EP1707769A2 - Ausgleichseinrichtung für Brennkraftmaschine - Google Patents

Ausgleichseinrichtung für Brennkraftmaschine Download PDF

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Publication number
EP1707769A2
EP1707769A2 EP06005873A EP06005873A EP1707769A2 EP 1707769 A2 EP1707769 A2 EP 1707769A2 EP 06005873 A EP06005873 A EP 06005873A EP 06005873 A EP06005873 A EP 06005873A EP 1707769 A2 EP1707769 A2 EP 1707769A2
Authority
EP
European Patent Office
Prior art keywords
oil
balance
peripheral surface
inner peripheral
balance shaft
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.)
Granted
Application number
EP06005873A
Other languages
English (en)
French (fr)
Other versions
EP1707769B1 (de
EP1707769A3 (de
Inventor
Mamoru Honda
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.)
Aisin Corp
Original Assignee
Aisin Seiki Co Ltd
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 Aisin Seiki Co Ltd filed Critical Aisin Seiki Co Ltd
Publication of EP1707769A2 publication Critical patent/EP1707769A2/de
Publication of EP1707769A3 publication Critical patent/EP1707769A3/de
Application granted granted Critical
Publication of EP1707769B1 publication Critical patent/EP1707769B1/de
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • 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
    • 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
    • F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
    • 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

Definitions

  • the present invention relates to a balancer of an engine.
  • balancers In general four-cylinder engines, rotation of a crank shaft becomes unbalanced due to an inertial force resulting from vertical reciprocating motion of a piston, for example. This causes vertical vibrations of the engine.
  • various types of balancers have been proposed and put into practical use. Such balancers have two balance shafts with eccentric balance weights, and the balance shafts are rotated in opposite directions by means of a torque of the crank shaft to suppress the engine vibrations.
  • a balancer of this type is disclosed in, for example, Japanese Unexamined Patent Application Publication No. 2001-280110 .
  • two balance shafts having eccentric balance weights are rotatably and axially supported to a housing provided in an oil pan below a cylinder block, and covered with the housing not to contact an oil in the oil pan or oil flowing out from the cylinder block.
  • the housing has an opening for discharging an oil residual in the housing after lubrication of a bearing portion of the balance shaft, on the rotating balance shaft. The opening is positioned above an oil level of the oil pan.
  • the bearing portion of the balance shaft is lubricated with an oil supplied through an oil path.
  • an oil in a weight chamber is discharged from an end face extending along a radius direction of the balance weight along with the rotation of the balance shaft through the opening. This aims at well-lubricating the bearing portion of the balance shaft, and preventing the oil from being agitated to thereby minimize a power loss.
  • the above balancer has a problem in that a clearance between an inner surface of the balance chamber and an outer surface of the balance weight is uniform, so the oil in the weight chamber is only rotated along with the rotation of the balance weight and is hardly discharged from the opening.
  • the present invention has been accomplished to solve the above problem, and accordingly, it is an object of the present invention to provide an engine balancer that facilitates the discharge of an oil.
  • an engine balancer includes: a housing attached to a cylinder block; a pair of balance shafts which are axially supported to the housing rotatably in parallel to each other, and one of which receives a transmitted torque of a crank shaft; and a balance weight rotatably provided in a weight chamber formed in the housing together with the balance shafts characterized in that the engine balancer further comprises an oil is supplied to a supporting portion of the balance shafts, an oil discharging path communicating with the weight chamber and the outside is formed in the housing, and a distance between an inner peripheral surface of the weight chamber and the balance shaft is reduced toward an opening of the oil discharging path.
  • the inner peripheral surface has an arc shape as viewed in an axial direction of the balance shaft, and an R center of the arc is offset from an axial center of the balance shaft to gradually reduce the distance between the inner peripheral surface of the weight chamber and the balance shaft toward the opening of the oil discharging path.
  • a clearance between the inner peripheral surface of the weight chamber and an outer peripheral surface of the balance weight is gradually reduced to the opening of the oil discharging path, and the minimum value of the clearance is set to 1 to 2 mm.
  • the distance between the inner peripheral surface of the weight chamber and the balance shaft is reduced toward the opening of the oil discharging path, whereby a force acts on the oil that flows along with the rotation of the balance shaft, in such a direction as to compress the oil.
  • the applied pressure pushes the oil flowing along the balance shaft into the oil discharging path.
  • the R center of the inner peripheral surface is offset from an R center of the balance shaft and an outer peripheral surface to gradually reduce the distance between the inner peripheral surface and the balance shaft toward the opening of the oil discharging path. Accordingly, a curvature of the inner peripheral surface is not uniform, which facilitates machining. A machining cost is equivalent to that of the balancer having no offset mechanism.
  • the minimum value of the clearance between the inner peripheral surface of the weight chamber and the outer peripheral surface of the balance weight is set to 1 to 2 mm, whereby a friction applied to the balance shaft can be reduced.
  • Fig. 1 is a schematic front view of an engine
  • Fig. 2 is a schematic side view of the engine.
  • a crank shaft 12 as an output shaft of the engine is supported to a lower end of a cylinder block 11 of the engine, rotatably about an axial line of the shaft 12.
  • the crank shaft 12 is connected with a piston (not shown) through a connecting rod.
  • a driving gear 13 is rotatably fixed to and integrated with the crank shaft 12.
  • An oil pan 14 for storing an oil is fixed below the cylinder block 11.
  • a balancer 20 is secured inside the oil pan 14 at the lower end of the cylinder block 11.
  • the balancer functions to cancel an inertial force of the piston, which acts thereon in the movement direction of the piston at the time of starting the engine.
  • the cylinder block 11 is attached with an oil pump (not shown) for pushing an oil in the oil pan 14 into each lubricating portion of the engine. As described below, the oil pumped with the oil pump is partially supplied to a lubricating portion of the balancer 20 as well.
  • the balancer 20 is made of aluminum alloy or cast iron, and includes a first housing 21 and a second housing 22 that are clamped with each other by means of a clamp (not shown).
  • a clamp (not shown).
  • recesses 23a and 23b are formed opposite to each other so as to define a weight chamber 23 as mentioned later.
  • recesses 24a and 24b are formed opposite to each other so as to define a gear chamber 24 separate from the weight chamber 23.
  • a first balance shaft 25 and a second balance shaft 26 (only the first balance shaft 25 is shown in Fig. 2) are rotatably supported between the first housing 21 and the second housing 22.
  • the balance shafts 25 and 26 are integrated with balance weights 27 and 28 of substantially semi-circular shape.
  • the balance weights 27 and 28 are arranged in the weight chamber 23 and rotated in the chamber.
  • the balance weights 27 and 28 may be formed separately from the balance shafts 25 and 26, and rotatably and integrally clamped with the shafts 25 and 26 by means of a bolt or the like.
  • One ends of the individual balance shafts 25 and 26 protrude into the gear chamber 24, and a first driven gear 31 and a second driven gear 32 arranged in the gear chamber 35 and meshed with each other are fixed thereto, whereby the balance shafts 25 and 26 are rotated in opposite directions.
  • the driving gear 13 meshes with the second driven gear 32, and a gear ratio of the driving gear 13 to the second driven gear 32 is set to 2 : 1. Accordingly, the balance shafts 25 and 26 are rotated at a rotational speed twice that of the clank shaft 12.
  • a chain driving method and a belt driving method may be adopted in addition to the gear driving method.
  • the first housing 21 includes an oil discharging path 41 that communicates with an inner space of the weight chamber 23 and the outside of the balancer 20, that is, communicates with an inner space of the oil pan 14 to discharge an oil in the weight chamber 23.
  • the oil discharging path 41 has an opening 41a in an inner peripheral surface 23c opposite to an outer peripheral surface 27a of the balance weight 27, and has an opening 41b in a side surface 21a of the first housing 21.
  • Figs. 4A and 4B show the oil discharging path 41, but an oil discharging path may be formed on the second balance shaft 26 side.
  • the inner peripheral surface 23c of the recess 23a is curved in an arc shape with its center (R center 02) set to the axial line extending along the axial line of the balance shaft 25.
  • the outer peripheral surface 27a of the balance weight 27 is curved in an arc shape with its center (R center 01) set to the axial center of the balance shafts 25 and 26.
  • the R center.02 of the inner peripheral surface 23c is offset from the R center 01 of the balance shaft 25 and the outer peripheral surface 27a.
  • the offset direction is set such that a distance L1 between the inner peripheral surface 23c and the R center 01 of the outer peripheral surface 27a as viewed in the vertical direction is shorter than a distance L2 therebetween as viewed in the horizontal direction in Fig. 4A. Accordingly, as shown in Fig. 4B, the distance between the balance shaft 25 and the inner peripheral surface 23c is gradually reduced toward the opening 41a of the oil discharging path 41 in the rotational direction of the balance shaft 25 (counterclockwise direction of Fig. 4B). Likewise, as shown in Fig. 4A, the distance (clearance) between the outer peripheral surface 27a of the balance weight 27 and the inner peripheral surface 23c of the recess 23a is gradually reduced toward the opening 41a of the oil discharging path 41 in the rotational direction of the balance shaft 25.
  • the minimum value of the clearance between the balance weight 27 and the inner peripheral surface 23c is determined based on a friction between the balance shaft and the oil in the weight chamber 23.
  • Fig. 5 shows a friction relative to the minimum value of a clearance that varies. As apparent from Fig. 5, it is desirable to set the minimum clearance value to 1 to 2 mm, for example, 1.5 mm.
  • the crank shaft 12 rotates, and its rotational force is transmitted to the second balance shaft 26 through the driving gear 13 and the driven gear 32.
  • the interlocked operation of the driven gear 32 and the driven gear 31 provided to the first balance shaft 25 causes the balance shafts 25 and 26 to rotate in opposite directions, thereby suppressing a vertical vibration and muffled sound resulting from the secondary inertial force of the engine.
  • Supporting portions of the balance shafts 25 and 26 of the balancer 20 are supplied with a part of the oil fed from the oil pan 14 and pushed into each lubrication portion of the engine by an oil pump after starting the engine.
  • the oil supplied to the supporting portions partially flows into the weight chamber 23.
  • the oil in the weight chamber 23 moves along the balance shaft 25 while being pressed against the side face of the balance weight 27 in the rotational direction, along with the rotation of the balance shaft 25.
  • the distance between the balance shaft 25 and the inner peripheral surface 23c of the weight chamber 23 is reduced toward the opening of the oil discharging path 41, so a pressure is applied to the oil in such a direction as to compress the passing oil.
  • This pressure pushes the oil into the oil discharging path 41.
  • the oil is discharged efficiently from the weight chamber 23 by means of the pressure caused by the clearance and the rotational force of the balance shaft 25.
  • the oil between the inner peripheral surface 23c and the outer peripheral surface 27a of the balance weight 27 is also discharged to the oil discharging path 41 by means of the pressure caused by the clearance and the rotational force.
  • the present invention produces the following beneficial effects.
  • the R center 02 of the inner peripheral surface 23c is offset from the axial center of the balance shaft 25 (R center 01 of the outer peripheral surface of the balance weight 27) to gradually change the distance between the inner peripheral surface 23c and the balance shaft 25 and the outer peripheral surface 27a of the balance weight 27.
  • the distance may be changed by the other method. For example, it may be formed into an elliptical shape as view in the axial direction of the balance shaft 25.
  • the amount and direction of the offset from the axial center of the balance shaft 25 (R center 01) from the R center 02 of the inner peripheral surface 23c may be appropriately changed.
  • the offset amount and direction may be changed in accordance with the position and shaft of the oil discharging path 41.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
EP20060005873 2005-03-28 2006-03-22 Ausgleichseinrichtung für Brennkraftmaschine Expired - Fee Related EP1707769B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2005091286A JP4552725B2 (ja) 2005-03-28 2005-03-28 エンジンのバランサ装置

Publications (3)

Publication Number Publication Date
EP1707769A2 true EP1707769A2 (de) 2006-10-04
EP1707769A3 EP1707769A3 (de) 2009-01-21
EP1707769B1 EP1707769B1 (de) 2010-02-17

Family

ID=36579870

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20060005873 Expired - Fee Related EP1707769B1 (de) 2005-03-28 2006-03-22 Ausgleichseinrichtung für Brennkraftmaschine

Country Status (3)

Country Link
EP (1) EP1707769B1 (de)
JP (1) JP4552725B2 (de)
DE (1) DE602006012240D1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114000934A (zh) * 2021-10-22 2022-02-01 中船动力研究院有限公司 一种挡油通风装置及发动机机座

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014077455A (ja) 2012-10-09 2014-05-01 Toyota Motor Corp バランサ装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000000726A1 (en) * 1998-06-30 2000-01-06 Simpson Industries, Inc. Oil/air scavenging system for balance shaft housings
EP1081345A1 (de) * 1999-09-03 2001-03-07 Honda Giken Kogyo Kabushiki Kaisha Ausgleichswellegehause
EP1484488A1 (de) * 2002-03-11 2004-12-08 Honda Giken Kogyo Kabushiki Kaisha Ausgleichsvorrichtung für motor

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3356160B2 (ja) * 1993-09-16 2002-12-09 日産自動車株式会社 内燃機関のバランサ装置
JPH0914354A (ja) * 1995-06-30 1997-01-14 Kubota Corp バランサ装置付きエンジン
JP4072251B2 (ja) * 1998-08-12 2008-04-09 本田技研工業株式会社 エンジンのバランサシャフト支持構造
JP2000088059A (ja) * 1998-09-11 2000-03-28 Nissan Motor Co Ltd バランサシャフトのハウジング構造
JP3705137B2 (ja) * 2001-02-22 2005-10-12 マツダ株式会社 エンジンのバランサシャフト装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2000000726A1 (en) * 1998-06-30 2000-01-06 Simpson Industries, Inc. Oil/air scavenging system for balance shaft housings
EP1081345A1 (de) * 1999-09-03 2001-03-07 Honda Giken Kogyo Kabushiki Kaisha Ausgleichswellegehause
EP1484488A1 (de) * 2002-03-11 2004-12-08 Honda Giken Kogyo Kabushiki Kaisha Ausgleichsvorrichtung für motor

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114000934A (zh) * 2021-10-22 2022-02-01 中船动力研究院有限公司 一种挡油通风装置及发动机机座

Also Published As

Publication number Publication date
EP1707769B1 (de) 2010-02-17
EP1707769A3 (de) 2009-01-21
DE602006012240D1 (de) 2010-04-01
JP2006275082A (ja) 2006-10-12
JP4552725B2 (ja) 2010-09-29

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