DE4205283C2 - Reciprocating piston engine with hypocycloidal crank mechanism, especially an internal combustion engine - Google Patents

Reciprocating piston engine with hypocycloidal crank mechanism, especially an internal combustion engine

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Publication number
DE4205283C2
DE4205283C2 DE19924205283 DE4205283A DE4205283C2 DE 4205283 C2 DE4205283 C2 DE 4205283C2 DE 19924205283 DE19924205283 DE 19924205283 DE 4205283 A DE4205283 A DE 4205283A DE 4205283 C2 DE4205283 C2 DE 4205283C2
Authority
DE
Germany
Prior art keywords
bearing
push rod
eccentric
reciprocating piston
arrow
Prior art date
Legal status (The legal status 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 status listed.)
Expired - Fee Related
Application number
DE19924205283
Other languages
German (de)
Other versions
DE4205283A1 (en
Inventor
Jiri Seidl
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bayerische Motoren Werke AG
Original Assignee
Bayerische Motoren Werke AG
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Filing date
Publication date
Application filed by Bayerische Motoren Werke AG filed Critical Bayerische Motoren Werke AG
Priority to DE19924205283 priority Critical patent/DE4205283C2/en
Publication of DE4205283A1 publication Critical patent/DE4205283A1/en
Application granted granted Critical
Publication of DE4205283C2 publication Critical patent/DE4205283C2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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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
    • 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
    • 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
    • F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups

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

Description

Die Erfindung geht gemäß dem Oberbegriff des Pa­ tentanspruches 1 von der DE-A-36 19 488 aus.The invention goes according to the preamble of Pa claim 1 from DE-A-36 19 488.

Bei dieser bekannten Hubkolbenmaschine sind zur oszillie­ renden Hubsteuerung orthogonal zueinander geführter Schubstangen auf einem Hubzapfen der Kurbelwelle zwei zu­ einander diametral und miteinander drehfest angeordnete Exzenter drehbeweglich vorgesehen. Diese Exzenter sind in den Lageraugen der Schubstangen jeweils mittelbar in zu den oszillierend gesteuerten Schubstangen quer bewegli­ chen Führungssteinen gelagert. Der Zweck dieser Einrich­ tung ist, quer zur Kurbeldrehachse aus Toleranzabweichun­ gen bewegter Bauteile des bekannten Kurbelgetriebes re­ sultierende Beanspruchung der jeweiligen Schubstangen- Kolben-Anordnung zu verringern.In this known reciprocating machine are for oscillation stroke control orthogonal to each other Push rods on a crankshaft crank pin two diametrically and rotatably arranged with each other Eccentric rotatably provided. These eccentrics are in the bearing eyes of the push rods each indirectly in the oscillatingly controlled push rods move transversely Chen guide stones stored. The purpose of this institution tion is transverse to the crank axis of rotation from tolerance deviations gene moving components of the known crank mechanism right resulting stress on the respective push rod Reduce piston arrangement.

Diese bekannte Anordnung zum Ausgleich von Toleranzabwei­ chungen durch relative Beweglichkeit miteinander an­ triebsfest verbundener Teile des Kurbelgetriebes verrin­ gert zwar im wesentlichen Biegebelastungen der Schub­ stange und Seitenkräfte an den Kolben, wie dies bei­ spielsweise mit anderen Mitteln teilweise auch bei den bekannten hypozykloidischen Kurbelgetrieben der DE-A-37 23 950 und der US-2,271,766 erzielt ist. Jedoch erfordert die bekannte Anordnung nach der eingangs genannten DE-A- 36 19 488 mit den in den Schubstangen quer zu deren Hubrichtungen schwing- bzw. verschiebebeweglich gelager­ ten Führungssteinen relativ großbauende Lageraugen, die bei nicht mehr in den Zylindern unterzubringenden Abmes­ sungen in nachteiliger Weise eine Hubkolbenmaschine von relativ großen Ausmaßen bedingen. Ferner geht damit eine Erhöhung der oszillierenden Masse jeder Schubstange ein­ schließlich der Masse des entsprechenden Ausgleichsge­ wichtes einher, wodurch das Gewicht der Hubkolbenmaschine sich erhöht.This known arrangement to compensate for tolerance deviation relative mobility with each other drive-connected parts of the crank mechanism Although the thrust essentially bends rod and side forces on the piston, like this at for example with other means, sometimes also with the known hypocycloidal crank mechanisms of DE-A-37 23 950  and US 2,271,766 is achieved. However requires the known arrangement according to the aforementioned DE-A- 36 19 488 with those in the push rods across them Stroke directions that can be moved or moved ten guide stones relatively large-build bearing eyes, the with dimensions no longer to be accommodated in the cylinders solutions disadvantageously a reciprocating machine from relatively large dimensions. Furthermore, one goes Increase the oscillating mass of each push rod finally the mass of the corresponding compensation ge important, which reduces the weight of the reciprocating machine increases.

Der Erfindung liegt die Aufgabe zugrunde, eine Hubkolben­ maschine der im Oberbegriff des Patentanspruches 1 be­ schriebenen Bauart so zu verbessern, daß die einem dyna­ mischen Ausgleich der Toleranzabweichungen dienende rela­ tive Beweglichkeit miteinander antriebsfest verbundener Teile des Kurbelgetriebes auf baulich einfache Weise zwi­ schen gegebenen Triebwerksteilen erreicht ist.The invention has for its object a reciprocating piston machine in the preamble of claim 1 be to improve the design so that the dyna mix compensation of tolerance deviations serving rela tive agility connected to each other Parts of the crank mechanism in a structurally simple way between given engine parts is reached.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, daß das Lagerauge eine den Exzenter aufnehmende Lagerbohrung aufweist mit in orthogonalen Richtungen unterschiedlich groß gewählten Lagerspielen, wobei das größere Lagerspiel in Querrichtung zur oszillierenden Schubstange gewählt ist.This object is achieved in that the bearing eye a bearing bore receiving the eccentric has different in orthogonal directions large camp games, the larger camp game selected in the transverse direction to the oscillating push rod is.

Mit der erfindungsgemäß baulich einfach erzielten Querbe­ weglichkeit des Exzenters in der ovalen Lagerbohrung der Schubstange genügt es, das den Exzenter unmittelbar in der ovalen Lagerbohrung aufnehmende Lagerauge der Schub­ stange in den Abmessungen lediglich auf die jeweilige Maschinenleistung abgestellt zu gestalten, so daß mit dem dadurch relativ kleinbauenden Lagerauge die Schubstange bevorzugt in den Zylindern untergebracht werden kann. Da­ mit lassen sich in vorteilhafter Weise sowohl die Au­ ßenmaße der Hubkolbenmaschine als auch die translatorisch und rotatorisch bewegten Massen des Kurbelgetriebes redu­ zieren.With the Querbe, which is structurally simple to achieve according to the invention movement of the eccentric in the oval bearing bore of the It is sufficient to push the eccentric directly in the thrust of the oval bearing bore receiving eye bar in size only to the respective Machine power turned off so that with the thereby relatively small bearing eye the push rod can preferably be accommodated in the cylinders. There  with both the Au dimensions of the reciprocating piston machine as well as the translational and rotationally moved masses of the crank mechanism redu adorn.

Anspruch 2 beschreibt einen bevorzugten Wert für das in Querrichtung zur Schubstange größere Lagerspiel, das in vorteilhafter Weise bei zuverlässiger hydrodynamischer Schmierung eine ausreichende Querbeweglichkeit des Exzen­ ters zuläßt, um die bei mittleren Schubstangenstellungen aus Toleranzabweichungen der Kurbelgetriebe-Bauteile her­ rührenden Querbelastungen an der mit den Kolben starr verbundenen Schubstange im wesentlichen zu vermeiden.Claim 2 describes a preferred value for the in Transverse direction to the push rod greater bearing play, which in advantageously with reliable hydrodynamic Lubrication sufficient lateral mobility of the eccentric ters allows for the middle push rod positions from tolerance deviations of the crank gear components touching transverse loads on the rigid with the pistons to essentially avoid connected connecting rod.

Die übrigen Ansprüche 3 mit 5 betreffen die Ausbildung der ovalen Lagerbohrung in der Schubstange. Bei den Aus­ gestaltungen nach den Ansprüchen 3 und 4 bildet jeweils die ovale Lagerbohrung in der Schubstange die Laufbahn für einen z. B. mit einem Gleitlagerring oder einem Wälz­ lager ausgerüsteten Exzenter. Bei der Ausgestaltung nach Anspruch 5 wird dagegen die ovale Lagerbohrung im Lager­ auge der Schubstange mittels zweier in der Außenkontur kreisrunder Lagerschalen erzielt, die jeweils von einem mittleren Innenkontur-Bereich aus zu den beiden umfängli­ chen Enden hin abnehmende Dicken aufweisen. Derartige La­ gerschalen mit einer kreisrunden Außenkontur und einer ovalen Innenkontur sind an sich im Stand der Technik be­ kannt.The remaining claims 3 to 5 relate to training the oval bearing hole in the push rod. With the Aus designs according to claims 3 and 4 respectively the oval bearing hole in the push rod the raceway for a z. B. with a plain bearing ring or a roller bearing equipped eccentric. When designing after Claim 5, however, is the oval bearing bore in the camp eye of the push rod by means of two in the outer contour circular bearing shells, each by one middle inner contour area from to the two circumferentially Chen ends have decreasing thicknesses. Such La shells with a circular outer contour and one oval inner contours are in the state of the art knows.

Die Erfindung ist anhand eines bevorzugten, in der Zeich­ nung dargestellten Ausführungsbeispiels beschrieben.The invention is based on a preferred, in the drawing tion described embodiment.

Für eine nicht näher dargestellte Hubkolbenmaschine 1 ist in der einzigen Figur ein hypozykloidisches Kurbelge­ triebe 2 gezeigt, das eine Kolben 3 in diametral ange­ ordneten Zylindern 4 starr verbindende Schubstange 5 um­ faßt. Die Schubstange 5 weist zur Aufnahme eines auf ei­ nem Hubzapfen 6 einer um die Achse 7 drehenden Kurbel­ welle (nicht gezeigt) gesteuert drehbeweglich angeordne­ ten Exzenters 8 ein Lagerauge 9 auf. Um aus Toleranzab­ weichungen bewegter Bauteile des Kurbelgetriebes 2 quer zur Kurbelwellenachse 7 bzw. quer zur oszillierenden Schubstange 5 gemäß Pfeil A resultierende Beanspruchungen im wesentlichen zu vermeiden, ist der mit einem zwischen parallelen Führungen 10 angeordnete weitere Exzenter 11 drehfest verbundene und mit diesem gemeinsam um den Hub­ zapfen 6 drehbewegliche Exzenter 8 in dem Lagerauge 9 zur oszillierend gesteuerten Schubstange 5 querbeweglich vor­ gesehen.For a not shown piston engine 1 , a hypocycloid crank mechanism 2 is shown in the single figure, the piston 3 in diametrically arranged cylinders 4 rigid connecting connecting rod 5 summarizes. The push rod 5 has an egg on nem crank pin 6 of a rotating around the axis 7 for receiving the crank shaft (not shown) controlled rotationally movably arrange th eccentric 8 in a bearing eye. 9 In order to substantially avoid stresses resulting from deviations in moving components of the crank mechanism 2 transversely to the crankshaft axis 7 or transversely to the oscillating push rod 5 according to arrow A, the further eccentric 11 , which is arranged between parallel guides 10 , is connected in a rotationally fixed manner and together with the latter Hub pin 6 rotatable eccentric 8 seen in the bearing eye 9 to the oscillatingly controlled push rod 5 transversely.

Hierzu weist das Lagerauge 9 eine den Exzenter 8 aufneh­ mende Lagerbohrung 12 auf mit in orthogonalen Richtungen unterschiedlich groß gewählten Lagerspielen, wobei das größere Lagerspiel in Querrichtung gemäß Pfeil B zur os­ zillierenden Schubstange 5 gewählt ist.For this purpose, the bearing eye 9 has an eccentric 8 receiving bearing bore 12 with differently selected bearing clearances in orthogonal directions, the larger bearing clearance in the transverse direction according to arrow B to the oscillating push rod 5 being selected.

Vorzugsweise ist das der relativen Querbeweglichkeit des Hubsteuer-Exzenters 8 zur Schubstange 5 dienende Lager­ spiel in Richtung Pfeil B gegenüber dem Lagerspiel in Richtung Pfeil A der oszillierenden Schubstange 5 um 0,4% bis 0,8% des in Pfeilrichtung A gemessenen Durchmessers D der Lagerbohrung 12 größer gewählt.Preferably, the relative transverse mobility of the stroke control eccentric 8 to the push rod 5 serving bearing in the direction of arrow B compared to the bearing play in the direction of arrow A of the oscillating push rod 5 by 0.4% to 0.8% of the diameter D measured in the direction of arrow A. Bearing bore 12 chosen larger.

Mit dem Durchmesser D der Lagerbohrung 12 und dem Außen­ durchmesser d des Hubsteuer-Exzenters 8 ergibt sich in Hubrichtung gemäß Pfeil A der Schubstange 5 ein absolutes Lagerspiel zu: D - d. In zur Hubrichtung gemäß Pfeil A orthogonaler Richtung gemäß Pfeil B ergibt sich mit den weiter vorne angegebenen Werten ein absolutes Lagerspiel zu (D - d) + D (1,004 ÷ 1,008). With the diameter D of the bearing bore 12 and the outer diameter d of the stroke control eccentric 8 , an absolute bearing play results in the stroke direction according to arrow A of the push rod 5 : D - d. In the direction orthogonal to the stroke direction according to arrow A according to arrow B, the values given further above result in an absolute bearing play of (D - d) + D (1.004 ÷ 1.008).

Erzielt ist die ovale Lagerbohrung 12 vorzugsweise mit­ tels zweier in der Außenkontur kreisrunder Lagerschalen 13, 14 in einer zylindrischen Durchbrechung 15 im Lager­ auge 9 der Schubstange 5, wobei die Lagerschalen 13, 14 jeweils von einem mittleren Innenkontur-Bereich aus zu den beiden umfänglichen Enden 13', 14' hin abnehmende Dicken aufweisen.The oval bearing bore 12 is preferably achieved with two means in the outer contour of circular bearing shells 13 , 14 in a cylindrical opening 15 in the bearing eye 9 of the push rod 5 , the bearing shells 13 , 14 each from a central inner contour area to the two circumferential ends 13 ', 14 ' have decreasing thicknesses.

Weiter ist eine spanabhebend oval gestaltete Lagerbohrung möglich sowie auch eine in diametralen Bereichen einer zunächst kreisrunden Lagerbohrung mittels plastischer Verformung oval gestaltete Lagerbohrung.There is also a machined oval bearing hole possible as well as one in diametrical areas initially circular bearing bore using plastic Deformation oval bearing bore.

Claims (5)

1. Hubkolbenmaschine mit hypozykloidischem Kurbelge­ triebe, insbesondere Brennkraftmaschine,
  • - mit einer Kolben (3) in diametral angeordneten Zy­ lindern (4) starr verbindenden Schubstange (5), die
  • - zur Aufnahme eines auf dem Hubzapfen (6) einer Kur­ belwelle gesteuert drehbeweglich angeordneten Excenters (8) ein Lagerauge (9) aufweist und
  • - der Excenter in dem Lagerauge zur oszillierend ge­ steuerten Schubstange quer beweglich vorgesehen ist,dadurch gekennzeichnet,
  • - daß das Lagerauge (9) eine den Excenter (8) auf­ nehmende Lagerbohrung (12) aufweist mit in orthogonalen Richtungen unterschiedlich groß ge­ wählten Lagerspielen, wobei
  • - das größere Lagerspiel in Querrichtung (Pfeil B) zur oszillierenden Schubstange (5) gewählt ist.
1. reciprocating machine with hypocycloidal crank mechanisms, in particular internal combustion engine,
  • - With a piston ( 3 ) in diametrically arranged Zy alleviate ( 4 ) rigid connecting connecting rod ( 5 )
  • - For receiving a on the crank pin ( 6 ) a Kur belwelle controlled rotatably arranged eccentric ( 8 ) has a bearing eye ( 9 ) and
  • - The eccentric in the bearing eye for the oscillating ge controlled push rod is provided to be movable transversely, characterized in that
  • - That the bearing eye ( 9 ) has an eccentric ( 8 ) on the bearing bore ( 12 ) with different sized ge in the orthogonal directions bearing play, where
  • - The larger bearing play in the transverse direction (arrow B) for the oscillating push rod ( 5 ) is selected.
2. Hubkolbenmaschine nach Anspruch 1, dadurch gekenn­ zeichnet, daß das der relativen Querbeweglichkeit des Excenters (8) zur Schubstange (5) dienende Lagerspiel (gemäß Pfeil B) gegenüber dem Lagerspiel (gemäß Pfeil A) in Richtung der oszillierenden Schubstange (5) um 0,4%-0,8% des in Richtung der Schubstange gemessenen Durchmessers (D) der La­ gerbohrung (12) größer gewählt ist.2. Reciprocating piston engine according to claim 1, characterized in that the relative transverse mobility of the eccentric ( 8 ) to the push rod ( 5 ) serving bearing play (according to arrow B) compared to the bearing play (according to arrow A) in the direction of the oscillating push rod ( 5 ) 0.4% -0.8% of the diameter (D) of the bearing bore ( 12 ) measured in the direction of the push rod is chosen larger. 3. Hubkolbenmaschine nach Anspruch 1 und 2, gekenn­ zeichnet durch eine spanabhebend oval gestaltete Lagerbohrung.3. reciprocating piston machine according to claim 1 and 2, characterized is characterized by a machined oval Bearing bore. 4. Hubkolbenmaschine nach Anspruch 1 und 2, gekenn­ zeichnet durch eine in diametralen Bereichen einer zunächst kreisrunden Lagerbohrung mittels plastischer Verformung oval gestaltete Lager­ bohrung.4. reciprocating piston machine according to claim 1 and 2, marked characterized by one in diametrical areas First use a circular bearing hole plastic deformation oval shaped bearings drilling. 5. Hubkolbenmaschine nach Anspruch 1 und 2, dadurch gekennzeichnet, daß eine ovale Lagerbohrung (12) erzielt ist mittels zweier in den Außenkonturen kreisrunder Lagerschalen (13, 14) mit jeweils von einem mittleren Innenkontur-Bereich aus zu den beiden umfänglichen Enden (13', 14') hin abnehmen­ den Dicken.5. Reciprocating piston machine according to claim 1 and 2, characterized in that an oval bearing bore ( 12 ) is achieved by means of two bearing shells ( 13 , 14 ) which are circular in the outer contours, each with a central inner contour area from the two circumferential ends ( 13 ' , 14 ') decrease the thickness.
DE19924205283 1992-02-21 1992-02-21 Reciprocating piston engine with hypocycloidal crank mechanism, especially an internal combustion engine Expired - Fee Related DE4205283C2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE19924205283 DE4205283C2 (en) 1992-02-21 1992-02-21 Reciprocating piston engine with hypocycloidal crank mechanism, especially an internal combustion engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19924205283 DE4205283C2 (en) 1992-02-21 1992-02-21 Reciprocating piston engine with hypocycloidal crank mechanism, especially an internal combustion engine

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DE4205283A1 DE4205283A1 (en) 1993-08-26
DE4205283C2 true DE4205283C2 (en) 2000-07-27

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CN101526028B (en) * 2009-01-16 2012-04-18 黄安陶 Vertical cylinder piston type internal combustion engine

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DE19504891A1 (en) * 1995-02-14 1996-08-22 Bayerische Motoren Werke Ag Reciprocating engine, in particular an internal combustion engine with a hypocycloidal crank mechanism
AU5704296A (en) * 1995-05-10 1996-11-29 Implico B.V. An internal combustion engine
DE19607920A1 (en) * 1996-03-01 1997-09-04 Bayerische Motoren Werke Ag Hypocycloidal crank mechanism for reciprocating piston machines, in particular internal combustion engines
DE19623552A1 (en) * 1996-06-13 1997-12-18 Bayerische Motoren Werke Ag Reciprocating piston machine with a hypocycloid piston lifting gear with Watt's guidance, in particular with pistons in opposing cylinders
DE19637091C2 (en) * 1996-09-12 2002-12-12 Andreas Vigh Rodless double-piston internal combustion engine
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US2271766A (en) * 1940-05-06 1942-02-03 Harry A Huebotter Engine
DE3619488A1 (en) * 1986-02-27 1987-03-05 Toan Dat Tran Straight sliding crank mechanism
DE3723950A1 (en) * 1987-02-03 1988-08-11 Helmut Prof Dr Krauch Regenerative heat engine with a hypocycloidal eccentric crank mechanism

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US2271766A (en) * 1940-05-06 1942-02-03 Harry A Huebotter Engine
DE3619488A1 (en) * 1986-02-27 1987-03-05 Toan Dat Tran Straight sliding crank mechanism
DE3723950A1 (en) * 1987-02-03 1988-08-11 Helmut Prof Dr Krauch Regenerative heat engine with a hypocycloidal eccentric crank mechanism

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101526028B (en) * 2009-01-16 2012-04-18 黄安陶 Vertical cylinder piston type internal combustion engine

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