EP1009938A2 - Arbre compensateur - Google Patents

Arbre compensateur

Info

Publication number
EP1009938A2
EP1009938A2 EP99944262A EP99944262A EP1009938A2 EP 1009938 A2 EP1009938 A2 EP 1009938A2 EP 99944262 A EP99944262 A EP 99944262A EP 99944262 A EP99944262 A EP 99944262A EP 1009938 A2 EP1009938 A2 EP 1009938A2
Authority
EP
European Patent Office
Prior art keywords
balance
shaft
center
balance weight
mass distribution
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.)
Withdrawn
Application number
EP99944262A
Other languages
German (de)
English (en)
Inventor
Werner Bauss
Roland Klaar
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.)
Eisengiesserei Monforts GmbH and Co
Original Assignee
Eisengiesserei Monforts GmbH and Co
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 Eisengiesserei Monforts GmbH and Co filed Critical Eisengiesserei Monforts GmbH and Co
Publication of EP1009938A2 publication Critical patent/EP1009938A2/fr
Withdrawn legal-status Critical Current

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
    • 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

Definitions

  • the invention relates to a balancer shaft to compensate for inertial forces and / or moments of inertia in internal combustion engines of the reciprocating piston type, in which, with the aid of balancing weights which adjoin the geometric shaft longitudinal ends on bearing parts or the like and are arranged diagonally opposite one another in the direction of the shaft axis with respect to the geometric shaft center an eccentric mass distribution is set.
  • the balance shaft has two balance weights.
  • a balancing shaft with two equal balancing weights is described in DE 4412476 A 1.
  • the known balancing weights have (each individually) - seen in the direction of the shaft axis - essentially the same cross section everywhere (measured perpendicular to the shaft axis).
  • the mass per unit length (along the axis) of each of the counterweights is essentially the same everywhere.
  • the known balancer shafts For the bearing in the machine housing, the known balancer shafts have bearing journals on the two longitudinal shaft ends. A drive wheel is usually attached to one bearing journal. Depending on the task (balancing mass moments or mass forces), the balancer shafts are driven at the same or twice the speed of the crankshaft of the respective machine.
  • the balance shafts are often housed in the engine housing of the machine. If a position below an existing oil bath level is required, the balance shaft is enclosed with a cylindrical sleeve to reduce splashing losses.
  • the aim is to design the balance shaft as stiff as possible in order to avoid disturbances caused by the shaft's own bending vibrations. For this reason, separately machined axle journals are drilled in axially aligned holes. conditions are firmly inserted at the respective wavelength end. It is also provided that the balance weights are formed in one piece as part of the balance shaft. The counterweights can optionally also be firmly connected to the inner wall of the aforementioned casing.
  • Balance shafts are effective due to their weight. This weight and the drive power required to operate the shaft result in additional energy consumption.
  • the invention is accordingly based on the first aim of achieving maximum balancing of mass moments or forces with minimal weight.
  • the geometry of the respective balancing shaft or the balancing weights arranged eccentrically therein can also generate undesired additional vibrational forces in the respective machine. These vibrational forces depend on the natural frequency behavior of the balance shaft and its parts.
  • Another object of the invention is to dampen the natural vibrations in such a way that the desired smoothness is not adversely affected thereby.
  • the invention has for its object to overcome the aforementioned disadvantages and to achieve the goals.
  • the solution according to the invention is described in the characterizing part of patent claim 1. Some improvements and further refinements of the invention are specified in the subclaims.
  • the essence of the present invention is to provide a mass distribution that is eccentric with respect to the geometric center of each balance weight.
  • the center of gravity of the individual balance weight should lie between its geometric center and the adjacent wavelength end.
  • the balancing weights have the same mass distribution everywhere along the length of the shaft.
  • the geometry of the counterweights is preferably determined in such a way that the center of gravity of the respective one can also be referred to as unbalance Balance weight - compared to the case in the prior art (DE 44 12 476 A1) - is shifted axially outwards (in the direction of the bearings) and / or radially (away from the shaft axis); In this sense, the center of gravity of the individual balance weight is the point of application of the respective force.
  • the goals striven for by the invention can be achieved in that the mass per (axis) length unit in the counterweight decreases from the longitudinal ends to the center.
  • This unequal mass distribution can be set by material inhomogeneity of the counterweights and / or by a correspondingly unequal geometry.
  • the aim of the invention to reduce the weight which is sufficient to compensate for the gravitational forces of the respective machine becomes clear - in the case of the geometric compensation - that it is usually sufficient, especially with axial mass eccentricity, if the largest cross section of the compensation weight is approximately equal half the cross section of the balancer shaft.
  • the unbalance magnification of the balance shaft is to be carried out by moving part of the balance mass from the center of the shaft to the radial and axial shaft periphery. It can be advantageous here if the individual counterweight (with an axial distance from the shaft center) has a bead projecting radially beyond the circumference of its regions closer to the shaft center.
  • a geometry of the balancing weights preferred in the context of the invention can be described by saying that the cross section of the individual balancing weight or the mass per (axis) length unit increases in the direction from the geometric shaft center to the wavelength end adjacent to the balancing weight. A steady increase in the cross section in the axial direction is preferably provided within the scope of the invention.
  • the corresponding slope with which the cross-section of the individual balancing weight is to change in the longitudinal direction depends on the various forces and frequencies typical of the respective motor.
  • the slope can be determined, for example, by iterative methods. In experiments, gradients (core angle) - in the axial direction - in the order of 2 - 20 °, preferably 4 - 10 °, were found with constant inclination.
  • the two balance weights of a shaft shaped according to the invention can be designed differently in the axial and radial directions.
  • a balance shaft can therefore have two completely different balance weights.
  • the desired conformity between low weight and counter torque to be achieved with non-disruptive natural frequency behavior can be obtained solely through the claimed geometry of the balancing weights themselves, which act as unbalances. If necessary, the individual balance weight can be inherently homogeneous.
  • the counterweights can be integrally formed on the inner surface of an outer cylindrical shell.
  • a casing is known to reduce churning losses in the oil pan of an engine.
  • the casing as a tube with a solid wall, can determine the rigidity or design strength of the entire balancer shaft. This gives a correspondingly great freedom to design the counterweights themselves in the sense of solving the task mentioned at the beginning.
  • an externally cylindrical shell encloses the counterweights, the latter should - insofar as their radial extension fits - on the inner surface of the Fit the cover in one piece. Cavities therefore remain within the envelope in addition to the counterweights.
  • an open through connection (a hole or a hole) between the two cavities is created between the two cavities, which are created in addition to the preferably diagonally opposite balance weights, in the area of the smallest cross sections of the balance weights - i.e. in the area of the largest cross sections of the cavities intended.
  • the cross section of holes between the two cavities should preferably be small compared to the cross section of the adjacent cavities.
  • the balance shaft in one piece from cast iron, preferably GGG-70. This not only has advantages in terms of manufacturing costs but also material-related in terms of damping natural vibrations (reducing possible noise pollution) of the balance shaft or its balance weights.
  • FIG. 1 shows a section (along the shaft axis) through a balancer shaft according to the invention.
  • Fig. 2 is a perspective view of essential parts of the shaft of Fig. 1;
  • the balance shaft designated 1 as a whole according to FIGS. 1 and 2 has axle journals 2 and 3 which are firmly inserted in axially aligned bores 4 at the respective shaft end.
  • the balance shaft 1 has diagonally opposite Balance weights 5 and 6 within an outer cylindrical shell 7 (tube) and in one piece with this.
  • the left-hand journal 2 in FIG. 1 carries a drive element 8, for example a gear, in addition to the bearing point.
  • the journal 2 and 3 and the outer surface of the sleeve 7 are rotationally symmetrical with respect to the shaft axis 9.
  • an eccentric mass distribution with respect to its geometric length L measured in the direction of the shaft axis 9 is provided within each balance weight 5, 6, the center of gravity S of each balance weight 5, 6 - as shown in FIG. 1 - between the geometric center M of its length L and the adjacent bearing part 10, 11.
  • the two counterweights 5, 6 should extend as far as the bearing parts 10, 11. Its length L is measured between the geometric shaft center Z and the respective limit to the bearing part 10 or 11.
  • the cross section of the individual balancing weight 5, 6 increases continuously in the direction from the geometric shaft center Z to the respective shaft longitudinal end on the bearing part 10, 11.
  • the cross section of the individual counterweight 5, 6 increases from a minimum in the area of the geometric shaft center Z to a maximum of approximately half the shaft cross section - in the vicinity of the shaft ends or adjacent to the transition to the bearing parts 10, 11.
  • the counterweights 5, 6 are preferably integrally formed on the inner surface 12 of the outer cylindrical shell 7.
  • the cavities 13, 14 remaining within the tubular shell 7 in the region of the smallest cross sections of the Balance weights 5, 6 - that is, in the area of the geometric shaft center Z - an open through connection or a hole 15 is provided.
  • the hole diameter should - especially to improve the natural frequency behavior - much smaller than the sum of those in this area maximum cross sections of the cavities 13, 14.
  • a balance shaft 1 in the form shown in FIGS. 1 and 2 was produced in an experiment from cast iron GGG-70.
  • the length of the balancer shaft 1 - measured over the bearing parts 10, 11 receiving the bore 4 - was 240 " mm.
  • the diameter of the sleeve 7 was 63 mm.
  • the wall thickness of the sleeve 7 was 9 mm.
  • the clear width of the bore 4 was 17 mm
  • the thickness of the longitudinal ends 10, 11 receiving the bore 4 measured in the direction of the shaft axis 9 was 23 mm.
  • the core angle K which describes the inclination of the counterweights 5, 6 between the shaft axis 9 and the inner surface 18 of the counterweights 5, 6, was 6 ° 1
  • the diameter of the essentially circular hole 15 in the region of the geometric shaft center Z was 20 mm.
  • FIGS. 1 and 2 show - each with an additional representation of the sections A-A and B-B perpendicular to the longitudinal axis 9 - two exemplary embodiments deviating from FIGS. 1 and 2, in which the same parts as before are to be designated.
  • the balancer shaft 1 according to FIG. 3 has two balancing weights 5 and 6 which are identical to one another.
  • the eccentric mass shift is - in contrast to FIGS. 1 and 2 - achieved by a mass shift in the radial direction, namely into the beads 19 and 20.
  • part of the mass is thus moved radially from the inside of the balancer shaft over the original circumference 21 of the balancer weights 5 and 6.
  • the outer diameter of the balancer shaft 1 is enlarged, but the mass contained in the beads 19 and 20 acts, because of the arrangement far from the center Z, in function as an unbalance much more than if the same mass adjoins the shaft inside the shaft axis would be 9.
  • FIG. 4 shows an exemplary embodiment of a mixed form of FIGS. 1 and 3.
  • the mass distribution is the same as that in FIG. 1.
  • a mass distribution is partly as in FIG. 1 and partly as in FIG 3 provided. 4 speaks for itself.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Abstract

L'invention concerne un arbre compensateur comprenant des contrepoids d'équilibrage à répartition excentrique des masses pour la compensation des forces dues aux masses et des moments d'inertie, dans des moteurs à combustion interne à piston alternatif. En vue d'optimiser le poids de l'arbre et, de ce fait, la compensation des forces et des moments à obtenir pour un régime de fréquence propre non perturbé, l'invention est caractérisée en ce qu'il est prévu, également à l'intérieur de chaque poids compensateur, une répartition excentrique des masses par rapport à son centre géométrique.
EP99944262A 1998-07-04 1999-07-03 Arbre compensateur Withdrawn EP1009938A2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19830051 1998-07-04
DE1998130051 DE19830051C1 (de) 1998-07-04 1998-07-04 Ausgleichswelle
PCT/DE1999/002029 WO2000001955A2 (fr) 1998-07-04 1999-07-03 Arbre compensateur

Publications (1)

Publication Number Publication Date
EP1009938A2 true EP1009938A2 (fr) 2000-06-21

Family

ID=7873069

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99944262A Withdrawn EP1009938A2 (fr) 1998-07-04 1999-07-03 Arbre compensateur

Country Status (3)

Country Link
EP (1) EP1009938A2 (fr)
DE (2) DE19830051C1 (fr)
WO (1) WO2000001955A2 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2823279B1 (fr) * 2001-04-09 2005-11-11 Renault Sas Arbre d'equilibrage comportant des blocs d'equilibrage cylindriques realises par surmoulage
DE10207452A1 (de) * 2002-01-22 2003-07-24 Opel Adam Ag Ausgleichseinheit, zur Reduzierung der bei Hubkolben-Verbrennungsmotoren von einer Kurbelwelle verursachten Massenkräften 2. Ordnung
DE10207458A1 (de) * 2002-01-22 2003-07-31 Opel Adam Ag Hubkolben-Brennkraftmaschine in Reihenbauart mit Massenausgleichswellen
DE102008060084A1 (de) 2008-12-02 2010-06-10 Schaeffler Kg Ausgleichswelle
DE102012220120A1 (de) 2012-11-05 2014-05-08 Magna Powertrain Ag & Co. Kg Ausgleichswelle
DE102013207800A1 (de) * 2013-04-29 2014-10-30 Magna Powertrain Ag & Co. Kg Ausgleichswelle
DE102018119524B4 (de) * 2018-08-10 2020-10-29 Bayerische Motoren Werke Aktiengesellschaft Verfahren zur Bildung eines Systems aus Ausgleichswelle und Lager oder Lagering

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2838957A (en) * 1954-06-14 1958-06-17 Gen Motors Corp Engine balancing means
JPS6184434A (ja) * 1984-09-29 1986-04-30 Mitsubishi Motors Corp エンジンのバランサ装置
US4741303A (en) * 1986-10-14 1988-05-03 Tecumseh Products Company Combination counterbalance and oil slinger for horizontal shaft engines
DE4030568A1 (de) * 1990-09-27 1992-04-09 Bayerische Motoren Werke Ag Mit einem steuernocken versehene steuerwelle zur periodischen betaetigung von maschineneinrichtungen, insbesondere gaswechselventile in brennkraftmaschinen
US5375571A (en) * 1994-04-08 1994-12-27 Ford Motor Company Coaxially mounted engine balance shafts
DE4412476A1 (de) * 1994-04-14 1995-10-19 Otto Michael Militzer Ausgleichswelle
US5483932A (en) * 1994-04-21 1996-01-16 Simpson Industries, Inc. Hollow balance shaft
US5857388A (en) * 1996-07-09 1999-01-12 Simpson Industries, Inc. Balance shafts having minimal mass

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0001955A2 *

Also Published As

Publication number Publication date
WO2000001955A3 (fr) 2000-03-16
DE29903372U1 (de) 1999-06-10
DE19830051C1 (de) 1999-11-25
WO2000001955A2 (fr) 2000-01-13

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