational non-uniformities of the crankshaft of an internal combustion piston engine
AU2006239735B2 (en) * 2005-04-27 2012-02-02 Satchell, Peter Ralph Mr A balanced crank assembly
CN103348162A (zh) * 2011-01-21 2013-10-09 梅塔电机和能源技术有限公司 用于减小活塞式内燃机的曲轴的转动不均衡性的装置
US9057371B2 (en) 2010-02-09 2015-06-16 Meta Motoren-Und Energie-Technik Gmbh Method for varying the duration of a supply stroke of a pump element, and a pump device

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2311820B (en) * 1996-04-02 2000-03-15 Patrick Michael Cransto Walker Crankshaft and piston arrangement

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US672320A (en) * 1899-12-13 1901-04-16 Robert Edgar Ford Counterbalance.
US2047419A (en) * 1933-02-16 1936-07-14 Chrysler Corp Internal combustion engine
US2255773A (en) * 1937-08-24 1941-09-16 Heftler Paul Vibrationless power plant
US2632340A (en) * 1949-04-07 1953-03-24 Gen Motors Corp V-6 engine
US2997951A (en) * 1957-11-01 1961-08-29 William F Huck Wiping and polishing device for intaglio printing presses

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US672320A (en) * 1899-12-13 1901-04-16 Robert Edgar Ford Counterbalance.
US2047419A (en) * 1933-02-16 1936-07-14 Chrysler Corp Internal combustion engine
US2255773A (en) * 1937-08-24 1941-09-16 Heftler Paul Vibrationless power plant
US2632340A (en) * 1949-04-07 1953-03-24 Gen Motors Corp V-6 engine
US2997951A (en) * 1957-11-01 1961-08-29 William F Huck Wiping and polishing device for intaglio printing presses

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3257109A (en) * 1964-01-06 1966-06-21 Miehle Goss Dexter Inc Regenerative system for alternating motion
US3372624A (en) * 1964-12-10 1968-03-12 Philips Corp Rolling diaphragm device with inertia force compensating means
US3528319A (en) * 1968-01-30 1970-09-15 President Shizuoka Univ Perfectly balanced vibrationless rotation - reciprocation device of crankshaft planetary motion system
US4351202A (en) * 1969-11-24 1982-09-28 Summers Robert F Engine
US4152956A (en) * 1976-08-24 1979-05-08 Rudolf Hintze Compressor for air-conditioning devices for vehicles
US4481918A (en) * 1981-10-15 1984-11-13 Triumph Motorcycles (Meriden) Limited Means for reducing vibration in reciprocating engines
US4924727A (en) * 1987-09-09 1990-05-15 Gerber Garment Technologies, Inc. Cutting machine having balanced reciprocating cutter drive mechanism
US4819593A (en) * 1988-04-28 1989-04-11 Briggs & Stratton Corporation Pivoting balancer system
US5282397A (en) * 1992-03-19 1994-02-01 Briggs & Stratton Corporation Engine balancing system having at least one pivoting counterbalance weight
US5758615A (en) * 1995-10-18 1998-06-02 Meta Motoren-Und-Energie-Technik Gmbh Arrangement for vibration compensation in a reciprocating-piston internal-combustion engine
US6295962B1 (en) * 1996-04-02 2001-10-02 Naxsym Engine Technology Ltd. Crankshaft and piston arrangement
US6202537B1 (en) 1999-07-13 2001-03-20 Caterpillar Inc. Connecting rod for horizontally opposed compressor
US20040211384A1 (en) * 2003-04-28 2004-10-28 Karl Glinsner Mass balancing for internal combustion engine
EP1473451A1 (en) * 2003-04-28 2004-11-03 Bombardier-Rotax GmbH & Co. KG Mass balancing for internal combustion engine
US7040273B2 (en) 2003-04-28 2006-05-09 Brp-Rotax Gmbh & Co. Kg Mass balancing for internal combustion engine
WO2006113971A1 (en) * 2005-04-27 2006-11-02 Righteous Design Pty Ltd A balanced crank assembly
AU2006239735B2 (en) * 2005-04-27 2012-02-02 Satchell, Peter Ralph Mr A balanced crank assembly
US20110083631A1 (en) * 2007-05-31 2011-04-14 Meta Motoren- Und Energie-Technik Gmbh Method and device for reducing rotational non-uniformities of the crankshaft of an internal combustion piston engine
US8701616B2 (en) * 2007-05-31 2014-04-22 Meta Motoren- Und Energie-Technik Gmbh Method and device for reducing rotational non-uniformities of the crankshaft of an internal combustion piston engine
US9057371B2 (en) 2010-02-09 2015-06-16 Meta Motoren-Und Energie-Technik Gmbh Method for varying the duration of a supply stroke of a pump element, and a pump device
CN103348162A (zh) * 2011-01-21 2013-10-09 梅塔电机和能源技术有限公司 用于减小活塞式内燃机的曲轴的转动不均衡性的装置
CN103348162B (zh) * 2011-01-21 2016-03-16 梅塔电机和能源技术有限公司 用于减小活塞式内燃机的曲轴的转动不均衡性的装置

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