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WO1990003504A1 - Vilebrequin - Google Patents

Vilebrequin Download PDF

Info

Publication number
WO1990003504A1
WO1990003504A1 PCT/EP1989/000377 EP8900377W WO9003504A1 WO 1990003504 A1 WO1990003504 A1 WO 1990003504A1 EP 8900377 W EP8900377 W EP 8900377W WO 9003504 A1 WO9003504 A1 WO 9003504A1
Authority
WO
WIPO (PCT)
Prior art keywords
crankshaft
rotation
eccentric
beta
wheel
Prior art date
Application number
PCT/EP1989/000377
Other languages
German (de)
English (en)
Inventor
Eduard Igenbergs
Original Assignee
Igenwert Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE19883832250 external-priority patent/DE3832250A1/de
Application filed by Igenwert Gmbh filed Critical Igenwert Gmbh
Publication of WO1990003504A1 publication Critical patent/WO1990003504A1/fr

Links

Classifications

    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • 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
    • F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
    • F02B41/02—Engines with prolonged expansion
    • F02B41/04—Engines with prolonged expansion in main cylinders

Definitions

  • the double crankshaft is a device by means of which the linear movement of a piston is converted into a rotary movement.
  • the "simple crankshaft” is used for this.
  • the up and down movement of the piston is controlled by the crankshaft, the movement of the piston in the cylinder corresponds to a simple angular function.
  • the double crankshaft was developed to effect a different sequence of piston movements with the aim of achieving improved combustion in the internal combustion engine combined with a higher torque.
  • a lever was inserted between the eccentric of the crankshaft and the connecting rod bearing, which lever rotates around the bearing on the eccentric of the crankshaft and whose movement is coupled with the rotation of the crankshaft.
  • This coupling can take place in the same or opposite direction to the crankshaft direction of rotation. A different reduction ratio is possible and there can be a phase shift between the movements.
  • the intermediate piece which is connected between the crankshaft and the connecting rod, is positively guided by the crankshaft through a mechanical coupling (e.g. gearwheel gear).
  • the crankshaft and the intermediate piece run at the angular velocities Omega 1 and Omega 2 in the same or opposite directions and are shifted from one another by the phase angle ny.
  • Fig. 1 shows schematically the arrangement.
  • crank drive configurations that have a flat course of the piston stroke at top dead center and for which parameter values this then applies.
  • Fig. 2 shows qualitatively such a desired piston profile over the crank angle.
  • the torque results in force x lever arm.
  • the component acting in the connecting rod axis is determined from the gas force acting on the piston and multiplied by the lever arm acting for this force to the crankshaft.
  • the force is broken down in the x and y directions and the lever arms are taken parallel to the axes, so that the total torque is composed of two parts.
  • the pressure p (phi) prevailing in the combustion chamber is calculated using the formulas of the ideal cycle according to Setzer.
  • M d F * tan (beta) * (r 1 * cos (phi) + r 2 * cos (psi)) + F *
  • tan (beta) sin (beta) / cos (beta)
  • beta To get a function that only depends on phi, beta must be eliminated.
  • M d F * tan (beta) * r * cos (phi) + F * r * sin (phi)
  • tan (beta) sin (beta) / cos (beta)
  • r y (phi) r 1 * cos (phi) + r 2 * cos (psi)
  • the intermediate rod must run in the opposite direction to the crankshaft.
  • L which is the ratio of the crankshaft eccentric length plus the intermediate rod length to the length of the connecting rod
  • phase shift between the rotational movement of the crankshaft and the rotational movement of the intermediate rod if one observes a flat course of the piston movement in the vicinity of the top dead center wishes.
  • 1: 1 coupling between the crankshaft rotation and the rotation of the intermediate rod is suitable for internal combustion engines.
  • the significantly higher torque of the modified engine can also be reduced if design measures do not allow an ideal crank mechanism with the same lengths of r 1 and r 2 . With slight deviations of the two lengths, a flat course of the piston at top dead center is no longer possible, but the torque remains higher.
  • Fig. 9 shows the dependence of the phase shift ny opt on the rod ratio. To smooth the top
  • the upper graph shows the piston curve over 2 * pi or, in the case of an irregular piston curve, over 6 * pi -12 * pi crank angle.
  • the lower graphic also shows the course of the joint between the intermediate piece and the connecting rod.
  • the inner circle corresponds to the crankshaft eccentricity
  • the outer circle has the radius of the lengths of the crankshaft eccentricity r 1 and intermediate shaft r 2 .
  • the double crankshaft is a crankshaft with eccentrics on which bearings are attached. These bearings are used as connecting rod bearings in conventional crankshafts. With the double crankshaft, another crank is mounted in the eccentrics. The rotation of this crank in the eccentrics is coupled to the rotation of the crankshaft.
  • the system is shown in FIG.
  • the fixed bearing (1) and the wall of the cylinder (8) are in a fixed, unchangeable relation, as they are e.g. is caused by installation in a housing.
  • the eccentric (2) rotates around the main bearing (1) with the length r 1 , at the end of which is the eccentric bearing (3).
  • the eccentric (4) with the length r 2 rotates around this.
  • the end of this eccentric (5) is again designed as a bearing for the connecting rod (6) with the length r 3 , which establishes the connection to the piston bearing (7).
  • the angular velocity of the crankshaft eccentric a ⁇ / dt (9) and the eccentric bearing is firmly coupled by a device.
  • the two orbital frequencies are preferably the same and are shifted from one another by a phase u.
  • crankshaft is a conventional crankshaft as used, for example, in internal combustion engines (piston engines) det.
  • the bearings referred to as connecting rod bearings in a conventional crankshaft serve as crank bearings.
  • the rotation of the cranks in the crank bearings is coupled with the rotation of the crankshaft for each crank via a fixed reduction.
  • This reduction is preferably generated by a gear transmission.
  • the coupling is always such that the same overall configuration occurs during the same phase of the processes in the combustion chamber.
  • a connecting rod bearing is attached to the crank, which is mounted in the eccentric, then the movement of a piston can be controlled from this bearing via a connecting rod, which piston is movable in a cylinder and whose end facing away from the connecting rod is the combustion chamber.
  • the eccentricity of the eccentric of the crankshaft and its angle in relation to a given coordinate system, the length of the crank and the coupling of its rotation with the rotation of the crankshaft as well as the length of the connecting rod are now used to control the piston stroke in a new way as a function of time. In this way, an improved combustion process and a higher torque can be achieved with an appropriate choice of the parameters mentioned.
  • the coupling of the movement of the crankshaft and the eccentric bearing can be done by a gear transmission.
  • a gear is firmly connected to the crankshaft bearing, so it always has the same position with respect to the housing in which the crankshaft bearing and the cylinder are installed.
  • a second gear which meshes with the first, is fixed to the axle of the eccentric bearing connected. In this way, a rotation of the eccentric bearing coupled to the rotation of the crankshaft is achieved.
  • the double crankshaft consists of a simple crankshaft, in which the connecting rod bearing mounted on the crankshaft eccentric is used to support an additional lever that carries at the other end of the connecting rod bearing.
  • This additional lever is set in a circular motion around the bearing attached to the crankshaft eccentric. This circular movement is firmly coupled to the crankshaft rotation.
  • the bearing on the crankshaft eccentric can in turn be designed as an eccentric, which is mounted in the crankshaft eccentric and also rotates coupled with the crankshaft rotation.
  • the coupling of the rotation of the additional rod or of the eccentric and the crankshaft can have a different reduction ratio and a different phase angle.
  • the double crankshaft is particularly suitable for effecting a flat course of the piston movement in the vicinity of the top dead center by superimposing the rotation of the crankshaft and additional rod or the eccentric.
  • a flat course of the piston near top dead center is only brought about by the double crankshaft according to one or more of the preceding claims if the direction of rotation of the additional rod or of the eccentric is opposite to the direction of rotation of the crankshaft.
  • the flat course of the piston near top dead center is only achieved if the phase angle between crankshaft rotation and the rotation of the additional rod or the eccentric has a certain value. With a given arrangement, this angle only depends on the standing ratio.
  • This rod ratio is the ratio of the sum of the length of the eccentric of the crankshaft and the length of the additional rod or eccentric to the length of the connecting rod.
  • An engine with a double crankshaft according to one or more of the preceding training forms a significant in the case that the direction of rotation is opposite and the optimal phase angle from the rod ratio or has been determined with the aid of a calculation method, with the same energy supply as with the conventional Otto engine higher maximum torque.
  • the piston stroke h is calculated from the following parts: a: Part of the crankshaft crank
  • the case ⁇ + ( ⁇ + ⁇ ) means the rectified rotation.
  • the case ⁇ - ( ⁇ + ⁇ ) the opposite direction.
  • ⁇ is the phase angle between the two rotations. 15 shows examples of the rectified rotation.
  • Fig. 16 shows examples of the opposite rotation.
  • crankshaft arrangement shows an embodiment of the crankshaft arrangement according to the invention.
  • fixed wheels 100 are arranged on the crankshaft bearings 102 in a rotationally fixed manner.
  • Unwinding wheels 110 which roll on the fixed wheels 100, are rotatably supported in the crankshaft 112, the unwinding wheels 110 being positively guided by the crankshaft 112 when the crankshaft 112 rotates.
  • a drive wheel 120 is also provided on the shaft of each roll-off wheel 110 and performs the same rotational movements as the roll-off wheel 110.
  • the drive wheels 120 drive inner wheels 130 which are connected to the crank pins 132. If the crankshaft 112 now rotates about its axis, the rolling wheels 110, one of which is arranged on one side, must each roll on the associated fixed wheel 100. In this case, the drive wheels 120 are driven and in turn drive the inner wheels 130, which results in an opposite movement synchronous with the crankshaft rotation for the inner wheels.
  • a further gear mechanism for generating the synchronous, opposite movement is shown in FIG. 22.
  • an at least partially hollow cylindrical outer dimension 210 is provided, which is driven by at least one correction wheel 208 on its outer circumference.
  • An inner wheel 206 runs on the inner circumference of the outer wheel 210 because it rotates about its own axis 204 and at the same time about the crankshaft axis 202 of the crankshaft 200.
  • FIG. 23 shows a similar embodiment of the crankshaft arrangement to FIG. 21.
  • the unwinding wheels 310 run on the fixed wheels 300 connected to the crankshaft bearings 302, which are rotatably mounted in a crankshaft element 312.
  • the shaft of each rolling wheel 310 is connected to an eccentric 330, wherein each of the two eccentric legs 331 is connected to a shaft of an opposite pair of drive wheels 310, 311 and an eccentric central part 332 extends between the eccentric legs eccentrically to the common axis of both shafts.
  • ⁇ is the phase angle between the two rotations.
  • 15 shows examples of the directional rotation.
  • Fig. 16 shows examples of the opposite rotation.
  • FIG 21 shows an embodiment of the crankshaft arrangement according to the invention.
  • fixed wheels 100 are arranged on the crankshaft bearings 102 in a rotationally fixed manner.
  • Roll-off wheels 110 which roll on the fixed wheels 100, are rotatably mounted in the crankshaft 112, the roll-off wheels 110 being positively guided by the crankshaft 112 when the latter rotates.
  • the rolling wheels 110 can also be stored in compensating masses 114 which are firmly connected to the crankshaft 112.
  • a drive wheel 120 is also provided on the shaft of each roll-off wheel 110 and performs the same rotational movements as the roll-off wheel 110.
  • the drive wheels 120 drive inner wheels 130 which are connected to the crank pins 132. Now the crankshaft 112 rotates around hers
  • Axle the rolling wheels 110, one of which is arranged on one side, must each roll on the associated fixed wheel 100.
  • Drive wheels 120 drive and in turn drive the inner wheels 130, which results in an opposite movement synchronous to the crankshaft rotation for the inner wheels.
  • FIG. 22 Another transmission for generating the synchronous, counter-rotating movement is shown in FIG. 22.
  • an at least partially hollow cylindrical outer wheel 210 is provided, which is driven by at least one correction wheel 208 on its outer circumference.
  • An inner wheel 206 runs on the inner circumference of the outer wheel 210, which thereby rotates about its own axis 204 and at the same time about the crankshaft axis 202 of the crankshaft 200.
  • FIG. 23 shows a similar embodiment of the crankshaft arrangement to that of FIG. 21.
  • the unwinding wheels 310 run on the fixed wheels 300, which are non-rotatably connected to the crankshaft bearings 302 and which are in a crankshaft element 312 are rotatably mounted.
  • the shaft of each rolling wheel 310 is connected to an eccentric 330, wherein each of the two eccentric legs 331 is connected to a shaft of an opposite pair of drive wheels 310, 311 and an eccentric central part 332 extends between the eccentric legs eccentrically to the common axis of both shafts.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Ocean & Marine Engineering (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Transmission Devices (AREA)

Abstract

Ensemble de vilebrequin où des paliers agencés sur les excentriques dudit vilebrequin sont munis d'autres manivelles, la rotation de chacune desdites manivelles sur les excentriques étant couplée à la rotation du vilebrequin.
PCT/EP1989/000377 1988-09-22 1989-04-07 Vilebrequin WO1990003504A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19883832250 DE3832250A1 (de) 1987-10-09 1988-09-22 Doppelkurbelwelle
DEP3832250.1 1988-09-22

Publications (1)

Publication Number Publication Date
WO1990003504A1 true WO1990003504A1 (fr) 1990-04-05

Family

ID=6363517

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1989/000377 WO1990003504A1 (fr) 1988-09-22 1989-04-07 Vilebrequin

Country Status (1)

Country Link
WO (1) WO1990003504A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1774203A4 (fr) * 2004-06-29 2009-11-04 Thomas Mark Venettozzi Mecanisme de vilebrequin epitrochoide et procede
DE102020200699A1 (de) 2020-01-22 2021-07-22 Robert Bosch Gesellschaft mit beschränkter Haftung Verfahren zum Modellieren eines Verbrennungsprozesses

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR610029A (fr) * 1925-06-22 1926-08-28 Moteur à combustion interne à courses variables
FR617720A (fr) * 1926-04-20 1927-02-24 Moteur à combustion interne
FR642091A (fr) * 1927-10-07 1928-08-21 Perfectionnement apporté dans l'établissement des moteurs à quatre temps dans le but de prolonger la détente
US3861239A (en) * 1972-06-05 1975-01-21 Edward M Mcwhorter Internal combustion engine combustion control crankshaft

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR610029A (fr) * 1925-06-22 1926-08-28 Moteur à combustion interne à courses variables
FR617720A (fr) * 1926-04-20 1927-02-24 Moteur à combustion interne
FR642091A (fr) * 1927-10-07 1928-08-21 Perfectionnement apporté dans l'établissement des moteurs à quatre temps dans le but de prolonger la détente
US3861239A (en) * 1972-06-05 1975-01-21 Edward M Mcwhorter Internal combustion engine combustion control crankshaft

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1774203A4 (fr) * 2004-06-29 2009-11-04 Thomas Mark Venettozzi Mecanisme de vilebrequin epitrochoide et procede
AU2005260125B2 (en) * 2004-06-29 2011-08-11 Thomas Mark Venettozzi Epitrochoidal crankshaft mechanism and method
DE102020200699A1 (de) 2020-01-22 2021-07-22 Robert Bosch Gesellschaft mit beschränkter Haftung Verfahren zum Modellieren eines Verbrennungsprozesses
DE102020200699B4 (de) 2020-01-22 2022-01-27 Robert Bosch Gesellschaft mit beschränkter Haftung Verfahren zum Modellieren eines Verbrennungsprozesses

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