US2235160A - Piston machine with crankshaft - Google Patents

Piston machine with crankshaft Download PDF

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Publication number
US2235160A
US2235160A US219497A US21949738A US2235160A US 2235160 A US2235160 A US 2235160A US 219497 A US219497 A US 219497A US 21949738 A US21949738 A US 21949738A US 2235160 A US2235160 A US 2235160A
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United States
Prior art keywords
motor
crankshaft
piston
axis
turning
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Expired - Lifetime
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US219497A
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English (en)
Inventor
Ljungstrom Fredrik
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Volvo Construction Equipment AB
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Bolinder Munktell AB
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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
    • 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
    • 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
    • F16F15/264—Rotating balancer shafts
    • 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
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle 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
    • Y10T74/2173—Cranks and wrist pins
    • Y10T74/2183—Counterbalanced
    • Y10T74/2184—Vibration dampers

Definitions

  • I 7 I Such vibrations, for instance in combustion which appear especially with motors having only r the machine.
  • The' stationary motor body is, howevengnevertheless exposed to 'balancedaround this axis, so that the machine body with respect to the said pressure reaction impulsesoscillates asa pendulum with atleast th'e'fly wheel has mink ig The' -impuls'esfin this reaction moment which'ar ,stiiimor'euneven than those which. are taken:upffbyfthejflylwheel are transierred directly through to the.
  • the invention relates in the first place to machines .ibein'g-Tasymm'etrical with respect to the axis of rotation of the crankshaft and for instance hav inc vertical cylinder, whereby balance weights j are provided which dynamically balance the t machine around its axis of rotation.
  • the weight :of the machine becomes by this decidedly greater,
  • the fly wheel is imagined to be stationary while the motor bodyis allowed to rotate, with the mere difference that the fly wheel and the motor body have changed places.
  • a construction with rotating cylinder plant is often used on aero motors.
  • the motor body will of course in this case be accelerated to the same degree as the fly wheel according to the aforesaid but in opposite direction, and v the acceleration, on a radius of inertia of 0.5 m., during a quarter of a revolution is 0.5 m./sec.
  • the power of acceleration is of course independent of whether the fly wheel or the motorbody or both rotate, as both are subject to the same turning moment although in opposite directions. If, therefore, the fly wheel rotates with 5 revolutions/sec. and the motor body ismade free so that it can rotate about the motor shaft, it will also now be subject to an acceleration of 0.5 m./sec.
  • a spring device is disposed between the motor body and its support, which device brings the motor body back towards the original position after each reaction impulse while delivering an even turning moment to the surroundings, whereby the motor body makes a pendulum movement with the crankshaft of the motor as the axis of rotation. Because of the fact that the motor additionally is balanced about this axis, vibrations originating from the turning reaction moments are effectively avoided.
  • the said spring device is preferably combined with means which automatically set the same, and thereby increase the spring power on increasing reaction turning moment and vice versa, so that the device can take up turning moments varying within broad limits without altering the position of the motor.
  • a further feature of the invention is to provide means for eliminating vibrations in the neighbourhood of the motor, originating from the unbalance of the reciprocating members (piston, connecting rod), of the motor. It is known to counterbalance said members by means which are heavier than the same, and which are adapted to move in paths equivalent to those of the members.
  • themeans comprise movable eccentric disc elements journalled on eccentrics on the crankshaft, and balance weights Journalled on said elements, whereby means are provided for guiding said weights.
  • FIG. I shows a longitudinalv section through a one-cylinder internal combustion motorhcon structed accordingto the invention.
  • Fig. II shows the motor viewedin the direction of the shaft. partly in section on the llneiII-QII Orr-fer.
  • Fig. III shows adiagram illustrating the work I ing manner of the motor.'-
  • Fig. VI shows 'the same element partly inan axial section.
  • l a Figs. VII and VIII show side elevations of details pertaining to the same embodiment.
  • Fig. IX shows another embodiment of means for balancing the movable members of a machine viewed in a vertical section in the plane of. the crankshaft on the line IX-IX of Fig. K.
  • Fig. X shows a section on the line X-e-X of Fig. IX.
  • Figs. XI and X11 illustrate diagrammatically the machine according to this embodiment and adetail thereof, respectively.
  • Fig. XIII shows a portion of a piston machine embodiment of the int:
  • crank case below the shaft the crank case is,formed as a balance weight 20 (Fig. II), which statically and dynamically balances the motor body which is pivotable in the frame bearings I! about the axis of the crankshaft.
  • the weight of the motor aggregate becomes in this way greater below than above the crankshaft.
  • the linear extension of the motor is nevertheless smaller in the lower part.
  • the motor is preferably symmetrical on each side of the symmetry plane IIII (Fig. I), in which all the forces on the piston, the connect ing rod and the crankshaft are active.
  • a spring device which in the embodiment according to Figs. I--IV consists in one or several springs 22, connected to a lever 21,
  • a piston 24 is arranged which moves in a cylinder 25 which, through a conduit 26, is in servo-motor-cylinder 21 is connected an oil con-' duit 36 which is provided with a check valve 31.
  • An oil discharge channel 38 extends from the cylinder 2? at a distance above its bottom.
  • the pipe 50 may be provided with spherical surfaces'engaging flange 52 and a flange of the silencer 5i.
  • Packing rings 53 may be disposed in said surfaces.
  • the cylinder ll may oscillate relatively to the stationary silencer 5
  • the mode of operation is as follows:
  • the pulsatingreactions acting on the motor body l0, H, with its balance weight 20 are, during normal operation of the motor, transferred through the lever 23 and the spring member 22 to the stationary frame 88.
  • the motor body thereby acts as an oscillating fly wheel, while the spring 22 transfers an equalized reaction turn- 1 ing moment to the surroundings;
  • the spring is automatically set against the lever- 23 by the servo-motor cooperating with the spring, dependent on the size of the reaction impulses on the motor housing Hi, .[If the lever 23 is iturned downwardly in Fig.
  • the slide valve 28- will in a certain positionopen connection with the conduit 83 for pressure 011, hich flows into the cylinder chamber 25 below the piston 24, resulting in a compression and setting of the spring 22.
  • the slide valve 28 In a certain upper .position of the slide valve 28 its channel '32 on the contrary, communicates with the discharge conduit 84, and oil can now flow out from the cylinder chamber below the piston 25.
  • This setting lengthor the piston stroke of the cylinder 25 is in accordance with the invention so determined that it is several times, for instance ten times, greater than the oscillation amplitude of the motor body III, II.
  • this oscillation amplitude may be kept within utmost reasonable limits and may thus on 0.5 in. radius be restricted to somewhat over one cm.
  • the compression length of the spring is for instance ten times the swinging amplitude of the motor, the turning moment transferred to the surroundings varies with one tenth of the mean turning moment. If this mean turning moment is as in the above example one fourth of the maximum turning moment during the explosion period (in reality the diiference is much greater), the reactive impulses transferred to the surroundings in a motor of conventional type will be deassume creased to one tenth of the mean turning moment,
  • the oscillation path or the amplitude would therefore, if allowed to be freely developed, increase to values which would be practically inconceivable.
  • the slide valve 28 connected to the lever 23 is for this reason preferably formed as a dash pot or buifer piston which enlarge oscillating movement of the motor passes the outlet opening 38 of the cylinder 21, whereby oil confined-in this cylinder below the opening 38 takes up the excess of turning moment of the motor.
  • Fig. IV serves merely to illustrate the working manner of a device balancing the inner movable motor members.
  • the piston is, as in the foregoing, designated by I2, and the connecting rod by i3.
  • the counterweight 44 working between vertical guide members is arranged diametrically opposite the piston l2, and cooperates with the same crankshaft as the piston by means of a connecting rod or lever 43, which in Fig. IV is half as long as the connecting rod I 8.
  • the stroke of the eccentric lever 43 is also half as long as that of the connecting rod 83.
  • the counterweight do is in this case twice the weight of the piston 42 and, moreover, the weight of the arm d3 is twice that of the connecting rod 03.
  • the piston mechanism is obviously from dynamic point of view characterised by two reciprocating uniform movements; one of which has half the dimension of the other but works with double the weight.
  • the balance is proper, as the center of gravity of the system always coincides with the axis of rotation.
  • Figs. V-VIII an embodiment of a balance device for the piston mechanism according to the invention is shown. which permits a several times greater decrease of eccentricity or stroke length 01 the balancing masses.
  • l2 again designates the piston, and It the connecting rod which, at one end, is journalled on the crank pin ll of the crankshaft l5.
  • an imaginary eccentric arm 60 is illustrated in Fig. V, which at one end is joumalled in the eccentric 8i diametrically opposite to the crank pin l4, and in its other end carries a balance weight-G2.
  • the members balancing the piston mechanism produce vertical acceleration and retardation forces symmetric with the forces which act on the piston I2, and on the connecting rod I3, which latter however, may be said to correspond to a weightless imaginary eccentric lever 80.
  • the movable counter-balancing members are therefore to be adapted also to balance those parts of the connecting rod, which more or less have an acceleration course characterized by the movements of the piston. 1
  • crankshaft I5 is provided with two cylindrical eccentrics I22, the center lines I 24 oi which are eccentrically displaced relatively to the axis of rotation H of the crankshaft on the diametrically opposed side of the shaft I I4.
  • the crankshaft I5 is provided with two cylindrical eccentrics I22, the center lines I 24 oi which are eccentrically displaced relatively to the axis of rotation H of the crankshaft on the diametrically opposed side of the shaft I I4.
  • the center lines I25 which with their outer surface preierably being cylindrical are iournalled in the crank case Ill; and the center lines I2 of which are positioned in" a plane through the axis of ro-' tation 2
  • the eccentricity of the sleeves I25 is so chosen that the distance I28 (Fig. XII) between their axis I26 and the axis 12! of the eccentrics I23, is as many or substantially as many times smaller than the distance between theaxis III and I21, as the distance between the axis I24 and 2i is smaller than the distance between the axis H4 and H.
  • the motor case and the eccentric sleeves I2! move in the same manner as the element I2. I3, although on adecreased scale.
  • the movement-of the motor case and the sleeves I25 is diametrically opposed tothe movement of the piston I2 and the connecting rod I3.
  • rod l3 and of the, motor "case. are eduivalentto the paths of theconnectingrod; "and the il -y ton l2, merely with the diiierence that theiirst mentioned paths are diametrically opposed to the last mentioned, and moreover to'a great extent decreased.
  • the motor case is m: I
  • crank I4 is provided. with counter-weights" vertical. up and-"down movementot the motor case'is arcuate; Thus the movement does not 60 -ever, as;itsfainplitude is verysmall, the actual path of movement, will difler merely by a few degrees from a straight line, which is without prac- I tical importance.
  • the bars may of course'be rejplaced by guides or the like, provided for in- 'j sce ex tly along 'a'jtraight line. How
  • the amplitude of the movements of the machine and the piston will be in inverse proportion to the weight or mass of the bodies.
  • the movable motor case may in the embodiment according to Figs. IX-XII be prevented from rotating relatively to the surroundings by means of a spring member cated in Fig. XI.
  • the motor may of course be provided with means for taking up and equalizing the uneven turning moments,such as described in connection with Figs. I-III.
  • Fig. XIII shows an balance weights I32 for the crank are omitted, so that the center of gravity of the crank is spaced from the axis of shaft. Also in this case a balancing by means of the motor casing may be accomplished in accordance with the invention.
  • I23 designates the eccentrics of the crankshaft IS, the axis of rotation I24 of which lies at a distance from the axis of rotation 2
  • the axis 2I was in other words the. axis of the crankshaft in the foregoin g embodiment.
  • the bars I33 are in Fig. XIII concentrically journalled relatively to the axis 2i.
  • the axis H is, however, in turn displaced relative to the axis I 31 of the crankshaft I 5, so that the distance between the axis 2
  • the axis of rotation ll of the bars I33 in the embodiment according to Fig. m1, being eccentric to the axis of rotation I31 of the crankshaft I5, is positioned hr 2.
  • the axis 2i is positioned on the side opposite the axis I31, relative to the axis lid of the crank.
  • the center of gravity of by the fact that it positively is,
  • I36 diagrammatically .indiembodiment in which the 7' be journalied in needle bearings.
  • the invention is applicable to all kinds of single or multi-cylinder machines with vertical cylinders. Moreover, the invention may be applied to compressors and other kinds of piston machines having vibrations. Multi-cylinder machines are suitably provided with separate spring means for each cylinder, which are built independent of each other. The advantages gained by the invention are especially noticeable at slowrotating, for instance one-cylinder'machines, for driving vessels such as fishing boats, or the like. According to my invention a strong and simple machine may be utilized without being forced to take into account irritating shaking of the hull of the vessel.
  • the pressure oil required for the operation of the servo-motor in the embodiment according to Fig. I may be taken from the oil circulation system of the motor.
  • the eccentric disc 60a according to Figs.
  • V-VIII may be provided with an external bearing surface against the weight 62a, only extending through part of the circumference, that is to say a portion (a segment) of the disc at the lower end thereof in Fig. V. may be cut away.
  • the inner bore of the frame .620; is in such case provided with a sliding or bearing surface in the form of an arc which does not enclose the whole disc 60a;
  • the excenter sleeves I25 in the embodiment according to Figs; IX-XII may on the outer face
  • the invention does not exclude supporting the whole motor aggregate on a soft resilient base, for instance in order to avoid noise vibrations.
  • the bearing housings I1 or the base supporting the same may be mounted on a resilient support.
  • Figs. IX-XIII two different positive movements are shown, which eliminate the shaking action of'the movable motor members on the surroundings. These positive movements are caused directly by the "crankshaft.
  • crankshaft said'body being turnable with re- A' greater number of other movements is, however, conceivspect to said crankshaft in a plane normal to the axis of rotation of said shaft, supporting structure for turnably supporting said body-about said crankshaft, said body being substantially dynamically balanced about its turning axis, and means for resiliently resisting turning of said body with respect to said supporting structure,
  • said means providing increasing resistance upon increasing turning of said body from a normal position.
  • a body structure a crankshaft rotatably mounted in said body, -a piston connected to said crankshaft and reeiprocable within said body, supporting structure, said body being turnably mounted with respect to said supporting structure about an axis concentric with the axis of rotation of said crankshaft, said body being substantially dynamically balanced about said axis, and means for resiliently resisting turning of said body with respect to said supporting structure, said means providing increasing resistance upon increasing turning of said body from a normal position.
  • a body structure including a cylinder, a piston reciprocable within said cylinder, a crankshaft rotatable with respect to said body, supporting structure for turnably supporting said body in a plane normal to the axis of rotation of said crankshaft, said body being substantially dynamically balanced-about its turning axis', the weight of that portion of said body on the side of said crankshaft occupied by said cylinder being substan tially less than the weight of the portion on the opposite side, and means for resiliently resisting turning of said body with respect to said sup,- porting structure, said means providing increasing resistanceupon increasing turning of said body from a normal position.
  • a body structure including a cylinder, a piston reciprocable within said cylinder, a crankshaft rotatable with respect to said body, supporting structure for turnably supporting said body in a plane normal to the axis of rotation of said crankshaft, said body being substantially dynamically balanced about its turning axis, resilient means for resisting turning of said body with respect to said supporting structure, and means for varying the resistance to turning offered by said resilient means, so as to increase the resistance the further said body turns from a normal position.
  • a body structure including a cylinder, 8. piston reciprocable within said cylinder, a crankshaft rotatable with respect to said body, supporting structure for turnably supporting said body in a plane normal to the axis of rotation of said crankshaft, said body being substantially dynamically balanced about its turning axis, resilient means for resisting turning of said body with respect to said supporting structure, and means responsive to increasing tendency of said body to turn for increasing the resistance to turning offered by said resilient means.
  • a body structure including a cylinder, a piston reciprocable within said. cylinder, a crankshaft rotatable with respect to said body, supporting structure for turnably supporting said body in a plane normal to the axis of rotation of said crankshaft, said body being substantially dynamically balanced about its turning axis, a movable abutment, spring means disposed between'said body and said abutment for limiting turning of the body with respect to said supporting structure, and means responsive to an increase in the turning amplitude of said body for moving said abutment in a direction to increase the resistance to turning offered by said spring means.
  • a body structure including a cylinder, 9, piston reciprocable within said cylinder, a crankshaft rotatable with respect to said body, supporting structure for turnably supporting said body in a plane normal to the axis of rotation of said crankshaft, said body being substantially dynamically balanced about its turning axis, a movable abutment, spring means disposed between said body and said abutment for limiting turning of the body with respect to said supporting structure, and means responsive toan' increasein the turnmg amplitude of said body for moving said abutment a distance substantially greater than said increase in amplitude and in a direction to increase the resistance to turning offered by said spring means.
  • a body structure including a cylinder, a piston reciprocable within said cylinder, a. crankshaft rotatable with respect to said body, supporting structure for turnably supporting said body in a plane normal to the axis of rotation of said crankshaft, said body being substantially dynamically balanced about its turning axis, a piston abutment, spring means between said body and abutment for limiting turning of the body with respect to said supporting structure, means for applying fluid pressure to said piston abutment, a valve for controlling said fluid pressure, and
  • valve for controlling said fluid pressure, means for adjusting said valve in response to variations in the turning amplitude of said body so that an increase in said amplitude results in an increase in the fluid pressure, and liquid bufler means for positively limiting said amplitude.
  • a body structure including a cylinder, 9. piston reciprocable within said cylinder, a crankshaft rotatable with respect to said body, supporting structure for turnably supporting said body in a plane normal to the axis of rotation of said crankshaft, said body being substantially dynamically balanced about its turning axis, a piston abutment, spring means between said body and abutment for limiting turning of the body with respect to said supporting structure, means for applying fluid pressure to said piston abutment, a slide valve for controlling said fluid pressure.
  • valve means connecting said valve to said body so that the valve is moved by turning of the body, the valve being arranged to increase the pressure upon an increase in the turning amplitude of the body, and means associated with said valve providing a liquid bufler for positively limiting movement of said valve and the turning amplitude of said body connected thereto.
  • a body structure including a cylinder, a piston reciprocable within said cylinder, 9. crankshaft rotatable with respect to said body, supporting .mounted on said eccentric structure for turncbly supporting said body in s. plane normal to the axis of rotation of said crankshaft-an eccentric rotatable with said crankshaft, a member eccentrically jam-nailed on said eccentric, and a balancing weight rotatably mounted on said member and reciprccably guided with respect to said body.
  • a dynamically balanced crankmeans for limiting turning of said body tire with respect to said supporting structure.

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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)
  • Transmission Devices (AREA)
  • Reciprocating Pumps (AREA)
  • Vibration Prevention Devices (AREA)
US219497A 1937-07-21 1938-07-16 Piston machine with crankshaft Expired - Lifetime US2235160A (en)

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SE517182X 1937-07-21

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DE (2) DE723713C (fr)
FR (1) FR840855A (fr)
GB (2) GB517182A (fr)

Cited By (27)

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US2706607A (en) * 1950-03-31 1955-04-19 British Petroleum Co Supporting of engines and other machinery
US2767411A (en) * 1951-10-03 1956-10-23 Pittsburgh Steel Co Nail making machine
US3178964A (en) * 1960-06-21 1965-04-20 Renault Engine propulsion units
US3282542A (en) * 1963-07-12 1966-11-01 Yarrow & Co Ltd Anti-vibration mounting
US3468190A (en) * 1967-06-05 1969-09-23 Ford Motor Co Mechanism for balancing reciprocating masses of internal combustion engines
US4407169A (en) * 1979-11-29 1983-10-04 Menen Balan R Counterweight system for positive displacement piston type device
EP0093530A2 (fr) * 1982-04-26 1983-11-09 National Research Development Corporation Dispositif de montage pour système oscillant
US4616608A (en) * 1983-12-01 1986-10-14 Honda Giken Kogyo Kabushiki Kaisha Balancer device for a reciprocating engine
US4656981A (en) * 1983-08-24 1987-04-14 Kawasaki Jukogyo Kabushiki Kaisha Balancing mechanism for reciprocating piston engine
US4781156A (en) * 1987-12-09 1988-11-01 Ford Motor Company Engine vibration balancer
US4819593A (en) * 1988-04-28 1989-04-11 Briggs & Stratton Corporation Pivoting balancer system
US4926810A (en) * 1988-10-05 1990-05-22 Ford Motor Company Engine vibration balancer
US5560267A (en) * 1994-06-21 1996-10-01 Borg-Warner Automotive, Inc. Camshaft vibration damper
US5755194A (en) * 1995-07-06 1998-05-26 Tecumseh Products Company Overhead cam engine with dry sump lubrication system
US6223713B1 (en) 1996-07-01 2001-05-01 Tecumseh Products Company Overhead cam engine with cast-in valve seats
US20030121489A1 (en) * 2001-12-28 2003-07-03 Rotter Terrence M. Balance system for single cylinder engine
US20040007198A1 (en) * 2002-07-11 2004-01-15 Bonde Kevin G. Crankcase cover with oil passages
US20040011010A1 (en) * 2002-07-18 2004-01-22 Rotter Terrence M. Panel type air filter element with integral baffle
US6684846B1 (en) 2002-07-18 2004-02-03 Kohler Co. Crankshaft oil circuit
US6732701B2 (en) 2002-07-01 2004-05-11 Kohler Co. Oil circuit for twin cam internal combustion engine
US6739304B2 (en) 2002-06-28 2004-05-25 Kohler Co. Cross-flow cylinder head
US6742488B2 (en) 2002-07-18 2004-06-01 Kohler Co. Component for governing air flow in and around cylinder head port
US20040211384A1 (en) * 2003-04-28 2004-10-28 Karl Glinsner Mass balancing for internal combustion engine
US6837207B2 (en) 2002-07-18 2005-01-04 Kohler Co. Inverted crankcase with attachments for an internal combustion engine
US6978751B2 (en) 2002-07-18 2005-12-27 Kohler Co. Cam follower arm for an internal combustion engine
US20080041174A1 (en) * 1999-06-04 2008-02-21 Michael Lagaly Bearing Structure for a Reciprocating Shaft in a Reciprocating Saw
AT509820B1 (de) * 2010-04-23 2012-10-15 Steyr Motors Gmbh Hubkolben-verbrennungskraftmaschine mit massenausgleichsvorrichtung

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DE891804C (de) * 1950-04-07 1953-10-01 Gertrud Schnuerle Zweitakt-Brennkraftmaschine
DE2142998C2 (de) * 1971-08-27 1982-08-19 Klöckner-Humboldt-Deutz AG, 5000 Köln Vorrichtung zum Ausgleich der Massenkräfte zweiter Ordnung bei Hubkolbenmaschinen
US4481918A (en) * 1981-10-15 1984-11-13 Triumph Motorcycles (Meriden) Limited Means for reducing vibration in reciprocating engines
FR2675223A1 (fr) * 1991-04-15 1992-10-16 Peugeot Dispositif d'equilibrage dynamique pour un moteur a combustion interne a pistons alternatifs.
DE4217633C1 (en) * 1992-05-28 1993-05-13 Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De Balance weights for IC engine - has weights mounted on eccentric ball-races on either side of each crank
CN103335060B (zh) * 2013-06-07 2015-12-16 宁波念初机械工业有限公司 一种中高速中大型压力机的动平衡机构
DE102021207144B4 (de) 2021-07-07 2023-03-02 Bernd Rodemüller Zweitakt-Hubkolbenmotor mit genau einem Arbeitszylinder und Massenausgleich

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DE368772C (de) * 1923-02-12 Jules Leroy Vorrichtung zur Umwandlung der geradlinigen Kolbenbewegung in eine Drehbewegung der Welle bei Motoren
US947233A (en) * 1909-03-29 1910-01-25 Henry Charles Hammond Device for converting reciprocating into rotary motion.
GB191507258A (en) * 1914-05-20 1900-01-01 Page Stoakes Jones Ambrose Improved Mechanism for Converting Rotary Motion into Reciprocating Motion and vice versa.
GB122345A (en) * 1918-04-30 1919-01-23 Hugo Moren Improvements in Balancing Internal Combustion Engines.

Cited By (37)

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US2706607A (en) * 1950-03-31 1955-04-19 British Petroleum Co Supporting of engines and other machinery
US2767411A (en) * 1951-10-03 1956-10-23 Pittsburgh Steel Co Nail making machine
US3178964A (en) * 1960-06-21 1965-04-20 Renault Engine propulsion units
US3282542A (en) * 1963-07-12 1966-11-01 Yarrow & Co Ltd Anti-vibration mounting
US3468190A (en) * 1967-06-05 1969-09-23 Ford Motor Co Mechanism for balancing reciprocating masses of internal combustion engines
US4407169A (en) * 1979-11-29 1983-10-04 Menen Balan R Counterweight system for positive displacement piston type device
EP0093530A2 (fr) * 1982-04-26 1983-11-09 National Research Development Corporation Dispositif de montage pour système oscillant
EP0093530A3 (en) * 1982-04-26 1984-12-12 National Research Development Corporation A mounting for a vibrating system
US4656981A (en) * 1983-08-24 1987-04-14 Kawasaki Jukogyo Kabushiki Kaisha Balancing mechanism for reciprocating piston engine
US4616608A (en) * 1983-12-01 1986-10-14 Honda Giken Kogyo Kabushiki Kaisha Balancer device for a reciprocating engine
US4781156A (en) * 1987-12-09 1988-11-01 Ford Motor Company Engine vibration balancer
US4819593A (en) * 1988-04-28 1989-04-11 Briggs & Stratton Corporation Pivoting balancer system
US4926810A (en) * 1988-10-05 1990-05-22 Ford Motor Company Engine vibration balancer
US5560267A (en) * 1994-06-21 1996-10-01 Borg-Warner Automotive, Inc. Camshaft vibration damper
US5755194A (en) * 1995-07-06 1998-05-26 Tecumseh Products Company Overhead cam engine with dry sump lubrication system
US5979392A (en) * 1995-07-06 1999-11-09 Tecumseh Products Company Overhead cam engine with integral head
US5988135A (en) * 1995-07-06 1999-11-23 Tecumseh Products Company Overhead vertical camshaft engine with external camshaft drive
US6032635A (en) * 1995-07-06 2000-03-07 Tecumseh Products Company Overhead cam engine with integral head
US6223713B1 (en) 1996-07-01 2001-05-01 Tecumseh Products Company Overhead cam engine with cast-in valve seats
US8141444B2 (en) * 1999-06-04 2012-03-27 Black & Decker Inc. Bearing structure for a reciprocating shaft in a reciprocating saw
US20080041174A1 (en) * 1999-06-04 2008-02-21 Michael Lagaly Bearing Structure for a Reciprocating Shaft in a Reciprocating Saw
US20030121489A1 (en) * 2001-12-28 2003-07-03 Rotter Terrence M. Balance system for single cylinder engine
US6874458B2 (en) 2001-12-28 2005-04-05 Kohler Co. Balance system for single cylinder engine
US6739304B2 (en) 2002-06-28 2004-05-25 Kohler Co. Cross-flow cylinder head
US6732701B2 (en) 2002-07-01 2004-05-11 Kohler Co. Oil circuit for twin cam internal combustion engine
US6837206B2 (en) 2002-07-11 2005-01-04 Kohler Co. Crankcase cover with oil passages
US20040007198A1 (en) * 2002-07-11 2004-01-15 Bonde Kevin G. Crankcase cover with oil passages
US6978751B2 (en) 2002-07-18 2005-12-27 Kohler Co. Cam follower arm for an internal combustion engine
US6837207B2 (en) 2002-07-18 2005-01-04 Kohler Co. Inverted crankcase with attachments for an internal combustion engine
US6752846B2 (en) 2002-07-18 2004-06-22 Kohler Co. Panel type air filter element with integral baffle
US6742488B2 (en) 2002-07-18 2004-06-01 Kohler Co. Component for governing air flow in and around cylinder head port
US6684846B1 (en) 2002-07-18 2004-02-03 Kohler Co. Crankshaft oil circuit
US20040011010A1 (en) * 2002-07-18 2004-01-22 Rotter Terrence M. Panel type air filter element with integral baffle
US20040211384A1 (en) * 2003-04-28 2004-10-28 Karl Glinsner 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
AT509820B1 (de) * 2010-04-23 2012-10-15 Steyr Motors Gmbh Hubkolben-verbrennungskraftmaschine mit massenausgleichsvorrichtung
US8746200B2 (en) 2010-04-23 2014-06-10 Steyr Motors Gmbh Reciprocating-piston internal combustion engine with mass balancing device

Also Published As

Publication number Publication date
GB517182A (en) 1940-01-23
GB517363A (en) 1940-01-26
DE723713C (de) 1942-08-10
DE742776C (de) 1943-12-10
FR840855A (fr) 1939-05-05

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