WO2021187033A1 - Balancer device and balancer device provided with oil pump - Google Patents

Balancer device and balancer device provided with oil pump 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
Other languages
French (fr)
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
Publication date
Application filed by 日立Astemo株式会社 filed Critical 日立Astemo株式会社
Publication of WO2021187033A1 publication Critical patent/WO2021187033A1/en

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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

A balancer device comprising: a balancer housing (8); and a balancer shaft (9) that is rotatably supported by the balancer housing (8). The balancer shaft (9) is provided with, sequentially from to one end (9a) thereof in a rotation axis direction, a first balancer weight (10), a balancer gear (30), and a second balancer weight (31). A first balancer bearing (16f) that rotatably supports the balancer shaft (9) is provided between the first balancer weight (10) and the balancer gear (30).　Accordingly, the first balancer weight (10), the first balancer bearing (16f), and the balancer gear (30) are aligned sequentially from the one end (9a) of the balancer shaft (9) in the rotation axis direction.

Description

バランサ装置およびオイルポンプ付きバランサ装置Balancer device and balancer device with oil pump
　本発明は、バランサ装置およびオイルポンプ付きバランサ装置に関する。 The present invention relates to a balancer device and a balancer device with an oil pump.
　バランサ装置として、例えば以下の特許文献１に記載されたバランサ装置が知られている。 As a balancer device, for example, the balancer device described in Patent Document 1 below is known.
　特許文献１に記載のバランサ装置では、バランサシャフトの回転軸線方向の一端部から順に、バランサギア、バランサウエイト、軸受が設けられている。バランサギアは、クランクシャフトからの回転力が伝達される伝達ギアと噛み合っている。 In the balancer device described in Patent Document 1, 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.
中国特許出願第１０２７９７７８９号明細書Chinese Patent Application No. 1027977789
　特許文献１に記載のバランサ装置では、バランサシャフトが回転駆動されると、バランサウエイト側において、バランサシャフトが、バランサウエイトの回転に伴って、軸受を支点として径方向へ振れる。これにより、バランサシャフトの一端部に設けられたバランサギアが、バランサシャフトの径方向に振られて伝達ギアに強く当接することにより、歯打ち音が発生する虞がある。 In the balancer device described in Patent Document 1, when the balancer shaft is rotationally driven, the balancer shaft swings in the radial direction with the bearing as a fulcrum as the balancer weight rotates. As a result, the balancer gear provided at one end of the balancer shaft is shaken in the radial direction of the balancer shaft and strongly abuts on the transmission gear, which may cause a rattling noise.
　本発明は、従来の実情に鑑みて案出されたもので、バランサギアと伝達ギアとの間で発生する歯打ち音を抑制することができるバランサ装置およびオイルポンプ付きバランサ装置を提供することを一つの目的としている。 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.
　本発明では、その一態様として、第１バランサ軸受部が、第１バランサウエイトとバランサギアとの間、および、第１バランサウエイトと共にバランサギアを挟む位置、の一方に設けられている。 In the present invention, as one aspect thereof, 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.
　本発明によれば、バランサギアと伝達ギアとの間で発生する歯打ち音を抑制することができる。 According to the present invention, it is possible to suppress the rattling noise generated between the balancer gear and the transmission gear.
第１の実施形態のバランサ装置を搭載した内燃機関の部分断面図である。It is a partial cross-sectional view of the internal combustion engine equipped with the balancer device of 1st Embodiment. 第１の実施形態のバランサ装置の斜視図である。It is a perspective view of the balancer device of 1st Embodiment. 第１の実施形態のバランサ装置の分解斜視図である。It is an exploded perspective view of the balancer device of 1st Embodiment. 従来技術のバランサ装置の部分的な断面図である。It is a partial cross-sectional view of the balancer device of the prior art. 第２の実施形態のバランサ装置の分解斜視図である。It is an exploded perspective view of the balancer device of the 2nd Embodiment. 第３の実施形態のバランサ装置の分解斜視図である。It is an exploded perspective view of the balancer device of 3rd Embodiment. 第４の実施形態のバランサ装置の分解斜視図である。It is an exploded perspective view of the balancer device of 4th Embodiment. 第５の実施形態のバランサ装置の分解斜視図である。It is an exploded perspective view of the balancer device of 5th Embodiment. 第６の実施形態のバランサ装置の分解斜視図である。It is an exploded perspective view of the balancer device of the sixth embodiment. 第７の実施形態のバランサ装置の分解斜視図である。It is an exploded perspective view of the balancer device of 7th Embodiment.
　以下、本発明のバランサ装置の実施形態を図面に基づき説明する。 Hereinafter, embodiments of the balancer device of the present invention will be described with reference to the drawings.
　［第１の実施形態］
　図１は、第１の実施形態のバランサ装置を搭載した内燃機関１の部分断面図である。 [First Embodiment]
FIG. 1 is a partial cross-sectional view of an internal combustion engine 1 equipped with the balancer device of the first embodiment.
　内燃機関１、例えば直列３気筒の内燃機関のエンジンブロック２には、クランクシャフト３が回転可能に収容されている。クランクシャフト３は、その回転軸線の方向が内燃機関１の前後方向と一致するように配置されている。 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.
　クランクシャフト３の回転軸線の方向における一端部３ａには、クランクスプロケット４が、その中央に形成された取付孔４ａを介して取付固定されている。クランクスプロケット４の外周には、複数のギア歯部４ｂが形成されている。 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.
　また、エンジンブロック２の下部には、内部に潤滑油であるオイルを貯留するオイルパン５が、図示せぬ複数の固定部材、例えばボルトによって取り付けられている。オイルパン５内には、図１に示すように最も下方に位置した後述の第１バランサウエイト１０がオイルの油面６よりも上側になるように、オイルが貯留されている。また、オイルパン５内において、オイルポンプ７の吸入口７ａが、第１バランサウエイト１０よりも下方でオイルに漬かるように配置されている。 Further, at the lower part of the engine block 2, 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.
　エンジンブロック２の下部とオイルパン５とによって取り囲まれた空間には、内燃機関１のモーメント振動を抑制するバランサ装置が収容されている。バランサ装置は、オイルポンプ７が搭載されたオイルポンプ付きバランサ装置として構成されている。このバランサ装置は、バランサハウジング８と、該バランサハウジング８によって回転可能に支持され、クランクシャフト３からの回転力が伝達されるバランサシャフト９と、該バランサシャフト９の外周部に固定された後述のバランサギア３０、第１バランサウエイト１０および後述の第２バランサウエイト３１と、を備えている。バランサシャフト９は、その回転軸線の方向がクランクシャフト３の回転軸線の方向つまり内燃機関１の前後方向と一致するように配置されている。オイルポンプ７のオイルポンプシャフト１１の回転軸線の方向における一端部である前端部には、ポンプスプロケット１２が固定部材、例えばボルト１３によって取付固定されている。 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.
　ポンプスプロケット１２の外周には、複数のギア歯部１２ａが形成されている。ポンプスプロケット１２のギア歯部１２ａとクランクスプロケット４のギア歯部４ｂとの間には、駆動チェーン１４が巻き回されている。駆動チェーン１４には、エンジンブロック２の下部付近に設けられた油圧式のテンショナ１５によって所定の張力が付与されるようになっている。この駆動チェーン１４、クランクスプロケット４およびポンプスプロケット１２を介して、クランクシャフト３からの回転力が、オイルポンプシャフト１１に伝達される。 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.
　図２は、第１の実施形態のバランサ装置の斜視図、図３は、第１の実施形態のバランサ装置の分解斜視図である。 FIG. 2 is a perspective view of the balancer device of the first embodiment, and FIG. 3 is an exploded perspective view of the balancer device of the first embodiment.
　まず、以下の説明の便宜のため、バランサシャフト９の回転軸線の方向を「回転軸線方向」と定義し、バランサシャフト９の回転軸線に対する径方向を「径方向」と定義し、さらに、バランサシャフト９の回転軸線の周囲の方向を「周方向」と定義する。バランサシャフト９の回転軸線方向の両端部９ａ，９ｂのうち第１バランサウエイト１０が設けられる側の端部を「一端部９ａ」と定義し、第２バランサウエイト３１が設けられる側の端部を「他端部９ｂ」と定義する。 First, for the convenience of the following explanation, 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", and further, the balancer shaft. The direction around the rotation axis of 9 is defined as the "circumferential direction". Of the ends 9a and 9b of the balancer shaft 9 in the direction of the rotation axis, the end on the side where the first balancer weight 10 is provided is defined as "one end 9a", and 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".
　バランサハウジング８は、金属材料、例えばアルミニウムによるダイキャストによって概ね矩形状の厚板状に形成されている。バランサハウジング８は、該バランサハウジング８と別体に形成された軸受ハウジング１６と協働してバランサシャフト９を回転可能に支持する。バランサハウジング８は、バランサシャフト９の周方向の一部の領域を覆う長方形の基部１７と、基部１７の第１バランサウエイト１０側の長手方向端部から外方に矩形状に張り出した張出部１８と、を有している。 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.
　基部１７は、バランサシャフト９が設けられる側に平坦な面１７ａを有しており、該面１７ａにバランサシャフト９の周方向に沿って円弧面状に窪む、バランサシャフト９の周方向の一部の領域を覆う円弧凹部１７ｂを備えている。また、基部１７は、バランサシャフト９の一端部９ａ側において、段差部１７ｃを介して面１７ａよりも第１バランサウエイト１０側に位置し、かつ軸受ハウジング１６との合わせ面となる平坦な基部合わせ面１７ｄを有している。基部合わせ面１７ｄには、軸受ハウジング１６に矩形状に突出形成された凸部１６ｈが嵌め合わされる矩形凹状の凹部１７ｅがバランサシャフト９の回転軸線方向に沿って陥没形成されている。凹部１７ｅの底部には、バランサハウジング８の軽量化のために設けられた三角形状の２つの肉抜き部１７ｆが開口形成されている。基部合わせ面１７ｄには、軸受ハウジング１６の合わせ面１６ａに設けられた図示せぬ位置決め孔に圧入されるダウエルピン１９ａが設けられている。また、基部合わせ面１７ｄのうちダウエルピン１９ａよりも第１バランサウエイト１０側には、軸受ハウジング１６の取付部１６ｂに設けられた固定部材貫通孔１６ｄを介して固定部材、例えばボルト２０がねじ留めされるねじ穴１７ｈが形成されている。 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. On the base mating 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. At the bottom of the recess 17e, 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. Further, 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.
　張出部１８は、基部合わせ面１７ｄと面一に形成され、軸受ハウジング１６の合わせ面１６ａと合わされる平坦な張出部合わせ面１８ａを有している。また、張出部合わせ面１８ａには、軸受ハウジング１６の合わせ面１６ａに設けられた図示せぬ位置決め孔に圧入されるダウエルピン１９ｂが設けられている。また、張出部合わせ面１８ａのうちダウエルピン１９ｂよりも第１バランサウエイト１０側には、軸受ハウジング１６の取付部１６ｃに設けられた固定部材貫通孔１６ｅを介してボルト２１がねじ留めされるねじ穴１８ｃが形成されている。また、張出部１８は、矩形の板状をなす接続部２２を介して基部１７の側方に接続されている。接続部２２には、バランサハウジング８の軽量化のために設けられた概ね長方形の２つの肉盗み部２３が開口形成されている。 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.
　また、基部１７のうち第１バランサウエイト１０と反対側の長手方向端部には、軸受ハウジング１６がバランサハウジング８に取り付けられた状態で、軸受ハウジング１６と対向する端壁部２４が形成されている。この端壁部２４には、軸受ハウジング１６の後述の円形の第１バランサ軸受部１６ｆと共にバランサシャフト９を軸受する円形の第２バランサ軸受部２４ａが回転軸線方向に沿って貫通形成されている。第１および第２バランサ軸受部１６ｆ，２４ａの内径は、後述の第１および第２ニードルベアリング２８，２９の外径に対応した大きさに設定されている。 Further, at the longitudinal end of the base 17 opposite to the first balancer weight 10, an end wall portion 24 facing the bearing housing 16 is formed with the bearing housing 16 attached to the balancer housing 8. There is. A circular second balancer bearing portion 24a for bearing the balancer shaft 9 is formed through the end wall portion 24 together with the circular first balancer bearing portion 16f described later of the bearing housing 16 along the rotation axis direction. The inner diameters of the first and second balancer bearings 16f and 24a are set to a size corresponding to the outer diameters of the first and second needle bearings 28 and 29, which will be described later.
　また、バランサハウジング８の四隅、つまり端壁部２４の両側部、基部合わせ面１７ｄの側方および張出部合わせ面１８ａの側方には、エンジンブロック２の下部に取り付けられる取付部２５がバランサハウジング８と一体に形成されている。各取付部２５は、エンジンブロック２への取付の際に図示せぬボルトが貫通するボルト貫通孔２５ａが基部１７の厚み方向に貫通形成されている。 Further, at the four corners of the balancer housing 8, that is, on both sides of the end wall portion 24, on the side of the base mating surface 17d and on the side of the overhanging mating surface 18a, 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.
　バランサシャフト９の回転軸線方向における一端部９ａ付近および他端部９ｂ付近には、バランサシャフト９の軸受けに供する円柱状の第１ジャーナル部２６および第２ジャーナル部２７がそれぞれ形成されている。 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.
　第１ジャーナル部２６は、第２ジャーナル部２７を除くバランサシャフト９の他の部分よりも外径が大きい円柱状をなしており、バランサシャフト９の回転軸線方向において一端部９ａから他端部９ｂ側へ僅かにオフセットした位置に形成されている。換言すれば、バランサシャフト９の一端部９ａは、第１ジャーナル部２６から第２ジャーナル部２７とは反対側へバランサシャフト９の回転軸線方向に沿って僅かに突出している。第１ジャーナル部２６は、軸受ハウジング１６の第１バランサ軸受部１６ｆに設けられる円筒状の第１ニードルベアリング２８を介して回転可能に支持されている。 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.
　第２ジャーナル部２７は、第１ジャーナル部２６を除くバランサシャフト９の他の部分よりも外径が大きい円柱状をなしており、バランサシャフト９の回転軸線方向において他端部９ｂから一端部９ａ側へ僅かにオフセットした位置に形成されている。換言すれば、バランサシャフト９の他端部９ｂは、第２ジャーナル部２７から第１ジャーナル部２６とは反対側へバランサシャフト９の回転軸線方向に沿って僅かに突出している。第２ジャーナル部２７は、端壁部２４の第２バランサ軸受部２４ａに設けられる円筒状の第２ニードルベアリング２９を介して後述のバランサギア３０と第２バランサウエイト３１との間で回転可能に支持されている。 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.
　第１および第２ジャーナル部２６，２７によって回転可能に支持されるバランサシャフト９には、一端部９ａから他端部９ｂにかけて順に、第１バランサウエイト１０、バランサギア３０および第２バランサウエイト３１が設けられている。 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.
　第１バランサウエイト１０は、バランサシャフト９の一端部９ａの外周部に固定されており、バランサシャフト９の回転軸線を中心として径方向に偏位した状態で拡径する扇状に形成されている。第１バランサウエイト１０は、その厚さ方向に貫通するウエイト貫通孔１０ａを介してボルト３２によってバランサシャフト９の一端部９ａ側の軸方向端面９ｃのねじ穴９ｄにねじ留めされることでバランサシャフト９に取付固定されている。 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.
　バランサギア３０は、金属材料、例えば、鉄で形成されたヘリカルギアであり、第１ジャーナル部２６を挟んで第１バランサウエイト１０と反対側の回転軸線方向位置において、バランサシャフト９の外周部に連結されている。バランサギア３０は、軸受ハウジング１６に設けられた図示せぬギア収容部内に収容される。なお、バランサギア３０は、鋳鉄で形成されたものを使用しても良い。 The balancer gear 30 is a helical gear made of a metal material, for example, iron, and is located on the outer peripheral portion of the balancer shaft 9 at a position in the direction of the rotation axis opposite to the first balancer weight 10 with the first journal portion 26 interposed therebetween. It is connected. The balancer gear 30 is housed in a gear housing portion (not shown) provided in the bearing housing 16. The balancer gear 30 may be made of cast iron.
　第２バランサウエイト３１は、第１バランサウエイト１０と同様の形状を有しており、バランサシャフト９の他端部９ｂの外周部に固定されている。第２バランサウエイト３１は、バランサシャフト９の回転軸線を中心として第１バランサウエイト１０とは１８０度反対側へ径方向に偏位した状態で拡径する扇状に形成されている。第２バランサウエイト３１は、その厚さ方向に貫通するウエイト貫通孔３１ａを介してボルト３３によってバランサシャフト９の他端部９ｂ側の軸方向端面９ｅの図示せぬねじ穴にねじ留めされることでバランサシャフト９に取付固定されている。 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.
　軸受ハウジング１６は、アルミニウム製のバランサハウジング８よりも単位体積重量（単位体積当たりの重量）が大きい金属材料、例えば、鉄によって形成されている。なお、軸受ハウジング１６は、鋳鉄で形成されたものを使用しても良い。軸受ハウジング１６は、オイルポンプ７のオイルポンプシャフト１１の支持に供し、オイルポンプシャフト１１の回転軸線に対する周方向において、バランサシャフト９の回転軸線と平行なオイルポンプシャフト１１の回転軸線に対する全周を覆うシャフト支持部１６ｇと、基部合わせ面１７ｄおよび張出部合わせ面１８ａに接合される軸受ハウジング１６の合わせ面１６ａからバランサハウジング８側へ矩形状に突出し、バランサハウジング８の凹部１７ｅに嵌め合わされる凸部１６ｈと、シャフト支持部１６ｇの両側部から外側に突出し、基部合わせ面１７ｄおよび張出部合わせ面１８ａとの取付に供する一対の取付部１６ｂ，１６ｃとを有している。なお、シャフト支持部１６ｇは、軸受ハウジング１６によって、周方向において、全周を覆われている必要は無く、レイアウトに応じて、軸受ハウジング１６と、軸受ハウジング１６とは別体に形成された部材であるキャップ部材等と、により、シャフト支持部１６ｇの一部または全体を覆っても良い。 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. It has a convex portion 16h and a pair of mounting portions 16b and 16c that project outward from both side portions of the shaft support portion 16g and are used for mounting with the base mating surface 17d and the overhanging mating surface 18a. 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.
　シャフト支持部１６ｇと凸部１６ｈとに跨る部位には、第１バランサウエイト１０とバランサギア３０との間でバランサシャフト９の第１ジャーナル部２６を回転可能に支持する第１バランサ軸受部１６ｆがバランサシャフト９の回転軸線方向に貫通形成されている。つまり、第１バランサ軸受部１６ｆは、バランサシャフト９の回転軸線に対する周方向において、バランサシャフト９の第１ジャーナル部２６の全周を覆っている。なお、第１バランサ軸受部１６ｆは、軸受ハウジング１６によって、周方向において、全周を覆われている必要は無く、レイアウトに応じて、軸受ハウジング１６と、軸受ハウジング１６とは別体に形成された部材であるキャップ部材等と、により、第１バランサ軸受部１６ｆの一部または全体を覆っても良い。 At a portion straddling the shaft support portion 16g and the convex portion 16h, a first balancer bearing portion 16f that rotatably supports the first journal portion 26 of the balancer shaft 9 between the first balancer weight 10 and the balancer gear 30 is provided. It is formed through the balancer shaft 9 in the direction of the rotation axis. That is, the first balancer bearing portion 16f covers the entire circumference of the first journal portion 26 of the balancer shaft 9 in the circumferential direction with respect to the rotation axis of the balancer shaft 9. The first balancer bearing portion 16f does not need to be covered by the bearing housing 16 on the entire circumference 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 first balancer bearing portion 16f may be covered with a cap member or the like which is a member.
　また、シャフト支持部１６ｇには、オイルポンプシャフト１１を回転可能に支持するシャフト軸受部１６ｉが、バランサシャフト９と平行なオイルポンプシャフト１１の回転軸線方向に貫通形成されている。第１バランサ軸受部１６ｆは、シャフト軸受部１６ｉよりも凸部１６ｈの先端部寄りの位置に設けられており、バランサシャフト９の径方向においてシャフト軸受部１６ｉとオーバーラップしている。 Further, in the shaft support portion 16g, 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.
　また、軸受ハウジング１６は、その外側面から径方向外側に拡張された拡張部１６ｊを有している。この拡張部１６ｊの内部であってオイルポンプ７と対向する部位には、オイルポンプ７の一端が開口したポンプボディ３４との間でバランサギア３０および後述の中間ギア３５を収容する図示せぬギア収容部が設けられている。 Further, 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.
　オイルポンプ７は、オイルポンプシャフト１１の第１端部１１ａと軸方向反対位置にある図示せぬ第２端部に設けられていて、ポンプボディ３４と、該ポンプボディ３４の内部のポンプ要素収容部内に収容された図示せぬポンプ要素と、該ポンプ要素を駆動するオイルポンプシャフト１１と、を備えている。 The oil pump 7 is provided at a second end (not shown) opposite to the first end 11a of the oil pump shaft 11 in the axial direction, and accommodates the pump body 34 and the pump elements inside the pump body 34. A pump element (not shown) housed in the portion and an oil pump shaft 11 for driving the pump element are provided.
　ポンプボディ３４は、その外周部に、軸受ハウジング１６への取付の際にボルト３６が貫通する４つのボルト貫通穴３４ａを有している。ポンプボディ３４は、各ボルト貫通穴３４ａを介して、軸受ハウジング１６に設けられたねじ穴部１６ｎに、各ボルト３６をねじ留めすることで、軸受ハウジング１６に取り付けられている。また、軸受ハウジング１６に対するポンプボディ３４の位置決めは、ポンプボディ３４の開口端面に設けられた位置決めピン３４ｂ，３４ｃを、拡張部１６ｊに設けられた位置決め穴５５，５６に嵌め合わせることにより行われる。 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.
　オイルポンプシャフト１１は、バランサシャフト９と並行して延びるように配置されている。つまり、オイルポンプシャフト１１は、その回転軸線方向がバランサシャフト９の回転軸線方向と平行となるようにバランサシャフト９の径方向に隣接して並列に配置されている。オイルポンプシャフト１１の全長は、バランサシャフト９の全長よりも短くなっていて、一端部９ａ寄りに一端部９ａと隣接して並列に配置されている。 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.
　オイルポンプシャフト１１の第１端部１１ａには、円柱状の大径部１１ｂが形成されている。大径部１１ｂは、後述する第３ジャーナル部３８を除くオイルポンプシャフト１１の他の部分よりも外径が大きい円柱状をなしている。この大径部１１ｂの第１端部１１ａ側の軸方向端面１１ｃには、ポンプスプロケット１２の対向端面に付き当てた状態でポンプスプロケット１２がボルト３７を介して取り付けられる。これにより、ポンプスプロケット１２のオイルポンプ７側への移動が規制される。 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.
　また、オイルポンプシャフト１１のうちバランサシャフト９の第１ジャーナル部２６と径方向に隣接する部位には、円柱状の第３ジャーナル部３８が形成されている。第３ジャーナル部３８は、大径部１１ｂを除くオイルポンプシャフト１１の他の部分よりも外径が大きい円柱状をなしている。第３ジャーナル部３８は、円筒状の第３ニードルベアリング３９を介して軸受ハウジング１６のシャフト軸受部１６ｉに回転可能に支持されている。 Further, 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.
　回転軸線方向において第３ジャーナル部３８と隣接した中間ギア３５は、軸受ハウジング１６と同様の金属材料、本実施形態では鉄で形成されたヘリカルギアである。なお、中間ギア３５は、鋳鉄で形成されたものを使用しても良い。中間ギア３５は、第３ジャーナル部３８とポンプボディ３４との間の回転軸線方向位置に、径方向から見てバランサギア３０と軸方向にオーバーラップするように、オイルポンプシャフト１１の外周部に連結されている。この時、バランサシャフト９はクランクシャフト３と反対方向へ同回転速度で回転するよう、クランクスプロケット４、ポンプスプロケット１２、中間ギア３５、バランサギア３０の歯数比が設定されている。そのため、中間ギア３５の歯数と、バランサギア３０の歯数を同じにすることもあり、中間ギア３５の歯数よりも、バランサギア３０の歯数の方が少ないこともあり、またはバランサギア３０の歯数の方が多いこともある。 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. At this time, 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. Therefore, 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.
　次に、オイルポンプ７付きのバランサ装置の組立方法について以下に説明する。 Next, the method of assembling the balancer device with the oil pump 7 will be described below.
　まず、バランサシャフト９の外周部にバランサギア３０を連結するとともに、バランサシャフト９の第１ジャーナル部２６に第１ニードルベアリング２８を取り付けておく。さらに、オイルポンプシャフト１１の外周部に中間ギア３５を連結するとともに、オイルポンプシャフト１１の第３ジャーナル部３８に第３ニードルベアリング３９を取り付けておく。 First, 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.
　次に、バランサハウジング８の凹部１７ｅ側から、バランサギア３０が連結されたバランサシャフト９の他端部９ｂを、バランサハウジング８に設けられ、周方向において、バランサシャフト９の第２ジャーナル部２７の全周を覆う第２バランサ軸受部２４ａに挿入する。なお、第２バランサ軸受部２４ａは、バランサハウジング８によって、周方向において、全周を覆われている必要は無く、レイアウトに応じて、バランサハウジング８とは別体に形成された部材であるキャップ部材などにより、第２バランサ軸受部２４ａの一部を覆っても良い。 Next, from the recess 17e side of the balancer housing 8, 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.
　このとき、バランサシャフト９の一端部９ａが凹部１７ｅよりも第２バランサ軸受部２４ａ側に位置するようにバランサハウジング８を挿入し、バランサシャフト９の第２ジャーナル部２７に第２ニードルベアリング２９を取り付ける。 At this time, 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.
　そして、バランサギア３０および中間ギア３５の軸受ハウジング１６側の側面に設けられた図示せぬ合いマークを見ながら、バランサシャフト９上のバランサギア３０に対してオイルポンプシャフト１１上の中間ギア３５の位相合わせを行う。 Then, while looking at the unshown alignment marks provided on the side surfaces of the balancer gear 30 and the intermediate gear 35 on the bearing housing 16 side, the intermediate gear 35 on the oil pump shaft 11 with respect to the balancer gear 30 on the balancer shaft 9 Perform phase matching.
　次に、バランサハウジング８の凹部１７ｅにシャフト軸受部１６ｉの凸部１６ｈを嵌め合わせるようにして、バランサハウジング８に軸受ハウジング１６を取り付ける。この取付の際には、バランサハウジング８の基部合わせ面１７ｄおよび張出部合わせ面１８ａ上に設けられた２つのダウエルピン１９ａ，１９ｂが、軸受ハウジング１６の合わせ面１６ａの対応する位置決め孔に圧入される。そして、軸受ハウジング１６の２つの固定部材貫通孔１６ｄ，１６ｅを介して基部１７のねじ穴１７ｈおよび張出部１８のねじ穴１８ｃに２つのボルト２０，２１をねじ留めする。 Next, 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. At the time of this mounting, 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. NS. Then, 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.
　軸受ハウジング１６の取付後には、バランサギア３０と中間ギア３５とを噛み合わせた状態で、バランサシャフト９およびオイルポンプシャフト１１を軸方向にスライドさせて、バランサシャフト９の外周部の第１ニードルベアリング２８およびオイルポンプシャフト１１の外周部の第３ニードルベアリング３９を、第１バランサ軸受部１６ｆおよびシャフト軸受部１６ｉに圧入する。この圧入と同時に、バランサシャフト９の外周部の第２ニードルベアリング２９が第２バランサ軸受部２４ａに圧入される。 After mounting 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. At the same time as this press-fitting, 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.
　次に、軸受ハウジング１６にオイルポンプ７のポンプボディ３４を取り付ける。この取付は、ポンプボディ３４の各ボルト貫通孔３４ａを介して軸受ハウジング１６の各ねじ穴部１６ｎに各ボルト３６をねじ留めすることで行われる。 Next, 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.
　ポンプボディ３４の取付後には、バランサシャフト９の一端部９ａへの第１バランサウエイト１０の取り付け、バランサシャフト９の他端部９ｂへの第２バランサウエイト３１の取り付け、オイルポンプシャフト１１の第１端部１１ａへのポンプスプロケット１２の取り付けを、ボルト３２，３３，３７の締結により行う。 After the pump body 34 is attached, 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, and 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.
　かかるバランサ装置では、内燃機関１が始動されてクランクシャフト３が回転すると、クランクスプロケット４、駆動チェーン１４およびポンプスプロケット１２を介して、オイルポンプシャフト１１がクランクシャフト３と同一方向に回転する。これに伴い、バランサシャフト９は、中間ギア３５とバランサギア３０との噛み合い伝達を経てオイルポンプシャフト１１と反対方向へ同速度で回転する。ただし、バランサシャフト９は、中間ギア３５とバランサギア３０との噛み合い伝達を経てオイルポンプシャフト１１と反対方向へ同速度で回転させなくてもよい。また、このとき、バランサシャフト９はクランクシャフト３と反対方向へ同回転速度で回転させなくてもよい。そして、バランサシャフト９の回転により、第１および第２バランサウエイト１０，３１がバランサシャフト９と一体となって回転することで、直列３気筒の内燃機関１のピストンの往復運動に起因した内燃機関のモーメント振動が低減される。 In such a balancer device, when the internal combustion engine 1 is started and the crankshaft 3 rotates, the oil pump shaft 11 rotates in the same direction as the crankshaft 3 via the crank sprocket 4, the drive chain 14, and the pump sprocket 12. Along with this, the balancer shaft 9 rotates at the same speed in the direction opposite to that of the oil pump shaft 11 via meshing transmission between the intermediate gear 35 and the balancer gear 30. However, the balancer shaft 9 does not have to be rotated at the same speed in the direction opposite to the oil pump shaft 11 through the meshing transmission between the intermediate gear 35 and the balancer gear 30. Further, at this time, the balancer shaft 9 does not have to be rotated in the direction opposite to that of the crankshaft 3 at the same rotation speed. Then, the rotation of the balancer shaft 9 causes the first and second balancer weights 10 and 31 to rotate integrally with the balancer shaft 9, so that the internal combustion engine is caused by the reciprocating motion of the piston of the in-line 3-cylinder internal combustion engine 1. Moment vibration is reduced.
　［第１の実施形態の効果］
　図４は、従来技術のバランサ装置の部分的な断面図である。 [Effect of the first embodiment]
FIG. 4 is a partial cross-sectional view of a prior art balancer device.
　従来技術のバランサ装置では、バランサシャフト９の回転軸線方向の一端部９ａから順に、バランサギア３０、第１バランサウエイト１０、第１ニードルベアリング２８が設けられている。より詳細には、図４に示すように、バランサシャフト９の一端部９ａは、バランサハウジング８の外側に突出して自由端となっており、この自由端にバランサギア３０および第１バランサウエイト１０が設けられ、さらに、第１ニードルベアリング２８がバランサハウジング８の軸受孔８ｓの内周面に固定されている。 In the balancer device of the prior art, 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.
　かかるバランサ装置において、バランサシャフト９が回転駆動すると、自由端である一端部９ａに設けられた第１バランサウエイト１０が回転する。例えば図４に示すように、回転方向においてバランサシャフト９よりも下側に第１バランサウエイト１０の重量部が位置するとき、バランサシャフト９は、第１バランサウエイト１０により、図４に矢印Ａで示すように、バランサシャフト９の下方側に振られる（撓む）。これにより、第１バランサウエイト１０の外側に隣接したバランサギア３０も、図４に矢印Ｂで示すように、下方に振られて、伝達ギア４０に強く当接し、伝達ギア４０との間で歯打ち音が発生するという問題があった。 In such a balancer device, when the balancer shaft 9 is rotationally driven, the first balancer weight 10 provided at one end 9a, which is a free end, rotates. For example, as shown in FIG. 4, when the weight portion of the first balancer weight 10 is located below the balancer shaft 9 in the rotation direction, 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. As a result, 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.
　これに対し、第１の実施形態では、バランサシャフト９の回転軸線方向端部から順に、第１バランサウエイト１０、バランサギア３０が設けられており、さらに、第１バランサウエイト１０とバランサギア３０との間に、バランサシャフト９を回転可能に支持する第１バランサ軸受部１６ｆが設けられている。つまり、バランサシャフト９の回転軸線方向の一端部９ａから順に、第１バランサウエイト１０、第１バランサ軸受部１６ｆ、バランサギア３０が整列している。換言すれば、第１バランサウエイト１０が、自由端である一端部９ａの外周部に固定され、第１バランサ軸受部１６ｆが、第１ニードルベアリング２８を介してバランサシャフト９を支持しており、さらに、バランサギア３０が、第１バランサ軸受部１６ｆを挟んで第１バランサウエイト１０とは反対側においてバランサシャフト９に固定されている。このため、バランサシャフト９の回転駆動時に第１バランサウエイト１０の回転によりバランサシャフト９が径方向に振られたときに、この振れが、第１バランサ軸受部１６ｆを支持する軸受ハウジング１６によって抑制されるので、第１バランサ軸受部１６ｆよりも回転軸線方向内側のバランサギア３０に伝達され難くなっている。従って、バランサシャフト９の回転駆動時にバランサギア３０が径方向に振られて中間ギア３５に強く当接し、バランサギア３０と中間ギア３５との間から歯打ち音が生じることを抑制することができる。 On the other hand, in the first embodiment, 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. In other words, 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. Further, 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. Therefore, when the balancer shaft 9 is rotationally driven, 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. ..
　また、本実施形態では、シャフト軸受部１６ｉおよび第１バランサ軸受部１６ｆは、バランサハウジング８とは別体に形成された軸受ハウジング１６に設けられている。すなわち、上記の順序で第１バランサウエイト１０、第１バランサ軸受部１６ｆ、バランサギア３０を配置する場合、軸受ハウジング１６がバランサハウジング８と一体に形成されていると、バランサギア３０および中間ギア３５に設けられた合いマークが軸受ハウジング１６によって見えづらくなるため、バランサギア３０と中間ギア３５との位相合わせが困難になり、バランサ装置の組立効率が低下してしまう。これに対し、本実施形態では、シャフト軸受部１６ｉおよび第１バランサ軸受部１６ｆがバランサハウジング８と別体の軸受ハウジング１６に設けられることで、バランサ装置の組立時に、軸受ハウジング１６が組み付けられていない状態で、第１バランサウエイト１０側からバランサギア３０および中間ギア３５に設けられた合いマークを見ながら、バランサギア３０と中間ギア３５の位相合わせを容易に行うことが可能となり、バランサ装置の組立効率を向上させることができる。 Further, in the present embodiment, 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. On the other hand, in the present embodiment, 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. In this state, 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.
　さらに、本実施形態では、オイルポンプシャフト１１は、その回転軸線方向における第１端部１１ａおよび第２端部を有し、第１端部１１ａには、内燃機関からの回転力が伝達されるポンプスプロケット１２が設けられ、第２端部には、オイルポンプ７が設けられている。このため、単一のオイルポンプシャフト１１が、オイルポンプ７の駆動およびバランサギア３０の反転の双方に寄与する。より詳細には、オイルポンプシャフト１１は、ポンプスプロケット１２からの回転によりオイルポンプ７を駆動するとともに、オイルポンプシャフト１１の外周部の中間ギア３５により、バランサギア３０の外周部のバランサギア３０を反転させる。よって、新たなシャフトを設けてバランサシャフト９を反転させる場合よりも、簡素な構造で効率良くオイルポンプ７の駆動およびバランサギア３０の反転の双方を行うことができる。 Further, in the present embodiment, 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.
　また、本実施形態では、オイルポンプ７は、軸受ハウジング１６に取り付けられている。このため、オイルポンプ７がバランサハウジング８に取り付けられている場合と比べて、オイルポンプシャフト１１の径方向の位置合わせが容易となる。より詳細には、仮にオイルポンプ７がバランサハウジング８に取り付けられている場合には、両者の間の取付誤差により、軸受ハウジング１６のシャフト軸受部１６ｉに対してオイルポンプ７の軸受部の径方向の位置ずれが生じ、オイルポンプシャフト１１の径方向の位置合わせが困難になる虞がある。しかし、本実施形態のように、オイルポンプ７が軸受ハウジング１６に直接取り付けられることで上記の取付誤差が排除され、オイルポンプシャフト１１の径方向の位置合わせが容易となる。 Further, in the present embodiment, 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.
　さらに、本実施形態では、軸受ハウジング１６は、バランサシャフト９の回転軸線方向においてオイルポンプ７と対向するように設けられ、バランサギア３０および中間ギア３５を収容するギア収容部を備える。このため、例えば外部入力等の要因により、オイルパン５内のオイルが飛散し、ギア収容部内に侵入しようとしても、バランサギア３０および中間ギア３５はギア収容部により覆われているため、ギア収容部によってオイルの侵入が抑制される。これにより、オイルがバランサギア３０および中間ギア３５に到達して回転抵抗が生じることを抑制することができる。 Further, in the present embodiment, 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.
　また、本実施形態では、バランサハウジング８は、バランサシャフト９が設けられる側の面１７ａに凹部１７ｂを有し、軸受ハウジング１６は、凹部１７ｅに嵌め合わされる凸部１６ｈを有する。このため、凹部１７ｅと凸部１６ｈとによる凹凸嵌合により、バランサハウジング８に対する軸受ハウジング１６の位置決めを容易に行うことができる。 Further, in the present embodiment, 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.
　さらに、本実施形態では、バランサハウジング８の基部合わせ面１７ｄおよび張出部合わせ面１８ａには、凹部１７ｅを挟んで両側に、軸受ハウジング１６との位置決めに供する一対の位置決め孔が設けられており、また、軸受ハウジング１６にも、同様に、バランサハウジング８との位置決めに供する一対の位置決め孔が設けられている。そして、一対のダウエルピン１９ａ，１９ｂがバランサハウジング８の一対の位置決め孔および軸受ハウジング１６の一対の位置決め孔に嵌め合わされる。このため、各位置決め孔とダウエルピン１９ａ，１９ｂとの凹凸嵌合により、バランサハウジング８に対する軸受ハウジング１６の位置決めを容易に行うことができる。 Further, in the present embodiment, 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. Similarly, 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.
　なお、一対のダウエルピン１９ａ，１９ｂが、軸受ハウジング１６に設けられた一対の位置決め孔の少なくとも一方に設けられた状態で、バランサハウジング８の基部合わせ面１７ｄの凹部１７ｅを挟んで両側に設けられた一対の位置決め孔の少なくとも一方に嵌め合わされてもよい。 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.
　また、本実施形態では、第１バランサウエイト１０は、オイルパン５内のオイルの油面６よりも鉛直上側に位置するようにオイルパン５内に配置されている。このため、バランサシャフト９の回転駆動時に第１バランサウエイト１０がオイルの油面６をたたき難いので、バランサシャフト９の回転抵抗の発生やオイルのエアレーションの発生を抑制することができる。従って、バランサ装置を効率良く稼動するとともに、空気を含まないオイルによって内燃機関の各摺動部等を滑らかに潤滑することができる。 Further, in the present embodiment, 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.
　さらに、本実施形態では、中間ギア３５および軸受ハウジング１６が同じ金属材料である鉄により形成されている。なお、中間ギア３５および軸受ハウジング１６を、鋳鉄で形成されたものを使用しても良い。このため、何らかの要因、例えば運転開始後の内燃機関の温度上昇等により中間ギア３５および軸受ハウジング１６に熱膨張または熱収縮が生じた場合に、中間ギア３５および軸受ハウジング１６の双方が同じ割合で膨張または収縮するので、中間ギア３５および軸受ハウジング１６が異なる金属材料で形成されている場合に比べて、オイルポンプシャフト１１の回転軸線方向（スラスト方向）における中間ギア３５と軸受ハウジング１６との間のクリアランスを容易に管理することができる。 Further, in the present embodiment, 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.
　また、本実施形態では、バランサギア３０と中間ギア３５および軸受ハウジング１６が同じ線膨張係数である金属材料の１つの鉄により形成されている一方、バランサハウジング８が鉄よりも線膨張係数の大きいアルミニウムで形成されている。 Further, in the present embodiment, 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.
　このため、何らかの要因、例えば運転開始後の内燃機関の温度上昇等により軸受ハウジング１６に熱膨張または熱収縮が生じ、中間ギア３５とバランサギア３０の回転軸間距離が変化したとしても、中間ギア３５とバランサギア３０も軸受ハウジング１６と同じ割合で膨張または収縮するので、中間ギア３５の歯部とバランサギア３０の歯部との間におけるバックラッシを容易に管理することができる。 Therefore, even if 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.
　なお、軸受ハウジング１６の材料は、バランサハウジング８の材料の線膨張係数よりも、バランサギア３０と中間ギア３５の材料の線膨張係数よりも近いものを使用しても、上述のような効果が得られる。 Even if the material of the bearing housing 16 is closer to the coefficient of linear expansion of the material of the balancer housing 8 than the coefficient of linear expansion of the material of the balancer gear 30 and the intermediate gear 35, the above-mentioned effect can be obtained. can get.
　［第２の実施形態］
　図５は、第２の実施形態のバランサ装置の分解斜視図である。 [Second Embodiment]
FIG. 5 is an exploded perspective view of the balancer device of the second embodiment.
　第２の実施形態では、第１の実施形態のバランサハウジング８に軸受ハウジング１６が一体化されてアルミニウム製のバランサハウジング８が形成されており、さらに、第２バランサ軸受部２４ａが半割状に形成されている。このため、第１バランサ軸受部１６ｆおよびシャフト軸受部１６ｉがバランサハウジング８に形成されており、第２バランサ軸受部２４ａが、バランサハウジング８の端壁部２４と一体に形成された半割状の第１軸受半部２４ｂと、バランサハウジング８と別体の第１キャップ部材４１に形成された第２軸受半部４１ｆとによって構成されている。 In 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.
　端壁部２４の上部には、基部１７の面１７ａから段差部１７ｉを介して第１キャップ部材４１側にオフセットした平坦面１７ｊが形成されている。この平坦面１７ｊの中央部よりも僅かにオイルポンプシャフト１１寄りの位置には、平坦面１７ｊに対して円弧面状に窪む第１軸受半部２４ｂがバランサシャフト９の回転軸線方向に沿って形成されている。また、平坦面１７ｊのうち第１軸受半部２４ｂを挟んで両側には、第２バランサウエイト３１寄りの位置に、第１キャップ部材４１に設けられた図示せぬ２つの位置決め孔に圧入される一対のダウエルピン４２ａ，４２ｂが設けられている。さらに、平坦面１７ｊのうち第１軸受半部２４ｂを挟んで両側には、一対のダウエルピン４２ａ，４２ｂよりも第１バランサウエイト１０寄りの位置に、第１キャップ部材４１に設けられた一対のボルト貫通孔４１ｄ，４１ｅを介してボルト４３，４４がねじ留めされる一対のねじ穴１７ｋ，１７ｍが形成されている。 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. At a position slightly closer to the oil pump shaft 11 than the central portion of the flat surface 17j, 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. Further, 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. Further, 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.
　第１キャップ部材４１は、金属材料、例えばアルミニウムによって形成されている。第１キャップ部材４１は、第２ニードルベアリング２９の外周に沿って湾曲した板状をなす円弧部４１ａと、該円弧部４１ａの両端と一体に形成され、平坦面１７ｊと平行に延びる矩形の板状の一対の側部４１ｂ，４１ｃと、を有している。 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.
　円弧部４１ａの内側面には、端壁部２４の第１軸受半部２４ｂとの間で円形の第２バランサ軸受部２４ａを構成する第２軸受半部４１ｆが設けられている。第２軸受半部４１ｆは、バランサシャフト９の回転軸線方向に沿って設けられている。 On the inner surface of the arc portion 41a, 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.
　一対の側部４１ｂ，４１ｃは、平坦面１７ｊに設けられたねじ穴１７ｋ，１７ｍに対応する位置に、ボルト４３，４４が貫通するボルト貫通孔４１ｄ，４１ｅを有している。
［第２の実施形態の効果］
　第２の実施形態では、シャフト軸受部１６ｉおよび第１バランサ軸受部１６ｆは、バランサハウジング８に形成され、第２バランサ軸受部２４ａは、バランサハウジング８と、バランサハウジング８とは別体に形成された第１キャップ部材４１とによって構成される。このため、第２バランサ軸受部２４ａに第２ニードルベアリング２９を圧入せずに、第１軸受半部２４ｂ上に設置された第２ニードルベアリング２９に第１キャップ部材４１を被せるだけで良いから、第１の実施形態のバランサ装置よりも容易にバランサシャフト９の組付を行うことができる。 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.
[Effect of the second embodiment]
In the second embodiment, 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.
　［第３の実施形態］
　図６は、第３の実施形態のバランサ装置の分解斜視図である。 [Third Embodiment]
FIG. 6 is an exploded perspective view of the balancer device of the third embodiment.
　第３の実施形態では、第１の実施形態のバランサハウジング８に軸受ハウジング１６のシャフト軸受部１６ｉを含む部分が一体化されてアルミニウム製のバランサハウジング８が形成されていて、第１バランサ軸受部１６ｆが半割状に形成されている。具体的には、シャフト軸受部１６ｉおよび第２バランサ軸受部２４ａがバランサハウジング８に形成されており、第１バランサ軸受部１６ｆが、バランサハウジング８の基部１７と一体に形成された半割状の第３軸受半部１７ｎと、バランサハウジング８と別体の第２キャップ部材４５に形成された第４軸受半部４５ｂとによって構成されている。 In 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. Specifically, 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.
　バランサハウジング８の基部１７の基部合わせ面１７ｄには、該基部合わせ面１７ｄに対して円弧面状に窪む第３軸受半部１７ｎがバランサシャフト９の回転軸線方向に沿って形成されている。また、基部合わせ面１７ｄのうち第３軸受半部１７ｎを挟んで両側には、一対のねじ穴１７ｈ，１７ｏが形成されており、このねじ穴１７ｈ，１７ｏには、第２キャップ部材４５に設けられた一対のボルト貫通孔４５ｃ，４５ｄを介して一対のボルト４６，４７がねじ留めされることで、第２キャップ部材４５がバランサハウジング８に取付固定される。 On the base mating surface 17d of the base 17 of 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.
　第２キャップ部材４５は、アルミニウム製のバランサハウジング８よりも単位体積重量が大きい金属材料、例えば鉄によって形成されている。なお、第２キャップ部材４５は、鋳鉄で形成されたものを使用しても良い。第２キャップ部材４５は、第１の実施形態の軸受ハウジング１６の凸部１６ｈと、軸受ハウジング１６のシャフト軸受部１６ｉを含む部位とを取り除いた残りの部位として形成されている。第２キャップ部材４５の合わせ面４５ａには、第３軸受半部１７ｎとの間で円形の第１バランサ軸受部１６ｆを構成する円弧面状の第４軸受半部４５ｂが形成されている。第２キャップ部材４５のうち基部合わせ面１７ｄ上の一対のねじ穴１７ｈ，１７ｏに対向する位置には、一対のボルト４６，４７が貫通する一対のボルト貫通孔４５ｃ，４５ｄが貫通形成されている。 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. On the mating surface 45a of the second cap member 45, 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. ..
　［第３の実施形態の効果］
　第３の実施形態では、シャフト軸受部１６ｉおよび第２バランサ軸受部２４ａは、バランサハウジング８に形成され、第１バランサ軸受部１６ｆは、バランサハウジング８と、バランサハウジング８よりも単位体積重量が大きい第１キャップ部材４１とによって構成されている。つまり、シャフト軸受部１６ｉおよび第２バランサ軸受部２４ａは、アルミニウム製のバランサハウジング８に形成され、第１バランサ軸受部１６ｆは、バランサハウジング８と、鉄で形成された第１キャップ部材４１とによって構成されている。このため、シャフト軸受部１６ｉを構成する部位も、鉄よりも軽量なアルミニウムによって形成されるので、第１の実施形態のバランサ装置よりも、バランサ装置を軽量化することができる。 [Effect of the third embodiment]
In the third embodiment, 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.
　［第４の実施形態］
　図７は、第４の実施形態のバランサ装置の分解斜視図である。 [Fourth Embodiment]
FIG. 7 is an exploded perspective view of the balancer device of the fourth embodiment.
　第４の実施形態では、第１の実施形態のバランサハウジング８に軸受ハウジング１６が一体化されてアルミニウム製のバランサハウジング８が形成されている。このため、第１および第２バランサ軸受部１６ｆ，２４ａおよびシャフト軸受部１６ｉがバランサハウジング８に形成されている。 In 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.
　［第４の実施形態の効果］
　第４の実施形態では、シャフト軸受部１６ｉ、第１バランサ軸受部１６ｆおよび第２バランサ軸受部２４ａが全て、バランサハウジング８に一体に形成されている。このようにシャフト軸受部１６ｉ等を形成することで、第１の実施形態の軸受ハウジング１６、第２の実施形態の第１キャップ部材４１や、第３の実施形態の第２キャップ部材４５が不要になるので、バランサ装置の部品点数を減少させるとともに、バランサ装置の製造コストを削減することができる。 [Effect of Fourth Embodiment]
In the fourth embodiment, 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. By forming the shaft bearing portion 16i and the like in this way, 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.
　［第５の実施形態］
　図８は、第５の実施形態のバランサ装置の分解斜視図である。 [Fifth Embodiment]
FIG. 8 is an exploded perspective view of the balancer device according to the fifth embodiment.
　第５の実施形態では、第３の実施形態のバランサハウジング８の第２バランサ軸受部２４ａが半割状に形成されていて、シャフト軸受部１６ｉがバランサハウジング８と一体に形成されている。さらに、第１バランサ軸受部１６ｆが、バランサハウジング８の基部１７と一体に形成された半割状の第３軸受半部１７ｎと、バランサハウジング８と別体の第２キャップ部材４５に形成された第４軸受半部４５ｂとによって構成され、第２バランサ軸受部２４ａが、バランサハウジング８の端壁部２４と一体に形成された半割状の第１軸受半部２４ｂと、バランサハウジング８と別体の第１キャップ部材４１に形成された第２軸受半部４１ｆとによって構成されている。 In 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.
　［第５の実施形態の効果］
　第５の実施形態では、シャフト軸受部１６ｉは、バランサハウジング８に形成され、第１バランサ軸受部１６ｆは、バランサハウジング８と、該バランサハウジング８とは別体に形成された第２キャップ部材４５とによって構成され、第２バランサ軸受部２４ａは、バランサハウジング８と、該バランサハウジング８とは別体に形成された第１キャップ部材４１とによって構成されている。 [Effect of Fifth Embodiment]
In the fifth embodiment, 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.
　このため、第１および第２バランサ軸受部１６ｆ，２４ａが共に半割状に形成される。これにより、第１および第２バランサ軸受部１６ｆ，２４ａに第１および第２ニードルベアリング２８，２９を圧入せずに、第３および第１軸受半部１７ｎ，２４ｂ上に設置された第１および第２ニードルベアリング２８，２９に第２および第１キャップ部材４５，４１を被せれば良いので、バランサシャフト９の組付を容易に行うことができる。 Therefore, both the first and second balancer bearing portions 16f and 24a are formed in a half-split shape. As a result, 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.
　［第６の実施形態］
　図９は、第６の実施形態のバランサ装置の分解斜視図である。 [Sixth Embodiment]
FIG. 9 is an exploded perspective view of the balancer device of the sixth embodiment.
　第６の実施形態では、図７におけるシャフト軸受部１６ｉおよび第１バランサ軸受部１６ｆが半割状に形成されている。このため、第２バランサ軸受部２４ａと、第３軸受半部１７ｎと、シャフト軸受部１６ｉの下側の半部である第５軸受半部１８ｄとが、バランサハウジング８に形成され、第４軸受半部４５ｂと、シャフト軸受部１６ｉの上側の半部である第６軸受半部４８ｂとが、第３キャップ部材４８に形成されている。 In 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.
　バランサハウジング８の張出部１８は、段差部１８ｅを介して基部１７の基部合わせ面１７ｄよりも上下方向オイルポンプ７側にオフセットした位置に設けられた張出部合わせ面１８ａを有している。この張出部合わせ面１８ａのうち第３軸受半部１７ｎ寄りの位置には、円弧面状に窪む第５軸受半部１８ｄがオイルポンプシャフト１１の回転軸線方向に沿って形成されている。また、張出部合わせ面１８ａの外側縁部付近には、第３キャップ部材４８に設けられた図示せぬ位置決め孔に圧入されるダウエルピン４９が設けられている。さらに、張出部合わせ面１８ａのうちダウエルピン４９と第５軸受半部１８ｄとの間の位置にはねじ穴１８ｆが設けられており、このねじ穴１８ｆには第３キャップ部材４８に設けられたボルト貫通孔４８ｄを介してボルト５０がねじ留めされることで、第３キャップ部材４８がバランサハウジング８に取付固定される。 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. Further, near the outer edge portion of 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. Further, 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.
　第３キャップ部材４８は、張出部１８の張出部合わせ面１８ａと対向する位置に、張出部合わせ面１８ａと突き合わされるオイルポンプシャフト側合わせ面４８ａを有している。このオイルポンプシャフト側合わせ面４８ａのうち第４軸受半部４５ｂ寄りの位置には、円弧面状に窪む第６軸受半部４８ｂが、オイルポンプシャフト１１の回転軸線方向に沿って形成されている。 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.
　また、第３キャップ部材４８のうち張出部合わせ面１８ａ上のねじ穴１８ｆと対向する位置には、ボルト５０が貫通するボルト貫通孔４８ｄが貫通形成されている。 Further, 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.
　［第６の実施形態の効果］
　第６の実施形態では、シャフト軸受部１６ｉおよび第１バランサ軸受部１６ｆは、バランサハウジング８と、該バランサハウジング８とは別体に形成された第３キャップ部材４８とによって構成され、第２バランサ軸受部２４ａは、バランサハウジング８に形成されている。 [Effect of the sixth embodiment]
In the sixth embodiment, 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.
　このため、半割状の第３および第５軸受半部１７ｎ，１８ｄ上に第１および第３ニードルベアリング２８，３９を設置した状態で第３キャップ部材４８を被せることにより、第１および第３ニードルベアリング２８，３９が同時に組付けされる。従って、バランサシャフト９およびオイルポンプシャフト１１を軸方向にスライドさせて第１および第３ニードルベアリング２８，３９を組み付ける場合に比べて、第１および第３ニードルベアリング２８，３９の組付を容易に行うことができる。 Therefore, 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.
　［第７の実施形態］
　図１０は、第７の実施形態のバランサ装置の分解斜視図である。 [7th Embodiment]
FIG. 10 is an exploded perspective view of the balancer device of the seventh embodiment.
　第１～第６の実施形態では、バランサシャフト９の回転軸線方向の一端部９ａから順に、第１バランサウエイト１０、第１バランサ軸受部１６ｆ、バランサギア３０が設けられていたが、第７の実施形態では、バランサシャフト９の回転軸線方向の一端部９ａから順に、第１バランサウエイト１０、バランサギア３０、第１バランサ軸受部１６ｆが設けられている。つまり、バランサギア３０は、バランサシャフト９の回転軸線の方向において、第１バランサウエイト１０よりも第１バランサ軸受部１６ｆに近い位置である近傍に配置されていればよい。換言すれば、バランサギア３０は、第１バランサ軸受部１６ｆから第１バランサウエイト１０までの距離よりも、第１バランサ軸受部１６ｆからバランサギア３０までの距離の方が短くなるように配置されていれば良い。 In the first to sixth embodiments, 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. In the 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. In other words, 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.
　また、第１バランサ軸受部１６ｆの視点で見れば、第１バランサ軸受部１６ｆは、バランサシャフト９の回転軸線方向において、第１バランサウエイト１０と共にバランサギア３０を挟む位置に配置されている。 Further, from the viewpoint of the first balancer bearing portion 16f, 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.
　また、上記の構成に合わせて、オイルポンプシャフト１１の回転軸線方向の一端部１１ｂから順に、中間ギア３５、第３ジャーナル部３８が設けられている。 Further, according to the above configuration, 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.
　［第７の実施形態の効果］
　第７の実施形態では、バランサシャフト９の回転軸線方向の一端部９ａから順に、第１バランサウエイト１０、バランサギア３０、第１バランサ軸受部１６ｆが設けられている。 [Effect of the seventh embodiment]
In 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.
　このため、バランサギア３０は、剛性が比較的高い第１バランサ軸受部１６ｆに対して、第１バランサウエイト１０よりも近い位置に配置されている。従って、バランサギア３０が第１バランサ軸受部１６ｆに対して第１バランサウエイト１０よりも遠い位置に配置される場合と比べて、第１バランサウエイト１０の回転時のバランサギア３０の径方向の振れを小さくし、バランサギア３０と中間ギア３５との歯打ち音の発生を抑制することができる。 Therefore, 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.
　また、本実施形態では、第１ジャーナル部２６よりも直径の大きいバランサギア３０が、第１ジャーナル部２６よりも外側に配置されている。 Further, in the present embodiment, the balancer gear 30 having a diameter larger than that of the first journal portion 26 is arranged outside the first journal portion 26.
　このため、バランサギア３０が第１ジャーナル部２６よりも内側に配置されている場合と比べて、バランサギア３０と中間ギア３５との位相合わせが容易となり、バランサ装置を容易に組み立てることができる。 Therefore, as compared with the case where 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.
　以上説明した実施形態では、第１、第２、第３ニードルベアリング２８，２９，３９は、本発明の意図を逸脱しない範囲で、その機能を同一とするローラベアリング、ボールベアリング等、他の転がり軸受、および滑り軸受と置き換えることも出来る。 In the embodiment described above, the 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.
　以上説明した実施形態中のバランサギア３０、中間ギア３５は、本発明の意図を逸脱しない範囲で、その機能を同一とするスパーギアと置き換えることもできる。 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.
　以上説明した実施形態に基づくバランサ装置としては、例えば以下に述べる態様のものが考えられる。 As the balancer device based on the embodiment described above, for example, the one described below can be considered.
　内燃機関に設けられるバランサ装置は、その一態様として、前記内燃機関に取り付けられたバランサハウジングと、前記バランサハウジングによって回転可能に支持されたバランサシャフトであって、前記バランサシャフトの回転軸線方向端部から順に、第１バランサウエイトと、バランサギアと、第２バランサウエイトとが設けられた前記バランサシャフトと、前記バランサシャフトと並行して配置され、前記バランサギアと噛み合う中間ギアが設けられたシャフトと、前記シャフトを回転可能に支持するシャフト軸受部と、前記第１バランサウエイトと前記第２バランサウエイトとの間に配置され、前記バランサシャフトを回転可能に支持し、前記バランサシャフトの回転軸線に対する径方向において、前記シャフト軸受部とオーバーラップする位置に設けられた第１バランサ軸受部であって、前記第１バランサウエイトと前記バランサギアとの間、および、前記第１バランサウエイトと共に前記バランサギアを挟む位置、の一方に設けられた前記第１バランサ軸受部と、前記バランサシャフトを回転可能に支持する第２バランサ軸受部と、を備える。 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.
　バランサ装置の好ましい態様において、前記シャフト軸受部および前記第１バランサ軸受部は、前記バランサハウジングとは別体に形成された軸受ハウジングに設けられている。 In a preferred embodiment of the balancer device, the shaft bearing portion and the first balancer bearing portion are provided in a bearing housing formed separately from the balancer housing.
　別の好ましい態様では、前記バランサ装置の態様のいずれかにおいて、前記軸受ハウジングの材料は、前記バランサハウジングの材料よりも単位体積重量が大きい。 In another preferred embodiment, in any of the aspects of the balancer device, the material of the bearing housing has a larger unit volume weight than the material of the balancer housing.
　別の好ましい態様では、前記バランサ装置の態様のいずれかにおいて、前記軸受ハウジングの材料は、前記バランサハウジングの材料よりも、前記バランサギアおよび前記中間ギアとの線膨張係数が近い。 In another preferred embodiment, in any of the aspects of the balancer device, 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.
　別の好ましい態様では、前記バランサ装置の態様のいずれかにおいて、前記シャフトは、該シャフトの回転軸線方向における第１端部および第２端部を有し、前記第１端部には、前記内燃機関からの回転力が伝達されるスプロケットが設けられ、前記第２端部には、オイルポンプが設けられている。 In another preferred embodiment, in any of the aspects of the balancer device, 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.
　別の好ましい態様では、前記バランサ装置の態様のいずれかにおいて、前記オイルポンプは、前記軸受ハウジングに取り付けられている。 In another preferred embodiment, in any of the aspects of the balancer device, the oil pump is attached to the bearing housing.
　別の好ましい態様では、前記バランサ装置の態様のいずれかにおいて、前記第１バランサ軸受部は、前記第１バランサウエイトと前記バランサギアとの間に設けられ、前記軸受ハウジングは、前記バランサシャフトの回転軸線方向において前記オイルポンプと対向するように設けられ、前記バランサギアおよび前記中間ギアを収容するギア収容部を備える。 In another preferred embodiment, in any of the aspects of the balancer device, 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.
　別の好ましい態様では、前記バランサ装置の態様のいずれかにおいて、前記バランサハウジングは、前記バランサシャフトが設けられる側の面に凹部を有し、前記軸受ハウジングは、前記凹部に嵌め合わされる凸部を有する。 In another preferred embodiment, in any of the aspects of the balancer device, 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. Have.
　別の好ましい態様では、前記バランサ装置の態様のいずれかにおいて、前記バランサハウジングの前記面には、前記凹部を挟んで両側に、前記軸受ハウジングとの位置決めに供する一対の位置決め孔が設けられており、前記軸受ハウジングにも、同様に、前記一対の位置決め孔が設けられており、前記バランサハウジングの位置決め孔および前記軸受ハウジングの位置決め孔の両方に嵌め合わされる一対のピンが設けられている。 In another preferred embodiment, in any of the aspects of the balancer device, 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. Similarly, 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.
　別の好ましい態様では、前記バランサ装置の態様のいずれかにおいて、前記第２バランサ軸受部は、前記バランサハウジングに形成されている。 In another preferred embodiment, in any of the aspects of the balancer device, the second balancer bearing portion is formed in the balancer housing.
　別の好ましい態様では、前記バランサ装置の態様のいずれかにおいて、前記軸受ハウジングに設けられた前記シャフト軸受部は、前記シャフトの回転軸線に対する周方向において、前記シャフトの全周を覆い、前記軸受ハウジングに設けられた前記第１バランサ軸受部は、前記バランサシャフトの回転軸線に対する周方向において、前記バランサシャフトの全周を覆い、前記第２バランサ軸受部は、前記バランサハウジングと、前記バランサハウジングと別体に形成された部材と、により形成されて、前記バランサシャフトの回転軸線に対する周方向において、前記バランサシャフトを覆う。 In another preferred embodiment, in any of the aspects of the balancer device, 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.
　別の好ましい態様では、前記バランサ装置の態様のいずれかにおいて、前記第１バランサ軸受部、前記第２バランサ軸受部および前記シャフト軸受部の少なくとも１つに、前記バランサシャフトを回転可能に支持する転がり軸受が設けられている。 In another preferred embodiment, in any of the aspects of the balancer device, rolling that rotatably supports the balancer shaft on at least one of the first balancer bearing portion, the second balancer bearing portion and the shaft bearing portion. Bearings are provided.
　別の好ましい態様では、前記バランサ装置の態様のいずれかにおいて、前記第１バランサウエイトは、オイルパン内のオイルの油面よりも上側に位置するように前記オイルパン内に配置されている。 In another preferred embodiment, in any of the aspects of the balancer device, 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.
　別の好ましい態様では、前記バランサ装置の態様のいずれかにおいて、前記シャフト軸受部および前記第１バランサ軸受部は、前記バランサハウジングに形成され、前記第２バランサ軸受部は、前記バランサハウジングと、該バランサハウジングとは別体に形成された第１キャップ部材とによって構成される。 In another preferred embodiment, in any of the aspects of the balancer device, 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.
　別の好ましい態様では、前記バランサ装置の態様のいずれかにおいて、前記シャフト軸受部および前記第２バランサ軸受部は、前記バランサハウジングに形成され、前記第１バランサ軸受部は、前記バランサハウジングと、該バランサハウジングとは別体に形成されたキャップ部材とによって構成されている。 In another preferred embodiment, in any of the aspects of the balancer device, 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.
　別の好ましい態様では、前記バランサ装置の態様のいずれかにおいて、前記シャフト軸受部、前記第１バランサ軸受部および前記第２バランサ軸受部は、前記バランサハウジングに形成されている。 In another preferred embodiment, in any of the aspects of the balancer device, the shaft bearing portion, the first balancer bearing portion and the second balancer bearing portion are formed in the balancer housing.
　別の好ましい態様では、前記バランサ装置の態様のいずれかにおいて、前記シャフト軸受部は、前記バランサハウジングに形成され、前記第１バランサ軸受部は、前記バランサハウジングと、該バランサハウジングとは別体に形成された第２キャップ部材とによって構成され、前記第２バランサ軸受部は、前記バランサハウジングと、該バランサハウジングとは別体に形成された第１キャップ部材とによって構成されている。 In another preferred embodiment, in any of the aspects of the balancer device, 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.
　別の好ましい態様では、前記バランサ装置の態様のいずれかにおいて、前記シャフト軸受部および前記第１バランサ軸受部は、前記バランサハウジングと、該バランサハウジングとは別体に形成された第３キャップ部材とによって構成され、前記第２バランサ軸受部は、前記バランサハウジングに形成されている。 In another preferred embodiment, in any of the aspects of the balancer device, 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.
　別の好ましい態様では、前記バランサ装置の態様のいずれかにおいて、前記シャフト軸受部は、前記バランサハウジングと、前記バランサハウジングと別体に形成された部材と、によって形成されて、前記シャフトの回転軸線に対する周方向において、前記シャフトを覆い、
　前記第１バランサ軸受部は、前記バランサハウジングと、前記バランサハウジングと別体に形成された部材と、によって形成されて、前記バランサシャフトの回転軸線に対する周方向において、前記バランサシャフトの全周を覆い、前記バランサハウジングに設けられた前記第２バランサ軸受部は、前記バランサシャフトの回転軸線に対する周方向において、前記バランサシャフトの全周を覆う。 In another preferred embodiment, in any of the aspects of the balancer device, 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.
　以上説明した実施例に基づく別のバランサ装置としては、例えば以下に述べる態様のものが考えられる。 As another balancer device based on the above-described embodiment, for example, the one described below can be considered.
　内燃機関に設けられるオイルポンプ付きバランサ装置は、その一態様として、前記内燃機関に取り付けられたバランサハウジングと、前記バランサハウジングによって回転可能に支持されたバランサシャフトであって、第１バランサウエイトと、バランサギアと、第２バランサウエイトとが設けられた前記バランサシャフトと、前記バランサシャフトと並行して配置され、前記バランサギアと噛み合う中間ギアが設けられたオイルポンプシャフトと、前記オイルポンプシャフトが挿入されたオイルポンプハウジングと、前記オイルポンプシャフトを回転可能に支持するシャフト軸受部と、前記オイルポンプハウジングが取り付けられ、前記シャフト軸受部が形成された軸受ハウジングと、前記第１バランサウエイトと前記バランサギアの間に配置され、前記バランサシャフトを回転可能に支持し、前記シャフト軸受部と全部またはその一部が同一部材において形成された第１バランサ軸受部であって、前記第１バランサウエイトと前記バランサギアとの間、および、前記第１バランサウエイトと共に前記バランサギアを挟む位置、の一方に設けられた前記第１バランサ軸受部と、前記バランサシャフトを回転可能に支持する第２バランサ軸受部と、を備える。 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. The oil pump housing, the shaft bearing portion that rotatably supports the oil pump shaft, the bearing housing to which the oil pump housing is attached and the shaft bearing portion is formed, the first balancer weight, and the balancer. 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.

Claims (20)

  1. 　内燃機関に設けられるバランサ装置であって、
    　前記内燃機関に取り付けられたバランサハウジングと、
    　前記バランサハウジングによって回転可能に支持されたバランサシャフトであって、前記バランサシャフトの回転軸線方向端部から順に、第１バランサウエイトと、バランサギアと、第２バランサウエイトとが設けられた前記バランサシャフトと、
    　前記バランサシャフトと並行して配置され、前記バランサギアと噛み合う中間ギアが設けられたシャフトと、
    　前記シャフトを回転可能に支持するシャフト軸受部と、
    　前記第１バランサウエイトと前記第２バランサウエイトとの間に配置され、前記バランサシャフトを回転可能に支持し、前記バランサシャフトの回転軸線に対する径方向において、前記シャフト軸受部とオーバーラップする位置に設けられた第１バランサ軸受部であって、前記第１バランサウエイトと前記バランサギアとの間、および、前記第１バランサウエイトと共に前記バランサギアを挟む位置、の一方に設けられた前記第１バランサ軸受部と、
    　前記バランサシャフトを回転可能に支持する第２バランサ軸受部と、
    　を備えたバランサ装置。     A balancer device installed in an internal combustion engine.
    The balancer housing attached to the internal combustion engine and
    A balancer shaft rotatably supported by the balancer housing, the balancer shaft provided with a first balancer weight, a balancer gear, and a second balancer weight in order from the end of the balancer shaft in the direction of the rotation axis. When,
    A shaft that is arranged in parallel with the balancer shaft and is provided with an intermediate gear that meshes with the balancer gear.
    A shaft bearing that rotatably supports the shaft and
    It is arranged between the first balancer weight and the second balancer weight, supports the balancer shaft rotatably, and is provided at a position overlapping the shaft bearing portion in the radial direction of the balancer shaft with respect to the rotation axis. The first balancer bearing portion 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. Department and
    A second balancer bearing that rotatably supports the balancer shaft,
    Balancer device equipped with.
  2. 　請求項１に記載のバランサ装置において、
    　前記シャフト軸受部および前記第１バランサ軸受部は、前記バランサハウジングとは別体に形成された軸受ハウジングに設けられていることを特徴とするバランサ装置。     In the balancer device according to claim 1,
    A balancer device, wherein the shaft bearing portion and the first balancer bearing portion are provided in a bearing housing formed separately from the balancer housing.
  3. 　請求項２に記載のバランサ装置において、
    　前記軸受ハウジングの材料は、前記バランサハウジングの材料よりも単位体積重量が大きいことを特徴とするバランサ装置。     In the balancer device according to claim 2.
    A balancer device characterized in that the material of the bearing housing has a larger unit volume weight than the material of the balancer housing.
  4. 　請求項２に記載のバランサ装置において、
    　前記軸受ハウジングの材料は、前記バランサハウジングの材料よりも、前記バランサギアおよび前記中間ギアとの線膨張係数が近いことを特徴とするバランサ装置。     In the balancer device according to claim 2.
    The balancer device is characterized in that the material of the bearing housing has a linear expansion coefficient closer to that of the balancer gear and the intermediate gear than that of the material of the balancer housing.
  5. 　請求項２に記載のバランサ装置において、
    　前記シャフトは、該シャフトの回転軸線方向における第１端部および第２端部を有し、
    　前記第１端部には、前記内燃機関からの回転力が伝達されるスプロケットが設けられ、
    　前記第２端部には、オイルポンプが設けられていることを特徴とするバランサ装置。     In the balancer device according to claim 2.
    The shaft has a first end and a second end in the direction of the rotation axis of the shaft.
    A sprocket to which the rotational force from the internal combustion engine is transmitted is provided at the first end portion.
    A balancer device characterized in that an oil pump is provided at the second end portion.
  6. 　請求項５に記載のバランサ装置において、
    　前記オイルポンプは、前記軸受ハウジングに取り付けられていることを特徴とするバランサ装置。     In the balancer device according to claim 5,
    The oil pump is a balancer device, characterized in that it is attached to the bearing housing.
  7. 　請求項６に記載のバランサ装置において、
    　前記第１バランサ軸受部は、前記第１バランサウエイトと前記バランサギアとの間に設けられ、
    　前記軸受ハウジングは、前記バランサシャフトの回転軸線方向において前記オイルポンプと対向するように設けられ、前記バランサギアおよび前記中間ギアを収容するギア収容部を備えることを特徴とするバランサ装置。     In the balancer device according to claim 6,
    The first balancer bearing portion is provided between the first balancer weight and the balancer gear.
    The bearing housing is provided so as to face the oil pump in the direction of the rotation axis of the balancer shaft, and includes a gear accommodating portion for accommodating the balancer gear and the intermediate gear.
  8. 　請求項２に記載のバランサ装置において、
    　前記バランサハウジングは、前記バランサシャフトが設けられる側の面に凹部を有し、
    　前記軸受ハウジングは、前記凹部に嵌め合わされる凸部を有することを特徴とするバランサ装置。     In the balancer device according to claim 2.
    The balancer housing has a recess on the surface on the side where the balancer shaft is provided.
    The bearing housing is a balancer device having a convex portion fitted into the concave portion.
  9. 　請求項８に記載のバランサ装置において、
    　前記バランサハウジングの前記面には、前記凹部を挟んで両側に、前記軸受ハウジングとの位置決めに供する一対の位置決め孔が設けられており、
    　前記軸受ハウジングにも、同様に、前記一対の位置決め孔が設けられており、
    　前記バランサハウジングの位置決め孔および前記軸受ハウジングの位置決め孔の両方に嵌め合わされる一対のピンが設けられたことを特徴とするバランサ装置。     In the balancer device according to claim 8.
    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.
    Similarly, the bearing housing is also provided with the pair of positioning holes.
    A balancer device characterized in that a pair of pins fitted into both the positioning hole of the balancer housing and the positioning hole of the bearing housing are provided.
  10. 　請求項２に記載のバランサ装置において、
    　前記第２バランサ軸受部は、前記バランサハウジングに形成されていることを特徴とするバランサ装置。     In the balancer device according to claim 2.
    The balancer device is characterized in that the second balancer bearing portion is formed in the balancer housing.
  11. 　請求項２に記載のバランサ装置において、
    　前記軸受ハウジングに設けられた前記シャフト軸受部は、前記シャフトの回転軸線に対する周方向において、前記シャフトの全周を覆い、
    　前記軸受ハウジングに設けられた前記第１バランサ軸受部は、前記バランサシャフトの回転軸線に対する周方向において、前記バランサシャフトの全周を覆い、
    　前記第２バランサ軸受部は、前記バランサハウジングと、前記バランサハウジングと別体に形成された部材と、により形成されて、前記バランサシャフトの回転軸線に対する周方向において、前記バランサシャフトを覆うことを特徴とするバランサ装置。     In the balancer device according to claim 2.
    The shaft bearing portion provided in the bearing housing covers the entire circumference of the shaft in the circumferential direction with respect to the rotation axis of the shaft.
    The first balancer bearing portion provided in the bearing housing covers the entire circumference of the balancer shaft in the circumferential direction with respect to the rotation axis of the balancer shaft.
    The second balancer bearing portion is formed by the balancer housing and a member formed separately from the balancer housing, and covers the balancer shaft in a circumferential direction with respect to the rotation axis of the balancer shaft. Balancer device.
  12. 　請求項１に記載のバランサ装置において、
    　前記第１バランサ軸受部、前記第２バランサ軸受部および前記シャフト軸受部の少なくとも１つに、前記バランサシャフトを回転可能に支持する転がり軸受が設けられたことを特徴とするバランサ装置。     In the balancer device according to claim 1,
    A balancer device characterized in that at least one of the first balancer bearing portion, the second balancer bearing portion, and the shaft bearing portion is provided with a rolling bearing that rotatably supports the balancer shaft.
  13. 　請求項１に記載のバランサ装置において、
    　前記第１バランサウエイトは、オイルパン内のオイルの油面よりも上側に位置するように前記オイルパン内に配置されていることを特徴とするバランサ装置。     In the balancer device according to claim 1,
    The balancer device is characterized in that 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.
  14. 　請求項１に記載のバランサ装置において、
    　前記シャフト軸受部および前記第１バランサ軸受部は、前記バランサハウジングに形成され、
    　前記第２バランサ軸受部は、前記バランサハウジングと、該バランサハウジングとは別体に形成された第１キャップ部材とによって構成されることを特徴とするバランサ装置。     In the balancer device according to claim 1,
    The shaft bearing portion and the first balancer bearing portion are formed in the balancer housing.
    The balancer device is characterized in that the second balancer bearing portion is composed of the balancer housing and a first cap member formed separately from the balancer housing.
  15. 　請求項１に記載のバランサ装置において、
    　前記シャフト軸受部および前記第２バランサ軸受部は、前記バランサハウジングに形成され、
    　前記第１バランサ軸受部は、前記バランサハウジングと、該バランサハウジングとは別体に形成されたキャップ部材とによって構成されていることを特徴とするバランサ装置。     In the balancer device according to claim 1,
    The shaft bearing portion and the second balancer bearing portion are formed in the balancer housing.
    The balancer device is characterized in that the first balancer bearing portion is composed of the balancer housing and a cap member formed separately from the balancer housing.
  16. 　請求項１に記載のバランサ装置において、
    　前記シャフト軸受部、前記第１バランサ軸受部および前記第２バランサ軸受部は、前記バランサハウジングに形成されていることを特徴とするバランサ装置。     In the balancer device according to claim 1,
    A balancer device, wherein the shaft bearing portion, the first balancer bearing portion, and the second balancer bearing portion are formed in the balancer housing.
  17. 　請求項１に記載のバランサ装置において、
    　前記シャフト軸受部は、前記バランサハウジングに形成され、
    　前記第１バランサ軸受部は、前記バランサハウジングと、該バランサハウジングとは別体に形成された第２キャップ部材とによって構成され、
    　前記第２バランサ軸受部は、前記バランサハウジングと、該バランサハウジングとは別体に形成された第１キャップ部材とによって構成されていることを特徴とするバランサ装置。     In the balancer device according to claim 1,
    The shaft bearing portion is formed in the balancer housing.
    The first balancer bearing portion is composed of the balancer housing and a second cap member formed separately from the balancer housing.
    The balancer device is characterized in that the second balancer bearing portion is composed of the balancer housing and a first cap member formed separately from the balancer housing.
  18. 　請求項１に記載のバランサ装置において、
    　前記シャフト軸受部および前記第１バランサ軸受部は、前記バランサハウジングと、該バランサハウジングとは別体に形成された第３キャップ部材とによって構成され、
    　前記第２バランサ軸受部は、前記バランサハウジングに形成されていることを特徴とするバランサ装置。     In the balancer device according to claim 1,
    The shaft bearing portion and the first balancer bearing portion are composed of the balancer housing and a third cap member formed separately from the balancer housing.
    The balancer device is characterized in that the second balancer bearing portion is formed in the balancer housing.
  19. 　請求項１に記載のバランサ装置において、
    　前記シャフト軸受部は、前記バランサハウジングと、前記バランサハウジングと別体に形成された部材と、によって形成されて、前記シャフトの回転軸線に対する周方向において、前記シャフトを覆い、
    　前記第１バランサ軸受部は、前記バランサハウジングと、前記バランサハウジングと別体に形成された部材と、によって形成されて、前記バランサシャフトの回転軸線に対する周方向において、前記バランサシャフトの全周を覆い、
    　前記バランサハウジングに設けられた前記第２バランサ軸受部は、前記バランサシャフトの回転軸線に対する周方向において、前記バランサシャフトの全周を覆うことを特徴とするバランサ装置。     In the balancer device according to claim 1,
    The shaft bearing portion is formed by the balancer housing and a member formed separately from the balancer housing, and covers the shaft in a circumferential direction with respect to the rotation axis of the shaft.
    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 is a balancer device that covers the entire circumference of the balancer shaft in a circumferential direction with respect to the rotation axis of the balancer shaft.
  20. 　内燃機関に設けられるオイルポンプ付きバランサ装置であって、
    　前記内燃機関に取り付けられたバランサハウジングと、
    　前記バランサハウジングによって回転可能に支持されたバランサシャフトであって、第１バランサウエイトと、バランサギアと、第２バランサウエイトとが設けられた前記バランサシャフトと、
    　前記バランサシャフトと並行して配置され、前記バランサギアと噛み合う中間ギアが設けられたオイルポンプシャフトと、
    　前記オイルポンプシャフトが挿入されたオイルポンプハウジングと、
    　前記オイルポンプシャフトを回転可能に支持するシャフト軸受部と、
    　前記オイルポンプハウジングが取り付けられ、前記シャフト軸受部が形成された軸受ハウジングと、
    　前記第１バランサウエイトと前記第２バランサウエイトの間に配置され、前記バランサシャフトを回転可能に支持し、前記シャフト軸受部と全部またはその一部が同一部材において形成された第１バランサ軸受部であって、前記第１バランサウエイトと前記バランサギアとの間、および、前記第１バランサウエイトと共に前記バランサギアを挟む位置、の一方に設けられた前記第１バランサ軸受部と、
    　前記バランサシャフトを回転可能に支持する第２バランサ軸受部と、
    　を備えたオイルポンプ付きバランサ装置。     A balancer device with an oil pump installed in an internal combustion engine.
    The balancer housing attached to the internal combustion engine and
    A balancer shaft rotatably supported by the balancer housing, the balancer shaft provided with a first balancer weight, a balancer gear, and a second balancer weight.
    An oil pump shaft arranged in parallel with the balancer shaft and provided with an intermediate gear that meshes with the balancer gear.
    The oil pump housing into which the oil pump shaft is inserted and
    A shaft bearing that rotatably supports the oil pump shaft,
    A bearing housing to which the oil pump housing is attached and the shaft bearing portion is formed,
    A first balancer bearing portion that is arranged between the first balancer weight and the second balancer weight, rotatably supports the balancer shaft, and is formed in the same member as the shaft bearing portion in whole or in part. The first balancer bearing portion 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.
    A second balancer bearing that rotatably supports the balancer shaft,
    Balancer device with oil pump.
PCT/JP2021/006996 2020-03-18 2021-02-25 Balancer device and balancer device provided with oil pump WO2021187033A1 (en)

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5458501U (en) * 1977-09-30 1979-04-23
JP2000297845A (en) * 1999-04-14 2000-10-24 Isuzu Motors Ltd Balancer shaft for internal combustion engine
JP2001082165A (en) * 1999-09-09 2001-03-27 Daihatsu Motor Co Ltd Vibration reducing device for engine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5458501U (en) * 1977-09-30 1979-04-23
JP2000297845A (en) * 1999-04-14 2000-10-24 Isuzu Motors Ltd Balancer shaft for internal combustion engine
JP2001082165A (en) * 1999-09-09 2001-03-27 Daihatsu Motor Co Ltd Vibration reducing device for engine

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