WO2021187033A1 - Dispositif d'équilibrage et dispositif d'équilibrage pourvu d'une pompe à huile - Google Patents

Dispositif d'équilibrage et dispositif d'équilibrage pourvu d'une pompe à huile Download PDF

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Publication number
WO2021187033A1
WO2021187033A1 PCT/JP2021/006996 JP2021006996W WO2021187033A1 WO 2021187033 A1 WO2021187033 A1 WO 2021187033A1 JP 2021006996 W JP2021006996 W JP 2021006996W WO 2021187033 A1 WO2021187033 A1 WO 2021187033A1
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WO
WIPO (PCT)
Prior art keywords
balancer
shaft
housing
bearing
bearing portion
Prior art date
Application number
PCT/JP2021/006996
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English (en)
Japanese (ja)
Inventor
政志 澤田
崇 平野
淳 稲田
Original Assignee
日立Astemo株式会社
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Filing date
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Publication of WO2021187033A1 publication Critical patent/WO2021187033A1/fr

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    • 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
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • 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
    • 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
    • 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

Definitions

  • the present invention relates to a balancer device and a balancer device with an oil pump.
  • balancer device for example, the balancer device described in Patent Document 1 below is known.
  • a balancer gear, a balancer weight, and a bearing are provided in order from one end in the rotation axis direction of the balancer shaft.
  • the balancer gear meshes with a transmission gear to which the rotational force from the crankshaft is transmitted.
  • the present invention has been devised in view of the conventional circumstances, and provides a balancer device capable of suppressing a rattling noise generated between a balancer gear and a transmission gear, and a balancer device with an oil pump. It has one purpose.
  • the first balancer bearing portion is provided between the first balancer weight and the balancer gear, and at a position where the balancer gear is sandwiched together with the first balancer weight.
  • FIG. 1 is a partial cross-sectional view of an internal combustion engine 1 equipped with the balancer device of the first embodiment.
  • the crankshaft 3 is rotatably housed in the internal combustion engine 1, for example, the engine block 2 of an in-line 3-cylinder internal combustion engine.
  • the crankshaft 3 is arranged so that the direction of its rotation axis coincides with the front-rear direction of the internal combustion engine 1.
  • a crank sprocket 4 is mounted and fixed to one end 3a in the direction of the rotation axis of the crankshaft 3 via a mounting hole 4a formed in the center thereof.
  • a plurality of gear teeth 4b are formed on the outer periphery of the crank sprocket 4.
  • an oil pan 5 for storing oil as a lubricating oil is attached to a plurality of fixing members (for example, bolts) (not shown). Oil is stored in the oil pan 5 so that the first balance weight 10 described later, which is located at the lowermost position as shown in FIG. 1, is above the oil level 6 of the oil. Further, in the oil pan 5, the suction port 7a of the oil pump 7 is arranged so as to be immersed in the oil below the first balance weight 10.
  • a balancer device that suppresses the moment vibration of the internal combustion engine 1 is housed in the space surrounded by the lower part of the engine block 2 and the oil pan 5.
  • the balancer device is configured as a balancer device with an oil pump equipped with an oil pump 7. This balancer device will be described later, which is fixed to the balancer housing 8, the balancer shaft 9 rotatably supported by the balancer housing 8 and the rotational force from the crankshaft 3 is transmitted, and the outer peripheral portion of the balancer shaft 9. It includes a balancer gear 30, a first balancer weight 10, and a second balancer weight 31, which will be described later.
  • the balancer shaft 9 is arranged so that the direction of its rotation axis coincides with the direction of the rotation axis of the crankshaft 3, that is, the front-rear direction of the internal combustion engine 1.
  • a pump sprocket 12 is attached and fixed to a front end portion of the oil pump 7 in the direction of the rotation axis of the oil pump shaft 11 by a fixing member, for example, a bolt 13.
  • a plurality of gear teeth 12a are formed on the outer circumference of the pump sprocket 12.
  • a drive chain 14 is wound between the gear teeth 12a of the pump sprocket 12 and the gear teeth 4b of the crank sprocket 4.
  • a predetermined tension is applied to the drive chain 14 by a hydraulic tensioner 15 provided near the lower part of the engine block 2. The rotational force from the crankshaft 3 is transmitted to the oil pump shaft 11 via the drive chain 14, the crank sprocket 4, and the pump sprocket 12.
  • FIG. 2 is a perspective view of the balancer device of the first embodiment
  • FIG. 3 is an exploded perspective view of the balancer device of the first embodiment.
  • the direction of the rotation axis of the balancer shaft 9 is defined as the "rotation axis direction”
  • the radial direction of the balancer shaft 9 with respect to the rotation axis is defined as the “radial direction”
  • the balancer shaft is defined as the "circumferential direction”.
  • the end on the side where the first balancer weight 10 is provided is defined as "one end 9a”
  • the end on the side where the second balancer weight 31 is provided is defined as "one end 9a”. It is defined as "the other end 9b”.
  • the balancer housing 8 is formed into a substantially rectangular thick plate by die casting with a metal material such as aluminum.
  • the balancer housing 8 rotatably supports the balancer shaft 9 in cooperation with the bearing housing 16 formed separately from the balancer housing 8.
  • the balancer housing 8 has a rectangular base portion 17 that covers a part of the circumferential direction of the balancer shaft 9, and a protruding portion that projects outward in a rectangular shape from the longitudinal end portion of the base portion 17 on the first balancer weight 10 side. It has 18.
  • the base portion 17 has a flat surface 17a on the side on which the balancer shaft 9 is provided, and is recessed in the surface 17a in an arcuate shape along the circumferential direction of the balancer shaft 9, which is one of the circumferential directions of the balancer shaft 9. It is provided with an arc recess 17b that covers the region of the portion. Further, the base portion 17 is located on the one end portion 9a side of the balancer shaft 9 on the first balance weight 10 side with respect to the surface 17a via the step portion 17c, and is a flat base alignment that serves as a mating surface with the bearing housing 16. It has a surface 17d.
  • a rectangular concave recess 17e into which a convex portion 16h formed so as to protrude in a rectangular shape is fitted to the bearing housing 16 is recessed along the direction of the rotation axis of the balancer shaft 9.
  • two triangular lightening portions 17f provided for weight reduction of the balancer housing 8 are formed as openings.
  • the base mating surface 17d is provided with a dowel pin 19a that is press-fitted into a positioning hole (not shown) provided in the mating surface 16a of the bearing housing 16.
  • a fixing member for example, a bolt 20, is screwed to the first balancer weight 10 side of the base mating surface 17d with respect to the dowel pin 19a via a fixing member through hole 16d provided in the mounting portion 16b of the bearing housing 16.
  • a screw hole 17h is formed.
  • the overhanging portion 18 is formed flush with the base mating surface 17d and has a flat overhanging mating surface 18a that is aligned with the mating surface 16a of the bearing housing 16. Further, the overhanging portion mating surface 18a is provided with a dowel pin 19b that is press-fitted into a positioning hole (not shown) provided in the mating surface 16a of the bearing housing 16. Further, a screw in which a bolt 21 is screwed to the first balancer weight 10 side of the overhanging portion mating surface 18a with respect to the dowel pin 19b via a fixing member through hole 16e provided in the mounting portion 16c of the bearing housing 16. A hole 18c is formed. Further, the overhanging portion 18 is connected to the side of the base portion 17 via a connecting portion 22 having a rectangular plate shape. The connection portion 22 is formed with openings of two substantially rectangular meat stealing portions 23 provided for reducing the weight of the balancer housing 8.
  • a mounting portion 25 attached to the lower part of the engine block 2 is a balancer. It is integrally formed with the housing 8.
  • Each mounting portion 25 is formed with a bolt through hole 25a through which a bolt (not shown) penetrates when mounted on the engine block 2 in the thickness direction of the base portion 17.
  • a columnar first journal portion 26 and a second journal portion 27 used for bearings of the balancer shaft 9 are formed in the vicinity of one end 9a and the other end 9b in the direction of the rotation axis of the balancer shaft 9, respectively.
  • the first journal portion 26 has a columnar shape having an outer diameter larger than that of the other portions of the balancer shaft 9 excluding the second journal portion 27, and has one end portion 9a to the other end portion 9b in the direction of the rotation axis of the balancer shaft 9. It is formed at a position slightly offset to the side. In other words, one end 9a of the balancer shaft 9 slightly protrudes from the first journal portion 26 to the side opposite to the second journal portion 27 along the rotation axis direction of the balancer shaft 9.
  • the first journal portion 26 is rotatably supported via a cylindrical first needle bearing 28 provided in the first balancer bearing portion 16f of the bearing housing 16.
  • the second journal portion 27 has a columnar shape having an outer diameter larger than that of the other portions of the balancer shaft 9 excluding the first journal portion 26, and the other end portion 9b to the one end portion 9a in the direction of the rotation axis of the balancer shaft 9. It is formed at a position slightly offset to the side. In other words, the other end 9b of the balancer shaft 9 slightly protrudes from the second journal portion 27 to the side opposite to the first journal portion 26 along the rotation axis direction of the balancer shaft 9.
  • the second journal portion 27 can rotate between the balancer gear 30 and the second balancer weight 31, which will be described later, via a cylindrical second needle bearing 29 provided in the second balancer bearing portion 24a of the end wall portion 24. It is supported.
  • the balancer shaft 9 rotatably supported by the first and second journal portions 26, 27 has a first balance weight 10, a balance gear 30, and a second balance weight 31 in this order from one end 9a to the other end 9b. It is provided.
  • the first balancer weight 10 is fixed to the outer peripheral portion of one end portion 9a of the balancer shaft 9, and is formed in a fan shape that expands in diameter in a state of being displaced in the radial direction about the rotation axis of the balancer shaft 9.
  • the first balancer weight 10 is screwed to the screw hole 9d of the axial end surface 9c on the one end portion 9a side of the balancer shaft 9 by a bolt 32 through the weight through hole 10a penetrating in the thickness direction of the balancer shaft 9. It is attached and fixed to 9.
  • the second balancer weight 31 has the same shape as the first balancer weight 10, and is fixed to the outer peripheral portion of the other end 9b of the balancer shaft 9.
  • the second balancer weight 31 is formed in a fan shape that expands in diameter in a state of being displaced 180 degrees in the radial direction from the first balancer weight 10 about the rotation axis of the balancer shaft 9.
  • the second balancer weight 31 is screwed into a screw hole (not shown) on the axial end surface 9e on the other end 9b side of the balancer shaft 9 by a bolt 33 through a weight through hole 31a penetrating in the thickness direction thereof. It is attached and fixed to the balancer shaft 9.
  • the bearing housing 16 is made of a metal material having a larger unit volume weight (weight per unit volume) than the aluminum balancer housing 8, for example, iron.
  • the bearing housing 16 may be made of cast iron.
  • the bearing housing 16 is used to support the oil pump shaft 11 of the oil pump 7, and makes the entire circumference of the oil pump shaft 11 parallel to the rotation axis of the balancer shaft 9 in the circumferential direction with respect to the rotation axis of the oil pump shaft 11.
  • the shaft support portion 16g to be covered and the mating surface 16a of the bearing housing 16 joined to the base mating surface 17d and the overhanging mating surface 18a project in a rectangular shape toward the balancer housing 8 and are fitted into the recess 17e of the balancer housing 8.
  • the shaft support portion 16g does not need to be covered by the bearing housing 16 in the circumferential direction, and the bearing housing 16 and the bearing housing 16 are formed separately according to the layout. A part or the whole of the shaft support portion 16g may be covered with a cap member or the like.
  • a shaft bearing portion 16i that rotatably supports the oil pump shaft 11 is formed so as to penetrate in the rotation axis direction of the oil pump shaft 11 parallel to the balancer shaft 9.
  • the first balancer bearing portion 16f is provided at a position closer to the tip portion of the convex portion 16h than the shaft bearing portion 16i, and overlaps with the shaft bearing portion 16i in the radial direction of the balancer shaft 9.
  • the bearing housing 16 has an expansion portion 16j that extends radially outward from the outer surface thereof.
  • a gear (not shown) that accommodates a balancer gear 30 and an intermediate gear 35 described later between the expansion portion 16j and a pump body 34 having an open end of the oil pump 7 at a portion facing the oil pump 7.
  • a containment unit is provided.
  • the pump body 34 has four bolt through holes 34a on the outer peripheral portion thereof through which the bolts 36 penetrate when attached to the bearing housing 16.
  • the pump body 34 is attached to the bearing housing 16 by screwing each bolt 36 into the screw hole portion 16n provided in the bearing housing 16 via the bolt through holes 34a. Further, the positioning of the pump body 34 with respect to the bearing housing 16 is performed by fitting the positioning pins 34b, 34c provided on the open end surface of the pump body 34 into the positioning holes 55, 56 provided in the expansion portion 16j.
  • the oil pump shaft 11 is arranged so as to extend in parallel with the balancer shaft 9. That is, the oil pump shaft 11 is arranged in parallel adjacent to the radial direction of the balancer shaft 9 so that its rotation axis direction is parallel to the rotation axis direction of the balancer shaft 9.
  • the total length of the oil pump shaft 11 is shorter than the total length of the balancer shaft 9, and is arranged in parallel with one end portion 9a close to one end portion 9a.
  • a columnar large diameter portion 11b is formed at the first end portion 11a of the oil pump shaft 11.
  • the large diameter portion 11b has a columnar shape having an outer diameter larger than that of other portions of the oil pump shaft 11 except for the third journal portion 38, which will be described later.
  • the pump sprocket 12 is attached to the axial end surface 11c on the first end portion 11a side of the large diameter portion 11b via the bolt 37 in a state of being in contact with the facing end surface of the pump sprocket 12. As a result, the movement of the pump sprocket 12 to the oil pump 7 side is restricted.
  • a columnar third journal portion 38 is formed in a portion of the oil pump shaft 11 that is radially adjacent to the first journal portion 26 of the balancer shaft 9.
  • the third journal portion 38 has a columnar shape having an outer diameter larger than that of other portions of the oil pump shaft 11 except for the large diameter portion 11b.
  • the third journal portion 38 is rotatably supported by the shaft bearing portion 16i of the bearing housing 16 via a cylindrical third needle bearing 39.
  • the intermediate gear 35 adjacent to the third journal portion 38 in the direction of the rotation axis is a helical gear made of the same metal material as the bearing housing 16 and iron in the present embodiment.
  • the intermediate gear 35 may be made of cast iron.
  • the intermediate gear 35 is located on the outer peripheral portion of the oil pump shaft 11 so as to be axially overlapped with the balancer gear 30 when viewed from the radial direction at a position in the rotation axis direction between the third journal portion 38 and the pump body 34. It is connected.
  • the gear ratios of the crank sprocket 4, the pump sprocket 12, the intermediate gear 35, and the balancer gear 30 are set so that the balancer shaft 9 rotates in the opposite direction to the crank shaft 3 at the same rotation speed.
  • the number of teeth of the intermediate gear 35 and the number of teeth of the balancer gear 30 may be the same, and the number of teeth of the balancer gear 30 may be smaller than the number of teeth of the intermediate gear 35, or the balancer gear 30. There may be more 30 teeth.
  • the balancer gear 30 is connected to the outer peripheral portion of the balancer shaft 9, and the first needle bearing 28 is attached to the first journal portion 26 of the balancer shaft 9. Further, the intermediate gear 35 is connected to the outer peripheral portion of the oil pump shaft 11, and the third needle bearing 39 is attached to the third journal portion 38 of the oil pump shaft 11.
  • the other end 9b of the balancer shaft 9 to which the balancer gear 30 is connected is provided in the balancer housing 8, and in the circumferential direction, the second journal portion 27 of the balancer shaft 9 It is inserted into the second balancer bearing portion 24a that covers the entire circumference.
  • the second balancer bearing portion 24a does not need to be covered with the balancer housing 8 on the entire circumference in the circumferential direction, and is a cap formed separately from the balancer housing 8 depending on the layout. A part of the second balancer bearing portion 24a may be covered with a member or the like.
  • the balancer housing 8 is inserted so that one end 9a of the balancer shaft 9 is located closer to the second balancer bearing portion 24a than the recess 17e, and the second needle bearing 29 is inserted into the second journal portion 27 of the balancer shaft 9. Install.
  • the bearing housing 16 is attached to the balancer housing 8 so that the convex portion 16h of the shaft bearing portion 16i is fitted into the concave portion 17e of the balancer housing 8.
  • two dowel pins 19a and 19b provided on the base mating surface 17d and the overhanging mating surface 18a of the balancer housing 8 are press-fitted into the corresponding positioning holes of the mating surface 16a of the bearing housing 16.
  • the two bolts 20 and 21 are screwed into the screw holes 17h of the base 17 and the screw holes 18c of the overhanging portion 18 through the two fixing member through holes 16d and 16e of the bearing housing 16.
  • the balancer shaft 9 and the oil pump shaft 11 are slid in the axial direction with the balancer gear 30 and the intermediate gear 35 meshed with each other, and the first needle bearing on the outer peripheral portion of the balancer shaft 9 is provided.
  • the third needle bearing 39 on the outer periphery of the 28 and the oil pump shaft 11 is press-fitted into the first balancer bearing portion 16f and the shaft bearing portion 16i.
  • the second needle bearing 29 on the outer peripheral portion of the balancer shaft 9 is press-fitted into the second balancer bearing portion 24a.
  • the pump body 34 of the oil pump 7 is attached to the bearing housing 16. This mounting is performed by screwing each bolt 36 into each screw hole portion 16n of the bearing housing 16 through each bolt through hole 34a of the pump body 34.
  • the first balancer weight 10 is attached to one end 9a of the balancer shaft 9
  • the second balancer weight 31 is attached to the other end 9b of the balancer shaft 9
  • the first oil pump shaft 11 is attached.
  • the pump sprocket 12 is attached to the end portion 11a by fastening the bolts 32, 33, and 37.
  • FIG. 4 is a partial cross-sectional view of a prior art balancer device.
  • the balancer gear 30, the first balancer weight 10, and the first needle bearing 28 are provided in order from one end 9a in the direction of the rotation axis of the balancer shaft 9. More specifically, as shown in FIG. 4, one end 9a of the balancer shaft 9 protrudes to the outside of the balancer housing 8 and has a free end, and the balancer gear 30 and the first balance weight 10 are attached to the free end. Further, the first needle bearing 28 is fixed to the inner peripheral surface of the bearing hole 8s of the balancer housing 8.
  • the first balancer weight 10 provided at one end 9a, which is a free end, rotates.
  • the balancer shaft 9 is subjected to the first balancer weight 10 by the arrow A in FIG. As shown, it is swung (flexed) downward of the balancer shaft 9.
  • the balancer gear 30 adjacent to the outside of the first balancer weight 10 is also swung downward as shown by the arrow B in FIG. 4, strongly abuts on the transmission gear 40, and has teeth with the transmission gear 40. There was a problem that a tapping sound was generated.
  • the first balancer weight 10 and the balancer gear 30 are provided in order from the end of the balancer shaft 9 in the direction of the rotation axis, and further, the first balancer weight 10 and the balancer gear 30 are provided.
  • a first balancer bearing portion 16f that rotatably supports the balancer shaft 9 is provided between the two. That is, the first balancer weight 10, the first balancer bearing portion 16f, and the balancer gear 30 are aligned in this order from one end portion 9a in the rotation axis direction of the balancer shaft 9.
  • the first balancer weight 10 is fixed to the outer peripheral portion of the one end portion 9a which is a free end, and the first balancer bearing portion 16f supports the balancer shaft 9 via the first needle bearing 28.
  • the balancer gear 30 is fixed to the balancer shaft 9 on the side opposite to the first balancer weight 10 with the first balancer bearing portion 16f interposed therebetween. Therefore, when the balancer shaft 9 is oscillated in the radial direction due to the rotation of the first balancer weight 10 during the rotational drive of the balancer shaft 9, this deflection is suppressed by the bearing housing 16 that supports the first balancer bearing portion 16f. Therefore, it is difficult for the balancer gear 30 to be transmitted to the balancer gear 30 inside the rotation axis direction of the first balancer bearing portion 16f.
  • the balancer gear 30 is swung in the radial direction and strongly abuts on the intermediate gear 35, and it is possible to suppress the generation of rattling noise between the balancer gear 30 and the intermediate gear 35. ..
  • the shaft bearing portion 16i and the first balancer bearing portion 16f are provided in the bearing housing 16 formed separately from the balancer housing 8. That is, when the first balancer weight 10, the first balancer bearing portion 16f, and the balancer gear 30 are arranged in the above order, if the bearing housing 16 is integrally formed with the balancer housing 8, the balancer gear 30 and the intermediate gear 35 Since the alignment mark provided on the balancer housing 16 is made difficult to see by the bearing housing 16, it becomes difficult to align the phase of the balancer gear 30 and the intermediate gear 35, and the assembly efficiency of the balancer device is lowered.
  • the shaft bearing portion 16i and the first balancer bearing portion 16f are provided in the bearing housing 16 which is separate from the balancer housing 8, so that the bearing housing 16 is assembled at the time of assembling the balancer device.
  • the balancer gear 30 and the intermediate gear 35 can be easily phase-matched while looking at the alignment marks provided on the balancer gear 30 and the intermediate gear 35 from the first balancer weight 10 side. Assembly efficiency can be improved.
  • the oil pump shaft 11 has a first end portion 11a and a second end portion in the direction of its rotation axis, and the rotational force from the internal combustion engine is transmitted to the first end portion 11a.
  • a pump sprocket 12 is provided, and an oil pump 7 is provided at the second end. Therefore, a single oil pump shaft 11 contributes to both driving the oil pump 7 and reversing the balancer gear 30. More specifically, the oil pump shaft 11 drives the oil pump 7 by rotation from the pump sprocket 12, and the balancer gear 30 on the outer peripheral portion of the balancer gear 30 is driven by the intermediate gear 35 on the outer peripheral portion of the oil pump shaft 11. Invert. Therefore, it is possible to efficiently drive the oil pump 7 and reverse the balancer gear 30 with a simple structure, as compared with the case where a new shaft is provided and the balancer shaft 9 is reversed.
  • the oil pump 7 is attached to the bearing housing 16. Therefore, the radial alignment of the oil pump shaft 11 becomes easier as compared with the case where the oil pump 7 is attached to the balancer housing 8. More specifically, if the oil pump 7 is attached to the balancer housing 8, the radial direction of the bearing portion of the oil pump 7 with respect to the shaft bearing portion 16i of the bearing housing 16 due to an attachment error between the two. There is a risk that the position of the oil pump shaft 11 will be displaced and it will be difficult to align the oil pump shaft 11 in the radial direction. However, as in the present embodiment, the oil pump 7 is directly attached to the bearing housing 16 to eliminate the above attachment error and facilitate the radial alignment of the oil pump shaft 11.
  • the bearing housing 16 is provided so as to face the oil pump 7 in the direction of the rotation axis of the balancer shaft 9, and includes a gear accommodating portion for accommodating the balancer gear 30 and the intermediate gear 35. Therefore, even if the oil in the oil pan 5 is scattered due to a factor such as an external input and tries to enter the gear accommodating portion, the balancer gear 30 and the intermediate gear 35 are covered by the gear accommodating portion, so that the gear accommodating. The intrusion of oil is suppressed by the part. As a result, it is possible to prevent the oil from reaching the balancer gear 30 and the intermediate gear 35 and causing rotational resistance.
  • the balancer housing 8 has a recess 17b on the surface 17a on the side where the balancer shaft 9 is provided, and the bearing housing 16 has a convex portion 16h fitted into the recess 17e. Therefore, the bearing housing 16 can be easily positioned with respect to the balancer housing 8 by the uneven fitting of the concave portion 17e and the convex portion 16h.
  • the base mating surface 17d and the overhanging mating surface 18a of the balancer housing 8 are provided with a pair of positioning holes for positioning with the bearing housing 16 on both sides of the recess 17e.
  • the bearing housing 16 is also provided with a pair of positioning holes for positioning with the balancer housing 8. Then, the pair of dowel pins 19a and 19b are fitted into the pair of positioning holes of the balancer housing 8 and the pair of positioning holes of the bearing housing 16. Therefore, the bearing housing 16 can be easily positioned with respect to the balancer housing 8 by the uneven fitting of the positioning holes and the dowel pins 19a and 19b.
  • the pair of dowel pins 19a and 19b are provided on both sides of the balancer housing 8 with the recesses 17e of the base mating surface 17d of the balancer housing 8 provided in a state where the pair of dowel pins 19a and 19b are provided in at least one of the pair of positioning holes provided in the bearing housing 16. It may be fitted into at least one of the pair of positioning holes.
  • the first balance weight 10 is arranged in the oil pan 5 so as to be located vertically above the oil level 6 of the oil in the oil pan 5. Therefore, since it is difficult for the first balancer weight 10 to hit the oil level 6 of the oil when the balancer shaft 9 is rotationally driven, it is possible to suppress the generation of rotational resistance of the balancer shaft 9 and the generation of oil aeration. Therefore, the balancer device can be operated efficiently, and each sliding portion of the internal combustion engine can be smoothly lubricated by oil containing no air.
  • the intermediate gear 35 and the bearing housing 16 are formed of iron, which is the same metal material.
  • the intermediate gear 35 and the bearing housing 16 may be made of cast iron. Therefore, when the intermediate gear 35 and the bearing housing 16 undergo thermal expansion or contraction due to some factor, for example, the temperature rise of the internal gear engine after the start of operation, both the intermediate gear 35 and the bearing housing 16 have the same ratio. Since it expands or contracts, it is between the intermediate gear 35 and the bearing housing 16 in the rotation axis direction (thrust direction) of the oil pump shaft 11 as compared with the case where the intermediate gear 35 and the bearing housing 16 are made of different metal materials. Clearance can be easily managed.
  • the balancer gear 30, the intermediate gear 35, and the bearing housing 16 are formed of iron, which is one of the metal materials having the same coefficient of linear expansion, while the balancer housing 8 has a coefficient of linear expansion larger than that of iron. It is made of aluminum.
  • the bearing housing 16 undergoes thermal expansion or contraction due to some factor, for example, the temperature rise of the internal combustion engine after the start of operation, and the distance between the rotating shafts of the intermediate gear 35 and the balancer gear 30 changes, the intermediate gear Since the 35 and the balancer gear 30 also expand or contract at the same rate as the bearing housing 16, backlash between the tooth portion of the intermediate gear 35 and the tooth portion of the balancer gear 30 can be easily managed.
  • FIG. 5 is an exploded perspective view of the balancer device of the second embodiment.
  • the bearing housing 16 is integrated with the balancer housing 8 of the first embodiment to form an aluminum balancer housing 8, and further, the second balancer bearing portion 24a is formed in a half shape. It is formed. Therefore, the first balancer bearing portion 16f and the shaft bearing portion 16i are formed in the balancer housing 8, and the second balancer bearing portion 24a is formed in a half-split shape integrally with the end wall portion 24 of the balancer housing 8. It is composed of a first bearing half portion 24b and a second bearing half portion 41f formed on a first cap member 41 that is separate from the balancer housing 8.
  • a flat surface 17j offset from the surface 17a of the base 17 to the first cap member 41 side via the step portion 17i is formed on the upper portion of the end wall portion 24.
  • a first bearing half portion 24b recessed in an arcuate shape with respect to the flat surface 17j is along the rotation axis direction of the balancer shaft 9. It is formed.
  • the flat surface 17j is press-fitted into two positioning holes (not shown) provided in the first cap member 41 at positions closer to the second balancer weight 31 on both sides of the first bearing half portion 24b.
  • a pair of dowel pins 42a and 42b are provided.
  • a pair of bolts provided on the first cap member 41 at positions closer to the first balancer weight 10 than the pair of dowel pins 42a and 42b on both sides of the flat surface 17j with the first bearing half portion 24b interposed therebetween.
  • a pair of screw holes 17k and 17m are formed through which the bolts 43 and 44 are screwed through the through holes 41d and 41e.
  • the first cap member 41 is made of a metal material such as aluminum.
  • the first cap member 41 is a rectangular plate formed integrally with an arc portion 41a having a curved plate shape along the outer circumference of the second needle bearing 29 and both ends of the arc portion 41a and extending in parallel with the flat surface 17j. It has a pair of side portions 41b and 41c in the shape of a shape.
  • a second bearing half portion 41f forming a circular second balancer bearing portion 24a with the first bearing half portion 24b of the end wall portion 24 is provided.
  • the second bearing half portion 41f is provided along the rotation axis direction of the balancer shaft 9.
  • the pair of side portions 41b and 41c have bolt through holes 41d and 41e through which the bolts 43 and 44 penetrate at positions corresponding to the screw holes 17k and 17m provided on the flat surface 17j.
  • the shaft bearing portion 16i and the first balancer bearing portion 16f are formed in the balancer housing 8, and the second balancer bearing portion 24a is formed separately from the balancer housing 8 and the balancer housing 8. It is composed of the first cap member 41. Therefore, it is sufficient to cover the second needle bearing 29 installed on the first bearing half portion 24b with the first cap member 41 without press-fitting the second needle bearing 29 into the second balancer bearing portion 24a.
  • the balancer shaft 9 can be assembled more easily than the balancer device of the first embodiment.
  • FIG. 6 is an exploded perspective view of the balancer device of the third embodiment.
  • the balancer housing 8 of the first embodiment is integrated with the portion of the bearing housing 16 including the shaft bearing portion 16i to form the aluminum balancer housing 8, and the first balancer bearing portion is formed.
  • 16f is formed in a half shape.
  • the shaft bearing portion 16i and the second balancer bearing portion 24a are formed in the balancer housing 8, and the first balancer bearing portion 16f is formed in a half-split shape integrally with the base portion 17 of the balancer housing 8. It is composed of a third bearing half portion 17n and a fourth bearing half portion 45b formed on a second cap member 45 that is separate from the balancer housing 8.
  • a third bearing half portion 17n recessed in an arcuate shape with respect to the base mating surface 17d is formed along the rotation axis direction of the balancer shaft 9. Further, a pair of screw holes 17h and 17o are formed on both sides of the base mating surface 17d with the third bearing half portion 17n interposed therebetween, and the screw holes 17h and 17o are provided in the second cap member 45.
  • the second cap member 45 is attached and fixed to the balancer housing 8 by screwing the pair of bolts 46 and 47 through the pair of bolt through holes 45c and 45d.
  • the second cap member 45 is made of a metal material having a unit volume weight larger than that of the aluminum balancer housing 8, for example, iron.
  • the second cap member 45 may be made of cast iron.
  • the second cap member 45 is formed as a remaining portion after removing the convex portion 16h of the bearing housing 16 of the first embodiment and the portion including the shaft bearing portion 16i of the bearing housing 16.
  • an arcuate fourth bearing half portion 45b forming a circular first balancer bearing portion 16f with the third bearing half portion 17n is formed.
  • a pair of bolt through holes 45c and 45d through which a pair of bolts 46 and 47 penetrate are formed at positions of the second cap member 45 facing the pair of screw holes 17h and 17o on the base mating surface 17d. ..
  • the shaft bearing portion 16i and the second balancer bearing portion 24a are formed in the balancer housing 8, and the first balancer bearing portion 16f has a unit volume weight larger than that of the balancer housing 8 and the balancer housing 8. It is composed of a first cap member 41. That is, the shaft bearing portion 16i and the second balancer bearing portion 24a are formed in the aluminum balancer housing 8, and the first balancer bearing portion 16f is formed by the balancer housing 8 and the first cap member 41 made of iron. It is configured. Therefore, since the portion constituting the shaft bearing portion 16i is also made of aluminum, which is lighter than iron, the balancer device can be made lighter than the balancer device of the first embodiment.
  • FIG. 7 is an exploded perspective view of the balancer device of the fourth embodiment.
  • the bearing housing 16 is integrated with the balancer housing 8 of the first embodiment to form the aluminum balancer housing 8. Therefore, the first and second balancer bearing portions 16f and 24a and the shaft bearing portion 16i are formed in the balancer housing 8.
  • the shaft bearing portion 16i, the first balancer bearing portion 16f, and the second balancer bearing portion 24a are all integrally formed with the balancer housing 8.
  • the bearing housing 16 of the first embodiment, the first cap member 41 of the second embodiment, and the second cap member 45 of the third embodiment are unnecessary. Therefore, the number of parts of the balancer device can be reduced, and the manufacturing cost of the balancer device can be reduced.
  • FIG. 8 is an exploded perspective view of the balancer device according to the fifth embodiment.
  • the second balancer bearing portion 24a of the balancer housing 8 of the third embodiment is formed in a half shape, and the shaft bearing portion 16i is integrally formed with the balancer housing 8. Further, the first balancer bearing portion 16f is formed on a half-split third bearing half portion 17n integrally formed with the base portion 17 of the balancer housing 8 and a second cap member 45 separate from the balancer housing 8.
  • the second balancer bearing portion 24a which is composed of the fourth bearing half portion 45b, is separated from the half-split first bearing half portion 24b formed integrally with the end wall portion 24 of the balancer housing 8 and the balancer housing 8. It is composed of a second bearing half portion 41f formed on the first cap member 41 of the body.
  • the shaft bearing portion 16i is formed in the balancer housing 8, and the first balancer bearing portion 16f is the balancer housing 8 and the second cap member 45 formed separately from the balancer housing 8.
  • the second balancer bearing portion 24a is composed of a balancer housing 8 and a first cap member 41 formed separately from the balancer housing 8.
  • both the first and second balancer bearing portions 16f and 24a are formed in a half-split shape.
  • the first and second needle bearings 28 and 29 installed on the third and first bearing halves 17n and 24b without press-fitting the first and second needle bearings 28 and 29 into the first and second balancer bearings 16f and 24a. Since the second needle bearings 28 and 29 may be covered with the second and first cap members 45 and 41, the balancer shaft 9 can be easily assembled.
  • FIG. 9 is an exploded perspective view of the balancer device of the sixth embodiment.
  • the shaft bearing portion 16i and the first balancer bearing portion 16f in FIG. 7 are formed in a half-split shape. Therefore, the second balancer bearing portion 24a, the third bearing half portion 17n, and the fifth bearing half portion 18d, which is the lower half portion of the shaft bearing portion 16i, are formed in the balancer housing 8 to form the fourth bearing.
  • the half portion 45b and the sixth bearing half portion 48b, which is the upper half portion of the shaft bearing portion 16i, are formed in the third cap member 48.
  • the overhanging portion 18 of the balancer housing 8 has an overhanging portion mating surface 18a provided at a position offset to the vertical oil pump 7 side from the base mating surface 17d of the base 17 via the stepped portion 18e. ..
  • a fifth bearing half portion 18d recessed in an arcuate shape is formed along the rotation axis direction of the oil pump shaft 11 at a position closer to the third bearing half portion 17n in the overhanging portion mating surface 18a.
  • a dowel pin 49 that is press-fitted into a positioning hole (not shown) provided in the third cap member 48 is provided.
  • a screw hole 18f is provided at a position between the dowel pin 49 and the fifth bearing half portion 18d on the overhanging portion mating surface 18a, and the screw hole 18f is provided in the third cap member 48.
  • the third cap member 48 is attached and fixed to the balancer housing 8 by screwing the bolt 50 through the bolt through hole 48d.
  • the third cap member 48 has an oil pump shaft side mating surface 48a that is abutted against the overhanging mating surface 18a at a position facing the overhanging mating surface 18a of the overhanging portion 18.
  • a sixth bearing half portion 48b recessed in an arcuate shape is formed along the rotation axis direction of the oil pump shaft 11 at a position closer to the fourth bearing half portion 45b on the oil pump shaft side mating surface 48a. There is.
  • a bolt through hole 48d through which the bolt 50 penetrates is formed through the third cap member 48 at a position facing the screw hole 18f on the overhanging portion mating surface 18a.
  • the shaft bearing portion 16i and the first balancer bearing portion 16f are composed of the balancer housing 8 and the third cap member 48 formed separately from the balancer housing 8, and the second balancer.
  • the bearing portion 24a is formed in the balancer housing 8.
  • the first and third cap members 48 are placed on the half-split third and fifth bearing halves 17n and 18d with the first and third needle bearings 28 and 39 installed. Needle bearings 28 and 39 are assembled at the same time. Therefore, as compared with the case where the balancer shaft 9 and the oil pump shaft 11 are slid in the axial direction to assemble the first and third needle bearings 28 and 39, the first and third needle bearings 28 and 39 can be easily assembled. It can be carried out.
  • FIG. 10 is an exploded perspective view of the balancer device of the seventh embodiment.
  • the first balancer weight 10, the first balancer bearing portion 16f, and the balancer gear 30 are provided in order from one end portion 9a in the rotation axis direction of the balancer shaft 9, but the seventh embodiment.
  • the first balancer weight 10, the balancer gear 30, and the first balancer bearing portion 16f are provided in order from one end portion 9a in the rotation axis direction of the balancer shaft 9. That is, the balancer gear 30 may be arranged near the position closer to the first balancer bearing portion 16f than the first balancer weight 10 in the direction of the rotation axis of the balancer shaft 9.
  • the balancer gear 30 is arranged so that the distance from the first balancer bearing portion 16f to the balancer gear 30 is shorter than the distance from the first balancer bearing portion 16f to the first balancer weight 10. Just do it.
  • the first balancer bearing portion 16f is arranged at a position sandwiching the balancer gear 30 together with the first balancer weight 10 in the direction of the rotation axis of the balancer shaft 9.
  • an intermediate gear 35 and a third journal portion 38 are provided in order from one end portion 11b in the rotation axis direction of the oil pump shaft 11.
  • the first balancer weight 10, the balancer gear 30, and the first balancer bearing portion 16f are provided in order from one end portion 9a in the rotation axis direction of the balancer shaft 9.
  • the balancer gear 30 is arranged at a position closer to the first balancer bearing portion 16f, which has a relatively high rigidity, than the first balancer weight 10. Therefore, as compared with the case where the balancer gear 30 is arranged at a position farther than the first balancer weight 10 with respect to the first balancer bearing portion 16f, the radial runout of the balancer gear 30 during rotation of the first balancer weight 10 Can be reduced to suppress the generation of rattling noise between the balancer gear 30 and the intermediate gear 35.
  • the balancer gear 30 having a diameter larger than that of the first journal portion 26 is arranged outside the first journal portion 26.
  • the balancer gear 30 is arranged inside the first journal portion 26, the phase matching between the balancer gear 30 and the intermediate gear 35 becomes easier, and the balancer device can be easily assembled.
  • first, second, and third needle bearings 28, 29, and 39 are other rolling elements such as roller bearings and ball bearings having the same function as long as the intention of the present invention is not deviated. It can also be replaced with bearings and plain bearings.
  • the balancer gear 30 and the intermediate gear 35 in the above-described embodiment can be replaced with spur gears having the same function as long as the intent of the present invention is not deviated.
  • balancer device based on the embodiment described above, for example, the one described below can be considered.
  • the balancer device provided in the internal combustion engine is, as one aspect, a balancer housing attached to the internal combustion engine and a balancer shaft rotatably supported by the balancer housing, and is an end portion of the balancer shaft in the direction of the rotation axis. From the first, the balancer shaft provided with the first balancer weight, the balancer gear, and the second balancer weight, and the shaft provided in parallel with the balancer shaft and provided with an intermediate gear that meshes with the balancer gear. , The shaft bearing portion that rotatably supports the shaft, and the diameter of the balancer shaft with respect to the rotation axis of the balancer shaft, which is arranged between the first balancer weight and the second balancer weight and rotatably supports the balancer shaft.
  • a first balancer bearing portion provided at a position overlapping the shaft bearing portion in the direction, and the balancer gear is provided between the first balancer weight and the balancer gear, and together with the first balancer weight.
  • the first balancer bearing portion provided at one of the sandwiching positions and the second balancer bearing portion that rotatably supports the balancer shaft are provided.
  • the shaft bearing portion and the first balancer bearing portion are provided in a bearing housing formed separately from the balancer housing.
  • the material of the bearing housing has a larger unit volume weight than the material of the balancer housing.
  • the material of the bearing housing has a closer coefficient of linear expansion to the balancer gear and the intermediate gear than the material of the balancer housing.
  • the shaft has a first end and a second end in the direction of rotation of the shaft, the first end of which is the internal combustion engine.
  • a sprocket to which the rotational force from the engine is transmitted is provided, and an oil pump is provided at the second end portion.
  • the oil pump is attached to the bearing housing.
  • the first balancer bearing portion is provided between the first balancer weight and the balancer gear, and the bearing housing is a rotation of the balancer shaft. It is provided so as to face the oil pump in the axial direction, and includes a gear accommodating portion for accommodating the balancer gear and the intermediate gear.
  • the balancer housing has a recess on the side surface on which the balancer shaft is provided, and the bearing housing has a protrusion that is fitted into the recess.
  • the surface of the balancer housing is provided with a pair of positioning holes for positioning with the bearing housing on both sides of the recess.
  • the bearing housing is also provided with the pair of positioning holes, and is provided with a pair of pins fitted into both the positioning holes of the balancer housing and the positioning holes of the bearing housing.
  • the second balancer bearing portion is formed in the balancer housing.
  • the shaft bearing portion provided in the bearing housing covers the entire circumference of the shaft in a circumferential direction with respect to the rotation axis of the shaft.
  • the first balancer bearing portion provided in the above covers the entire circumference of the balancer shaft in the circumferential direction with respect to the rotation axis of the balancer shaft, and the second balancer bearing portion is separate from the balancer housing and the balancer housing. It is formed by a member formed on the body and covers the balancer shaft in a circumferential direction with respect to the rotation axis of the balancer shaft.
  • the first balancer weight is arranged in the oil pan so as to be located above the oil level of the oil in the oil pan.
  • the shaft bearing portion and the first balancer bearing portion are formed in the balancer housing, and the second balancer bearing portion is formed in the balancer housing and the balancer housing. It is composed of a first cap member formed separately from the balancer housing.
  • the shaft bearing portion and the second balancer bearing portion are formed in the balancer housing, and the first balancer bearing portion is formed in the balancer housing and the balancer housing. It is composed of a cap member formed separately from the balancer housing.
  • the shaft bearing portion, the first balancer bearing portion and the second balancer bearing portion are formed in the balancer housing.
  • the shaft bearing portion is formed in the balancer housing, and the first balancer bearing portion is a separate body of the balancer housing and the balancer housing. It is composed of a formed second cap member, and the second balancer bearing portion is composed of the balancer housing and a first cap member formed separately from the balancer housing.
  • the shaft bearing portion and the first balancer bearing portion include the balancer housing and a third cap member formed separately from the balancer housing.
  • the second balancer bearing portion is formed in the balancer housing.
  • the shaft bearing portion is formed by the balancer housing and a member formed separately from the balancer housing, and the rotation axis of the shaft. Cover the shaft in the circumferential direction with respect to The first balancer bearing portion is formed by the balancer housing and a member formed separately from the balancer housing, and covers the entire circumference of the balancer shaft in a circumferential direction with respect to the rotation axis of the balancer shaft.
  • the second balancer bearing portion provided in the balancer housing covers the entire circumference of the balancer shaft in the circumferential direction with respect to the rotation axis of the balancer shaft.
  • balancer device based on the above-described embodiment, for example, the one described below can be considered.
  • One aspect of the balancer device with an oil pump provided in the internal combustion engine is a balancer housing attached to the internal combustion engine, a balancer shaft rotatably supported by the balancer housing, and a first balance weight.
  • the balancer shaft provided with the balancer gear and the second balancer weight, the oil pump shaft arranged in parallel with the balancer shaft and provided with the intermediate gear that meshes with the balancer gear, and the oil pump shaft are inserted.
  • a first balancer bearing portion that is arranged between gears, rotatably supports the balancer shaft, and is formed in the same member as the shaft bearing portion in whole or in part, and is the first balancer weight and the balancer bearing portion.
  • the first balancer bearing portion provided between the balancer gear and at a position where the balancer gear is sandwiched together with the first balancer weight, and a second balancer bearing portion that rotatably supports the balancer shaft. , Equipped with.

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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)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Lubrication Details And Ventilation Of Internal Combustion Engines (AREA)

Abstract

Dispositif d'équilibrage comprenant : un carter d'équilibrage (8) ; et un arbre d'équilibrage (9) qui est supporté rotatif par le carter d'équilibrage (8). L'arbre d'équilibrage (9) est pourvu, de manière séquentielle, à partir de son extrémité (9a) dans une direction d'axe de rotation, d'un premier poids d'équilibrage (10), d'un pignon d'équilibrage (30) et d'un second poids d'équilibrage (31). Un premier palier d'équilibrage (16f) qui supporte de manière rotative l'arbre d'équilibrage (9) est disposé entre le premier poids d'équilibrage (10) et l'engrenage d'équilibrage (30).　En conséquence, le premier poids d'équilibrage (10), le premier palier d'équilibrage (16f) et le pignon d'équilibrage (30) sont alignés de manière séquentielle à partir de l'extrémité (9a) de l'arbre d'équilibrage (9) dans la direction de l'axe de rotation.
PCT/JP2021/006996 2020-03-18 2021-02-25 Dispositif d'équilibrage et dispositif d'équilibrage pourvu d'une pompe à huile WO2021187033A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2020-047076 2020-03-18
JP2020047076A JP2023062210A (ja) 2020-03-18 2020-03-18 バランサ装置およびオイルポンプ付きバランサ装置

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WO2021187033A1 true WO2021187033A1 (fr) 2021-09-23

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5458501U (fr) * 1977-09-30 1979-04-23
JP2000297845A (ja) * 1999-04-14 2000-10-24 Isuzu Motors Ltd 内燃機関のバランサシャフト
JP2001082165A (ja) * 1999-09-09 2001-03-27 Daihatsu Motor Co Ltd エンジンの振動低減装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5458501U (fr) * 1977-09-30 1979-04-23
JP2000297845A (ja) * 1999-04-14 2000-10-24 Isuzu Motors Ltd 内燃機関のバランサシャフト
JP2001082165A (ja) * 1999-09-09 2001-03-27 Daihatsu Motor Co Ltd エンジンの振動低減装置

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