WO2012096519A2 - Volant de vilebrequin de moteur - Google Patents

Volant de vilebrequin de moteur Download PDF

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Publication number
WO2012096519A2
WO2012096519A2 PCT/KR2012/000281 KR2012000281W WO2012096519A2 WO 2012096519 A2 WO2012096519 A2 WO 2012096519A2 KR 2012000281 W KR2012000281 W KR 2012000281W WO 2012096519 A2 WO2012096519 A2 WO 2012096519A2
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WO
WIPO (PCT)
Prior art keywords
journal
shaft
center
journals
press
Prior art date
Application number
PCT/KR2012/000281
Other languages
English (en)
Korean (ko)
Other versions
WO2012096519A3 (fr
Inventor
강민우
오헌식
Original Assignee
대동공업 주식회사
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 대동공업 주식회사 filed Critical 대동공업 주식회사
Publication of WO2012096519A2 publication Critical patent/WO2012096519A2/fr
Publication of WO2012096519A3 publication Critical patent/WO2012096519A3/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/02—Arrangements of lubricant conduits
    • 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
    • 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
    • F02B77/00—Component parts, details or accessories, not otherwise provided for
    • 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
    • F16C3/20—Shape of crankshafts or eccentric-shafts having regard to balancing
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/1045—Details of supply of the liquid to the bearing
    • F16C33/1055—Details of supply of the liquid to the bearing from radial inside, e.g. via a passage through the shaft and/or inner sleeve
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/02—Arrangements of lubricant conduits
    • F01M2011/028—Arrangements of lubricant conduits for lubricating balance 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
    • F02B75/06—Engines with means for equalising torque
    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/53—Spring-damper, e.g. gas springs
    • 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
    • F16C3/02—Shafts; Axles

Definitions

  • the present invention relates to a balance shaft, and more particularly, to an engine balance shaft installed in an engine for implementing a vibration canceling function.
  • the cylinder block the cylinder head is installed on the cylinder block and the inlet / exhaust valve and opening and closing mechanism is installed, and the engine oil is stored in the lower cylinder block It consists of an oil pan.
  • the cylinder block has several cylinders, for example four cylinders for four-cylinder engines and six cylinders for six-cylinder engines, and within each cylinder a piston that compresses and explodes the compressed air mixed with fuel is reciprocated. It is possible.
  • Each piston is connected to a connecting rod, and a lower end of the connecting rod is connected to a crank shaft for converting the linear motion of the piston into a rotary motion. And the rotational force of the crankshaft is to be transmitted to the transmission to change the rotational speed through the clutch.
  • crankshaft is rotated by the movement of the lowering piston when the mixed air explodes in the cylinder, ie the force transmitted to the lowering of the piston in the explosive stroke, and the force that tries to stop the rotation during the other strokes of suction, compression and exhaust stroke. This will work.
  • one end of the crankshaft is equipped with a flywheel for maximizing the force that the crankshaft tries to stop by inducing rotational inertia, which allows the crankshaft to rotate continuously and smoothly regardless of each stroke position.
  • the balance shaft as an idle gear, is electrically connected to the crankshaft and is integrally provided with a deflected weight called a 'weight'.
  • the weight that is deflected for generating the vibration force that is, the cross-sectional shape of the shaft having the weight is constantly formed regardless of the section (or area), and thus the engine.
  • the response to the inequality moment that appears differently depending on the section in the longitudinal direction is not effective.
  • the oil passage is formed in the center of the balance shaft in the center of the balance shaft so that oil can be continuously provided to the journal side connected to the cylinder block, conventionally, after drilling the oil passage by drilling a hole from the shaft end, By closing the hole formed in the tip by using a separate sealing member, there is a problem that a separate member such as a sealing member after processing is required to form a sealed oil passage.
  • the technical problem to be solved by the present invention is to provide an engine balance shaft that can effectively cope with the inequality moments that occur differently in each section, that is, the area, without forming a weight deflection distance from the cross-sectional area or the central axis of the weight.
  • the present invention is to provide an engine balance shaft that does not require a separate member (sealing member) for sealing the oil passage after processing while improving the ease of processing in forming the oil passage in the balance shaft. will be.
  • the present invention is installed in the engine for implementing the vibration canceling function, the shaft portion of the cross-sectional structure having a deflected center of gravity; And a journal portion including a plurality of journals formed at uneven intervals in the shaft portion, wherein the shaft portion has an indentation hole in the front thereof, and an oil passage is formed along the axial direction in the center thereof, and an inlet shaft is formed in the indentation hole.
  • the formed balance gear is press-fitted and fixed, and an inflow passage communicating with the oil passage is formed in a journal adjacent to the balance gear among the plurality of journals constituting the journal portion, and spaced apart from the balance gear among the plurality of journals constituting the journal portion.
  • the journal in position provides an engine balance shaft, characterized in that an oil passage is formed in communication with the oil passage.
  • the shaft portion has a vertical asymmetric cross-sectional shape with respect to the horizontal axis, a lower weight consisting of two inclined surfaces and the arc surface connecting the two inclined front end, and the lower weight based on the horizontal axis And an upper protrusion of an asymmetrical shape.
  • an inclined edge surface may be further formed at a corner portion where the inclined surface and the arc surface of the lower weight meet.
  • the shaft portion may be divided into a front region, a center region, and a rear region based on a plurality of journals, and the upper protrusion formed at the center of the front region is formed higher than the upper protrusion formed at the center of the central region, and the rear region.
  • the upper protrusion of the may have a configuration consisting of an inclined structure that gradually increases in height toward the shaft end.
  • the lower weight at the end of the rear region is preferably configured to gradually reduce the radius of the weight toward the end of the shaft.
  • a groove may be formed in the center of the journal outer surface constituting the journal portion so that the lubricant may be continuously supplied between the journal and the bearing surrounding the journal.
  • the oil passage may extend from the center of the vertical wall surface of the press fitting hole and may be exposed to the outside through the press fitting hole before assembling the balance gear.
  • the engine balance shaft according to the embodiment of the present invention, only the configuration of differently forming the height of the upper protrusion for each axial region, differently generated for each section, that is, without forming a weight deflection distance from the cross-sectional area or the central axis of the weight differently It is possible to implement an engine balance shaft that can effectively respond to the inequality moment.
  • a press-fitting hole is formed at the tip of the shaft portion with a predetermined diameter, and the oil passage is formed in the axial direction along the center of the shaft from the press-fitting hole, thereby improving the ease of processing in forming the oil passage in the balance shaft.
  • a separate member sealing member
  • FIG. 1 is a perspective view of an engine balance shaft according to an embodiment of the present invention.
  • FIG. 2 is a transverse cross-sectional view of the balance shaft shown in FIG. 1.
  • FIG. 2 is a transverse cross-sectional view of the balance shaft shown in FIG. 1.
  • FIG. 3 is a sectional view taken along the line A-A of the balance shaft according to FIG. 2;
  • FIG. 4 is a sectional view taken along the line B-B of the balance shaft according to FIG. 2;
  • FIG. 5 is a sectional view taken along the line B-B of the balance shaft according to FIG. 2;
  • FIG. 1 is a perspective view of an engine balance shaft according to an embodiment of the present invention
  • Figure 2 is a cross-sectional view for showing a longitudinal cross-sectional shape of the balance shaft shown in FIG.
  • the balance shaft according to the present invention is installed in the engine for implementing the vibration canceling function, and includes a shaft portion 1 of the cross-sectional structure having a deflected center of gravity.
  • the shaft portion 1 is provided with a journal portion 2 having a configuration in which a plurality of journals 20, 22, 24 are formed at uneven intervals, and the balance shaft is formed by each journal formed in the journal portion 2. It is supported and fixed to a cylinder block (not shown) of the engine.
  • the press-in hole 10 is recessed in a predetermined diameter in front of the shaft portion 1, and an oil passage 3 is formed long in the center of the shaft portion 1 along the axial direction. At this time, the oil passage 3 extends from the center of the vertical wall surface of the press-in hole 10, and thus, the oil passage 3 is press-fitted before assembling the balance gear 4 described later in the press-in hole 10. It may be exposed to the outside through the hole 10.
  • the press-fit hole 10 is press-fitted and fixed with a balance gear 4 having an inlet shaft, thereby closing the front opening of the oil passage 3 exposed to the outside as before assembly, and forming a plurality of journal parts 2.
  • an inlet passage 30 is formed in communication with the oil passage 3 in the vertical direction.
  • an exhaust passage 32 communicating with the oil passage 3 is provided in the journals 22 and 24 existing at a position spaced apart from the balance gear 4 among a plurality of journals constituting the journal portion 2.
  • a groove (groove, 200) in communication with the inlet passage 30 is formed in the center of the outer surface of the journal 20 constituting the journal portion (2).
  • the provided oil flows into the oil passage 3 formed longitudinally in the center of the balance shaft via the groove 200 and the inlet passage 30.
  • the oil flowing through the oil passage 3 is provided between the journals 22 and 24 and the bearings through the drainage passages 32 and 34 formed in the other journals 22 and 24 so that the bearings can be rotated at high speed. To prevent the journal from sticking.
  • the shaft 1 is based on a plurality of journals, preferably three journals, the front (a), the center (b) and the rear region (b).
  • the shaft portion 1 which is divided and is formed in each area has a cross-sectional structure of vertically asymmetrical shape with respect to the horizontal axis XC in common.
  • the cross-sectional shape of the shaft portion 1 will be described in more detail with reference to FIGS. 3 to 5.
  • 3 to 5 are cross-sectional views of the balance shaft shown in FIG. 2 as viewed from A-A, B-B and C-C directions, respectively.
  • the shaft portion 1 has a lower weight composed of two inclined surfaces 120 and an arc surface 122 connecting the two inclined surfaces 120. 12) and the lower weight 12 and the asymmetrical shape of the upper protrusion 14 with respect to the horizontal axis XC.
  • the lower weight 12 generates a vibration force for canceling vibration when the engine is driven, and the vibration force may vary in size depending on the length of the upper protrusion 14.
  • Engine vibrations are caused by unbalanced moments in two-dimensional directions caused by a combination of reciprocating motion of the piston and rotation of the crankshaft during engine operation, especially in the case of high-load in-line four-cylinder diesel engines, mainly in the engine center between journals and other journals. Occurs as Therefore, in view of this, it is preferable to configure the cross-sectional shape in the case of the shaft portion 1 so that differential vibrating force can be generated for each region.
  • the upper protrusions 14 and 3 formed at the center of the front region a are higher than the upper protrusions 14 and 4 formed at the center of the central region b, as shown in FIGS. Adopted the formed configuration. In this case, since a larger vibration force is generated in the central region b than the front region a, the vibration of the engine can be more effectively attenuated.
  • the weight of the lower weight 12 is reduced. Since the center is located at a further distance from the center of the axis, it is possible to generate greater vibration force. Therefore, the angle of the inclined surface 120 of the lower weight 12 may be increased or the edge surface 124 may be formed as described above.
  • the height of the upper protrusion 14 formed thereon gradually decreases toward the end of the shaft portion 1. It has an inclined structure, the weight 12 of the rear region (c) end may also be configured to gradually reduce the radius of the weight 12 toward the end of the shaft (1).
  • the space of the cylinder block may be changed in accordance with the reduction of the cross section of the rear region C of the shaft portion 1 to secure space. Therefore, it is possible to secure enough installation space of the start motor to be installed adjacent to the cylinder block, which is advantageous in installing engine driving related parts around the engine.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Ocean & Marine Engineering (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

L'invention porte sur un volant de vilebrequin de moteur. Le volant de vilebrequin de moteur selon la présente invention comprend : une partie d'arbre ayant une structure transversale ayant un centre de gravité décalé ; et une partie de tourillon comprenant une pluralité de tourillons formés à des intervalles irréguliers dans la partie d'arbre, les caractéristiques clés étant que : la partie d'arbre a un trou d'emmanchement à la presse vers l'avant de celle-ci, tandis qu'un passage d'huile est formé dans le sens de la longueur axialement au centre de celle-ci ; un engrenage différentiel constitué d'un arbre d'agencement est fixé par emmanchement à la presse dans le trou d'emmanchement à la presse ; parmi la pluralité de tourillons qui constituent la partie de tourillon, le tourillon qui est adjacent à l'engrenage différentiel est formé de façon à avoir un passage de débit entrant qui est raccordé au passage d'huile ; et, parmi la pluralité de tourillons qui constituent la partie de tourillon, un tourillon situé dans une position espacée de l'engrenage différentiel est formé de façon à avoir un passage d'évacuation d'huile qui est raccordé au passage d'huile.
PCT/KR2012/000281 2011-01-11 2012-01-11 Volant de vilebrequin de moteur WO2012096519A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR1020110002725A KR101421014B1 (ko) 2011-01-11 2011-01-11 엔진 밸런스 샤프트
KR10-2011-0002725 2011-01-11

Publications (2)

Publication Number Publication Date
WO2012096519A2 true WO2012096519A2 (fr) 2012-07-19
WO2012096519A3 WO2012096519A3 (fr) 2012-11-15

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Application Number Title Priority Date Filing Date
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WO (1) WO2012096519A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110030109A (zh) * 2018-01-12 2019-07-19 丰田自动车株式会社 内燃机

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101862142B1 (ko) * 2016-11-10 2018-07-05 (주)동보 밸런스 샤프트 어셈블리
KR101868436B1 (ko) * 2016-11-10 2018-06-20 (주)동보 밸런스 샤프트 어셈블리

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6239042U (fr) * 1985-08-27 1987-03-09
JPH0519632Y2 (fr) * 1986-06-18 1993-05-24
JPS6333044U (fr) * 1986-08-21 1988-03-03
JP3312844B2 (ja) * 1996-03-29 2002-08-12 株式会社クボタ ４気筒エンジンの２軸バランサ装置
JP2001200893A (ja) * 2000-01-18 2001-07-27 Kubota Corp エンジンのバランサ装置
US20090016907A1 (en) * 2006-02-28 2009-01-15 Matthew Williamson Dynamic balancer with speed-related control mechanism
JP4850883B2 (ja) * 2008-08-21 2012-01-11 株式会社クボタ エンジンの回転バランサ

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110030109A (zh) * 2018-01-12 2019-07-19 丰田自动车株式会社 内燃机
CN110030109B (zh) * 2018-01-12 2021-05-07 丰田自动车株式会社 内燃机

Also Published As

Publication number Publication date
WO2012096519A3 (fr) 2012-11-15
KR20120081400A (ko) 2012-07-19
KR101421014B1 (ko) 2014-07-18

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