WO1991002911A1 - Mecanisme alternatif, notamment pour moteurs a piston alternatif - Google Patents

Mecanisme alternatif, notamment pour moteurs a piston alternatif Download PDF

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Publication number
WO1991002911A1
WO1991002911A1 PCT/EP1990/001244 EP9001244W WO9102911A1 WO 1991002911 A1 WO1991002911 A1 WO 1991002911A1 EP 9001244 W EP9001244 W EP 9001244W WO 9102911 A1 WO9102911 A1 WO 9102911A1
Authority
WO
WIPO (PCT)
Prior art keywords
crankshaft
push rod
pivot
housing
crank
Prior art date
Application number
PCT/EP1990/001244
Other languages
German (de)
English (en)
Inventor
Motoren Werke Aktiengesellschaft Bayerische
Original Assignee
Fischer, Gert
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
Application filed by Fischer, Gert filed Critical Fischer, Gert
Publication of WO1991002911A1 publication Critical patent/WO1991002911A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
    • F01B9/026—Rigid connections between piston and rod; Oscillating pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
    • F01B9/023—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft of Bourke-type or Scotch yoke
    • 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
    • F02B75/24—Multi-cylinder engines with cylinders arranged oppositely relative to main shaft and of "flat" type
    • F02B75/246—Multi-cylinder engines with cylinders arranged oppositely relative to main shaft and of "flat" type with only one crankshaft of the "pancake" type, e.g. pairs of connecting rods attached to common crankshaft bearing
    • 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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H21/00—Gearings comprising primarily only links or levers, with or without slides
    • F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
    • F16H21/16—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for interconverting rotary motion and reciprocating motion
    • F16H21/18—Crank gearings; Eccentric gearings
    • F16H21/36—Crank gearings; Eccentric gearings without swinging connecting-rod, e.g. with epicyclic parallel motion, slot-and-crank motion

Definitions

  • the invention is based on DE-PS 883 540.
  • This document shows and describes lifting gears designed on the kinematic basis of a pair of cardan circles. If a small circle rolls without slip in a circle twice as large, then two circumferential points lying opposite each other on the diameter of the small circle execute rectilinear reciprocating movements directed orthogonally.
  • the connection of a push rod of a reciprocating piston machine via one of the circumferential points to an output shaft can be carried out either by the combination of two counter-controlled eccentrics or by a crankshaft with an eccentric.
  • the other circumferential point provided on one of the eccentrics interacts with a guide slide that is slidably guided in a machine housing.
  • DE-PS 883 540 shows how complex, however, realizable mass balancing can be in a cardan circuit pair or hypocycloid lifting gear.
  • this known lifting gear which instead of an orthogonal guide slide has a gear made of a ring gear with a pinion for counter-eccentric control, the circumferential point of the pinion which causes the oscillating movement of a push rod with a piston is regarded as a first center of mass , which is assigned a counter mass on the other circumferential point that oscillates perpendicular to it.
  • the known lifting gear comprises a primary eccentric connected to an output shaft in a rotationally fixed manner, on which a secondary eccentric connected to connecting rods is movably assigned in opposite directions via an auxiliary gear to the primary eccentric.
  • a secondary eccentric connected to connecting rods is movably assigned in opposite directions via an auxiliary gear to the primary eccentric.
  • the center of gravity of the aforementioned masses can be placed in the center of the primary eccentric by means of a first additional counter-mass on the secondary eccentric.
  • the center of gravity of the entire system is placed in the geometric axis of the main shaft or the ring gear by means of a second counterweight on the primary eccentric, whereby a statically and dynamically balanced lifting gear is achieved.
  • the counterweights used for dynamic compensation are subdivided into counterbalance pairs which are arranged essentially symmetrically to the push rod plane. This results disadvantageously in a relatively wide-construction and elaborately designed lifting gear.
  • Another disadvantage of this lifting gear is the additional mass, which, in addition to the oscillating mass, also increases the first and second counter masses, which makes the known lifting gear relatively heavy.
  • the invention has for its object to achieve a complete mass balance in a generic lifting gear in a simple manner with little construction.
  • the basic idea of the invention is to connect the disk-like pivot connecting a push rod to a crankshaft in a rotationally fixed manner with the pivot which engages slidably in transverse straight guides and to give these pivot overall a dimensioning which serves the oscillating mass balance, the crankshaft for rotational mass balance is provided with correspondingly arranged counterweights so that the overall center of gravity of the oscillating and rotating masses lies in the axis of the crankshaft. Since the guide and compensating pivots cause a system-specific rotation of the push rod or connecting pivot, which is opposite to the direction of rotation of the crankshaft, an expensive auxiliary gear mechanism consisting of a ring gear and pinion can advantageously be omitted.
  • crankshaft with a relatively large crank pin spacing offers the advantage of a relatively large distance between the two compensating and push rod pivot pins arranged diametrically eccentrically with respect to one another with a relatively small overlap for the mutual rotationally fixed connection. With this arrangement, an effective mass balance is achieved even with a small construction effort for the compensating pivots by a relatively large center of gravity.
  • guide blocks with sliding surfaces are preferably assigned to these pivot pins.
  • Fig. 1 is a double piston push rod with a
  • Fig. 2 the lifting gear in plan view.
  • a lifting gear 1 for a piston engine designed as a boxer engine comprises a common push rod 5 for pistons 3 in cylinders 4 arranged in alignment with one another.
  • This has a central receptacle 6 for the rotatable mounting of a disk-like pivot 7, which over an eccentric bearing bore 8 is rotatably connected to the crank pin 9 of a crankshaft 11 mounted in the housing 10 of the reciprocating piston machine 2.
  • the lifting gear 1, designed in the manner of a pair of cardan circles or a hypocycloid gear, on the push rod pivot 7 comprises, on both sides in the crank pin region, non-rotatably engaging pivot 12, which cooperate via guide stones 13 with straight guide 14 fixed to the housing and directed transversely to the oscillating push rod 5.
  • the aforementioned pivot pins 12 are designed as solid disk bodies and serve as such to compensate for the oscillating masses which are formed by the push rod 5, the pistons 3 arranged at both ends and the push rod pivot pin 7. To increase the compensating effect, the compensating pivot pins 12 can be provided with heavy metal inserts 15.
  • the latter is designed except for an area 16 for arranging a bearing bore 8 for the crank pin 9 and for a rotationally fixed connection with the compensating pivot pin 12.
  • the pivots 7 and 12 which are arranged diametrically eccentrically to one another, only overlap via the small area 16 for the rotationally fixed connection.
  • the area 16 of the push rod pivot 7 contributes as a rotating part to the action of the compensating pivot 12.
  • crankshaft 11 In order to compensate for the rotating masses of the lifting gear 1, the crankshaft 11 has counterweights 18 which act diametrically arranged on the compensating pivot pins 12 equipped with guide stones 13 and which have a common center of gravity of the rotating and oscillating lifting gear parts in the axis 17 of the crankshaft 11.
  • crankshaft 11 is constructed and has the compensating pivot 12 on the crank cheeks 19 which are arranged axially adjacent to one another and over the The outer circumference serves as a bearing journal for rotatable arrangement in crankshaft bearings 20 in the housing 10 of the reciprocating machine 2.
  • the two crank cheeks 19 are connected by the crank pin 9 pressed into each crank cheek 19, which passes through the compensating pivot pin 12 and the push rod pivot pin 7.
  • the counterweights 18 mentioned above are arranged on each crank arm 19 on the output shaft side.
  • the housing 10 can be formed from halves divided over the middle of the crankshaft bearing 20, each with one of the cylinders 4 arranged in alignment with one another.
  • each half of the housing 10 can have linear guides 14, which are arranged adjacent to the respective crankshaft bearing 20, with slideways 21 for the guide blocks 13 on the compensating pivot pin 12.
  • each crankshaft bearing 20, including the adjacent sliding tracks 21 can also be formed in a one-piece part 22 separate from the housing 10, the parts 22 that can be fixed between the mutually braced halves of the housing 10 are preassembled on the bearing journals of the respective crank web 19 of the built crankshaft 11
  • This configuration is suitable for pistons 3 arranged in one piece with the push rod 5.
  • the invention is suitable for both single and multi-cylinder engines, for. B. with four or eight cylinders.

Landscapes

  • 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)

Abstract

L'invention concerne un mécanisme alternatif, notamment pour des moteurs à piston alternatif, se présentant sous la forme d'une paire de cercles de cardan ou d'un engrenage hypocycloïdal, dans lequel l'équilibrage total des masses est réalisé simplement et avec peu de composants structuraux. A cet effet, un tourillon discoïde (7) qui relie une bielle (5) à un vilebrequin (11) est relié de manière solidaire en rotation à des tourillons (12) qui s'engagent de manière coulissante dans des glissières transversales, et tous ces tourillons (12) sont dimensionnés de manière à assurer l'équilibre des masses en vibration. L'équilibre des masses en rotation est réalisé grâce au fait que le vilebrequin (11) est équipé de contrepoids disposés de manière appropriée, de sorte que le centre de gravité de toutes les masses en vibration et en rotation se situe dans l'axe du vilebrequin.
PCT/EP1990/001244 1989-08-22 1990-07-31 Mecanisme alternatif, notamment pour moteurs a piston alternatif WO1991002911A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19893927593 DE3927593A1 (de) 1989-08-22 1989-08-22 Hubgetriebe, insbesondere fuer hubkolbenmaschinen
DEP3927593.0890822 1989-08-22

Publications (1)

Publication Number Publication Date
WO1991002911A1 true WO1991002911A1 (fr) 1991-03-07

Family

ID=6387556

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1990/001244 WO1991002911A1 (fr) 1989-08-22 1990-07-31 Mecanisme alternatif, notamment pour moteurs a piston alternatif

Country Status (2)

Country Link
DE (1) DE3927593A1 (fr)
WO (1) WO1991002911A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2470808A (en) * 2009-05-01 2010-12-08 Keith Gordon Hall Positive Displacement Machines with balanced hypocycloidal drive

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4108311C2 (de) * 1991-03-14 2000-09-21 Bayerische Motoren Werke Ag Hypozykloiden-Hubgetriebe für Hubkolbenmaschinen in Boxerbauart
DE4139716A1 (de) * 1991-12-02 1993-06-03 Bayerische Motoren Werke Ag Hubkolbenmaschine, insbesondere brennkraftmaschine, mit hypozykloidischem kurbelgetriebe
DE4142385A1 (de) * 1991-12-20 1993-06-24 Bayerische Motoren Werke Ag Mehrzylindrige hubkolbenmaschine mit einem hypozykloid-hubgetriebe, insbesondere brennkraftmaschine
DE9300052U1 (de) * 1993-01-05 1993-03-04 Kropp, Jürgen, 2300 Kiel Kurbelwellengetriebe mit Ruhelage
DE19504890A1 (de) * 1995-02-14 1996-08-22 Bayerische Motoren Werke Ag Hubkolbenmaschine mit in Kurbelwellenrichtung in einem Maschinengehäuse benachbarten Zylindern
DE19509155A1 (de) * 1995-03-14 1996-09-19 Bayerische Motoren Werke Ag Hypozykloidisches Kurbelgetriebe für Hubkolbenmaschinen, insbesondere für Brennkraftmaschinen mit gegenüberliegenden Zylinderreihen
DE19509156A1 (de) * 1995-03-14 1996-09-19 Bayerische Motoren Werke Ag Verbindungsstange zwischen Kolben und Hubtriebwerk einer Hubkolbenmaschine, insbesondere Brennkraftmaschine mit hypozykloidischem Hubtriebwerk
DE19607920A1 (de) * 1996-03-01 1997-09-04 Bayerische Motoren Werke Ag Hypozykloidisches Kurbelgetriebe für Hubkolbenmaschinen, insbesondere Brennkraftmaschinen
IT1310116B1 (it) * 1999-07-16 2002-02-11 Fiat Auto Spa Perfezionamenti relativi ai motori alternativi a combustione internaprovvisti di un manovellismo ipocicloidale.

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1003222A (fr) * 1946-12-18 1952-03-17 Dispositif de transformation de mouvement et machines (moteurs à explosion, notamment) utilisant ce dispositif
GB1060372A (en) * 1963-11-13 1967-03-01 Bancroft Charles Improvements in or relating to reciprocating compressors, pumps, engines and the like
GB1227399A (fr) * 1968-08-13 1971-04-07
DE2720284A1 (de) * 1977-05-05 1978-12-21 Franz Prof Dipl Ing Huf Schubkurbel-system-baureihe
US4173151A (en) * 1977-06-30 1979-11-06 Grundy Reed H Motion translating mechanism

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2205975A5 (fr) * 1972-11-08 1974-05-31 Erap Elf Entr Rech Activ Petro
DE7600908U1 (de) * 1976-01-15 1976-05-26 Oppelcz, Ludwig Explosionsmotor mit sich linear bewegendem kurbelzapfen
DE3619488A1 (de) * 1986-02-27 1987-03-05 Toan Dat Tran Kurbelgetriebe-geradeschubsystem

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1003222A (fr) * 1946-12-18 1952-03-17 Dispositif de transformation de mouvement et machines (moteurs à explosion, notamment) utilisant ce dispositif
GB1060372A (en) * 1963-11-13 1967-03-01 Bancroft Charles Improvements in or relating to reciprocating compressors, pumps, engines and the like
GB1227399A (fr) * 1968-08-13 1971-04-07
DE2720284A1 (de) * 1977-05-05 1978-12-21 Franz Prof Dipl Ing Huf Schubkurbel-system-baureihe
US4173151A (en) * 1977-06-30 1979-11-06 Grundy Reed H Motion translating mechanism

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2470808A (en) * 2009-05-01 2010-12-08 Keith Gordon Hall Positive Displacement Machines with balanced hypocycloidal drive

Also Published As

Publication number Publication date
DE3927593A1 (de) 1991-02-28

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